64 FR 54141, Oct. 5, 1999, unless otherwise noted.
This part establishes the regulations for the implementation of provisions relating to commercial and industrial equipment in Part B of Title III of the Energy Policy and Conservation Act (42 U.S.C. 6291-6309) and in Part C of Title III of the Energy Policy and Conservation Act (42 U.S.C. 6311-6317), which establishes an energy conservation program for certain commercial and industrial equipment.
[70 FR 60414, Oct. 18, 2005]
The following definitions apply for purposes of this part. Any words or terms not defined in this Section or elsewhere in this part shall be defined as provided in Section 340 of the Act.
Act means the Energy Policy and Conservation Act of 1975, as amended, 42 U.S.C. 6291-6316.
Alternate efficiency determination method or AEDM means a method of calculating the efficiency of a commercial HVAC and WH product, in terms of the descriptor used in or under section 342(a) of the Act to state the energy conservation standard for that product.
Btu means British thermal unit, which is the quantity of heat required to raise the temperature of one pound of water by one degree Fahrenheit.
Commercial HVAC & WH product means any small, large, or very large commercial package air-conditioning and heating equipment (as defined in § 431.92), packaged terminal air conditioner (as defined in § 431.92), packaged terminal heat pump (as defined in § 431.92), single package vertical air conditioner (as defined in § 431.92), single package vertical heat pump (as defined in § 431.92), computer room air conditioner (as defined in § 431.92), variable refrigerant flow multi-split air conditioner (as defined in § 431.92), variable refrigerant flow multi-split heat pump (as defined in § 431.92), unitary dedicated outdoor air system (as defined in § 431.92), commercial packaged boiler (as defined in § 431.82), hot water supply boiler (as defined in § 431.102), commercial warm air furnace (as defined in § 431.72), instantaneous water heater (as defined in § 431.102), storage water heater (as defined in § 431.102), or unfired hot water storage tank (as defined in § 431.102).
Covered equipment means any electric motor, as defined in § 431.12; commercial heating, ventilating, and air conditioning, and water heating product (HVAC & WH product), as defined in § 431.172; commercial refrigerator, freezer, or refrigerator-freezer, as defined in § 431.62; automatic commercial ice maker, as defined in § 431.132; commercial clothes washer, as defined in § 431.152; distribution transformer, as defined in § 431.192; illuminated exit sign, as defined in § 431.202; traffic signal module or pedestrian module, as defined in § 431.222; unit heater, as defined in § 431.242; commercial prerinse spray valve, as defined in § 431.262; mercury vapor lamp ballast, as defined in § 431.282; refrigerated bottled or canned beverage vending machine, as defined in § 431.292; walk-in cooler and walk-in freezer, as defined in § 431.302; metal halide ballast and metal halide lamp fixture, as defined in § 431.322.
DOE or the Department means the U.S. Department of Energy.
Energy conservation standard means any standards meeting the definitions of that term in 42 U.S.C. 6291(6) and 42 U.S.C. 6311(18) as well as any other water conservation standards and design requirements found in this part or parts 430 or 431.
EPCA means the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6316.
Flue loss means the sum of the sensible heat and latent heat above room temperature of the flue gases leaving the appliance.
Gas means propane or natural gas as defined by the Federal Power Commission.
Import means to import into the customs territory of the United States.
Independent laboratory means a laboratory or test facility not controlled by, affiliated with, having financial ties with, or under common control with the manufacturer or distributor of the covered equipment being evaluated.
Industrial equipment means an article of equipment, regardless of whether it is in fact distributed in commerce for industrial or commercial use, of a type which:
(1) In operation consumes, or is designed to consume energy;
(2) To any significant extent, is distributed in commerce for industrial or commercial use; and
(3) Is not a “covered product” as defined in Section 321(2) of EPCA, 42 U.S.C. 6291(2), other than a component of a covered product with respect to which there is in effect a determination under Section 341(c) of EPCA, 42 U.S.C. 6312(c).
ISO means International Organization for Standardization.
Manufacture means to manufacture, produce, assemble, or import.
Manufacturer means any person who manufactures industrial equipment, including any manufacturer of a commercial packaged boiler.
Manufacturer's model number means the identifier used by a manufacturer to uniquely identify the group of identical or essentially identical commercial equipment to which a particular unit belongs. The manufacturer's model number typically appears on equipment nameplates, in equipment catalogs and in other product advertising literature.
Private labeler means, with respect to any product covered under this part, an owner of a brand or trademark on the label of a covered product which bears a private label. A covered product bears a private label if:
(1) Such product (or its container) is labeled with the brand or trademark of a person other than a manufacturer of such product;
(2) The person with whose brand or trademark such product (or container) is labeled has authorized or caused such product to be so labeled; and
(3) The brand or trademark of a manufacturer of such product does not appear on such label.
Secretary means the Secretary of Energy.
State means a State, the District of Columbia, Puerto Rico, or any territory or possession of the United States.
State regulation means a law or regulation of a State or political subdivision thereof.
[69 FR 61923, Oct. 21, 2004, as amended at 71 FR 71369, Dec. 8, 2006; 74 FR 12071, Mar. 23, 2009; 75 FR 666, Jan. 5, 2010; 76 FR 12503, Mar. 7, 2011; 77 FR 28987, May 16, 2012; 79 FR 26601, May 9, 2014; 87 FR 45197, July 27, 2022; 89 FR 82071, Oct. 9, 2024; 90 FR 43384, Sept. 9, 2025]
Requests for error corrections pertaining to an energy conservation standard rule for commercial or industrial equipment shall follow those procedures and provisions detailed in 10 CFR 430.5 of this chapter.
[81 FR 57758, Aug. 24, 2016]
The procedures, interpretations, and policies for consideration of new or revised energy conservation standards and test procedures set forth in appendix A to subpart C of part 430 of this chapter shall apply to the consideration of new or revised energy conservation standards and test procedures considered for adoption under this part.
[85 FR 8711, Feb. 14, 2020]
69 FR 61923, Oct. 21, 2004, unless otherwise noted.
This subpart contains energy conservation requirements for electric motors. It contains test procedures that EPCA requires DOE to prescribe, related requirements, energy conservation standards prescribed by EPCA, labeling rules, and compliance procedures. It also identifies materials incorporated by reference in this part. This subpart does not cover “small electric motors,” which are addressed in subpart X of this part. This subpart does not cover electric motors that are “dedicated-purpose pool pump motors,” which are addressed in subpart Z of this part.
[77 FR 26633, May 4, 2012, as amended at 86 FR 40774, July 29, 2021]
The following definitions apply for purposes of this subpart, and of subparts U and V of this part. Any words or terms not defined in this Section or elsewhere in this part shall be defined as provided in Section 340 of the Act.
Accreditation means recognition by an accreditation body that a laboratory is competent to test the efficiency of electric motors according to the scope and procedures given in IEEE 112-2017 Test Method B, CSA C390-10, or IEC 60034-2-1:2014 Method 2-1-1B (incorporated by reference, see § 431.15).
Accreditation body means an organization or entity that conducts and administers an accreditation system and grants accreditation.
Accreditation system means a set of requirements to be fulfilled by a testing laboratory, as well as rules of procedure and management, that are used to accredit laboratories.
Accredited laboratory means a testing laboratory to which accreditation has been granted.
Air-over electric motor means an electric motor that does not reach thermal equilibrium (i.e., thermal stability), during a rated load temperature test according to section 2 of appendix B, without the application of forced cooling by a free flow of air from an external device not mechanically connected to the motor within the motor enclosure.
Alternative efficiency determination method or AEDM means, with respect to an electric motor, a method of calculating the total power loss and average full load efficiency.
Average full load efficiency means the arithmetic mean of the full load efficiencies of a population of electric motors of duplicate design, where the full load efficiency of each motor in the population is the ratio (expressed as a percentage) of the motor's useful power output to its total power input when the motor is operated at its full rated load, rated voltage, and rated frequency.
Basic model means all units of electric motors manufactured by a single manufacturer, that are within the same equipment class, have electrical characteristics that are essentially identical, and do not have any differing physical or functional characteristics that affect energy consumption or efficiency.
Brake electric motor means a motor that contains a dedicated mechanism for speed reduction, such as a brake, either within or external to the motor enclosure
Certificate of conformity means a document that is issued by a certification program, and that gives written assurance that an electric motor complies with the energy efficiency standard applicable to that motor, as specified in § 431.25.
Certification program means a certification system that determines conformity by electric motors with the energy efficiency standards prescribed by and pursuant to the Act.
Certification system means a system, that has its own rules of procedure and management, for giving written assurance that a product, process, or service conforms to a specific standard or other specified requirements, and that is operated by an entity independent of both the party seeking the written assurance and the party providing the product, process or service.
Component set means a combination of motor parts that require the addition of more than two endshields (and their associated bearings) to create an operable motor. These parts may consist of any combination of a stator frame, wound stator, rotor, shaft, or endshields. For the purpose of this definition, the term “operable motor” means an electric motor engineered for performing in accordance with nameplate ratings.
CSA means Canadian Standards Association.
Definite purpose electric motor means any electric motor that cannot be used in most general purpose applications and is designed either:
(1) To standard ratings with standard operating characteristics or standard mechanical construction for use under service conditions other than usual, such as those specified in NEMA MG 1-2016, Paragraph 14.3, “Unusual Service Conditions,” (incorporated by reference, see § 431.15); or
(2) For use on a particular type of application.
Definite purpose motor means any electric motor that cannot be used in most general purpose applications and is designed either:
(1) To standard ratings with standard operating characteristics or standard mechanical construction for use under service conditions other than usual, such as those specified in NEMA MG 1-2016, Paragraph 14.3, “Unusual Service Conditions,” (incorporated by reference, see § 431.15); or
(2) For use on a particular type of application.
Electric motor means a machine that converts electrical power into rotational mechanical power.
Electric motor with encapsulated windings means an electric motor capable of passing the conformance test for water resistance described in NEMA MG 1-2016, Paragraph 12.62 (incorporated by reference, see § 431.15).
Electric motor with moisture resistant windings means an electric motor that is capable of passing the conformance test for moisture resistance generally described in NEMA MG 1-2016, paragraph 12.63 (incorporated by reference, see § 431.15).
Electric motor with sealed windings means an electric motor capable of passing the conformance test for water resistance described in NEMA MG 1-2016, paragraph 12.62 (incorporated by reference, see § 431.15).
Enclosed motor means an electric motor so constructed as to prevent the free exchange of air between the inside and outside of the case but not sufficiently enclosed to be termed airtight.
Equipment class means one of the combinations of an electric motor's horsepower (or standard kilowatt equivalent), number of poles, and open or enclosed construction, with respect to a category of electric motor for which § 431.25 prescribes nominal full-load efficiency standards.
Fire pump electric motor means an electric motor, including any IEC-equivalent, that meets the requirements of section 9.5 of NFPA 20 (incorporated by reference, see § 431.15).
General purpose electric motor means any electric motor that is designed in standard ratings with either:
(1) Standard operating characteristics and mechanical construction for use under usual service conditions, such as those specified in NEMA MG 1-2016, paragraph 14.2, “Usual Service Conditions,” (incorporated by reference, see § 431.15) and without restriction to a particular application or type of application; or
(2) Standard operating characteristics or standard mechanical construction for use under unusual service conditions, such as those specified in NEMA MG 1-2016, paragraph 14.3, “Unusual Service Conditions,” (incorporated by reference, see § 431.15) or for a particular type of application, and which can be used in most general purpose applications.
General purpose electric motor (subtype I) means a general purpose electric motor that:
(1) Is a single-speed, induction motor;
(2) Is rated for continuous duty (MG1) operation or for duty type S1 (IEC);
(3) Contains a squirrel-cage (MG1) or cage (IEC) rotor;
(4) Has foot-mounting that may include foot-mounting with flanges or detachable feet;
(5) Is built in accordance with NEMA T-frame dimensions or their IEC metric equivalents, including a frame size that is between two consecutive NEMA frame sizes or their IEC metric equivalents;
(6) Has performance in accordance with NEMA Design A (MG1) or B (MG1) characteristics or equivalent designs such as IEC Design N (IEC);
(7) Operates on polyphase alternating current 60-hertz sinusoidal power, and:
(i) Is rated at 230 or 460 volts (or both) including motors rated at multiple voltages that include 230 or 460 volts (or both), or
(ii) Can be operated on 230 or 460 volts (or both); and
(8) Includes, but is not limited to, explosion-proof construction.
References to “MG1” above refer to NEMA Standards Publication MG 1-2016 (incorporated by reference in § 431.15). References to “IEC” above refer to IEC 60034-1, 60034-12:2016, 60050-411, and 60072-1 (incorporated by reference in § 431.15), as applicable.
General purpose electric motor (subtype II) means any general purpose electric motor that incorporates design elements of a general purpose electric motor (subtype I) but, unlike a general purpose electric motor (subtype I), is configured in one or more of the following ways:
(1) Is built in accordance with NEMA U-frame dimensions as described in NEMA MG 1-1967 (incorporated by reference, see § 431.15) or in accordance with the IEC metric equivalents, including a frame size that is between two consecutive NEMA frame sizes or their IEC metric equivalents;
(2) Has performance in accordance with NEMA Design C characteristics as described in MG1 or an equivalent IEC design(s) such as IEC Design H;
(3) Is a close-coupled pump motor;
(4) Is a footless motor;
(5) Is a vertical solid shaft normal thrust motor (as tested in a horizontal configuration) built and designed in a manner consistent with MG1;
(6) Is an eight-pole motor (900 rpm); or
(7) Is a polyphase motor with a voltage rating of not more than 600 volts, is not rated at 230 or 460 volts (or both), and cannot be operated on 230 or 460 volts (or both).
With the exception of the NEMA Motor Standards MG1-1967 (incorporated by reference in § 431.15), references to “MG1” above refer to NEMA MG 1-2016 (incorporated by reference in § 431.15). References to “IEC” above refer to IEC 60034-1, 60034-12, 60050-411, and 60072-1 (incorporated by reference in § 431.15), as applicable.
IEC means the International Electrotechnical Commission.
IEC Design H motor means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of direct-on-line starting
(4) Has 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 160 kW at a frequency of 60 Hz; and
(6) Conforms to Sections 9.1, 9.2, and 9.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design HE means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of direct-on-line starting;
(4) Has 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 160 kW at a frequency of 60 Hz; and
(6) Conforms to section 9.1, Table 3, and Section 9.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design HEY means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of star-delta starting;
(4) Has 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 160 kW at a frequency of 60 Hz; and
(6) Conforms to section 5.7, Table 3 and Section 9.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design HY means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of star-delta starting;
(4) Has 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 160 kW at a frequency of 60 Hz; and
(6) Conforms to Section 5.7, Section 9.2 and Section 9.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design N motor means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of direct-on-line starting;
(4) Has 2, 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 1600 kW at a frequency of 60 Hz; and
(6) Conforms to Sections 6.1, 6.2, and 6.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for torque characteristics, locked rotor apparent power, and starting requirements, respectively. If a motor has an increased safety designation of type “e,”, the locked rotor apparent power shall be in accordance with the appropriate values specified in IEC 60079-7:2015 (incorporated by reference, see § 431.15).
IEC Design NE means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of direct-on-line starting;
(4) Has 2, 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 1600 kW at a frequency of 60 Hz; and
(6) Conforms to section 6.1, Table 3 and Section 6.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design NEY means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of star-delta starting;
(4) Has 2, 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 1600 kW at a frequency of 60 Hz; and
(6) Conforms to section 5.4, Table 3 and Section 6.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEC Design NY means an electric motor that:
(1) Is an induction motor designed for use with three-phase power;
(2) Contains a cage rotor;
(3) Is capable of star-delta starting;
(4) Has 2, 4, 6, or 8 poles;
(5) Is rated from 0.12 kW to 1600 kW at a frequency of 60 Hz; and
(6) Conforms to Section 5.4, Section 6.2 and Section 6.3 of the IEC 60034-12:2016 (incorporated by reference, see § 431.15) specifications for starting torque, locked rotor apparent power, and starting requirements, respectively.
IEEE means the Institute of Electrical and Electronics Engineers, Inc.
Immersible electric motor means an electric motor primarily designed to operate continuously in free-air, but is also capable of temporarily withstanding complete immersion in liquid for a continuous period of no less than 30 minutes.
Inverter means an electronic device that converts an input AC or DC power into a controlled output AC or DC voltage or current. An inverter may also be called a converter.
Inverter-capable electric motor means an electric motor designed for direct online starting and is suitable for operation on an inverter without special filtering.
Inverter-only electric motor means an electric motor designed specifically for operation fed by an inverter with a temperature rise within the specified insulation thermal class or thermal limits.
Liquid-cooled electric motor means a motor that is cooled by liquid circulated using a designated cooling apparatus such that the liquid or liquid-filled conductors come into direct contact with the parts of the motor but is not submerged in a liquid during operation.
NEMA means the National Electrical Manufacturers Association.
NEMA Design A motor means a squirrel-cage motor that:
(1) Is designed to withstand full-voltage starting and developing locked-rotor torque as shown in NEMA MG 1-2016, paragraph 12.38.1 (incorporated by reference, see § 431.15);
(2) Has pull-up torque not less than the values shown in NEMA MG 1-2016, paragraph 12.40.1;
(3) Has breakdown torque not less than the values shown in NEMA MG 1-2016, paragraph 12.39.1;
(4) Has a locked-rotor current higher than the values shown in NEMA MG 1-2016, Paragraph 12.35.2 for 60 hertz and NEMA MG 1-2016, Paragraph 12.35.4 for 50 hertz; and
(5) Has a slip at rated load of less than 5 percent for motors with fewer than 10 poles.
NEMA Design B motor means a squirrel-cage motor that is:
(1) Designed to withstand full-voltage starting;
(2) Develops locked-rotor, breakdown, and pull-up torques adequate for general application as specified in Sections 12.38, 12.39 and 12.40 of NEMA MG 1-2016 (incorporated by reference, see § 431.15);
(3) Draws locked-rotor current not to exceed the values shown in Section 12.35.2 for 60 hertz and 12.35.4 for 50 hertz of NEMA MG 1-2016; and
(4) Has a slip at rated load of less than 5 percent for motors with fewer than 10 poles.
NEMA Design C motor means a squirrel-cage motor that:
(1) Is designed to withstand full-voltage starting and developing locked-rotor torque for high-torque applications up to the values shown in NEMA MG 1-2016, paragraph 12.38.2 (incorporated by reference, see § 431.15);
(2) Has pull-up torque not less than the values shown in NEMA MG 1-2016, paragraph 12.40.2;
(3) Has breakdown torque not less than the values shown in NEMA MG 1-2016, paragraph 12.39.2;
(4) Has a locked-rotor current not to exceed the values shown in NEMA MG 1-2016, paragraphs 12.35.2 for 60 hertz and 12.35.4 for 50 hertz; and
(5) Has a slip at rated load of less than 5 percent.
Nominal full-load efficiency means, with respect to an electric motor, a representative value of efficiency selected from the “nominal efficiency” column of Table 12-10, NEMA MG 1-2016, (incorporated by reference, see § 431.15), that is not greater than the average full-load efficiency of a population of motors of the same design.
Open motor means an electric motor having ventilating openings which permit passage of external cooling air over and around the windings of the machine.
Partial electric motor means an assembly of motor components necessitating the addition of no more than two endshields, including bearings, to create an electric motor capable of operation in accordance with the applicable nameplate ratings.
Rated frequency means 60 Hz and corresponds to the frequency of the electricity supplied either:
(1) Directly to the motor, in the case of electric motors capable of operating without an inverter; or
(2) To the inverter in the case on inverter-only electric motors.
Rated load (or full-load, full rated load, or rated full-load) means the rated output power of an electric motor.
Rated voltage means the input voltage of a motor or inverter used when making representations of the performance characteristics of a given electric motor and selected by the motor's manufacturer to be used for testing the motor's efficiency.
Special purpose motor means any motor, other than a general purpose motor or definite purpose motor, which has special operating characteristics or special mechanical construction, or both, designed for a particular application.
Special purpose electric motor means any electric motor, other than a general purpose motor or definite electric purpose motor, which has special operating characteristics or special mechanical construction, or both, designed for a particular application.
Specialized frame size means an electric motor frame size for which the rated output power of the motor exceeds the motor frame size limits specified for standard frame size. Specialized frame sizes have maximum diameters corresponding to the following NEMA Frame Sizes:
| Motor horsepower/standard kilowatt equivalent | Maximum NEMA frame diameters | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 48 | 48 | 48 | 48 | 48 | 140 | 140 | |
| 1.5/1.1 | 48 | 48 | 48 | 48 | 140 | 140 | 140 | 140 |
| 2/1.5 | 48 | 48 | 48 | 48 | 140 | 140 | 180 | 180 |
| 3/2.2 | 140 | 48 | 140 | 140 | 180 | 180 | 180 | 180 |
| 5/3.7 | 140 | 140 | 140 | 140 | 180 | 180 | 210 | 210 |
| 7.5/5.5 | 180 | 140 | 180 | 180 | 210 | 210 | 210 | 210 |
| 10/7.5 | 180 | 180 | 180 | 180 | 210 | 210 | ||
| 15/11 | 210 | 180 | 210 | 210 | ||||
| 20/15 | 210 | 210 | 210 | 210 | ||||
Standard frame size means a motor frame size that aligns with the specifications in NEMA MG 1-2016, section 13.2 for open motors, and NEMA MG 1-2016, section 13.3 for enclosed motors (incorporated by reference, see § 431.15).
Submersible electric motor means an electric motor that:
(1) Is intended to operate continuously only while submerged in liquid;
(2) Is capable of operation while submerged in liquid for an indefinite period of time; and
(3) Has been sealed to prevent ingress of liquid from contacting the motor's internal parts.
Total power loss means that portion of the energy used by an electric motor not converted to rotational mechanical power, expressed in percent.
Totally enclosed non-ventilated (TENV) electric motor means an electric motor that is built in a frame-surface cooled, totally enclosed configuration that is designed and equipped to be cooled only by free convection.
[69 FR 61923, Oct. 21, 2004, as amended at 74 FR 12071, Mar. 23, 2009; 77 FR 26633, May 4, 2012; 78 FR 75993, Dec. 13, 2013; 79 FR 31009, May 29, 2014; 86 FR 21, Jan. 4, 2021; 87 FR 63654, Oct. 19, 2022; 87 FR 64689, Oct. 26, 2022; 88 FR 36150, Sept. 29, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the U.S. Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the sources in the following paragraphs:
(b) CSA. Canadian Standards Association, Sales Department, 5060 Spectrum Way, Suite 100, Mississauga, Ontario, L4W 5N6, Canada; (800) 463-6727; www.shopcsa.ca/onlinestore/welcome.asp.
(1) CSA C390-10 (reaffirmed 2019), (“CSA C390-10”), Test methods, marking requirements, and energy efficiency levels for three-phase induction motors, including Updates No. 1 through 3, Revised January 2020; IBR approved for § 431.12 and appendix B to this subpart.
(2) CSA C747-09 (reaffirmed 2019) (“CSA C747-09”), Energy efficiency test methods for small motors, including Update No. 1 (August 2016), October 2009; IBR approved for appendix B to this subpart.
(c) IEC. International Electrotechnical Commission Central Office, 3, rue de Varembé, P.O. Box 131, CH-1211 GENEVA 20, Switzerland; + 41 22 919 02 11; webstore.iec.ch.
(1) IEC 60034-1 Edition 12.0 2010-02, (“IEC 60034-1”), Rotating Electrical Machines, Part 1: Rating and Performance, February 2010, IBR approved as follows: section 4: Duty, clause 4.2.1 and Figure 1, IBR approved for § 431.12.
(2) IEC 60034-1, Edition 12.0 2010-02, (“IEC 60034-1:2010”), Rotating Electrical Machines—Part 1: Rating and Performance, IBR approved for appendix B to this subpart.
(3) IEC 60034-2-1:2014, Rotating electrical machines—Part 2-1: Standard methods for determining losses and efficiency from tests (excluding machines for traction vehicles), Edition 2.0, 2014-06; IBR approved for § 431.12 and appendix B to this subpart.
(4) IEC 60034-12:2016, Rotating electrical machines, Part 12: Starting performance of single-speed three-phase cage induction motors, Edition 3.0, 2016-11; IBR approved for § 431.12.
(5) IEC 60050-411, International Electrotechnical Vocabulary Chapter 411: Rotating machines, 1996, IBR approved as follows: sections 411-33-07 and 411-37-26, IBR approved for § 431.12.
(6) IEC 60051-1:2016, Edition 6.0 2016-02, (“IEC 60051-1:2016”), Direct acting indicating analogue electrical measuring instruments and their accessories—Part 1: Definitions and general requirements common to all parts, IBR approved for appendix B to this subpart.
(7) IEC 60072-1, Dimensions and Output Series for Rotating Electrical Machines—Part 1: Frame numbers 56 to 400 and flange numbers 55 to 1080, Sixth edition, 1991-02; IBR approved as follows: clauses 2, 3, 4.1, 6.1, 7, and 10, and Tables 1, 2 and 4; IBR approved for § 431.12 and appendix B to this subpart.
(8) IEC 60079-7:2015, Explosive atmospheres—Part 7: Equipment protection by increased safety “e”, Edition 5.0, 2015-06; IBR approved for § 431.12.
(9) IEC 61800-9-2:2017, Adjustable speed electrical power drive systems—Part 9-2: Ecodesign for power drive systems, motor starters, power electronics and their driven applications—Energy efficiency indicators for power drive systems and motor starters, Edition 1.0, 2017-03; IBR approved for appendix B to this subpart.
(d) IEEE. Institute of Electrical and Electronics Engineers, Inc., 445 Hoes Lane, P.O. Box 1331, Piscataway, NJ 08855-1331; (800) 678-IEEE (4333); www.ieee.org/web/publications/home/index.html.
(1) IEEE Std 112-2017 (“IEEE 112-2017”), IEEE Standard Test Procedure for Polyphase Induction Motors and Generators, approved December 6, 2017; IBR approved for § 431.12 and appendix B to this subpart.
(2) IEEE Std 114-2010 (“IEEE 114-2010”), Test Procedure for Single-Phase Induction Motors, December 23, 2010; IBR approved for appendix B to this subpart.
(e) NEMA. National Electrical Manufacturers Association, 1300 North 17th Street, Suite 1752, Rosslyn, Virginia 22209; (703) 841-3200; www.nema.org/.
(1) ANSI/NEMA MG 1-2016 (Revision 1, 2018) (“NEMA MG 1-2016”), Motors and Generators, ANSI-approved June 15, 2021; IBR approved for § 431.12 and appendix B to this subpart.
(f) NFPA. National Fire Protection Association, 1 Batterymarch Park, Quincy, MA 02169-7471; (617) 770-3000; www.nfpa.org/.
(1) NFPA 20, Standard for the Installation of Stationary Pumps for Fire Protection, 2022 Edition, ANSI-approved April 8, 2021. IBR approved for § 431.12.
(2) [Reserved]
[77 FR 26634, May 4, 2012, as amended at 78 FR 75994, Dec. 13, 2013; 86 FR 21, Jan. 4, 2021; 87 FR 63656, Oct. 19, 2022]
For purposes of 10 CFR part 431 and EPCA, the test procedures for measuring the energy efficiency of an electric motor shall be the test procedures specified in appendix B to this subpart B.
(a) Testing pursuant to § 431.17(a)(5)(ii) must be conducted in an accredited laboratory for which the accreditation body was:
(1) The National Institute of Standards and Technology/National Voluntary Laboratory Accreditation Program (NIST/NVLAP); or
(2) A laboratory accreditation body having a mutual recognition arrangement with NIST/NVLAP; or
(3) An organization classified by the Department, pursuant to § 431.19, as an accreditation body.
(b) NIST/NVLAP is under the auspices of the National Institute of Standards and Technology (NIST)/National Voluntary Laboratory Accreditation Program (NVLAP), which is part of the U.S. Department of Commerce. NIST/NVLAP accreditation is granted on the basis of conformance with criteria published in 15 CFR part 285. The National Voluntary Laboratory Accreditation Program, “Procedures and General Requirements,” NIST Handbook 150-10, April 2020, (referenced for guidance only, see § 429.3 of this subchapter) present the technical requirements of NVLAP for the Efficiency of Electric Motors field of accreditation. This handbook supplements NIST Handbook 150, National Voluntary Laboratory Accreditation Program “Procedures and General Requirements,” which contains 15 CFR part 285 plus all general NIST/NVLAP procedures, criteria, and policies. Information regarding NIST/NVLAP and its Efficiency of Electric Motors Program (EEM) can be obtained from NIST/NVLAP, 100 Bureau Drive, Mail Stop 2140, Gaithersburg, MD 20899-2140, (301) 975-4016 (telephone), or (301) 926-2884 (fax).
[69 FR 61923, Oct. 21, 2004, as amended at 77 FR 26635, May 4, 2012; 87 FR 63657, Oct. 19, 2022]
(a) Except as provided for fire pump electric motors in paragraph (b) of this section, each general purpose electric motor (subtype I) with a power rating of 1 horsepower or greater, but not greater than 200 horsepower, including a NEMA Design B or an equivalent IEC Design N motor that is a general purpose electric motor (subtype I), manufactured (alone or as a component of another piece of equipment) on or after December 19, 2010, but before June 1, 2016, shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/Standard kilowatt equivalent | Nominal full-load efficiency | |||||
|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||
| 6 | 4 | 2 | 6 | 4 | 2 | |
| 1/.75 | 82.5 | 85.5 | 77.0 | 82.5 | 85.5 | 77.0 |
| 1.5/1.1 | 86.5 | 86.5 | 84.0 | 87.5 | 86.5 | 84.0 |
| 2/1.5 | 87.5 | 86.5 | 85.5 | 88.5 | 86.5 | 85.5 |
| 3/2.2 | 88.5 | 89.5 | 85.5 | 89.5 | 89.5 | 86.5 |
| 5/3.7 | 89.5 | 89.5 | 86.5 | 89.5 | 89.5 | 88.5 |
| 7.5/5.5 | 90.2 | 91.0 | 88.5 | 91.0 | 91.7 | 89.5 |
| 10/7.5 | 91.7 | 91.7 | 89.5 | 91.0 | 91.7 | 90.2 |
| 15/11 | 91.7 | 93.0 | 90.2 | 91.7 | 92.4 | 91.0 |
| 20/15 | 92.4 | 93.0 | 91.0 | 91.7 | 93.0 | 91.0 |
| 25/18.5 | 93.0 | 93.6 | 91.7 | 93.0 | 93.6 | 91.7 |
| 30/22 | 93.6 | 94.1 | 91.7 | 93.0 | 93.6 | 91.7 |
| 40/30 | 94.1 | 94.1 | 92.4 | 94.1 | 94.1 | 92.4 |
| 50/37 | 94.1 | 94.5 | 93.0 | 94.1 | 94.5 | 93.0 |
| 60/45 | 94.5 | 95.0 | 93.6 | 94.5 | 95.0 | 93.6 |
| 75/55 | 94.5 | 95.0 | 93.6 | 94.5 | 95.4 | 93.6 |
| 100/75 | 95.0 | 95.4 | 93.6 | 95.0 | 95.4 | 94.1 |
| 125/90 | 95.0 | 95.4 | 94.1 | 95.0 | 95.4 | 95.0 |
| 150/110 | 95.4 | 95.8 | 94.1 | 95.8 | 95.8 | 95.0 |
| 200/150 | 95.4 | 95.8 | 95.0 | 95.8 | 96.2 | 95.4 |
(b) Each fire pump electric motor that is a general purpose electric motor (subtype I) or general purpose electric motor (subtype II) manufactured (alone or as a component of another piece of equipment) on or after December 19, 2010, but before June 1, 2016, shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/standard kilowatt equivalent | Nominal full-load efficiency | |||||||
|---|---|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||||
| 8 | 6 | 4 | 2 | 8 | 6 | 4 | 2 | |
| 1/.75 | 74.0 | 80.0 | 82.5 | 74.0 | 80.0 | 82.5 | 75.5 | |
| 1.5/1.1 | 75.5 | 84.0 | 84.0 | 82.5 | 77.0 | 85.5 | 84.0 | 82.5 |
| 2/1.5 | 85.5 | 85.5 | 84.0 | 84.0 | 82.5 | 86.5 | 84.0 | 84.0 |
| 3/2.2 | 86.5 | 86.5 | 86.5 | 84.0 | 84.0 | 87.5 | 87.5 | 85.5 |
| 5/3.7 | 87.5 | 87.5 | 87.5 | 85.5 | 85.5 | 87.5 | 87.5 | 87.5 |
| 7.5/5.5 | 88.5 | 88.5 | 88.5 | 87.5 | 85.5 | 89.5 | 89.5 | 88.5 |
| 10/7.5 | 89.5 | 90.2 | 89.5 | 88.5 | 88.5 | 89.5 | 89.5 | 89.5 |
| 15/11 | 89.5 | 90.2 | 91.0 | 89.5 | 88.5 | 90.2 | 91.0 | 90.2 |
| 20/15 | 90.2 | 91.0 | 91.0 | 90.2 | 89.5 | 90.2 | 91.0 | 90.2 |
| 25/18.5 | 90.2 | 91.7 | 91.7 | 91.0 | 89.5 | 91.7 | 92.4 | 91.0 |
| 30/22 | 91.0 | 92.4 | 92.4 | 91.0 | 91.0 | 91.7 | 92.4 | 91.0 |
| 40/30 | 91.0 | 93.0 | 93.0 | 91.7 | 91.0 | 93.0 | 93.0 | 91.7 |
| 50/37 | 91.7 | 93.0 | 93.0 | 92.4 | 91.7 | 93.0 | 93.0 | 92.4 |
| 60/45 | 92.4 | 93.6 | 93.6 | 93.0 | 91.7 | 93.6 | 93.6 | 93.0 |
| 75/55 | 93.6 | 93.6 | 94.1 | 93.0 | 93.0 | 93.6 | 94.1 | 93.0 |
| 100/75 | 93.6 | 94.1 | 94.1 | 93.0 | 93.0 | 94.1 | 94.5 | 93.6 |
| 125/90 | 93.6 | 94.1 | 94.5 | 93.6 | 93.6 | 94.1 | 94.5 | 94.5 |
| 150/110 | 93.6 | 94.5 | 95.0 | 93.6 | 93.6 | 95.0 | 95.0 | 94.5 |
| 200/150 | 93.6 | 94.5 | 95.0 | 94.5 | 94.1 | 95.0 | 95.0 | 95.0 |
| 250/186 | 94.5 | 95.4 | 95.4 | 94.5 | 94.5 | 95.0 | 95.0 | 95.4 |
| 300/224 | 95.4 | 95.4 | 95.0 | 95.0 | 95.4 | 95.4 | ||
| 350/261 | 95.4 | 95.4 | 95.0 | 95.0 | 95.4 | 95.4 | ||
| 400/298 | 95.4 | 95.4 | 95.4 | 95.4 | ||||
| 450/336 | 95.8 | 95.8 | 95.4 | 95.4 | ||||
| 500/373 | 95.8 | 95.8 | 95.8 | 95.4 | ||||
(c) Except as provided for fire pump electric motors in paragraph (b) of this section, each general purpose electric motor (subtype II) with a power rating of 1 horsepower or greater, but not greater than 200 horsepower, including a NEMA Design B or an equivalent IEC Design N motor that is a general purpose electric motor (subtype II), manufactured (alone or as a component of another piece of equipment) on or after December 19, 2010, but before June 1, 2016, shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/ Standard kilowatt equivalent |
Nominal full-load efficiency | |||||||
|---|---|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||||
| 8 | 6 | 4 | 2 | 8 | 6 | 4 | 2 | |
| 1/.75 | 74.0 | 80.0 | 82.5 | 74.0 | 80.0 | 82.5 | 75.5 | |
| 1.5/1.1 | 75.5 | 84.0 | 84.0 | 82.5 | 77.0 | 85.5 | 84.0 | 82.5 |
| 2/1.5 | 85.5 | 85.5 | 84.0 | 84.0 | 82.5 | 86.5 | 84.0 | 84.0 |
| 3/2.2 | 86.5 | 86.5 | 86.5 | 84.0 | 84.0 | 87.5 | 87.5 | 85.5 |
| 5/3.7 | 87.5 | 87.5 | 87.5 | 85.5 | 85.5 | 87.5 | 87.5 | 87.5 |
| 7.5/5.5 | 88.5 | 88.5 | 88.5 | 87.5 | 85.5 | 89.5 | 89.5 | 88.5 |
| 10/7.5 | 89.5 | 90.2 | 89.5 | 88.5 | 88.5 | 89.5 | 89.5 | 89.5 |
| 15/11 | 89.5 | 90.2 | 91.0 | 89.5 | 88.5 | 90.2 | 91.0 | 90.2 |
| 20/15 | 90.2 | 91.0 | 91.0 | 90.2 | 89.5 | 90.2 | 91.0 | 90.2 |
| 25/18.5 | 90.2 | 91.7 | 91.7 | 91.0 | 89.5 | 91.7 | 92.4 | 91.0 |
| 30/22 | 91.0 | 92.4 | 92.4 | 91.0 | 91.0 | 91.7 | 92.4 | 91.0 |
| 40/30 | 91.0 | 93.0 | 93.0 | 91.7 | 91.0 | 93.0 | 93.0 | 91.7 |
| 50/37 | 91.7 | 93.0 | 93.0 | 92.4 | 91.7 | 93.0 | 93.0 | 92.4 |
| 60/45 | 92.4 | 93.6 | 93.6 | 93.0 | 91.7 | 93.6 | 93.6 | 93.0 |
| 75/55 | 93.6 | 93.6 | 94.1 | 93.0 | 93.0 | 93.6 | 94.1 | 93.0 |
| 100/75 | 93.6 | 94.1 | 94.1 | 93.0 | 93.0 | 94.1 | 94.5 | 93.6 |
| 125/90 | 93.6 | 94.1 | 94.5 | 93.6 | 93.6 | 94.1 | 94.5 | 94.5 |
| 150/110 | 93.6 | 94.5 | 95.0 | 93.6 | 93.6 | 95.0 | 95.0 | 94.5 |
| 200/150 | 93.6 | 94.5 | 95.0 | 94.5 | 94.1 | 95.0 | 95.0 | 95.0 |
(d) Each NEMA Design B or an equivalent IEC Design N motor that is a general purpose electric motor (subtype I) or general purpose electric motor (subtype II), excluding fire pump electric motors, with a power rating of more than 200 horsepower, but not greater than 500 horsepower, manufactured (alone or as a component of another piece of equipment) on or after December 19, 2010, but before June 1, 2016 shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/ standard kilowatt equivalent |
Nominal full-load efficiency | |||||||
|---|---|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||||
| 8 | 6 | 4 | 2 | 8 | 6 | 4 | 2 | |
| 250/186 | 94.5 | 95.4 | 95.4 | 94.5 | 94.5 | 95.0 | 95.0 | 95.4 |
| 300/224 | 95.4 | 95.4 | 95.0 | 95.0 | 95.4 | 95.4 | ||
| 350/261 | 95.4 | 95.4 | 95.0 | 95.0 | 95.4 | 95.4 | ||
| 400/298 | 95.4 | 95.4 | 95.4 | 95.4 | ||||
| 450/336 | 95.8 | 95.8 | 95.4 | 95.4 | ||||
| 500/373 | 95.8 | 95.8 | 95.8 | 95.4 | ||||
(e) For purposes of determining the required minimum nominal full-load efficiency of an electric motor that has a horsepower or kilowatt rating between two horsepower or two kilowatt ratings listed in any table of energy conservation standards in paragraphs (a) through (d) of this section, each such motor shall be deemed to have a listed horsepower or kilowatt rating, determined as follows:
(1) A horsepower at or above the midpoint between the two consecutive horsepowers shall be rounded up to the higher of the two horsepowers;
(2) A horsepower below the midpoint between the two consecutive horsepowers shall be rounded down to the lower of the two horsepowers; or
(3) A kilowatt rating shall be directly converted from kilowatts to horsepower using the formula 1 kilowatt = (1/0.746) horsepower. The conversion should be calculated to three significant decimal places, and the resulting horsepower shall be rounded in accordance with paragraph (e)(1) or (e)(2) of this section, whichever applies.
(f) The standards in Table 1 through Table 4 of this section do not apply to definite purpose electric motors, special purpose electric motors, or those motors exempted by the Secretary.
(g) The standards in Table 5 through Table 7 of this section apply only to electric motors, including partial electric motors, that satisfy the following criteria:
(1) Are single-speed, induction motors;
(2) Are rated for continuous duty (MG 1) operation or for duty type S1 (IEC);
(3) Contain a squirrel-cage (MG 1) or cage (IEC) rotor;
(4) Operate on polyphase alternating current 60-hertz sinusoidal line power;
(5) Are rated 600 volts or less;
(6) Have a 2-, 4-, 6-, or 8-pole configuration,
(7) Are built in a three-digit or four-digit NEMA frame size (or IEC metric equivalent), including those designs between two consecutive NEMA frame sizes (or IEC metric equivalent), or an enclosed 56 NEMA frame size (or IEC metric equivalent),
(8) Produce at least one horsepower (0.746 kW) but not greater than 500 horsepower (373 kW), and
(9) Meet all of the performance requirements of one of the following motor types: A NEMA Design A, B, or C motor or an IEC Design N, NE, NEY, NY or H, HE, HEY, HY motor.
(h) Each NEMA Design A motor, NEMA Design B motor, and IEC Design N (including NE, NEY, or NY variants) motor that is an electric motor meeting the criteria in paragraph (g) of this section and with a power rating from 1 horsepower through 500 horsepower, but excluding fire pump electric motors, manufactured (alone or as a component of another piece of equipment) on or after June 1, 2016, but before June 1, 2027, shall have a nominal full-load efficiency of not less than the following:
| Motor horsepower/ standard kilowatt equivalent |
Nominal full-load efficiency (%) | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 77.0 | 77.0 | 85.5 | 85.5 | 82.5 | 82.5 | 75.5 | 75.5 |
| 1.5/1.1 | 84.0 | 84.0 | 86.5 | 86.5 | 87.5 | 86.5 | 78.5 | 77.0 |
| 2/1.5 | 85.5 | 85.5 | 86.5 | 86.5 | 88.5 | 87.5 | 84.0 | 86.5 |
| 3/2.2 | 86.5 | 85.5 | 89.5 | 89.5 | 89.5 | 88.5 | 85.5 | 87.5 |
| 5/3.7 | 88.5 | 86.5 | 89.5 | 89.5 | 89.5 | 89.5 | 86.5 | 88.5 |
| 7.5/5.5 | 89.5 | 88.5 | 91.7 | 91.0 | 91.0 | 90.2 | 86.5 | 89.5 |
| 10/7.5 | 90.2 | 89.5 | 91.7 | 91.7 | 91.0 | 91.7 | 89.5 | 90.2 |
| 15/11 | 91.0 | 90.2 | 92.4 | 93.0 | 91.7 | 91.7 | 89.5 | 90.2 |
| 20/15 | 91.0 | 91.0 | 93.0 | 93.0 | 91.7 | 92.4 | 90.2 | 91.0 |
| 25/18.5 | 91.7 | 91.7 | 93.6 | 93.6 | 93.0 | 93.0 | 90.2 | 91.0 |
| 30/22 | 91.7 | 91.7 | 93.6 | 94.1 | 93.0 | 93.6 | 91.7 | 91.7 |
| 40/30 | 92.4 | 92.4 | 94.1 | 94.1 | 94.1 | 94.1 | 91.7 | 91.7 |
| 50/37 | 93.0 | 93.0 | 94.5 | 94.5 | 94.1 | 94.1 | 92.4 | 92.4 |
| 60/45 | 93.6 | 93.6 | 95.0 | 95.0 | 94.5 | 94.5 | 92.4 | 93.0 |
| 75/55 | 93.6 | 93.6 | 95.4 | 95.0 | 94.5 | 94.5 | 93.6 | 94.1 |
| 100/75 | 94.1 | 93.6 | 95.4 | 95.4 | 95.0 | 95.0 | 93.6 | 94.1 |
| 125/90 | 95.0 | 94.1 | 95.4 | 95.4 | 95.0 | 95.0 | 94.1 | 94.1 |
| 150/110 | 95.0 | 94.1 | 95.8 | 95.8 | 95.8 | 95.4 | 94.1 | 94.1 |
| 200/150 | 95.4 | 95.0 | 96.2 | 95.8 | 95.8 | 95.4 | 94.5 | 94.1 |
| 250/186 | 95.8 | 95.0 | 96.2 | 95.8 | 95.8 | 95.8 | 95.0 | 95.0 |
| 300/224 | 95.8 | 95.4 | 96.2 | 95.8 | 95.8 | 95.8 | ||
| 350/261 | 95.8 | 95.4 | 96.2 | 95.8 | 95.8 | 95.8 | ||
| 400/298 | 95.8 | 95.8 | 96.2 | 95.8 | ||||
| 450/336 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 500/373 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
(i) Starting on June 1, 2016, each NEMA Design C motor and IEC Design H (including HE, HEY, or HY variants) motor that is an electric motor meeting the criteria in paragraph (g) of this section and with a power rating from 1 horsepower through 200 horsepower manufactured (alone or as a component of another piece of equipment) shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/standard kilowatt equivalent | Nominal full-load efficiency (%) | |||||
|---|---|---|---|---|---|---|
| 4 Pole | 6 Pole | 8 Pole | ||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 85.5 | 85.5 | 82.5 | 82.5 | 75.5 | 75.5 |
| 1.5/1.1 | 86.5 | 86.5 | 87.5 | 86.5 | 78.5 | 77.0 |
| 2/1.5 | 86.5 | 86.5 | 88.5 | 87.5 | 84.0 | 86.5 |
| 3/2.2 | 89.5 | 89.5 | 89.5 | 88.5 | 85.5 | 87.5 |
| 5/3.7 | 89.5 | 89.5 | 89.5 | 89.5 | 86.5 | 88.5 |
| 7.5/5.5 | 91.7 | 91.0 | 91.0 | 90.2 | 86.5 | 89.5 |
| 10/7.5 | 91.7 | 91.7 | 91.0 | 91.7 | 89.5 | 90.2 |
| 15/11 | 92.4 | 93.0 | 91.7 | 91.7 | 89.5 | 90.2 |
| 20/15 | 93.0 | 93.0 | 91.7 | 92.4 | 90.2 | 91.0 |
| 25/18.5 | 93.6 | 93.6 | 93.0 | 93.0 | 90.2 | 91.0 |
| 30/22 | 93.6 | 94.1 | 93.0 | 93.6 | 91.7 | 91.7 |
| 40/30 | 94.1 | 94.1 | 94.1 | 94.1 | 91.7 | 91.7 |
| 50/37 | 94.5 | 94.5 | 94.1 | 94.1 | 92.4 | 92.4 |
| 60/45 | 95.0 | 95.0 | 94.5 | 94.5 | 92.4 | 93.0 |
| 75/55 | 95.4 | 95.0 | 94.5 | 94.5 | 93.6 | 94.1 |
| 100/75 | 95.4 | 95.4 | 95.0 | 95.0 | 93.6 | 94.1 |
| 125/90 | 95.4 | 95.4 | 95.0 | 95.0 | 94.1 | 94.1 |
| 150/110 | 95.8 | 95.8 | 95.8 | 95.4 | 94.1 | 94.1 |
| 200/150 | 96.2 | 95.8 | 95.8 | 95.4 | 94.5 | 94.1 |
(j) Starting on June 1, 2016, each fire pump electric motor meeting the criteria in paragraph (g) of this section and with a power rating of 1 horsepower through 500 horsepower, manufactured (alone or as a component of another piece of equipment) shall have a nominal full-load efficiency that is not less than the following:
| Motor horsepower/ standard kilowatt equivalent |
Nominal full-load efficiency (%) | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 75.5 | 82.5 | 82.5 | 80.0 | 80.0 | 74.0 | 74.0 | |
| 1.5/1.1 | 82.5 | 82.5 | 84.0 | 84.0 | 85.5 | 84.0 | 77.0 | 75.5 |
| 2/1.5 | 84.0 | 84.0 | 84.0 | 84.0 | 86.5 | 85.5 | 82.5 | 85.5 |
| 3/2.2 | 85.5 | 84.0 | 87.5 | 86.5 | 87.5 | 86.5 | 84.0 | 86.5 |
| 5/3.7 | 87.5 | 85.5 | 87.5 | 87.5 | 87.5 | 87.5 | 85.5 | 87.5 |
| 7.5/5.5 | 88.5 | 87.5 | 89.5 | 88.5 | 89.5 | 88.5 | 85.5 | 88.5 |
| 10/7.5 | 89.5 | 88.5 | 89.5 | 89.5 | 89.5 | 90.2 | 88.5 | 89.5 |
| 15/11 | 90.2 | 89.5 | 91.0 | 91.0 | 90.2 | 90.2 | 88.5 | 89.5 |
| 20/15 | 90.2 | 90.2 | 91.0 | 91.0 | 90.2 | 91.0 | 89.5 | 90.2 |
| 25/18.5 | 91.0 | 91.0 | 92.4 | 91.7 | 91.7 | 91.7 | 89.5 | 90.2 |
| 30/22 | 91.0 | 91.0 | 92.4 | 92.4 | 91.7 | 92.4 | 91.0 | 91.0 |
| 40/30 | 91.7 | 91.7 | 93.0 | 93.0 | 93.0 | 93.0 | 91.0 | 91.0 |
| 50/37 | 92.4 | 92.4 | 93.0 | 93.0 | 93.0 | 93.0 | 91.7 | 91.7 |
| 60/45 | 93.0 | 93.0 | 93.6 | 93.6 | 93.6 | 93.6 | 91.7 | 92.4 |
| 75/55 | 93.0 | 93.0 | 94.1 | 94.1 | 93.6 | 93.6 | 93.0 | 93.6 |
| 100/75 | 93.6 | 93.0 | 94.5 | 94.1 | 94.1 | 94.1 | 93.0 | 93.6 |
| 125/90 | 94.5 | 93.6 | 94.5 | 94.5 | 94.1 | 94.1 | 93.6 | 93.6 |
| 150/110 | 94.5 | 93.6 | 95.0 | 95.0 | 95.0 | 94.5 | 93.6 | 93.6 |
| 200/150 | 95.0 | 94.5 | 95.0 | 95.0 | 95.0 | 94.5 | 94.1 | 93.6 |
| 250/186 | 95.4 | 94.5 | 95.0 | 95.4 | 95.0 | 95.4 | 94.5 | 94.5 |
| 300/224 | 95.4 | 95.0 | 95.4 | 95.4 | 95.0 | 95.4 | ||
| 350/261 | 95.4 | 95.0 | 95.4 | 95.4 | 95.0 | 95.4 | ||
| 400/298 | 95.4 | 95.4 | 95.4 | 95.4 | ||||
| 450/336 | 95.4 | 95.8 | 95.4 | 95.8 | ||||
| 500/373 | 95.4 | 95.8 | 95.8 | 95.8 | ||||
(k) For purposes of determining the required minimum nominal full-load efficiency of an electric motor that has a horsepower or kilowatt rating between two horsepower or two kilowatt ratings listed in any table of energy conservation standards in paragraphs (h) through (l) of this section, each such motor shall be deemed to have a listed horsepower or kilowatt rating, determined as follows:
(1) A horsepower at or above the midpoint between the two consecutive horsepowers shall be rounded up to the higher of the two horsepowers;
(2) A horsepower below the midpoint between the two consecutive horsepowers shall be rounded down to the lower of the two horsepowers; or
(3) A kilowatt rating shall be directly converted from kilowatts to horsepower using the formula 1 kilowatt = (1/0.746) horsepower. The conversion should be calculated to three significant decimal places, and the resulting horsepower shall be rounded in accordance with paragraph (k)(1) or (k)(2) of this section, whichever applies.
(l) The standards in Table 5 through Table 7 of this section do not apply to the following electric motors exempted by the Secretary, or any additional electric motors that the Secretary may exempt:
(1) Air-over electric motors;
(2) Component sets of an electric motor;
(3) Liquid-cooled electric motors;
(4) Submersible electric motors; and
(5) Inverter-only electric motors.
(m) The standards in tables 8 through 10 of this section apply only to electric motors, including partial electric motors, that satisfy the following criteria:
(1) Are single-speed, induction motors;
(2) Are rated for continuous duty (MG 1) operation or for duty type S1 (IEC);
(3) Contain a squirrel-cage (MG 1) or cage (IEC) rotor;
(4) Operate on polyphase alternating current 60-hertz sinusoidal line power;
(5) Are rated 600 volts or less;
(6) Have a 2-, 4-, 6-, or 8-pole configuration,
(7) Are built in a three-digit or four-digit NEMA frame size (or IEC metric equivalent), including those designs between two consecutive NEMA frame sizes (or IEC metric equivalent), or an enclosed 56 NEMA frame size (or IEC metric equivalent),
(8) Produce at least one horsepower (0.746 kW) but not greater than 750 horsepower (559 kW), and
(9) Meet all of the performance requirements of one of the following motor types: A NEMA Design A, B, or C motor or an IEC Design N, NE, NEY, NY or H, HE, HEY, HY motor.
(n) Starting on June 1, 2027, each NEMA Design A motor, NEMA Design B motor, and IEC Design N (including NE, NEY, or NY variants) motor that is an electric motor meeting the criteria in paragraph (m) of this section and with a power rating from 1 horsepower through 750 horsepower, but excluding fire pump electric motors and air-over electric motors, manufactured (alone or as a component of another piece of equipment) shall have a nominal full-load efficiency of not less than the following:
| Motor horsepower/standard kilowatt equivalent | Nominal full-load efficiency (%) | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 77.0 | 77.0 | 85.5 | 85.5 | 82.5 | 82.5 | 75.5 | 75.5 |
| 1.5/1.1 | 84.0 | 84.0 | 86.5 | 86.5 | 87.5 | 86.5 | 78.5 | 77.0 |
| 2/1.5 | 85.5 | 85.5 | 86.5 | 86.5 | 88.5 | 87.5 | 84.0 | 86.5 |
| 3/2.2 | 86.5 | 85.5 | 89.5 | 89.5 | 89.5 | 88.5 | 85.5 | 87.5 |
| 5/3.7 | 88.5 | 86.5 | 89.5 | 89.5 | 89.5 | 89.5 | 86.5 | 88.5 |
| 7.5/5.5 | 89.5 | 88.5 | 91.7 | 91.0 | 91.0 | 90.2 | 86.5 | 89.5 |
| 10/7.5 | 90.2 | 89.5 | 91.7 | 91.7 | 91.0 | 91.7 | 89.5 | 90.2 |
| 15/11 | 91.0 | 90.2 | 92.4 | 93.0 | 91.7 | 91.7 | 89.5 | 90.2 |
| 20/15 | 91.0 | 91.0 | 93.0 | 93.0 | 91.7 | 92.4 | 90.2 | 91.0 |
| 25/18.5 | 91.7 | 91.7 | 93.6 | 93.6 | 93.0 | 93.0 | 90.2 | 91.0 |
| 30/22 | 91.7 | 91.7 | 93.6 | 94.1 | 93.0 | 93.6 | 91.7 | 91.7 |
| 40/30 | 92.4 | 92.4 | 94.1 | 94.1 | 94.1 | 94.1 | 91.7 | 91.7 |
| 50/37 | 93.0 | 93.0 | 94.5 | 94.5 | 94.1 | 94.1 | 92.4 | 92.4 |
| 60/45 | 93.6 | 93.6 | 95.0 | 95.0 | 94.5 | 94.5 | 92.4 | 93.0 |
| 75/55 | 93.6 | 93.6 | 95.4 | 95.0 | 94.5 | 94.5 | 93.6 | 94.1 |
| 100/75 | 95.0 | 94.5 | 96.2 | 96.2 | 95.8 | 95.8 | 94.5 | 95.0 |
| 125/90 | 95.4 | 94.5 | 96.2 | 96.2 | 95.8 | 95.8 | 95.0 | 95.0 |
| 150/110 | 95.4 | 94.5 | 96.2 | 96.2 | 96.2 | 95.8 | 95.0 | 95.0 |
| 200/150 | 95.8 | 95.4 | 96.5 | 96.2 | 96.2 | 95.8 | 95.4 | 95.0 |
| 250/186 | 96.2 | 95.4 | 96.5 | 96.2 | 96.2 | 96.2 | 95.4 | 95.4 |
| 300/224 | 95.8 | 95.4 | 96.2 | 95.8 | 95.8 | 95.8 | ||
| 350/261 | 95.8 | 95.4 | 96.2 | 95.8 | 95.8 | 95.8 | ||
| 400/298 | 95.8 | 95.8 | 96.2 | 95.8 | ||||
| 450/336 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 500/373 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 550/410 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 600/447 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 650/485 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 700/522 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
| 750/559 | 95.8 | 96.2 | 96.2 | 96.2 | ||||
(o) Starting on June 1, 2027, each NEMA Design A motor, NEMA Design B motor, and IEC Design N (including NE, NEY, or NY variants) motor that is an air-over electric motor meeting the criteria in paragraph (m) of this section and with a power rating from 1 horsepower through 250 horsepower, built in a standard frame size, but excluding fire pump electric motors, manufactured (alone or as a component of another piece of equipment) shall have a nominal full-load efficiency of not less than the following:
| Motor horsepower/standard kilowatt equivalent | Nominal full-load efficiency (%) | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 77.0 | 77.0 | 85.5 | 85.5 | 82.5 | 82.5 | 75.5 | 75.5 |
| 1.5/1.1 | 84.0 | 84.0 | 86.5 | 86.5 | 87.5 | 86.5 | 78.5 | 77.0 |
| 2/1.5 | 85.5 | 85.5 | 86.5 | 86.5 | 88.5 | 87.5 | 84.0 | 86.5 |
| 3/2.2 | 86.5 | 85.5 | 89.5 | 89.5 | 89.5 | 88.5 | 85.5 | 87.5 |
| 5/3.7 | 88.5 | 86.5 | 89.5 | 89.5 | 89.5 | 89.5 | 86.5 | 88.5 |
| 7.5/5.5 | 89.5 | 88.5 | 91.7 | 91.0 | 91.0 | 90.2 | 86.5 | 89.5 |
| 10/7.5 | 90.2 | 89.5 | 91.7 | 91.7 | 91.0 | 91.7 | 89.5 | 90.2 |
| 15/11 | 91.0 | 90.2 | 92.4 | 93.0 | 91.7 | 91.7 | 89.5 | 90.2 |
| 20/15 | 91.0 | 91.0 | 93.0 | 93.0 | 91.7 | 92.4 | 90.2 | 91.0 |
| 25/18.5 | 91.7 | 91.7 | 93.6 | 93.6 | 93.0 | 93.0 | 90.2 | 91.0 |
| 30/22 | 91.7 | 91.7 | 93.6 | 94.1 | 93.0 | 93.6 | 91.7 | 91.7 |
| 40/30 | 92.4 | 92.4 | 94.1 | 94.1 | 94.1 | 94.1 | 91.7 | 91.7 |
| 50/37 | 93.0 | 93.0 | 94.5 | 94.5 | 94.1 | 94.1 | 92.4 | 92.4 |
| 60/45 | 93.6 | 93.6 | 95.0 | 95.0 | 94.5 | 94.5 | 92.4 | 93.0 |
| 75/55 | 93.6 | 93.6 | 95.4 | 95.0 | 94.5 | 94.5 | 93.6 | 94.1 |
| 100/75 | 95.0 | 94.5 | 96.2 | 96.2 | 95.8 | 95.8 | 94.5 | 95.0 |
| 125/90 | 95.4 | 94.5 | 96.2 | 96.2 | 95.8 | 95.8 | 95.0 | 95.0 |
| 150/110 | 95.4 | 94.5 | 96.2 | 96.2 | 96.2 | 95.8 | 95.0 | 95.0 |
| 200/150 | 95.8 | 95.4 | 96.5 | 96.2 | 96.2 | 95.8 | 95.4 | 95.0 |
| 250/186 | 96.2 | 95.4 | 96.5 | 96.2 | 96.2 | 96.2 | 95.4 | 95.4 |
(p) Starting on June 1, 2027, each NEMA Design A motor, NEMA Design B motor, and IEC Design N (including NE, NEY, or NY variants) motor that is an air-over electric motor meeting the criteria in paragraph (m) of this section and with a power rating from 1 horsepower through 20 horsepower, built in a specialized frame size, but excluding fire pump electric motors, manufactured (alone or as a component of another piece of equipment) shall have a nominal full-load efficiency of not less than the following:
| Motor horsepower/standard kilowatt equivalent | Nominal full-load efficiency (%) | |||||||
|---|---|---|---|---|---|---|---|---|
| 2 Pole | 4 Pole | 6 Pole | 8 Pole | |||||
| Enclosed | Open | Enclosed | Open | Enclosed | Open | Enclosed | Open | |
| 1/.75 | 74.0 | 82.5 | 82.5 | 80.0 | 80.0 | 74.0 | 74.0 | |
| 1.5/1.1 | 82.5 | 82.5 | 84.0 | 84.0 | 85.5 | 84.0 | 77.0 | 75.5 |
| 2/1.5 | 84.0 | 84.0 | 84.0 | 84.0 | 86.5 | 85.5 | 82.5 | 85.5 |
| 3/2.2 | 85.5 | 84.0 | 87.5 | 86.5 | 87.5 | 86.5 | 84.0 | 86.5 |
| 5/3.7 | 87.5 | 85.5 | 87.5 | 87.5 | 87.5 | 87.5 | 85.5 | 87.5 |
| 7.5/5.5 | 88.5 | 87.5 | 89.5 | 88.5 | 89.5 | 88.5 | 85.5 | 88.5 |
| 10/7.5 | 89.5 | 88.5 | 89.5 | 89.5 | 89.5 | 90.2 | ||
| 15/11 | 90.2 | 89.5 | 91.0 | 91.0 | ||||
| 20/15 | 90.2 | 90.2 | 91.0 | 91.0 | ||||
(q) For purposes of determining the required minimum nominal full-load efficiency of an electric motor that has a horsepower or kilowatt rating between two horsepower or two kilowatt ratings listed in any table of energy conservation standards in paragraphs (n) through (p) through of this section, each such motor shall be deemed to have a listed horsepower or kilowatt rating, determined as follows:
(1) A horsepower at or above the midpoint between the two consecutive horsepowers shall be rounded up to the higher of the two horsepowers;
(2) A horsepower below the midpoint between the two consecutive horsepowers shall be rounded down to the lower of the two horsepowers; or
(3) A kilowatt rating shall be directly converted from kilowatts to horsepower using the formula 1 kilowatt = (1⁄0.746) horsepower. The conversion should be calculated to three significant decimal places, and the resulting horsepower shall be rounded in accordance with paragraphs (q)(1) or (2) of this section, whichever applies.
(r) The standards in tables 8 through 10 of this section do not apply to the following electric motors exempted by the Secretary, or any additional electric motors that the Secretary may exempt:
(1) Component sets of an electric motor;
(2) Liquid-cooled electric motors;
(3) Submersible electric motors; and
(4) Inverter-only electric motors.
[79 FR 31010, May 29, 2014, as amended at 87 FR 63657, Oct. 19, 2022; 88 FR 36150, Sept. 29, 2023]
Any State regulation providing for any energy conservation standard, or other requirement with respect to the energy efficiency or energy use, of an electric motor that is not identical to a Federal standard in effect under this subpart is preempted by that standard, except as provided for in Section 345(a) and 327(b) and (c) of the Act.
(a) Electric motor nameplate —
(1) Required information. The permanent nameplate of an electric motor for which standards are prescribed in § 431.25 must be marked clearly with the following information:
(i) The motor's nominal full load efficiency (as of the date of manufacture), derived from the motor's average full load efficiency as determined pursuant to this subpart; and
(ii) A Compliance Certification number (“CC number”) supplied by DOE to the manufacturer or private labeler, pursuant to § 431.36(f), and applicable to that motor. Such CC number must be on the nameplate of a motor beginning 90 days after either:
(A) The manufacturer or private labeler has received the number upon submitting a Compliance Certification covering that motor, or
(B) The expiration of 21 days from DOE's receipt of a Compliance Certification covering that motor, if the manufacturer or private labeler has not been advised by DOE that the Compliance Certification fails to satisfy § 431.36.
(2) Display of required information. All orientation, spacing, type sizes, type faces, and line widths to display this required information shall be the same as or similar to the display of the other performance data on the motor's permanent nameplate. The nominal full-load efficiency shall be identified either by the term “Nominal Efficiency” or “Nom. Eff.” or by the terms specified in paragraph 12.58.2 of NEMA MG1-2009, (incorporated by reference, see § 431.15) as for example “NEMA Nom. Eff. ____.” The Compliance Certification number issued pursuant to § 431.36 shall be in the form “CC ____.”
(3) Optional display. The permanent nameplate of an electric motor, a separate plate, or decalcomania, may be marked with the encircled lower case letters “ee”, for example,
or with some comparable designation or logo, if the motor meets the applicable standard prescribed in § 431.25, as determined pursuant to this subpart, and is covered by a Compliance Certification that satisfies § 431.36.
(b) Disclosure of efficiency information in marketing materials.
(1) The same information that must appear on an electric motor's permanent nameplate pursuant to paragraph (a)(1) of this section, shall be prominently displayed:
(i) On each page of a catalog that lists the motor; and
(ii) In other materials used to market the motor.
(2) The “ee” logo, or other similar logo or designations, may also be used in catalogs and other materials to the same extent they may be used on labels under paragraph (a)(3) of this section.
[69 FR 61923, Oct. 21, 2004, as amended at 77 FR 26637, May 4, 2012]
The provisions of § 431.31 supersede any State regulation to the extent required by Section 327 of the Act. Pursuant to the Act, all State regulations that require the disclosure for any electric motor of information with respect to energy consumption, other than the information required to be disclosed in accordance with this part, are superseded.
Section 431.36 sets forth the procedures for manufacturers to certify that electric motors comply with the applicable energy efficiency standards set forth in this subpart.
(a) General. A manufacturer or private labeler shall not distribute in commerce any basic model of an electric motor which is subject to an energy efficiency standard set forth in this subpart unless it has submitted to the Department a Compliance Certification certifying, in accordance with the provisions of this section, that the basic model meets the requirements of the applicable standard. The representations in the Compliance Certification must be based upon the basic model's energy efficiency as determined in accordance with the applicable requirements of this subpart. This means, in part, that either:
(1) The representations as to the basic model must be based on use of a certification organization; or
(2) Any testing of the basic model on which the representations are based must be conducted at an accredited laboratory.
(b) Required contents —
(1) General representations. Each Compliance Certification must certify that:
(i) The nominal full load efficiency for each basic model of electric motor distributed is not less than the minimum nominal full load efficiency required for that motor by § 431.25;
(ii) All required determinations on which the Compliance Certification is based were made in compliance with the applicable requirements prescribed in this subpart;
(iii) All information reported in the Compliance Certification is true, accurate, and complete; and
(iv) The manufacturer or private labeler is aware of the penalties associated with violations of the Act and the regulations thereunder, and of 18 U.S.C. 1001 which prohibits knowingly making false statements to the Federal Government.
(2) Specific data.
(i) For each rating of electric motor (as the term “rating” is defined in the definition of basic model) which a manufacturer or private labeler distributes, the Compliance Certification must report the nominal full load efficiency, determined pursuant to §§ 431.16 and 431.17, of the least efficient basic model within that rating.
(ii) The Compliance Certification must identify the basic models on which actual testing has been performed to meet the requirements of § 431.17.
(iii) The format for a Compliance Certification is set forth in appendix C of this subpart.
(c) Optional contents. In any Compliance Certification, a manufacturer or private labeler may at its option request that DOE provide it with a unique Compliance Certification number (“CC number”) for any brand name, trademark or other label name under which the manufacturer or private labeler distributes electric motors covered by the Certification. Such a Compliance Certification must also identify all other names, if any, under which the manufacturer or private labeler distributes electric motors, and to which the request does not apply.
(d) Signature and submission. A manufacturer or private labeler must submit the Compliance Certification either on its own behalf, signed by a corporate official of the company, or through a third party (for example, a trade association or other authorized representative) acting on its behalf. Where a third party is used, the Compliance Certification must identify the official of the manufacturer or private labeler who authorized the third party to make representations on the company's behalf, and must be signed by a corporate official of the third party. The Compliance Certification must be submitted to the Department electronically at https://www.regulations.doe.gov/ccms. Alternatively, the Compliance Certification may be submitted by certified mail to: Certification and Compliance Reports, U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, EE-2J, Forrestal Building, 1000 Independence Avenue, SW., Washington, DC 20585-0121.
(e) New basic models. For electric motors, a Compliance Certification must be submitted for a new basic model only if the manufacturer or private labeler has not previously submitted to DOE a Compliance Certification, that meets the requirements of this section, for a basic model that has the same rating as the new basic model, and that has a lower nominal full load efficiency than the new basic model.
(f) Response to Compliance Certification; Compliance Certification Number (CC number) —
(1) DOE processing of Certification. Promptly upon receipt of a Compliance Certification, the Department will determine whether the document contains all of the elements required by this section, and may, in its discretion, determine whether all or part of the information provided in the document is accurate. The Department will then advise the submitting party in writing either that the Compliance Certification does not satisfy the requirements of this section, in which case the document will be returned, or that the Compliance Certification satisfies this section. The Department will also advise the submitting party of the basis for its determination.
(2) Issuance of CC number(s).
(i) Initial Compliance Certification. When DOE advises that the initial Compliance Certification submitted by or on behalf of a manufacturer or private labeler is acceptable, either:
(A) DOE will provide a single unique CC number, “CC________,” to the manufacturer or private labeler, and such CC number shall be applicable to all electric motors distributed by the manufacturer or private labeler, or
(B) When required by paragraph (f)(3) of this section, DOE will provide more than one CC number to the manufacturer or private labeler.
(ii) Subsequent Compliance Certification. When DOE advises that any other Compliance Certification is acceptable, it will provide a unique CC number for any brand name, trademark or other name when required by paragraph (f)(3) of this section.
(iii) When DOE declines to provide a CC number as requested by a manufacturer or private labeler in accordance with § 431.36(c), DOE will advise the requester of the reasons for such refusal.
(3) Issuance of two or more CC numbers.
(i) DOE will provide a unique CC number for each brand name, trademark or other label name for which a manufacturer or private labeler requests such a number in accordance with § 431.36(c), except as follows. DOE will not provide a CC number for any brand name, trademark or other label name
(A) For which DOE has previously provided a CC number, or
(B) That duplicates or overlaps with other names under which the manufacturer or private labeler sells electric motors.
(ii) Once DOE has provided a CC number for a particular name, that shall be the only CC number applicable to all electric motors distributed by the manufacturer or private labeler under that name.
(iii) If the Compliance Certification in which a manufacturer or private labeler requests a CC number is the initial Compliance Certification submitted by it or on its behalf, and it distributes electric motors not covered by the CC number(s) DOE provides in response to the request(s), DOE will also provide a unique CC number that shall be applicable to all of these other motors.
[69 FR 61923, Oct. 21, 2004, as amended at 76 FR 59006, Sept. 23, 2011; 77 FR 26638, May 4, 2012]
Manufacturers of electric motors subject to energy conservation standards in § 431.25 must test in accordance with this appendix.
For any other electric motor that is not currently covered by the energy conservation standards at § 431.25, manufacturers of this equipment must test in accordance with this appendix 180 days after the effective date of the final rule adopting energy conservation standards for such motor. For any other electric motor that is not currently covered by the energy conservation standards at § 431.25, manufacturers choosing to make any representations respecting of energy efficiency for such motors must test in accordance with this appendix.
0. Incorporation by Reference
In § 431.15, DOE incorporated by reference the entire standard for CSA C390-10, CSA C747-09, IEC 60034-1:2010, IEC 60034-2-1:2014, IEC 60051-1:2016, IEC 61800-9-2:2017, IEEE 112-2017, IEEE 114-2010, and NEMA MG 1-2016; however, only enumerated provisions of those documents are applicable as follows. In cases where there is a conflict, the language of this appendix takes precedence over those documents. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
0.1. CSA C390-10
(a) Section 1.3 “Scope,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix;
(b) Section 3.1 “Definitions,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix;
(c) Section 5 “General test requirements—Measurements,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix;
(d) Section 7 “Test method,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix;
(e) Table 1 “Resistance measurement time delay,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix;
(f) Annex B “Linear regression analysis,” as specified in sections 2.1.1 and 2.3.3.2 of this appendix; and
(g) Annex C “Procedure for correction of dynamometer torque readings” as specified in sections 2.1.1 and 2.3.3.2 of this appendix.
0.2. CSA C747-09
(a) Section 1.6 “Scope” as specified in sections 2.3.1.2 and 2.3.2.2 of this appendix;
(b) Section 3 “Definitions” as specified in sections 2.3.1.2 and 2.3.2.2 of this appendix;
(c) Section 5 “General test requirements” as specified in sections 2.3.1.2 and 2.3.2.2 of this appendix; and
(d) Section 6 “Test method” as specified in sections 2.3.1.2 and 2.3.2.2 of this appendix.
0.3. IEC 60034-1:2010
(a) Section 4.2.1 as specified in section 1.2 of this appendix;
(b) Section 7.2 as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, and 2.3.3.3 of this appendix;
(c) Section 8.6.2.3.3 as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, and 2.3.3.3 of this appendix; and
(d) Table 5 as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, and 2.3.3.3 of this appendix.
0.4. IEC 60034-2-1:2014
(a) Method 2-1-1A (which also includes paragraphs (b) through (f) of this section) as specified in sections 2.3.1.3 and 2.3.2.3 of this appendix;
(b) Method 2-1-1B (which also includes paragraphs (b) through (e), (g), and (i) of this section) as specified in sections 2.1.2 and 2.3.3.3 of this appendix;
(c) Section 3 “Terms and definitions” as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, 2.3.3.3, and 2.4.1 of this appendix;
(d) Section 4 “Symbols and abbreviations” as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, 2.3.3.3 and 2.4.1 of this appendix;
(e) Section 5 “Basic requirements” as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, 2.3.3.3, and 2.4.1 of this appendix;
(f) Section 6.1.2 “Method 2-1-1A—Direct measurement of input and output” (except Section 6.1.2.2, “Test Procedure”) as specified in sections 2.3.1.3 and 2.3.2.3 of this appendix;
(g) Section 6.1.3 “Method 2-1-1B—Summations of losses, additional load losses according to the method of residual losses” as specified in sections 2.1.2 and 2.3.3.3 of this appendix; and
(h) Section 7.1. “Preferred Testing Methods” as specified in section 2.4.1 of this appendix;
(i) Annex D, “Test report template for 2-1-1B” as specified in sections 2.1.2 and 2.3.3.3 of this appendix.
0.5. IEC 60051-1:2016
(a) Section 5.2 as specified in sections 2.1.2, 2.3.1.3, 2.3.2.3, and 2.3.3.3 of this appendix; and
(b) [Reserved].
0.6. IEC 61800-9-2:2017
(a) Section 3 “Terms, definitions, symbols, and abbreviated terms” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(b) Section 7.7.2, “Input-output measurement of PDS losses” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(c) Section 7.7.3.1, “General” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(d) Section 7.7.3.2. “Power analyser and transducers” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(e) Section 7.7.3.3, “Mechanical Output of the motor” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(f) Section 7.7.3.5, “PDS loss determination according to input-output method” as specified in sections 2.4.2 and 2.4.3 of this appendix;
(g) Section 7.10 “Testing Conditions for PDS testing” as specified in sections 2.4.2 and 2.4.3 of this appendix.
0.7. IEEE 112-2017
(a) Test Method A (which also includes paragraphs (c) through (g), (i), and (j) of this section) as specified in section 2.3.2.1 of this appendix;
(b) Test Method B (which also includes paragraphs (c) through (f), (h), (k) and (l) of this section) as specified in sections 2.1.3 and 2.3.3.1 of this appendix;
(c) Section 3, “General” as specified in sections 2.1.3, 2.3.2.1, and 2.3.3.1 of this appendix;
(d) Section 4, “Measurements” as specified in sections 2.1.3, 2.3.2.1, and 2.3.3.1 of this appendix;
(e) Section 5, “Machine losses and tests for losses” as specified in sections 2.1.3, 2.3.2.1, and 2.3.3.1 of this appendix;
(f) Section 6.1, “General” as specified in sections 2.1.3, 2.3.2.1, and 2.3.3.1 of this appendix;
(g) Section 6.3, “Efficiency test method A—Input-output” as specified in section 2.3.2.1 of this appendix;
(h) Section 6.4, “Efficiency test method B—Input-output” as specified in sections 2.1.3 and 2.3.3.1 of this appendix;
(i) Section 9.2, “Form A—Method A” as specified in section 2.3.2.1 of this appendix;
(j) Section 9.3, “Form A2—Method A calculations” as specified in section 2.3.2.1 of this appendix;
(k) Section 9.4, “Form B—Method B” as specified in sections 2.1.3, and 2.3.3.1 of this appendix; and
(l) Section 9.5, “Form B2—Method B calculations” as specified in sections 2.1.3 and 2.3.3.1 of this appendix.
0.8. IEEE 114-2010
(a) Section 3.2, “Test with load” as specified in section 2.3.1.1 of this appendix;
(b) Section 4, “Testing Facilities as specified in section 2.3.1.1 of this appendix;
(c) Section 5, “Measurements” as specified in section 2.3.1.1 of this appendix;
(d) Section 6, “General” as specified in section 2.3.1.1 of this appendix;
(e) Section 7, “Type of loss” as specified in section 2.3.1.1 of this appendix;
(f) Section 8, “Efficiency and Power Factor” as specified in section 2.3.1.1 of this appendix;
(g) Section 10 “Temperature Tests” as specified in section 2.4.1.1 of this appendix;
(h) Annex A, Section A.3 “Determination of Motor Efficiency” as specified in section 2.4.1.1 of this appendix; and
(i) Annex A, Section A.4 “Explanatory notes for form 3, test data” as specified in section 2.4.1.1 of this appendix.
0.9. NEMA MG 1-2016
(a) Paragraph 1.40.1, “Continuous Rating” as specified in section 1.2 of this appendix;
(b) Paragraph 12.58.1, “Determination of Motor Efficiency and Losses” as specified in the introductory paragraph to section 2.1 of this appendix, and
(c) Paragraph 34.1, “Applicable Motor Efficiency Test Methods” as specified in section 2.2 of this appendix;
(d) Paragraph 34.2.2 “AO Temperature Test Procedure 2—Target Temperature with Airflow” as specified in section 2.2 of this appendix;
(e) Paragraph 34.4, “AO Temperature Test Procedure 2—Target Temperature with Airflow” as specified in section 2.2 of this appendix.
1. Scope and Definitions
1.1 Scope. The test procedure applies to the following categories of electric motors: Electric motors that meet the criteria listed at § 431.25(g); Electric motors above 500 horsepower; Small, non-small-electric-motor electric motor; and Electric motors that are synchronous motors; and excludes the following categories of motors: inverter-only electric motors that are air-over electric motors, component sets of an electric motor, liquid-cooled electric motors, and submersible electric motors.
1.2 Definitions. Definitions contained in §§ 431.2 and 431.12 are applicable to this appendix, in addition to the following terms (“MG1” refers to NEMA MG 1-2016 and IEC refers to IEC 60034-1:2010 and IEC 60072-1):
Electric motors above 500 horsepower is defined as an electric motor having a rated horsepower above 500 and up to 750 hp that meets the criteria listed at § 431.25(g), with the exception of criteria § 431.25(g)(8).
Small, non-small-electric-motor electric motor (“SNEM” ) means an electric motor that:
(a) Is not a small electric motor, as defined § 431.442 and is not a dedicated-purpose pool pump motor as defined at § 431.483;
(b) Is rated for continuous duty (MG 1) operation or for duty type S1 (IEC);
(c) Operates on polyphase or single-phase alternating current 60-hertz (Hz) sinusoidal line power; or is used with an inverter that operates on polyphase or single-phase alternating current 60-hertz (Hz) sinusoidal line power;
(d) Is rated for 600 volts or less;
(e) Is a single-speed induction motor capable of operating without an inverter or is an inverter-only electric motor;
(f) Produces a rated motor horsepower greater than or equal to 0.25 horsepower (0.18 kW); and
(g) Is built in the following frame sizes: any two-, or three-digit NEMA frame size (or IEC metric equivalent) if the motor operates on single-phase power; any two-, or three-digit NEMA frame size (or IEC metric equivalent) if the motor operates on polyphase power, and has a rated motor horsepower less than 1 horsepower (0.75 kW); or a two-digit NEMA frame size (or IEC metric equivalent), if the motor operates on polyphase power, has a rated motor horsepower equal to or greater than 1 horsepower (0.75 kW), and is not an enclosed 56 NEMA frame size (or IEC metric equivalent).
Synchronous Electric Motor means an electric motor that:
(a) Is not a dedicated-purpose pool pump motor as defined at § 431.483 or is not an air-over electric motor;
(b) Is a synchronous electric motor;
(c) Is rated for continuous duty (MG 1) operation or for duty type S1 (IEC);
(d) Operates on polyphase or single-phase alternating current 60-hertz (Hz) sinusoidal line power; or is used with an inverter that operates on polyphase or single-phase alternating current 60-hertz (Hz) sinusoidal line power;
(e) Is rated 600 volts or less;
(f) Produces at least 0.25 hp (0.18 kW) but not greater than 750 hp (559 kW).
2. Test Procedures
2.1. Test Procedures for Electric Motors that meet the criteria listed at § 431.25(g), and electric motors above 500 horsepower that are capable of operating without an inverter. Air-over electric motors must be tested in accordance with Section 2.2. Inverter-only electric motors must be tested in accordance with 2.4.
Efficiency and losses must be determined in accordance with NEMA MG 1-2016, Paragraph 12.58.1, “Determination of Motor Efficiency and Losses,” or one of the following testing methods:
2.1.1. CSA C390-10 (see section 0.1 of this appendix)
2.1.2. IEC 60034-2-1:2014, Method 2-1-1B (see section 0.4(b) of this appendix). The supply voltage shall be in accordance with Section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in Section 8.6.2.3.3 of IEC 60034-1:2010, using the shortest possible time instead of the time interval specified in Table 5 to IEC 60034-1:2010, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with Section 5.2 of IEC 60051-1:2016, or
2.1.3. IEEE 112-2017, Test Method B (see section 0.7(b) of this appendix).
2.2. Test Procedures for Air-Over Electric Motors
Except noted otherwise in section 2.2.1 and 2.2.2 of this appendix, efficiency and losses of air-over electric motors must be determined in accordance with NEMA MG 1-2016 (excluding Paragraph 12.58.1).
2.2.1. The provisions in Paragraph 34.4.1.a.1 of NEMA MG 1-2016 related to the determination of the target temperature for polyphase motors must be replaced by a single target temperature of 75 °C for all insulation classes.
2.2.2. The industry standards listed in Paragraph 34.1 of NEMA MG 1-2016, “Applicable Motor Efficiency Test Methods” must correspond to the versions identified in section 0 of this appendix, specifically IEEE 112-2017, IEEE 114-2010, CSA C390-10, CSA C747-09, and IEC 60034-2-1:2014. In addition, when testing in accordance with IEC 60034-2-1:2014, the additional testing instructions in section 2.1.2 of this appendix apply.
2.3. Test Procedures for SNEMs capable of operating without an inverter. Air-over SNEMs must be tested in accordance with section 2.2. of this appendix. Inverter-only SNEMs must be tested in accordance with section 2.4. of this appendix.
2.3.1. The efficiencies and losses of single-phase SNEMs that are not air-over electric motors and are capable of operating without an inverter, are determined using one of the following methods:
2.3.1.1. IEEE 114-2010 (see section 0.8 of this appendix);
2.3.1.2. CSA C747-09 (see section 0.2 of this appendix), or
2.3.1.3. IEC 60034-2-1:2014 Method 2-1-1A (see section 0.4(a) of this appendix),. The supply voltage shall be in accordance with Section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in Section 8.6.2.3.3 of IEC 60034-1:2010, using the shortest possible time instead of the time interval specified in Table 5 of IEC 60034-1:2010, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with Section 5.2 of IEC 60051-1:2016.
2.3.1.3.1. Additional IEC 60034-2-1:2014 Method 2-1-1A Torque Measurement Instructions. If using IEC 60034-2-1:2014 Method 2-1-1A to measure motor performance, follow the instructions in section 2.3.1.3.2. of this appendix, instead of Section 6.1.2.2 of IEC 60034-2-1:2014;
2.3.1.3.2. Couple the machine under test to a load machine. Measure torque using an in-line, shaft-coupled, rotating torque transducer or stationary, stator reaction torque transducer. Operate the machine under test at the rated load until thermal equilibrium is achieved (rate of change 1 K or less per half hour). Record U, I, Pel, n, T, θc.
2.3.2. The efficiencies and losses of polyphase electric motors considered with rated horsepower less than 1 that are not air-over electric motors, and are capable of operating without an inverter, are determined using one of the following methods:
2.3.2.1. IEEE 112-2017 Test Method A (see section 0.7(a) of this appendix);
2.3.2.2. CSA C747-09 (see section 0.2 of this appendix); or
2.3.2.3. IEC 60034-2-1:2014 Method 2-1-1A (see section 0.4(a) of this appendix). The supply voltage shall be in accordance with Section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in Section 8.6.2.3.3 of IEC 60034-1:2010 using the shortest possible time instead of the time interval specified in Table 5 of IEC 60034-1:2010, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with Section 5.2 of IEC 60051-1:2016.
2.3.2.3.1. Additional IEC 60034-2-1:2014 Method 2-1-1A Torque Measurement Instructions. If using IEC 60034-2-1:2014 Method 2-1-1A to measure motor performance, follow the instructions in section 2.3.2.3.2. of this appendix, instead of Section 6.1.2.2 of IEC 60034-2-1:2014;
2.3.2.3.2. Couple the machine under test to load machine. Measure torque using an in-line shaft-coupled, rotating torque transducer or stationary, stator reaction torque transducer. Operate the machine under test at the rated load until thermal equilibrium is achieved (rate of change 1 K or less per half hour). Record U, I, Pel, n, T, θc.
2.3.3. The efficiencies and losses of polyphase SNEMs with rated horsepower equal to or greater than 1 that are not air-over electric motors, and are capable of operating without an inverter, are determined using one of the following methods:
2.3.3.1. IEEE 112-2017 Test Method B (see section 0.7(b) of this appendix);
2.3.3.2. CSA C390-10 (see section 0.1 of this appendix); or
2.3.3.3. IEC 60034-2-1:2014 Method 2-1-1B (see section 0.4(b) of this appendix). The supply voltage shall be in accordance with Section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in Section 8.6.2.3.3 of IEC 60034-1:2010 using the shortest possible time instead of the time interval specified in Table 5 of IEC 60034-1:2010, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with Section 5.2 of IEC 60051-1:2016.
2.4. Test Procedures for Electric Motors that are Synchronous Motors and Inverter-only Electric Motors
Section 2.4.1 of this appendix applies to electric motors that are synchronous motors that do not require an inverter to operate. Sections 2.4.2. and 2.4.3. of this appendix apply to electric motors that are synchronous motors and are inverter-only; and to induction electric motors that are inverter-only electric motors.
2.4.1. The efficiencies and losses of electric motors that are synchronous motors that do not require an inverter to operate, are determined in accordance with IEC 60034-2-1:2014, Section 3 “Terms and definitions,” Section 4 “Symbols and abbreviations,” Section 5 “Basic requirements,” and Section 7.1. “Preferred Testing Methods.”
2.4.2. The efficiencies and losses of electric motors (inclusive of the inverter) that are that are inverter-only and do not include an inverter, are determined in accordance with IEC 61800-9-2:2017. Test must be conducted using an inverter that is listed as recommended in the manufacturer's catalog or that is offered for sale with the electric motor. If more than one inverter is available in manufacturer's catalogs or if more than one inverter is offered for sale with the electric motor, test using the least efficient inverter. Record the manufacturer, brand and model number of the inverter used for the test. If there are no inverters specified in the manufacturer catalogs or offered for sale with the electric motor, testing must be conducted using an inverter that meets the criteria described in section 2.4.2.2. of this appendix.
2.4.2.1. The inverter shall be set up according to the manufacturer's instructional and operational manual included with the product. Manufacturers shall also record switching frequency in Hz, max frequency in Hz, Max output voltage in V, motor control method (i.e., V/f ratio, sensor less vector, etc.), load profile setting (constant torque, variable torque, etc.), and saving energy mode (if used). Deviation from the resulting settings, such as switching frequency or load torque curves for the purpose of optimizing test results shall not be permitted.
2.4.2.2. If there are no inverters specified in the manufacturer catalogs or offered for sale with the electric motor, test with a two-level voltage source inverter. No additional components influencing output voltage or output current shall be installed between the inverter and the motor, except those required for the measuring instruments. For motors with a rated speed up to 3 600 min-1, the switching frequency shall not be higher than 5 kHz. For motors with a rated speed above 3 600 min-1, the switching frequency shall not be higher than 10 kHz. Record the manufacturer, brand and model number of the inverter used for the test.
2.4.3. The efficiencies and losses of electric motors (inclusive of the inverter) that are inverter-only and include an inverter are determined in accordance with IEC 61800-9-2:2017.
2.4.3.1. The inverter shall be set up according to the manufacturer's instructional and operational manual included with the product. Manufacturers shall also record switching frequency in Hz, max frequency in Hz, Max output voltage in V, motor control method (i.e., V/f ratio, sensor less vector, etc.), load profile setting (constant torque, variable torque, etc.), and saving energy mode (if used). Deviation from the resulting settings, such as switching frequency or load torque curves for the purpose of optimizing test results shall not be permitted.
3. Procedures for the Testing of Certain Electric Motor Categories
Prior to testing according to section 2 of this appendix, each basic model of the electric motor categories listed below must be set up in accordance with the instructions of this section to ensure consistent test results. These steps are designed to enable a motor to be attached to a dynamometer and run continuously for testing purposes. For the purposes of this appendix, a “standard bearing” is a 600- or 6000-series, either open or grease-lubricated double-shielded, single-row, deep groove, radial ball bearing.
3.1. Brake Electric Motors:
Brake electric motors shall be tested with the brake component powered separately from the motor such that it does not activate during testing. Additionally, for any 10-minute period during the test and while the brake is being powered such that it remains disengaged from the motor shaft, record the power consumed (i.e., watts). Only power used to drive the motor is to be included in the efficiency calculation; power supplied to prevent the brake from engaging is not included in this calculation. In lieu of powering the brake separately, the brake may be disengaged mechanically, if such a mechanism exists and if the use of this mechanism does not yield a different efficiency value than separately powering the brake electrically.
3.2. Close-Coupled Pump Electric Motors and Electric Motors with Single or Double Shaft Extensions of Non-Standard Dimensions or Design:
To attach the unit under test to a dynamometer, close-coupled pump electric motors and electric motors with single or double shaft extensions of non-standard dimensions or design must be tested using a special coupling adapter.
3.3. Electric Motors with Non-Standard Endshields or Flanges:
If it is not possible to connect the electric motor to a dynamometer with the non-standard endshield or flange in place, the testing laboratory shall replace the non-standard endshield or flange with an endshield or flange meeting NEMA or IEC specifications. The replacement component should be obtained from the manufacturer or, if the manufacturer chooses, machined by the testing laboratory after consulting with the manufacturer regarding the critical characteristics of the endshield.
3.4. Electric Motors with Non-Standard Bases, Feet or Mounting Configurations:
An electric motor with a non-standard base, feet, or mounting configuration may be mounted on the test equipment using adaptive fixtures for testing as long as the mounting or use of adaptive mounting fixtures does not have an adverse impact on the performance of the electric motor, particularly on the cooling of the motor.
3.5. Electric Motors with a Separately-Powered Blower:
For electric motors furnished with a separately-powered blower, the losses from the blower's motor should not be included in any efficiency calculation. This can be done either by powering the blower's motor by a source separate from the source powering the electric motor under test or by connecting leads such that they only measure the power of the motor under test.
3.6. Immersible Electric Motors:
Immersible electric motors shall be tested with all contact seals removed but be otherwise unmodified.
3.7. Partial Electric Motors:
Partial electric motors shall be disconnected from their mated piece of equipment. After disconnection from the equipment, standard bearings and/or endshields shall be added to the motor, such that it is capable of operation. If an endshield is necessary, an endshield meeting NEMA or IEC specifications should be obtained from the manufacturer or, if the manufacturer chooses, machined by the testing laboratory after consulting with the manufacturer regarding the critical characteristics of the endshield.
3.8. Vertical Electric Motors and Electric Motors with Bearings Incapable of Horizontal Operation:
Vertical electric motors and electric motors with thrust bearings shall be tested in a horizontal or vertical configuration in accordance with the applicable test procedure under section 2 through section 2.4.3. of this appendix, depending on the testing facility's capabilities and construction of the motor, except if the motor is a vertical solid shaft normal thrust general purpose electric motor (subtype II), in which case it shall be tested in a horizontal configuration in accordance with the applicable test procedure under section 2 through section 2.4.3. of this appendix. Preference shall be given to testing a motor in its native orientation. If the unit under test cannot be reoriented horizontally due to its bearing construction, the electric motor's bearing(s) shall be removed and replaced with standard bearings. If the unit under test contains oil-lubricated bearings, its bearings shall be removed and replaced with standard bearings. If necessary, the unit under test may be connected to the dynamometer using a coupling of torsional rigidity greater than or equal to that of the motor shaft.
[87 FR 63657, Oct. 19, 2022]
Certification of Compliance With Energy Efficiency Standards for Electric Motors (Office of Management and Budget Control Number: 1910-1400. Expires February 13, 2014)
An electronic form is available at https://www.regulations.doe.gov/ccms/.
1. Name and Address of Company (the “company”):
2. Name(s) to be Marked on Electric Motors to Which this Compliance Certification Applies:
3. If manufacturer or private labeler wishes to receive a unique Compliance Certification number for use with any particular brand name, trademark, or other label name, fill out the following two items:
A. List each brand name, trademark, or other label name for which the company requests a Compliance Certification number:
B. List other name(s), if any, under which the company sells electric motors (if not listed in item 2 above):
Submit electronically at https://www.regulations.doe.gov/ccms.
Submit paper form by Certified Mail to: U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies (EE-2J), Forrestal Building, 1000 Independence Avenue, SW., Washington, DC 20585-0121.
This Compliance Certification reports on and certifies compliance with requirements contained in 10 CFR Part 431 (Energy Conservation Program for Certain Commercial and Industrial Equipment) and Part C of the Energy Policy and Conservation Act (Pub. L. 94-163), and amendments thereto. It is signed by a responsible official of the above named company. Attached and incorporated as part of this Compliance Certification is a Listing of Electric Motor Efficiencies. For each rating of electric motor* for which the Listing specifies the nominal full load efficiency of a basic model, the company distributes no less efficient basic model with that rating and all basic models with that rating comply with the applicable energy efficiency standard.
* For this purpose, the term “rating” means one of the combinations of an electric motor's horsepower (or standard kilowatt equivalent), number of poles, motor type, and open or enclosed construction, with respect to which § 431.25 of 10 CFR Part 431 prescribes nominal full load efficiency standards.
Person to Contact for Further Information:
Name:
Address:
Telephone Number:
Facsimile Number:
If any part of this Compliance Certification, including the Attachment, was prepared by a third party organization under the provisions of 10 CFR 431.36, the company official authorizing third party representations:
Name:
Address:
Telephone Number:
Facsimile Number:
Third Party Organization Officially Acting as Representative:
Third Party Organization:
Responsible Person at the Organization:
Address:
Telephone Number:
Facsimile Number:
All required determinations on which this Compliance Certification is based were made in conformance with the applicable requirements in 10 CFR Part 431, subpart B. All information reported in this Compliance Certification is true, accurate, and complete. The company is aware of the penalties associated with violations of the Act and the regulations thereunder, and is also aware of the provisions contained in 18 U.S.C. 1001, which prohibits knowingly making false statements to the Federal Government.
Signature:
Date:
Name:
Title:
Firm or Organization:
Attachment of Certification of Compliance With Energy Efficiency Standards for Electric Motor Efficiencies
Date:
Name of Company:
Motor Type (i.e., general purpose electric motor (subtype I), fire pump electric motor, general purpose electric motor (subtype II), NEMA Design B general purpose electric motor)
| Motor horsepower/standard kilowatt equivalent | Least efficient basic model—(model numbers(s)) Nominal full-load efficiency |
|||||||
|---|---|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||||
| 8 | 6 | 4 | 2 | 8 | 6 | 4 | 2 | |
| 1/.75 | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| 1.5/1.1 | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| 2/1.5 | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| 3/2.2 | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| 5/3.7 | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| Etc | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| Note: Place an asterisk beside each reported nominal full load efficiency that is determined by actual testing rather than by application of an alternative efficiency determination method. Also list below additional basic models that were subjected to actual testing. | ||||||||
Basic Model means all units of a given type of electric motor (or class thereof) manufactured by a single manufacturer, and which
(i) have the same rating,
(ii) have electrical design characteristics that are essentially identical, and
(iii) do not have any differing physical or functional characteristics that affect energy consumption or efficiency.
Rating means one of the combinations of an electric motor's horsepower (or standard kilowatt equivalent), number of poles, motor type, and open or enclosed construction, with respect to which § 431.25 of 10 CFR Part 431 prescribes nominal full load efficiency standards.
| Motor horsepower/standard kilowatt equivalent | Least efficient basic model—(model numbers(s)) Nominal full-load efficiency |
|||||||
|---|---|---|---|---|---|---|---|---|
| Open motors (number of poles) |
Enclosed motors (number of poles) |
|||||||
| 8 | 6 | 4 | 2 | 8 | 6 | 4 | 2 | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
| Etc | ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ |
| ______ | ______ | ______ | ______ | ______ | ______ | ______ | ______ | |
[69 FR 61923, Oct. 21, 2004, as amended at 76 FR 59006, Sept. 23, 2011]
70 FR 60414, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for commercial refrigerators, freezers and refrigerator-freezers, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
Air-curtain angle means:
(1) For equipment without doors and without a discharge air grille or discharge air honeycomb, the angle between a vertical line extended down from the highest point on the manufacturer's recommended load limit line and the load limit line itself, when the equipment is viewed in cross-section; and
(2) For all other equipment without doors, the angle formed between a vertical line and the straight line drawn by connecting the point at the inside edge of the discharge air opening with the point at the inside edge of the return air opening, when the equipment is viewed in cross-section.
Basic model means all commercial refrigeration equipment manufactured by one manufacturer within a single equipment class, having the same primary energy source, and that have essentially identical electrical, physical, and functional characteristics that affect energy consumption.
Blast chiller means commercial refrigeration equipment, other than a blast freezer, that is capable of the rapid temperature pull-down of hot food products from 135 °F to 40 °F within a period of four hours, when measured according to the test procedure at appendix D to subpart C of part 431.
Blast freezer means commercial refrigeration equipment that is capable of the rapid temperature pull-down of hot food products from 135 °F to 40 °F within a period of four hours and capable of achieving a final product temperature of less than 32 °F, when measured according to the test procedure at appendix D to subpart C of this part.
Buffet table or preparation table means a commercial refrigerator with an open-top refrigerated area, that may or may not include a lid, for displaying or storing merchandise and other perishable materials in pans or other removable containers for customer self-service or food production and assembly. The unit may or may not be equipped with a refrigerated storage compartment underneath the pans or other removable containers that is not thermally separated from the open-top refrigerated area.
Chef base or griddle stand means commercial refrigeration equipment that has a maximum height of 32 in., including any legs or casters, and that is designed and marketed for the express purpose of having a griddle or other cooking appliance placed on top of it that is capable of reaching temperatures hot enough to cook food.
Closed solid means equipment with doors, and in which more than 75 percent of the outer surface area of all doors on a unit are not transparent.
Closed transparent means equipment with doors, and in which 25 percent or more of the outer surface area of all doors on the unit are transparent.
Commercial freezer means a unit of commercial refrigeration equipment in which all refrigerated compartments in the unit are capable of operating below 32 °F (±2 °F).
Commercial hybrid means a unit of commercial refrigeration equipment:
(1) That consists of two or more thermally separated refrigerated compartments that are in two or more different equipment families, and
(2) That is sold as a single unit.
Commercial refrigerator means a unit of commercial refrigeration equipment in which all refrigerated compartments in the unit are capable of operating at or above 32 °F (±2 °F).
Commercial refrigerator-freezer means a unit of commercial refrigeration equipment consisting of two or more refrigerated compartments where at least one refrigerated compartment is capable of operating at or above 32 °F (±2 °F) and at least one refrigerated compartment is capable of operating below 32 °F (±2 °F).
Commercial refrigerator, freezer, and refrigerator-freezer means refrigeration equipment that—
(1) Is not a consumer product (as defined in § 430.2 of this chapter);
(2) Is not designed and marketed exclusively for medical, scientific, or research purposes;
(3) Operates at a chilled, frozen, combination chilled and frozen, or variable temperature;
(4) Displays or stores merchandise and other perishable materials horizontally, semi-vertically, or vertically;
(5) Has transparent or solid doors, sliding or hinged doors, a combination of hinged, sliding, transparent, or solid doors, or no doors;
(6) Is designed for pull-down temperature applications or holding temperature applications; and
(7) Is connected to a self-contained condensing unit or to a remote condensing unit.
Customer order storage cabinet means a commercial refrigerator, freezer, or refrigerator-freezer that stores customer orders and includes individual, secured compartments with doors that are accessible to customers for order retrieval.
Door means a movable panel that separates the interior volume of a unit of commercial refrigeration equipment from the ambient environment and is designed to facilitate access to the refrigerated space for the purpose of loading and unloading product. This includes hinged doors, sliding doors, and drawers. This does not include night curtains.
Door angle means:
(1) For equipment with flat doors, the angle between a vertical line and the line formed by the plane of the door, when the equipment is viewed in cross-section; and
(2) For equipment with curved doors, the angle formed between a vertical line and the straight line drawn by connecting the top and bottom points where the display area glass joins the cabinet, when the equipment is viewed in cross-section.
Fully open (for drawers) means opened not less than 80% of their full travel.
High-temperature refrigerator means a commercial refrigerator that is not capable of an operating temperature at or below 40.0 °F.
Holding temperature application means a use of commercial refrigeration equipment other than a pull-down temperature application, except a blast chiller or freezer.
Horizontal Closed means equipment with hinged or sliding doors and a door angle greater than or equal to 45°.
Horizontal Open means equipment without doors and an air-curtain angle greater than or equal to 80° from the vertical.
Ice-cream freezer means:
(1) Prior to the compliance date(s) of any amended energy conservation standard(s) issued after January 1, 2023 for ice-cream freezers (see § 431.66), a commercial freezer that is capable of an operating temperature at or below −5.0 °F and that the manufacturer designs, markets, or intends specifically for the storing, displaying, or dispensing of ice cream or other frozen desserts; or
(2) Upon the compliance date(s) of any amended energy conservation standard(s) issued after January 1, 2023 for ice-cream freezers (see § 431.66), a commercial freezer that is capable of an operating temperature at or below −13.0 °F and that the manufacturer designs, markets, or intends specifically for the storing, displaying, or dispensing of ice cream or other frozen desserts.
Integrated average temperature means the average temperature of all test package measurements taken during the test.
Lighting occupancy sensor means a device which uses passive infrared, ultrasonic, or other motion-sensing technology to automatically turn off or dim lights within the equipment when no motion is detected in the sensor's coverage area for a certain preset period of time.
Lowest application product temperature means the integrated average temperature (or for buffet tables or preparation tables, the average pan temperature of all measurements taken during the test) at which a given basic model is capable of consistently operating that is closest to the integrated average temperature (or for buffet tables or preparation tables, the average pan temperature of all measurements taken during the test) specified for testing under the DOE test procedure (see § 431.64).
Low-temperature freezer means a commercial freezer that is not an ice-cream freezer.
Medium-temperature refrigerator means a commercial refrigerator that is capable of an operating temperature at or below 40.0 °F.
Mobile refrigerated cabinet means commercial refrigeration equipment that is designed and marketed to operate only without a continuous power supply.
Night curtain means a device which is temporarily deployed to decrease air exchange and heat transfer between the refrigerated case and the surrounding environment.
Operating temperature means the range of integrated average temperatures at which a self-contained commercial refrigeration unit or remote-condensing commercial refrigeration unit with a thermostat is capable of operating or, in the case of a remote-condensing commercial refrigeration unit without a thermostat, the range of integrated average temperatures at which the unit is marketed, designed, or intended to operate.
Pull-down temperature application means a commercial refrigerator with doors that, when fully loaded with 12-ounce beverage cans at 90 degrees F, can cool those beverages to an average stable temperature of 38 degrees F in 12 hours or less.
Rating temperature means the integrated average temperature a unit must maintain during testing (i.e., either as listed in the table at § 431.66(d)(1) or the lowest application product temperature).
Remote condensing unit means a factory-made assembly of refrigerating components designed to compress and liquefy a specific refrigerant that is remotely located from the refrigerated equipment and consists of one or more refrigerant compressors, refrigerant condensers, condenser fans and motors, and factory supplied accessories.
Scheduled lighting control means a device which automatically shuts off or dims the lighting in a display case at scheduled times throughout the day.
Self-contained condensing unit means a factory-made assembly of refrigerating components designed to compress and liquefy a specific refrigerant that is an integral part of the refrigerated equipment and consists of one or more refrigerant compressors, refrigerant condensers, condenser fans and motors, and factory-supplied accessories.
Semivertical Open means equipment without doors and an air-curtain angle greater than or equal to 10° and less than 80° from the vertical.
Service over counter means equipment that has sliding or hinged doors in the back intended for use by sales personnel, with glass or other transparent material in the front for displaying merchandise, and that has a height not greater than 66 in. and is intended to serve as a counter for transactions between sales personnel and customers.
Test package means a packaged material that is used as a standard product temperature-measuring device.
Transparent means greater than or equal to 45 percent light transmittance, as determined in accordance with ASTM E1084-86 (Reapproved 2009) (incorporated by reference, see § 431.63) at normal incidence and in the intended direction of viewing.
Vertical Closed means equipment with hinged or sliding doors and a door angle less than 45°.
Vertical Open means equipment without doors and an air-curtain angle greater than or equal to 0° and less than 10° from the vertical.
Wedge case means a commercial refrigerator, freezer, or refrigerator-freezer that forms the transition between two regularly shaped display cases.
[88 FR 66222, Sept. 26, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Avenue SW, EE-5B, Washington, DC 20024, (202)-586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email: fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section:
(b) ANSI. American National Standards Institute, 25 W. 43rd Street, 4th Floor, New York, NY 10036, 212-642-4900, or go to http://www.ansi.org:
(1) ANSI /AHAM HRF-1-2004, Energy, Performance and Capacity of Household Refrigerators, Refrigerator-Freezers and Freezers, approved July 7, 2004, IBR approved for § 431.64 and appendices A and B to subpart C to part 431.
(2) AHAM HRF-1-2008 (“HRF-1-2008”), Association of Home Appliance Manufacturers, Energy and Internal Volume of Refrigerating Appliances (2008) including Errata to Energy and Internal Volume of Refrigerating Appliances, Correction Sheet issued November 17, 2009, IBR approved for § 431.64 and appendices A and B to subpart C to part 431.
(c) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Blvd., Suite 500, Arlington, VA 22201; (703) 524-8800; ahri@ahrinet.org; www.ahrinet.org/.
(1) ARI Standard 1200-2006, Performance Rating of Commercial Refrigerated Display Merchandisers and Storage Cabinets, 2006; IBR approved for § 431.66.
(2) AHRI Standard 1200 (I-P)-2010 (“AHRI Standard 1200 (I-P)-2010”), 2010 Standard for Performance Rating of Commercial Refrigerated Display Merchandisers and Storage Cabinets, 2010; IBR approved for § 431.66.
(3) AHRI Standard 1200-2023 (I-P) (“AHRI 1200-2023”), 2023 Standard for Performance Rating of Commercial Refrigerated Display Merchandisers and Storage Cabinets, copyright 2023; IBR approved for appendices B, C, and D to this subpart.
(4) AHRI Standard 1320-2011 (I-P), (“AHRI 1320-2011”) 2011 Standard for Performance Rating of Commercial Refrigerated Display Merchandisers and Storage Cabinets for Use With Secondary Refrigerants, copyright 2011; IBR approved for appendix B to this subpart.
(d) ASHRAE. The American Society of Heating, Refrigerating, and Air-Conditioning Engineers, Inc., 1971 Tullie Circle NE, Atlanta, GA 30329; (404) 636-8400; ashrae@ashrae.org; www.ashrae.org/.
(1) ANSI/ASHRAE Standard 72-2022 (ASHRAE 72-2022), Method of Testing Open and Closed Commercial Refrigerators and Freezers, approved June 30, 2022; IBR approved for appendices B, C, and D to this subpart.
(2) Errata sheet for ANSI/ASHRAE Standard 72-2022 (ASHRAE 72-2022 Errata), Method of Testing Open and Closed Commercial Refrigerators and Freezers, November 11, 2022; IBR approved for appendices B, C, and D to this subpart.
(e) ASTM. ASTM International, 100 Barr Harbor Drive, P.O. Box C700, West Conshohocken, PA 19428; (877) 909-2786; www.astm.org/.
(1) ASTM E1084-86 (Reapproved 2009), Standard Test Method for Solar Transmittance (Terrestrial) of Sheet Materials Using Sunlight, approved April 1, 2009; IBR approved for § 431.62.
(2) ASTM F2143-16, Standard Test Method for Performance of Refrigerated Buffet and Preparation Tables, approved May 1, 2016; IBR approved for appendix C to this subpart.
[74 FR 1139, Jan. 9, 2009, as amended at 77 FR 10318, Feb. 21, 2012; 78 FR 62993, Oct. 23, 2013; 79 FR 22308, Apr. 21, 2014; 88 FR 66224, Sept. 26, 2023]
(a) Scope. This section provides the test procedures for measuring, pursuant to EPCA, the energy consumption or energy efficiency for a given equipment category of commercial refrigerators, freezers, and refrigerator-freezers.
(b) Testing and calculations.
(1) Determine the daily energy consumption and volume or total display area of each covered commercial refrigerator, freezer, or refrigerator-freezer by conducting the appropriate test procedure set forth below in appendix B, to this subpart. The daily energy consumption of commercial refrigeration equipment shall be calculated using raw measured values and the final test results shall be reported in increments of 0.01 kWh/day.
(2) Determine the daily energy consumption and pan storage volume, pan display area, and refrigerated volume of each buffet table or preparation table by conducting the appropriate test procedure set forth below in appendix C to this subpart. The daily energy consumption shall be calculated using raw measured values and the final test results shall be recorded in increments of 0.01 kWh/day.
(3) Determine the energy consumption per weight of product and product capacity of each blast chiller and blast freezer by conducting the appropriate test procedure set forth below in appendix D to this subpart. The energy consumption per weight of product shall be calculated using raw measured values and the final test results shall be recorded in increments of 0.01 kWh/lb.
[88 FR 66225, Sept. 26, 2023]
(a) In this section—
(1) The term “AV” means the adjusted volume (ft3) (defined as 1.63 × frozen temperature compartment volume (ft3) + chilled temperature compartment volume (ft3)) with compartment volumes measured in accordance with the Association of Home Appliance Manufacturers Standard HRF1-1979.
(2) The term “V” means the chilled or frozen compartment volume (ft3) (as defined in the Association of Home Appliance Manufacturers Standard HRF1-1979).
(3) For the purpose of paragraph (d) of this section, the term “TDA” means the total display area (ft2) of the case, as defined in ARI Standard 1200-2006, appendix D (incorporated by reference, see § 431.63). For the purpose of paragraph (e) of this section, the term “TDA” means the total display area (ft2) of the case, as defined in AHRI Standard 1200 (I-P)-2010, appendix D (incorporated by reference, see § 431.63).
(b)
(1) Each commercial refrigerator, freezer, and refrigerator-freezer with a self-contained condensing unit designed for holding temperature applications manufactured on or after January 1, 2010 and before March 27, 2017 shall have a daily energy consumption (in kilowatt-hours per day) that does not exceed the following:
| Category | Maximum daily energy consumption (kilowatt hours per day) |
|---|---|
| Refrigerators with solid doors | 0.10V + 2.04. |
| Refrigerators with transparent doors | 0.12V + 3.34. |
| Freezers with solid doors | 0.40V + 1.38. |
| Freezers with transparent doors | 0.75V + 4.10. |
| Refrigerator/freezers with solid doors | the greater of 0.27AV-0.71 or 0.70. |
(2) Each service over the counter, self-contained, medium temperature commercial refrigerator (SOC-SC-M) manufactured on or after January 1, 2012, shall have a total daily energy consumption (in kilowatt hours per day) of not more than 0.6 × TDA + 1.0. As used in the preceding sentence, “TDA” means the total display area (ft2) of the case, as defined in the AHRI Standard 1200 (I-P)-2010, appendix D (incorporated by reference, see § 431.63).
(c) Each commercial refrigerator with a self-contained condensing unit designed for pull-down temperature applications and transparent doors manufactured on or after January 1, 2010 and before March 27, 2017 shall have a daily energy consumption (in kilowatt-hours per day) of not more than 0.126V + 3.51.
(d) Each commercial refrigerator, freezer, and refrigerator-freezer with a self-contained condensing unit and without doors; commercial refrigerator, freezer, and refrigerator-freezer with a remote condensing unit; and commercial ice-cream freezer manufactured on or after January 1, 2012 and before March 27, 2017 shall have a daily energy consumption (in kilowatt-hours per day) that does not exceed the levels specified:
(1) For equipment other than hybrid equipment, refrigerator-freezers or wedge cases:
| Equipment category | Condensing unit configuration |
Equipment family |
Rating temp. (°F) |
Operating temp. (°F) |
Equipment class designation * |
Maximum daily energy consumption (kWh/day) |
|---|---|---|---|---|---|---|
| Remote Condensing Commercial Refrigerators and Commercial Freezers | Remote (RC) | Vertical Open (VOP) | 38 (M) 0 (L) |
≥32±2 <32±2 |
VOP.RC.M VOP.RC.L |
0.82 × TDA + 4.07 2.27 × TDA + 6.85 |
| Semivertical Open (SVO) | 38 (M) 0 (L) |
≥32±2 <32±2 |
SVO.RC.M SVO.RC.L |
0.83 × TDA + 3.18 2.27 × TDA + 6.85 |
||
| Horizontal Open (HZO) | 38 (M) 0 (L) |
≥32±2 <32±2 |
HZO.RC.M HZO.RC.L |
0.35 × TDA + 2.88 0.57 × TDA + 6.88 |
||
| Vertical Closed Transparent (VCT) | 38 (M) 0 (L) |
≥32±2 <32±2 |
VCT.RC.M VCT.RC.L |
0.22 × TDA + 1.95 0.56 × TDA + 2.61 |
||
| Horizontal Closed Transparent (HCT) | 38 (M) 0 (L) |
≥32±2 <32±2 |
HCT.RC.M HCT.RC.L |
0.16 × TDA + 0.13 0.34 × TDA + 0.26 |
||
| Vertical Closed Solid (VCS) | 38 (M) 0 (L) |
≥32±2 <32±2 |
VCS.RC.M VCS.RC.L |
0.11 × V + 0.26 0.23 × V + 0.54 |
||
| Horizontal Closed Solid (HCS) | 38 (M) 0 (L) |
≥32±2 <32±2 |
HCS.RC.M HCS.RC.L |
0.11 × V + 0.26 0.23 × V + 0.54 |
||
| Service Over Counter (SOC) | 38 (M) 0 (L) |
≥32±2 <32±2 |
SOC.RC.M SOC.RC.L |
0.51 × TDA + 0.11 1.08 × TDA + 0.22 |
||
| Self-Contained Commercial Refrigerators and Commercial Freezers without Doors | Self-Contained (SC) | Vertical Open (VOP) | 38 (M) 0 (L) |
≥32±2 <32±2 |
VOP.SC.M VOP.SC.L |
1.74 × TDA + 4.71 4.37 × TDA + 11.82 |
| Semivertical Open (SVO) | 38 (M) 0 (L) |
≥32±2 <32±2 |
SVO.SC.M SVO.SC.L |
1.73 × TDA + 4.59 4.34 × TDA + 11.51 |
||
| Horizontal Open | 38 (M) 0 (L) |
≥32±2 <32±2 |
HZO.SC.M HZO.SC.L |
0.77 × TDA + 5.55 1.92 × TDA + 7.08 |
||
| Commercial Ice-Cream Freezers | Remote (RC) | Vertical Open (VOP) | −15 (I) | ≤−5±2** ** | VOP.RC.I | 2.89 × TDA + 8.7 |
| Semivertical Open (SVO) | SVO.RC.I | 2.89 × TDA + 8.7 | ||||
| Horizontal Open (HZO) | HZO.RC.I | 0.72 × TDA + 8.74 | ||||
| Vertical Closed Transparent (VCT) | VCT.RC.I | 0.66 × TDA + 3.05 | ||||
| Horizontal Closed Transparent (HCT) | HCT.RC.I | 0.4 × TDA + 0.31 | ||||
| Vertical Closed Solid (VCS) | VCS.RC.I | 0.27 × V + 0.63 | ||||
| Horizontal Closed Solid (HCS) | HCS.RC.I | 0.27 × V + 0.63 | ||||
| Service Over Counter (SVO) | SOC.RC.I | 1.26 × TDA + 0.26 | ||||
| Self-Contained (SC) | Vertical Open (VOP) | VOP.SC.I | 5.55 × TDA + 15.02 | |||
| Semivertical Open (SVO) | SVO.SC.I | 5.52 × TDA + 14.63 | ||||
| Horizontal Open (HZO) | HZO.SC.I | 2.44 × TDA + 9 | ||||
| Vertical Closed Transparent (VCT) | VCT.SC.I | 0.67 × TDA + 3.29 | ||||
| Horizontal Closed Transparent (HCT) | HCT.SC.I | 0.56 × TDA + 0.43 | ||||
| Vertical Closed Solid (VCS) | VCS.SC.I | 0.38 × V + 0.88 | ||||
| Horizontal Closed Solid (HCS) | HCS.SC.I | 0.38 × V + 0.88 | ||||
| Service Over Counter (SVO) | SOC.SC.I | 1.76 × TDA + 0.36 | ||||
| * The meaning of the letters in this column is indicated in the three columns to the left. | ||||||
| ** Ice-cream freezer is defined in 10 CFR 431.62 as a commercial freezer that is designed to operate at or below −5 °F (−21 °C) and that the manufacturer designs, markets, or intends for the storing, displaying, or dispensing of ice cream. | ||||||
(2) For commercial refrigeration equipment with two or more compartments (i.e., hybrid refrigerators, hybrid freezers, hybrid refrigerator-freezers, and non-hybrid refrigerator-freezers), the maximum daily energy consumption (MDEC) for each model shall be the sum of the MDEC values for all of its compartments. For each compartment, measure the TDA or volume of that compartment, and determine the appropriate equipment class based on that compartment's equipment family, condensing unit configuration, and designed operating temperature. The MDEC limit for each compartment shall be the calculated value obtained by entering that compartment's TDA or volume into the standard equation in paragraph (d)(1) of this section for that compartment's equipment class. Measure the calculated daily energy consumption (CDEC) or total daily energy consumption (TDEC) for the entire case:
(i) For remote condensing commercial hybrid refrigerators, hybrid freezers, hybrid refrigerator-freezers, and non-hybrid refrigerator-freezers, where two or more independent condensing units each separately cool only one compartment, measure the total refrigeration load of each compartment separately according to the ARI Standard 1200-2006 test procedure (incorporated by reference, see § 431.63). Calculate compressor energy consumption (CEC) for each compartment using Table 1 in ARI Standard 1200-2006 using the saturated evaporator temperature for that compartment. The CDEC for the entire case shall be the sum of the CEC for each compartment, fan energy consumption (FEC), lighting energy consumption (LEC), anti-condensate energy consumption (AEC), defrost energy consumption (DEC), and condensate evaporator pan energy consumption (PEC) (as measured in ARI Standard 1200-2006).
(ii) For remote condensing commercial hybrid refrigerators, hybrid freezers, hybrid refrigerator-freezers, and non-hybrid refrigerator-freezers, where two or more compartments are cooled collectively by one condensing unit, measure the total refrigeration load of the entire case according to the ARI Standard 1200-2006 test procedure (incorporated by reference, see § 431.63). Calculate a weighted saturated evaporator temperature for the entire case by:
(A) Multiplying the saturated evaporator temperature of each compartment by the volume of that compartment (as measured in ARI Standard 1200-2006),
(B) Summing the resulting values for all compartments, and
(C) Dividing the resulting total by the total volume of all compartments.
Calculate the CEC for the entire case using Table 1 in ARI Standard 1200-2006 (incorporated by reference, see § 431.63), using the total refrigeration load and the weighted average saturated evaporator temperature. The CDEC for the entire case shall be the sum of the CEC, FEC, LEC, AEC, DEC, and PEC.
(iii) For self-contained commercial hybrid refrigerators, hybrid freezers, hybrid refrigerator-freezers, and non-hybrid refrigerator-freezers, measure the TDEC for the entire case according to the ARI Standard 1200-2006 test procedure (incorporated by reference, see § 431.63).
(3) For remote-condensing and self-contained wedge cases, measure the CDEC or TDEC according to the ARI Standard 1200-2006 test procedure (incorporated by reference, see § 431.63). The MDEC for each model shall be the amount derived by incorporating into the standards equation in paragraph (d)(1) of this section for the appropriate equipment class a value for the TDA that is the product of:
(i) The vertical height of the air-curtain (or glass in a transparent door) and
(ii) The largest overall width of the case, when viewed from the front.
(e) Each commercial refrigerator, freezer, and refrigerator-freezer with a self-contained condensing unit designed for holding temperature applications and with solid or transparent doors; commercial refrigerator with a self-contained condensing unit designed for pull-down temperature applications and with transparent doors; commercial refrigerator, freezer, and refrigerator-freezer with a self-contained condensing unit and without doors; commercial refrigerator, freezer, and refrigerator-freezer with a remote condensing unit; and commercial ice-cream freezer manufactured on or after March 27, 2017, shall have a daily energy consumption (in kilowatt-hours per day) that does not exceed the levels specified:
(1) For equipment other than hybrid equipment, refrigerator/freezers, or wedge cases:
| Equipment category | Condensing unit configuration |
Equipment family |
Rating temp. °F |
Operating temp. °F |
Equipment class designation * |
Maximum daily energy consumption kWh/day |
|---|---|---|---|---|---|---|
| Remote Condensing Commercial Refrigerators and Commercial Freezers | Remote (RC) | Vertical Open (VOP) | 38 (M) | ≥32 | VOP.RC.M | 0.64 × TDA + 4.07. |
| 0 (L) | <32 | VOP.RC.L | 2.2 × TDA + 6.85. | |||
| Semivertical Open (SVO) | 38 (M) | ≥32 | SVO.RC.M | 0.66 × TDA + 3.18. | ||
| 0 (L) | <32 | SVO.RC.L | 2.2 × TDA + 6.85. | |||
| Horizontal Open (HZO) | 38 (M) | ≥32 | HZO.RC.M | 0.35 × TDA + 2.88. | ||
| 0 (L) | <32 | HZO.RC.L | 0.55 × TDA + 6.88. | |||
| Vertical Closed Transparent (VCT) | 38 (M) | ≥32 | VCT.RC.M | 0.15 × TDA + 1.95. | ||
| 0 (L) | <32 | VCT.RC.L | 0.49 × TDA + 2.61. | |||
| Horizontal Closed Transparent (HCT) | 38 (M) | ≥32 | HCT.RC.M | 0.16 × TDA + 0.13. | ||
| 0 (L) | <32 | HCT.RC.L | 0.34 × TDA + 0.26. | |||
| Vertical Closed Solid (VCS) | 38 (M) | ≥32 | VCS.RC.M | 0.1 × V + 0.26. | ||
| 0 (L) | <32 | VCS.RC.L | 0.21 × V + 0.54. | |||
| Horizontal Closed Solid (HCS) | 38 (M) | ≥32 | HCS.RC.M | 0.1 × V + 0.26. | ||
| 0 (L) | <32 | HCS.RC.L | 0.21 × V + 0.54. | |||
| Service Over Counter (SOC) | 38 (M) | ≥32 | SOC.RC.M | 0.44 × TDA + 0.11. | ||
| 0 (L) | <32 | SOC.RC.L | 0.93 × TDA + 0.22. | |||
| Self-Contained Commercial Refrigerators and Commercial Freezers Without Doors | Self-Contained (SC) | Vertical Open (VOP) | 38 (M) | ≥32 | VOP.SC.M | 1.69 × TDA + 4.71. |
| 0 (L) | <32 | VOP.SC.L | 4.25 × TDA + 11.82. | |||
| Semivertical Open (SVO) | 38 (M) | ≥32 | SVO.SC.M | 1.7 × TDA + 4.59. | ||
| 0 (L) | <32 | SVO.SC.L | 4.26 × TDA + 11.51. | |||
| Horizontal Open (HZO) | 38 (M) | ≥32 | HZO.SC.M | 0.72 × TDA + 5.55. | ||
| 0 (L) | <32 | HZO.SC.L | 1.9 × TDA + 7.08. | |||
| Self-Contained Commercial Refrigerators and Commercial Freezers With Doors | Self-Contained (SC) | Vertical Closed Transparent (VCT) | 38 (M) | ≥32 | VCT.SC.M | 0.1 × V + 0.86. |
| 0 (L) | <32 | VCT.SC.L | 0.29 × V + 2.95. | |||
| Vertical Closed Solid (VCS) | 38 (M) | ≥32 | VCS.SC.M | 0.05 × V + 1.36. | ||
| <32 | VCS.SC.L | 0.22 × V + 1.38. | ||||
| Horizontal Closed Transparent (HCT) | 38 (M) | ≥32 | HCT.SC.M | 0.06 × V + 0.37. | ||
| 0 (L) | <32 | HCT.SC.L | 0.08 × V + 1.23. | |||
| Horizontal Closed Solid (HCS) | ≥32 | HCS.SC.M | 0.05 × V + 0.91. | |||
| 0 (L) | <32 | HCS.SC.L | 0.06 × V + 1.12. | |||
| Service Over Counter (SOC) | ≥32 | SOC.SC.M | 0.52 × TDA + 1. | |||
| 0 (L) | <32 | SOC.SC.L | 1.1 × TDA + 2.1. | |||
| Self-Contained Commercial Refrigerators with Transparent Doors for Pull-Down Temperature Applications | Self-Contained (SC) | Pull-Down (PD) | 38 (M) | ≥32 | PD.SC.M | 0.11 × V + 0.81. |
| Commercial Ice-Cream Freezers | Remote (RC) | Vertical Open (VOP) | −15 (I) | ≤−5** | VOP.RC.I | 2.79 × TDA + 8.7. |
| Semivertical Open (SVO) | SVO.RC.I | 2.79 × TDA + 8.7. | ||||
| Horizontal Open (HZO) | HZO.RC.I | 0.7 × TDA + 8.74. | ||||
| Vertical Closed Transparent (VCT) | VCT.RC.I | 0.58 × TDA + 3.05. | ||||
| Horizontal Closed Transparent (HCT) | HCT.RC.I | 0.4 × TDA + 0.31. | ||||
| Vertical Closed Solid (VCS) | VCS.RC.I | 0.25 × V + 0.63. | ||||
| Horizontal Closed Solid (HCS) | HCS.RC.I | 0.25 × V + 0.63. | ||||
| Service Over Counter (SOC) | SOC.RC.I | 1.09 × TDA + 0.26. | ||||
| Self-Contained (SC) | Vertical Open (VOP) | VOP.SC.I | 5.4 × TDA + 15.02. | |||
| Semivertical Open (SVO) | SVO.SC.I | 5.41 × TDA + 14.63. | ||||
| Horizontal Open (HZO) | HZO.SC.I | 2.42 × TDA + 9. | ||||
| Vertical Closed Transparent (VCT) | VCT.SC.I | 0.62 × TDA + 3.29. | ||||
| Horizontal Closed Transparent (HCT) | HCT.SC.I | 0.56 × TDA + 0.43. | ||||
| Vertical Closed Solid (VCS) | VCS.SC.I | 0.34 × V + 0.88. | ||||
| Horizontal Closed Solid (HCS) | HCS.SC.I | 0.34 × V + 0.88. | ||||
| Service Over Counter (SOC) | SOC.SC.I | 1.53 × TDA + 0.36. | ||||
| * The meaning of the letters in this column is indicated in the columns to the left. | ||||||
| ** Ice-cream freezer is defined in 10 CFR 431.62 as a commercial freezer that is designed to operate at or below −5 °F *(−21 °C) and that the manufacturer designs, markets, or intends for the storing, displaying, or dispensing of ice cream. | ||||||
(2) For commercial refrigeration equipment with two or more compartments (i.e., hybrid refrigerators, hybrid freezers, hybrid refrigerator-freezers, and non-hybrid refrigerator-freezers), the maximum daily energy consumption for each model shall be the sum of the MDEC values for all of its compartments. For each compartment, measure the TDA or volume of that compartment, and determine the appropriate equipment class based on that compartment's equipment family, condensing unit configuration, and designed operating temperature. The MDEC limit for each compartment shall be the calculated value obtained by entering that compartment's TDA or volume into the standard equation in paragraph (e)(1) of this section for that compartment's equipment class. Measure the CDEC or TDEC for the entire case as described in § 431.66(d)(2)(i) through (iii), except that where measurements and calculations reference ARI Standard 1200-2006 (incorporated by reference, see § 431.63), AHRI Standard 1200 (I-P)-2010 (incorporated by reference, see § 431.63) shall be used.
(3) For remote condensing and self-contained wedge cases, measure the CDEC or TDEC according to the AHRI Standard 1200 (I-P)-2010 test procedure (incorporated by reference, see § 431.63). For wedge cases in equipment classes for which a volume metric is used, the MDEC shall be the amount derived from the appropriate standards equation in paragraph (e)(1) of this section. For wedge cases of equipment classes for which a TDA metric is used, the MDEC for each model shall be the amount derived by incorporating into the standards equation in paragraph (e)(1) of this section for the equipment class a value for the TDA that is the product of:
(i) The vertical height of the air curtain (or glass in a transparent door) and
(ii) The largest overall width of the case, when viewed from the front.
(f) Exclusions. The energy conservation standards in paragraphs (b) through (e) of this section do not apply to salad bars, buffet tables, and chef bases or griddle stands.
[70 FR 60414, Oct. 18, 2005, as amended at 74 FR 1140, Jan. 9, 2009; 78 FR 62993, Oct. 23, 2013; 79 FR 22308, Apr. 21, 2014; 79 FR 17816, Mar. 28, 2014]
On or after September 20, 2024, any representations, including for certification of compliance, made with respect to the energy use or efficiency of commercial refrigeration equipment, except for buffet tables or preparation tables, blast chillers, blast freezers, or mobile refrigerated cabinets, must be made in accordance with the results of testing pursuant to this appendix. Prior to September 20, 2024, any representations with respect to energy use or efficiency of commercial refrigeration equipment, except for buffet tables or preparation tables, blast chillers, blast freezers, or mobile refrigerated cabinets, must be made either in accordance with the results of testing pursuant to this appendix or with the results of testing pursuant to this appendix as it appeared in appendix B to subpart C of part 431 in the 10 CFR parts 200-499 edition revised as of January 1, 2023. Buffet tables or preparation tables are subject to the test method requirements in appendix C to subpart C of part 431. Blast chillers and blast freezers are subject to the test method requirements in appendix D to subpart C of part 431.
The test procedure for equipment cooled only by secondary coolants in section 1.1.3 of this appendix is not required for use until the compliance date(s) of any amended energy conservation standard(s) (see § 431.66) for such commercial refrigeration equipment.
High-temperature refrigerators must be tested as medium-temperature refrigerators according to section 2.1.3 of this appendix based on the lowest application product temperature until the compliance date(s) of any amended energy conservation standard(s) (see § 431.66) established for high-temperature refrigerators. On and after the compliance date(s) of such energy conservation standard(s) (see § 431.66), high-temperature refrigerators must be tested as high-temperature refrigerators according to section 2.1.4 of this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.63 the entire standard for AHRI 1200-2023; AHRI 1320-2011; ASHRAE 72-2022 and ASHRAE 72-2022 Errata (the latter two collectively referenced as ASHRAE 72-2022 with Errata). However, only enumerated provisions of AHRI 1200-2023 and AHRI 1320-2011 are applicable to this appendix as follows:
0.1. AHRI 1200-2023
(a) Section 3, “Definitions,” as referenced in section 1.1 of this appendix.
(b) Section 3.2.8, “Dew Point,” as referenced in section 2.2. of this appendix.
(c) Section 3.2.20, “Total Display Area (TDA),” as referenced in section 3.2 of this appendix.
(d) Section 4, “Test Requirements,” as referenced in section 1.1 of this appendix.
(e) Section 4.1.1.1, “High Temperature Applications,” as referenced in section 2.1.4 of this appendix.
(f) Section 4.1.1.2, “Ice Cream Applications,” as referenced in section 2.1.1 of this appendix.
(g) Section 4.1.1.3, “Low Temperature Applications,” as referenced in section 2.1.2 of this appendix.
(h) Section 4.1.1.4, “Medium Temperature Applications,” as referenced in section 2.1.3 of this appendix.
(i) Section 5.1, “Rating Requirements for Remote Commercial Refrigerated Display Merchandisers and Storage Cabinets” as referenced in sections 1.1.2, 1.1.3, and 1.5.3.3 of this appendix.
(j) Section 5.2, “Rating Requirements for Self-Contained Commercial Refrigerated Display Merchandisers and Storage Cabinets,” as referenced in section 1.1.1 of this appendix.
(k) Section 9, “Symbols and Subscripts,” as referenced in section 1.1 and 2.2 of this appendix.
(l) Appendix C, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Refrigerated Volume Calculation—Normative” as referenced in section 3.1 of this appendix.
(m) Appendix D, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Total Display Area (TDA) Calculation—Normative,” as referenced in section 3.2 of this appendix.
0.2. AHRI 1320-2011
(a) Sections 5.2.7 and 5.2.8 as referenced in section 1.1.3 of this appendix.
(b) [Reserved].
1. Test Procedure
1.1. Determination of Daily Energy Consumption. Determine the daily energy consumption of each covered commercial refrigerator, freezer, or refrigerator-freezer by conducting the test procedure set forth in AHRI 1200-2023, section 3, “Definitions,” section 4, “Test Requirements,” and section 9, “Symbols and Subscripts.”
1.1.1. For each commercial refrigerator, freezer, or refrigerator-freezer with a self-contained condensing unit, also use AHRI 1200-2023, section 5.2, “Rating Requirements for Self-Contained Commercial Refrigerated Display Merchandisers and Storage Cabinets.”
1.1.2. For each commercial refrigerator, freezer, or refrigerator-freezer with a remote condensing unit, also use AHRI 1200-2023, section 5.1, “Rating Requirements for Remote Commercial Refrigerated Display Merchandisers and Storage Cabinets.”
1.1.3. For each commercial refrigerator, freezer, or refrigerator-freezer used with a secondary coolant, test according to section 1.1.2 of this appendix, except in place of the equations for CDEC and CEC in sections 5.1.2 and 5.1.2.1 of AHRI 1200-2023, respectively, apply the following equations:
CDEC = CEC + [FEC + LEC + AEC + DEC + PEC]* + CPEC
CEC = [(Qrt + QCP) · (t − tdt)]/(EER · 1000)
Where CPEC and QCP are as specified in sections 5.2.7 and 5.2.8 of AHRI 1320-2011 and EER is determined based on a temperature that is 6.0 °F lower than the secondary coolant cabinet inlet temperature.
1.2. Methodology for Determining Applicability of Transparent Door Equipment Families. To determine if a door for a given model of commercial refrigeration equipment is transparent:
(a) Calculate the outer door surface area including frames and mullions;
(b) calculate the transparent surface area within the outer door surface area excluding frames and mullions;
(c) calculate the ratio of (2) to (1) for each of the outer doors; and
(d) the ratio for the transparent surface area of all outer doors must be greater than 0.25 to qualify as a transparent equipment family.
1.3. Drawers. Drawers shall be treated as identical to doors when conducting the DOE test procedure. Commercial refrigeration equipment with drawers intended for use with pans shall be configured with stainless steel food service pans, installed in a configuration per the manufacturer's instructions utilizing the maximum pan sizes specified. If the manufacturer does not specify the pan sizes, the maximum pan depth and pan volume allowed shall be used. For commercial refrigeration equipment with drawers intended for use with pans, the net usable volume includes only the interior volume of the pan(s) in the drawer. The net usable volume shall be measured by the amount of water needed to fill all the pan(s) to within 0.5 inches of the top rim, or determined by calculating the total volume of all pan(s) using the pan manufacturers' published pan volume. For commercial refrigeration equipment with drawers not intended for pans, the net usable volume shall be equal to the total volume of the drawer to the top edge of the drawer. Test simulators shall be placed in commercial refrigeration equipment with drawers as follows: For each drawer, there shall be two test simulators placed at each of the following locations: at the left end, at the right end, and at consistent 24 inch to 48 inch intervals across the width of the drawer (for drawers wider than 48 inches). For drawers with overall internal width of 48 inches or less, only the left and right ends shall have test simulators. If test simulators are to be placed at a pan edge or divider, the test simulator shall be placed at the nearest adjacent location. For each drawer, one test simulator shall be placed on the bottom of the pan or drawer at each of the front and rear test simulator locations of the drawer. Test simulators shall be placed in contact with the drawer or pan end or ends unless load limiting stops are provided as part of the case. Test simulators shall be secured such that the test simulators do not move during the test. The net usable volume where test simulators are not required shall be filled with filler material so that between 60 percent and 80 percent of the net usable volume is occupied by test simulators and uniformly occupied by filler material.
1.4. Long-time Automatic Defrost. For commercial refrigeration equipment not capable of operating with defrost intervals of 24 hours or less, testing may be conducted using a two-part test method.
1.4.1. First Part of Test. The first part of the test shall be a 24-hour test starting in steady-state conditions and including eight hours of door opening (according to ASHRAE 72-2022 with Errata). The energy consumed in this test, ET1, shall be recorded.
1.4.2. Second Part of Test. The second part of the test shall be a defrost cycle, including any operation associated with a defrost. The start and end of the test period be determined as the last time before and first time after a defrost occurrence when the measured average simulator temperature (i.e., the instantaneous average of all test simulator temperature measurements) is within 0.5 °F of the IAT as measured during the first part of the test. The energy consumed in this test, ET2, and duration, tDI, shall be recorded.
1.4.3. Daily Energy Consumption. Based on the measured energy consumption in these two tests, the daily energy consumption (DEC) in kWh shall be calculated as:
Where:
DEC = daily energy consumption, in kWh;
ET 1 = energy consumed during the first part of the test, in kWh;
ET 2 = energy consumed during the second part of the test, in kWh;
tNDI = normalized length of defrosting time per day, in minutes;
tDI = length of time of defrosting test period, in minutes;
tDC = minimum time between defrost occurrences, in days; and
1440 = conversion factor, minutes per day.
1.5. Customer Order Storage Cabinets. Customer order storage cabinets shall conduct door openings according to ASHRAE 72-2022 with Errata, except that each door shall be opened to the fully open position for 8 seconds, once every 2 hours, for 6 door-opening cycles.
1.5.1. Ambient Compartments. For customer order storage cabinets that have at least one individual-secured compartment that is not capable of maintaining an integrated average temperature below the ambient dry-bulb temperature, the individual-secured compartment(s) at ambient dry-bulb temperature shall be categorized as a high-temperature refrigerator compartment for the purpose of testing and rating. All volume, total display area, and energy consumption calculations shall be included within the high-temperature refrigerator category and summed with other high-temperature refrigerator category compartment(s) calculations.
1.5.2. Convertible Compartments. For customer order storage cabinets that have individual-secured compartments that are convertible between the ambient dry-bulb temperature and the ≥32 °F operating temperature, the convertible compartment shall be tested as a medium-temperature refrigerator compartment or at the lowest application product temperature as specified in section 2.2 of this appendix.
1.5.3. Inverse Refrigeration Load Test. For customer order storage cabinets that supply refrigerant to multiple individual-secured compartments and that allow the suction pressure from the evaporator in each individual-secured compartment to float based on the temperature required to store the customer order in that individual-secured compartment, test according to section 1.1.2 of this appendix, except that energy (heat) loss shall be allowed at a rate and ΔT equivalent to the energy gains of a standard refrigerated cabinet as specified in sections 1.5.3.1-1.5.3.3 of this appendix.
1.5.3.1. Anti-sweat door heaters. Anti-sweat door heaters shall be de-energized for the inverse refrigeration load test specified in section 1.5.3. of this appendix.
1.5.3.2. Integrated Average Temperature. For medium-temperature refrigerator compartments, the integrated average temperature shall be 112.4 °F ±2.0 °F. For low-temperature freezer compartments, the integrated average temperature shall be 150.4 °F ±2.0 °F. For ambient compartments, the integrated average temperature shall be 75.4 °F ±2.0 °F.
1.5.3.3. Daily Energy Consumption. Determine the calculated daily energy consumption (“CDEC”) and the EER based on AHRI 1200-2023, section 5.1, “Rating Requirements for Remote Commercial Refrigerated Display Merchandisers and Storage Cabinets,” except that the compressor energy consumption (“CEC”) shall be calculated by applying the following equations:
ML = Nd × (Ae + Am)
Ae = [(Ha − Hc) − (Ht − Ha)] × ma
Am = Cp,liner × Wliner × ΔTliner
Where:
CEC = compressor energy consumption, kWh per day;
Q = inverse refrigeration load (does not include waste heat from auxiliary components and moisture infiltration), in BTU per h;
t = test duration, in h;
ML = moisture load impacts, BTU per day;
FEC = evaporator fan motor(s) energy consumption, Wh per day;
AEC = anti-condensate heater(s) energy consumption, Wh per day;
DEC = defrost heater(s) energy consumption, Wh per day;
3.412 = conversion factor, BTU per Wh;
EER = energy efficiency ratio, BTU per Wh;
1000 = conversion factor, W per kW;
Win = energy input measured over the test period for all energized components (heaters, controls, and fans) located in the refrigerated compartments, in Wh;
Nd = number of door openings during test, unitless;
Ae = enthalpy adjustment, BTU per day;
Am = moisture/frost accumulation, BTU per day;
Ha = ambient air enthalpy, BTU per pound;
Hc = compartment air enthalpy based on air conditions during cold operation (e.g., 0 °F dry bulb/−20 °F dew point for freezer compartment, 38 °F dry bulb/20 °F dew point for refrigerator compartment, 75 °F dry bulb/20 °F dew point for ambient compartment), BTU per pound;
Ht = compartment air enthalpy during heat leak test based on dew point being equal to ambient air dew point, BTU per pound;
ma = mass of compartment air exchanged (30% of total compartment volume) based density of air during cold operation, pounds;
Cp,liner = specific heat of liner material, BTU per °F per pound;
Wliner = weight of all liner parts, pounds; and
ΔTliner = maximum temperature rise of all liner parts (e.g., 4.5 °F, 2.5 °F, and 1 °F for freezer, refrigerator, and ambient compartments, respectively), °F.
2. Test Conditions
2.1. Integrated Average Temperatures. Conduct the testing required in section 1 of this appendix, and determine the daily energy consumption at the applicable integrated average temperature as follows:
2.1.1. Ice-Cream Freezers. Test ice-cream freezers and ice-cream freezer compartments to the integrated average temperature specified in section 4.1.1.2, “Ice Cream Applications,” of AHRI 1200-2023.
2.1.2. Low-Temperature Freezers. Test low-temperature freezers and low-temperature freezer compartments to the integrated average temperature specified in section 4.1.1.3, “Low Temperature Applications,” of AHRI 1200-2023.
2.1.3. Medium-Temperature Refrigerators. Test medium-temperature refrigerators and medium-temperature refrigerator compartments to the integrated average temperature specified in section 4.1.1.4, “Medium Temperature Applications,” of AHRI 1200-2023.
2.1.4. High-Temperature Refrigerators. Test high-temperature refrigerators and high-temperature refrigerator compartments to the integrated average temperature specified in section 4.1.1.1, “High Temperature Applications,” of AHRI 1200-2023.
2.2. Lowest Application Product Temperature. If a unit of commercial refrigeration equipment is not able to be operated at the integrated average temperature specified in section 2.1 of this appendix, test the unit at the lowest application product temperature (LAPT), as defined in § 431.62. For units equipped with a thermostat, LAPT is the measured temperature at the lowest thermostat setting of the unit (for units that are only able to operate at temperatures above the specified test temperature) or the highest thermostat setting of the unit (for units that are only able to operate at temperatures below the specified test temperature). For remote condensing equipment without a thermostat or other means of controlling temperature at the case, the lowest application product temperature is measured at the temperature achieved with the dew point temperature (as defined in section 3.2.8, “Dew Point,” of AHRI 1200-2023) or mid-point evaporator temperature (as defined in section 9, “Symbols and Subscripts,” of AHRI 1200-2023) set to 5 degrees colder than that required to maintain the manufacturer's specified application temperature that is closest to the specified integrated average temperature.
2.3. Testing at NSF Test Conditions. For commercial refrigeration equipment that is also tested in accordance with NSF test procedures (Type I and Type II), integrated average temperatures and ambient conditions used for NSF testing may be used in place of the DOE-prescribed integrated average temperatures and ambient conditions provided they result in a more stringent test. That is, the measured daily energy consumption of the same unit, when tested at the rating temperatures and/or ambient conditions specified in the DOE test procedure, must be lower than or equal to the measured daily energy consumption of the unit when tested with the rating temperatures or ambient conditions used for NSF testing. The integrated average temperature measured during the test may be lower than the range specified by the DOE applicable temperature specification provided in section 2.1 of this appendix, but may not exceed the upper value of the specified range. Ambient temperatures and/or humidity values may be higher than those specified in the DOE test procedure.
2.4. Liquid Refrigerant Pressure Required Accuracy. The liquid refrigerant pressure required accuracy is ±35 kPa (±5.1 psi).
2.5 Commercial Refrigerator, Freezer, and Refrigerator-Freezer connected to a Direct Expansion Remote Condensing Unit with R-744. For commercial refrigerators, freezers, and refrigerator-freezers connected to a direct expansion remote condensing unit with R-744, instead of the liquid refrigerant measurements for direct-expansion remote units specified in appendix A to ASHRAE 72-2022 with Errata, the liquid refrigerant measurements for direct-expansion remote units shall be: liquid refrigerant temperature shall be 30.0 °F with a tolerance for the average over test period of ±3.0 °F and a tolerance for the individual measurements of ±5.0 °F; liquid refrigerant pressure shall be the saturated liquid pressure corresponding to a condensing temperature in the range of 32.0 °F to 44.0 °F for the average over test period; and liquid refrigerant subcooling shall be greater than 2.0 °R for the average over test period.
2.6 Chef Base or Griddle Stand Test Conditions. For chef bases or griddle stands, instead of the dry-bulb temperature, wet-bulb temperature, and radiant heat temperature specified in appendix A to ASHRAE 72-2022 with Errata: dry-bulb temperature shall be 86.0 °F with a tolerance for the average over test period of ±1.8 °F and a tolerance for the individual measurements of ±3.6 °F; wet-bulb temperature shall be 73.7 °F with a tolerance for the average over test period of ±1.8 °F and a tolerance for the individual measurements of ±3.6 °F; and radiant heat temperature shall be greater than or equal to 81.0 °F.
3. Volume and Total Display Area
3.1. Determination of Volume. Determine the volume of a commercial refrigerator, freezer, and refrigerator-freezer using the method set forth in AHRI 1200-2023, appendix C, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Refrigerated Volume Calculation—Normative.”
3.2. Determination of Total Display Area. Determine the total display area of a commercial refrigerator, freezer, and refrigerator-freezer using the method set forth in AHRI 1200-2023, section 3.2.20, “Total Display Area (TDA),” and appendix D, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Total Display Area (TDA) Calculation—Normative.”
[88 FR 66225, Sept. 26, 2023]
On or after September 20, 2024, any representations, including for certification of compliance, made with respect to the energy use or efficiency of buffet tables or preparation tables must be made in accordance with the results of testing pursuant to this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.63 the entire standard for AHRI 1200-2023, ASHRAE 72-2022, ASHRAE 72-2022 Errata (the latter two collectively referenced as ASHRAE 72-2022 with Errata), and ASTM F2143-16. However, only enumerated provisions of those documents are applicable to this appendix as follows:
0.1. AHRI 1200-2023
(a) Section 3.2.17, “Refrigerated Volume (Vr),” as referenced in section 2.2 of this appendix.
(b) Normative Appendix C, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Refrigerated Volume Calculation,” as referenced in section 2.2 of this appendix.
0.2 ASHRAE 72-2022 with Errata
(a) Section 5.1, “Installation and Settings,” as referenced in section 1.3 of this appendix.
(b) Section 5.2, “Wall or Vertical Partition Placement,” as referenced in section 1.3 of this appendix.
(c) Section 5.3, “Components and Accessories,” as referenced in section 1.3 of this appendix.
(d) Section 6.1, “Ambient Temperature and Humidity,” as referenced in section 1.2 of this appendix.
(e) Section 7.1, “Sequence of Operations,” as referenced in section 1.5 of this appendix.
(f) Section 7.2, “Preparation Period” (excluding sections 7.2.1 and 7.2.2), as referenced in section 1.5 of this appendix.
(g) Section 7.3, “Test Periods A and B” (excluding sections 7.3.1, 7.3.2, 7.3.3, and 7.3.4), as referenced in sections 1.5 and 1.5.1 of this appendix.
(h) Section 7.4, “Test Alignment Period,” as referenced in section 1.5 of this appendix.
(i) Section 7.5, “Determining Stability,” as referenced in sections 1.5 and 1.5.2 of this appendix.
(j) Normative Appendix A, “Measurement Locations, Tolerances, Accuracies, and Other Characteristics,” (only the measured quantities specified in section 1.2 of this appendix) as referenced in sections 1.2 and 1.5.3 of this appendix.
0.3 ASTM F2143-16
(a) Section 3, “Terminology,” as referenced in section 1.1 of this appendix.
(b) Section 6.1, “Analytical Balance Scale,” as referenced in section 1.1 of this appendix.
(c) Section 6.2, “Pans,” as referenced in section 1.1 of this appendix.
(d) Section 7, “Reagents and Materials,” as referenced in section 1.1 of this appendix.
(e) Section 9, “Preparation of Apparatus” (section 9.6 only), as referenced in sections 1.1 and 1.4.2 of this appendix.
(f) Section 10.1, “General” (section 10.1.1 only), as referenced in sections 1.1 and 1.5.3 of this appendix.
(g) Section 10.2, “Pan Thermocouple Placement,” as referenced in section 1.1 of this appendix.
(h) Section 10.5, “Test” (sections 10.5.5 and 10.5.6 only), as referenced in sections 1.1 and 1.5.1 of this appendix.
(i) Section 11.4, “Energy Consumption” (section 11.4.1 only), as referenced in section 1.1 of this appendix.
(j) Section 11.5, “Production Capacity,” as referenced in sections 1.1 and 2.1 of this appendix.
1. Test Procedure
1.1. Determination of Daily Energy Consumption. Determine the daily energy consumption of each buffet table or preparation table with a self-contained condensing unit by conducting the test procedure set forth in ASTM F2143-16 section 3, “Terminology,” section 6.1, “Analytical Balance Scale,” section 6.2, “Pans,” section 7, “Reagents and Materials,” section 9.6, “Preparation of Apparatus”, section 10.1, “General” (section 10.1.1 only), section 10.2, “Pan Thermocouple Placement,” section 10.5, “Test” (sections 10.5.5 and 10.5.6 only), section 11.4, “Energy Consumption” (section 11.4.1 only), and section 11.5, “Production Capacity,” with additional instructions as described in the following sections.
1.2. Test Conditions. Ambient conditions and instrumentation for testing shall be as specified in the “Chamber conditions” and “Electricity supply and consumption of unit under test and components metered separately” portions of appendix A to ASHRAE 72-2022 with Errata and measured according to section 6.1 of ASHRAE 72-2022 with Errata and the specifications in appendix A of ASHRAE 72-2022 with Errata. The “highest point” of the buffet table or preparation table shall be determined as the highest point of the open-top refrigerated area of the buffet table or preparation table, without including the height of any lids or covers. The geometric center of the buffet table or preparation table is: for buffet tables or preparation tables without refrigerated compartments, the geometric center of the top surface of the open-top refrigerated area; and for buffet tables or preparation tables with refrigerated compartments, the geometric center of the door opening area for the refrigerated compartment.
1.3. Test Setup. Install the buffet table or preparation table according to sections 5.1, 5.2, and 5.3 of ASHRAE 72-2022 with Errata.
1.4. Test Load.
1.4.1. Pan Loading. Fill pans with distilled water to within 0.5 in. of the top edge of the pan. For pans that are not configured in a horizontal orientation, only the lowest side of the pan is filled to within 0.5 in. of the top edge of the pan with distilled water.
1.4.2. Refrigerated Compartments. Measure the temperature of any refrigerated compartment(s) as specified in section 9.6 of ASTM F2143-16. The thermocouples for measuring compartment air temperature shall be in thermal contact with the center of a 1.6-oz (45-g) cylindrical brass slug with a diameter and height of 0.75 in. The brass slugs shall be placed at least 0.5 in from any heat-conducting surface.
1.5. Stabilization and Test Period. Prepare the unit for testing and conduct two test periods to determine stability according to sections 7.1 through 7.5 of ASHRAE 72-2022 with Errata, excluding sections 7.2.1, 7.2.2, 7.3.1, 7.3.2, 7.3.3, and 7.3.4. The preparation period under section 7.2 of ASHRAE 72-2022 with Errata includes loading the test unit pans with distilled water and adjusting the controls to maintain the desired performance.
1.5.1. Test Periods A and B. Conduct two test periods, A and B, as specified in section 7.3 of ASHRAE 72-2022 with Errata (excluding sections 7.3.1, 7.3.2, 7.3.3, and 7.3.4). The 24-hour test periods shall begin with an 8-hour active period as specified in section 10.5.5 of ASTM F2143-16. Following the active period, the remaining 16 hours of the test period shall be a standby period with the pans remaining in place, any pan covers in the closed position, and with no additional door openings.
1.5.2. Stability. Average pan temperatures shall be used to determine stability, as specified in section 7.5 of ASHRAE 72-2022 with Errata, rather than average test simulator temperatures.
1.5.3. Data Recording. For each test period, record data as specified in section 10.1.1 of ASTM F2143-16, except record wet-bulb temperature rather than relative humidity. Rather than voltage, current, and power as specified in section 10.1.1 of ASTM F2143-16, record the electrical supply potential and frequency and energy consumption as specified in appendix A of ASHRAE 72-2022 with Errata.
1.6. Target Temperatures.
1.6.1. Average Pan Temperature. The average of all pan temperature measurements during the test period shall be 38 °F ±2 °F. If the unit under test is not able to be operated at this average temperature range, test the unit at the lowest application product temperature (LAPT), as defined in § 431.62. For units equipped with a thermostat, LAPT is measured at the lowest thermostat setting of the unit (for units that are only able to operate at temperatures above the specified test temperature) or the highest thermostat setting of the unit (for units that are only able to operate at temperatures below the specified test temperature).
1.6.2. Average Compartment Temperature. The average of all compartment temperature measurements during the test period shall be 38 °F ±2 °F. If the unit under test is not capable of maintaining both average pan temperature and average compartment temperature within the specified range, the average compartment temperature shall be the average temperature necessary to maintain average pan temperature within the specified range. If the unit is tested at the LAPT for the average pan temperature, as described in section 1.6.1 of this appendix, the average compartment temperature is the average of all compartment temperature measurements at that control setting.
2. Capacity Metrics
2.1. Pan Volume. Determine pan volume according to section 11.5 of ASTM F2143-16.
2.2. Refrigerated Volume. Determine the volume of any refrigerated compartments according to section 3.2.17 and appendix C of AHRI 1200-2023. The refrigerated volume excludes the volume occupied by pans loaded in the open-top display area for testing.
2.3. Pan Display Area. Determine the pan display area based on the total surface area of water in the test pans when filled to within 0.5 in. of the top edge of the pan, or for test pans that are not configured in a horizontal orientation, when the lowest side of the pan is filled to within 0.5 in. of the top edge of the pan with water.
[88 FR 66227, Sept. 26, 2023]
On or after September 20, 2024, any representations, including for certification of compliance, made with respect to the energy use or efficiency of blast chillers or blast freezers must be made in accordance with the results of testing pursuant to this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.63 the entire standard for AHRI 1200-2023, ASHRAE 72-2022, and ASHRAE 72-2022 Errata (the latter two collectively referenced as ASHRAE 72-2022 with Errata). However, only enumerated provisions of those documents are applicable to this appendix as follows:
0.1 AHRI 1200-2023
(a) Appendix C, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Refrigerated Volume Calculation—Normative,” as referenced in section 1.1.1. of this appendix.
(b) Reserved.
0.2 ASHRAE 72-2022 with Errata
(a) Section 4, “Instruments,” as referenced in section 1.2 of this appendix.
(b) Section 5, “Preparation of Unit Under Test” (except section 5.4, “Loading of Test Simulators and Filler Material”), as referenced in section 1.2 of this appendix.
(c) Section 6.1, “Ambient Temperature and Humidity,” as referenced in sections 1.2 and 1.4 of this appendix.
(d) Figure 6, “Location of Ambient Temperature Indicators,” as referenced in sections 1.2 and 1.4 of this appendix.
(e) Normative Appendix A, “Measurement Locations, Tolerances, Accuracies, and Other Characteristics,” (only the measured quantities specified in section 1.2.1 of this appendix) as referenced in sections 1.2 and 1.4 of this appendix.
1. Test Procedures
1.1. Scope. This section provides the test procedures for measuring the energy consumption in kilowatt-hours per pound (kWh/lb) for self-contained commercial blast chillers and blast freezers that have a refrigerated volume of up to 500 ft3.
1.1.1. Determination of Refrigerated Volume. Determine the refrigerated volume of a self-contained commercial blast chiller or blast freezer using the method set forth in AHRI 1200-2023, appendix C, “Commercial Refrigerated Display Merchandiser and Storage Cabinet Refrigerated Volume Calculation—Normative.”
1.2. Determination of Energy Consumption. Determine the energy consumption of each covered blast chiller or blast freezer by conducting the test procedure set forth in ASHRAE 72-2022 with Errata section 4, “Instruments,” section 5, “Preparation of Unit Under Test” (except section 5.4, “Loading of Test Simulators and Filler Material”), section 6.1, “Ambient Temperature and Humidity,” Figure 6, “Location of Ambient Temperature Indicators,” and normative appendix A, “Measurement Locations, Tolerances, Accuracies, and Other Characteristics” (only the measured quantities specified in section 1.2.1 of this appendix), as well as the requirements of this appendix.
1.2.1. Measured Quantities in Normative Appendix A of ASHRAE 72-2022 with Errata. The following measured quantities shall be in accordance with the specifications of normative appendix A of ASHRAE 72-2022 with Errata: dry bulb temperature (except for deviations specified in sections 1.3 and 1.4 of this appendix), electrical supply frequency, electrical supply potential, energy consumed (except for deviations specified in section 1.3 of this appendix), extent of non-perforated surface beyond edges of unit under test, front clearance, rear or side clearance, and time measurements.
1.2.2. Additional Specifications for ASHRAE 72-2022 with Errata. The term “refrigerator” used in ASHRAE 72-2022 with Errata shall instead refer to “blast chiller” or “blast freezer,” as applicable. In section 5.3 of ASHRAE 72-2022 with Errata, the phrase “all necessary components and accessories shall be installed prior to loading the storage and display areas with test simulators and filler material” shall be replaced with “all necessary components and accessories shall be installed prior to precooling the unit under test.” Section 5.3.5 shall also require that, prior to precooling the unit under test, the condensate pan shall be dry.
1.3. Data Recording Measurement Intervals. Measurements shall be continuously recorded during the test in intervals no greater than 10 seconds.
1.4. Test Conditions. The required test conditions shall have dry bulb temperature values according to Table D.1 when measured at point A in figure 6 of ASHRAE 72-2022 with Errata and according to section 6.1 of ASHRAE 72-2022 with Errata.
| Test condition | Value | Tolerance |
|---|---|---|
| Dry Bulb | 86.0 °F | Average over test period: ±1.8 °F.
Individual measurements: ±3.6 °F. |
1.5. Product Pan. The product pan shall be a 12 in. by 20 in. by 2.5 in., 22 gauge or heavier, and 300 series stainless steel pan. If the blast chiller or blast freezer is not capable of holding the 12 in. by 20 in. by 2.5 in. product pan dimensions, the manufacturer's recommended pan size shall be used, conforming as closely as possible to the 12 in. by 20 in. by 2.5 in. pan dimensions.
1.6. Product Temperature Measurement. The product temperature shall be measured in the geometric center of the measured product pans using an unweighted thermocouple placed 5⁄8 of an in. above the bottom of the measured product pan. The thermocouple leads shall be secured to the bottom of the measured product pan while also allowing for the transfer of the measured product pan from the heating source into the blast chiller's or blast freezer's cabinet.
1.7. Product Preparation. The product shall be made for each product pan and shall be loaded to 2 in. of product thickness (i.e., depth) within the product pan unless an additional product pan with a product thickness of less than 2 in. is needed to meet the product capacity determined in section 2.1 of this appendix. A 20-percent-by-volume propylene glycol (1,2-Propanediol) mixture in water shall be prepared. In each product pan, pour the propylene glycol mixture over #20 mesh southern yellow pine sawdust to create a 22 percent to 78 percent by mass slurry. An example of an acceptable sawdust specification is the American Wood Fibers brand, #20 Mesh Pine Sawdust. Mix until the sawdust becomes completely saturated and leave uncovered in the product pan. Verify that the product pan thermocouple is fully submerged in the product mixture and reposition the product pan thermocouple to the requirements of section 1.6. of this appendix if the product pan thermocouple is incorrectly positioned after mixing. Each product pan shall be weighed before and after the food product simulator is added and prior to heating the product. The weight of the product shall not include the weight of the pans, thermocouples, or wires. A cumulative total of the product weight shall be calculated and the product pans shall continue to be loaded with the product mixture until the cumulative total reaches, but not exceeds, the product capacity determined in section 2.1 of this appendix with a tolerance of ±5 percent or ±2 pounds, whichever is less. The cumulative total weight of product, the weight of product in each individual pan, and the number of pans shall be recorded.
1.8. Product Pan Heating. Measured product pans shall be maintained at an average temperature of 160.0 °F ±1.8 °F and individual pan temperatures shall be maintained at 160 °F ±10 °F for a minimum of 8 hours prior to being loaded into the blast chiller or blast freezer. Non-measured product pans shall also be heated for a minimum of 8 hours prior to being loaded into the blast chiller or blast freezer and the non-measured product pans shall be placed in alternating positions with the measured product pans in the heating device. Data acquisition for the temperature of the measured product pans and time measurements shall begin to be recorded prior to the minimum of 8 hours heating period.
1.9. Product Pan Distribution. The product pans shall be spaced evenly throughout each vertical column of rack positions in the blast chiller or blast freezer without the product pans touching any other product pans and without the product pans touching the top and the bottom of the blast chiller or blast freezer cabinet. For blast chillers or blast freezers that have an additional product pan with a product thickness of less than 2 in., the additional product pan shall be placed as close to the middle rack position as possible while maintaining an even distribution of all product pans. If not all rack positions are occupied by product pans, the product pan locations shall be recorded.
1.10. Measured Product Pans. If multiple product pans are required per level of the blast chiller or blast freezer (i.e., product pans can be loaded side-by-side at the same level), only the product temperature of one product pan per level shall be measured and the product pans measured should alternate vertical columns of the blast chiller or blast freezer cabinet so that each vertical column does not have two measured product pans on sequential levels. If a blast chiller or blast freezer requires an additional product pan with a thickness less than 2 in., the additional product pan shall not be measured for product temperature.
1.11. Stabilization. The blast chiller or blast freezer shall stabilize at the test conditions specified in section 1.4 of this appendix for at least 24 hours without operating.
1.12. Pre-cool Cycle. Data acquisition for the test condition temperatures specified in section 1.4 of this appendix and time measurements shall begin to be recorded prior to the pre-cool cycle. The pre-cool cycle shall be initiated on a blast chiller or blast freezer once the stabilization specified in section 1.11 of this appendix is complete. The fastest pre-cool cycle shall be selected. The pre-cool cycle shall be complete when the blast chiller or blast freezer notifies the user that the pre-cool is complete. If the blast chiller or blast freezer does not notify the user that the pre-cool cycle is complete, the pre-cool cycle shall be deemed complete when the blast chiller or blast freezer reaches 40 °F or 2 °F based on the blast chiller's or blast freezer's sensing probe for blast chillers and blast freezers, respectively. For blast chillers or blast freezers without any defined pre-cool cycles, the fastest blast chilling or blast freezing cycle shall be run with an empty cabinet until the blast chiller or blast freezer reaches 40 °F or 2 °F based on the blast chiller's or blast freezer's sensing probe. During the pre-cool cycle, the blast chiller's or blast freezer's sensing probe shall remain in its default or holstered position. The pre-cool test data to be recorded are the test condition temperatures specified in section 1.4 of this appendix, pre-cool cycle selected, pre-cool duration, and final pre-cool cabinet temperature based on the blast chiller's or blast freezer's sensing probe.
1.13. Loading. The blast chiller or blast freezer door shall be fully open to an angle of not less than 75 °F for loading at 4.0 ±1.0 minutes after the blast chiller or blast freezer completes the pre-cool cycle as specified in section 1.12 of this appendix. The door shall remain open to load all of the product pans for the entirety of the loading procedure. The door shall remain open for 20 seconds per roll-in rack and 15 seconds per product pan for roll-in and standard blast chillers or blast freezers, respectively. The total door open period shall have a tolerance of ±5 seconds. The blast chiller's or blast freezer's sensing probe shall be inserted into the geometric center of a product pan approximately 1 in. deep in the product mixture at the median pan level in the blast chiller or blast freezer. If the product pan at the median level is the additional product pan with less than 2 in. of product thickness, the closest product pan or product pan level that is farthest away from the evaporator fan shall be used to insert the blast chiller's or blast freezer's sensing probe. If the median pan level has capacity for multiple product pans, the probed product pan shall be the furthest away from the evaporator. The sensing probe shall not touch the bottom of the product pan or be exposed to the air. The location of the product pan with the sensing probe shall be recorded. The sensing probe shall be placed so that there is no interference with the product pan thermocouple. The product pan thermocouple wiring shall not affect the energy performance of the blast chiller or blast freezer. The door shall remain closed for the remainder of the test.
1.14. Blast Chilling or Blast Freezing Cycle. Determine the blast chilling or blast freezing cycle that will conduct the most rapid product temperature pulldown that is designed for the densest food product, as stated in the blast chiller's or blast freezer's manufacturer literature. A blast chilling cycle shall have a target temperature of 38.0 °F and a blast freezing cycle shall have a target temperature of 0.0 °F. The test condition temperatures specified in section 1.4 of this appendix and the time measurements shall continue to be recorded from the pre-cool cycle. Measured product pan temperatures shall continue to be recorded from the minimum of 8-hour period of heating prior to the loading of the product pans into the blast chiller or blast freezer. Electrical supply frequency, electrical supply potential, and energy consumed shall start to be recorded as soon as the blast chiller or blast freezer door is opened to load the product pans. Once the blast chiller or blast freezer door is closed, the blast chilling cycle or blast freezing cycle shall be selected and initiated as soon as is practicable. The blast chilling cycle or blast freezing cycle selected shall be recorded. The blast chilling or blast freezing test period shall continue from the door opening until all individual measured pan temperatures are at or below 40.0 °F or 2.0 °F for blast chiller and blast freezer tests, respectively, regardless of whether the selected cycle program has terminated. If all individual measured pan temperatures do not reach 40.0 °F or 2.0 °F for blast chiller and blast freezer tests, respectively, two hours after the selected cycle program has terminated, the test shall be repeated with the target temperature lowered by 1.0 °F until all individual measured pan temperatures are at or below 40.0 °F or 2.0 °F for blast chiller and blast freezer tests, respectively, at the conclusion of the test. The duration of the blast chiller or blast freezer test shall be recorded.
1.15. Calculations. The measured energy consumption determined in section 1.14 of this appendix shall be reported in kilowatt-hours and shall be divided by the cumulative total weight of product determined in section 1.7 of this appendix in pounds.
2. Capacity Metric
2.1. Product Capacity. Determine the product capacity by reviewing all manufacturer literature that is included with the blast chiller or blast freezer. The largest product capacity by weight that is stated in the manufacturer literature shall be the product capacity. If the blast chiller or blast freezer is able to operate as both a blast chiller and a blast freezer when set to different operating modes by the user and the manufacturer literature specifies different product capacities for blast chilling and blast freezing, the largest capacity by weight stated for the respective operating mode shall be the product capacity. If no product capacity is stated in the manufacturer literature, the product capacity shall be the product capacity that fills the maximum number of 12 in. by 20 in. by 2.5 in. pans that can be loaded into the blast chiller or blast freezer according to section 1.7 of this appendix. If the blast chiller or blast freezer with no product capacity stated in the manufacturer literature is not capable of meeting the definition of a blast chiller or blast freezer according to § 431.62 upon testing according to section 1 of this appendix, one 12 in. by 20 in. by 2.5 in. pan shall be removed from the blast chiller or blast freezer until the definition of a blast chiller or blast freezer is met according to § 431.62 when testing according to section 1 of this appendix.
[88 FR 66229, Sept. 26, 2023]
69 FR 61939, Oct. 21, 2004, unless otherwise noted.
This subpart contains energy conservation requirements for commercial warm air furnaces, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
[69 FR 61939, Oct. 21, 2004, as amended at 70 FR 60415, Oct. 18, 2005]
The following definitions apply for purposes of this subpart D, and of subparts J through M of this part. Any words or terms not defined in this Section or elsewhere in this part shall be defined as provided in Section 340 of the Act.
Basic model means all commercial warm air furnaces manufactured by one manufacturer within a single equipment class, that have the same nominal input rating and the same primary energy source (e.g. gas or oil) and that do not have any differing physical or functional characteristics that affect energy efficiency.
Commercial warm air furnace means a warm air furnace that is industrial equipment, and that has a capacity (rated maximum input) of 225,000 Btu per hour or more.
Thermal efficiency for a commercial warm air furnace equals 100 percent minus percent flue loss determined using test procedures prescribed under § 431.76.
Thermal efficiency two for a commercial warm air furnace equals 100 percent minus percent flue loss and jacket loss.
Warm air furnace means a self-contained oil-fired or gas-fired furnace designed to supply heated air through ducts to spaces that require it and includes combination warm air furnace/electric air conditioning units but does not include unit heaters and duct furnaces.
[69 FR 61939, Oct. 21, 2004, as amended at 76 FR 12503, Mar. 7, 2011; 78 FR 79598, Dec. 31, 2013; 88 FR 36233, June 2, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Ave. SW, EE-5B, Washington, DC 20585, (202) 586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit: www.archives.gov/federal-register/cfr/ibr-locations.html or email: fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section.
(b) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2311 Wilson Blvd., Suite 400, Arlington, VA 22201, (703) 524-8800, or online at: www.ahrinet.org.
(1) ANSI/AHRI 1500-2015 (“AHRI 1500-2015”), Performance Rating of Commercial Space Heating Boilers, ANSI-approved November 28, 2014; IBR approved for appendix A to this subpart.
(2) [Reserved]
(c) ANSI. American National Standards Institute. 25 W 43rd Street, 4th Floor, New York, NY 10036. (212) 642-4900 or online at: www.ansi.org.
(1) CSA/ANSI Z21.47:21, (“ANSI Z21.47-2021”), Gas-fired central furnaces, ANSI-approved April 21, 2021; IBR approved for appendices A and B to this subpart.
(2) [Reserved]
(d) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers Inc., 180 Technology Parkway NW, Peachtree Corners, Georgia 30092, (404) 636-8400, or online at: www.ashrae.org.
(1) ANSI/ASHRAE 103-2022 (“ASHRAE 103-2022”), Method of Testing for Annual Fuel Utilization Efficiency of Residential Central Furnaces and Boilers, approved January 10, 2022; IBR approved for appendix A to this subpart.
(2) [Reserved]
(e) ASME. American Society of Mechanical Engineers, Service Center, 22 Law Drive, P.O. Box 2900, Fairfield, NJ 07007, (973) 882-1170, or online at: www.asme.org.
(1) ANSI/ASME PTC 19.3-1974 (R2004), Supplement to ASME Performance Test Codes: Part 3: Temperature Measurement, Instruments and Apparatus, reaffirmed 2004; IBR approved for appendix A to this subpart.
(2) [Reserved]
(f) ASTM. ASTM International, 100 Barr Harbor Drive, P.O. Box C700, West Conshohocken, PA 19428, (877) 909-2786, or online at: www.astm.org/.
(1) ASTM D240-09, Standard Test Method for Heat of Combustion of Liquid Hydrocarbon Fuels by Bomb Calorimeter, approved July 1, 2009; IBR approved for appendix A to this subpart.
(2) ASTM D396-14a, Standard Specification for Fuel Oils, approved October 1, 2014; IBR approved for appendix A to this subpart.
(3) ASTM D4809-09a, Standard Test Method for Heat of Combustion of Liquid Hydrocarbon Fuels by Bomb Calorimeter (Precision Method); approved September 1, 2009; IBR approved for appendix A to this subpart.
(4) ASTM D5291-10, Standard Test Methods for Instrumental Determination of Carbon, Hydrogen, and Nitrogen in Petroleum Products and Lubricants, approved May 1, 2010; IBR approved for appendix A to this subpart.
(5) ASTM E230/E230M-17 (“ASTM E230/E230M-17”), Standard Specification for Temperature-Electromotive Force (emf) Tables for Standardized Thermocouples, approved November 1, 2017; IBR approved for appendix A to this subpart.
(g) NFPA. National Fire Protection Association, 1 Batterymarch Park, Quincy, MA 02169-7471, 1-800-344-3555, or online at: www.nfpa.org.
(1) NFPA 97 (“NFPA 97-2003”), Standard Glossary of Terms Relating to Chimneys, Vents, and Heat-Producing Appliances; copyright 2023; IBR approved for appendix A to this subpart.
(2) [Reserved]
(h) UL. Underwriters Laboratories, Inc., 333 Pfingsten Road, Northbrook, IL 60062, (847) 272-8800, or online at: www.ul.com.
(1) UL 727 (“UL 727-2018”), Standard for Safety Oil-Fired Central Furnaces, Tenth Edition, published January 31, 2018; IBR approved for appendix A to this subpart.
(2) [Reserved]
[88 FR 36234, June 2, 2023]
(a) Scope. This section prescribes the test requirements used to measure the energy efficiency of commercial warm air furnaces with a rated maximum input of 225,000 Btu per hour or more.
(b) Testing and calculations —
(1) Thermal efficiency. Test in accordance with appendix A to subpart D of this part when making representations of thermal efficiency.
(2) Thermal efficiency two. Test in accordance with appendix B to subpart D of this part when making representations of thermal efficiency two.
[88 FR 36234, June 2, 2023]
(a) Gas-fired commercial warm air furnaces. Each gas-fired commercial warm air furnace must meet the following energy efficiency standard levels:
(1) For gas-fired commercial warm air furnaces manufactured starting on January 1, 1994, until January 1, 2023, the TE at the maximum rated capacity (rated maximum input) must be not less than 80 percent; and
(2) For gas-fired commercial warm air furnaces manufactured starting on January 1, 2023, the TE at the maximum rated capacity (rated maximum input) must be not less than 81 percent.
(b) Oil-fired commercial warm air furnaces. Each oil-fired commercial warm air furnace must meet the following energy efficiency standard levels:
(1) For oil-fired commercial warm air furnaces manufactured starting on January 1, 1994, until January 1, 2023, the TE at the maximum rated capacity (rated maximum input) must be not less than 81 percent; and
(2) For oil-fired commercial warm air furnaces manufactured starting on January 1, 2023, the TE at the maximum rated capacity (rated maximum input) must be not less than 82 percent.
[81 FR 2528, Jan. 15, 2016]
On and after May 28, 2024, any representations made with respect to the energy use or efficiency of commercial warm air furnaces must be made in accordance with the results of testing pursuant to this section. At that time, manufacturers must use the relevant procedures specified in this appendix, which reference ANSI Z21.47-2021, ASHRAE 103-2022, UL 727-2018, or AHRI 1500-2015. On and after July 3, 2023 and prior to May 28, 2024, manufacturers must test commercial warm air furnaces in accordance with this appendix or 10 CFR 431.76 as it appeared on January 1, 2023. DOE notes that, because testing under this section is required as of May 28, 2024, manufacturers may wish to begin using this amended test procedure as soon as possible. Any representations made with respect to the energy use or efficiency of such commercial warm air furnaces must be made in accordance with whichever version is selected.
Manufacturers must use the results of testing under appendix B to this subpart to determine compliance with any standards for commercial warm air furnaces that use the thermal efficiency 2 (TE2) metric.
0. Incorporation by reference.
In § 431.75, DOE incorporated by reference the entire standard for AHRI 1500-2015, ANSI Z21.47-2021, ASHRAE 103-2022, ASME PTC 19.3-1974 (R2004), ASTM D240-09, ASTM D396-14a, ASTM D4809-09a, ASTM D5291-10, ASTM E230/E230M-17, NFPA 97-2003, and UL 727-2018. However, for standards AHRI 1500-2015, ANSI Z21.47-2021, ASHRAE 103-2022, and UL 727-2018, only the enumerated provisions of those documents apply to this appendix, as follows:
0.1 ANSI Z21.47-2021
(a) Sections 5.1, 5.1.4, 5.2, 5.3, 5.4, 5.5, 5.5.1, 5.6, and 7.2.1 as specified in section 1.1 of this appendix;
(b) Section 5.40 as specified in sections 1.1 and 3.1 of this appendix;
(c) Section 5.2.8 as specified in section 4.1 of this appendix;
(d) Annex I as specified in section 3.1 of this appendix.
0.2 ASHRAE 103-2022
(a) Sections 7.2.2.4, 7.8, and 9.2 as specified in section 2.2 of this appendix;
(b) Sections 11.3.7.1 and 11.3.7.2 as specified in section 4.1 of this appendix.
0.3 UL 727-2018
(a) Sections 2, 3, 37, 38 and 39, 40, 40.6, 41, 42, 43.2, 44, 45, and 46 as specified in section 1.2 of this appendix;
(b) Figure 40.3 as specified in section 2.1 of this appendix.
0.4 AHRI 1500-2015
(a) Section C3.2.1.1 as specified in section 1.2 of this appendix;
(b) Sections C7.2.4, C7.2.5, and C7.2.6.2 as specified in section 3.2 of this appendix.
1. Test setup and Testing. Where this section prescribes use of ANSI Z21.47-2021 or UL 727-2018, perform only the procedures pertinent to the measurement of the steady-state efficiency, as specified in this section.
1.1 Gas-fired commercial warm air furnaces. The test setup, including flue requirement, instrumentation, test conditions, and measurements for determining thermal efficiency are as specified in section 1.3 of this appendix, and the following sections of ANSI Z21.47-2021: 5.1 (General, including ASME PTC 19.3-1974 (R2004) as referenced in Section 5.1.4), 5.2 (Basic test arrangements), 5.3 (Test ducts and plenums), 5.4 (Test gases), 5.5 (Test pressures and burner adjustments), 5.6 (Static pressure and air flow adjustments), 5.40 (Thermal efficiency), and 7.2.1 (Basic test arrangements for direct vent central furnaces). If section 1.3 of this appendix and ANSI Z21.47-2021 have conflicting provisions (e.g., the number of thermocouples that should be used when testing units with flue outlets that have a cross-sectional area of 3.14 square inches or less), follow the provisions in section 1.3 of this appendix. The thermal efficiency test must be conducted only at the normal inlet test pressure, as specified in section 5.5.1 of ANSI Z21.47-2021, and at the maximum hourly Btu input rating specified by the manufacturer for the product being tested.
1.2 Oil-fired commercial warm air furnaces. The test setup, including flue requirement, instrumentation, test conditions, and measurement for measuring thermal efficiency is as specified in section 1.3 of this appendix and the following sections of UL 727-2018: 2 (Units of Measurement), 3 (Glossary, except that the definitions for “combustible” and “non-combustible” in sections 3.11 and 3.27 shall be as referenced in NFPA 97-2003), 37 (General), 38 and 39 (Test Installation), 40 (Instrumentation, except 40.4 and 40.6.2 through 40.6.7 which are not required for the thermal efficiency test, and including ASTM E230/E230M-17 as referenced in Sections 40.6), 41 (Initial Test Conditions), 42 (Combustion Test—Burner and Furnace), 43.2 (Operation Tests), 44 (Limit Control Cutout Test), 45 (Continuity of Operation Test), and 46 (Air Flow, Downflow or Horizontal Furnace Test). If section 1.3 of this appendix and UL 727-2018 have conflicting provisions (e.g., the number of thermocouples that should be used when testing units with flue outlets that have a cross-sectional area of 3.14 inches or less), follow the provisions in section 1.3 of this appendix. Conduct a fuel oil analysis for heating value, hydrogen content, carbon content, pounds per gallon, and American Petroleum Institute (API) gravity as specified in section C3.2.1.1 of AHRI 1500-2015, including the applicable provisions of ASTM D240-09, ASTM D4809-09a, ASTM D5291-10, and ASTM D396-14a, as referenced. The steady-state combustion conditions, specified in section 42.1 of UL 727-2018, are attained when variations of not more than 5 °F in the measured flue gas temperature occur for three consecutive readings taken 15 minutes apart.
1.3 Additional test setup requirements for gas-fired and oil-fired commercial warm air furnaces
1.3.1 Thermocouple setup for gas-fired and oil-fired commercial warm air furnaces with flue outlets that have a cross-sectional area of 3.14 square inches or less. For units with flue outlets having a cross-sectional area of 3.14 square inches or less, the flue gas temperatures may optionally be measured using five individual thermocouples, instead of nine thermocouples.
1.3.2 Procedure for flue gas measurements when testing units with multiple flue outlets. For units that have multiple flue outlets, record flue gas measurements (e.g., flue gas temperature, CO2 in the flue gasses) separately for each individual flue outlet and calculate a weighted-average value based on the readings of all flue outlets. To determine the weighted average for each measurement, first determine the input rating of the furnace module associated with each flue outlet. Then multiply the ratio of the input rating for the furnace module associated with each individual flue outlet to the total nameplate input rating of the furnace (i.e., the input rating associated with each individual flue outlet divided by the total nameplate input rating) by that flue outlet's respective component measurement and the sum of all of the products of the calculations for all of the flue outlets to determine the weighted-average values. Use the weighted-average values to determine flue loss, and whether equilibrium conditions are met before the official test period.
2. Additional test measurements
2.1 Determination of flue CO2 (carbon dioxide) or O2 (oxygen) for oil-fired commercial warm air furnaces. In addition to the flue temperature measurement specified in section 40.6.8 of UL 727-2018, locate one or two sampling tubes within six inches downstream from the flue temperature probe (as indicated on Figure 40.3 of UL 727-2018). If an open end tube is used, it must project into the flue one-third of the chimney connector diameter. If other methods of sampling the flue gas are used, place the sampling tube so as to obtain an average sample. There must be no air leak between the temperature probe and the sampling tube location. Collect the flue gas sample at the same time the flue gas temperature is recorded. The CO2 or O2 concentration of the flue gas must be as specified by the manufacturer for the product being tested, with a tolerance of ±0.1 percent. Determine the flue CO2 or O2 using an instrument with a reading error no greater than ±0.1 percent.
2.2 Procedure for the measurement of condensate for a gas-fired condensing commercial warm air furnace. The test procedure for the measurement of the condensate from the flue gas under steady-state operation must be conducted as specified in sections 7.2.2.4, 7.8, and 9.2 of ASHRAE 103-2022 under the maximum rated input conditions. This condensate measurement must be conducted for an additional 30 minutes of steady-state operation after completion of the steady-state thermal efficiency test specified in section 1.1 of this appendix.
3. Calculation of thermal efficiency
3.1 Gas-fired commercial warm air furnaces. Use the calculation procedure specified in Section 5.40, Thermal efficiency, of ANSI Z21.47-2021. When determining the flue loss that is used in the calculation of thermal efficiency, the calculation method specified in Annex I of ANSI Z21.47-2021 shall be used.
3.2 Oil-fired commercial warm air furnaces. Calculate the percent flue loss (in percent of heat input rate) by following the procedure specified in sections C7.2.4, C7.2.5, and C7.2.6.2 of the AHRI 1500-2015. The thermal efficiency must be calculated as: Thermal Efficiency (percent) = 100 percent − flue loss (in percent).
4. Procedure for the calculation of the additional heat gain and heat loss, and adjustment to the thermal efficiency, for a condensing commercial warm air furnace.
4.1 Calculate the latent heat gain from the condensation of the water vapor in the flue gas, and calculate heat loss due to the flue condensate down the drain, as specified in sections 11.3.7.1 and 11.3.7.2 of ASHRAE 103-2022, with the exception that in the equation for the heat loss due to hot condensate flowing down the drain in section 11.3.7.2, the assumed indoor temperature of 70 °F and the temperature term TOA must be replaced by the measured room temperature as specified in section 5.2.8 of ANSI Z21.47.
4.2 Adjustment to the thermal efficiency for condensing commercial warm air furnaces. Adjust the thermal efficiency as calculated in section 3.1 of this appendix by adding the latent gain, expressed in percent, from the condensation of the water vapor in the flue gas, and subtracting the heat loss (due to the flue condensate down the drain), also expressed in percent, both as calculated in section 4.1 of this appendix, to obtain the thermal efficiency of a condensing furnace.
[88 FR 36234, June 2, 2203]
Manufacturers must use the results of testing under this appendix B to determine compliance with any standards for commercial warm air furnaces that use the thermal efficiency 2 (TE2) metric. In addition, manufacturers may optionally make representations of energy use or efficiency of this equipment using TE2 as determined using this appendix starting on July 3, 2023.
0. Incorporation by Reference.
In § 431.75, DOE incorporates by reference the entire standard ANSI Z21.47-2021. However, only section 5.40 and Appendix J of ANSI Z21.47-2021 apply, as specified in sections 1.2 and 1.6 of this appendix.
1. Testing
1.1 Set up and test the unit according to sections 0 through 4 of appendix A to this subpart, while operating the unit at the maximum nameplate input rate (i.e., full load). Calculate thermal efficiency (TE) using the procedure specified in sections 3 and 4 of appendix A to this subpart.
1.2 For commercial warm air furnaces that are designed for outdoor installation (including but not limited to CWAFs that are weatherized, or approved for resistance to wind, rain, or snow), or indoor installation within an unheated space (i.e., isolated combustion systems), determine the jacket loss using Section 5.40 and Annex J of ANSI Z21.47-2021 while the unit is operating at the maximum nameplate input. The jacket shall consist of the surfaces surrounding the heating section of the furnace. The jacket includes all surfaces separating the heating section from the supply air, outside air, or condenser section, including the bottom surface separating the heating section from the basepan.
1.3 For commercial warm air furnaces that are designed only for indoor installation within a heated space, jacket loss shall be zero. For commercial warm air furnaces that are designed for indoor installation within a heated or unheated space, multiply the jacket loss determined in section 1.2 of this appendix by 1.7. For all other commercial warm air furnaces, including commercial warm air furnaces that are designed for outdoor installation (including but not limited to CWAFs that are weatherized, or approved for resistance to wind, rain, or snow), multiply the jacket loss determined in section 1.2 of this appendix by 3.3.
1.4 Subtract the jacket loss determined in section 1.3 of this appendix from the TE determined in section 1.1 of this appendix to determine the full-load efficiency.
1.5 Set up and test the unit according to sections 0 through 4 of appendix A to this subpart, while operating the unit at the nameplate minimum input rate (i.e., part load). Calculate TE using the procedure specified in sections 3 and 4 of appendix A to this subpart.
1.6 For commercial warm air furnaces that are designed for outdoor installation (including but not limited to CWAFs that are weatherized, or approved for resistance to wind, rain, or snow), or indoor installation within an unheated space (i.e., isolated combustion systems), determine the jacket loss using Section 5.40 and Annex J of ANSI Z21.47-2021 while the unit is operating at the minimum nameplate input. Alternatively, the jacket loss determined in section 1.2 of this appendix at the maximum nameplate input may be used.
1.7 For commercial warm air furnaces that are designed only for indoor installation within a heated space, jacket loss shall be zero. For commercial warm air furnaces that are designed for indoor installation within a heated or unheated space, multiply the jacket loss determined in section 1.6 of this appendix by 1.7. For all other commercial warm air furnaces, including commercial warm air furnaces that are designed for outdoor installation (including but not limited to CWAFs that are weatherized, or approved for resistance to wind, rain, or snow), multiply the jacket loss determined in section 1.6 of this appendix by 3.3.
1.8 Subtract the jacket loss determined in section 1.7 of this appendix from the TE determined in section 1.5 of this appendix to determine the part-load efficiency.
1.9 Calculate TE2 by taking the average of the full-load and part-load efficiencies as determined in sections 1.4 and 1.8 of this appendix, respectively.
[88 FR 36235, June 2, 2023]
69 FR 61960, Oct. 21, 2004, unless otherwise noted.
This subpart contains energy conservation requirements for certain commercial packaged boilers, pursuant to Part C of Title III of the Energy Policy and Conservation Act. (42 U.S.C. 6311-6317)
[69 FR 61960, Oct. 21, 2004, as amended at 70 FR 60415, Oct. 18, 2005]
The following definitions apply for purposes of this subpart E, and of subparts A and J through M of this part. Any words or terms not defined in this section or elsewhere in this part shall be defined as provided in 42 U.S.C. 6311.
Basic model means all commercial packaged boilers manufactured by one manufacturer within a single equipment class having the same primary energy source (e.g., gas or oil) and that have essentially identical electrical, physical and functional characteristics that affect energy efficiency.
Btu/h or Btu/hr means British thermal units per hour.
Combustion efficiency for a commercial packaged boiler is a measurement of how much of the fuel input energy is converted to useful heat in combustion and is calculated as 100-percent minus percent losses due to dry flue gas, incomplete combustion, and moisture formed by combustion of hydrogen, as determined with the test procedures prescribed under § 431.86 of this chapter.
Commercial packaged boiler means a packaged boiler that meets all of the following criteria:
(1) Has rated input of 300,000 Btu/h or greater;
(2) Is, to any significant extent, distributed in commerce for space conditioning and/or service water heating in buildings but does not meet the definition of “hot water supply boiler” in this part;
(3) Does not meet the definition of “field-constructed” in this section; and
(4) Is designed to:
(i) Operate at a steam pressure at or below 15 psig;
(ii) Operate at or below a water pressure of 160 psig and water temperature of 250 °F; or
(iii) Operate at the conditions specified in both paragraphs (4)(i) and (ii) of this definition.
Condensing boiler means a commercial packaged boiler that condenses part of the water vapor in the flue gases, and that includes a means of collecting and draining this condensate from its heat exchanger section.
Field-constructed means custom-designed equipment that requires welding of structural components in the field during installation. For the purposes of this definition, welding does not include attachment using mechanical fasteners or brazing; any jackets, shrouds, venting, burner, or burner mounting hardware are not structural components.
Flue condensate means liquid formed by the condensation of moisture in the flue gases.
Fuel input rate for a commercial packaged boiler means the measured rate at which the commercial packaged boiler uses energy and is determined using test procedures prescribed under § 431.86 of this chapter.
Manufacturer of a commercial packaged boiler means any person who manufactures, produces, assembles or imports such a boiler, including any person who:
(1) Manufactures, produces, assembles or imports a commercial packaged boiler in its entirety;
(2) Manufactures, produces, assembles or imports a commercial packaged boiler in part, and specifies or approves the boiler's components, including burners or other components produced by others, as for example by specifying such components in a catalogue by make and model number or parts number; or
(3) Is any vendor or installer who sells a commercial packaged boiler that consists of a combination of components that is not specified or approved by a person described in paragraph (1) or (2) of this definition.
Packaged boiler means a boiler that is shipped complete with heating equipment, mechanical draft equipment, and automatic controls and is usually shipped in one or more sections. If the boiler is shipped in more than one section, the sections may be produced by more than one manufacturer, and may be originated or shipped at different times and from more than one location.
Rated input means the maximum rate at which the commercial packaged boiler has been rated to use energy as indicated by the nameplate and in the manual shipped with the commercial packaged boiler.
Thermal efficiency for a commercial packaged boiler is determined using test procedures prescribed under § 431.86 and is the ratio of the heat absorbed by the water or the water and steam to the higher heating value in the fuel burned.
[69 FR 61960, Oct. 21, 2004, as amended at 74 FR 36354, July 22, 2009; 76 FR 12503, Mar. 7, 2011; 78 FR 79598, Dec. 31, 2013; 81 FR 89304, Dec. 9, 2016]
(a) General. We incorporate by reference the following standards into subpart E of part 431. The material listed has been approved for incorporation by reference by the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. Any subsequent amendment to a standard by the standard-setting organization will not affect the DOE regulations unless and until amended by DOE. Material is incorporated as it exists on the date of the approval and a notice of any change in the material will be published in the Federal Register. All approved material is available for inspection at the National Archives and Records Administration (NARA). For information on the availability of this material at NARA, call 202-741-6030 or go to http://www.archives.gov/federal_register/code_of_federal_regulations/ibr_locations.html. Also, this material is available for inspection at U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 6th Floor, 950 L'Enfant Plaza, SW., Washington, DC 20024, 202-586-2945, or go to: http://www1.eere.energy.gov/buildings/appliance_standards/. Standards can be obtained from the sources listed below.
(b) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Blvd., Suite 500, Arlington, VA 22201, (703) 524-8800, or go to: http://www.ahrinet.org.
(1) AHRI Standard 1500-2015, (“ANSI/AHRI Standard 1500-2015”), “2015 Standard for Performance Rating of Commercial Space Heating Boilers,” ANSI approved November 28, 2014, IBR approved for appendix A to subpart E as follows:
(i) Section 3—Definitions (excluding introductory text to section 3, introductory text to 3.2, 3.2.4, 3.2.7, 3.6, 3.12, 3.13, 3.20, 3.23, 3.24, 3.26, 3.27, and 3.31);
(ii) Section 5—Rating Requirements, 5.3 Standard Rating Conditions: (excluding introductory text to section 5.3, 5.3.5, 5.3.8, and 5.3.9);
(iii) Appendix C—Methods of Testing for Rating Commercial Space Heating Boilers—Normative, excluding C2.1, C2.7.2.2.2, C3.1.3, C3.5-C3.7, C4.1.1.1.2, C4.1.1.2.3, C4.1.2.1.5, C4.1.2.2.2, C4.1.2.2.3, C4.2, C5, C7.1, C7.2.12, C7.2.20;
(iv) Appendix D. Properties of Saturated Steam—Normative.
(v) Appendix E. Correction Factors for Heating Values of Fuel Gases—Normative.
(2) [Reserved].
[74 FR 36354, July 22, 2009, as amended at 81 FR 89305, Dec. 9, 2016]
(a) Scope. This section provides test procedures, pursuant to the Energy Policy and Conservation Act (EPCA), as amended, which must be followed for measuring the combustion efficiency and/or thermal efficiency of a gas- or oil-fired commercial packaged boiler.
(b) Testing and Calculations. Determine the thermal efficiency or combustion efficiency of commercial packaged boilers by conducting the appropriate test procedure(s) indicated in Table 1 of this section.
| Equipment category | Subcategory | Certified rated input Btu/h |
Standards efficiency metric (§ 431.87) |
Test procedure (corresponding to standards efficiency metric required by § 431.87) |
|---|---|---|---|---|
| Hot Water | Gas-fired | ≥300,000 and ≤2,500,000 | Thermal Efficiency | Appendix A, Section 2. |
| Hot Water | Gas-fired | >2,500,000 | Combustion Efficiency | Appendix A, Section 3. |
| Hot Water | Oil-fired | ≥300,000 and ≤2,500,000 | Thermal Efficiency | Appendix A, Section 2. |
| Hot Water | Oil-fired | >2,500,000 | Combustion Efficiency | Appendix A, Section 3. |
| Steam | Gas-fired (all*) | ≥300,000 and ≤2,500,000 | Thermal Efficiency | Appendix A, Section 2. |
| Steam | Gas-fired (all*) | >2,500,000 and ≤5,000,000 | Thermal Efficiency | Appendix A, Section 2. |
| >5,000,000 | Thermal Efficiency | Appendix A, Section 2. OR Appendix A, Section 3 with Section 2.4.3.2. |
||
| Steam | Oil-fired | ≥300,000 and ≤2,500,000 | Thermal Efficiency | Appendix A, Section 2. |
| Steam | Oil-fired | >2,500,000 and ≤5,000,000 | Thermal Efficiency | Appendix A, Section 2. |
| >5,000,000 | Thermal Efficiency | Appendix A, Section 2. OR Appendix A, Section 3. with Section 2.4.3.2. |
||
| * Equipment classes for commercial packaged boilers as of July 22, 2009 (74 FR 36355) distinguish between gas-fired natural draft and all other gas-fired (except natural draft). | ||||
(c) Field Tests. The field test provisions of appendix A may be used only to test a unit of commercial packaged boiler with rated input greater than 5,000,000 Btu/h.
[81 FR 89305, Dec. 9, 2016]
(a) Each commercial packaged boiler listed in table 1 of this paragraph (a) and manufactured on or after the effective date listed must meet the indicated energy conservation standard.
| Equipment category | Subcategory | Certified rated input | Efficiency level—effective date: March 2, 2012 * |
|---|---|---|---|
| Hot Water Commercial Packaged Boilers | Gas-fired | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 80.0% ET. |
| Hot Water Commercial Packaged Boilers | Gas-fired | >2,500,000 Btu/h | 82.0% EC. |
| Hot Water Commercial Packaged Boilers | Oil-fired | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 82.0% ET. |
| Hot Water Commercial Packaged Boilers | Oil-fired | >2,500,000 Btu/h | 84.0% EC. |
| Steam Commercial Packaged Boilers | Gas-fired, all, except natural draft | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 79.0% ET. |
| Steam Commercial Packaged Boilers | Gas-fired, all, except natural draft | >2,500,000 Btu/h | 79.0% ET. |
| Steam Commercial Packaged Boilers | Gas-fired—natural draft | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 77.0% ET. |
| Steam Commercial Packaged Boilers | Gas-fired—natural draft | >2,500,000 Btu/h | 77.0% ET. |
| Steam Commercial Packaged Boilers | Oil-fired | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 81.0% ET. |
| Steam Commercial Packaged Boilers | Oil-fired | >2,500,000 Btu/h | 81.0% ET. |
| * Where EC is combustion efficiency and ET is thermal efficiency. | |||
(b) Each commercial packaged boiler listed in table 2 of this paragraph (b) and manufactured on or after the effective date listed in Table 2 must meet the indicated energy conservation standard.
| Equipment category | Subcategory | Certified rated input | Efficiency level—effective date: March 2, 2022 * |
|---|---|---|---|
| Steam Commercial Packaged Boilers | Gas-fired—natural draft | ≥300,000 Btu/h and ≤2,500,000 Btu/h | 79.0% ET. |
| Steam Commercial Packaged Boilers | Gas-fired—natural draft | >2,500,000 Btu/h | 79.0% ET. |
| * Where ET is thermal efficiency. | |||
[88 FR 64352, Sept. 19, 2023]
Prior to December 4, 2017, manufacturers must make any representations with respect to the energy use or efficiency of commercial packaged boilers in accordance with the results of testing pursuant to this Appendix or the test procedures as they appeared in 10 CFR 431.86 revised as of January 1, 2016. On and after December 4, 2017, manufacturers must make any representations with respect to energy use or efficiency in accordance with the results of testing pursuant to this appendix.
1. Definitions.
For purposes of this appendix, the Department of Energy incorporates by reference the definitions established in section 3 of the American National Standards Institute (ANSI) and Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Standard 1500, “2015 Standard for Performance Rating of Commercial Space Heating Boilers,” beginning with 3.1 and ending with 3.35 (incorporated by reference, see § 431.85; hereafter “ANSI/AHRI Standard 1500-2015”), excluding the introductory text to section 3, the introductory text to section 3.2, “Boiler”; 3.2.4, “Heating Boiler”; 3.2.7, “Packaged Boiler”; 3.6, “Combustion Efficiency”; 3.12, “Efficiency, Combustion”; 3.13, “Efficiency, Thermal”; 3.20, “Gross Output”; 3.23, “Input Rating”; 3.24, “Net Rating”; 3.26, “Published Rating”; 3.26.1, “Standard Rating”; 3.27, “Rating Conditions”; 3.27.1, “Standard Rating Conditions”; and 3.31, “Thermal Efficiency.” In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over ANSI/AHRI Standard 1500-2015.
1.1. In all incorporated sections of ANSI/AHRI Standard 1500-2015, references to the manufacturer's “specifications,” “recommendations,” “directions,” or “requests” mean the manufacturer's instructions in the installation and operation manual shipped with the commercial packaged boiler being tested or in supplemental instructions provided by the manufacturer pursuant to § 429.60(b)(4) of this chapter. For parameters or considerations not specified in this appendix, refer to the manual shipped with the commercial packaged boiler. Should the manual shipped with the commercial packaged boiler not provide the necessary information, refer to the supplemental instructions for the basic model pursuant to § 429.60(b)(4) of this chapter. The supplemental instructions provided pursuant to § 429.60(b)(4) of this chapter do not replace or alter any requirements in this appendix nor do they override the manual shipped with the commercial packaged boiler. In cases where these supplemental instructions conflict with any instructions or provisions provided in the manual shipped with the commercial packaged boiler, use the manual shipped with the commercial packaged boiler.
1.2. Unless otherwise noted, in all incorporated sections of ANSI/AHRI Standard 1500-2015, the term “boiler” means a commercial packaged boiler as defined in § 431.82.
1.3. Unless otherwise noted, in all incorporated sections of ANSI/AHRI Standard 1500-2015, the term “input rating” means “rated input” as defined in § 431.82.
2. Thermal Efficiency Test.
2.
1. Test Setup.
2.1.1. Instrumentation. Use instrumentation meeting the minimum requirements found in Table C1 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85).
2.1.2. Data collection and sampling. Record all test data in accordance with Table 2.1 and Table 2.2. Do not use Section C5 and Table C4 of Appendix C of ANSI/AHRI Standard 1500-2015.
| Item recorded | Additional instruction |
|---|---|
| Date of Test | None. |
| Manufacturer | None. |
| Commercial Packaged Boiler Model Number | None. |
| Burner Model Number & Manufacturer | None. |
| Nozzle description and oil pressure | None. |
| Oil Analysis—H, C, API Gravity, lb/gal and Btu/lb | None. |
| Gas Manifold Pressure | Record at start and end of test. |
| Gas line pressure at meter | Measurement may be made manually. |
| Gas temperature | Measurement may be made manually. |
| Barometric Pressure (Steam and Natural Gas Only) | Measurement may be made manually. |
| Gas Heating Value, Btu/ft 3* | Record at start and end of test. |
| * Multiplied by correction factors, as applicable, in accordance with Appendix E of ANSI/AHRI Standard 1500-2015. | |
2.1.3. Instrument Calibration. Instruments must be calibrated at least once per year and a calibration record, containing at least the date of calibration and the method of calibration, must be kept as part of the data underlying each basic model certification, pursuant to § 429.71 of this chapter.
2.1.4. Test Setup and Apparatus. Set up the commercial packaged boiler for thermal efficiency testing according to the provisions of Section C2 (except section C2.1) of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85).
2.1.4.1. For tests of oil-fired commercial packaged boilers, determine the weight of fuel consumed using one of the methods specified in the following sections 2.1.4.1.1. or 2.1.4.1.2. of this appendix:
2.1.4.1.1. If using a scale, determine the weight of fuel consumed as the difference between the weight of the oil vessel before and after each measurement period, as specified in sections 2.1.4.1.3.1. or 2.1.4.1.3.2. of this appendix, determined using a scale meeting the accuracy requirements of Table C1 of Appendix C of ANSI/AHRI Standard 1500-2015.
2.1.4.1.2. If using a flow meter, first determine the volume of fuel consumed as the total volume over the applicable measurement period as specified in 2.1.4.1.3.1. or 2.1.4.1.3.2. of this appendix and as measured by a flow meter meeting the accuracy requirements of Table C1 of Appendix C of ANSI/AHRI Standard 1500-2015 upstream of the oil inlet port of the commercial packaged boiler. Then determine the weight of fuel consumed by multiplying the total volume of fuel over the applicable measurement period by the density of oil as determined pursuant to C3.2.1.1.3. of Appendix C of ANSI/AHRI Standard 1500-2015.
2.1.4.1.3. The applicable measurement period for the purposes of determining fuel input rate must be as specified in section 2.1.4.1.3.1. of this appendix for the “Warm-Up Period” or section 2.1.4.1.3.2. of this appendix for the “Test Period.”
2.1.4.1.3.1. For the purposes of confirming steady-state operation during the “Warm-Up Period,” the measurement period must be 15 minutes and tT in Equation C2 in Section C7.2.3.1 of Appendix C of ANSI/AHRI Standard 1500-2015 must be 0.25 hours to determine fuel input rate.
2.1.4.1.3.2. For the purposes of determining thermal efficiency during the “Test Period,” the measurement period and tT are as specified in sections 2.3.4 and 2.3.5 of this appendix.
2.1.4.2 For tests of gas-fired commercial packaged boilers, install a volumetric gas meter meeting the accuracy requirements of Table C1 of Appendix C of ANSI/AHRI Standard 1500-2015 upstream of the gas inlet port of the commercial packaged boiler. Record the accumulated gas volume consumed for each applicable measurement period. Use Equation C7.2.3.2. of Appendix C of ANSI/AHRI Standard 1500-2015 to calculate fuel input rate.
2.1.4.2.1. The applicable measurement period for the purposes of determining fuel input rate must be as specified in section 2.1.4.2.1.1. of this appendix for the “Warm-Up Period” and 2.1.4.2.1.2. of this appendix for the “Test Period.”
2.1.4.2.1.1. For the purposes of confirming steady-state operation during the “Warm-Up Period,” the measurement period must be 15 minutes and tT in Equation C2 in Section C7.2.3.1 of Appendix C of ANSI/AHRI Standard 1500-2015 must be 0.25 hours to determine fuel input rate.
2.1.4.2.1.2. For the purposes of determining thermal efficiency during the “Test Period,” the measurement period and tT are as specified in sections 2.3.4 and 2.3.5 of this appendix.
2.1.4.3 In addition to the provisions of Section C2.2.1.2 of ANSI/AHRI Standard 1500-2015, vent gases may alternatively be discharged vertically into a straight stack section without elbows. R-7 minimum insulation must extend 6 stack diameters above the flue collar, the thermocouple grid must be located at a vertical distance of 3 stack diameters above the flue collar, and the sampling tubes for flue gases must be installed within 1 stack diameter beyond the thermocouple grid. If dilution air is introduced into the flue gases before the plane of the thermocouple and flue gas sampling points, utilize an alternate plane of thermocouple grid and flue gas sampling point located downstream from the heat exchanger and upstream from the point of dilution air introduction.
2.1.5. Additional Requirements for Outdoor Commercial Packaged Boilers. If the manufacturer provides more than one outdoor venting arrangement, the outdoor commercial packaged boiler (as defined in Section 3.2.6 of ANSI/AHRI Standard 1500-2015; incorporated by reference, see § 431.85) must be tested with the shortest total venting arrangement as measured by adding the straight lengths of venting supplied with the equipment. If the manufacturer does not provide an outdoor venting arrangement, install the outdoor commercial packaged boiler venting consistent with the procedure specified in Section C2.2 of Appendix C of ANSI/AHRI Standard 1500-2015.
2.1.6. Additional Requirements for Steam Tests. In addition to the provisions of Section C2 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85), the following requirements apply for steam tests.
2.1.6.1. Insulate all steam piping from the commercial packaged boiler to the steam separator, and extend insulation at least one foot (1 ft.) beyond the steam separator, using insulation meeting the requirements specified in Table 2.3 of this appendix.
2.1.6.2. A temperature sensing device must be installed in the insulated steam piping prior to the water separator if the commercial packaged boiler produces superheated steam.
2.1.6.3. Water entrained in the steam and water condensing within the steam piping must be collected and used to calculate the quality of steam during the “Test Period.” Steam condensate must be collected and measured using either a cumulative (totalizing) flow rate or by measuring the mass of the steam condensate. Instrumentation used to determine the amount of steam condensate must meet the requirements identified in Table C1 in Appendix C of ANSI/AHRI Standard 1500-2015.
2.1.7. Additional Requirements for Water Tests. In addition to the provisions of section C2 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85), the following requirements apply for water tests.
2.1.7.1. Insulate all water piping between the commercial packaged boiler and the location of the temperature measuring equipment, including one foot (1 ft.) beyond the sensor, using insulation meeting the requirements specified in Table 2.3 of this appendix.
2.1.7.2. Install a temperature measuring device at Point B of Figure C9 of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85). Water entering the commercial packaged boiler must first enter the run of a tee and exit from the top outlet of the tee. The remaining connection of the tee must be plugged. Measure the inlet water temperature at Point B in the run of a second tee located 12 ± 2 pipe diameters downstream from the first tee and no more than the greater of 12 inches or 6 pipe diameters from the inlet of the commercial packaged boiler. The temperature measuring device shall extend into the water flow at the point of exit from the side outlet of the second tee. All inlet piping between the temperature measuring device and the inlet of the commercial packaged boilers must be wrapped with R-7 insulation.
2.1.7.3. Do not use Section C2.7.2.2.2 or its subsections of ANSI/AHRI Standard 1500-2015 for water meter calibration.
2.1.8. Flue Gas Sampling. In section C2.5.2 of Appendix C of ANSI/AHRI Standard 1500-2015, replace the last sentence with the following: When taking flue gas samples from a rectangular plane, collect samples at 1⁄4, 1⁄2, and 3⁄4 the distance from one side of the rectangular plane in the longer dimension and along the centerline midway between the edges of the plane in the shorter dimension and use the average of the three samples. The tolerance in each dimension for each measurement location is ± 1 inch.
2.2. Test Conditions.
2.2.1. General. Use the test conditions from Section 5 and Section C3 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85) for thermal efficiency testing but do not use the following sections:
(1) 5.3 Introductory text
(2) 5.3.5 (and subsections; see sections 2.2.3. and 2.2.4. of this appendix)
(3) 5.3.8 (see section 2.2.5. of this appendix)
(4) 5.3.9 (see section 2.2.6. of this appendix)
(5) C3.1.3 (and subsections)
(6) C3.5 (including Table C2; see section 2.2.7. of this appendix)
(7) C3.6 (see section 2.2.5. of this appendix)
(8) C3.7 (see section 2.2.6. of this appendix)
2.2.2. Burners for Oil-Fired Commercial Packaged Boilers. In addition to section C3.3 of Appendix C of ANSI/AHRI Standard 1500-2015, the following applies: For oil-fired commercial packaged boilers, test the unit with the particular make and model of burner as certified (or to be certified) by the manufacturer. If multiple burners are specified in the certification report for that basic model, then use any of the listed burners for testing.
2.2.3. Water Temperatures. Maintain the outlet temperature measured at Point C in Figure C9 of Appendix C of ANSI/AHRI Standard 1500-2015 at 180 °F ± 2 °F and maintain the inlet temperature measured at Point B at 80 °F ± 5 °F during the “Warm-up Period” and “Test Period” as indicated by 1-minute interval data pursuant to Table 2.2 of this appendix. Each reading must meet these temperature requirements. Use the inlet temperature and flow rate measured at Point B in Figure C9 of Appendix C of ANSI/AHRI Standard 1500-2015 for calculation of thermal efficiency.
2.2.4 Exceptions to Water Temperature Requirements. For commercial packaged boilers that require a higher flow rate than that resulting from the water temperature requirements of sections 2.2.3 of this appendix to prevent boiling, use a recirculating loop and maintain the inlet temperature at Point B of Figure C9 of Appendix C of ANSI/AHRI Standard 1500-2015 at 140 °F ± 5 °F during the “Warm-up Period” and “Test Period” as indicated by 1-minute interval data pursuant to Table 2.2 of this appendix. Each reading must meet these temperature requirements. Use the inlet temperature and flow rate measured at Point A in Figure C9 of Appendix C of ANSI/AHRI Standard 1500-2015 for calculation of thermal efficiency.
2.2.5 Air Temperature. For tests of non-condensing boilers, maintain ambient room temperature between 65 °F and 100 °F at all times during the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) as indicated by 1-minute interval data pursuant to Table 2.2 of this appendix. For tests of condensing boilers, maintain ambient room temperature between 65 °F and 85 °F at all times during the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) as indicated by 1-minute interval data pursuant to Table 2.2 of this appendix. The ambient room temperature may not differ by more than ± 5 °F from the average ambient room temperature during the entire “Test Period” at any reading. Measure the room ambient temperature within 6 feet of the front of the unit at mid height. The test air temperature, measured at the air inlet of the commercial packaged boiler, must be within ± 5 °F of the room ambient temperature when recorded at the 1-minute interval defined by Table 2.2 of this appendix.
2.2.6. Ambient Humidity. For condensing boilers, maintain ambient room relative humidity below 80-percent at all times during both the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) pursuant to Table 2.2 of this appendix. Measure the ambient humidity in the same location as ambient air temperature in section 2.2.5 of this appendix.
2.2.7. Flue Gas Temperature. The flue gas temperature during the test must not vary from the flue gas temperature measured at the start of the Test Period (as defined in Section C4 of ANSI/AHRI Standard 1500-2015) when recorded at the interval defined in Table 2.2 of this appendix by more than the limits prescribed in Table 2.4 of this appendix.
| Fuel type | Non-condensing | Condensing |
|---|---|---|
| Gas | ± 2 percent | Greater of ± 3 percent and ± 5 °F |
| Light Oil | ± 2 percent | |
| Heavy Oil | Greater of ± 3 percent and ± 5 °F |
2.3. Test Method.
2.3.1. General. Conduct the thermal efficiency test as prescribed in Section C4 “Test Procedure” of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85) excluding sections:
(1) C4.1.1.1.2 (see section 2.3.1.1 of this appendix)
(2) C4.1.1.2.3 (see 2.3.4 of this appendix)
(3) C4.1.2.1.5 (see section 2.3.2. of this appendix)
(4) C4.1.2.2.2
(5) C4.1.2.2.3 (see 2.3.5 of this appendix)
(6) C4.2
(7) C4.2.1
(8) C4.2.2
2.3.1.1. Adjust oil or non-atmospheric gas to produce the required firebox pressure and CO2 or O2 concentration in the flue gas, as described in Section 5.3.1 of ANSI/AHRI Standard 1500-2015. Conduct steam tests with steam pressure at the pressure specified in the manufacturer literature shipped with the commercial packaged boiler or in the manufacturer's supplemental testing instructions pursuant to § 429.60(b)(4) of this chapter, but not exceeding 15 psig. If no pressure is specified in the manufacturer literature shipped with the commercial packaged boiler or in the manufacturer's supplemental testing instructions (pursuant to § 429.60(b)(4) of this chapter), or if a range of operating pressures is specified, conduct testing at a steam pressure equal to atmospheric pressure. If necessary to maintain steam quality as required by Section 5.3.7 of ANSI/AHRI Standard 1500-2015, increase steam pressure in 1 psig increments by throttling with a valve beyond the separator until the test is completed and the steam quality requirements have been satisfied, but do not increase the steam pressure to greater than 15 psig.
2.3.2. Water Test Steady-State. Ensure that a steady-state is reached by confirming that three consecutive readings have been recorded at 15-minute intervals pursuant to Table 2.2 of this appendix that indicate that the measured fuel input rate is within ± 2-percent of the rated input. Water temperatures must meet the conditions specified in sections 2.2.3 and 2.2.4 of this appendix as applicable.
2.3.3. Condensate Collection for Condensing Commercial Packaged Boilers. Collect condensate in a covered vessel so as to prevent evaporation.
2.3.4. Steam Test Duration. Replace Section C4.1.1.2.3 of ANSI/AHRI Standard 1500-2015 with the following: The test period is one hour in duration if the steam condensate is measured or two hours if feedwater is measured. The test period must end with a 15-minute reading (steam condensate or feedwater and separator weight reading) pursuant to Table 2.2 of this appendix. When feedwater is measured, the water line at the end of the test must be within 0.25 inches of the starting level.
2.3.5. Water Test Duration. Replace Section C4.1.2.2.3 of ANSI/AHRI Standard 1500-2015 with the following: The test period is one hour for condensing commercial packaged boilers and 30 minutes for non-condensing commercial packaged boilers, and ends with a 15-minute interval reading pursuant to Table 2.2 of this appendix.
2.4. Calculations.
2.4.1. General. To determine the thermal efficiency of commercial packaged boilers, use the variables in section C6 of Appendix C of ANSI/AHRI Standard 1500-2015 and calculation procedure for the thermal efficiency test specified in section C7.2 of Appendix C of ANSI/AHRI Standard 1500-2015, excluding sections C7.2.12 and C7.2.20.
2.4.2. Use of Steam Properties Table. If the average measured temperature of the steam is higher than the value in Table D1 in Appendix D of ANSI/AHRI Standard 1500-2015 that corresponds to the average measured steam pressure, then use Table 2.5 of this appendix to determine the latent heat of superheated steam in (Btu/lb). Use linear interpolation for determining the latent heat of steam in Btu/lb if the measured steam pressure is between two values listed in Table D1 in Appendix D of ANSI/AHRI Standard 1500-2015 or in Table 2.5 of this appendix.
2.4.3. Alternative Thermal Efficiency Calculation for Large Steam Commercial Packaged Boilers. To determine the thermal efficiency of commercial packaged boilers with a fuel input rate greater than 5,000,000 Btu/h according to the steam test pursuant to Section C4.1.1 of ANSI/AHRI Standard 1500-2015, either:
2.4.3.1. Calculate the thermal efficiency of commercial packaged boiler models in steam mode in accordance with the provisions of section 2.4.1 of this appendix, or
2.4.3.2. Measure and calculate combustion efficiency Effyss in steam mode according to Section 3. Combustion Efficiency Test of this appendix and convert to thermal efficiency using the following equation:
EffyT = Effyss − 2.0
where EffyT is the thermal efficiency and EFFYss is the combustion efficiency as defined in C6 of ANSI/AHRI Standard 1500-2015. The combustion efficiency Effyss is as calculated in Section C7.2.14 of ANSI/AHRI Standard 1500-2015.
2.4.4. Rounding. Round the final thermal efficiency value to nearest one tenth of one percent.
3. Combustion Efficiency Test.
3.1. Test Setup.
3.1.1. Instrumentation. Use instrumentation meeting the minimum requirements found in Table C1 of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85).
3.1.2. Data collection and sampling. Record all test data in accordance with Table 3.1 and Table 3.2 of this appendix. Do not use Section C5 and Table C4 of Appendix C in ANSI/AHRI Standard 1500-2015.
| Item recorded | Additional instruction |
|---|---|
| Date of Test | None. |
| Manufacturer | None. |
| Commercial Packaged Boiler Model Number | None. |
| Burner Model Number & Manufacturer | None. |
| Nozzle description and oil pressure | None. |
| Oil Analysis—H, C, API Gravity, lb/gal and Btu/lb | None. |
| Gas Manifold Pressure | Record at start and end of test. |
| Gas line pressure at meter | Measurement may be made manually. |
| Gas temperature | Measurement may be made manually. |
| Barometric Pressure (Steam and Natural Gas Only) | Measurement may be made manually. |
| Gas Heating Value, Btu/ft 3 * | Record at start and end of test. |
| * Multiplied by correction factors, as applicable, in accordance with Appendix E of ANSI/AHRI Standard 1500-2015. | |
3.1.3. Instrument Calibration. Instruments must be calibrated at least once per year and a calibration record, containing at least the date of calibration and the method of calibration, must be kept as part of the data underlying each basic model certification, pursuant to § 429.71 of this chapter.
3.1.4. Test Setup and Apparatus. Set up the commercial packaged boiler for combustion efficiency testing according to the provisions of Section C2 (except section C2.1) of Appendix C of ANSI/AHRI Standard 1500-2015.
3.1.4.1. For tests of oil-fired commercial packaged boilers, determine the weight of fuel consumed using one of the methods specified in sections 3.1.4.1.1. or 3.1.4.1.2. of this appendix:
3.1.4.1.1. If using a scale, determine the weight of fuel consumed as the difference between the weight of the oil vessel before and after each measurement period, as specified in sections 3.1.4.1.3.1. or 3.1.4.1.3.2. of this appendix, determined using a scale meeting the accuracy requirements of Table C1 of ANSI/AHRI Standard 1500-2015.
3.1.4.1.2. If using a flow meter, first determine the volume of fuel consumed as the total volume over the applicable measurement period, as specified in sections 3.1.4.1.3.1. or 3.1.4.1.3.2. of this appendix, and as measured by a flow meter meeting the accuracy requirements of Table C1 of ANSI/AHRI Standard 1500-2015 upstream of the oil inlet port of the commercial packaged boiler. Then determine the weight of fuel consumed by multiplying the total volume of fuel over the applicable measurement period by the density of oil, in pounds per gallon, as determined pursuant to Section C3.2.1.1.3. of ANSI/AHRI Standard 1500-2015.
3.1.4.1.3. The applicable measurement period for the purposes of determining fuel input rate must be as specified in section 3.1.4.1.3.1. of this appendix for the “Warm-Up Period” or 3.1.4.1.3.2. of this appendix for the “Test Period.”
3.1.4.1.3.1. For the purposes of confirming steady-state operation during the “Warm-Up Period,” the measurement period must be 15 minutes and tT in Equation C2 in Section C7.2.3.1 of ANSI/AHRI Standard 1500-2015 must be 0.25 hours to determine fuel input rate.
3.1.4.1.3.2. For the purposes of determining combustion efficiency during the “Test Period,” the measurement period and tT are 0.5 hours pursuant to section 3.3.1.1. of this appendix.
3.1.4.2 For tests of gas-fired commercial packaged boilers, install a volumetric gas meter meeting the accuracy requirements of Table C1 of ANSI/AHRI Standard 1500-2015 upstream of the gas inlet port of the commercial packaged boiler. Record the accumulated gas volume consumed for each applicable measurement period. Use Equation C7.2.3.2. of ANSI/AHRI Standard 1500-2015 to calculate fuel input rate.
3.1.4.2.1. The applicable measurement period for the purposes of determining fuel input rate must be as specified in section 3.1.4.2.1.1. of this appendix for the “Warm-Up Period” and 3.1.4.2.1.2. of this appendix for the “Test Period.”
3.1.4.2.1.1. For the purposes of confirming steady-state operation during the “Warm-Up Period,” the measurement period must be 15 minutes and tT in Equation C2 in Section C7.2.3.1 of ANSI/AHRI Standard 1500-2015 must be 0.25 hour to determine fuel input rate.
3.1.4.2.1.2. For the purposes of determining combustion efficiency during the “Test Period,” the measurement period and tT are 0.5 hour pursuant to section 3.3.1.1. of this appendix.
3.1.4.3. In addition to the provisions of Section C2.2.1.2 of ANSI/AHRI Standard 1500-2015, vent gases may alternatively be discharged vertically into a straight stack section without elbows. R-7 minimum insulation must extend 6 stack diameters above the flue collar, the thermocouple grid must be located at a vertical distance of 3 stack diameters above the flue collar, and the sampling tubes for flue gases must be installed within 1 stack diameter beyond the thermocouple grid. If dilution air is introduced into the flue gases before the plane of the thermocouple and flue gas sampling points, utilize an alternate plane of thermocouple grid and flue gas sampling point located downstream from the heat exchanger and upstream from the point of dilution air introduction.
3.1.5. Additional Requirements for Outdoor Commercial Packaged Boilers. If the manufacturer provides more than one outdoor venting arrangement, the outdoor commercial packaged boiler (as defined in section 3.2.6 of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85) must be tested with the shortest total venting arrangement as measured by adding the straight lengths of venting supplied with the equipment. If the manufacturer does not provide an outdoor venting arrangement, install the outdoor commercial packaged boiler venting consistent with the procedure specified in Section C2.2 of Appendix C of ANSI/AHRI Standard 1500-2015.
3.1.6. Additional Requirements for Field Tests.
3.1.6.1 Field tests are exempt from the requirements of Section C2.2 of Appendix C of ANSI/AHRI Standard 1500-2015. Measure the flue gas temperature according to Section C2.5.1 of Appendix C of ANSI/AHRI Standard 1500-2015 and the thermocouple grids identified in Figure C12 of ANSI/AHRI Standard 1500-2015, with the following modification: the thermocouple grid may be staggered vertically by up to 1.5 inches to allow the use of instrumented rods to be inserted through holes drilled in the venting.
3.1.6.2. Field tests are exempt from the requirements of Section C2.6.3 of Appendix C of ANSI/AHRI Standard 1500-2015.
3.1.7. Additional Requirements for Water Tests. In addition to the provisions of Section C2 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85) the following requirements apply for water tests:
3.1.7.1. Insulate all water piping between the commercial packaged boiler and the location of the temperature measuring equipment, including one foot (1 ft.) beyond the sensor, using insulation meeting the requirements specified in Table 2.3 of this appendix.
3.1.7.2. Install a temperature measuring device at Point B of Figure C9 of ANSI/AHRI Standard 1500-2015. Water entering the commercial packaged boiler must first enter the run of a tee and exit from the top outlet of the tee. The remaining connection of the tee must be plugged. Measure the inlet water temperature at Point B in the run of a second tee located 12 ± 2 pipe diameters downstream from the first tee and no more than the greater of 12 inches or 6 pipe diameters from the inlet of the commercial packaged boiler. The temperature measuring device shall extend into the water flow at the point of exit from the side outlet of the second tee. All inlet piping between the temperature measuring device and the inlet of the commercial packaged boilers must be wrapped with R-7 insulation. Field tests must also measure the inlet water temperature at Point B in Figure C9, however they are not required to use the temperature measurement piping described in this section 3.1.7. of this appendix.
3.1.7.3. Do not use Section C2.7.2.2.2 or its subsections of ANSI/AHRI Standard 1500-2015 for water meter calibration.
3.1.8. Flue Gas Sampling. In section C2.5.2 of Appendix C of ANSI/AHRI Standard 1500-2015, replace the last sentence with the following: When taking flue gas samples from a rectangular plane, collect samples at 1⁄4, 1⁄2, and 3⁄4 the distance from one side of the rectangular plane in the longer dimension and along the centerline midway between the edges of the plane in the shorter dimension and use the average of the three samples. The tolerance in each dimension for each measurement location is ± 1 inch.
3.2. Test Conditions.
3.2.1. General. Use the test conditions from Sections 5 and C3 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference; see § 431.85) for combustion efficiency testing but do not use the following sections:
(1) 5.3 Introductory text
(2) 5.3.5 (and subsections; see sections 3.2.3, 3.2.3.1, and 3.2.3.2 of this appendix)
(3) 5.3.7 (excluded for field tests only)
(4) 5.3.8 (see section 3.2.4 of this appendix)
(5) 5.3.9 (see section 3.2.5 of this appendix)
(6) C3.1.3 (and subsections)
(7) C3.5 (including Table C2; see section 3.2.6 of this appendix)
(8) C3.6 (see section 3.2.4 of this appendix)
(9) C3.7 (see section 3.2.5 of this appendix)
3.2.2. Burners for Oil-Fired Commercial Packaged Boilers. In addition to Section C3.3 of Appendix C of ANSI/AHRI Standard 1500-2015, the following applies: for oil-fired commercial packaged boilers, test the unit with the particular make and model of burner as certified (or to be certified) by the manufacturer. If multiple burners are specified in the certification report for that basic model, then use any of the listed burners for testing.
3.2.3. Water Temperatures. Maintain the outlet temperature measured at Point C in Figure C9 at 180 °F ± 2 °F and maintain the inlet temperature measured at Point B at 80 °F ± 5 °F during the “Warm-up Period” and “Test Period” as indicated by 1-minute interval data pursuant to Table 3.2 of this appendix. Each reading must meet these temperature requirements. Field tests are exempt from this requirement and instead must comply with the requirements of section 3.2.3.1 of this appendix.
3.2.3.1. For field tests, the inlet temperature measured at Point A and Point B in Figure C9 and the outlet temperature measured and Point C in Figure C9 of ANSI/AHRI Standard 1500-2015 must be recorded in the data underlying that model's certification pursuant to § 429.71 of this chapter, and the difference between the inlet (measured at Point B) and outlet temperature (measured at Point C) must not be less than 20 °F at any point during the “Warm-up Period” and “Test Period,” after stabilization has been achieved, as indicated by 1-minute interval data pursuant to Table 3.2 of this appendix.
3.2.3.2 For commercial packaged boilers that require a higher flow rate than that resulting from the water temperature requirements of sections 3.2.3 of this appendix to prevent boiling, use a recirculating loop and maintain the inlet temperature at Point B of Figure C9 of ANSI/AHRI Standard 1500-2015 at 140 °F ± 5 °F during the “Warm-up Period” and “Test Period” as indicated by 1-minute interval data pursuant to Table 3.2 of this appendix. Each reading must meet these temperature requirements.
3.2.4. Air Temperature. For tests of non-condensing boilers (except during field tests), maintain ambient room temperature between 65 °F and 100 °F at all times during the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) as indicated by 1-minute interval data pursuant to Table 3.2 of this appendix. For tests of condensing boilers (except during field tests), maintain ambient room temperature between 65 °F and 85 °F at all times during the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) as indicated by 1-minute interval data pursuant to Table 3.2 of this appendix. The ambient room temperature may not differ by more than ± 5 °F from the average ambient room temperature during the entire “Test Period” at any 1-minute interval reading. Measure the room ambient temperature within 6 feet of the front of the unit at mid height. The test air temperature, measured at the air inlet of the commercial packaged boiler, must be within ± 5 °F of the room ambient temperature when recorded at the 1-minute interval defined by Table 3.2 of this appendix. For field tests, record the ambient room temperature at 1-minute intervals in accordance with Table 3.2 of this appendix.
3.2.5. Ambient Humidity. For condensing boilers (except during field tests), maintain ambient room relative humidity below 80-percent relative humidity at all times during both the “Warm-up Period” and “Test Period” (as described in Section C4 of Appendix C of ANSI/AHRI Standard 1500-2015) pursuant to Table 3.2 of this appendix. Measure the ambient humidity in the same location as ambient air temperature. For field tests of condensing boilers, record the ambient room relative humidity in accordance with Table 3.2 of this appendix.
3.2.6. Flue Gas Temperature. The flue gas temperature during the test must not vary from the flue gas temperature measured at the start of the Test Period (as defined in Section C4 of ANSI/AHRI Standard 1500-2015) when recorded at the interval defined in Table 3.2 by more than the limits prescribed in Table 3.3 of this appendix. For field tests, flue gas temperature does not need to be within the limits in Table 3.3 of this appendix but must be recorded at the interval specified in Table 3.2 of this appendix.
| Fuel type | Non-condensing | Condensing |
|---|---|---|
| Gas | ± 2 percent | Greater of ± 3 percent and ± 5 °F. |
| Light Oil | ± 2 percent | |
| Heavy Oil | Greater of ± 3 percent and ± 5 °F |
3.3. Test Method.
3.3.1. General. Conduct the combustion efficiency test using the test method prescribed in Section C4 “Test Procedure” of Appendix C of ANSI/AHRI Standard 1500-2015 excluding sections:
(1) C4.1.1.1.2 (see section 3.3.1.2 of this appendix)
(2) C4.1.1.2.3
(3) C4.1.2.1.5 (see section 3.3.2 of this appendix)
(4) C4.1.2.2.2
(5) C4.1.2.2.3
(6) C4.2
(7) C4.2.1
(8) C4.2.2
3.3.1.1. The duration of the “Test Period” for combustion efficiency outlined in sections C4.1.1.2 of Appendix C of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85) and C4.1.2.2 of Appendix C of ANSI/AHRI Standard 1500-2015 is 30 minutes. For condensing commercial packaged boilers, condensate must be collected for the 30 minute Test Period.
3.3.1.2. Adjust oil or non-atmospheric gas to produce the required firebox pressure and CO2 or O2 concentration in the flue gas, as described in section 5.3.1 of ANSI/AHRI Standard 1500-2015. Conduct steam tests with steam pressure at the pressure specified in the manufacturer literature shipped with the commercial packaged boiler or in the manufacturer's supplemental testing instructions pursuant to § 429.60(b)(4) of this chapter, but not exceeding 15 psig. If no pressure is specified in the manufacturer literature shipped with the commercial packaged boiler or in the manufacturer's supplemental testing instructions (pursuant to § 429.60(b)(4)) of this chapter, or if a range of operating pressures is specified, conduct testing at a steam pressure equal to atmospheric pressure. If necessary to maintain steam quality as required by section 5.3.7 of ANSI/AHRI Standard 1500-2015, increase steam pressure in 1 psig increments by throttling with a valve beyond the separator until the test is completed and the steam quality requirements have been satisfied, but do not increase the steam pressure to greater than 15 psig.
3.3.2. Water Test Steady-State. Ensure that a steady-state is reached by confirming that three consecutive readings have been recorded at 15-minute intervals that indicate that the measured fuel input rate is within ± 2-percent of the rated input. Water temperatures must meet the conditions specified in sections 3.2.3, 3.2.3.1, and 3.2.3.2 of this appendix as applicable.
3.3.3. Procedure for the Measurement of Condensate for a Condensing Commercial Packaged Boiler. Collect flue condensate using a covered vessel so as to prevent evaporation. Measure the condensate from the flue gas during the “Test Period.” Flue condensate mass must be measured within 5 minutes after the end of the “Test Period” (defined in C4.1.1.2 and C4.1.2.2 of ANSI/AHRI Standard 1500-2015) to prevent evaporation loss from the sample. Determine the mass of flue condensate for the “Test Period” by subtracting the tare container weight from the total weight of the container and flue condensate measured at the end of the ”Warm-up Period.”
3.4. Calculations.
3.4.1. General. To determine the combustion efficiency of commercial packaged boilers, use the variables in Section C6 and calculation procedure for the combustion efficiency test specified in Section C7.3 of Appendix C (including the specified subsections of C7.2) of ANSI/AHRI Standard 1500-2015 (incorporated by reference, see § 431.85).
3.4.2. Rounding. Round the final combustion efficiency value to nearest one tenth of a percent.
[81 FR 89306, Dec. 9, 2016]
69 FR 61969, Oct. 21, 2004, unless otherwise noted.
This subpart specifies test procedures and energy conservation standards for certain commercial air conditioners and heat pumps, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
[69 FR 61969, Oct. 21, 2004, as amended at 70 FR 60415, Oct. 18, 2005]
The following definitions apply for purposes of this subpart, and of subparts J through M of this part. Any words or terms not defined in this section or elsewhere in this part shall be defined as provided in 42 U.S.C. 6311. For definitions that reference the application for which the equipment is marketed, DOE will consider any publicly available document published by the manufacturer (e.g., product literature, catalogs, and packaging labels) to determine marketing intent. For definitions in this section that pertain to computer room air conditioners, italicized terms within a definition indicate terms that are separately defined in this section.
Applied Coefficient of performance, or ACOP means the ratio of the heating capacity to the power input, including system pump power, for water-source heat pumps. ACOP is expressed in watts per watt and determined according to appendix C1 of this subpart.
Basic model means:
(1) For air-cooled, three-phase, small commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h and air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h. All units manufactured by one manufacturer, having the same primary energy source, and, which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency; where essentially identical electrical, physical, and functional (or hydraulic) characteristics means:
(i) For split systems manufactured by outdoor unit manufacturers (OUMs): all individual combinations having the same model of outdoor unit, which means comparably performing compressor(s) [a variation of no more than five percent in displacement rate (volume per time) as rated by the compressor manufacturer, and no more than five percent in capacity and power input for the same operating conditions as rated by the compressor manufacturer], outdoor coil(s) [no more than five percent variation in face area and total fin surface area; same fin material; same tube material], and outdoor fan(s) [no more than ten percent variation in airflow and no more than twenty percent variation in power input];
(ii) For split systems having indoor units manufactured by independent coil manufacturers (ICMs): all individual combinations having comparably performing indoor coil(s) [plus or minus one square foot face area, plus or minus one fin per inch fin density, and the same fin material, tube material, number of tube rows, tube pattern, and tube size]; and
(iii) For single-package systems: all individual models having comparably performing compressor(s) [no more than five percent variation in displacement rate (volume per time) rated by the compressor manufacturer, and no more than five percent variations in capacity and power input rated by the compressor manufacturer corresponding to the same compressor rating conditions], outdoor coil(s) and indoor coil(s) [no more than five percent variation in face area and total fin surface area; same fin material; same tube material], outdoor fan(s) [no more than ten percent variation in outdoor airflow], and indoor blower(s) [no more than ten percent variation in indoor airflow, with no more than twenty percent variation in fan motor power input];
(iv) Except that:
(A) For single-package systems and single-split systems, manufacturers may instead choose to make each individual model/combination its own basic model provided the testing and represented value requirements in 10 CFR 429.67 are met; and
(B) For multi-split, multi-circuit, and multi-head mini-split combinations, a basic model may not include both individual small-duct, high velocity (SDHV) combinations and non-SDHV combinations even when they include the same model of outdoor unit. The manufacturer may choose to identify specific individual combinations as additional basic models.
(2) For commercial package air conditioning and heating equipment (excluding air-cooled, three-phase, commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h). All units manufactured by one manufacturer within a single equipment class, having the same or comparably performing compressor(s), heat exchangers, and air moving system(s) that have a common “nominal” cooling capacity.
(3) For computer room air conditioners. All units manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., electric or gas), and which have the same or comparably performing compressor(s), heat exchangers, and air moving system(s) that have a common “nominal” cooling capacity.
(4) For direct expansion-dedicated outdoor air system. All units manufactured by one manufacturer, having the same primary energy source (e.g., electric or gas), within a single equipment class; with the same or comparably performing compressor(s), heat exchangers, ventilation energy recovery system(s) (if present), and air moving system(s) that have a common “nominal” moisture removal capacity.
(5) For packaged terminal air conditioner (PTAC) or packaged terminal heat pump (PTHP). All units manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., electric or gas), and which have the same or comparable compressors, same or comparable heat exchangers, and same or comparable air moving systems that have a cooling capacity within 300 Btu/h of one another.
(6) For single package vertical units. All units manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., electric or gas), and which have the same or comparably performing compressor(s), heat exchangers, and air moving system(s) that have a rated cooling capacity within 1500 Btu/h of one another.
(7) For variable refrigerant flow systems (excluding air-cooled, three-phase, variable refrigerant flow air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h). All units manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., electric or gas), and which have the same or comparably performing compressor(s) that have a common “nominal” cooling capacity and the same heat rejection medium (e.g., air or water) (includes VRF water source heat pumps).
(8) For water-source heat pumps. All units manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., electric or gas), and which have the same or comparable compressors, same or comparable heat exchangers, and same or comparable “nominal” cooling capacity.
Ceiling-mounted means a configuration of a computer room air conditioner for which the unit housing the evaporator coil is configured for indoor installation on or through a ceiling.
Ceiling-mounted ducted means a configuration of a ceiling-mounted computer room air conditioner that is configured for use with discharge ducting (even if the unit is also configurable for use without discharge ducting).
Ceiling-mounted non-ducted means a configuration of a ceiling-mounted computer room air conditioner that is configured only for use without discharge ducting.
Coefficient of performance, or COP, means the ratio of the produced cooling effect of an air conditioner or heat pump (or its produced heating effect, depending on the mode of operation) to its net work input, when both the cooling (or heating) effect and the net work input are expressed in identical units of measurement. For air-cooled commercial package air conditioning and heating equipment (excluding equipment with a cooling capacity less than 65,000 Btu/h), COP is measured per appendix A to this subpart.
Coefficient of performance 2, or COP2, means the ratio of the produced cooling effect of an air conditioner or heat pump (or its produced heating effect, depending on the mode of operation) to its net work input, when both the cooling (or heating) effect and the net work input are expressed in identical units of measurement. COP2 must be used with a subscript to indicate the outdoor temperature in degrees Fahrenheit at which the COP2 was measured (e.g., COP217 for COP2 measured at 17 °F). For air-cooled commercial package air conditioning and heating equipment (excluding equipment with a cooling capacity less than 65,000 Btu/h), COP2 is measured per appendix A1 to this subpart.
Commercial package air-conditioning and heating equipment means air-cooled, water-cooled, evaporatively-cooled, or water source (not including ground water source) electrically operated, unitary central air conditioners and central air-conditioning heat pumps for commercial application.
Computer room air conditioner means commercial package air-conditioning and heating equipment (packaged or split) that is marketed for use in computer rooms, data processing rooms, or other information technology cooling applications and not a covered consumer product under 42 U.S.C. 6291(1)-(2) and 42 U.S.C. 6292. A computer room air conditioner may be provided with, or have as available options, an integrated humidifier, temperature and/or humidity control of the supplied air, and reheating function. Computer room air conditioners include, but are not limited to, the following configurations as defined in this section: down-flow, horizontal-flow, up-flow ducted, up-flow non-ducted, ceiling-mounted ducted, ceiling mounted non-ducted, roof-mounted, and wall-mounted.
Direct expansion-dedicated outdoor air system, or DX-DOAS, means a unitary dedicated outdoor air system that is capable of dehumidifying air to a 55 °F dew point—when operating under Standard Rating Condition A as specified in Table 4 or Table 5 of AHRI 920-2020 (incorporated by reference, see § 431.95) with a barometric pressure of 29.92 in Hg—for any part of the range of airflow rates advertised in manufacturer materials, and has a moisture removal capacity of less than 324 lb/h.
Double-duct air conditioner or heat pump means air-cooled commercial package air conditioning and heating equipment that meets the following criteria—
(1) Is either a horizontal single package or split-system unit; or a vertical unit that consists of two components that may be shipped or installed either connected or split; or a vertical single package unit that is not intended for exterior mounting on, adjacent interior to, or through an outside wall;
(2) Is intended for indoor installation with ducting of outdoor air from the building exterior to and from the unit (e.g., the unit and/or all of its components are non-weatherized);
(3) If it is a horizontal unit, the complete unit shall have a maximum height of 35 inches or the unit shall have components that do not exceed a maximum height of 35 inches. If it is a vertical unit, the complete (split, connected, or assembled) unit shall have components that do not exceed a maximum depth of 35 inches; and
(4) Has a rated cooling capacity greater than or equal to 65,000 Btu/h and less than 300,000 Btu/h.
Down-flow means a configuration of floor-mounted computer room air conditioner in which return air enters above the top of the evaporator coil and discharge air leaves below the bottom of the evaporator coil.
Ducted Condenser means a configuration of computer room air conditioner for which the condenser or condensing unit that manufacturer's installation instructions indicate is intended to exhaust condenser air through a duct(s).
Energy efficiency ratio, or EER, means the ratio of the produced cooling effect of an air conditioner or heat pump to its net work input, expressed in Btu/watt-hour. For commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), EER is measured per appendix A to this subpart.
Energy efficiency ratio 2, or EER2, means the ratio of the produced cooling effect of an air conditioner or heat pump to its net work input, expressed in Btu/watt-hour. For commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), EER2 is measured per appendix A1 to this subpart.
Floor-mounted means a configuration of a computer room air conditioner for which the unit housing the evaporator coil is configured for indoor installation on a solid floor, raised floor, or floor-stand. Floor-mounted computer room air conditioners are one of the following three configurations: down-flow, horizontal-flow, and up-flow.
Fluid economizer means an option available with a computer room air conditioner in which a fluid (other than air), cooled externally from the unit, provides cooling of the indoor air to reduce or eliminate unit compressor operation when outdoor temperature is low. The fluid may include, but is not limited to, chilled water, water/glycol solution, or refrigerant. An external fluid cooler such as, but not limited to a dry cooler, cooling tower, or condenser is utilized for heat rejection. This component is sometimes referred to as a free cooling coil, econ-o-coil, or economizer.
Heat Recovery (in the context of variable refrigerant flow multi-split air conditioners or variable refrigerant flow multi-split heat pumps) means that the air conditioner or heat pump is also capable of providing simultaneous heating and cooling operation, where recovered energy from the indoor units operating in one mode can be transferred to one or more other indoor units operating in the other mode. A variable refrigerant flow multi-split heat recovery heat pump is a variable refrigerant flow multi-split heat pump with the addition of heat recovery capability.
Heating seasonal performance factor, or HSPF means the total heating output of a central air-conditioning heat pump during its normal annual usage period for heating, expressed in Btu's and divided by the total electric power input, expressed in watt-hours, during the same period.
Horizontal-flow means a configuration of a floor-mounted computer room air conditioner that is neither a down-flow nor an up-flow unit.
Integrated energy efficiency ratio, or IEER, means a weighted average calculation of mechanical cooling EERs determined for four load levels and corresponding rating conditions, expressed in Btu/watt-hour. IEER is measured:
(1) Per appendix A to this subpart for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h);
(2) Per appendix C1 to this subpart for water-source heat pumps;
(3) Per appendix D1 to this subpart for variable refrigerant flow multi-split air conditioners and heat pumps (other than air-cooled with rated cooling capacity less than 65,000 Btu/h); and
(4) Per appendix G1 to this subpart for single package vertical air conditioners and single package vertical heat pumps.
Integrated seasonal coefficient of performance 2 or ISCOP2, means a seasonal weighted-average heating efficiency for heat pump dedicated outdoor air systems, expressed in W/W, as measured according to appendix B of this subpart.
Integrated seasonal moisture removal efficiency 2, or ISMRE2, means a seasonal weighted average dehumidification efficiency for dedicated outdoor air systems, expressed in lbs. of moisture/kWh, as measured according to appendix B of this subpart.
Integrated ventilation and heating efficiency, or IVHE, means a sum of the space heating provided (Btu) divided by the sum of the energy consumed (Wh), including mechanical heating, supplementary electric resistance heating, and heating season ventilation operating modes. IVHE with subscript C (IVHEC) refers to the IVHE of heat pumps using a cold-climate heating load line. For air-cooled commercial package air conditioning and heating equipment (excluding equipment with a cooling capacity less than 65,000 Btu/h), IVHE and IVHEC are measured per appendix A1 to this subpart.
Integrated ventilation, economizing, and cooling, or IVEC, means a sum of the space cooling provided (Btu) divided by the sum of the energy consumed (Wh), including mechanical cooling, economizing, and cooling season ventilation operating modes. For commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), IVEC is measured per appendix A1 to this subpart.
Large commercial package air-conditioning and heating equipment means commercial package air-conditioning and heating equipment that is rated—
(1) At or above 135,000 Btu per hour; and
(2) Below 240,000 Btu per hour (cooling capacity).
Net sensible coefficient of performance, or NSenCOP, means a ratio of the net sensible cooling capacity in kilowatts to the total power input in kilowatts for computer room air conditioners, as measured in appendix E1 of this subpart.
Non-standard size means a packaged terminal air conditioner or packaged terminal heat pump with existing wall sleeve dimensions having an external wall opening of less than 16 inches high or less than 42 inches wide, and a cross-sectional area less than 670 square inches.
Packaged terminal air conditioner means a wall sleeve and a separate un-encased combination of heating and cooling assemblies specified by the builder and intended for mounting through the wall, and that is industrial equipment. It includes a prime source of refrigeration, separable outdoor louvers, forced ventilation, and heating availability by builder's choice of hot water, steam, or electricity.
Packaged terminal heat pump means a packaged terminal air conditioner that utilizes reverse cycle refrigeration as its prime heat source, that has a supplementary heat source available, with the choice of hot water, steam, or electric resistant heat, and that is industrial equipment.
Roof-mounted means a configuration of a computer room air conditioner that is not wall-mounted, and for which the unit housing the evaporator coil is configured for outdoor installation.
Seasonal energy efficiency ratio or SEER means the total cooling output of a central air conditioner or central air-conditioning heat pump, expressed in Btu's, during its normal annual usage period for cooling and divided by the total electric power input, expressed in watt-hours, during the same period.
Sensible Coefficient of Performance, or SCOP means the net sensible cooling capacity in watts divided by the total power input in watts (excluding reheaters and humidifiers).
Single package unit means any central air conditioner or central air-conditioning heat pump in which all the major assemblies are enclosed in one cabinet.
Single package vertical air conditioner means:
(1) Air-cooled commercial package air conditioning and heating equipment that—
(i) Is factory-assembled as a single package that—
(A) Has major components that are arranged vertically;
(B) Is an encased combination of cooling and optional heating components; and
(C) Is intended for exterior mounting on, adjacent interior to, or through an outside wall;
(ii) Is powered by a single-or 3-phase current;
(iii) May contain 1 or more separate indoor grilles, outdoor louvers, various ventilation options, indoor free air discharges, ductwork, well plenum, or sleeves; and
(iv) Has heating components that may include electrical resistance, steam, hot water, or gas, but may not include reverse-cycle refrigeration as a heating means; and
(2) Includes single-phase single package vertical air conditioner with cooling capacity less than 65,000 Btu/h, as defined in this section.
Single package vertical heat pump means:
(1) A single package vertical air conditioner that—
(i) Uses reverse-cycle refrigeration as its primary heat source; and
(ii) May include secondary supplemental heating by means of electrical resistance, steam, hot water, or gas; and
(2) Includes single-phase single package vertical heat pump with cooling capacity less than 65,000 Btu/h, as defined in this section.
Single-phase single package vertical air conditioner with cooling capacity less than 65,000 Btu/h means air-cooled commercial package air conditioning and heating equipment that meets the criteria in paragraphs (1)(i) through (iv) of the definition for a single package vertical air conditioner in this section; that is single-phase; has a cooling capacity less than 65,000 Btu/h, and that:
(1) Is weatherized, determined by a model being denoted for “Outdoor Use” or marked as “Suitable for Outdoor Use” on the equipment nameplate; or
(2) Is non-weatherized and is a model that has optional ventilation air provisions available. When such ventilation air provisions are present on the unit, the unit must be capable of drawing in and conditioning outdoor air for delivery to the conditioned space at a rate of at least 400 cubic feet per minute, as determined in accordance with § 429.134(x)(3) of this chapter, while the equipment is operating with the same drive kit and motor settings used to determine the certified efficiency rating of the equipment (as required for submittal to DOE by § 429.43(b)(4)(xi) of this chapter).
Single-phase single package vertical heat pump with cooling capacity less than 65,000 Btu/h means air-cooled commercial package air conditioning and heating equipment that meets the criteria in paragraphs (1)(i) and (ii) of the definition for a single package vertical heat pump in this section; that is single-phase; has a cooling capacity less than 65,000 Btu/h, and that:
(1) Is weatherized, determined by a model being denoted for “Outdoor Use” or marked as “Suitable for Outdoor Use” on the equipment nameplate; or
(2) Is non-weatherized and is a model that has optional ventilation air provisions available. When such ventilation air provisions are present on the unit, the unit must be capable of drawing in and conditioning outdoor air for delivery to the conditioned space at a rate of at least 400 cubic feet per minute, as determined in accordance with § 429.134(x)(3) of this chapter, while the equipment is operating with the same drive kit and motor settings used to determine the certified efficiency rating of the equipment (as required for submittal to DOE by § 429.43(b)(4)(xii) of this chapter).
Small commercial package air-conditioning and heating equipment means commercial package air-conditioning and heating equipment that is rated below 135,000 Btu per hour (cooling capacity).
Small-duct, high-velocity commercial package air conditioning and heating equipment means a basic model of commercial package, split-system air conditioning and heating equipment that:
(1) Has a rated cooling capacity no greater than 65,000 Btu/h;
(2) Is powered by three-phase current;
(3) Is air-cooled; and
(4) Is paired with an indoor unit that:
(i) Includes an indoor blower housed with the coil;
(ii) Is designed for, and produces, at least 1.2 inches of external static pressure when operated at the certified air volume rate of 220-350 CFM per rated ton cooling in the highest default cooling airflow-controls setting; and
(iii) When applied in the field, uses high velocity room outlets generally greater than 1,000 fpm that have less than 6.0 square inches of free area.
Space-constrained commercial package air conditioning and heating equipment means a basic model of commercial package air conditioning and heating equipment (packaged or split) that:
(1) Is air-cooled;
(2) Is powered by three-phase current;
(3) Is not a single package vertical air conditioner or a single package vertical heat pump;
(4) Has a rated cooling capacity no greater than 30,000 Btu/h;
(5) Has an outdoor or indoor unit having at least two overall exterior dimensions or an overall displacement that:
(i) Is substantially smaller than those of other units that are:
(A) Currently usually installed in site-built single-family homes; and
(B) Of a similar cooling, and, if a heat pump, heating capacity; and
(ii) If increased, would certainly result in a considerable increase in the usual cost of installation or would certainly result in a significant loss in the utility of the product to the consumer; and
(6) Of a product type that was available for purchase in the United States as of December 1, 2000.
Split system means any central air conditioner or central air conditioning heat pump in which one or more of the major assemblies are separate from the others.
Standard size means a packaged terminal air conditioner or packaged terminal heat pump with wall sleeve dimensions having an external wall opening of greater than or equal to 16 inches high or greater than or equal to 42 inches wide, and a cross-sectional area greater than or equal to 670 square inches.
Unitary dedicated outdoor air system, or unitary DOAS, means a category of small, large, or very large commercial package air-conditioning and heating equipment that is capable of providing ventilation and conditioning of 100-percent outdoor air and is marketed in materials (including but not limited to, specification sheets, insert sheets, and online materials) as having such capability.
Up-flow means a configuration of a floor-mounted computer room air conditioner in which return air enters below the bottom of the evaporator coil and discharge air leaves above the top of the evaporator coil.
Up-flow ducted means a configuration of an up-flow computer room air conditioner that is configured for use with discharge ducting (even if the unit is also configurable for use without discharge ducting).
Up-flow non-ducted means a configuration of an up-flow computer room air conditioner that is configured only for use without discharge ducting.
Variable Refrigerant Flow Multi-Split Air Conditioner means a unit of commercial package air-conditioning and heating equipment that is configured as a split system air conditioner incorporating a single refrigerant circuit, with one or more outdoor units, at least one variable-speed compressor or an alternate compressor combination for varying the capacity of the system by three or more steps, and multiple indoor fan coil units, each of which is individually metered and individually controlled by an integral control device and common communications network and which can operate independently in response to multiple indoor thermostats. Variable refrigerant flow implies three or more steps of capacity control on common, inter-connecting piping.
Variable Refrigerant Flow Multi-Split Heat Pump means a unit of commercial package air-conditioning and heating equipment that is configured as a split system heat pump that uses reverse cycle refrigeration as its primary heating source and which may include secondary supplemental heating by means of electrical resistance, steam, hot water, or gas. The equipment incorporates a single refrigerant circuit, with one or more outdoor units, at least one variable-speed compressor or an alternate compressor combination for varying the capacity of the system by three or more steps, and multiple indoor fan coil units, each of which is individually metered and individually controlled by a control device and common communications network and which can operate independently in response to multiple indoor thermostats. Variable refrigerant flow implies three or more steps of capacity control on common, inter-connecting piping.
Ventilation energy recovery system, or VERS, means a system that preconditions outdoor ventilation air entering the equipment through direct or indirect thermal and/or moisture exchange with the exhaust air, which is defined as the building air being exhausted to the outside from the equipment.
Very large commercial package air-conditioning and heating equipment means commercial package air-conditioning and heating equipment that is rated—
(1) At or above 240,000 Btu per hour; and
(2) Below 760,000 Btu per hour (cooling capacity).
Wall-mounted means a configuration of a computer room air conditioner for which the unit housing the evaporator coil is configured for installation on or through a wall.
Water-source heat pump means commercial package air-conditioning and heating equipment that is a single-phase or three-phase reverse-cycle heat pump that uses a circulating water loop as the heat source for heating and as the heat sink for cooling. The main components are a compressor, refrigerant-to-water heat exchanger, refrigerant-to-air heat exchanger, refrigerant expansion devices, refrigerant reversing valve, and indoor fan (except that coil-only units do not include an indoor fan). Such equipment includes, but is not limited to, water-to-air water-loop heat pumps.
[69 FR 61969, Oct. 21, 2004, as amended at 70 FR 60415, Oct. 18, 2005; 73 FR 58828, Oct. 7, 2008; 74 FR 12073, Mar. 23, 2009; 76 FR 12503, Mar. 7, 2011; 77 FR 28988, May 16, 2012; 78 FR 79598, Dec. 31, 2013; 80 FR 42664, July 17, 2015; 80 FR 79669, Dec. 23, 2015; 81 FR 2529, Jan. 15, 2016; 87 FR 45197, July 27, 2022; 87 FR 63896, Oct. 20, 2022; 87 FR 75167, Dec. 7, 2022; 87 FR 77325, Dec. 16, 2022; 88 FR 21838, Apr. 11, 2023; 88 FR 36386, 36424, June 2, 2023; 88 FR 84228, Dec. 4, 2023; 89 FR 44035, May 20, 2024]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the sources in the following paragraphs of this section.
(b) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2311 Wilson Blvd., Suite 400, Arlington, VA 22201; (703) 524-8800; www.ahrinet.org.
(1) ANSI/AHRI Standard 210/240-2008 (AHRI 210/240-2008), 2008 Standard for Performance Rating of Unitary Air-Conditioning & Air-Source Heat Pump Equipment, approved by ANSI on October 27, 2011, and updated by addendum 1 in June 2011 and addendum 2 in March 2012; IBR approved for § 431.96 and appendix F to this subpart.
(2) AHRI Standard 210/240-2023 (AHRI 210/240-2023), 2023 Standard for Performance Rating of Unitary Air-conditioning & Air-source Heat Pump Equipment, copyright May 2020; IBR approved for appendix F1 to this subpart.
(3) AHRI Standard 310/380-2014 (“AHRI 310/380-2014”), “Standard for Packaged Terminal Air-Conditioners and Heat Pumps,” February 2014; IBR approved for § 431.96.
(4) AHRI Standard 340/360-2022 (I-P) (“AHRI 340/360-2022”), 2022 Standard for Performance Rating of Commercial and Industrial Unitary Air-conditioning and Heat Pump Equipment, approved January 26, 2022; IBR approved for appendix A to this subpart.
(5) AHRI Standard 390(I-P)-2021 (“AHRI 390-2021”), 2021 Standard for Performance Rating of Single Package Vertical Air-Conditioners and Heat Pumps, copyright 2021; (AHRI 390-2021), IBR approved for appendices G and G1 to this subpart.
(6) AHRI Standard 600-2023 (I-P) (“AHRI 600-2023”), 2023 Standard for Performance Rating of Water/Brine to Air Heat Pump Equipment, AHRI-approved September 11, 2023; IBR approved for appendix C1 to this subpart.
(7) AHRI Standard 920 (I-P) with Addendum 1 (“AHRI 920-2020”), “2020 Standard for Performance Rating of Direct Expansion-Dedicated Outdoor Air System Units,” copyright 2021; IBR approved for § 431.92; appendix B to this subpart.
(8) AHRI Standard 1060 (I-P) (“AHRI 1060-2018”), “2018 Standard for Performance Rating of Air-to-Air Exchangers for Energy Recovery Ventilation Equipment,” copyright 2018; IBR approved for appendix B to this subpart.
(9) ANSI/AHRI Standard 1230-2010 (AHRI 1230-2010), 2010 Standard for Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump Equipment, approved August 2, 2010, and updated by addendum 1 in March 2011; IBR approved for § 431.96 and appendices D and F to this subpart.
(10) AHRI Standard 1230 (I-P), (“AHRI 1230-2021'), “2021 Standard for Performance Rating of Variable Refrigerant Flow (VRF) Multi-Split Air-Conditioning and Heat Pump Equipment”, copyright in 2021; IBR approved for appendix D1 to this subpart.
(11) AHRI Standard 1340-2023 (I-P) (“AHRI 1340-2023”), 2023 Standard for Performance Rating of Commercial and Industrial Unitary Air-conditioning and Heat Pump Equipment, approved November 16, 2023; IBR approved for appendix A1 to this subpart.
(12) AHRI Standard 1360-2022 (I-P) (“AHRI 1360-2022”), 2022 Standard for Performance Rating of Computer and Data Processing Room Air Conditioners, copyright 2022; IBR approved for appendix E1 to this subpart.
(c) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers, 180 Technology Parkway, Peachtree Corners, Georgia 30092; (404) 636-8400; www.ashrae.org.
(1) ANSI/ASHRAE Standard 16-1983 (RA 2014), (“ANSI/ASHRAE 16”), “Method of Testing for Rating Room Air Conditioners and Packaged Terminal Air Conditioners,” ASHRAE reaffirmed July 3, 2014, IBR approved for § 431.96.
(2) ANSI/ASHRAE Standard 37-2009 (“ANSI/ASHRAE 37-2009”), Methods of Testing for Rating Electrically Driven Unitary Air-Conditioning and Heat Pump Equipment, approved June 24, 2009; IBR approved for § 431.96 and appendices A, A1, B, C1, D1, E1, F1, G, and G1 to this subpart.
(3) Errata Sheet for ANSI/ASHRAE Standard 37-2009, Methods of Testing for Rating Electrically Driven Unitary Air-Conditioning and Heat Pump Equipment, March 27, 2019; IBR approved for appendices C1 and D1 to this subpart.
(4) ANSI/ASHRAE Standard 41.1- 2013 (“ANSI/ASHRAE 41.1-2013”), “Standard Method for Temperature Measurement,” ANSI-approved January 30, 2013; IBR approved for appendix B to this subpart.
(5) ANSI/ASHRAE Standard 41.6- 2014 (“ANSI/ASHRAE 41.6-2014”), “Standard Method for Humidity Measurement,” ANSI-approved July 3, 2014; IBR approved for appendix B to this subpart.
(6) ANSI/ASHRAE Standard 58-1986 (RA 2014), (“ANSI/ASHRAE 58”), “Method of Testing for Rating Room Air-Conditioner and Packaged Terminal Air-Conditioner Heating Capacity,” ASHRAE reaffirmed July 3, 2014, IBR approved for § 431.96.
(7) ASHRAE Standard 127-2007, “Method of Testing for Rating Computer and Data Processing Room Unitary Air Conditioners,” approved on June 28, 2007, (ASHRAE 127-2007), IBR approved for § 431.96 and appendix E to this subpart.
(8) ANSI/ASHRAE Standard 127-2020 (“ANSI/ASHRAE 127-2020”), Method of Rating Air-Conditioning Units Serving Data Center (DC) and Other Information Technology Equipment (ITE) Spaces, ANSI-approved on November 30, 2020; IBR approved for appendix E1 to this subpart.
(9) ANSI/ASHRAE Standard 198- 2013 (“ANSI/ASHRAE 198-2013”), “Method of Test for Rating DX-Dedicated Outdoor Air Systems for Moisture Removal Capacity and Moisture Removal Efficiency,” ANSI-approved January 30, 2013; IBR approved for appendix B to this subpart.
(d) IIR. International Institute of Refrigeration, 177 Boulevard Malesherbes 75017 Paris, France; +33 (0)1 42 27 32 35; www.iifiir.org.
(1) Properties of Secondary Working Fluids for Indirect Systems, including Section 2.3 Errata Sheet, Melinder, published 2010 (“Melinder 2010”), IBR approved for appendix C1 to this subpart.
(2) [Reserved]
(e) ISO. International Organization for Standardization, Chemin de Blandonnet 8, CP 401, 1214 Vernier, Geneva, Switzerland; +41 22 749 01 11; www.iso.org/store.html.
(1) ISO Standard 13256-1 (“ISO 13256-1:1998”), “Water-source heat pumps—Testing and rating for performance—Part 1: Water-to-air and brine-to-air heat pumps,” approved 1998; IBR approved for appendix C to this subpart.
(2) [Reserved]
[77 FR 28989, May 16, 2012, as amended at 80 FR 37148, June 30, 2015; 80 FR 79669, Dec. 23, 2015; 87 FR 45198, July 27, 2022; 87 FR 63896, Oct. 20, 2022; 87 FR 75168, Dec. 7, 2022; 87 FR 77325, Dec. 16, 2022; 88 FR 21839, Apr. 11, 2023; 88 FR 84228, Dec. 4, 2023; 89 FR 44037, May 20, 2024]
(a) Scope. This section contains test procedures for measuring, pursuant to EPCA, the energy efficiency of any small, large, or very large commercial package air-conditioning and heating equipment, packaged terminal air conditioners and packaged terminal heat pumps, computer room air conditioners, variable refrigerant flow systems, single package vertical air conditioners and single package vertical heat pumps, and direct expansion-dedicated outdoor air systems.
(b) Testing and calculations.
(1) Determine the energy efficiency and capacity of each category of covered equipment by conducting the test procedure(s) listed in table 1 to this paragraph (b) along with any additional testing provisions set forth in paragraphs (c) through (g) of this section and appendices A through G1 to this subpart, that apply to the energy efficiency descriptor for that equipment, category, and cooling capacity. The omitted sections of the test procedures listed in table 1 must not be used. For equipment with multiple appendices listed in table 1, consult the notes at the beginning of those appendices to determine the applicable appendix to use for testing.
(2) After June 24, 2016, any representations made with respect to the energy use or efficiency of packaged terminal air conditioners and heat pumps (PTACs and PTHPs) must be made in accordance with the results of testing pursuant to this section. Manufacturers conducting tests of PTACs and PTHPs after July 30, 2015 and prior to June 24, 2016, must conduct such test in accordance with either table 1 to this section or § 431.96 as it appeared at 10 CFR part 431, subpart F, in the 10 CFR parts 200 to 499 edition revised as of January 1, 2014. Any representations made with respect to the energy use or efficiency of such packaged terminal air conditioners and heat pumps must be in accordance with whichever version is selected.
| Equipment | Category | Cooling capacity or moisture removal capacity 1 | Energy efficiency descriptor | Use tests, conditions, and procedures in | Additional test procedure provisions as indicated in the listed paragraphs of this section |
|---|---|---|---|---|---|
| Commercial Package Air Conditioning and Heating Equipment | Air-Cooled, 3-Phase, AC and HP | <65,000 Btu/h | SEER and HSPF | Appendix F to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Air-Cooled, 3-Phase, AC and HP | <65,000 Btu/h | SEER2 and HSPF2 | Appendix F1 to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Air-Cooled AC and HP (excluding double-duct AC and HP) | ≥65,000 Btu/h and <760,000 Btu/h | EER, IEER, and COP | Appendix A to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Air-Cooled AC and HP (excluding double-duct AC and HP) | ≥65,000 Btu/h and <760,000 Btu/h | EER2, COP2, IVEC, and IVHE | Appendix A1 to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Double-duct AC and HP | ≥65,000 Btu/h and <300,000 Btu/h | EER, IEER, and COP | Appendix A to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Double-duct AC and HP | ≥65,000 Btu/h and <300,000 Btu/h | EER2, COP2, IVEC, and IVHE | Appendix A1 to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Water-Cooled and Evaporatively-Cooled AC | <760,000 Btu/h | EER and IEER | Appendix A to this subpart 2 | None. |
| Commercial Package Air Conditioning and Heating Equipment | Water-Cooled and Evaporatively-Cooled AC | <760,000 Btu/h | EER2 and IVEC | Appendix A1 to this subpart 2 | None. |
| Water-Source Heat Pumps | HP | <760,000 Btu/h | EER and COP | Appendix C to this subpart 2 | None. |
| Water-Source Heat Pumps | HP | <760,000 Btu/h | IEER and ACOP | Appendix C1 to this subpart 2 | None. |
| Packaged Terminal Air Conditioners and Heat Pumps | AC and HP | <760,000 Btu/h | EER and COP | Paragraph (g) of this section | Paragraphs (c), (e), and (g). |
| Computer Room Air Conditioners | AC | <760,000 Btu/h | SCOP | Appendix E to this subpart 2 | None. |
| Computer Room Air Conditioners | AC | <760,000 Btu/h or <930,000 Btu/h 3 | NSenCOP | Appendix E1 to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems | AC | <65,000 Btu/h (3-phase) | SEER | Appendix F to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems | AC | <65,000 Btu/h (3-phase) | SEER2 | Appendix F1 to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Air-cooled | HP | <65,000 Btu/h (3-phase) | SEER and HSPF | Appendix F to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Air-cooled | HP | <65,000 Btu/h (3-phase) | SEER2 and HSPF2 | Appendix F1 to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Air-cooled | AC and HP | ≥65,000 Btu/h and <760,000 Btu/h | EER and COP | Appendix D to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Air-cooled | AC and HP | ≥65,000 Btu/h and <760,000 Btu/h | IEER and COP | Appendix D1 to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Water-source | HP | <760,000 Btu/h | EER and COP | Appendix D to this subpart 2 | None. |
| Variable Refrigerant Flow Multi-split Systems, Water-source | HP | <760,000 Btu/h | IEER and COP | Appendix D1 to this subpart 2 | None. |
| Single Package Vertical Air Conditioners and Single Package Vertical Heat Pumps | AC and HP | <760,000 Btu/h | EER and COP | Appendix G to this subpart 2 | None. |
| Single Package Vertical Air Conditioners and Single Package Vertical Heat Pumps | AC and HP | <760,000 Btu/h | EER, IEER, and COP | Appendix G1 to this subpart 2 | None. |
| Direct Expansion-Dedicated Outdoor Air Systems | All | <324 lbs. of moisture removal/hr | ISMRE2 and ISCOP2 | Appendix B to this subpart | None. |
| 1 Moisture removal capacity applies only to direct expansion-dedicated outdoor air systems. | |||||
| 2 For equipment with multiple appendices listed in this table, consult the notes at the beginning of those appendices to determine the applicable appendix to use for testing. | |||||
| 3 For upflow ducted and downflow floor-mounted computer room air conditioners, the test procedure in appendix E1 to this subpart applies to equipment with net sensible cooling capacity less than 930,000 Btu/h. For all other configurations of computer room air conditioners, the test procedure in appendix E1 to this subpart applies to equipment with net sensible cooling capacity less than 760,000 Btu/h. | |||||
(c) Optional break-in period for tests conducted using AHRI 210/240-2008, AHRI 1230-2010, and ASHRAE 127-2007. Manufacturers may optionally specify a “break-in” period, not to exceed 20 hours, to operate the equipment under test prior to conducting the test method specified by AHRI 210/240-2008 or ASHRAE 127-2007 (incorporated by reference; see § 431.95). A manufacturer who elects to use an optional compressor break-in period in its certification testing should record this information (including the duration) in the test data underlying the certified ratings that is required to be maintained under 10 CFR 429.71.
(d) Refrigerant line length corrections for tests conducted using AHRI 1230-2010. For test setups where it is physically impossible for the laboratory to use the required line length listed in Table 3 of the AHRI 1230-2010 (incorporated by reference, see § 431.95), then the actual refrigerant line length used by the laboratory may exceed the required length and the following correction factors are applied:
| Piping length beyond minimum, X (ft) |
Piping length beyond minimum, Y (m) |
Cooling capacity correction % |
|---|---|---|
| 0>X ≤20 | 0>Y ≤6.1 | 1 |
| 20>X ≤40 | 6.1>Y ≤12.2 | 2 |
| 40>X ≤60 | 12.2>Y ≤18.3 | 3 |
| 60>X ≤80 | 18.3>Y ≤24.4 | 4 |
| 80>X ≤100 | 24.4>Y ≤30.5 | 5 |
| 100 >X ≤120 | 30.5>Y ≤36.6 | 6 |
(e) Additional provisions for equipment set-up. The only additional specifications that may be used in setting up the basic model for test are those set forth in the installation and operation manual shipped with the unit. Each unit should be set up for test in accordance with the manufacturer installation and operation manuals. Paragraphs (e)(1) through (3) of this section provide specifications for addressing key information typically found in the installation and operation manuals.
(1) If a manufacturer specifies a range of superheat, sub-cooling, and/or refrigerant pressure in its installation and operation manual for a given basic model, any value(s) within that range may be used to determine refrigerant charge or mass of refrigerant, unless the manufacturer clearly specifies a rating value in its installation and operation manual, in which case the specified rating value shall be used.
(2) The air flow rate used for testing must be that set forth in the installation and operation manuals being shipped to the commercial customer with the basic model and clearly identified as that used to generate the DOE performance ratings. If a rated air flow value for testing is not clearly identified, a value of 400 standard cubic feet per minute (scfm) per ton shall be used.
(3) For VRF systems, the test set-up and the fixed compressor speeds (i.e., the maximum, minimum, and any intermediate speeds used for testing) should be recorded and maintained as part of the test data underlying the certified ratings that is required to be maintained under 10 CFR 429.71.
(f) Manufacturer involvement in assessment or enforcement testing for variable refrigerant flow systems. A manufacturer's representative will be allowed to witness assessment and/or enforcement testing for VRF systems. The manufacturer's representative will be allowed to inspect and discuss set-up only with a DOE representative and adjust only the modulating components during testing in the presence of a DOE representative that are necessary to achieve steady-state operation. Only previously documented specifications for set-up as specified under paragraphs (d) and (e) of this section will be used.
(g) Test Procedures for Packaged Terminal Air Conditioners and Packaged Terminal Heat Pumps —
(1) Cooling mode testing. The test method for testing packaged terminal air conditioners and packaged terminal heat pumps in cooling mode shall consist of application of the methods and conditions in AHRI 310/380-2014 sections 3, 4.1, 4.2, 4.3, and 4.4 (incorporated by reference; see § 431.95), and in ANSI/ASHRAE 16 (incorporated by reference; see § 431.95) or ANSI/ASHRAE 37 (incorporated by reference; see § 431.95), except that instruments used for measuring electricity input shall be accurate to within ±0.5 percent of the quantity measured. Where definitions provided in AHRI 310/380-2014, ANSI/ASHRAE 16, and/or ANSI/ASHRAE 37 conflict with the definitions provided in 10 CFR 431.92, the 10 CFR 431.92 definitions shall be used. Where AHRI 310/380-2014 makes reference to ANSI/ASHRAE 16, it is interpreted as reference to ANSI/ASHRAE 16-1983 (RA 2014).
(2) Heating mode testing. The test method for testing packaged terminal heat pumps in heating mode shall consist of application of the methods and conditions in AHRI 310/380-2014 sections 3, 4.1, 4.2 (except the section 4.2.1.2(b) reference to ANSI/ASHRAE 37), 4.3, and 4.4 (incorporated by reference; see § 431.95), and in ANSI/ASHRAE 58 (incorporated by reference; see § 431.95). Where definitions provided in AHRI 310/380-2014 or ANSI/ASHRAE 58 conflict with the definitions provided in 10 CFR 431.92, the 10 CFR 431.92 definitions shall be used. Where AHRI 310/380-2014 makes reference to ANSI/ASHRAE 58, it is interpreted as reference to ANSI/ASHRAE 58-1986 (RA 2014).
(3) Wall sleeves. For packaged terminal air conditioners and packaged terminal heat pumps, the unit must be installed in a wall sleeve with a 14 inch depth if available. If a 14 inch deep wall sleeve is not available, use the available wall sleeve option closest to 14 inches in depth. The area(s) between the wall sleeve and the insulated partition between the indoor and outdoor rooms must be sealed to eliminate all air leakage through this area.
(4) Optional pre-filling of the condensate drain pan. For packaged terminal air conditioners and packaged terminal heat pumps, test facilities may add water to the condensate drain pan of the equipment under test (until the water drains out due to overflow devices or until the pan is full) prior to conducting the test method specified by AHRI 310/380-2014 (incorporated by reference, see § 431.95). No specific level of water mineral content or water temperature is required for the water added to the condensate drain pan.
(5) Filter selection. For packaged terminal air conditioners and packaged terminal heat pumps, the indoor filter used during testing shall be the standard or default filter option shipped with the model. If a particular model is shipped without a filter, the unit must be tested with a MERV-1 filter sized appropriately for the filter slot.
[77 FR 28989, May 16, 2012; 80 FR 11857, Mar. 5, 2015, as amended at 80 FR 37148, June 30, 2015; 80 FR 79669, Dec. 23, 2015; 87 FR 45198, July 27, 2022; 87 FR 63897, Oct. 20, 2022; 87 FR 75168, Dec. 7, 2022; 87 FR 77325, Dec. 16, 2022; 88 FR 21839, Apr. 11, 2023; 88 FR 36424, June 2, 2023; 88 FR 84228, Dec. 4, 2023; 89 FR 44037, May 20, 2024; 90 FR 6794, Jan. 21, 2025]
(a) All basic models of commercial package air conditioning and heating equipment must be tested for performance using the applicable DOE test procedure in § 431.96, be compliant with the applicable standards set forth in paragraphs (b) through (i) of this section, and be certified to the Department under 10 CFR part 429.
(b) Each air-cooled commercial package air conditioning and heating equipment (excluding air-cooled equipment with cooling capacity less than 65,000 Btu/h and double-duct air conditioners or heat pumps) manufactured on or after January 1, 2023, and before January 1, 2029, must meet the applicable minimum energy efficiency standard level(s) set forth in table 1 to this paragraph (b). Each air-cooled commercial package air conditioning and heating equipment (excluding air-cooled equipment with cooling capacity less than 65,000 Btu/h and double-duct air conditioners or heat pumps) manufactured on or after January 1, 2029, must meet the applicable minimum energy efficiency standard level(s) set forth in table 2 to this paragraph (b). Each water-cooled commercial package air conditioning and heating equipment manufactured on or after the compliance date listed in table 3 to this paragraph (b) must meet the applicable minimum energy efficiency standard level(s) set forth in table 3. Each evaporatively-cooled commercial air conditioning and heating equipment manufactured on or after the compliance date listed in table 4 to this paragraph (b) must meet the applicable minimum energy efficiency standard level(s) set forth in table 4. Each double-duct air conditioner or heat pump manufactured on or after January 1, 2010, must meet the applicable minimum energy efficiency standard level(s) set forth in table 5 to this paragraph (b).
| Cooling capacity | Subcategory | Supplementary heating type | Minimum
efficiency 1 |
Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|---|
| Air-Cooled Commercial Package Air Conditioning and Heating Equipment With a Cooling Capacity Greater Than or Equal to 65,000 Btu/h (Excluding Double-Duct Air Conditioners and Heat Pumps) | ||||
| ≥65,000 Btu/h and <135,000 Btu/h | AC | Electric Resistance Heating or No Heating | IEER = 14.8 | January 1, 2023. |
| ≥65,000 Btu/h and <135,000 Btu/h | AC | All Other Types of Heating | IEER = 14.6 | January 1, 2023. |
| ≥65,000 Btu/h and <135,000 Btu/h | HP | Electric Resistance Heating or No Heating | IEER = 14.1
COP = 3.4 |
January 1, 2023. |
| ≥65,000 Btu/h and <135,000 Btu/h | HP | All Other Types of Heating | IEER = 13.9
COP = 3.4 |
January 1, 2023. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | Electric Resistance Heating or No Heating | IEER = 14.2 | January 1, 2023. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | All Other Types of Heating | IEER = 14.0 | January 1, 2023. |
| ≥135,000 Btu/h and <240,000 Btu/h | HP | Electric Resistance Heating or No Heating | IEER = 13.5
COP = 3.3 |
January 1, 2023. |
| ≥135,000 Btu/h and <240,000 Btu/h | HP | All Other Types of Heating | IEER = 13.3
COP = 3.3 |
January 1, 2023. |
| ≥240,000 Btu/h and <760,000 Btu/h | AC | Electric Resistance Heating or No Heating | IEER = 13.2 | January 1, 2023. |
| ≥240,000 Btu/h and <760,000 Btu/h | AC | All Other Types of Heating | IEER = 13.0 | January 1, 2023. |
| ≥240,000 Btu/h and <760,000 Btu/h | HP | Electric Resistance Heating or No Heating | IEER = 12.5
COP = 3.2 |
January 1, 2023. |
| ≥240,000 Btu/h and <760,000 Btu/h | HP | All Other Types of Heating | IEER = 12.3
COP = 3.2 |
January 1, 2023. |
| 1 See section 3 of appendix A to this subpart for the test conditions upon which the COP standards are based. | ||||
| Cooling capacity | Subcategory | Supplementary heating type | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|---|
| Air-Cooled Commercial Package Air Conditioning and Heating Equipment With a Cooling Capacity Greater Than or Equal to 65,000 Btu/h (Excluding Double-Duct Air Conditioners and Heat Pumps) | ||||
| ≥65,000 Btu/h and <135,000 Btu/h | AC | Electric Resistance Heating or No Heating | IVEC = 14.3 | January 1, 2029. |
| ≥65,000 Btu/h and <135,000 Btu/h | AC | All Other Types of Heating | IVEC = 13.8 | January 1, 2029. |
| ≥65,000 Btu/h and <135,000 Btu/h | HP | All Types of Heating | IVEC = 13.4
IVHE = 6.2 |
January 1, 2029. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | Electric Resistance Heating or No Heating | IVEC = 13.8 | January 1, 2029. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | All Other Types of Heating | IVEC = 13.3 | January 1, 2029. |
| ≥135,000 Btu/h and <240,000 Btu/h | HP | All Types of Heating | IVEC = 13.1
IVHE = 6.0 |
January 1, 2029. |
| ≥240,000 Btu/h and <760,000 Btu/h | AC | Electric Resistance Heating or No Heating | IVEC = 12.9 | January 1, 2029. |
| ≥240,000 Btu/h and <760,000 Btu/h | AC | All Other Types of Heating | IVEC = 12.2 | January 1, 2029. |
| ≥240,000 Btu/h and <760,000 Btu/h | HP | All Types of Heating | IVEC = 12.1
IVHE = 5.8 |
January 1, 2029. |
| Cooling capacity | Supplementary heating type | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|
| Water-Cooled Commercial Package Air Conditioning Equipment | |||
| <65,000 Btu/h | All | EER = 12.1 | October 29, 2003. |
| ≥65,000 Btu/h and <135,000 Btu/h | No Heating or Electric Resistance Heating | EER = 12.1 | June 1, 2013. |
| ≥65,000 Btu/h and <135,000 Btu/h | All Other Types of Heating | EER = 11.9 | June 1, 2013. |
| ≥135,000 Btu/h and <240,000 Btu/h | No Heating or Electric Resistance Heating | EER = 12.5 | June 1, 2014. |
| ≥135,000 Btu/h and <240,000 Btu/h | All Other Types of Heating | EER = 12.3 | June 1, 2014. |
| ≥240,000 Btu/h and <760,000 Btu/h | No Heating or Electric Resistance Heating | EER = 12.4 | June 1, 2014. |
| ≥240,000 Btu/h and <760,000 Btu/h | All Other Types of Heating | EER = 12.2 | June 1, 2014. |
| Cooling capacity | Supplementary heating type | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|
| Evaporatively-Cooled Commercial Package Air Conditioning Equipment | |||
| <65,000 Btu/h | All | EER = 12.1 | October 29, 2003. |
| ≥65,000 Btu/h and <135,000 Btu/h | No Heating or Electric Resistance Heating | EER = 12.1 | June 1, 2013. |
| ≥65,000 Btu/h and <135,000 Btu/h | All Other Types of Heating | EER = 11.9 | June 1, 2013. |
| ≥135,000 Btu/h and <240,000 Btu/h | No Heating or Electric Resistance Heating | EER = 12.0 | June 1, 2014. |
| ≥135,000 Btu/h and <240,000 Btu/h | All Other Types of Heating | EER = 11.8 | June 1, 2014. |
| ≥240,000 Btu/h and <760,000 Btu/h | No Heating or Electric Resistance Heating | EER = 11.9 | June 1, 2014. |
| ≥240,000 Btu/h and <760,000 Btu/h | All Other Types of Heating | EER = 11.7 | June 1, 2014. |
| Cooling capacity | Subcategory | Supplementary heating type | Minimum
efficiency 1 |
Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|---|
| Double-Duct Air Conditioners or Heat Pumps | ||||
| ≥65,000 Btu/h and <135,000 Btu/h | AC | Electric Resistance Heating or No Heating | EER = 11.2 | January 1, 2010. |
| ≥65,000 Btu/h and <135,000 Btu/h | AC | All Other Types of Heating | EER = 11.0 | January 1, 2010. |
| ≥65,000 Btu/h and <135,000 Btu/h | HP | Electric Resistance Heating or No Heating | EER = 11.0 COP = 3.3 |
January 1, 2010. |
| ≥65,000 Btu/h and <135,000 Btu/h | HP | All Other Types of Heating | EER = 10.8 COP = 3.3 |
January 1, 2010. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | Electric Resistance Heating or No Heating | EER = 11.0 | January 1, 2010. |
| ≥135,000 Btu/h and <240,000 Btu/h | AC | All Other Types of Heating | EER = 10.8 | January 1, 2010. |
| ≥135,000 Btu/h and <240,000 Btu/h | HP | Electric Resistance Heating or No Heating | EER = 10.6 COP = 3.2 |
January 1, 2010. |
| ≥135,000 Btu/h and <240,000 Btu/h | HP | All Other Types of Heating | EER = 10.4 COP = 3.2 |
January 1, 2010. |
| ≥240,000 Btu/h and <300,000 Btu/h | AC | Electric Resistance Heating or No Heating | EER = 10.0 | January 1, 2010. |
| ≥240,000 Btu/h and <300,000 Btu/h | AC | All Other Types of Heating | EER = 9.8 | January 1, 2010. |
| ≥240,000 Btu/h and <300,000 Btu/h | HP | Electric Resistance Heating or No Heating | EER = 9.5 COP = 3.2 |
January 1, 2010. |
| ≥240,000 Btu/h and <300,000 Btu/h | HP | All Other Types of Heating | EER = 9.3 COP = 3.2 |
January 1, 2010. |
| 1 See section 3 of appendix A to this subpart for the test conditions upon which the COP standards are based. | ||||
(c) Each water-source heat pump manufactured starting on the compliance date listed in table 6 to this paragraph (c) must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (c).
| Cooling capacity | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|
| Water-Source Heat Pumps (Water-to-Air, Water-Loop) | ||
| <17,000 Btu/h | EER = 12.2
COP = 4.3 |
October 9, 2015. |
| ≥17,000 Btu/h and <65,000 Btu/h | EER = 13.0
COP = 4.3 |
October 9, 2015. |
| ≥65,000 Btu/h and <135,000 Btu/h | EER = 13.0
COP = 4.3 |
October 9, 2015. |
(d) Each non-standard size packaged terminal air conditioner (PTAC) and packaged terminal heat pump (PTHP) manufactured on or after October 7, 2010, must meet the applicable minimum energy efficiency standard level(s) set forth in table 7 to this paragraph (d). Each standard size PTAC manufactured on or after October 8, 2012, and before January 1, 2017, must meet the applicable minimum energy efficiency standard level(s) set forth in table 7. Each standard size PTHP manufactured on or after October 8, 2012, must meet the applicable minimum energy efficiency standard level(s) set forth in table 7. Each standard size PTAC manufactured on or after January 1, 2017, must meet the applicable minimum energy efficiency standard level(s) set forth in table 8 to this paragraph (d).
| Equipment type | Category | Cooling capacity | Minimum efficiency | Compliance date: products
manufactured on and after . . . |
|---|---|---|---|---|
| PTAC | Standard Size | <7,000 Btu/h | EER = 11.7 | October 8, 2012.2 |
| ≥7,000 Btu/h and ≤15,000 Btu/h | EER = 13.8−(0.3 × Cap 1) | October 8, 2012.2 | ||
| >15,000 Btu/h | EER = 9.3 | October 8, 2012.2 | ||
| Non-Standard Size | <7,000 Btu/h | EER = 9.4 | October 7, 2010. | |
| ≥7,000 Btu/h and ≤15,000 Btu/h | EER = 10.9−(0.213 × Cap 1) | October 7, 2010. | ||
| >15,000 Btu/h | EER = 7.7 | October 7, 2010. | ||
| PTHP | Standard Size | <7,000 Btu/h | EER = 11.9 COP = 3.3 |
October 8, 2012. |
| ≥7,000 Btu/h and ≤15,000 Btu/h | EER = 14.0−(0.3 × Cap 1) COP = 3.7−(0.052 × Cap 1) |
October 8, 2012. | ||
| >15,000 Btu/h | EER = 9.5 COP = 2.9 |
October 8, 2012. | ||
| Non-Standard Size | <7,000 Btu/h | EER = 9.3 COP = 2.7 |
October 7, 2010. | |
| ≥7,000 Btu/h and ≤15,000 Btu/h | EER = 10.8−(0.213 × Cap 1) COP = 2.9−(0.026 × Cap 1) |
October 7, 2010. | ||
| >15,000 Btu/h | EER = 7.6 COP = 2.5 |
October 7, 2010. | ||
| 1 “Cap” means cooling capacity in thousand Btu/h at 95 °F outdoor dry-bulb temperature. | ||||
| 2 And manufactured before January 1, 2017. See table 8 to this paragraph (d) for updated efficiency standards that apply to this category of equipment manufactured on and after January 1, 2017. | ||||
| Equipment type | Category | Cooling capacity | Minimum efficiency | Compliance date: products
manufactured on and after . . . |
|---|---|---|---|---|
| PTAC | Standard Size | <7,000 Btu/h | EER = 11.9 | January 1, 2017. |
| ≥7,000 Btu/h and ≤15,000 Btu/h | EER = 14.0−(0.3 × Cap 1) | January 1, 2017. | ||
| >15,000 Btu/h | EER = 9.5 | January 1, 2017. | ||
| 1 “Cap” means cooling capacity in thousand Btu/h at 95 °F outdoor dry-bulb temperature. | ||||
(e)
(1) Each single package vertical air conditioner and single package vertical heat pump manufactured on or after January 1, 2010, but before October 9, 2015 (for models ≥65,000 Btu/h and <135,000 Btu/h), or October 9, 2016 (for models ≥135,000 Btu/h and <240,000 Btu/h), must meet the applicable minimum energy conservation standard level(s) set forth in this paragraph (e)(1).
| Equipment type | Cooling capacity | Sub-
category |
Efficiency level | Compliance date: products
manufactured on and after . . . |
|---|---|---|---|---|
| Single package vertical air conditioners and single package vertical heat pumps, single-phase and three-phase | <65,000 Btu/h | AC
HP |
EER = 9.0
EER = 9.0 COP = 3.0 |
January 1, 2010.
January 1, 2010. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥65,000 Btu/h and <135,000 Btu/h | AC
HP |
EER = 8.9
EER = 8.9 COP = 3.0 |
January 1, 2010.
January 1, 2010. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥135,000 Btu/h and <240,000 Btu/h | AC
HP |
EER = 8.6
EER = 8.6 COP = 2.9 |
January 1, 2010.
January 1, 2010. |
(2) Each single package vertical air conditioner and single package vertical heat pump manufactured on and after October 9, 2015 (for models ≥65,000 Btu/h and <135,000 Btu/h), or October 9, 2016 (for models ≥135,000 Btu/h and <240,000 Btu/h), but before September 23, 2019, must meet the applicable minimum energy conservation standard level(s) set forth in this paragraph (e)(2).
| Equipment type | Cooling capacity | Sub-
category |
Efficiency level | Compliance date: products
manufactured on and after . . . |
|---|---|---|---|---|
| Single package vertical air conditioners and single package vertical heat pumps, single-phase and three-phase | <65,000 Btu/h | AC
HP |
EER = 9.0
EER = 9.0 COP = 3.0 |
January 1, 2010.
January 1, 2010. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥65,000 Btu/h and <135,000 Btu/h | AC
HP |
EER = 10.0
EER = 10.0 COP = 3.0 |
October 9, 2015.
October 9, 2015. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥135,000 Btu/h and <240,000 Btu/h | AC
HP |
EER = 10.0
EER = 10.0 COP = 3.0 |
October 9, 2016.
October 9, 2016. |
(3) Each single package vertical air conditioner and single package vertical heat pump manufactured on and after September 23, 2019, must meet the applicable minimum energy conservation standard level(s) set forth in this paragraph (e)(3).
| Equipment type | Cooling capacity | Sub-
category |
Efficiency level | Compliance date: products
manufactured on and after . . . |
|---|---|---|---|---|
| Single package vertical air conditioners and single package vertical heat pumps, single-phase and three-phase | <65,000 Btu/h | AC
HP |
EER = 11.0
EER = 11.0 COP = 3.3 |
September 23, 2019.
September 23, 2019. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥65,000 Btu/h and <135,000 Btu/h | AC
HP |
EER = 10.0
EER = 10.0 COP = 3.0 |
October 9, 2015.
October 9, 2015. |
| Single package vertical air conditioners and single package vertical heat pumps | ≥135,000 Btu/h and <240,000 Btu/h | AC
HP |
EER = 10.0
EER = 10.0 COP = 3.0 |
October 9, 2016.
October 9, 2016. |
(f)
(1) Each computer room air conditioner with a net sensible cooling capacity less than 65,000 Btu/h manufactured on or after October 29, 2012, and before May 28, 2024 and each computer room air conditioner with a net sensible cooling capacity greater than or equal to 65,000 Btu/h and less than 760,000 Btu/h manufactured on or after October 29, 2013, and before May 28, 2024 must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (f)(1).
| Equipment type | Net sensible cooling capacity | Minimum SCOP efficiency | |
|---|---|---|---|
| Downflow | Upflow | ||
| Air-Cooled | <65,000 Btu/h | 2.20 | 2.09 |
| ≥65,000 Btu/h and <240,000 Btu/h | 2.10 | 1.99 | |
| ≥240,000 Btu/h and <760,000 Btu/h | 1.90 | 1.79 | |
| Water-Cooled | <65,000 Btu/h | 2.60 | 2.49 |
| ≥65,000 Btu/h and <240,000 Btu/h | 2.50 | 2.39 | |
| ≥240,000 Btu/h and <760,000 Btu/h | 2.40 | 2.29 | |
| Water-Cooled with Fluid Economizer | <65,000 Btu/h | 2.55 | 2.44 |
| ≥65,000 Btu/h and <240,000 Btu/h | 2.45 | 2.34 | |
| ≥240,000 Btu/h and <760,000 Btu/h | 2.35 | 2.24 | |
| Glycol-Cooled | <65,000 Btu/h | 2.50 | 2.39 |
| ≥65,000 Btu/h and <240,000 Btu/h | 2.15 | 2.04 | |
| ≥240,000 Btu/h and <760,000 Btu/h | 2.10 | 1.99 | |
| Glycol-Cooled with Fluid Economizer | <65,000 Btu/h | 2.45 | 2.34 |
| ≥65,000 Btu/h and <240,000 Btu/h | 2.10 | 1.99 | |
| ≥240,000 Btu/h and <760,000 Btu/h | 2.05 | 1.94 | |
(2) Each computer room air conditioner manufactured on or after May 28, 2024, must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (f)(2).
| Equipment type | Downflow and upflow ducted | Upflow non-ducted and horizontal flow | ||||
|---|---|---|---|---|---|---|
| Net sensible cooling capacity | Minimum NSenCOP
efficiency |
Net sensible cooling capacity | Minimum NSenCOP
efficiency |
|||
| Downflow | Upflow ducted | Upflow
non-ducted |
Horizontal flow | |||
| Air-Cooled | <80,000 Btu/h | 2.70 | 2.67 | <65,000 Btu/h | 2.16 | 2.65 |
| ≥80,000 Btu/h and <295,000 Btu/h | 2.58 | 2.55 | ≥65,000 Btu/h and <240,000 Btu/h | 2.04 | 2.55 | |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.36 | 2.33 | ≥240,000 Btu/h and <760,000 Btu/h | 1.89 | 2.47 | |
| Air-Cooled with Fluid Economizer | <80,000 Btu/h
≥80,000 Btu/h and <295,000 Btu/h |
2.70
2.58 |
2.67
2.55 |
<65,000 Btu/h
≥65,000 Btu/h and <240,000 Btu/h |
2.09
1.99 |
2.65
2.55 |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.36 | 2.33 | ≥240,000 Btu/h and <760,000 Btu/h | 1.81 | 2.47 | |
| Water-Cooled | <80,000 Btu/h | 2.82 | 2.79 | <65,000 Btu/h | 2.43 | 2.79 |
| ≥80,000 Btu/h and <295,000 Btu/h | 2.73 | 2.70 | ≥65,000 Btu/h and <240,000 Btu/h | 2.32 | 2.68 | |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.67 | 2.64 | ≥240,000 Btu/h and <760,000 Btu/h | 2.20 | 2.60 | |
| Water-Cooled with Fluid Economizer | <80,000 Btu/h
≥80,000 Btu/h and <295,000 Btu/h |
2.77
2.68 |
2.74
2.65 |
<65,000 Btu/h
≥65,000 Btu/h and <240,000 Btu/h |
2.35
2.24 |
2.71
2.60 |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.61 | 2.58 | ≥240,000 Btu/h and <760,000 Btu/h | 2.12 | 2.54 | |
| Glycol-Cooled | <80,000 Btu/h | 2.56 | 2.53 | <65,000 Btu/h | 2.08 | 2.48 |
| ≥80,000 Btu/h and <295,000 Btu/h | 2.24 | 2.21 | ≥65,000 Btu/h and <240,000 Btu/h | 1.90 | 2.18 | |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.21 | 2.18 | ≥240,000 Btu/h and <760,000 Btu/h | 1.81 | 2.18 | |
| Glycol-Cooled with Fluid Economizer | <80,000 Btu/h
≥80,000 Btu/h and <295,000 Btu/h |
2.51
2.19 |
2.48
2.16 |
<65,000 Btu/h
≥65,000 Btu/h and <240,000 Btu/h |
2.00
1.82 |
2.44
2.10 |
| ≥295,000 Btu/h and <930,000 Btu/h | 2.15 | 2.12 | ≥240,000 Btu/h and <760,000 Btu/h | 1.73 | 2.10 | |
| Equipment type | Net sensible cooling capacity | Minimum NSenCOP
efficiency |
|
|---|---|---|---|
| Ducted | Non-ducted | ||
| Air-Cooled with Free Air Discharge Condenser | <29,000 Btu/h | 2.05 | 2.08 |
| ≥29,000 Btu/h and <65,000 Btu/h | 2.02 | 2.05 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.92 | 1.94 | |
| Air-Cooled with Free Air Discharge Condenser and Fluid Economizer | <29,000 Btu/h | 2.01 | 2.04 |
| ≥29,000 Btu/h and <65,000 Btu/h | 1.97 | 2 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.87 | 1.89 | |
| Air-Cooled with Ducted Condenser | <29,000 Btu/h | 1.86 | 1.89 |
| ≥29,000 Btu/h and <65,000 Btu/h | 1.83 | 1.86 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.73 | 1.75 | |
| Air-Cooled with Fluid Economizer and Ducted Condenser | <29,000 Btu/h | 1.82 | 1.85 |
| ≥29,000 Btu/h and <65,000 Btu/h | 1.78 | 1.81 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.68 | 1.7 | |
| Water-Cooled | <29,000 Btu/h | 2.38 | 2.41 |
| ≥29,000 Btu/h and <65,000 Btu/h | 2.28 | 2.31 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 2.18 | 2.2 | |
| Water-Cooled with Fluid Economizer | <29,000 Btu/h | 2.33 | 2.36 |
| ≥29,000 Btu/h and <65,000 Btu/h | 2.23 | 2.26 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 2.13 | 2.16 | |
| Glycol-Cooled | <29,000 Btu/h | 1.97 | 2 |
| ≥29,000 Btu/h and <65,000 Btu/h | 1.93 | 1.98 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.78 | 1.81 | |
| Glycol-Cooled with Fluid Economizer | <29,000 Btu/h | 1.92 | 1.95 |
| ≥29,000 Btu/h and <65,000 Btu/h | 1.88 | 1.93 | |
| ≥65,000 Btu/h and <760,000 Btu/h | 1.73 | 1.76 | |
(g)
(1) Each variable refrigerant flow air conditioner or heat pump manufactured on or after the compliance date listed in table 15 to this paragraph (g)(1) and prior to January 1, 2024, must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (g)(1).
| Equipment type | Cooling
capacity |
Heating type 1 | Efficiency level | Compliance date: equipment
manufactured on and after . . . |
|---|---|---|---|---|
| VRF Multi-Split Air Conditioners (Air-Cooled) | ≥65,000 Btu/h and <135,000 Btu/h | No Heating or Electric Resistance Heating | 11.2 EER | January 1, 2010. |
| All Other Types of Heating | 11.0 EER | January 1, 2010. | ||
| ≥135,000 Btu/h and <240,000 Btu/h | No Heating or Electric Resistance Heating | 11.0 EER | January 1, 2010. | |
| All Other Types of Heating | 10.8 EER | January 1, 2010. | ||
| ≥240,000 Btu/h and <760,000 Btu/h | No Heating or Electric Resistance Heating | 10.0 EER | January 1, 2010. | |
| All Other Types of Heating | 9.8 EER | January 1, 2010. | ||
| VRF Multi-Split Heat Pumps (Air-Cooled) | ≥65,000 Btu/h and <135,000 Btu/h | No Heating or Electric Resistance Heating | 11.0 EER, 3.3 COP | January 1, 2010. |
| All Other Types of Heating | 10.8 EER, 3.3 COP | January 1, 2010. | ||
| ≥135,000 Btu/h and <240,000 Btu/h | No Heating or Electric Resistance Heating | 10.6 EER, 3.2 COP | January 1, 2010. | |
| All Other Types of Heating | 10.4 EER, 3.2 COP | January 1, 2010. | ||
| ≥240,000 Btu/h and <760,000 Btu/h | No Heating or Electric Resistance Heating | 9.5 EER, 3.2 COP | January 1, 2010. | |
| All Other Types of Heating | 9.3 EER, 3.2 COP | January 1, 2010. | ||
| VRF Multi-Split Heat Pumps (Water-Source) | <17,000 Btu/h | Without Heat Recovery | 12.0 EER,
4.2 COP |
October 29, 2012.
October 29, 2003. |
| With Heat Recovery | 11.8 EER
4.2 COP |
October 29, 2012.
October 29, 2003. |
||
| ≥17,000 Btu/h and <65,000 Btu/h | All | 12.0 EER, 4.2 COP | October 29, 2003. | |
| ≥65,000 Btu/h and <135,000 Btu/h | All | 12.0 EER, 4.2 COP | October 29, 2003. | |
| ≥135,000 Btu/h and <760,000 Btu/h | Without Heat Recovery | 10.0 EER, 3.9 COP | October 29, 2013. | |
| With Heat Recovery | 9.8 EER, 3.9 COP | October 29, 2013. | ||
| 1 VRF multi-split heat pumps (air-cooled) with heat recovery fall under the category of “All Other Types of Heating” unless they also have electric resistance heating, in which case it falls under the category for “No Heating or Electric Resistance Heating.” | ||||
(2) Each variable refrigerant flow air conditioner or heat pump (except air-cooled systems with cooling capacity less than 65,000 Btu/h) manufactured on or after January 1, 2024, must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (g)(2).
| Equipment type | Size category | Heating type | Minimum efficiency |
|---|---|---|---|
| VRF Multi-Split Air Conditioners (Air-Cooled) | ≥65,000 and <135,000 Btu/h | All | 15.5 IEER. |
| ≥135,000 and <240,000 Btu/h | All | 14.9 IEER. | |
| ≥240,000 Btu/h and <760,000 Btu/h | All | 13.9 IEER. | |
| VRF Multi-Split Heat Pumps (Air-Cooled) | ≥65,000 and <135,000 Btu/h | Heat Pump without Heat Recovery | 14.6 IEER, 3.3 COP. |
| Heat Pump with Heat Recovery | 14.4 IEER, 3.3 COP. | ||
| ≥135,000 and <240,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
13.9 IEER, 3.2 COP.
13.7 IEER, 3.2 COP. |
|
| ≥240,000 Btu/h and <760,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
12.7 IEER, 3.2 COP.
12.5 IEER, 3.2 COP. |
|
| VRF Multi-Split Heat Pumps (Water-Source) | <65,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
16.0 IEER, 4.3 COP.
15.8 IEER, 4.3 COP. |
| ≥65,000 and <135,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
16.0 IEER, 4.3 COP.
15.8 IEER, 4.3 COP. |
|
| ≥135,000 and <240,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
14.0 IEER, 4.0 COP.
13.8 IEER, 4.0 COP. |
|
| ≥240,000 Btu/h and <760,000 Btu/h | Heat Pump without Heat Recovery
Heat Pump with Heat Recovery |
12.0 IEER, 3.9 COP.
11.8 IEER, 3.9 COP. |
(h) Each direct expansion-dedicated outdoor air system manufactured on or after the compliance date listed in table 17 to this paragraph (h) must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (h).
| Equipment
category |
Subcategory | Efficiency level | Compliance date: equipment manufactured starting on . . . |
|---|---|---|---|
| Direct expansion-dedicated outdoor air systems | (AC)—Air-cooled without ventilation energy recovery systems | ISMRE2 = 3.8 | May 1, 2024. |
| (AC w/VERS)—Air-cooled with ventilation energy recovery systems | ISMRE2 = 5.0 | May 1, 2024. | |
| (ASHP)—Air-source heat pumps without ventilation energy recovery systems | ISMRE2 = 3.8 ISCOP2 = 2.05 |
May 1, 2024. | |
| (ASHP w/VERS)—Air-source heat pumps with ventilation energy recovery systems | ISMRE2 = 5.0 ISCOP2 = 3.20 |
May 1, 2024. | |
| (WC)—Water-cooled without ventilation energy recovery systems | ISMRE2 = 4.7 | May 1, 2024. | |
| (WC w/VERS)—Water-cooled with ventilation energy recovery systems | ISMRE2 = 5.1 | May 1, 2024. | |
| (WSHP)—Water-source heat pumps without ventilation energy recovery systems | ISMRE2 = 3.8 ISCOP2 = 2.13 |
May 1, 2024. | |
| (WSHP w/VERS)—Water-source heat pumps with ventilation energy recovery systems | ISMRE2 = 4.6 ISCOP2 = 4.04 |
May 1, 2024. |
(i) Air-cooled, three-phase, commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h and air-cooled, three-phase variable refrigerant flow multi-split air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h manufactured on or after the compliance date listed in tables 18 and 19 to this paragraph (i) must meet the applicable minimum energy efficiency standard level(s) set forth in this paragraph (i).
| Equipment type | Cooling
capacity |
Subcategory | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|---|
| Commercial Package Air Conditioning Equipment | <65,000 Btu/h | Split-System | 13.0 SEER | June 16, 2008.1 |
| Commercial Package Air Conditioning Equipment | <65,000 Btu/h | Single-Package | 14.0 SEER | January 1, 2017.1 |
| Commercial Package Air Conditioning and Heating Equipment | <65,000 Btu/h | Split-System | 14.0 SEER 8.2 HSPF |
January 1, 2017.1 |
| Commercial Package Air Conditioning and Heating Equipment | <65,000 Btu/h | Single-Package | 14.0 SEER 8.0 HSPF |
January 1, 2017.1 |
| VRF Air Conditioners | <65,000 Btu/h | 13.0 SEER | June 16, 2008.1 | |
| VRF Heat Pumps | <65,000 Btu/h | 13.0 SEER 7.7 HSPF |
June 16, 2008.1 | |
| 1 And manufactured before January 1, 2025. For equipment manufactured on or after January 1, 2025, see table 19 to this paragraph (i) for updated efficiency standards. | ||||
| Equipment type | Cooling
capacity |
Subcategory | Minimum efficiency | Compliance date: equipment
manufactured starting on . . . |
|---|---|---|---|---|
| Commercial Package Air Conditioning Equipment | <65,000 Btu/h | Split-System | 13.4 SEER2 | January 1, 2025. |
| Commercial Package Air Conditioning Equipment | <65,000 Btu/h | Single-Package | 13.4 SEER2 | January 1, 2025. |
| Commercial Package Air Conditioning and Heating Equipment | <65,000 Btu/h | Split-System | 14.3 SEER2 7.5 HSPF2 |
January 1, 2025. |
| Commercial Package Air Conditioning and Heating Equipment | <65,000 Btu/h | Single-Package | 13.4 SEER2 6.7 HSPF2 |
January 1, 2025. |
| Space-Constrained Commercial Package Air Conditioning Equipment | ≤30,000 Btu/h | Split-System | 12.7 SEER2 | January 1, 2025. |
| Space-Constrained Commercial Package Air Conditioning Equipment | ≤30,000 Btu/h | Single-Package | 13.9 SEER2 | January 1, 2025. |
| Space-Constrained Commercial Package Air Conditioning and Heating Equipment | ≤30,000 Btu/h | Split-System | 13.9 SEER2 7.0 HSPF2 |
January 1, 2025. |
| Space-Constrained Commercial Package Air Conditioning and Heating Equipment | ≤30,000 Btu/h | Single-Package | 13.9 SEER2 6.7 HSPF2 |
January 1, 2025. |
| Small-Duct, High-Velocity Commercial Package Air Conditioning | <65,000 Btu/h | Split-System | 13.0 SEER2 | January 1, 2025. |
| Small-Duct, High-Velocity Commercial Package Air Conditioning and Heating Equipment | <65,000 Btu/h | Split-System | 14.0 SEER2 6.9 HSPF2 |
January 1, 2025. |
| VRF Air Conditioners | <65,000 Btu/h | 13.4 SEER2 | January 1, 2025. | |
| VRF Heat Pumps | <65,000 Btu/h | 13.4 SEER2 7.5 HSPF2 |
January 1, 2025. |
[89 FR 44134, May 20, 2024]
Prior to May 15, 2025, representations with respect to the energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with:
(a) The applicable provisions (appendix A to subpart F of part 431 for air-cooled equipment, and table 1 to § 431.96 for water-cooled and evaporatively-cooled equipment) as they appeared in subpart F of 10 CFR part 431, revised as of January 1, 2024; or
(b) This appendix.
Beginning May 15, 2025, and prior to the compliance date of amended standards for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h) based on integrated ventilation, economizing, and cooling (IVEC) and integrated ventilation and heating efficiency (IVHE) (see § 431.97), representations with respect to energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with this appendix.
Beginning on the compliance date of amended standards for commercial package air conditioning and heating equipment (excluding equipment with a cooling capacity less than 65,000 Btu/h) based on IVEC and IVHE (see § 431.97), representations with respect to energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with appendix A1 to this subpart.
Manufacturers may also certify compliance with any amended energy conservation standards for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h) based on IVEC or IVHE prior to the applicable compliance date for those standards (see § 431.97), and those compliance certifications must be based on testing in accordance with appendix A1 to this subpart.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for AHRI 340/360-2022 and ANSI/ASHRAE 37-2009. However, certain enumerated provisions of AHRI 340/360-2022 and ANSI/ASHRAE 37-2009, as set forth in this section 1 are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1. AHRI 340/360-2022:
(a) Section 1 Purpose is inapplicable,
(b) Section 2 Scope is inapplicable,
(c) The following subsections of Section 3 Definitions are inapplicable: 3.2 (Basic Model), 3.4 (Commercial and Industrial Unitary Air-conditioning Equipment), 3.5 (Commercial and Industrial Unitary Heat Pump), 3.7 (Double-duct System), 3.8 (Energy Efficiency Ratio (EER)), 3.12 (Heating Coefficient of Performance (COPH)), 3.14 (Integrated Energy Efficiency Ratio (IEER)), 3.23 (Published Rating), 3.26 (Single Package Air-Conditioners), 3.27 (Single Package Heat Pumps), 3.29 (Split System Air-conditioners), 3.30 (Split System Heat Pump), 3.36 (Year Round Single Package Air-conditioners),
(d) Section 7 Minimum Data Requirements for Published Ratings is inapplicable,
(e) Section 8 Operating Requirements is inapplicable,
(f) Section 9 Marking and Nameplate Data is inapplicable,
(g) Section 10 Conformance Conditions is inapplicable,
(h) Appendix B References—Informative is inapplicable,
(i) Appendix D Unit Configuration for Standard Efficiency Determination—Normative is inapplicable,
(j) Appendix F International Rating Conditions—Normative is inapplicable,
(k) Appendix G Examples of IEER Calculations—Informative is inapplicable,
(l) Appendix H Example of Determination of Fan and Motor Efficiency for Non-standard Integrated Indoor Fan and Motors—Informative is inapplicable, and
(m) Appendix I Double-duct System Efficiency Metrics with Non-Zero Outdoor Air External Static Pressure (ESP)—Normative is inapplicable.
1.2. ANSI/ASHRAE 37-2009:
(a) Section 1 Purpose is inapplicable
(b) Section 2 Scope is inapplicable, and
(c) Section 4 Classifications is inapplicable.
2. General
Determine the applicable energy efficiency metrics (IEER, EER, and COP) in accordance with this appendix and the applicable sections of AHRI 340/360-2022 and ANSI/ASHRAE 37-2009.
Section 3 of this appendix provides additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by AHRI 340/360-2022, followed by ANSI/ASHRAE 37-2009. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
3. Test Conditions
The following conditions specified in Table 6 of AHRI 340/360-2022 apply when testing to certify to the energy conservation standards in § 431.97. For cooling mode tests for equipment subject to standards in terms of EER, test using the “Standard Rating Conditions Cooling”. For cooling mode tests for equipment subject to standards in terms of IEER, test using the “Standard Rating Conditions Cooling” and the “Standard Rating Part-Load Conditions (IEER)”. For heat pump heating mode tests for equipment subject to standards in terms of COP, test using the “Standard Rating Conditions (High Temperature Steady State Heating)”.
For equipment subject to standards in terms of EER, representations of IEER made using the “Standard Rating Part-Load Conditions (IEER)” in Table 6 of AHRI 340/360-2022 are optional. For equipment subject to standards in terms of IEER, representations of EER made using the “Standard Rating Conditions Cooling” in Table 6 of AHRI 340/360-2022 are optional. Representations of COP made using the “Standard Rating Conditions (Low Temperature Steady State Heating)” in Table 6 of AHRI 340/360-2022 are optional and are not to be used as the basis for determining compliance with energy efficiency standards in terms of COP.
[89 FR 44046, May 20, 2024]
Prior to May 15, 2025, representations with respect to the energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with:
(a) The applicable provisions (appendix A to subpart F of part 431 for air-cooled equipment, and table 1 to § 431.96 for water-cooled and evaporatively-cooled equipment) as it appeared in subpart F of 10 CFR part 431, revised as of January 1, 2024; or
(b) Appendix A to this subpart.
Beginning May 15, 2025, and prior to the compliance date of amended standards for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h) based on integrated ventilation, economizing, and cooling (IVEC) and integrated ventilation and heating efficiency (IVHE) (see § 431.97), representations with respect to energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with appendix A to this subpart.
Beginning on the compliance date of amended standards for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h) based on IVEC and IVHE (see § 431.97), representations with respect to energy use or efficiency of commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h), including compliance certifications, must be based on testing conducted in accordance with this appendix.
Manufacturers may also certify compliance with any amended energy conservation standards for commercial package air conditioning and heating equipment (excluding air-cooled equipment with a cooling capacity less than 65,000 Btu/h) based on IVEC or IVHE prior to the applicable compliance date for those standards (see § 431.97), and those compliance certifications must be based on testing in accordance with this appendix.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for AHRI 1340-2023 and ANSI/ASHRAE 37-2009. However, certain enumerated provisions of AHRI 1340-2023 and ANSI/ASHRAE 37-2009, as listed in this section 1 are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1. AHRI 1340-2023:
(a) Section 1 Purpose is inapplicable,
(b) Section 2 Scope is inapplicable,
(c) The following subsections of section 3 Definitions are inapplicable: 3.2.2 (Barometric Relief Damper), 3.2.3 (Basic Model), 3.2.5 (Commercial and Industrial Unitary Air-conditioner and Heat Pump Equipment), 3.2.5.1 (Commercial and Industrial Unitary Air-Conditioning System), 3.2.5.2 (Commercial and Industrial Unitary Heat Pump System), 3.2.7 (Double-duct System), 3.2.9 (Desiccant Dehumidification Component), 3.2.10 (Drain Pan Heater), 3.2.11.1 (Air Economizer), 3.2.12 (Energy Efficiency Ratio 2), 3.2.13 (Evaporative Cooling), 3.2.13.1 (Direct Evaporative Cooling System), 3.2.13.2 (Indirect Evaporative Cooling System), 3.2.14 (Fresh Air Damper), 3.2.15 (Fire, Smoke, or Isolation Damper), 3.2.17 (Hail Guard), 3.2.19 (Heating Coefficient of Performance 2 (COP2H)), 3.2.20 (High-Effectiveness Indoor Air Filtration), 3.2.22 (Indoor Single Package Air-conditioners), 3.2.23 (Integrated Ventilation, Economizing, and Cooling Efficiency (IVEC)), 3.2.34 (Integrated Ventilation and Heating Efficiency (IVHE)), 3.2.29 (Non-standard Ducted Condenser Fan), 3.2.31.2 (Boost2 Heating Operating Level (B2)), 3.2.34 (Power Correction Capacitor), 3.2.35 (Powered Exhaust Air Fan), 3.2.36 (Powered Return Air Fan), 3.2.37 (Process Heat Recovery, Reclaim, or Thermal Storage Coil), 3.2.38 (Published Rating), 3.2.41 (Refrigerant Reheat Coil), 3.2.42 (Single Package Air-conditioner), 3.2.43 (Single Package Heat Pumps), 3.2.44 (Single Package System), 3.2.45 (Sound Trap), 3.2.46 (Split System), 3.2.51 (Steam or Hydronic Heat Coils), 3.2.53 (UV Lights), 3.2.55 (Ventilation Energy Recovery System (VERS)), 3.2.56 (Year Round Single Package Air-conditioner), 3.2.57 (Year Round Single Package Heat Pump),
(d) Subsection 5.2 (Optional System Features) of section 5 Test Requirements is inapplicable,
(e) The following subsections of section 6 Rating Requirements are inapplicable: 6.4 (Rating Values), 6.5 (Uncertainty), and 6.6 (Verification Testing),
(f) Section 7 Minimum Data Requirements for Published Ratings is inapplicable,
(g) Section 8 Operating Requirements is inapplicable,
(h) Section 9 Marking and Nameplate Data is inapplicable,
(i) Section 10 Conformance Conditions is inapplicable,
(j) Appendix B References—Informative is inapplicable,
(k) Sections D.1 (Purpose) and D.2 (Configuration Requirements) of Appendix D Unit Configuration for Standard Efficiency Determination—Normative are inapplicable,
(l) Appendix F International Rating Conditions—Normative is inapplicable,
(m) Appendix G Example of Determination of Fan and Motor Efficiency for Non-standard Integrated Indoor Fan and Motors—Informative is inapplicable, and
(n) Appendix H Determination of Low-temperature Cut-in and Cut-out Temperatures—Normative is inapplicable.
1.2. ANSI/ASHRAE 37-2009:
(a) Section 1 Purpose is inapplicable
(b) Section 2 Scope is inapplicable, and
(c) Section 4 Classifications is inapplicable.
2. General
For air conditioners and heat pumps, determine IVEC and IVHE (as applicable) in accordance with this appendix and the applicable sections of AHRI 1340-2023 and ANSI/ASHRAE 37-2009. Representations of energy efficiency ratio 2 (EER2) and IVHEC may optionally be made. Representations of coefficient of performance 2 (COP2) at 5 °F, 17 °F, and 47 °F may optionally be made.
Sections 3 and 4 of this appendix provide additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by AHRI 1340-2023, followed by ANSI/ASHRAE 37-2009. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
3. Test Conditions
The following conditions specified in AHRI 1340-2023 apply when testing to certify to the energy conservation standards in § 431.97. For cooling mode, use the rating conditions in Table 7 of AHRI 1340-2023. For heat pump heating mode tests, use the rating conditions in Table 23 of AHRI 1340-2023 and the IVHE building load profile in Table 22 of AHRI 1340-2023.
Representations of EER2 made using the “Cooling Bin A” conditions in Table 7 of AHRI 1340-2023 are optional. Representations of IVHEC made using the IVHEC Cold Climate building load profile in Table 22 of AHRI 1340-2023 are optional. Representations of COP247, COP217, and COP25 are optional.
4. Tower Fan and Pump Power Rate (TFPPR)
Where equations 8, 10, 11, and 13 to AHRI 1340-2023 call for using the cooling tower fan and condenser water pump power rate (TFPPR) for the cooling bin specified in Table 7 to AHRI 1340-2023, instead use the TFPPR value for the cooling bin specified in table 1 to this appendix. Where equation 22 to AHRI 1340-2023 calls for using a value of 0.0094 W/(Btu/h) for TFPPR, instead use a value of 0.0102 W/(Btu/h).
| Cooling bin | Cooling Bin A | Cooling Bin B | Cooling Bin C | Cooling Bin D |
|---|---|---|---|---|
| Tower Fan and Pump Power Rate (TFPPR), W/(Btu/h) | 0.0102 | 0.0099 | 0.0121 | 0.0430 |
5. Additional Heating Operating Level Provisions
5.1. Boost2 Heating Operating Level Definition
In place of the boost2 heating operating level definition in section 3.2.31.2 of AHRI 1340-2023, use the following definition: An operating level allowed by the controls at 5.0 °F outdoor dry-bulb temperature with a capacity at 5.0 °F outdoor dry-bulb temperature that is less than or equal to the maximum capacity allowed by the controls at 5.0 °F outdoor dry-bulb temperature and greater than the capacity of:
(a) The boost heating operating level at 5.0 °F outdoor dry-bulb temperature, if there is an operating level that meets the definition for boost heating operating level specified in section 3.2.31.1 of AHRI 1340-2023; or
(b) The high heating operating level at 5.0 °F outdoor dry-bulb temperature, if there is not an operating level that meets the definition for boost heating operating level specified in section 3.2.31.1 of AHRI 1340-2023.
5.2. Requirements for H5B2 Test in Table 23 to AHRI 1340-2023
In place of the third to last paragraph of section 6.3.6 of AHRI 1340-2023, use the following provisions.
Run the H5B2 test in Table 23 of AHRI 1340-2023 only if there is an operating level allowed by the controls at 5.0 °F that meets the definition of the boost2 heating operating level specified in section 5.1 of this appendix, and the H5B2 test is being used to determine the capacity at 5.0 °F outdoor dry-bulb temperature and/or COP25.
If the unit has a boost heating operating level, run the H5B2 test in Table 23 of AHRI 1340-2023 with an operating level allowed by the controls at 5.0 °F outdoor dry-bulb temperature that has a capacity at 5.0 °F outdoor dry-bulb temperature that is greater than the capacity of the boost heating operating level at 5.0 °F outdoor dry-bulb temperature and less than or equal to the maximum capacity allowed by the controls at 5.0 °F outdoor dry-bulb temperature.
If the unit does not have a boost heating operating level, run the H5B2 test in Table 23 of AHRI 1340-2023 with an operating level allowed by the controls at 5.0 °F outdoor dry-bulb temperature that has a capacity at 5.0 °F outdoor dry-bulb temperature that is greater than the capacity of the high heating operating level at 5.0 °F outdoor dry-bulb temperature and less than or equal to the maximum capacity allowed by the controls at 5.0 °F outdoor dry-bulb temperature. Use the indoor airflow that is used by the controls at 5.0 °F outdoor dry-bulb temperature when operating at the chosen operating level.
The H5B2 test shall not be used in the calculation of IVHE or IVHEC.
5.3. Operating Level Requirements for COP2
Any references to COP2H in AHRI 1340-2023 shall be considered synonymous with COP2 as defined in § 431.92. In place of section 6.3.14.2 of AHRI 1340-2023, use the following provisions.
To determine COP247, use capacity and power determined for the H47H test.
To determine COP217, the following provisions apply. For units without a boost heating operating level, use capacity and power determined for the H17H test. For units with a boost operating level, use capacity and power determined for the H17B test.
To determine COP25, the following provisions apply. For units without a boost heating operating level and without a boost2 heating operating level, use capacity and power determined for the H5H test. For units with a boost heating operating level and without a boost2 heating operating level, use capacity and power determined for the H5B test. For units with a boost2 heating operating level, use capacity and power determined for the H5B2 test.
6. Set-Up and Test Provisions for Specific Components
When testing equipment that includes any of the features listed in table 2 to this appendix, test in accordance with the set-up and test provisions specified in table 2.
| Component | Description | Test provisions |
|---|---|---|
| Air Economizers | An automatic system that enables a cooling system to supply outdoor air to reduce or eliminate the need for mechanical cooling during mild or cold weather | For any air economizer that is factory-installed, place the economizer in the 100% return position and close and seal the outside air dampers for testing. For any modular air economizer shipped with the unit but not factory-installed, do not install the economizer for testing. |
| Barometric Relief Dampers | An assembly with dampers and means to automatically set the damper position in a closed position and one or more open positions to allow venting directly to the outside a portion of the building air that is returning to the unit, rather than allowing it to recirculate to the indoor coil and back to the building | For any barometric relief dampers that are factory-installed, close and seal the dampers for testing. For any modular barometric relief dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Desiccant Dehumidification Components | An assembly that reduces the moisture content of the supply air through moisture transfer with solid or liquid desiccants | Disable desiccant dehumidification components for testing. |
| Drain Pan Heaters | A heater that heats the drain pan to make certain that water shed from the outdoor coil during a defrost does not freeze | Disconnect drain pan heaters for testing. |
| Evaporative Pre-cooling of Air-cooled Condenser Intake Air | Water is evaporated into the air entering the air-cooled condenser to lower the dry-bulb temperature and thereby increase efficiency of the refrigeration cycle | Disconnect the unit from a water supply for testing i.e., operate without active evaporative cooling. |
| Fire/Smoke/Isolation Dampers | A damper assembly including means to open and close the damper mounted at the supply or return duct opening of the equipment | For any fire/smoke/isolation dampers that are factory-installed, set the dampers in the fully open position for testing. For any modular fire/smoke/isolation dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Fresh Air Dampers | An assembly with dampers and means to set the damper position in a closed and one open position to allow air to be drawn into the equipment when the indoor fan is operating | For any fresh air dampers that are factory-installed, close and seal the dampers for testing. For any modular fresh air dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Hail Guards | A grille or similar structure mounted to the outside of the unit covering the outdoor coil to protect the coil from hail, flying debris and damage from large objects | Remove hail guards for testing. |
| High-Effectiveness Indoor Air Filtration | Indoor air filters with greater air filtration effectiveness than the filters used for testing | Test with the standard filter. |
| Power Correction Capacitors | A capacitor that increases the power factor measured at the line connection to the equipment | Remove power correction capacitors for testing. |
| Process Heat recovery/Reclaim Coils/Thermal Storage | A heat exchanger located inside the unit that conditions the equipment's supply air using energy transferred from an external source using a vapor, gas, or liquid | Disconnect the heat exchanger from its heat source for testing. |
| Refrigerant Reheat Coils | A heat exchanger located downstream of the indoor coil that heats the supply air during cooling operation using high pressure refrigerant in order to increase the ratio of moisture removal to cooling capacity provided by the equipment | De-activate refrigerant reheat coils for testing so as to provide the minimum (none if possible) reheat achievable by the system controls. |
| Steam/Hydronic Heat Coils | Coils used to provide supplemental heating | Test with steam/hydronic heat coils in place but providing no heat. |
| UV Lights | A lighting fixture and lamp mounted so that it shines light on the indoor coil, that emits ultraviolet light to inhibit growth of organisms on the indoor coil surfaces, the condensate drip pan, and/other locations within the equipment | Turn off UV lights for testing. |
| Ventilation Energy Recovery System (VERS) | An assembly that preconditions outdoor air entering the equipment through direct or indirect thermal and/or moisture exchange with the exhaust air, which is defined as the building air being exhausted to the outside from the equipment | For any VERS that is factory-installed, place the VERS in the 100% return position and close and seal the outside air dampers and exhaust air dampers for testing, and do not energize any VERS subcomponents (e.g., energy recovery wheel motors). For any VERS module shipped with the unit but not factory-installed, do not install the VERS for testing. |
[89 FR 44047, May 20, 2024]
Beginning July 24, 2023, representations with respect to energy use or efficiency of direct expansion-dedicated outdoor air systems must be based on testing conducted in accordance with this appendix. Manufacturers may elect to use this appendix early.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for AHRI 920-2020, AHRI 1060-2018; ANSI/ASHRAE 37-2009, ANSI/ASHRAE 41.1-2013, ANSI/ASHRAE 41.6-2014, and ANSI/ASHRAE 198-2013. However, only enumerated provisions of AHRI 920-2020, ANSI/ASHRAE 37-2009, ANSI/ASHRAE 41.6-2014, and ANSI/ASHRAE 198-2013, as listed in this section 1 are required. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1. AHRI 920-2020
(a) Section 3—Definitions, as specified in section 2.2.1(a) of this appendix;
(b) Section 5—Test Requirements, as specified in section 2.2.1(b) of this appendix;
(c) Section 6—Rating Requirements, as specified in section 2.2.1(c) of this appendix, omitting section 6.1.2 (but retaining sections 6.1.2.1-6.1.2.8) and 6.6.1;
(d) Section 11—Symbols and Subscripts, as specified in section 2.2.1(d) of this appendix;
(e) Appendix A—References—Normative, as specified in section 2.2.1(e) of this appendix; and
(f) Appendix C—ANSI/ASHRAE Standard 198 and ANSI/ASHRAE Standard 37 Additions, Clarifications and Exceptions—Normative, as specified in section 2.2.1(f) of this appendix.
1.2. ANSI/ASHRAE 37-2009
(a) Section 5.1—Temperature Measuring Instruments (excluding sections 5.1.1 and 5.1.2), as specified in sections 2.2.1(b) and (f) of this appendix;
(b) Section 5.2—Refrigerant, Liquid, and Barometric Pressure Measuring Instruments, as specified in section 2.2.1(b) of this appendix;
(c) Sections 5.3—Air Differential Pressure and Airflow Measurements, as specified in section 2.2.1(b) of this appendix;
(d) Sections 5.5(b)—Volatile Refrigerant Measurement, as specified in section 2.2.1(b) of this appendix;
(e) Section 6.1—Enthalpy Apparatus (excluding 6.1.1 and 6.1.3 through 6.1.6), as specified in section 2.2.1(b) of this appendix;
(f) Section 6.2—Nozzle Airflow Measuring Apparatus, as specified in section 2.2.1(b) of this appendix;
(g) Section 6.3—Nozzles, as specified in section 2.2.1(b) of this appendix;
(h) Section 6.4—External Static Pressure Measurements, as specified in section 2.2.1(b) of this appendix;
(i) Section 6.5—Recommended Practices for Static Pressure Measurements, as specified in section 2.2.1(f) of this appendix;
(j) Section 7.3—Indoor and Outdoor Air Enthalpy Methods, as specified in section 2.2.1(f) of this appendix;
(k) Section 7.4—Compressor Calibration Method, as specified in section 2.2.1(f) of this appendix;
(l) Section 7.5—Refrigerant Enthalpy Method, as specified in section 2.2.1(f) of this appendix;
(m) Section 7.6—Outdoor Liquid Coil Method, as specified in section 2.2.1(f) of this appendix;
(n) Section 7.7—Airflow Rate Measurement (excluding sections 7.7.1.2, 7.7.3, and 7.7.4), as specified in section 2.2.1(b) of this appendix;
(o) Table 1—Applicable Test Methods, as specified in section 2.2.1(f) of this appendix;
(p) Section 8.6—Additional Requirements for the Outdoor Air Enthalpy Method, as specified in section 2.2.1(f) of this appendix;
(q) Table 2b—Test Tolerances (I-P Units), as specified in sections 2.2.1(c) and 2.2(f) of this appendix; and
(r) Errata sheet issued on October 3, 2016, as specified in section 2.2.1(f) of this appendix.
1.3. ANSI/ASHRAE 41.6-2014
(a) Section 4—Classifications, as specified in section 2.2.1(f) of this appendix;
(b) Section 5—Requirements, as specified in section 2.2.1(f) of this appendix;
(c) Section 6—Instruments and Calibration, as specified in section 2.2.1(f) of this appendix;
(d) Section 7.1—Standard Method Using the Cooled-Surface Condensation Hygrometer as specified in section 2.2.1(f) of this appendix; and
(e) Section 7.4—Electronic and Other Humidity Instruments. As specified in section 2.2.1(f) of this appendix.
1.4. ANSI/ASHRAE 198-2013
(a) Section 4.4—Temperature Measuring Instrument, as specified in section 2.2.1(b) of this appendix;
(b) Section 4.5—Electrical Instruments, as specified in section 2.2.1(b) of this appendix;
(c) Section 4.6—Liquid Flow Measurement, as specified in section 2.2.1(b) of this appendix;
(d) Section 4.7—Time and Mass Measurements, as specified in section 2.2.1(b) of this appendix;
(e) Section 6.1—Test Room Requirements, as specified in section 2.2.1(b) of this appendix;
(f) Section 6.6—Unit Preparation, as specified in section 2.2.1(b) of this appendix;
(g) Section 7.1—Preparation of the Test Room(s), as specified in section 2.2.1(b) of this appendix;
(h) Section 7.2—Equipment Installation, as specified in section 2.2.1(b) of this appendix;
(i) Section 8.2—Equilibrium, as specified in section 2.2.1(b) of this appendix; and
(j) Section 8.4—Test Duration and Measurement Frequency, as specified in section 2.2.1(b) of this appendix.
2. Test Method
2.1. Capacity
Moisture removal capacity (in pounds per hour) and supply airflow rate (in standard cubic feet per minute) are determined according to AHRI 920-2020 as specified in section 2.2 of this appendix.
2.2. Efficiency
2.2.1. Determine the ISMRE2 for all DX-DOASes and the ISCOP2 for all heat pump DX-DOASes in accordance with the following sections of AHRI 920-2020 and the additional provisions described in this section.
(a) Section 3—Definitions, including the references to AHRI 1060-2018;
(i) Non-standard Low-static Fan Motor. A supply fan motor that cannot maintain external static pressure as high as specified in Table 7 of AHRI 920-2020 when operating at a manufacturer-specified airflow rate and that is distributed in commerce as part of an individual model within the same basic model of a DX-DOAS that is distributed in commerce with a different motor specified for testing that can maintain the required external static pressure.
(ii) Manufacturer-specified. Information provided by the manufacturer through manufacturer's installation instructions, as defined in Section 3.14 of AHRI 920-2020.
(iii) Reserved
(b) Section 5—Test Requirements, including the references to Sections 5.1, 5.2, 5.3, 5.5, 6.1, 6.2, 6.3, 6.4, and 7.7 (not including Sections 7.7.1.2, 7.7.3, and 7.7.4) of ANSI/ASHRAE 37-2009, and Sections 4.4, 4.5, 4.6, 4.7, 5.1, 6.1, 6.6, 7.1, 7.2, 8.2, and 8.4 of ANSI/ASHRAE 198-2013;
(i) All control settings are to remain unchanged for all Standard Rating Conditions once system set up has been completed, except as explicitly allowed or required by AHRI 920-2020 or as indicated in the supplementary test instructions (STI). Component operation shall be controlled by the unit under test once the provisions in section 2.2.1(c) of this appendix are met.
(ii) Break-in. The break-in conditions and duration specified in section 5.6 of AHRI 920-2020 shall be manufacturer-specified values.
(iii) Reserved
(c) Section 6—Rating Requirements (omitting sections 6.1.2 and 6.6.1), including the references to Table 2b of ANSI/ASHRAE 37-2009, and ANSI/ASHRAE 198-2013.
(i) For water-cooled DX-DOASes, the “Condenser Water Entering Temperature, Cooling Tower Water” conditions specified in Table 4 of AHRI 920-2020 shall be used. For water-source heat pump DX-DOASes, the “Water-Source Heat Pumps” conditions specified in Table 5 of AHRI 920-2020 shall be used.
(ii) For water-cooled or water-source DX- DOASes with integral pumps, set the external head pressure to 20 ft. of water column, with a −0/+1 ft. condition tolerance and a 1 ft. operating tolerance.
(iii) When using the degradation coefficient method as specified in Section 6.9.2 of AHRI 920-2020, Equation 20 applies to DX- DOAS without VERS, with deactivated VERS (see Section 5.4.3 of AHRI 920-2020), or sensible-only VERS tested under Standard Rating Conditions other than D.
(iv) Rounding requirements for representations are to be followed as stated in Sections 6.1.2.1 through 6.1.2.8 of AHRI 920-2020;
(d) Section 11—Symbols and Subscripts, including references to AHRI 1060-2018;
(e) Appendix A—References—Normative;
(f) Appendix C—ANSI/ASHRAE 198-2013 and ANSI/ASHRAE 37 Additions, Clarifications and Exceptions—Normative, including references to Sections 5.1, 6.5, 7.3, 7.4, 7.5, 7.6, 8.6, Table 1, Table 2b, and the errata sheet of ANSI/ASHRAE 37-2009, ANSI/ASHRAE 41.1-2013, Sections 4, 5, 6, 7.1, and 7.4 of ANSI/ASHRAE 41.6-2014, and AHRI 1060-2018;
(g) Appendix E—Typical Test Unit Installations—Informative, for information only.
2.2.2. Set-Up and Test Provisions for Specific Components. When testing a DX-DOAS that includes any of the features listed in Table 2.1 of this section, test in accordance with the set-up and test provisions specified in Table 2.1 of this section.
| Component | Description | Test provisions |
|---|---|---|
| Return and Exhaust Dampers | An automatic system that enables a DX-DOAS Unit to supply and use some return air (even if an optional VERS is not utilized) to reduce or eliminate the need for mechanical dehumidification or heating when ventilation air requirements are less than design | All dampers that allow return air to pass into the supply airstream shall be closed and sealed. Exhaust air dampers of DOAS units with VERS shall be open. Gravity dampers activated by exhaust fan discharge airflow shall be allowed to open by action of the exhaust airflow. |
| VERS Bypass Dampers | An automatic system that enables a DX-DOAS Unit to let outdoor ventilation air and return air bypass the VERS when preconditioning of outdoor ventilation is not beneficial | Test with the VERS bypass dampers installed, closed, and sealed. However, VERS bypass dampers may be opened if necessary for testing with deactivated VERS for Standard Rating Condition D. |
| Fire/Smoke/Isolation Dampers | A damper assembly including means to open and close the damper mounted at the supply or return duct opening of the equipment | The fire/smoke/isolation dampers shall be removed for testing. If it is not possible to remove such a damper, test with the damper fully open. For any fire/smoke/isolation dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Furnaces and Steam/Hydronic Heat Coils | Furnaces and steam/hydronic heat coils used to provide primary or supplementary heating | Test with the coils in place but providing no heat. |
| Power Correction Capacitors | A capacitor that increases the power factor measured at the line connection to the equipment. These devices are a requirement of the power distribution system supplying the unit | Remove power correction capacitors for testing. |
| Hail Guards | A grille or similar structure mounted to the outside of the unit covering the outdoor coil to protect the coil from hail, flying debris and damage from large objects | Remove hail guards for testing. |
| Ducted Condenser Fans | A condenser fan/motor assembly designed for optional external ducting of condenser air that provides greater pressure rise and has a higher rated motor horsepower than the condenser fan provided as a standard component with the equipment | Test with the ducted condenser fan installed and operating using zero external static pressure, unless the manufacturer specifies use of an external static pressure greater. than zero, in which case, use the manufacturer-specified external static pressure. |
| Sound Traps/Sound Attenuators | An assembly of structures through which the supply air passes before leaving the equipment or through which the return air from the building passes immediately after entering the equipment for which the sound insertion loss is at least 6 dB for the 125 Hz octave band frequency range | Removable sound traps/sound attenuators shall be removed for testing. Otherwise, test with sound traps/attenuators in place. |
| Humidifiers | A device placed in the supply air stream for moisture evaporation and distribution. The device may require building steam or water, hot water, electric or gas to operate | Remove humidifiers for testing. |
| UV Lights | A lighting fixture and lamp mounted so that it shines light on the conditioning coil, that emits ultraviolet light to inhibit growth of organisms on the conditioning coil surfaces, the condensate drip pan, and/other locations within the equipment | Remove UV lights for testing. |
| High-Effectiveness Indoor Air Filtration | Indoor air filters with greater air filtration effectiveness than MERV 8 or the lowest MERV filter distributed in commerce, whichever is greater | Test with a MERV 8 filter or the lowest MERV filter distributed in commerce, whichever is greater |
2.2.3. Optional Representations. Test provisions for the determination of the metrics indicated in paragraphs (a) through (d) of this section are optional and are determined according to the applicable provisions in section 2.2.1 of this appendix. The following metrics in AHRI 920-2020 are optional:
(a) ISMRE270;
(b) COPFull,x:
(c) COPDOAS,x: and
(d) ISMRE2 and ISCOP2 for water-cooled DX-DOASes using the “Condenser Water Entering Temperature, Chilled Water” conditions specified in Table 4 of AHRI 920-2020 and for water-source heat pump DX-DOASes using the “Water-Source Heat Pump, Ground-Source Closed Loop” conditions specified in Table 5 of AHRI 920-2020.
2.3 Synonymous Terms
(a) Any references to energy recovery or energy recovery ventilator (ERV) in AHRI 920-2020 and ANSI/ASHRAE 198-2013 shall be considered synonymous with ventilation energy recovery system (VERS) as defined in § 431.92.
(b) Reserved
[87 FR 45199, July 27, 2022]
Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standard at § 431.97 as that standard appeared in the January 1, 2023 edition of 10 CFR parts 200-499. Specifically, representations must be based on testing according to either this appendix or 10 CFR 431.96 as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2023.
Starting on November 29, 2024, voluntary representations with respect to energy use or efficiency of water-source heat pumps with cooling capacity greater than or equal to 135,000 Btu/h and less than 760,000 Btu/h must be based on testing according to this appendix. Manufacturers may also use this appendix to make voluntary representations with respect to energy use or efficiency prior to November 29, 2024.
Starting on November 29, 2024, voluntary representations with respect to the integrated energy efficiency ratio (IEER) and applied coefficient of performance (ACOP) of water-source heat pumps must be based on testing according to appendix C1 of this subpart. Manufacturers may also use appendix C1 to make voluntary representations with respect to IEER and ACOP prior to November 29, 2024.
Starting on the compliance date for any amended energy conservation standards for water-source heat pumps based on IEER and ACOP, any representations, including compliance certifications, made with respect to the energy use or energy efficiency of water-source heat pumps must be based on testing according to appendix C1 of this subpart.
Manufacturers may also certify compliance with any amended energy conservation standards for water-source heat pumps based on IEER and ACOP prior to the applicable compliance date for those standards, and those compliance certifications must be based on testing according to appendix C1 of this subpart.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for ISO 13256-1:1998. To the extent there is a conflict between the terms or provisions of a referenced industry standard and this appendix, the appendix provisions control.
2. General
Determine the energy efficiency ratio (EER) and coefficient of performance (COP) in accordance with ISO 13256-1:1998.
Section 3 of this appendix provides additional instructions for determining EER and COP.
3. Additional Provisions for Equipment Set-Up
The only additional specifications that may be used in setting up the basic model for testing are those set forth in the installation and operation manual shipped with the unit. Each unit should be set up for test in accordance with the manufacturer installation and operation manuals. Sections 3.1 through 3.2 of this appendix provide specifications for addressing key information typically found in the installation and operation manuals.
3.1. If a manufacturer specifies a range of superheat, sub-cooling, and/or refrigerant pressure in its installation and operation manual for a given basic model, any value(s) within that range may be used to determine refrigerant charge or mass of refrigerant, unless the manufacturer clearly specifies a rating value in its installation and operation manual, in which case the specified rating value must be used.
3.2. The airflow rate used for testing must be that set forth in the installation and operation manuals being shipped to the commercial customer with the basic model and clearly identified as that used to generate the DOE performance ratings. If a rated airflow value for testing is not clearly identified, a value of 400 standard cubic feet per minute (scfm) per ton must be used.
[88 FR 84230, Dec. 4, 2023]
Prior to the compliance date of amended standards for water-source heat pumps that rely on integrated energy efficiency ratio (IEER) and applied coefficient of performance (ACOP) published after January 1, 2023, representations with respect to the energy use or energy efficiency of water-source heat pumps, including compliance certifications, must be based on testing according to appendix C of this subpart.
Starting on November 29, 2024, voluntary representations with respect to the IEER and ACOP of water-source heat pumps must be based on testing according to this appendix. Manufacturers may also use this appendix to make voluntary representations with respect to IEER and ACOP prior to November 29, 2024.
Starting on the compliance date for any amended energy conservation standards for water-source heat pumps based on IEER and ACOP, any representations, including compliance certifications, made with respect to the energy use or energy efficiency of water-source heat pumps must be based on testing according to this appendix.
Manufacturers may also certify compliance with any amended energy conservation standards for water-source heat pumps based on IEER and ACOP prior to the applicable compliance date for those standards, and those compliance certifications must be based on testing according to this appendix.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95 the entire standards for AHRI 600-2023, ANSI/ASHRAE 37-2009 (as corrected by the Errata sheet for ANSI/ASHRAE 37-2009), and Melinder 2010. However, certain enumerated provisions of AHRI 600-2023 and ASHRAE 37-2009, as listed in this section 1, are inapplicable.
To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1. AHRI 600-2023
(a) Section 1 Purpose is inapplicable,
(b) Section 2 Scope is inapplicable,
(c) The following subsections of section 3 Definitions are inapplicable:
(1) 3.2.1 (Air Economizer),
(2) 3.2.3 (Barometric Relief Dampers),
(3) 3.2.4 (Basic Model),
(4) 3.2.5 (Coated Coils),
(5) 3.2.6 (Coefficients of Performance),
(6) 3.2.9 (Condenser Pump/Valves/Fittings),
(7) 3.2.10 (Condenser Water Reheat),
(8) 3.2.13 (Desiccant Dehumidification Components),
(9) 3.2.14 (Desuperheater),
(10) 3.2.15.1 (Energy Efficiency Ratio),
(11) 3.2.16 (Evaporative Cooling of Ventilation Air),
(12) 3.2.17 (Fire/Smoke/Isolation Dampers),
(13) 3.2.19 (Fresh Air Dampers),
(14) 3.2.21 (Grill Options),
(15) 3.2.23 (High-effectiveness Indoor Air Filtration),
(16) 3.2.24 (Hot Gas Bypass),
(17) 3.2.27 (Integrated Energy Efficiency Ratio),
(18) 3.2.28 (Low-static Heat Pump),
(19) 3.2.35 (Power Correction Capacitors),
(20) 3.2.36 (Powered Exhaust Air Fan),
(21) 3.2.37 (Powered Return Air Fan),
(22) 3.2.38 (Process Heat Recovery/Reclaim Coils/Thermal Storage),
(23) 3.2.40 (Published Rating),
(24) 3.2.42 (Refrigerant Reheat Coils),
(25) 3.2.43 (Single Package Heat Pumps),
(26) 3.2.44 (Sound Traps/Sound Attenuators),
(27) 3.2.45 (Split System Heat Pump),
(28) 3.2.51 (Steam/Hydronic Heat Coils),
(29) 3.2.53 (UV Lights),
(30) 3.2.54 (Ventilation Energy Recovery System),
(31) 3.2.55 (Water/Brine to Air Heat Pump Equipment), and
(32) 3.2.56 (Waterside Economizer),
(d) The following subsections of section 6 Rating Requirements are inapplicable:
(1) 6.5 (Residential Cooling Capacity and Efficiency),
(2) 6.6 (Residential Heating Capacity and Efficiency),
(3) 6.7 (Test Data vs Computer Simulation),
(4) 6.8 (Rounding and Precision),
(5) 6.9 (Uncertainty), and
(6) 6.10 (Verification Testing),
(e) Section 7 Minimum Data Requirements for Published Ratings is inapplicable
(f) Section 8 Operating Requirements is inapplicable,
(g) Section 9 Marking and Nameplate Data is inapplicable,
(h) Section 10 Conformance Conditions is inapplicable,
(i) Appendix B References—Informative is inapplicable,
(j) Sections D.1 (Purpose), D.2 (Configuration Requirements), and D.3 (Optional System Features) of Appendix D Unit Configuration For Standard Efficiency Determination—Normative are inapplicable, and
(k) Appendix F Example of Determination of Fan and Motor Efficiency for Non-standard Integrated Indoor Fan and Motors—Informative is inapplicable.
1.2. ANSI/ASHRAE 37-2009 (Even if Corrected by the Errata Sheet)
(a) Section 1 Purpose is inapplicable.
(b) Section 2 Scope is inapplicable.
(c) Section 4 Classification is inapplicable.
2. General
Determine integrated energy efficiency ratio (IEER) and heating applied coefficient of performance (ACOP) in accordance with this appendix and the applicable sections of AHRI 600-2023, ANSI/ASHRAE 37-2009, and Melinder 2010. Representations of AEER, EER, and COP may optionally be made.
Section 3 of this appendix provides additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by AHRI 600-2023, followed by ANSI/ASHRAE 37-2009. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE. Material is incorporated as it exists on the date of the approval, and a notification of any change in the incorporation must be published in the Federal Register.
3. Setup and Test Provisions for Specific Components
When testing a water-source heat pump that includes any of the features listed in table 1 to this appendix, test in accordance with the setup and test provisions specified in table 1 to this appendix.
| Component | Description | Setup and test provisions |
|---|---|---|
| Air Economizers | An automatic system that enables a cooling system to supply outdoor air to reduce or eliminate the need for mechanical cooling during mild or cold weather | For any air economizer that is factory-installed, place the economizer in the 100 percent return position and close and seal the outside air dampers for testing. For any modular air economizer shipped with the unit but not factory-installed, do not install the economizer for testing. |
| Barometric Relief Dampers | An assembly with dampers and means to automatically set the damper position in a closed position and one or more open positions to allow venting directly to the outside a portion of the building air that is returning to the unit, rather than allowing it to recirculate to the indoor coil and back to the building | For any barometric relief dampers that are factory-installed, close and seal the dampers for testing. For any modular barometric relief dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Desiccant Dehumidification Components | An assembly that reduces the moisture content of the supply air through moisture transfer with solid or liquid desiccants | Disable desiccant dehumidification components for testing. |
| Fire/Smoke/Isolation Dampers | A damper assembly including means to open and close the damper mounted at the supply or return duct opening of the equipment | For any fire/smoke/isolation dampers that are factory-installed, set the dampers in the fully open position for testing. For any modular fire/smoke/isolation dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Fresh Air Dampers | An assembly with dampers and means to set the damper position in a closed and one open position to allow air to be drawn into the equipment when the indoor fan is operating | For any fresh air dampers that are factory-installed, close and seal the dampers for testing. For any modular fresh air dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Power Correction Capacitors | A capacitor that increases the power factor measured at the line connection to the equipment | Remove power correction capacitors for testing. |
| Process Heat recovery/Reclaim Coils/Thermal Storage | A heat exchanger located inside the unit that conditions the equipment's supply air using energy transferred from an external source using a vapor, gas, or liquid | Disconnect the heat exchanger from its heat source for testing. |
| Refrigerant Reheat Coils | A heat exchanger located downstream of the indoor coil that heats the supply air during cooling operation using high-pressure refrigerant in order to increase the ratio of moisture removal to cooling capacity provided by the equipment | De-activate refrigerant reheat coils for testing so as to provide the minimum (none if possible) reheat achievable by the system controls. |
| Steam/Hydronic Heat Coils | Coils used to provide supplemental heating | Test with steam/hydronic heat coils in place but providing no heat. |
| UV Lights | A lighting fixture and lamp mounted so that it shines light on the indoor coil, that emits ultraviolet light to inhibit growth of organisms on the indoor coil surfaces, the condensate drip pan, and/other locations within the equipment | Turn off UV lights for testing. |
| Ventilation Energy Recovery System (VERS) | An assembly that preconditions outdoor air entering the equipment through direct or indirect thermal and/or moisture exchange with the exhaust air, which is defined as the building air being exhausted to the outside from the equipment | For any VERS that is factory-installed, place the VERS in the 100 percent return position and close and seal the outside air dampers and exhaust air dampers for testing, and do not energize any VERS subcomponents (e.g., energy recovery wheel motors). For any VERS module shipped with the unit but not factory-installed, do not install the VERS for testing. |
[88 FR 84230, Dec. 4, 2023]
Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standard from § 431.97 as that standard appeared in the January 1, 2022 edition of 10 CFR parts 200-499. Specifically, representations must be based upon results generated either under this appendix or under 10 CFR 431.96 as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2022.
For any amended standards for variable refrigerant flow multi-split air conditioners and heat pumps that rely on integrated energy efficiency ratio (IEER) published after January 1, 2022, manufacturers must use the results of testing under appendix D1 of this subpart to determine compliance. Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., appendix D or appendix D1) when determining compliance with the relevant standard.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for ANSI/AHRI 1230-2010. However, enumerated provisions of ANSI/AHRI 1230-2010, as listed in this section 1, are excluded. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 ANSI/AHRI 1230-2010:
(a) Section 5.1.2—Manufacturer involvement.
(b) Section 6.6—Verification testing and uncertainty is inapplicable as specified in section 2.2 of this appendix.
1.2 [Reserved.]
2. General. Determine the energy efficiency ratio (EER) and coefficient of performance (COP) (as applicable) in accordance with ANSI/AHRI 1230-2010.
Sections 3 through 6 of this appendix provide additional instructions for determining EER and COP.
3. Optional break-in period. Manufacturers may optionally specify a “break-in” period, not to exceed 20 hours, to operate the equipment under test prior to conducting the test method specified in this appendix. A manufacturer who elects to use an optional compressor break-in period in its certification testing should record this period's duration as part of the information in the supplemental testing instructions under 10 CFR 429.43.
4. Refrigerant line length corrections. For test set-ups where it is physically impossible for the laboratory to use the required line length listed in Table 3 of the ANSI/AHRI 1230-2010, then the actual refrigerant line length used by the laboratory may exceed the required length and the following cooling capacity correction factors are applied:
| Piping length beyond minimum, X
(ft) |
Piping length beyond minimum, Y
(m) |
Cooling capacity correction
(%) |
|---|---|---|
| 0> X ≤20 | 0> Y ≤6.1 | 1 |
| 20> X ≤40 | 6.1> Y ≤12.2 | 2 |
| 40> X ≤60 | 12.2> Y ≤18.3 | 3 |
| 60> X ≤80 | 18.3> Y ≤24.4 | 4 |
| 80> X ≤100 | 24.4> Y ≤30.5 | 5 |
| 100> X ≤120 | 30.5>Y ≤36.6 | 6 |
5. Additional provisions for equipment set-up. The only additional specifications that may be used in setting up the basic model for test are those set forth in the installation and operation manual shipped with the unit. Each unit should be set up for test in accordance with the manufacturer installation and operation manuals. Sections 5.1 through 5.3 of this appendix provide specifications for addressing key information typically found in the installation and operation manuals.
5.1. If a manufacturer specifies a range of superheat, sub-cooling, and/or refrigerant pressure in its installation and operation manual for a given basic model, any value(s) within that range may be used to determine refrigerant charge or mass of refrigerant, unless the manufacturer clearly specifies a rating value in its installation and operation manual, in which case the specified rating value must be used.
5.2. The airflow rate used for testing must be that set forth in the installation and operation manual being shipped to the commercial customer with the basic model and clearly identified as that used to generate the DOE performance ratings. If a rated airflow value for testing is not clearly identified, a value of 400 standard cubic feet per minute (scfm) per ton must be used.
5.3. The test set-up and the fixed compressor speeds (i.e., the maximum, minimum, and any intermediate speeds used for testing) should be recorded and maintained as part of the test data underlying the certified ratings that is required to be maintained under 10 CFR 429.71.
6. Manufacturer involvement in assessment or enforcement testing. A manufacturer's representative will be allowed to witness assessment and/or enforcement testing for variable refrigerant flow multi-split air conditioners and heat pumps. The manufacturer's representative will be allowed to inspect and discuss set-up only with a DOE representative. During testing, the manufacturer's representative may adjust only the modulating components that are necessary to achieve steady-state operation in the presence of a DOE representative. Only previously documented specifications for set-up as specified under sections 4 and 5 of this appendix will be used.
[87 FR 63898, Oct. 20, 2022]
Manufacturers must use the results of testing under this appendix to determine compliance with any amended standards for variable refrigerant flow multi-split air conditioners and heat pumps provided in § 431.97 that are published after January 1, 2022, and that rely on integrated energy efficiency ratio (IEER). Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., appendix D or appendix D1) when determining compliance with the relevant standard.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for AHRI 1230-2021 and ANSI/ASHRAE 37-2009, as corrected by the Errata sheet for ANSI/ASHRAE 37-2009 issued on March 27, 2019 (“ANSI/ASHRAE 37-2009 (as corrected)”). However, only enumerated provisions of AHRI 1230-2021 and ANSI/ASHRAE 37-2009 are required or excluded, as listed in this section 1. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 Provisions Required
1.1.1 AHRI 1230-2021
(a) Section 3—Definitions, except section 3.11, as specified in section 2 of this appendix,
(b) Section 5—Test Requirements, except section 5.1.2, as specified in sections 2 and 5.1 of this appendix,
(c) Section 6—Rating Requirements, except sections 6.3.3 and 6.5, as specified in sections 2, 4.1, 4.1.1, 4.2, 4.2.1, and 5.1 of this appendix,
(d) Section 11—Calculations is applicable as specified in sections 2, 5.2.1.2, and 5.2.2 of this appendix,
(e) Section 12—Symbols, Subscripts, and Superscripts as specified in section 2 of this appendix,
(f) Appendix E—ANSI/ASHRAE Standard 37-2009 Clarifications/Exceptions—Normative as specified in section 2 of this appendix.
1.1.2 [Reserved]
1.2 Provisions Excluded
1.2.1 ANSI/ASHRAE 37-2009 (as Corrected)
(a) Section 1—Purpose,
(b) Section 2—Scope, and
(c) Section 4—Classification.
2. General. Determine IEER and coefficient of performance (COP) (as applicable) in accordance with AHRI 1230-2021 and ANSI/ASHRAE 37-2009 (as corrected). Sections 3 through 5 of this appendix provide additional instructions for determining IEER and COP. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by AHRI 1230-2021, followed by ANSI/ASHRAE 37-2009 (as corrected).
The controls verification procedure specified in Appendix C of AHRI 1230-2021 is referenced as part of DOE's certification provisions at § 429.43(b) and product-specific enforcement provisions located at § 429.134(v)(3).
3. Definitions
3.1. Critical Parameter(s) are the following settings of modulating components of variable refrigerant flow multi-split air conditioners and heat pumps: compressor speed(s), outdoor fan speed(s), and outdoor variable valve position(s).
4. Test Conditions
4.1 Test Conditions for Air-Cooled VRF Multi-split Systems with Rated Cooling Capacity Greater Than 65,000 Btu/h. When testing to certify to the energy conservation standards in § 431.97, test using the “Standard Rating Conditions, Cooling” and “Standard Rating Part-Load Conditions (IEER)” conditions for cooling mode tests and “Standard Rating Conditions (High Temperature Steady-state Test for Heating)” conditions for heat pump heating mode tests, as specified in Table 9 in Section 6 of AHRI 1230-2021.
4.1.1 Representations of COP for air-cooled VRF multi-split systems with rated cooling capacity greater than 65,000 Btu/h made using the “Low Temperature Operation, Heating” condition specified in Table 9 in Section 6 of AHRI 1230-2021 are optional.
4.2 Test Conditions for Water-source VRF Multi-split Systems. When testing to certify to the energy conservation standards in § 431.97, test using the “Part-load Conditions (IEER)” conditions specified for “Water Loop Heat Pumps” in Table 10 of AHRI 1230-2021 for cooling mode tests and the “Standard Rating Test” conditions specified for “Water Loop Heat Pumps” in Table 11 in Section 6 of AHRI 1230-2021 for heat pump heating mode tests.
4.2.1 For water-source VRF multi-split systems, representations of EER made using the “Standard Rating Test” conditions specified for “Ground-loop Heat pumps” in Table 10 of Section 6 of AHRI 1230-2021 and representations of COP made using the “Standard Rating Test” conditions specified for “Ground-loop Heat Pumps” in Table 11 of Section 6 of AHRI 1230-2021 are optional.
5. Test Procedure
5.1 Control Settings. Control settings must be set in accordance with Sections 5.1.3, 5.1.4, 5.1.5, and 5.2 of AHRI 1230-2021. For systems equipped with head pressure controls, the head pressure controls must be set per manufacturer installation instructions or per factory settings if no instructions are provided. Indoor airflow-control settings must be set in accordance with Section 6.3.1 of AHRI 1230-2021. At each load point, critical parameters must be set to the values certified in the supplemental testing instructions (STI) provided by the manufacturer pursuant to § 429.43(b)(4) of this chapter. In cases in which a certified critical parameter value is not in the STI, the system must operate per commands from the system controls for that parameter. Once set, control settings must remain unchanged for the remainder of the test (except for allowable adjustment of critical parameters as described in section 5.2 of this appendix).
5.2 Allowable Critical Parameter Adjustments for IEER Cooling Tests. The following sections describe allowable adjustments to critical parameters after the initial system set-up (during which all control settings, including certified critical parameters, are set). Adjust critical parameters in order to achieve full- and part-load cooling capacity targets and sensible heat ratio (SHR) limits.
5.2.1 Critical Parameter Adjustments for Meeting Cooling Capacity Targets. Once critical parameters have been set to the values certified in the STI, if the unit cannot operate within 3% of the target cooling capacity (i.e., within 3% of the load fraction for a given part-load cooling test (75%, 50%, or 25% load) or within 3% of the certified cooling capacity for a 100% full-load cooling test), manually-controlled critical parameters must be adjusted according to the following provisions:
5.2.1.1. Cooling Capacity is Below Lower Tolerance. If, for any test, the cooling capacity operates below the lower tolerance for the target cooling capacity, increase the compressor speed(s) beyond the STI-certified value(s) until the cooling capacity operates within 3% of the target cooling capacity. If multiple compressors are present in the system, increase compressor speed by the same absolute increment in RPM or Hz for each compressor for which the following conditions apply:
(a) The STI specifies a non-zero compressor speed for the compressor for that test and
(b) The compressor has not yet reached its maximum capable operating speed. The compressor speed(s) must not be less than the STI-certified value(s) at any point during the test. Upward adjustments to compressor speed are not constrained by a budget on RSS Points Total (See section 5.2.1.2.1 of this appendix).
5.2.1.2 Cooling Capacity is Above Upper Tolerance. If, for any test, the cooling capacity operates above the upper tolerance for the target cooling capacity, adjust any manually-controlled critical parameters per the STI. If the STI does not include a hierarchy of instructions for adjustment of critical parameters to reduce cooling capacity during IEER cooling tests, then reduce only the compressor speed(s) to reduce cooling capacity. If multiple compressors are present in the system, decrease compressor speed by the same absolute increment for each compressor for which the following conditions apply:
(a) The STI specifies a non-zero compressor speed for the compressor for that test and
(b) The compressor has not yet reached minimum speed. Continue reducing cooling capacity in this manner until one of the following occurs:
(1) The unit operates within 3% of the target cooling capacity; or
(2) The RSS point total reaches a budget of 70 points (see section 5.2.1.2.1 of this appendix). For the 75%, 50%, and 25% part-load cooling test points, if the RSS point total reaches 70 during critical parameter adjustments before the capacity operates within 3% of the target cooling capacity, stop adjustment and follow cyclic degradation procedures in accordance with Section 11.2.2.1 of AHRI 1230-2021.
5.2.1.2.1 Measuring Critical Parameter Variation During Adjustment Period. When adjusting critical parameters to reduce cooling capacity, critical parameter variation must be calculated each time the critical parameters are adjusted, using the following equations:
(a) First, use equation 5.2-1 to calculate the absolute parameter percent difference () between each adjusted critical parameter and the value for that parameter certified in the STI.
Where:
“i” identifies the critical parameter—either compressors speed(s), outdoor fan speed(s), or outdoor variable valve position(s)
CPi ,Adj = The adjusted position of critical parameter “i” recorded at each measurement interval. If multiple components corresponding to a single parameter are present (e.g., multiple compressors), calculate the average position across all components corresponding to that parameter at each measurement interval when determining CPi,Adj.
CPi ,STI = The position of critical parameter “i” as certified in the STI. If multiple components corresponding to a single parameter are present, calculate the average position across all components corresponding to that parameter at each measurement interval when determining CPi,STI.
CPMax = The maximum operating position for Critical Parameter “i” as certified in the STI for the 100% load condition. If multiple components corresponding to a single parameter are present, calculate as the average value across all components corresponding to that critical parameter certified in the STI for the 100% load condition.
(b) Next, use equation 5.2-2 to this section to determine the accrued points for each critical parameter:
Where:
“i” identifies the critical parameter—either compressors speed(s), outdoor fan speed(s), or outdoor variable valve position(s)
NPVi = the nominal point value for critical parameter “i” as follows:
| Critical parameter | Nominal point value |
|---|---|
| Compressor Speed(s) | 13 |
| Outdoor Fan Speed(s) | 7 |
| Outdoor Variable Valve Position(s) | 1 |
(c) Finally, use equation 5.2-3 to this section to calculate the root-sum-squared (RSS) Points Total across all critical parameters.
5.2.2 Critical Parameter Adjustments for Meeting SHR Limits. The SHR for the 100% load test point and the 75% part-load test point must not be higher than 0.82 and 0.85, respectively (measured to the nearest hundredth). If the SHR is above the allowable limit, increase the compressor speed(s) until either the SHR is less than or equal to the allowable limit or the cooling capacity reaches 3% greater than the target cooling capacity for that test, whichever happens first. If multiple compressors are present in the system, increase compressor speed by the same absolute increment for each compressor for which the following conditions apply:
(a) The STI specifies a non-zero compressor speed for the compressor for that test and
(b) The compressor has not yet reached maximum speed. Upwards adjustments to compressor speed are not constrained by a budget on RSS Points Total. Should the SHR remain above the maximum limit when the cooling capacity reaches its upper 3% tolerance, no further compressor adjustments shall be made, and the calculation procedures specified in Section 11.2.2.2 of AHRI 1230-2021 must be applied using the adjusted SHR value obtained after increasing the compressor speed(s).
6. Set-Up and Test Provisions for Specific Components. When testing a VRF multi-split system that includes any of the specific components listed in table 6.1 to this appendix, test in accordance with the set-up and test provisions specified in table 6.1.
| Component | Description | Test provisions |
|---|---|---|
| Desiccant Dehumidification Components | An assembly that reduces the moisture content of the supply air through moisture transfer with solid or liquid desiccants | Disable desiccant dehumidification components for testing. |
| Air Economizers | An automatic system that enables a cooling system to supply outdoor air to reduce or eliminate the need for mechanical cooling during mild or cold weather | For any air economizer that is factory-installed, place the economizer in the 100% return position and close and seal the outside air dampers for testing. For any modular air economizer shipped with the unit but not factory-installed, do not install the economizer for testing. |
| Fresh Air Dampers | An assembly with dampers and means to set the damper position in a closed and one open position to allow air to be drawn into the equipment when the indoor fan is operating | For any fresh air dampers that are factory-installed, close and seal the dampers for testing. For any modular fresh air dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Hail Guards | A grille or similar structure mounted to the outside of the unit covering the outdoor coil to protect the coil from hail, flying debris, and damage from large objects | Remove hail guards for testing. |
| Low Ambient Cooling Dampers | An assembly with dampers and means to set the dampers in a position to recirculate the warmer condenser discharge air to allow for reliable operation at low outdoor ambient conditions | Remove low ambient cooling dampers for testing. |
| Power Correction Capacitors | A capacitor that increases the power factor measured at the line connection to the equipment. These devices are a requirement of the power distribution system supplying the unit | Remove power correction capacitors for testing. |
| Ventilation Energy Recovery Systems (VERS) | An assembly that preconditions outdoor air entering the equipment through direct or indirect thermal and/or moisture exchange with the exhaust air, which is defined as the building air being exhausted to the outside from the equipment | For any VERS that is factory-installed, place the VERS in the 100% return position and close and seal the outside air dampers and exhaust air dampers for testing, and do not energize any VERS subcomponents (e.g., energy recovery wheel motors). For any VERS module shipped with the unit but not factory-installed, do not install the VERS for testing. |
[87 FR 63898, Oct. 20, 2022]
Manufacturers must use the results of testing under this appendix to determine compliance with the relevant energy conservation standards for computer room air conditioners from § 431.97 as that standard appeared in the January 1, 2022 edition of 10 CFR parts 200 through 499. Specifically, representations, including compliance certifications, must be based upon results generated either under this appendix or under 10 CFR 431.96 as it appeared in the 10 CFR parts 200 through 499 edition revised as of January 1, 2022.
For any amended standards for computer room air conditioners that rely on net sensible coefficient of performance (NSenCOP) published after January 1, 2022, manufacturers must use the results of testing under appendix E1 to this subpart to determine compliance. Manufacturers may use appendix E1 to certify compliance with any amended standards prior to the applicable compliance date for those standards.
Specifically, representations, including compliance certifications, related to energy consumption must be based upon results generated under the appropriate appendix that applies (i.e., this appendix or appendix E1 to this subpart) when determining compliance with the relevant standard.
1. Incorporation by Reference.
DOE incorporated by reference in § 431.95 the entire standard for ASHRAE 127-2007. However, certain enumerated provisions of ASHRAE 127-2007, as listed in section 1.1, are inapplicable. To the extent that there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 ASHRAE 127-2007:
(a) Section 5.11 is inapplicable as specified in section 2 of this appendix.
(b) [Reserved]
1.2 [Reserved]
2. General. Determine the sensible coefficient of performance (SCOP) in accordance with ASHRAE 127-2007.
3. Optional break-in period. Manufacturers may optionally specify a “break-in” period, not to exceed 20 hours, to operate the equipment under test prior to conducting the test method specified in this appendix. A manufacturer who elects to use an optional compressor break-in period in its certification testing should record this period's duration as part of the information in the supplemental testing instructions under 10 CFR 429.43.
4. Additional provisions for equipment set-up. The only additional specifications that may be used in setting up the basic model for test are those set forth in the installation and operation manual shipped with the unit. Each unit should be set up for test in accordance with the manufacturer installation and operation manuals. Sections 4.1 and 4.2 of this appendix provide specifications for addressing key information typically found in the installation and operation manuals.
4.1. If a manufacturer specifies a range of superheat, sub-cooling, and/or refrigerant pressure in its installation and operation manual for a given basic model, any value(s) within that range may be used to determine refrigerant charge or mass of refrigerant, unless the manufacturer clearly specifies a rating value in its installation and operation manual, in which case the specified rating value must be used.
4.2. The airflow rate used for testing must be that set forth in the installation and operation manuals being shipped to the commercial customer with the basic model and clearly identified as that used to generate the DOE performance ratings. If a rated airflow value for testing is not clearly identified, a value of 400 standard cubic feet per minute (scfm) per ton must be used.
[88 FR 21840, Apr. 11, 2023]
Prior to the compliance date for any amended energy conservation standards based on NSenCOP for computer room air conditioners, representations with respect to energy use or efficiency of this equipment, including compliance certifications, must be based on testing pursuant to appendix E to this subpart. Subsequently, manufacturers must use the results of testing under this appendix to determine compliance with any amended energy conservation standards for computer room air conditioners provided in § 431.97 that are published after January 1, 2022, and that rely on net sensible coefficient of performance (NSenCOP). Specifically, representations, including compliance certifications, related to energy consumption must be based upon results generated under the appropriate appendix that applies (i.e., appendix E to this subpart or this appendix) when determining compliance with the relevant standard. Manufacturers may use this appendix to certify compliance with any amended standards prior to the applicable compliance date for those standards.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95 the entire standards for AHRI 1360-2022, ANSI/ASHRAE 37-2009, and ANSI/ASHRAE 127-2020. However, as listed in sections 1.1, 1.2, and 1.3 of this appendix, only certain enumerated provisions of AHRI 1360-2022 and ANSI/ASHRAE 127-2020 are applicable, and only certain enumerated provisions of ANSI/ASHRAE 37-2009 are not applicable. To the extent that there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 AHRI 1360-2022:
(a) The following sections of Section 3. Definitions—3.1 (Expressions of Provision), 3.2.2 (Air Sampling Device(s)), 3.2.7 (Computer and Data Processing Room Air Conditioner), 3.2.22 (Indoor Unit), 3.2.25 (Manufacturer's Installation Instruction), 3.2.27 (Net Sensible Cooling Capacity), 3.2.28 (Net Total Cooling Capacity), 3.2.37 (Standard Air) and 3.2.38 (Standard Airflow) are applicable.
(b) Section 5. Test Requirements, is applicable.
(c) The following sections of Section 6. Rating Requirements—6.1-6.3, 6.5 and 6.7 are applicable.
(d) Appendix C. Standard Configurations—Normative, is applicable.
(e) Section D2 of Appendix D. Non-Standard Indoor Fan Motors for CRAC units, is applicable.
(f) Appendix E. Method of Testing Computer and Data Processing Room Air Conditioners—Normative, is applicable.
(g) Appendix F. Indoor and Outdoor Air Condition Measurement—Normative is applicable.
1.2 ANSI/ASHRAE 127-2020:
(a) Appendix A—Figure A-1, Test duct for measuring air flow and static pressure on downflow units, is applicable.
(b) [Reserved].
1.3 ASHRAE 37-2009:
(a) Section 1 Purpose is inapplicable.
(b) Section 2 Scope is inapplicable.
(c) Section 4 Classification is inapplicable.
2. General. Determine the net sensible coefficient of performance (NSenCOP), in accordance with AHRI 1360-2022, ANSI/ASHRAE 127-2020, and ANSI/ASHRAE 37-2009. In cases where there is a conflict between these sources, the language of this appendix takes highest precedence, followed by AHRI 1360-2022, followed by ANSI/ASHRAE 127-2020, followed by ANSI/ASHRAE 37-2009. Any subsequent amendment to a referenced document by a standard-setting organization will not affect the test procedure in this appendix, unless and until this test procedure is amended by DOE. Material is incorporated as it exists on the date of the approval, and notification of any change in the incorporation will be published in the Federal Register.
3. Test Conditions
3.1. Test Conditions for Certification. When testing to certify to the energy conservation standards in § 431.97, test using the “Indoor Return Air Temperature Standard Rating Conditions” and “Heat Rejection/Cooling Fluid Standard Rating Conditions” conditions, as specified in Tables 3 and 4 of AHRI 1360-2022, respectively.
4. Set-Up and Test Provisions for Specific Components. When testing a unit that includes any of the features listed in Table 4.1 of this appendix, test in accordance with the set-up and test provisions specified in Table 4.1 of this appendix.
| Component | Description | Test provisions |
|---|---|---|
| Air Economizers | An automatic system that enables a cooling system to supply outdoor air to reduce or eliminate the need for mechanical cooling during mild or cold weather | For any air economizer that is factory-installed, place the economizer in the 100% return position and close and seal the outside air dampers for testing. For any modular air economizer shipped with the unit but not factory-installed, do not install the economizer for testing. |
| Process Heat Recovery/Reclaim Coils/Thermal Storage | A heat exchanger located inside the unit that conditions the equipment's supply air using energy transferred from an external source using a vapor, gas, or liquid | Disconnect the heat exchanger from its heat source for testing. |
| Evaporative Pre-cooling of Condenser Intake Air | Water is evaporated into the air entering the air-cooled condenser to lower the dry-bulb temperature and thereby increase efficiency of the refrigeration cycle | Disconnect the unit from the water supply for testing (i.e., operate without active evaporative cooling). |
| Steam/Hydronic Heat Coils | Coils used to provide supplemental heat | Test with steam/hydronic heat coils in place but providing no heat. |
| Refrigerant Reheat Coils | A heat exchanger located downstream of the indoor coil that heats the supply air during cooling operation using high pressure refrigerant in order to increase the ratio of moisture removal to cooling capacity provided by the equipment | De-activate refrigerant re-heat coils so as to provide the minimum (none if possible) reheat achievable by the system controls. |
| Fire/Smoke/Isolation Dampers | A damper assembly including means to open and close the damper mounted at the supply or return duct opening of the equipment | For any fire/smoke/isolation dampers that are factory-installed, close and seal the dampers for testing. For any modular fire/smoke/isolation dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Harmonic Distortion Mitigation Devices | A high voltage device that reduces harmonic distortion measured at the line connection of the equipment that is created by electronic equipment in the unit | Remove harmonic distortion mitigation devices for testing. |
| Humidifiers | A device placed in the supply air stream for moisture evaporation and distribution. The device may require building steam or water, hot water, electricity, or gas to operate | Test with humidifiers in place but providing no humidification. |
| Electric Reheat Elements | Electric reheat elements and controls that are located downstream of the cooling coil that may heat the air using electrical power during the dehumidification process | Test with electric reheat elements in place but providing no heat. |
| Non-standard Power Transformer | A device applied to a high voltage load that transforms input electrical voltage to that voltage necessary to operate the load | Disable the non-standard power transformer during testing. |
| Chilled Water Dual Cooling Coils | A secondary chilled water coil added in the indoor air stream for use as the primary or secondary cooling circuit in conjunction with a separate chiller | Test with chilled water dual cooling coils in place but providing no cooling. |
| High-Effectiveness Indoor Air Filtration | Indoor air filters with greater air filtration effectiveness than Minimum Efficiency Reporting Value (MERV) 8 for ducted units and MERV 1 for non-ducted units | Test with the filter offered by the manufacturer with the least air filtration effectiveness that meets or exceeds MERV 8 for ducted units and MERV 1 for non-ducted units. |
[88 FR 21841, Apr. 11, 2023]
Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standard from § 431.97 as that standard appeared in the January 1, 2022, edition of 10 CFR parts 200-499. Specifically, representations must be based upon results generated either under this appendix or under 10 CFR 431.96 as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2021.
For any amended standards for air-cooled, three-phase, small commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h and air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h that rely on SEER2 and HSPF2 published after January 1, 2021, manufacturers must use the results of testing under appendix F1 to determine compliance. Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., appendices F or F1) when determining compliance with the relevant standard. Manufacturers may also use appendix F1 to certify compliance with any amended standards that rely on SEER2 and HSPF2 prior to the applicable compliance date for those standards.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95, the entire standard for ANSI/AHRI 210/240-2008 and ANSI/AHRI 1230-2010. However, certain enumerated provisions of those standards, as set forth in this section 1, are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 ANSI/AHRI 210/240-2008:
(a) Section 6.5—Tolerances
(b) Reserved.
1.2 ANSI/AHRI 1230-2010:
(a) Section 5.1.2—Manufacturer involvement
(b) Section 6.6—Verification testing and uncertainty
2. General
2.1 Air-cooled, three-phase, small commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h. Determine the seasonal energy efficiency ratio (SEER) and heating seasonal performance factor (HSPF) (as applicable) in accordance with ANSI/AHRI 210/240-2008. Sections 3 to 6 of this appendix provide additional instructions for determining SEER and HSPF.
2.2 Air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h. Determine the SEER and HSPF (as applicable) in accordance with ANSI/AHRI 1230-2010.
Sections 3 through 6 of this appendix provide additional instructions for determining SEER and HSPF.
3. Optional break-in period. Manufacturers may optionally specify a “break-in” period, not to exceed 20 hours, to operate the equipment under test prior to conducting the test method specified in this appendix. A manufacturer who elects to use an optional compressor break-in period in its certification testing should record this period's duration as part of the information in the supplemental testing instructions under 10 CFR 429.43.
4. Additional provisions for equipment set-up. The only additional specifications that may be used in setting up the basic model for test are those set forth in the installation and operation manual shipped with the unit. Each unit should be set up for test in accordance with the manufacturer installation and operation manuals. Sections 3.1 through 3.3 of this appendix provide specifications for addressing key information typically found in the installation and operation manuals.
4.1. If a manufacturer specifies a range of superheat, sub-cooling, and/or refrigerant pressure in its installation and operation manual for a given basic model, any value(s) within that range may be used to determine refrigerant charge or mass of refrigerant, unless the manufacturer clearly specifies a rating value in its installation and operation manual, in which case the specified rating value shall be used.
4.2. The airflow rate used for testing must be that set forth in the installation and operation manuals being shipped to the commercial customer with the basic model and clearly identified as that used to generate the DOE performance ratings. If a rated airflow value for testing is not clearly identified, a value of 400 standard cubic feet per minute (scfm) per ton shall be used.
4.3. For air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h, the test set-up and the fixed compressor speeds (i.e., the maximum, minimum, and any intermediate speeds used for testing) should be recorded and maintained as part of the test data underlying the certified ratings that is required to be maintained under 10 CFR 429.71.
5. Refrigerant line length corrections for air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h. For test setups where it is physically impossible for the laboratory to use the required line length listed in Table 3 of ANSI/AHRI 1230-2010, then the actual refrigerant line length used by the laboratory may exceed the required length and the following cooling capacity correction factors are applied:
| Piping length beyond minimum, X (ft) |
Piping length beyond minimum, Y (m) |
Cooling capacity correction (%) |
|---|---|---|
| 0>X ≤20 | 0>Y ≤6.1 | 1 |
| 20>X ≤40 | 6.1>Y ≤12.2 | 2 |
| 40>X ≤60 | 12.2>Y ≤18.3 | 3 |
| 60>X ≤80 | 18.3>Y ≤24.4 | 4 |
| 80>X ≤100 | 24.4>Y ≤30.5 | 5 |
| 100 >X ≤120 | 30.5>Y ≤36.6 | 6 |
6. Manufacturer involvement in assessment or enforcement testing for air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h. A manufacturer's representative will be allowed to witness assessment and/or enforcement testing. The manufacturer's representative will be allowed to inspect and discuss set-up only with a DOE representative and adjust only the modulating components during testing in the presence of a DOE representative that are necessary to achieve steady-state operation. Only previously documented specifications for set-up as specified under sections 3 and 4 of this appendix will be used.
[87 FR 77327, Dec. 16, 2022; 87 FR 78513, Dec. 22, 2022]
Manufacturers must use the results of testing under this appendix to determine compliance with any amended standards for air-cooled, three-phase, small commercial package air conditioning and heating equipment with a cooling capacity of less than 65,000 Btu/h and air-cooled, three-phase, variable refrigerant flow multi-split air conditioners and heat pumps with a cooling capacity of less than 65,000 Btu/h provided in § 431.97 that are published after January 1, 2021, and that rely on seasonal energy efficiency ratio 2 (SEER2) and heating seasonal performance factor 2 (HSPF2). Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., appendices F or F1) when determining compliance with the relevant standard. Manufacturers may also use this appendix to certify compliance with any amended standards that rely on SEER2 and HSPF2 prior to the applicable compliance date for those standards.
1. Incorporation by Reference. DOE incorporated by reference in § 431.95, the entire standard for AHRI 210/240-2023 and ANSI/ASHRAE 37-2009. However, certain enumerated provisions of AHRI 210/240-2023 and ANSI/ASHRAE 37-2009, as set forth in this section 1, are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
1.1. AHRI 210/240-2023:
(a) Section 6 Rating Requirements—6.1 Standard Ratings—6.1.8 Tested Combinations or Tested Units
(b) Section 6 Rating Requirements—6.2 Application Ratings
(c) Section 6 Rating Requirements—6.4 Ratings
(d) Section 6 Rating Requirements—6.5 Uncertainty and Variability
(e) Section 7—Minimum Data Requirements for Published Ratings
(f) Section 8—Operating Requirements
(g) Section 9—Marking and Nameplate Data
(h) Section 10—Conformance Conditions
(i) Appendix C—Certification of Laboratory Facilities Used to Determine Performance of Unitary Air-Conditioning & Air-Source Heat Pump Equipment—Informative
(j) Appendix F—ANSI/ASHRAE Standard 116-2010 Clarifications/Exceptions—Normative—F15.2 and F17
(k) Appendix G—Unit Configuration for Standard Efficiency Determination—Normative
(l) Appendix H—Off-Mode Testing—Normative
(m) Appendix I Verification Testing—Normative
1.2. ANSI/ASHRAE 37-2009:
(a) Section 1—Purpose
(b) Section 2—Scope
(c) Section 4—Classification
2. General. Determine the seasonal energy efficiency ratio 2 (SEER2) and heating seasonal performance factor 2 (HSPF2) (as applicable) in accordance with AHRI 210/240-2023 and ANSI/ASHRAE 37-2009. Sections 3 and 4 to this appendix provide additional instructions for determining SEER2 and HSPF2.
3. Energy Measurement Accuracy. The Watt-hour (W⋅h) measurement system(s) shall be accurate within ± 0.5 percent or 0.5 W⋅h, whichever is greater, for both ON and OFF cycles. If two measurement systems are used, then the meters shall be switched within 15 seconds of the start of the OFF cycle and switched within 15 seconds prior to the start of the ON cycle.
4. Cycle Stability Requirements. Conduct three complete compressor OFF/ON cycles. Calculate the degradation coefficient CD for each complete cycle. If all three CD values are within 0.02 of the average CD then stability has been achieved, and the highest CD value of these three shall be used. If stability has not been achieved, conduct additional cycles, up to a maximum of eight cycles total, until stability has been achieved between three consecutive cycles. Once stability has been achieved, use the highest CD value of the three consecutive cycles that establish stability. If stability has not been achieved after eight cycles, use the highest CD from cycle one through cycle eight, or the default CD, whichever is lower.
[87 FR 77328, Dec. 16, 2022]
Prior to December 4, 2023, manufacturers must use the results of testing under either this appendix or § 431.96 as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2021, to determine compliance with the relevant standard from § 431.97 as that standard appeared in the January 1, 2021, edition of 10 CFR parts 200-499. On or after December 4, 2023, manufacturers must use the results of testing generated under this appendix to demonstrate compliance with the relevant standard from § 431.97 as that standard appeared in the January 1, 2021, edition of 10 CFR parts 200-499.
Beginning December 4, 2023, if manufacturers make voluntary representations with respect to the integrated energy efficiency ratio (IEER) of single packaged vertical air conditioners and single package vertical heat pumps, such representations must be based on testing conducted in accordance with appendix G1 to this subpart.
For any amended standards for single packaged vertical air conditioners and single package vertical heat pumps based on IEER published after January 1, 2021, manufacturers must use the results of testing under appendix G1 to this subpart to determine compliance. Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., this appendix or appendix G1) when determining compliance with the relevant standard. Manufacturers may also use appendix G1 to certify compliance with any amended standards prior to the applicable compliance date for those standards.
1. Incorporation by Reference.
DOE incorporated by reference in § 431.95 the entire standard for AHRI 390-2021 and ASHRAE 37-2009. However, only certain enumerated provisions of AHRI 390-2021 and ANSI/ASHRAE 37-2009 are required or excluded as listed in this section 1. To the extent there is a conflict between the terms or provisions of a referenced industry standard and this appendix, the appendix provisions control, followed by AHRI 390-2021, followed by ANSI/ASHRAE 37-2009.
1.1. Only the following provisions of AHRI 390-2021 apply:
(a) Section 3—Definitions (omitting sections 3.1, 3.2, 3.5, 3.12, and 3.15)
(b) Section 5—Test Requirements (omitting section 5.8.5)
(c) Section 6—Rating Requirements (omitting sections 6.1.1 and 6.2 through 6.5)
(d) Appendix A. “References—Normative”
(e) Appendix D. “Indoor and Outdoor Air Condition Measurement—Normative”
(f) Appendix E. “Method of Testing Single Package Vertical Units—Normative”
1.2. All provisions of ANSI/ASHRAE 37-2009 apply except for the following provisions:
(a) Section 1—Purpose
(b) Section 2—Scope
(c) Section 4—Classifications
2. General. Determine cooling capacity (Btu/h) and energy efficiency ratio (EER) for all single package vertical air conditioners and heat pumps and coefficient of performance (COP) for all single package vertical heat pumps, in accordance with the specified sections of AHRI 390-2021 and the specified sections of ANSI/ASHRAE 37-2009. Only identified provisions of AHRI 390-2021 are applicable and certain sections of ANSI/ASHRAE 37-2009 are inapplicable, as set forth in section 1 of this appendix. In addition, the instructions in section 3 of this appendix apply to determining EER and COP. Any subsequent amendment to a referenced document by a standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
3. Test Conditions. The “Standard Rating Full Load Capacity Test, Cooling” conditions for cooling mode tests and “Standard Rating Full Load Capacity Test, Heating” conditions for heat pump heating mode tests specified in Table 3 of section 5.8.3 of AHRI 390-2021 shall be used.
3.1. Optional Representations. Representations of COP for single package vertical heat pumps made using the “Low Temperature Operation, Heating” condition specified in Table 3 of section 5.8.3 of AHRI 390-2021 are optional and are determined according to the applicable provisions in section 1 of this appendix.
3.2. [Reserved]
[87 FR 75169, Dec. 7, 2022]
Beginning December 4, 2023, if manufacturers make voluntary representations with respect to the integrated energy efficiency ratio (IEER) of single packaged vertical air conditioners and single package vertical heat pumps, such representations must be based on testing conducted in accordance with this appendix.
Manufacturers must use the results of testing under this appendix to determine compliance with any amended standards for single packaged vertical air conditioners and single package vertical heat pumps based on IEER provided in § 431.97 that are published after January 1, 2021. Representations related to energy consumption must be made in accordance with the appropriate appendix that applies (i.e., appendix G to this subpart or this appendix) when determining compliance with the relevant standard. Manufacturers may also use this appendix to certify compliance with any amended standards prior to the applicable compliance date for those standards.
1. Incorporation by Reference
DOE incorporated by reference in § 431.95 the entire standard for AHRI 390-2021 and ASHRAE 37-2009. However, only certain enumerated provisions of AHRI 390-2021 and ANSI/ASHRAE 37-2009 are required or excluded as listed in this section 1. To the extent there is a conflict between the terms or provisions of a referenced industry standard and this appendix, the appendix provisions control, followed by AHRI 390-2021, followed by ANSI/ASHRAE 37-2009.
1.1. Only the following provisions of AHRI 390-2021 apply:
(a) Section 3—Definitions (omitting sections 3.1, 3.2, 3.5, 3.12, and 3.15)
(b) Section 5—Test Requirements (omitting section 5.8.5)
c) Section 6—Rating Requirements (omitting sections 6.1.1 and 6.3 through 6.5)
(d) Appendix A. “References—Normative”
(e) Appendix D. “Indoor and Outdoor Air Condition Measurement—Normative”
(f) Appendix E. “Method of Testing Single Package Vertical Units—Normative”
1.2. All provisions of ANSI/ASHRAE 37-2009 apply except for the following provisions:
(a) Section 1—Purpose
(b) Section 2—Scope
(c) Section 4—Classifications
2. General. Determine cooling capacity (Btu/h) and integrated energy efficiency ratio (IEER) for all single package vertical air conditioners and heat pumps and coefficient of performance (COP) for all single package vertical heat pumps, in accordance with the specified sections of AHRI 390-2021and the specified sections of ANSI/ASHRAE 37-2009. Only identified provisions of AHRI 390-2021 and ANSI/ASHRAE 37-2009 are applicable, as set forth in section 1 of this appendix. In addition, the instructions in section 4 of this appendix apply to determining IEER and COP. Any subsequent amendment to a referenced document by a standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
3. Test Conditions. The “Part-Load Standard Rating Conditions” conditions for cooling mode tests and “Standard Rating Full Load Capacity Test, Heating” conditions for heat pump heating mode tests specified in Table 3 of section 5.8.3 of AHRI 390-2021 shall be used.
3.1. Optional Representations. Representations of COP for single package vertical heat pumps made using the “Low Temperature Operation, Heating” condition specified in Table 3 of section 5.8.3 of AHRI 390-2021 are optional and are determined according to the applicable provisions in section 1.1 of this appendix.
4. Set-Up and Test Provisions for Specific Components. When testing a single package vertical unit (SPVU) that includes any of the features listed in table 4.1 to this appendix, test in accordance with the set-up and test provisions specified in table 4.1 to this appendix.
| Component | Description | Test provisions |
|---|---|---|
| Desiccant Dehumidification Components | An assembly that reduces the moisture content of the supply air through moisture transfer with solid or liquid desiccants | Disable desiccant dehumidification components for testing. |
| Air Economizers | An automatic system that enables a cooling system to supply outdoor air to reduce or eliminate the need for mechanical cooling during mid or cold weather | For any air economizer that is factory-installed, place the economizer in the 100% return position and close and seal the outside air dampers for testing. For any modular air economizer shipped with the unit but not factory-installed, do not install the economizer for testing. |
| Fresh Air Dampers | An assembly with dampers and means to set the damper position in a closed and one open position to allow air to be drawn into the equipment when the indoor fan is operating | For any fresh air dampers that are factory-installed, close and seal the dampers for testing. For any modular fresh air dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| Hail Guards | A grille or similar structure mounted to the outside of the unit covering the outdoor coil to protect the coil from hail, flying debris and damage from large objects | Remove hail guards for testing. |
| Power Correction Capacitors | A capacitor that increases the power factor measured at the line connection to the equipment | Remove power correction capacitors for testing. |
| Ventilation Energy Recovery System (VERS) | An assembly that preconditions outdoor air entering the equipment through direct or indirect thermal and/or moisture exchange with the exhaust air, which is defined as the building air being exhausted to the outside from the equipment | For any VERS that is factory-installed, place the VERS in the 100% return position and close and seal the outside air dampers and exhaust air dampers for testing, and do not energize any VERS subcomponents (e.g., energy recovery wheel motors). For any VERS module shipped with the unit but not factory-installed, do not install the VERS for testing. |
| Barometric Relief Dampers | An assembly with dampers and means to automatically set the damper position in a closed position and one or more open positions to allow venting directly to the outside a portion of the building air that is returning to the unit, rather than allowing it to recirculate to the indoor coil and back to the building | For any barometric relief dampers that are factory-installed, close and seal the dampers for testing. For any modular barometric relief dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
| UV Lights | A lighting fixture and lamp mounted so that it shines light on the indoor coil, that emits ultraviolet light to inhibit growth of organisms on the indoor coil surfaces, the condensate drip pan, and/other locations within the equipment | Turn off UV lights for testing. |
| Steam/Hydronic Heat Coils | Coils used to provide supplemental heating | Test with steam/hydronic heat coils in place but providing no heat. |
| Hot Gas Reheat | A heat exchanger located downstream of the indoor coil that heats the Supply Air during cooling operation using high pressure refrigerant in order to increase the ratio of moisture removal to Cooling Capacity provided by the equipment | De-activate refrigerant reheat coils for testing so as to provide the minimum (none if possible) reheat achievable by the system controls. |
| Sound Traps/Sound Attenuators | An assembly of structures through which the Supply Air passes before leaving the equipment or through which the return air from the building passes immediately after entering the equipment for which the sound insertion loss is at least 6 dB for the 125 Hz octave band frequency range | Removable sound traps/sound attenuators shall be removed for testing. Otherwise, test with sound traps/attenuators in place. |
| Fire/Smoke/Isolation Dampers | A damper assembly including means to open and close the damper mounted at the supply or return duct opening of the equipment | For any fire/smoke/isolation dampers that are factory-installed, set the dampers in the fully open position for testing. For any modular fire/smoke/isolation dampers shipped with the unit but not factory-installed, do not install the dampers for testing. |
[87 FR 75170, Dec. 7, 2022]
69 FR 61983, Oct. 21, 2004, unless otherwise noted.
This subpart contains energy conservation requirements for certain commercial water heaters, hot water supply boilers and unfired hot water storage tanks, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
[69 FR 61983, Oct. 21, 2004, as amended at 70 FR 60415, Oct. 18, 2005]
The following definitions apply for purposes of this subpart G, and of subparts J through M of this part. Any words or terms not defined in this section or elsewhere in this part shall be defined as provided in section 340 of the Act, 42 U.S.C. 6311.
Air-source commercial heat pump water heater means a commercial heat pump water heater that utilizes indoor or outdoor air as the heat source.
Basic model means all water heaters, hot water supply boilers, or unfired hot water storage tanks manufactured by one manufacturer within a single equipment class, having the same primary energy source (e.g., gas or oil) and that have essentially identical electrical, physical and functional characteristics that affect energy efficiency.
Coefficient of performance (COPh) means the dimensionless ratio of the rate of useful heat transfer gained by the water (expressed in Btu/h), to the rate of electric power consumed during operation (expressed in Btu/h).
Commercial heat pump water heater (CHPWH) means a water heater (including all ancillary equipment such as fans, blowers, pumps, storage tanks, piping, and controls, as applicable) that uses a refrigeration cycle, such as vapor compression, to transfer heat from a low-temperature source to a higher-temperature sink for the purpose of heating potable water, and operates with a current rating greater than 24 amperes or a voltage greater than 250 volts. Such equipment includes, but is not limited to, air-source heat pump water heaters, water-source heat pump water heaters, and direct geo-exchange heat pump water heaters.
Direct geo-exchange commercial heat pump water heater means a commercial heat pump water heater that utilizes the earth as a heat source and allows for direct exchange of heat between the earth and the refrigerant in the evaporator coils.
Flow-activated instantaneous water heater means an instantaneous water heater or hot water supply boiler that activates the burner or heating element only if heated water is drawn from the unit.
Fuel input rate means the maximum measured rate at which gas-fired or oil-fired commercial water heating equipment uses energy as determined using test procedures prescribed under § 431.106 of this part.
Ground-source closed-loop commercial heat pump water heater means a commercial heat pump water heater that utilizes a fluid circulated through a closed piping loop as a medium to transfer heat from the ground to the refrigerant in the evaporator. The piping loop may be buried inside the ground in horizontal trenches or vertical bores, or submerged in a surface water body.
Ground water-source commercial heat pump water heater means a commercial heat pump water heater that utilizes ground water as the heat source.
Hot water supply boiler means a packaged boiler (defined in § 431.82 of this part) that is industrial equipment and that:
(1) Has a rated input from 300,000 Btu/h to 12,500,000 Btu/h and of at least 4,000 Btu/h per gallon of stored water;
(2) Is suitable for heating potable water; and
(3) Meets either or both of the following conditions:
(i) It has the temperature and pressure controls necessary for heating potable water for purposes other than space heating; or
(ii) The manufacturer's product literature, product markings, product marketing, or product installation and operation instructions indicate that the boiler's intended uses include heating potable water for purposes other than space heating.
Indoor water-source commercial heat pump water heater means a commercial heat pump water heater that utilizes indoor water as the heat source.
Instantaneous water heater means a water heater that uses gas, oil, or electricity, including:
(1) Gas-fired instantaneous water heaters with a rated input both greater than 200,000 Btu/h and not less than 4,000 Btu/h per gallon of stored water;
(2) Oil-fired instantaneous water heaters with a rated input both greater than 210,000 Btu/h and not less than 4,000 Btu/h per gallon of stored water; and
(3) Electric instantaneous water heaters with a rated input both greater than 12 kW and not less than 4,000 Btu/h per gallon of stored water.
Rated input means the maximum rate at which commercial water heating equipment is rated to use energy as specified on the nameplate.
R-value means the thermal resistance of insulating material as determined using ASTM C177-13 or C518-15 (incorporated by reference; see § 431.105) and expressed in ( °F·ft2·h/Btu).
Residential-duty commercial water heater means any gas-fired storage, oil-fired storage, or electric instantaneous commercial water heater that meets the following conditions:
(1) For models requiring electricity, uses single-phase external power supply;
(2) Is not designed to provide outlet hot water at temperatures greater than 180 °F; and
(3) Does not meet any of the following criteria:
| Water heater type | Indicator of non-residential application |
|---|---|
| Gas-fired Storage | Rated input >105 kBtu/h; Rated storage volume >120 gallons. |
| Oil-fired Storage | Rated input >140 kBtu/h; Rated storage volume >120 gallons. |
| Electric Instantaneous | Rated input >58.6 kW; Rated storage volume >2 gallons. |
Standby loss means:
(1) For electric commercial water heating equipment (not including commercial heat pump water heaters), the average hourly energy required to maintain the stored water temperature expressed as a percent per hour (%/h) of the heat content of the stored water above room temperature and determined in accordance with appendix B or D to subpart G of part 431 (as applicable), denoted by the term “S”; or
(2) For gas-fired and oil-fired commercial water heating equipment, the average hourly energy required to maintain the stored water temperature expressed in British thermal units per hour (Btu/h) based on a 70 °F temperature differential between stored water and ambient room temperature and determined in accordance with appendix A or C to subpart G of part 431 (as applicable), denoted by the term “SL.”
Storage-type instantaneous water heater means an instantaneous water heater that includes a storage tank with a rated storage volume greater than or equal to 10 gallons.
Storage water heater means a water heater that uses gas, oil, or electricity to heat and store water within the appliance at a thermostatically-controlled temperature for delivery on demand, including:
(1) Gas-fired storage water heaters with a rated input both greater than 75,000 Btu/h and less than 4,000 Btu/h per gallon of stored water;
(2) Oil-fired storage water heaters with a rated input both greater than 105,000 Btu/h and less than 4,000 Btu/h per gallon of stored water; and
(3) Electric storage water heaters with a rated input both greater than 12 kW and less than 4,000 Btu/h per gallon of stored water.
Tank surface area means, for the purpose of determining portions of a tank requiring insulation, those areas of a storage tank, including hand holes and manholes, in its uninsulated or pre-insulated state, that do not have pipe penetrations or tank supports attached.
Thermal efficiency for an instantaneous water heater, a storage water heater or a hot water supply boiler means the ratio of the heat transferred to the water flowing through the water heater to the amount of energy consumed by the water heater as measured during the thermal efficiency test procedure prescribed in this subpart.
Unfired hot water storage tank means a tank used to store water that is heated externally, and that is industrial equipment.
[69 FR 61983, Oct. 21, 2004, as amended at 76 FR 12503, Mar. 7, 2011; 78 FR 79599, Dec. 31, 2013; 79 FR 40586, July 11, 2014; 81 FR 79321, Nov. 10, 2016; 88 FR 40494, June 21, 2023; 88 FR 69821, Oct. 6, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Avenue SW, EE-5B, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email: fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section.
(b) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers, 1791 Tullie Circle NE. Atlanta, GA 30329, (800) 527-4723, or go to https://www.ashrae.org.
(1) ANSI/ASHRAE Standard 118.1-2012, “Method of Testing for Rating Commercial Gas, Electric, and Oil Service Water-Heating Equipment,” approved by ASHRAE on October 26, 2012, IBR approved for appendix E to this subpart, as follows:
(i) Section 3—Definitions and Symbols;
(ii) Section 4—Classifications by Mode of Operation (sections 4.4, and 4.5 only);
(iii) Section 6—Instruments (except sections 6.3, 6.4 and 6.6);
(iv) Section 7—Apparatus (except section 7.4, Figures 1 through 4, section 7.7.5, Table 2, and section 7.7.7.4);
(v) Section 8—Methods of Testing:
(A) Section 8.2—Energy Supply, Section 8.2.1—Electrical Supply;
(B) Section 8.7—Water Temperature Control;
(vi) Section 9—Test Procedures: 9.1—Input Rating, Heating Capacity, Thermal Efficiency, Coefficient of Performance (COP), and Recovery Rating; 9.1.1—Full Input Rating;
(vii) Section 10—Calculation of Results: Section 10.3—Heat-Pump Water Heater Water-Heating Capacity, Coefficient of Performance (COP), and Recovery Rating; Section 10.3.1—Type IV and Type V Full-Capacity Test Method.
(2) [Reserved]
(c) ASTM. ASTM International, 100 Barr Harbor Drive, P.O. Box C700, West Conshohocken, PA 19428-2959, (610) 832-9585, or go to http://www.astm.org.
(1) ASTM C177-13, “Standard Test Method for Steady-State Heat Flux Measurements and Thermal Transmission Properties by Means of the Guarded-Hot-Plate Apparatus,” approved September 15, 2013, IBR approved for § 431.102.
(2) ASTM C518-15, “Standard Test Method for Steady-State Thermal Transmission Properties by Means of the Heat Flow Meter Apparatus,” approved September 1, 2015, IBR approved for § 431.102t.
(3) ASTM D2156-09 (Reapproved 2013), “Standard Test Method for Smoke Density in Flue Gases from Burning Distillate Fuels,” approved October 1, 2013, IBR approved for appendices A and C to this subpart.
(d) CSA Group, 5060 Spectrum Way, Suite 100, Mississauga, Ontario, Canada L4W 5N6, 800-463-6727, or go to http://www.csagroup.org/.
(1) ANSI Z21.10.3-2015 * CSA 4.3-2015 (“ANSI Z21.10.3-2015”), “Gas-fired water heaters, volume III, storage water heaters with input ratings above 75,000 Btu per hour, circulating and instantaneous,” approved by ANSI on October 5, 2015, IBR approved for appendices A, B, and C to this subpart, as follows:
(i) Annex E (normative) Efficiency test procedures—E.1—Method of test for measuring thermal efficiency, paragraph c—Vent requirements; and
(ii) Annex E (normative) Efficiency test procedures—E.1—Method of test for measuring thermal efficiency, paragraph f—Installation of temperature sensing means.
(2) [Reserved]
[77 FR 28996, May 16, 2012, as amended at 81 FR 79322, Nov. 10, 2016; 88 FR 69821, Oct. 6, 2023]
(a) Scope. This section contains test procedures for measuring, pursuant to EPCA, the energy efficiency of commercial water heating equipment.
(b) Testing and calculations. Determine the energy efficiency of commercial water heating equipment by conducting the applicable test procedure(s):
(1) Residential-duty commercial water heaters. Test in accordance with appendix E to subpart B of part 430 of this chapter.
(2) Commercial water heating equipment other than residential-duty commercial water heaters. Test in accordance with the appropriate test procedures in appendices to subpart G of this part.
(i) Gas-fired and oil-fired storage water heaters and storage-type instantaneous water heaters. Test according to appendix A to subpart G of this part.
(ii) Electric storage water heaters and storage-type instantaneous water heaters. Test according to appendix B to subpart G of this part.
(iii) Gas-fired and oil-fired instantaneous water heaters and hot water supply boilers (other than storage-type instantaneous water heaters). Test according to appendix C to subpart G of this part.
(iv) Electric instantaneous water heaters (other than storage-type instantaneous water heaters). Test according to appendix D to subpart G of this part.
(v) Commercial heat pump water heaters. Test according to appendix E to subpart G of this part.
[81 FR 79322, Nov. 10, 2016]
(a) Each commercial storage water heater, instantaneous water heater, and hot water supply boiler (excluding residential-duty commercial water heaters) must meet the applicable energy conservation standard level(s) as specified in the table to this paragraph. Any packaged boiler that provides service water that meets the definition of “commercial packaged boiler” in subpart E of this part, but does not meet the definition of “hot water supply boiler” in subpart G of this part, must meet the requirements that apply to it under subpart E of this part.
| Equipment | Size | Energy conservation standards a | |||
|---|---|---|---|---|---|
| Minimum thermal efficiency (equipment manufactured on and after October 9, 2015) (%) |
Minimum thermal efficiency (equipment manufactured on and after October 6, 2026) (%) |
Maximum standby loss (equipment manufactured on and after October 29, 2003) b |
Maximum standby loss (equipment manufactured on and after October 6, 2026) b |
||
| Electric storage water heaters | All | N/A | N/A | 0.30 + 27/Vm (%/h) | 0.30 + 27/Vm (%/h) |
| Gas-fired storage water heaters and storage-type instantaneous water heaters | All | 80 | 95 | Q/800 + 110(Vr)1/2 (Btu/h) | 0.86 × [Q/800 + 110(Vr)1/2] (Btu/h) |
| Oil-fired storage water heaters | All | 80 | 80 | Q/800 + 110(Vr)1/2 (Btu/h) | Q/800 + 110(Vr)1/2 (Btu/h) |
| Electric instantaneous water heaters c | <10 gal ≥10 gal |
80 77 |
80 77 |
N/A 2.30 + 67/Vm (%/h) |
N/A 2.30 + 67/Vm (%/h) |
| Gas-fired instantaneous water heaters and hot water supply boilers | <10 gal ≥10 gal |
80 80 |
96 96 |
N/A Q/800 + 110(Vr)1/2 (Btu/h) |
N/A Q/800 + 110(Vr)1/2 (Btu/h) |
| Oil-fired instantaneous water heater and hot water supply boilers | <10 gal ≥10 gal |
80 78 |
80 78 |
N/A Q/800 + 110(Vr)1/2 (Btu/h) |
N/A Q/800 + 110(Vr)1/2 (Btu/h) |
| a Vm is the measured storage volume, and Vr is the rated storage volume, both in gallons. Q is the rated input in Btu/h, as determined pursuant to 10 CFR 429.44. | |||||
| b Water heaters and hot water supply boilers with a rated storage volume greater than 140 gallons need not meet the standby loss requirement if: | |||||
| (1) The tank surface area is thermally insulated to R-12.5 or more, with the R-value as defined in § 431.102 | |||||
| (2) A standing pilot light is not used; and | |||||
| (3) For gas-fired or oil-fired storage water heaters, they have a flue damper or fan-assisted combustion. | |||||
| c The compliance date for energy conservation standards for electric instantaneous water heaters is January 1, 1994. | |||||
(b) Each unfired hot water storage tank manufactured on and after October 29, 2003, must have a minimum thermal insulation of R-12.5.
(c) Each residential-duty commercial water heater must meet the applicable energy conservation standard level(s) as follows:
| Equipment | Specifications a | Draw pattern | Uniform energy factor b | |
|---|---|---|---|---|
| Equipment manufactured before October 6, 2026 | Equipment manufactured after October 6, 2026 | |||
| Gas-fired storage | >75 kBtu/hr and ≤105 kBtu/hr and ≤120 gal | Very Small Low Medium High |
0.2674−(0.0009 × Vr) 0.5362−(0.0012 × Vr) 0.6002−(0.0011 × Vr) 0.6597−(0.0009 × Vr) |
0.5374−(0.0009 × Vr) 0.8062−(0.0012 × Vr) 0.8702−(0.0011 × Vr) 0.9297−(0.0009 × Vr) |
| Oil-fired storage | >105 kBtu/hr and ≤140 kBtu/hr and ≤120 gal | Very Small Low Medium High |
0.2932−(0.0015 × Vr) 0.5596−(0.0018 × Vr) 0.6194−(0.0016 × Vr) 0.6470−(0.0013 × Vr) |
0.2932−(0.0015 × Vr) 0.5596−(0.0018 × Vr) 0.6194−(0.0016 × Vr) 0.6470−(0.0013 × Vr) |
| Electric instantaneous | >12 kW and ≤58.6 kW and ≤2 gal | Very Small Low Medium High |
0.80 0.80 0.80 0.80 |
0.80 0.80 0.80 0.80 |
| a Additionally, to be classified as a residential-duty commercial water heater, a commercial water heater must meet the following conditions: (1) If the water heater requires electricity, it must use a single-phase external power supply; and (2) The water heater must not be designed to heat water to temperatures greater than 180 °F. | ||||
| b Vr is the rated storage volume (in gallons), as determined pursuant to 10 CFR 429.44. | ||||
[88 FR 69822, Oct. 6, 2023]
Prior to November 6, 2017, manufacturers must make any representations with respect to the energy use or efficiency of the subject commercial water heating equipment in accordance with the results of testing pursuant to this appendix or the procedures in 10 CFR 431.106 that were in place on January 1, 2016. On and after November 6, 2017, manufacturers must make any representations with respect to energy use or efficiency of gas-fired and oil-fired storage water heaters and storage-type instantaneous water heaters in accordance with the results of testing pursuant to this appendix to demonstrate compliance with the energy conservation standards at 10 CFR 431.110.
1. General
Determine the thermal efficiency and standby loss (as applicable) in accordance with the following sections of this appendix. Certain sections reference sections of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105). Where the instructions contained in the sections below conflict with instructions in Annex E.1 of ANSI Z21.10.3-2015, the instructions contained in this appendix control.
2. Test Set-Up
2.1. Placement of Water Heater. A water heater for installation on combustible floors must be placed on a 3⁄4-inch plywood platform supported by three 2 x 4-inch runners. If the water heater is for installation on noncombustible floors, suitable noncombustible material must be placed on the platform. When the use of the platform for a large water heater is not practical, the water heater may be placed on any suitable flooring. A wall-mounted water heater must be mounted on a simulated wall section.
2.2. Installation of Temperature Sensors. Inlet and outlet water piping must be turned vertically downward from the connections on the water heater so as to form heat traps. Temperature sensors for measuring supply and outlet water temperatures must be installed upstream from the inlet heat trap piping and downstream from the outlet heat trap piping, respectively, in accordance with Figure 2.1, 2.2, or 2.3 (as applicable based on the location of inlet and outlet piping connections) of this section.
The water heater must meet the requirements shown in Figure 2.1, 2.2, or 2.3 (as applicable) at all times during the conduct of the thermal efficiency and standby loss tests. Any factory-supplied heat traps must be installed per the installation instructions while ensuring the requirements in Figure 2.1, 2.2, or 2.3 are met. All dimensions specified in Figure 2.1, 2.2, and 2.3 and in this section are measured from the outer surface of the pipes and water heater outer casing (as applicable).
2.3 Installation of Temperature Sensors for Measurement of Mean Tank Temperature. Install temperature sensors inside the tank for measurement of mean tank temperature according to the instructions in paragraph f of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105). Calculate the mean tank temperature as the average of the six installed temperature sensors.
2.4. Piping Insulation. Insulate all water piping external to the water heater jacket, including heat traps and piping that are installed by the manufacturer or shipped with the unit, for at least 4 ft of piping length from the connection at the appliance, with material having an R-value not less than 4 °F·ft2·h/Btu. Ensure that the insulation does not contact any appliance surface except at the location where the pipe connections penetrate the appliance jacket or enclosure.
2.5. Temperature and Pressure Relief Valve Insulation. If the manufacturer has not provided a temperature and pressure relief valve, one shall be installed and insulated as specified in section 2.4 of this appendix.
2.6. Vent Requirements. Follow the requirements for venting arrangements specified in paragraph c of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105).
2.7. Energy Consumption. Install equipment that determines, within ± 1 percent:
2.7.1. The quantity and rate of fuel consumed.
2.7.2. The quantity of electricity consumed by factory-supplied water heater components.
3. Test Conditions
3.1. Water Supply
3.1.1. Water Supply Pressure. The pressure of the water supply must be maintained between 40 psi and the maximum pressure specified by the manufacturer of the unit being tested. The accuracy of the pressure-measuring devices must be within ± 1.0 pounds per square inch (psi).
3.1.2. Water Supply Temperature. During the steady-state verification period and the thermal efficiency test, the temperature of the supply water must be maintained at 70 °F ± 2 °F.
3.1.3. Isolate the water heater using a shutoff valve in the supply line with an expansion tank installed in the supply line downstream of the shutoff valve. There must be no shutoff means between the expansion tank and the appliance inlet.
3.2. Gas Pressure for Gas-Fired Equipment. The supply gas pressure must be within the range specified by the manufacturer on the nameplate of the unit being tested. The difference between the outlet pressure of the gas appliance pressure regulator and the value specified by the manufacturer on the nameplate of the unit being tested must not exceed the greater of: ± 10 percent of the nameplate value or ± 0.2 inches water column (in. w.c.). Obtain the higher heating value of the gas burned.
3.3. Ambient Room Temperature. During the soak-in period (as applicable), the steady-state verification period, the thermal efficiency test, and the standby loss test, maintain the ambient room temperature at 75 °F ± 10 °F at all times. Measure the ambient room temperature at 1-minute intervals during these periods, except for the soak-in period. Measure the ambient room temperature once before beginning the soak-in period, and ensure no actions are taken during the soak-in period that would cause the ambient room temperature to deviate from the allowable range. Measure the ambient room temperature at the vertical mid-point of the water heater and approximately 2 feet from the water heater jacket. Shield the sensor against radiation. Calculate the average ambient room temperature separately for the thermal efficiency test and standby loss test. During the thermal efficiency and standby loss tests, the ambient room temperature must not vary by more than ± 5.0 °F at any reading from the average ambient room temperature.
3.4. Test Air Temperature. During the steady-state verification period, the thermal efficiency test, and the standby loss test, the test air temperature must not vary by more than ± 5 °F from the ambient room temperature at any reading. Measure the test air temperature at 1-minute intervals during these periods and at a location within two feet of the air inlet of the water heater or the combustion air intake vent, as applicable. Shield the sensor against radiation. For units with multiple air inlets, measure the test air temperature at each air inlet, and maintain the specified tolerance on deviation from the ambient room temperature at each air inlet. For units without a dedicated air inlet, measure the test air temperature within two feet of any location on the water heater where combustion air is drawn.
3.5. Maximum Air Draft. During the steady-state verification period, the thermal efficiency test, and the standby loss test, the water heater must be located in an area protected from drafts of more than 50 ft/min. Prior to beginning the steady-state verification period and the standby loss test, measure the air draft within three feet of the jacket or enclosure of the water heater to ensure this condition is met. Ensure that no other changes that would increase the air draft are made to the test set-up or conditions during the conduct of the tests.
3.6. Setting the Tank Thermostat. Before starting the steady-state verification period (as applicable) or before the soak-in period (as applicable), the thermostat setting must first be obtained by starting with the water in the system at 70 °F ± 2 °F. Set the thermostat to ensure:
3.6.1. With the supply water temperature set as per section 3.1.2 of this appendix (i.e., 70 °F ± 2 °F), the water flow rate can be varied so that the outlet water temperature is constant at 70 °F ± 2 °F above the supply water temperature while the burner is firing at full firing rate; and
3.6.2. After the water supply is turned off and the thermostat reduces the fuel supply to a minimum, the maximum water temperature measured by the topmost tank temperature sensor (i.e., the highest of the 6 temperature sensors used for calculating mean tank temperature, as required by section 2.3 of this appendix) is 140 °F ± 5 °F.
3.7. Additional Requirements for Oil-Fired Equipment.
3.7.1. Venting Requirements. Connect a vertical length of flue pipe to the flue gas outlet of sufficient height so as to meet the minimum draft specified by the manufacturer.
3.7.2. Oil Supply. Adjust the burner rate so that the following conditions are met:
3.7.2.1. The CO2 reading is within the range specified by the manufacturer;
3.7.2.2. The fuel pump pressure is within ± 10 percent of manufacturer's specifications;
3.7.2.3. If either the fuel pump pressure or range for CO2 reading are not specified by the manufacturer on the nameplate of the unit, in literature shipped with the unit, or in supplemental test report instructions included with a certification report, then a default value of 100 psig is to be used for fuel pump pressure, and a default range of 9-12 percent is to be used for CO2 reading; and
3.7.2.4. Smoke in the flue does not exceed No. 1 smoke as measured by the procedure in ASTM D2156-09 (Reapproved 2013) (incorporated by reference, see § 431.105). To determine the smoke spot number, connect the smoke measuring device to an open-ended tube. This tube must project into the flue 1⁄4 to 1⁄2 of the pipe diameter.
3.7.2.5. If no settings on the water heater have been changed and the water heater has not been turned off since the end of a previously run thermal efficiency or standby loss test, measurement of the CO2 reading and conduct of the smoke spot test are not required prior to beginning a test. Otherwise, measure the CO2 reading and determine the smoke spot number, with the burner firing, before the beginning of the steady-state verification period prior to the thermal efficiency test, and prior to beginning the standby loss test.
3.8. Data Collection Intervals. Follow the data recording intervals specified in the following sections.
3.8.1. Soak-In Period. For units that require a soak-in period, measure the ambient room temperature, in °F, prior to beginning the soak-in period.
3.8.2. Steady-State Verification Period and Thermal Efficiency Test. For the steady-state verification period and the thermal efficiency test, follow the data recording intervals specified in Table 3.1 of this appendix.
| Item recorded | Before steady-state verification period |
Every 1 minute a |
Every 10 minutes |
|---|---|---|---|
| Gas supply pressure, in w.c. | X | ||
| Gas outlet pressure, in w.c. | X | ||
| Barometric pressure, in Hg | X | ||
| Fuel higher heating value, Btu/ft3 (gas) or Btu/lb (oil) | X | ||
| Oil pump pressure, psig (oil only) | X | ||
| CO2 reading, % (oil only) | X b | ||
| Oil smoke spot reading (oil only) | X b | ||
| Air draft, ft/min | X | ||
| Time, minutes/seconds | X | ||
| Fuel weight or volume, lb (oil) or ft3 (gas) | X c | ||
| Supply water temperature (TSWT), °F | X | ||
| Outlet water temperature (TOWT), °F | X | ||
| Ambient room temperature, °F | X | ||
| Test air temperature, °F | X | ||
| Water flow rate, (gpm) | X | ||
| Notes: | |||
| a These measurements are to be recorded at the start of the steady-state verification period and the end of the thermal efficiency test, as well as every minute during both periods. | |||
| b The smoke spot test and CO2 reading are not required prior to beginning the steady-state verification period if no settings on the water heater have been changed and the water heater has not been turned off since the end of a previously-run efficiency test (i.e., thermal efficiency or standby loss). | |||
| c Fuel and electricity consumption over the course of the entire thermal efficiency test must be measured and used in calculation of thermal efficiency. | |||
3. 8.3. Standby Loss Test. For the standby loss test, follow the data recording intervals specified in Table 3.2 of this appendix. Additionally, the fuel and electricity consumption over the course of the entire test must be measured and used in calculation of standby loss.
| Item recorded | Before test | Every 1 minute a |
|---|---|---|
| Gas supply pressure, in w.c. | X | |
| Gas outlet pressure, in w.c. | X | |
| Barometric pressure, in Hg | X | |
| Fuel higher heating value, Btu/ft 3 (gas) or Btu/lb (oil) | X | |
| Oil pump pressure, psig (oil only) | X | |
| CO2 reading, % (oil only) | X b | |
| Oil smoke spot reading (oil only) | X b | |
| Air draft, ft/min | X | |
| Time, minutes/seconds | X | |
| Mean tank temperature, °F | X c | |
| Ambient room temperature, °F | X | |
| Test air temperature, °F | X | |
| Notes: | ||
| a These measurements are to be recorded at the start and end of the test, as well as every minute during the test. | ||
| b The smoke spot test and CO2 reading are not required prior to beginning the standby loss test if no settings on the water heater have been changed and the water heater has not been turned off since the end of a previously-run efficiency test (i.e., thermal efficiency or standby loss). | ||
| c Mean tank temperature is calculated as the average of the 6 tank temperature sensors, installed per section 2.3 of this appendix. | ||
4. Determination of Storage Volume. Determine the storage volume by subtracting the tare weight, measured while the system is dry and empty, from the weight of the system when filled with water and dividing the resulting net weight of water by the density of water at the measured water temperature. The volume of the water contained in the water heater must be computed in gallons.
5. Thermal Efficiency Test. Before beginning the steady-state verification period, record the applicable parameters as specified in section 3.8.2 of this appendix. Begin drawing water from the unit by opening the main supply, and adjust the water flow rate to achieve an outlet water temperature of 70 °F ± 2 °F above supply water temperature. The thermal efficiency test shall be deemed complete when there is a continuous, one-hour-long period where the steady-state conditions specified in section 5.1 of this appendix have been met, as confirmed by consecutive readings of the relevant parameters recorded at 1-minute intervals (except for fuel input rate, which is determined at 10-minute intervals, as specified in section 5.4 of this appendix). During the one-hour-long period, the water heater must fire continuously at its full firing rate (i.e., no modulations or cut-outs) and no settings can be changed on the unit being tested at any time. The first 30 minutes of the one-hour-period where the steady-state conditions in section 5.1 of this appendix are met is the steady-state verification period. The final 30 minutes of the one-hour-period where the steady-state conditions in section 5.1 of this appendix are met is the thermal efficiency test. The last reading of the steady-state verification period must be the first reading of the thermal efficiency test (i.e., the thermal efficiency test starts immediately once the steady-state verification period ends).
5.
1. Steady-State Conditions. The following conditions must be met at consecutive readings taken at 1-minute intervals (except for fuel input rate, for which measurements are taken at 10-minute intervals) to verify the water heater has achieved steady-state operation during the steady-state verification period and thermal efficiency test.
5.1.1. The water flow rate must be maintained within ± 0.25 gallons per minute (gpm) of the initial reading at the start of the steady-state verification period;
5.1.2. Outlet water temperature must be maintained at 70 °F ± 2 °F above supply water temperature;
5.1.3. Fuel input rate must be maintained within ± 2 percent of the rated input certified by the manufacturer;
5.1.4. The supply water temperature must be maintained within ± 0.50 °F of the initial reading at the start of the steady-state verification period; and
5.1.5. The rise between the supply and outlet water temperatures must be maintained within ± 0.50 °F of its initial value taken at the start of the steady-state verification period for units with rated input less than 500,000 Btu/h, and maintained within ± 1.00 °F of its initial value for units with rated input greater than or equal to 500,000 Btu/h.
5.2. Water Flow Measurement. Measure the total weight of water heated during the 30-minute thermal efficiency test with either a scale or a water flow meter. With either method, the error of measurement of weight of water heated must not exceed 1 percent of the weight of the total draw.
5. 3. Determination of Fuel Input Rate. During the steady-state verification period and the thermal efficiency test, record the fuel consumed at 10-minute intervals. Calculate the fuel input rate over each 10-minute period using the equations in section 5.4 of this appendix. The measured fuel input rates for these 10-minute periods must not vary by more than ± 2 percent between any two readings. Determine the overall fuel input rate using the fuel consumption for the entire duration of the thermal efficiency test.
5. 4. Fuel Input Rate Calculation. To calculate the fuel input rate, use the following equation:
Where,
Q = Fuel input rate, expressed in Btu/h
Qs = Total fuel flow as metered, expressed in ft3 for gas-fired equipment and lb for oil-fired equipment
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment.
H = Higher heating value of fuel, expressed in Btu/ft3 for gas-fired equipment and Btu/lb for oil-fired equipment.
t = Duration of measurement of fuel consumption
5. 5. Thermal Efficiency Calculation. Thermal efficiency must be calculated using data from the 30-minute thermal efficiency test. Calculate thermal efficiency, Et, using the following equation:
Where,
K = 1.004 Btu/lb· °F, the nominal specific heat of water at 105 °F
W = Total weight of water heated, expressed in lb
θ1 = Average supply water temperature, expressed in °F
θ2 = Average outlet water temperature, expressed in °F
Q = Total fuel flow as metered, expressed in ft3 for gas-fired equipment and lb for oil-fired equipment.
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment
H. = Higher heating value of the fuel, expressed in Btu/ft3 for gas-fired equipment and Btu/lb for oil-fired equipment.
Ec = Electrical consumption of the water heater and, when used, the test set-up recirculating pump, expressed in Btu
6. Standby Loss Test
6.1. If no settings on the water heater have changed and the water heater has not been turned off since a previously run thermal efficiency or standby loss test, skip to section 6.3 of this appendix. Otherwise, conduct the soak-in period according to section 6.2 of this appendix.
6.2. Soak-In Period. Conduct a soak-in period, in which the water heater must sit without any draws taking place for at least 12 hours. Begin the soak-in period after setting the tank thermostat as specified in section 3.6 of this appendix, and maintain these thermostat settings throughout the soak-in period.
6.3. Begin the standby loss test at the first cut-out following the end of the soak-in period (if applicable); or at a cut-out following the previous thermal efficiency or standby loss test (if applicable). Allow the water heater to remain in standby mode. Do not change any settings on the water heater at any point until measurements for the standby loss test are finished. Begin recording the applicable parameters specified in section 3.8.3 of this appendix.
6. 4. At the second cut-out, record the time and ambient room temperature, and begin measuring the fuel and electricity consumption. Record the initial mean tank temperature and initial ambient room temperature. For the remainder of the test, continue recording the applicable parameters specified in section 3.8.3 of this appendix.
6. 5. Stop the test after the first cut-out that occurs after 24 hours, or at 48 hours, whichever comes first.
6. 6. Immediately after conclusion of the standby loss test, record the total fuel flow and electrical energy consumption, the final ambient room temperature, the duration of the standby loss test, and if the test ends at 48 hours without a cut-out, the final mean tank temperature, or if the test ends after a cut-out, the maximum mean tank temperature that occurs after the cut-out. Calculate the average of the recorded values of the mean tank temperature and of the ambient room temperature taken at each measurement interval, including the initial and final values.
6. 7. Standby Loss Calculation. To calculate the standby loss, follow the steps below:
6. 7.1. The standby loss expressed as a percentage (per hour) of the heat content of the stored water above room temperature must be calculated using the following equation:
Where,
ΔT3 = Average value of the mean tank temperature minus the average value of the ambient room temperature, expressed in °F
ΔT4 = Final mean tank temperature measured at the end of the test minus the initial mean tank temperature measured at the start of the test , expressed in °F
k = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency of the water heater determined in accordance with this appendix, expressed in %
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
t = Total duration of the test in hours
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment.
Qs = Total fuel flow as metered, expressed in ft3 (gas) or lb (oil)
H = Higher heating value of fuel, expressed in Btu/ft3 (gas) or Btu/lb (oil)
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the heat content of the stored water above room temperature
6.7.2. The standby loss expressed in Btu per hour must be calculated as follows:
SL (Btu per hour) = S (% per hour) × 8.25 (Btu/gal- °F) × Measured Volume (gal) × 70 ( °F).
Where, SL refers to the standby loss of the water heater, defined as the amount of energy required to maintain the stored water temperature expressed in Btu per hour
[81 FR 79323, Nov. 10, 2016]
Note: Prior to November 6, 2017, manufacturers must make any representations with respect to the energy use or efficiency of the subject commercial water heating equipment in accordance with the results of testing pursuant to this appendix or the procedures in 10 CFR 431.106 that were in place on January 1, 2016. On and after November 6, 2017, manufacturers must make any representations with respect to energy use or efficiency of electric storage water heaters and storage-type instantaneous water heaters in accordance with the results of testing pursuant to this appendix to demonstrate compliance with the energy conservation standards at 10 CFR 431.110.
1. General
Determine the standby loss in accordance with the following sections of this appendix. Certain sections reference sections of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105). Where the instructions contained in the sections below conflict with instructions in Annex E.1 of ANSI Z21.10.3-2015, the instructions contained in this appendix control.
2. Test Set-Up
2.1. Placement of Water Heater. A water heater for installation on combustible floors must be placed on a 3⁄4-inch plywood platform supported by three 2 × 4-inch runners. If the water heater is for installation on noncombustible floors, suitable noncombustible material must be placed on the platform. When the use of the platform for a large water heater is not practical, the water heater may be placed on any suitable flooring. A wall-mounted water heater must be mounted on a simulated wall section.
2.2. Installation of Temperature Sensors. Inlet and outlet piping must be turned vertically downward from the connections on a tank-type water heater so as to form heat traps. Temperature sensors for measuring supply water temperature must be installed upstream of the inlet heat trap piping, in accordance with Figure 2.1, 2.2, or 2.3 (as applicable) of this appendix.
The water heater must meet the requirements shown in either Figure 2.1, 2.2, or 2.3 (as applicable) at all times during the conduct of the standby loss test. Any factory-supplied heat traps must be installed per the installation instructions while ensuring the requirements in Figure 2.1, 2.2, or 2.3 are met. All dimensions specified in Figure 2.1, 2.2, and 2.3 are measured from the outer surface of the pipes and water heater outer casing (as applicable).
2.3. Installation of Temperature Sensors for Measurement of Mean Tank Temperature. Install temperature sensors inside the tank for measurement of mean tank temperature according to the instructions in paragraph f of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105 rt). Calculate the mean tank temperature as the average of the six installed temperature sensors.
2.4. Piping Insulation. Insulate all water piping external to the water heater jacket, including heat traps and piping that is installed by the manufacturer or shipped with the unit, for at least 4 ft of piping length from the connection at the appliance, with material having an R-value not less than 4 °F·ft2·h/Btu. Ensure that the insulation does not contact any appliance surface except at the location where the pipe connections penetrate the appliance jacket or enclosure.
2.5. Temperature and Pressure Relief Valve Insulation. If the manufacturer or has not provided a temperature and pressure relief valve, one shall be installed and insulated as specified in section 2.4 of this appendix.
2.6. Energy Consumption. Install equipment that determines, within ± 1 percent, the quantity of electricity consumed by factory-supplied water heater components.
3. Test Conditions
3.1. Water Supply
3.1.1. Water Supply Pressure. The pressure of the water supply must be maintained between 40 psi and the maximum pressure specified by the manufacturer of the unit being tested. The accuracy of the pressure-measuring devices must be within ± 1.0 pounds per square inch (psi).
3.1.2. Water Supply Temperature. When filling the tank with water prior to the soak-in period, maintain the supply water temperature at 70 °F ± 2 °F.
3.1.3. Isolate the water heater using a shutoff valve in the supply line with an expansion tank installed in the supply line downstream of the shutoff valve. There must be no shutoff means between the expansion tank and the appliance inlet.
3.2. Electrical Supply. Maintain the electrical supply voltage to within ± 5 percent of the voltage specified on the water heater nameplate. If a voltage range is specified on the nameplate, maintain the voltage to within ± 5 percent of the center of the voltage range specified on the nameplate.
3.3. Ambient Room Temperature. During the soak-in period and the standby loss test, maintain the ambient room temperature at 75 °F ± 10 °F at all times. Measure the ambient room temperature at 1-minute intervals during these periods, except for the soak-in period. Measure the ambient room temperature once before beginning the soak-in period, and ensure no actions are taken during the soak-in period that would cause the ambient room temperature to deviate from the allowable range. Measure the ambient room temperature at the vertical mid-point of the water heater and approximately 2 feet from the water heater jacket. Shield the sensor against radiation. Calculate the average ambient room temperature for the standby loss test. During the standby loss test, the ambient room temperature must not vary by more than ± 5.0 °F at any reading from the average ambient room temperature.
3.4. Maximum Air Draft. During the standby loss test, the water heater must be located in an area protected from drafts of more than 50 ft/min. Prior to beginning the standby loss test, measure the air draft within three feet of the jacket of the water heater to ensure this condition is met. Ensure that no other changes that would increase the air draft are made to the test set-up or conditions during the conduct of the test.
3.5. Setting the Tank Thermostat(s). Before starting the required soak-in period, the thermostat setting(s) must first be obtained as explained in the following sections. The thermostat setting(s) must be obtained by starting with the tank full of water at 70 °F ± 2 °F. After the tank is completely filled with water at 70 °F ± 2 °F, turn off the water flow, and set the thermostat(s) as follows.
3.5.1. For water heaters with a single thermostat, the thermostat setting must be set so that the maximum mean tank temperature after cut-out is 140 °F ± 5 °F.
3.5.2. For water heaters with multiple adjustable thermostats, set only the topmost and bottommost thermostats, and turn off any other thermostats for the duration of the standby loss test. Set the topmost thermostat first to yield a maximum mean water temperature after cut-out of 140 °F ± 5 °F, as calculated using only the temperature readings measured at locations in the tank higher than the heating element corresponding to the topmost thermostat (the lowermost heating element corresponding to the topmost thermostat if the thermostat controls more than one element). While setting the topmost thermostat, all lower thermostats must be turned off so that no elements below that (those) corresponding to the topmost thermostat are in operation. After setting the topmost thermostat, set the bottommost thermostat to yield a maximum mean water temperature after cut-out of 140 °F ± 5 °F. When setting the bottommost thermostat, calculate the mean tank temperature using all the temperature sensors installed in the tank as per section 2.3 of this appendix.
3.6. Data Collection Intervals. Follow the data recording intervals specified in the following sections.
3.6.1. Soak-In Period. Measure the ambient room temperature, in °F, every minute during the soak-in period.
3.6.2. Standby Loss Test. Follow the data recording intervals specified in Table 3.1 of this appendix. Additionally, the electricity consumption over the course of the entire test must be measured and used in calculation of standby loss.
| Item recorded | Before test | Every 1 minute a |
|---|---|---|
| Air draft, ft/min | X | |
| Time, minutes/seconds | X | |
| Mean tank temperature, °F | X b | |
| Ambient room temperature, °F | X | |
| Notes: | ||
| a These measurements are to be recorded at the start and end of the test, as well as every minute during the test. | ||
| b Mean tank temperature is calculated as the average of the 6 tank temperature sensors, installed per section 2.3 of this appendix. | ||
4. Determination of Storage Volume. Determine the storage volume by subtracting the tare weight, measured while the system is dry and empty, from the weight of the system when filled with water and dividing the resulting net weight of water by the density of water at the measured water temperature. The volume of water contained in the water heater must be computed in gallons.
5. Standby Loss Test
5.1. If no settings on the water heater have changed and the water heater has not been turned off since a previously run standby loss test, skip to section 5.3 of this appendix. Otherwise, conduct the soak-in period according to section 5.2 of this appendix.
5.2. Soak-In Period. Conduct a soak-in period, in which the water heater must sit without any draws taking place for at least 12 hours. Begin the soak-in period after setting the tank thermostat(s) as specified in section 3.5 of this appendix, and maintain these settings throughout the soak-in period.
5.3. Begin the standby loss test at the first cut-out following the end of the soak-in period (if applicable), or at a cut-out following the previous standby loss test (if applicable). Allow the water heater to remain in standby mode. At this point, do not change any settings on the water heater until measurements for the standby loss test are finished. Begin recording applicable parameters as specified in section 3.6.2 of this appendix.
5.4. At the second cut-out, record the time and ambient room temperature, and begin measuring the electric consumption. Record the initial mean tank temperature and initial ambient room temperature. For the remainder of the test, continue recording the applicable parameters specified in section 3.6.2 of this appendix.
5.5. Stop the test after the first cut-out that occurs after 24 hours, or at 48 hours, whichever comes first.
5.6. Immediately after conclusion of the standby loss test, record the total electrical energy consumption, the final ambient room temperature, the duration of the standby loss test, and if the test ends at 48 hours without a cut-out, the final mean tank temperature, or if the test ends after a cut-out, the maximum mean tank temperature that occurs after the cut-out. Calculate the average of the recorded values of the mean tank temperature and of the ambient air temperatures taken at each measurement interval, including the initial and final values.
5.7. Standby Loss Calculation. To calculate the standby loss, follow the steps below:
5.7.1 The standby loss expressed as a percentage (per hour) of the heat content of the stored water above room temperature must be calculated using the following equation:
Where,
ΔT3 = Average value of the mean tank temperature minus the average value of the ambient room temperature, expressed in °F
ΔT4 = Final mean tank temperature measured at the end of the test minus the initial mean tank temperature measured at the start of the test, expressed in °F
k = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency = 98 percent for electric water heaters with immersed heating elements
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
t = Total duration of the test in hours
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the heat content of the stored water above room temperature
[81 FR 79328, Nov. 10, 2016]
Prior to November 6, 2017, manufacturers must make any representations with respect to the energy use or efficiency of the subject commercial water heating equipment in accordance with the results of testing pursuant to this appendix or the procedures in 10 CFR 431.106 that were in place on January 1, 2016. On and after November 6, 2017, manufacturers must make any representations with respect to energy use or efficiency of gas-fired and oil-fired instantaneous water heaters and hot water supply boilers (other than storage-type instantaneous water heaters) in accordance with the results of testing pursuant to this appendix to demonstrate compliance with the energy conservation standards at 10 CFR 431.110.
1. General
Determine the thermal efficiency and standby loss (as applicable) in accordance with the following sections of this appendix. Certain sections reference sections of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105). Where the instructions contained in the sections below conflict with instructions in Annex E.1 of ANSI Z21.10.3-2015, the instructions contained in this appendix control.
2. Test Set-Up
2.
1. Placement of Water Heater. A water heater for installation on combustible floors must be placed on a 3⁄4-inch plywood platform supported by three 2 x 4-inch runners. If the water heater is for installation on noncombustible floors, suitable noncombustible material must be placed on the platform. When the use of the platform for a large water heater is not practical, the water heater may be placed on any suitable flooring. A wall-mounted water heater must be mounted on a simulated wall section.
2.
2. Test Configuration. If the instantaneous water heater or hot water supply boiler is not required to be tested using a recirculating loop, then set up the unit in accordance with Figures 2.1, 2.2, or 2.3 of this appendix (as applicable). If the unit is required to be tested using a recirculating loop, then set up the unit as per Figure 2.4 of this appendix.
2.2.1. If the instantaneous water heater or hot water supply boiler does not have any external piping, install an outlet water valve within 10 inches of piping length of the water heater jacket or enclosure. If the instantaneous water heater or hot water supply boiler includes external piping assembled at the manufacturer's premises prior to shipment, install water valves in the outlet piping within 5 inches of the end of the piping supplied with the unit.
2. 2.2. If the water heater is not able to achieve an outlet water temperature of 70 °F ± 2 °F (TOWT) above the supply water temperature at full firing rate, a recirculating loop with pump as shown in Figure 2.4 of this appendix must be used.
2.2.2.1. If a recirculating loop with a pump is used, then ensure that the inlet water temperature labeled as TIWT in Figure 2.4 of this appendix, is greater than or equal to 70 °F and less than or equal to 120 °F at all times during the thermal efficiency test and steady-state verification period (as applicable).
2.3. Installation of Temperature Sensors
2.3.1. Without Recirculating Loop.
2.3.1.1. Vertical Connections. Use Figure 2.1 (for top connections) and 2.2 (for bottom connections) of this appendix.
2.3.1.2. Horizontal Connections. Use Figure 2.3 of this appendix.
2.3.2. With Recirculating Loop. Set up the recirculating loop as shown in Figure 2.4 of this appendix.
2.3.3. For water heaters with multiple outlet water connections leaving the water heater jacket that are required to be operated to achieve the rated input, temperature sensors must be installed for each outlet water connection leaving the water heater jacket or enclosure that is used during testing, in accordance with the provisions in sections 2.3.1 and 2.3.2 of this appendix (as applicable).
2. 4. Piping Insulation. Insulate all water piping external to the water heater jacket or enclosure, including piping that is installed by the manufacturer or shipped with the unit, for at least 4 ft of piping length from the connection at the appliance with material having an R-value not less than 4 °F·ft2·h/Btu. Ensure that the insulation does not contact any appliance surface except at the location where the pipe connections penetrate the appliance jacket or enclosure.
2.5. Temperature and Pressure Relief Valve Insulation. If the manufacturer has not provided a temperature and pressure relief valve, one shall be installed and insulated as specified in section 2.4 of this appendix. The temperature and pressure relief valve must be installed in the outlet water piping, between the unit being tested and the outlet water valve.
2. 6. Vent Requirements. Follow the requirements for venting arrangements specified in paragraph c of Annex E.1 of ANSI Z21.10.3-2015 (incorporated by reference; see § 431.105).
2. 7. Energy Consumption. Install equipment that determines, within ± 1 percent:
2. 7.1. The quantity and rate of fuel consumed.
2.7.2. The quantity of electricity consumed by factory-supplied water heater components, and of the test loop recirculating pump, if used.
3. Test Conditions
3.1. Water Supply
3.1.1. Water Supply Pressure. The pressure of the water supply must be maintained between 40 psi and the maximum pressure specified by the manufacturer of the unit being tested. The accuracy of the pressure-measuring devices must be within ± 1.0 psi.
3. 1.2. Water Supply Temperature. During the thermal efficiency test and steady-state verification period (as applicable), the temperature of the supply water (TSWT) must be maintained at 70 °F ± 2 °F.
3.
2. Gas Pressure for Gas-Fired Equipment. The supply gas pressure must be within the range specified by the manufacturer on the nameplate of the unit being tested. The difference between the outlet pressure of the gas appliance pressure regulator and the value specified by the manufacturer on the nameplate of the unit being tested must not exceed the greater of: ± 10 percent of the nameplate value or ± 0.2 inches water column (in. w.c.). Obtain the higher heating value of the gas burned.
3.3. Ambient Room Temperature. Maintain the ambient room temperature at 75 °F ± 10 °F at all times during the steady-state verification period, the thermal efficiency test, and the standby loss test (as applicable). Measure the ambient room temperature at 1-minute intervals during these periods. Measure the ambient room temperature at the vertical mid-point of the water heater and approximately 2 feet from the water heater jacket or enclosure. Shield the sensor against radiation. Calculate the average ambient room temperature separately for the thermal efficiency test and the standby loss test. During the thermal efficiency and standby loss tests, the ambient room temperature must not vary by more than ± 5.0 °F at any reading from the average ambient room temperature.
3.4. Test Air Temperature. During the steady-state verification period, the thermal efficiency test, and the standby loss test (as applicable), the test air temperature must not vary by more than ± 5 °F from the ambient room temperature at any reading. Measure the test air temperature at 1-minute intervals during these periods and at a location within two feet of the air inlet of the water heater or the combustion air intake vent, as applicable. Shield the sensor against radiation. For units with multiple air inlets, measure the test air temperature at each air inlet, and maintain the specified tolerance on deviation from the ambient room temperature at each air inlet. For units without a dedicated air inlet, measure the test air temperature within two feet of any location on the water heater where combustion air is drawn.
3. 5. Maximum Air Draft. During the steady-state verification period, the thermal efficiency test, and the standby loss test (as applicable), the water heater must be located in an area protected from drafts of more than 50 ft/min. Prior to beginning the steady-state verification period and the standby loss test, measure the air draft within three feet of the jacket or enclosure of the water heater to ensure this condition is met. Ensure that no other changes that would increase the air draft are made to the test set-up or conditions during the conduct of the tests.
3.6. Primary Control
3.6.1. Thermostatically-Activated Water Heaters With an Internal Thermostat. Before starting the thermal efficiency test and the standby loss test (unless the thermostat is already set before the thermal efficiency test), the thermostat setting must be obtained. Set the thermostat to ensure:
3.6.1.1. With supply water temperature set as per section 3.1.2 of this appendix (i.e., 70 °F ± 2 °F) the water flow rate can be varied so that the outlet water temperature is constant at 70 °F ± 2 °F above the supply water temperature, while the burner is firing at full firing rate; and
3.6.1.2. After the water supply is turned off and the thermostat reduces the fuel supply to a minimum, the maximum heat exchanger outlet water temperature (TOHX) is 140 °F ± 5 °F.
3.6.1.3. If the water heater includes a built-in safety mechanism that prevents it from achieving a heat exchanger outlet water temperature of 140 °F ± 5 °F, adjust the thermostat to its maximum setting.
3.6.2. Flow-Activated Instantaneous Water Heaters and Thermostatically-Activated Instantaneous Water Heaters With an External Thermostat. Energize the primary control such that it is always calling for heating and the burner is firing at the full firing rate. Maintain the supply water temperature as per section 3.1.2 of this appendix (i.e., 70 °F ± 2 °F). Set the control so that the outlet water temperature (TOWT) is 140 °F ± 5 °F. If the water heater includes a built-in safety mechanism that prevents it from achieving a heat exchanger outlet water temperature of 140 °F ± 5 °F, adjust the control to its maximum setting.
3.7. Units With Multiple Outlet Water Connections
3.7.1. For each connection leaving the water heater that is required for the unit to achieve the rated input, the outlet water temperature must not differ from that of any other outlet water connection by more than 2 °F during the steady-state verification period and thermal efficiency test.
3.7.2. Determine the outlet water temperature representative for the entire unit at every required measurement interval by calculating the average of the outlet water temperatures measured at each connection leaving the water heater jacket or enclosure that is used during testing. Use the outlet water temperature representative for the entire unit in all calculations for the thermal efficiency and standby loss tests, as applicable.
3.8. Additional Requirements for Oil-Fired Equipment.
3. 8.1. Venting Requirements. Connect a vertical length of flue pipe to the flue gas outlet of sufficient height so as to meet the minimum draft specified by the manufacturer.
3.8.2. Oil Supply. Adjust the burner rate so that the following conditions are met:
3.8.2.1. The CO2 reading is within the range specified by the manufacturer;
3.8.2.2. The fuel pump pressure is within ± 10 percent of manufacturer's specifications;
3.8.2.3. If either the fuel pump pressure or range for CO2 reading are not specified by the manufacturer on the nameplate of the unit, in literature shipped with the unit, or in supplemental test report instructions included with a certification report, then a default value of 100 psig is to be used for fuel pump pressure, and a default range of 9-12 percent is to be used for CO2 reading; and
3.8.2.4. Smoke in the flue does not exceed No. 1 smoke as measured by the procedure in ASTM D2156-09 (Reapproved 2013) (incorporated by reference, see § 431.105). To determine the smoke spot number, the smoke measuring device shall be connected to an open-ended tube. This tube must project into the flue 1⁄4 to 1⁄2 of the pipe diameter.
3.8.2.5. If no settings on the water heater have been changed and the water heater has not been turned off since the end of a previously run thermal efficiency (or standby loss test for thermostatically-activated instantaneous water heaters with an internal thermostat), measurement of the CO2 reading and conduct of the smoke spot test are not required prior to beginning a test. Otherwise, measure the CO2 reading and determine the smoke spot number, with the burner firing, before beginning measurements for the steady-state verification period (prior to beginning the thermal efficiency test or standby loss test, as applicable). However, measurement of the CO2 reading and conduct of the smoke spot test are not required for the standby loss test for thermostatically-activated instantaneous water heaters with an external thermostat and flow-activated instantaneous water heaters.
3. 9. Data Collection Intervals. Follow the data recording intervals specified in the following sections.
3. 9.1. Steady-State Verification Period and Thermal Efficiency Test. For the steady-state verification period and the thermal efficiency test, follow the data recording intervals specified in Table 3.1 of this appendix. These data recording intervals must also be followed if conducting a steady-state verification period prior to conducting the standby loss test.
| Item recorded | Before steady-state verification period |
Every 1 minute a |
Every 10 minutes |
|---|---|---|---|
| Gas supply pressure, in w.c. | X | ||
| Gas outlet pressure, in w.c. | X | ||
| Barometric pressure, in Hg | X | ||
| Fuel higher heating value, Btu/ft 3 (gas) or Btu/lb (oil) | X | ||
| Oil pump pressure, psig (oil only) | X | ||
| CO2 reading, % (oil only) | X b | ||
| Oil smoke spot reading (oil only) | X b | ||
| Air draft, ft/min | X | ||
| Time, minutes/seconds | X | ||
| Fuel weight or volume, lb (oil) or ft 3 (gas) | Xc | ||
| Supply water temperature (TSWT), °F | X | ||
| Inlet water temperature (TIWT), °F | X d | ||
| Outlet water temperature (TOWT), °F | X | ||
| Ambient room temperature, °F | X | ||
| Test air temperature, °F | X | ||
| Water flow rate, gpm | X | ||
| Notes: | |||
| a These measurements are to be recorded at the start and end of both the steady-state verification period and the thermal efficiency test, as well as every minute during both periods. | |||
| b The smoke spot test and CO2 reading are not required prior to beginning the steady-state verification period if no settings on the water heater have been changed and the water heater has not been turned off since the end of a previously-run efficiency test (i.e., thermal efficiency or standby loss). | |||
| c Fuel and electricity consumption over the course of the entire thermal efficiency test must be measured and used in calculation of thermal efficiency. | |||
| d Only measured when a recirculating loop is used. | |||
3.9.2. Standby Loss Test. For the standby loss test, follow the data recording intervals specified in Table 3.2 of this appendix. (Follow the data recording intervals specified in Table 3.1 of this appendix of the steady-state verification period, if conducted prior to the standby loss test.) Additionally, the fuel and electricity consumption over the course of the entire test must be measured and used in calculation of standby loss.
| Item recorded | Before test | Every 1 minute a |
|---|---|---|
| Gas supply pressure, in w.c. | X | |
| Gas outlet pressure, in w.c. | X | |
| Barometric pressure, in Hg | X | |
| Fuel higher heating value, Btu/ft 3 (gas) or Btu/lb (oil) | X | |
| Oil pump pressure, psig (oil only) | X | |
| Air draft, ft/min | X | |
| Time, minutes/seconds | X | |
| Heat exchanger outlet water temperature (TOHX), °F | X | |
| Ambient room temperature, °F | X | |
| Test air temperature, °F | X | |
| Water flow rate, gpm | X b | |
| Inlet water temperature (TIWT), °F | X b | |
| Notes: | ||
| a These measurements are to be recorded at the start and end of the test, as well as every minute during the test. | ||
| b The water flow rate and supply water temperature and inlet water temperature (if a recirculating loop is used) must be measured during the steady-state verification period at 1-minute intervals. After the steady-state verification period ends, flow rate, supply water temperature, and inlet water temperature (if measured) are not required to be measured during the standby loss test, as there is no flow occurring during the standby loss test. | ||
4. Determination of Storage Volume. Determine the storage volume by subtracting the tare weight, measured while the system is dry and empty, from the weight of the system when filled with water and dividing the resulting net weight of water by the density of water at the measured water temperature. The volume of water contained in the water heater must be computed in gallons.
5. Fuel Input Rate
5.1. Determination of Fuel Input Rate. During the steady-state verification period and thermal efficiency test, as applicable, record the fuel consumption at 10-minute intervals. Calculate the fuel input rate for each 10-minute period using the equations in section 5.2 of this appendix. The measured fuel input rates for these 10-minute periods must not vary by more than ± 2 percent between any two readings. Determine the overall fuel input rate using the fuel consumption for the entire duration of the thermal efficiency test.
5.2. Fuel Input Rate Calculation. To calculate the fuel input rate, use the following equation:
Where:
Q = Fuel input rate, expressed in Btu/h
Qs = Total fuel flow as metered, expressed in ft3 for gas-fired equipment and lb for oil-fired equipment
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment.
H = Higher heating value of the fuel, expressed as Btu/ft3 for gas-fired equipment and Btu/lb for oil-fired equipment.
t = Duration of measurement of fuel consumption
6. Thermal Efficiency Test. Before beginning the steady-state verification period, record the applicable parameters as specified in section 3.9.1 of this appendix. Begin drawing water from the unit by opening the main supply and outlet water valve, and adjust the water flow rate to achieve an outlet water temperature of 70 °F ± 2 °F above supply water temperature. The thermal efficiency test shall be deemed complete when there is a continuous, one-hour-long period where the steady-state conditions specified in section 6.1 of this appendix have been met, as confirmed by consecutive readings of the relevant parameters at 1-minute intervals (except for fuel input rate, which is determined at 10-minute intervals, as specified in section 5.1 of this appendix). During the one-hour-long period, the water heater must fire continuously at its full firing rate (i.e., no modulation or cut-outs) and no settings can be changed on the unit being tested at any time. The first 30 minutes of the one-hour-period where the steady-state conditions in section 6.1 of this appendix are met is the steady-state verification period. The final 30 minutes of the one-hour-period where the steady-state conditions in section 6.1 of this appendix are met is the thermal efficiency test. The last reading of the steady-state verification period must be the first reading of the thermal efficiency test (i.e., the thermal efficiency test starts immediately once the steady-state verification period ends).
6.1. Steady-State Conditions. The following conditions must be met at consecutive readings taken at 1-minute intervals (except for fuel input rate, for which measurements are taken at 10-minute intervals) to verify the water heater has achieved steady-state operation during the steady-state verification period and the thermal efficiency test.
6.1.1. The water flow rate must be maintained within ± 0.25 gallons per minute (gpm) of the initial reading at the start of the steady-state verification period.
6.1.2. Outlet water temperature must be maintained at 70 °F ± 2 °F above supply water temperature.
6.1.3. Fuel input rate must be maintained within ± 2 percent of the rated input certified by the manufacturer.
6.1.4. The supply water temperature (TSWT) (or inlet water temperature (TIWT) if a recirculating loop is used) must be maintained within ± 0.50 °F of the initial reading at the start of the steady-state verification period.
6.1.5. The rise between supply (or inlet if a recirculating loop is used) and outlet water temperatures must be maintained within ± 0.50 °F of its initial value taken at the start of the steady-state verification period for units with rated input less than 500,000 Btu/h, and maintained within ± 1.00 °F of its initial value for units with rated input greater than or equal to 500,000 Btu/h.
6.2. Water Flow Measurement. Measure the total weight of water heated during the 30-minute thermal efficiency test with either a scale or a water flow meter. With either method, the error of measurement of weight of water heated must not exceed 1 percent of the weight of the total draw.
6.3. Thermal Efficiency Calculation. Thermal efficiency must be calculated using data from the 30-minute thermal efficiency test. Calculate thermal efficiency, Et, using the following equation:
Where:
K = 1.004 Btu/lb· °F, the nominal specific heat of water at 105 °F
W = Total weight of water heated, lb
θ1 = Average supply water temperature, expressed in °F
θ2 = Average outlet water temperature, expressed in °F
Q = Total fuel flow as metered, expressed in ft3 (gas) or lb (oil)
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment.
H = Higher heating value of the fuel, expressed in Btu/ft3 (gas) or Btu/lb (oil)
Ec = Electrical consumption of the water heater and, when used, the test set-up recirculating pump, expressed in Btu
7. Standby Loss Test. If the standby loss test is conducted immediately after a thermal efficiency test and no settings or conditions have been changed since the completion of the thermal efficiency test, then skip to section 7.2 or 7.3 of this appendix (as applicable). Otherwise, perform the steady-state verification in section 7.1 of this appendix. For thermostatically-activated instantaneous water heaters with an internal thermostat, use section 7.2 of this appendix to conduct the standby loss test, and for flow-activated and/or thermostatically-activated instantaneous water heaters with an external thermostat use section 7.3 of this appendix to conduct the standby loss test.
7.1. Steady-State Verification Period. For water heaters where the standby loss test is not conducted immediately following the thermal efficiency test, the steady-state verification period must be conducted before starting the standby loss test. Set the primary control in accordance with section 3.6 of this appendix, such that the primary control is always calling for heat and the water heater is firing continuously at the full firing rate (i.e., no modulation or cut-outs). Begin drawing water from the unit by opening the main supply and the outlet water valve, and adjust the water flow rate to achieve an outlet water temperature of 70 °F ± 2 °F above supply water temperature. The steady-state verification period is complete when there is a continuous 30-minute period where the steady-state conditions specified in section 7.1.1 of this appendix are met, as confirmed by consecutive readings of the relevant parameters recorded at 1-minute intervals (except for fuel input rate, which is determined at 10-minute intervals, as specified in section 5.1 of this appendix).
7.1.1. Steady-State Conditions. The following conditions must be met at consecutive readings taken at 1-minute intervals (except for fuel input rate, for which measurements are taken at 10-minute intervals) to verify the water heater has achieved steady-state operation during the steady-state verification period prior to conducting the standby loss test.
7.1.1.1. The water flow rate must be maintained within ± 0.25 gallons per minute (gpm) of the initial reading at the start of the steady-state verification period;
7.1.1.2. Fuel input rate must be maintained within ± 2 percent of the rated input certified by the manufacturer;
7.1.1.3. The supply water temperature (TSWT) (or inlet water temperature (TIWT) if a recirculating loop is used) must be maintained within ± 0.50 °F of the initial reading at the start of the steady-state verification period; and
7.1.1.4. The rise between the supply (or inlet if a recirculating loop is used) and outlet water temperatures must be maintained within ± 0.50 °F of its initial value taken at the start of the steady-state verification period for units with rated input less than 500,000 Btu/h, and maintained within ± 1.00 °F of its initial value for units with rated input greater than or equal to 500,000 Btu/h.
7.2. Thermostatically-Activated Instantaneous Water Heaters with an Internal Thermostat. For water heaters that will experience cut-in based on a temperature-activated control that is internal to the water heater, use the following steps to conduct the standby loss test.
7.2.1. Immediately after the thermal efficiency test or the steady-state verification period (as applicable), turn off the outlet water valve(s) (installed as per the provisions in section 2.2 of this appendix), and the water pump (if applicable) simultaneously and ensure that there is no flow of water through the water heater.
7. 2.2. After the first cut-out following the end of the thermal efficiency test or steady-state verification period (as applicable), allow the water heater to remain in standby mode. Do not change any settings on the water heater at any point until measurements for the standby loss test are finished. Begin recording the applicable parameters specified in section 3.9.2 of this appendix.
7. 2.3. At the second cut-out, record the time and ambient room temperature, and begin measuring the fuel and electricity consumption. Record the initial heat exchanger outlet water temperature (TOHX) and initial ambient room temperature. For the remainder of the test, continue recording the applicable parameters specified in section 3.9.2 of this appendix.
7. 2.4. Stop the test after the first cut-out that occurs after 24 hours, or at 48 hours, whichever comes first.
7. 2.5. Immediately after conclusion of the standby loss test, record the total fuel flow and electrical energy consumption, the final ambient room temperature, the duration of the standby loss test, and if the test ends at 48 hours without a cut-out, the final heat exchanger outlet temperature, or if the test ends after a cut-out, the maximum heat exchanger outlet temperature that occurs after the cut-out. Calculate the average of the recorded values of the heat exchanger outlet water temperature and the ambient room temperature taken at each measurement interval, including the initial and final values.
7. 2.6. Standby Loss Calculation. To calculate the standby loss, follow the steps below:
7. 2.6.1. The standby loss expressed as a percentage (per hour) of the heat content of the stored water above room temperature must be calculated using the following equation:
Where:
ΔT3 = Average value of the heat exchanger outlet water temperature (TOHX) minus the average value of the ambient room temperature, expressed in °F
ΔT4 = Final heat exchanger outlet water temperature (TOHX) measured at the end of the test minus the initial heat exchanger outlet water temperature (TOHX) measured at the start of the test, expressed in °F
K = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency of the water heater determined in accordance with section 6 of this appendix, expressed in %
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
T = Total duration of the test in hours
Cs = Correction applied to the heating value of a gas H, when it is metered at temperature and/or pressure conditions other than the standard conditions for which the value of H is based. Cs=1 for oil-fired equipment.
Qs = Total fuel flow as metered, expressed in ft3 (gas) or lb (oil)
H = Higher heating value of gas or oil, expressed in Btu/ft3 (gas) or Btu/lb (oil)
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the initial heat content of the stored water above room temperature
7.2.6.2. The standby loss expressed in Btu per hour must be calculated as follows:
SL (Btu per hour) = S (% per hour) × 8.25 (Btu/gal- °F) × Measured Volume (gal) × 70 ( °F).
Where, SL refers to the standby loss of the water heater, defined as the amount of energy required to maintain the stored water temperature expressed in Btu per hour.
7.3. Flow-Activated and Thermostatically-Activated Instantaneous Water Heaters with an External Thermostat. For water heaters that are either flow-activated or thermostatically-activated with an external thermostat, use the following steps to conduct the standby loss test.
7.3.1. Immediately after the thermal efficiency test or the steady-state verification period (as applicable), de-energize the primary control to end the call for heating. If the main burners do not cut out, then turn off the fuel supply.
7. 3.1.1. If the unit does not have an integral pump purge functionality, then turn off the outlet water valve and water pump at this time.
7.3.1.2. If the unit has an integral pump purge functionality, allow the pump purge operation to continue. After the pump purge operation is complete, immediately turn off the outlet water valve and water pump and continue recording the required parameters for the remainder of the test.
7.3.2. Recording Data
7.3.2.1. For units with pump purge functionality, record the initial heat exchanger outlet water temperature (TOHX), and ambient room temperature when the main burner(s) cut-out or the fuel supply is turned off. After the pump purge operation is complete, record the time as t = 0 and the initial electricity meter reading. Continue to monitor and record the heat exchanger outlet water temperature (TOHX) and time elapsed from the start of the test, and the electricity consumption as per the requirements in section 3.9.2 of this appendix.
7.3.2.2. For units not equipped with pump purge functionality, begin recording the measurements as per the requirements of section 3.9.2 of this appendix when the main burner(s) cut-out or the fuel supply is turned off. Specifically, record the time as t = 0, and record the initial heat exchanger outlet water temperature (TOHX), ambient room temperature, and electricity meter readings. Continue to monitor and record the heat exchanger outlet water temperature (TOHX) and the time elapsed from the start of the test as per the requirements in section 3.9.2 of this appendix.
7.3.3. Stopping Criteria. Stop the test when one of the following occurs:
7.3.3.1. The heat exchanger outlet water temperature (TOHX) decreases by 35 °F from its value recorded immediately after the main burner(s) has cut-out, and the pump purge operation (if applicable) is complete; or
7.3.3.2. 24 hours have elapsed from the start of the test.
7.3.4. At the end of the test, record the final heat exchanger outlet water temperature (TOHX), fuel consumed, electricity consumed from time t=0, and the time elapsed from the start of the test.
7.3.5. Standby Loss Calculation
7.3.5.1. Once the test is complete, use the following equation to calculate the standby loss as a percentage (per hour) of the heat content of the stored water above room temperature:
Where,
ΔT1 = Heat exchanger outlet water temperature (TOHX) measured after the pump purge operation is complete (if the unit is integrated with pump purge functionality); or after the main burner(s) cut-out (if the unit is not equipped with pump purge functionality) minus heat exchanger outlet water temperature (TOHX) measured at the end of the test, expressed in °F
ΔT2 = Heat exchanger outlet water temperature (TOHX) minus the ambient temperature, both measured after the main burner(s) cut-out, at the start of the test, expressed in °F
K = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency of the water heater determined in accordance with section 6 of this appendix, expressed in %
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
t = Total duration of the test in hours
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the initial heat content of the stored water above room temperature
7.3.5.2. The standby loss expressed in terms of Btu per hour must be calculated as follows:
SL (Btu per hour) = S (% per hour) × 8.25 (Btu/gal- °F) × Measured Volume (gal) × 70 ( °F)
Where, SL refers to the standby loss of the water heater, defined as the amount of energy required to maintain the stored water temperature expressed in Btu per hour.
[81 FR 79332, Nov. 10, 2016]
Note: Prior to November 6, 2017, manufacturers must make any representations with respect to the energy use or efficiency of the subject commercial water heating equipment in accordance with the results of testing pursuant to this appendix or the procedures in 10 CFR 431.106 that were in place on January 1, 2016. On and after November 6, 2017, manufacturers must make any representations with respect to energy use or efficiency of electric instantaneous water heaters (other than storage-type instantaneous water heaters) in accordance with the results of testing pursuant to this appendix to demonstrate compliance with the energy conservation standards at 10 CFR 431.110.
1. General
Determine the standby loss (as applicable) in accordance with the following sections of this appendix.
2. Test Set-Up
2.
1. Placement of Water Heater. A water heater for installation on combustible floors must be placed on a 3⁄4-inch plywood platform supported by three 2 × 4-inch runners. If the water heater is for installation on noncombustible floors, suitable noncombustible material must be placed on the platform. When the use of the platform for a large water heater is not practical, the water heater may be placed on any suitable flooring. A wall-mounted water heater must be mounted on a simulated wall section.
2.
2. Test Configuration. If the instantaneous water heater is not required to be tested using a recirculating loop, then set up the unit in accordance with Figure 2.1, 2.2, or 2.3 of this appendix (as applicable). If the unit is required to be tested using a recirculating loop, then set up the unit as per Figure 2.4 of this appendix.
2.2.1. If the instantaneous water heater does not have any external piping, install an outlet water valve within 10 inches of the piping length of the water heater jacket or enclosure. If the instantaneous water heater includes external piping assembled at the manufacturer's premises prior to shipment, install water valves in the outlet piping within 5 inches of the end of the piping supplied with the unit.
2.2.2. If the water heater is not able to achieve an outlet water temperature of 70 °F ± 2 °F above the supply water temperature at a constant maximum electricity input rate, a recirculating loop with pump as shown in Figure 2.4 of this appendix must be used.
2. 2.2.1. If a recirculating loop with a pump is used, then ensure that the inlet water temperature (labeled as TIWT in Figure 2.4 of this appendix) is greater than or equal to 70 °F and less than or equal to 120 °F at all times during the steady-state verification period.
2.3. Installation of Temperature Sensors
2.3.1. Without Recirculating Loop
2.3.1.1. Vertical Connections. Use Figure 2.1 (for top connections) and 2.2 (for bottom connections) of this appendix.
2.3.1.2. Horizontal Connections. Use Figure 2.3 of this appendix.
2.3.2. With Recirculating Loop. Set up the recirculating loop as shown in Figure 2.4 of this appendix.
2.3.3. For water heaters with multiple outlet water connections leaving the water heater jacket that are required to be operated to achieve the rated input, temperature sensors must be installed for each outlet water connection leaving the water heater jacket or enclosure that is used during testing, in accordance with sections 2.3.1 and 2.3.2 of this appendix.
2.4. Piping Insulation. Insulate all the water piping external to the water heater jacket or enclosure, including piping that is installed by the manufacturer or shipped with the unit, for at least 4 ft of piping length from the connection at the appliance with material having an R-value not less than 4 °F·ft2·h/Btu. Ensure that the insulation does not contact any appliance surface except at the location where the pipe connections penetrate the appliance jacket or enclosure.
2.5. Temperature and Pressure Relief Valve Insulation. If the manufacturer has not provided a temperature and pressure relief valve, one shall be installed and insulated as specified in section 2.4 of this appendix. The temperature and pressure relief valve must be installed in the outlet water piping between the unit being tested and the outlet water valve.
2. 6. Energy Consumption. Install equipment that determines, within ± 1 percent, the quantity of electricity consumed by factory-supplied water heater components, and of the test loop recirculating pump, if used.
3. Test Conditions
3.1. Water Supply
3.1.1. Water Supply Pressure. The pressure of the water supply must be maintained between 40 psi and the maximum pressure specified by the manufacturer of the unit being tested. The accuracy of the pressure-measuring devices must be ± 1.0 psi.
3.1.2. Water Supply Temperature. During the steady-state verification period, the temperature of the supply water (TSWT) must be maintained at 70 °F ± 2 °F.
.2. Electrical Supply. Maintain the electrical supply voltage to within ± 5 percent of the voltage specified on the water heater nameplate. If a voltage range is specified on the nameplate, maintain the voltage to within ± 5 percent of the center of the voltage range specified on the nameplate.
3. 3. Ambient Room Temperature. Maintain the ambient room temperature at 75 °F ± 10 °F at all times during the steady-state verification period and the standby loss test. Measure the ambient room temperature at 1-minute intervals during these periods. Measure the ambient room temperature at the vertical mid-point of the water heater and approximately 2 feet from the water heater jacket or enclosure. Shield the sensor against radiation. Calculate the average ambient room temperature for the standby loss test. During the standby loss test, the ambient room temperature must not vary more than ± 5.0 °F at any reading from the average ambient room temperature.
3.4. Maximum Air Draft. During the steady-state verification period and the standby loss test, the water heater must be located in an area protected from drafts of more than 50 ft/min. Prior to beginning steady-state verification before the standby loss test, measure the air draft within three feet of the jacket or enclosure of the water heater to ensure this condition is met. Ensure that no other changes that would increase the air draft are made to the test set-up or conditions during the conduct of the test.
3.5. Primary Control
3.5.1. Thermostatically-Activated Water Heaters with an Internal Thermostat. Before starting the steady-state verification prior to the standby loss test, the thermostat setting must be obtained. Set the thermostat to ensure:
3.5.1.1. With supply water temperature as per section 3.1.2 of this appendix (i.e., 70 °F ± 2 °F) the water flow rate can be varied so that the outlet water temperature is constant at 70 °F ± 2 °F above the supply water temperature, while the heating element is operating at the rated input.
3.5.1.2. After the water supply is turned off and the thermostat reduces the electricity supply to the heating element to a minimum, the maximum heat exchanger outlet water temperature (TOHX) is 140 °F ± 5 °F.
3.5.1.3. If the water heater includes a built-in safety mechanism that prevents it from achieving a heat exchanger outlet water temperature of 140 °F ± 5 °F, adjust the thermostat to its maximum setting.
3.5.2. Flow-Activated Instantaneous Water Heaters and Thermostatically-Activated Instantaneous Water Heaters with an External Thermostat. Before starting the steady-state verification prior to the standby loss test energize the primary control such that it is always calling for heating and the heating element is operating at the rated input. Maintain the supply water temperature as per section 3.1.2 of this appendix (i.e., 70 °F ± 2 °F). Set the control so that the outlet water temperature (TOWT) is 140 °F ± 5 °F. If the water heater includes a built-in safety mechanism that prevents it from achieving a heat exchanger outlet water temperature of 140 °F ± 5 °F, adjust the control to its maximum setting.
3.6. For Units With Multiple Outlet Water Connections
3.6.1. For each connection leaving the water heater that is required for the unit to achieve the rated input, the outlet water temperature must not differ from that of any other outlet water connection by more than 2 °F during the steady-state verification period prior to the standby loss test.
3.6.2. Determine the outlet water temperature representative for the entire unit at every required measurement interval by calculating the average of the outlet water temperatures measured at each connection leaving the water heater jacket or enclosure that is used during testing. Use the outlet water temperature representative for the entire unit in all calculations for the standby loss test.
3.7. Data Collection Intervals. During the standby loss test, follow the data recording intervals specified in Table 3.1 of this appendix. Also, the electricity consumption over the course of the entire test must be measured and used in calculation of standby loss.
3.7.1. Steady-State Verification Period. Follow the data recording intervals specified in Table 3.1 of this appendix.
| Item recorded | Before steady-state verification period |
Every 1 minute a |
Every 10 minutes |
|---|---|---|---|
| Air draft, ft/min | X | ||
| Time, minutes/seconds | X | ||
| Electricity Consumed, Btu | X | ||
| Supply water temperature (TSWT), °F | X | ||
| Inlet water temperature (TIWT), °F | X b | ||
| Outlet water temperature (TOWT), °F | X | ||
| Ambient room temperature, °F | X | ||
| Water flow rate, (gpm) | X | ||
| Notes: | |||
| a These measurements are to be recorded at the start and end, as well as every minute of the steady-state verification period. | |||
| b Only measured when a recirculating loop is used. | |||
3.7.2. Standby Loss Test. Follow the data recording intervals specified in Table 3.2 of this appendix. Additionally, the electricity consumption over the course of the entire test must be measured and used in calculation of standby loss.
| Item recorded | Before test | Every 1 minute a |
|---|---|---|
| Air draft, ft/min | X | |
| Time, minutes/seconds | X | |
| Heat exchanger outlet water temperature, °F (TOHX) | X | |
| Ambient room temperature, °F | X | |
| Note: | ||
| a These measurements are to be recorded at the start and end of the test, as well as every minute during the test. | ||
4. Determination of Storage Volume. Determine the storage volume by subtracting the tare weight—measured while the system is dry and empty—from the weight of the system when filled with water and dividing the resulting net weight of water by the density of water at the measured water temperature. The volume of water contained in the water heater must be computed in gallons.
5. Standby Loss Test. Perform the steady-state verification period in accordance with section 5.1 of this appendix. For thermostatically-activated instantaneous water heaters with an internal thermostat, use section 5.2 of this appendix to conduct the standby loss test, and for flow-activated and/or thermostatically-activated instantaneous water heaters with an external thermostat (including remote thermostatically activated and/or flow-activated instantaneous water heaters), use section 5.3 of this appendix to conduct the standby loss test.
Set the primary control in accordance with section 3.5 of this appendix, such that the primary control is always calling for heat and the water heater is operating at its full rated input. Begin drawing water from the unit by opening the main supply and the outlet water valve, and adjust the water flow rate to achieve an outlet water temperature of 70 °F ± 2 °F above supply water temperature. At this time, begin recording the parameters specified in section 3.7.1 of this appendix. The steady-state verification period is complete when there is a continuous 30-minute period where the steady-state conditions specified in section 5.1 of this appendix are met, as confirmed by consecutive readings of the relevant parameters recorded at 1-minute intervals (except for electric power input rate, which is determined at 10-minute intervals, as specified in section 3.7.1 of this appendix).
5.1. Steady-State Conditions. The following conditions must be met at consecutive readings taken at 1-minute intervals (except for electricity input rate, for which measurements are taken at 10-minute intervals) to verify the water heater has achieved steady-state operation prior to conducting the standby loss test.
5.1.1. The water flow rate must be maintained within ± 0.25 gallons per minute (gpm) of the initial reading at the start of the steady-state verification period;
5.1.2. Electric power input rate must be maintained within 2 percent of the rated input certified by the manufacturer.
5.1.3. The supply water temperature (or inlet water temperature if a recirculating loop is used) must be maintained within ± 0.50 °F of the initial reading at the start of the steady-state verification period; and
5.1.4. The rise between the supply (or inlet if a recirculating loop is used) and outlet water temperatures is maintained within ± 0.50 °F of its initial value taken at the start of the steady-state verification period for units with rated input less than 500,000 Btu/h, and maintained within ± 1.00 °F of its initial value for units with rated input greater than or equal to 500,000 Btu/h.
5.2. Thermostatically-Activated Instantaneous Water Heaters with an Internal Thermostat. For water heaters that will experience cut-in based on a temperature-activated control that is internal to the water heater, use the following steps to conduct the standby loss test.
5.2.1. Immediately after the steady-state verification period, turn off the outlet water valve(s) (installed as per the provisions in section 2.2 of this appendix), and the water pump (if applicable) simultaneously and ensure that there is no flow of water through the water heater.
5. 2.2. After the first cut-out following the steady-state verification period, allow the water heater to remain in standby mode. Do not change any settings on the water heater at any point until measurements for the standby loss test are finished. Begin recording the applicable parameters specified in section 3.7.2 of this appendix.
5. 2.3. At the second cut-out, record the time and ambient room temperature, and begin measuring the electricity consumption. Record the initial heat exchanger outlet water temperature (TOHX) and initial ambient room temperature. For the remainder of the test, continue recording the applicable parameters specified in section 3.7.2 of this appendix.
5. 2.4. Stop the test after the first cut-out that occurs after 24 hours, or at 48 hours, whichever comes first.
5. 2.5. Immediately after conclusion of the standby loss test, record the total electrical energy consumption, the final ambient room temperature, the duration of the standby loss test, and if the test ends at 48 hours without a cut-out, the final heat exchanger outlet temperature, or if the test ends after a cut-out, the maximum heat exchanger outlet temperature that occurs after the cut-out. Calculate the average of the recorded values of the heat exchanger outlet water temperature and of the ambient air temperatures taken at each measurement interval, including the initial and final values.
5. 2.6. Standby Loss Calculation. Calculate the standby loss, expressed as a percentage (per hour) of the heat content of the stored water above room temperature, using the following equation:
Where,
ΔT3 = Average value of the heat exchanger outlet water temperature (TOHX) minus the average value of the ambient room temperature, expressed in °F
ΔT4 = Final heat exchanger outlet water temperature (TOHX) measured at the end of the test minus the initial heat exchanger outlet water temperature (TOHX) measured at the start of the test, expressed in °F
k = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency = 98 percent for electric water heaters with immersed heating elements
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
t = Total duration of the test in hours
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the initial heat content of the stored water above room temperature
5.3. Flow-Activated and Thermostatically-Activated Instantaneous Water Heaters with an External Thermostat. For water heaters that are either flow-activated or thermostatically-activated with an external thermostat, use the following steps to conduct the standby loss test:
5.3.1. Immediately after the steady-state verification period, de-energize the primary control to end the call for heating. If the heating elements do not cut out, then turn off the electricity supply to the heating elements. After the heating elements have cut-out, or the electricity supply to the heating elements is turned off, begin recording the measurements as per the requirements in section 3.7.2 of this appendix.
5.3.1.1. If the unit does not have an integral pump purge functionality, then turn off the outlet water valve and water pump immediately after the main burners cut-out.
5.3.1.2. If the unit has an integral pump purge functionality, allow the pump purge operation to continue. After the pump purge operation is complete, immediately turn off the outlet water valve and water pump and continue recording the required parameters for the remainder of the test.
5.3.2. Recording Data
5.3.2.1. For units with pump purge functionality, record the initial heat exchanger outlet water temperature (TOHX), and ambient room temperature when the main heating element(s) cut-out or the electricity supply to the heating element(s) is turned off. After the pump purge operation is complete, record the time as t = 0 and the initial electricity meter reading. Continue to monitor and record the heat exchanger outlet water temperature (TOHX) and time elapsed from the start of the test as per the requirements in section 3.7.2 of this appendix.
5.3.2.2. For units not equipped with pump purge functionality, begin recording the measurements as per the requirements of section 3.7.2 of this appendix when the main heating element(s) cut-out or the electricity supply to the heating element(s) is turned off. Specifically, record the time as t = 0, and record the initial heat exchanger outlet water temperature (TOHX), ambient room temperature, and electricity meter readings. Continue to monitor and record the heat exchanger outlet water temperature (TOHX) and the time elapsed from the start of the test as per the requirements in section 3.7.2 of this appendix.
5.3.3. Stopping Criteria. Stop the test when one of the following occurs:
5.3.3.1. The heat exchanger outlet water temperature (TOHX) decreases by 35 °F from its value recorded after the main heating element(s) have cut-out, and the pump purge operation (if applicable) is complete; or
5.3.3.2. 24 hours have elapsed from the start of the test.
5. 3.4. At the end of the test, record the final heat exchanger outlet water temperature (TOHX), electricity consumed from time t = 0, and the time elapsed from the start of the test.
5.3.5. Standby Loss Calculation. Calculate the standby loss, expressed as a percentage (per hour) of the heat content of the stored water above room temperature, using the following equation:
Where,
ΔT1 = Heat exchanger outlet water temperature (TOHX) measured after the pump purge operation is complete (if the unit is integrated with pump purge functionality); or after the main heating element(s) cut-out (if the unit is not equipped with pump purge functionality) minus heat exchanger outlet water temperature (TOHX) measured at the end of the test, expressed in °F
ΔT2 = Heat exchanger outlet water temperature (TOHX) minus the ambient room temperature, both measured after the main heating element(s) cut-out at the start of the test, expressed in °F
k = 8.25 Btu/gallon· °F, the nominal specific heat of water
Va = Volume of water contained in the water heater in gallons measured in accordance with section 4 of this appendix
Et = Thermal efficiency = 98 percent for electric water heaters with immersed heating elements
Ec = Electrical energy consumed by the water heater during the duration of the test in Btu
t = Total duration of the test in hours
S = Standby loss, the average hourly energy required to maintain the stored water temperature expressed as a percentage of the initial heat content of the stored water above room temperature
[81 FR 79340, Nov. 10, 2016]
Note: On and after November 6, 2017, manufacturers must make any representations with respect to energy use or efficiency of commercial heat pump water heaters in accordance with the results of testing pursuant to this appendix.
1. General. Determine the COPh for commercial heat pump water heaters (CHPWHs) using the test procedure set forth below. Certain sections below reference ANSI/ASHRAE 118.1-2012 (incorporated by reference; see § 431.105). Where the instructions contained below differ from those contained in ANSI/ASHRAE 118.1-2012, the sections in this appendix control.
2. Definitions and Symbols. The definitions and symbols are as listed in section 3 of ANSI/ASHRAE 118.1-2012.
3. Instrumentation. The instruments required for the test are as described in section 6 of ANSI/ASHRAE 118.1-2012 (except sections 6.3, 6.4, and 6.6).
4. Test Set-Up. Follow the provisions described in this section to install the CHPWH for testing. Use the test set-up and installation instructions set forth for Type IV and Type V equipment (as applicable), defined in sections 4.4 and 4.5 of ANSI/ASHRAE 118.1-2012 and in accordance with the sections below:
4.
1. Test set-up and installation instructions.
4.1.1. For air-source CHPWHs, set up the unit for testing as per section 7.1 and Figure 5a of ANSI/ASHRAE 118.1-2012 for CHPWHs without an integral storage tank, and as per Figure 6 in section 7.7.1 of ANSI/ASHRAE 118.1-2012 for CHPWHs with an integral storage tank.
4. 1.2. For direct geo-exchange CHPWHs, set up the unit for testing as per section 7.1 and Figure 5b of ASNI/ASHRAE 118.1-2012 for CHPWHs without an integral storage tank, and as per Figure 7 in section 7.7.2 of ANSI/ASHRAE 118.1-2012 for CHPWHs with an integral storage tank.
4. 1.3. For indoor water-source, ground-source closed-loop, and ground water-source CHPWHs, set up the unit for testing as per section 7.1 and Figure 5c of ANSI/ASHRAE 118.1-2012 for CHPWHs without an integral storage tank, and as per Figure 8 in section 7.7.3 of ANSI/ASHRAE 118.1-2012 for CHPWHs with an integral storage tank.
4. 2. Use the water piping instructions described in section 7.2 of ANSI/ASHRAE 118.1-2012 and the special instructions described in section 7.7.6 of ANSI/ASHRAE 118.1-2012. Insulate all the pipes used for connections with material having a thermal resistance of not less than 4 h· °F·ft2/Btu for a total piping length of not less than 4 feet from the water heater connection ports.
4.3. Install the thermocouples, including the room thermocouples, as per the instructions in sections 7.3.1, 7.3.2, and 7.3.3 (as applicable) of ANSI/ASHRAE 118.1-2012.
4.4. Section 7.6 of ANSI/ASHRAE 118.1-2012 must be used if the manufacturer neither submits nor specifies a water pump applicable for the unit for laboratory testing.
4.5. Install the temperature sensors at the locations specified in Figure 5a, 5b, 5c, 6, 7, or 8 of ANSI/ASHRAE 118.1-2012, as applicable as per section 4.1 of this appendix. The sensor shall be installed in such a manner that the sensing portion of the device is positioned within the water flow and as close as possible to the center line of the pipe. Follow the instructions provided in sections 7.7.7.1 and 7.7.7.2 of ANSI/ASHRAE 118.1-2012 to install the temperature and flow-sensing instruments.
4.6. Use the following evaporator side rating conditions as applicable for each category of CHPWHs. These conditions are also mentioned in Table 5.1 of this appendix:
4.6.1. For air-source CHPWHs, maintain the evaporator air entering dry-bulb temperature at 80.6 °F ± 1 °F and wet-bulb temperature at 71.2 °F ± 1 °F throughout the conduct of the test.
4.6.2. For direct geo-exchange CHPWHs, maintain the evaporator refrigerant temperature at 32 °F ± 1 °F.
4.6.3. For indoor water-source CHPWHs, maintain the evaporator entering water temperature at 68 °F ± 1 °F.
4.6.4. For ground water-source CHPWHs, maintain the evaporator entering water temperature at 50 °F ± 1 °F.
4.6.5. For ground-source closed-loop CHPWHs, maintain the evaporator entering water temperature at 32 °F ± 1 °F.
4.6.5.1. For ground-source closed-loop CHPWHs, the evaporator water must be mixed with 15-percent methanol by-weight to allow the solution to achieve the rating conditions required in section 4.6.5.
4.7. The CHPWH being tested must be installed as per the instructions specified in sections 4.1 to 4.6 (as applicable) of this appendix. For all other installation requirements, use section 7.7.4 of ANSI/ASHRAE 118.1-2012 to resolve any issues related to installation (other than what is specified in this test procedure) of the equipment for testing. Do not make any alterations to the equipment except as specified in this appendix for installation, testing, and the attachment of required test apparatus and instruments.
4. 8. Use Table 3 of ANSI/ASHRAE 118.1-2012 for measurement tolerances of various parameters.
4.9. If the CHPWH is equipped with a thermostat that is used to control the throttling valve of the equipment, then use the provisions in section 7.7.7.3 of ANSI/ASHRAE 118.1-2012 to set up the thermostat.
4.10. For CHPWHs equipped with an integral storage tank, supplemental heat inputs such as electric resistance elements must be disabled as per section 7.7.8 of ANSI/ASHRAE 118.1-2012.
4.11. Install instruments to measure the electricity supply to the equipment as specified in section 7.5 of ANSI/ASHRAE 118.1-2012.
5. Test Procedure
Test all CHPWHs that are not equipped with an integral storage tank as per the provisions described in ANSI/ASHRAE 118.1-2012 for “Type IV” equipment as defined in section 4.4 of ANSI/ASHRAE 118.1-2012. Test all CHPWHs that are equipped with an integral storage tank as per the provisions described in ANSI/ASHRAE 118.1-2012 for “Type V” equipment as defined in section 4.5 of ANSI/ASHRAE 118.1-2012. Tests for all CHPWHs must follow the steps described below.
5.1. Supply the CHPWH unit with electricity at the voltage specified by the manufacturer. Follow the provisions in section 8.2.1 of ANSI/ASHRAE 118.1-2012 to maintain the electricity supply at the required level.
5.1.1. For models with multiple voltages specified by the manufacturer, use the minimum voltage specified by the manufacturer to conduct the test. Maintain the voltage as per the limits specified in section 8.2.1 of ANSI/ASHRAE 118.1-2012. The test may be repeated at other voltages at the manufacturer's discretion.
5.2. Set the condenser supply water temperature and outlet water temperature per the following provisions and as set forth in Table 5.1 of this section:
| Category of CHPWH | Evaporator side rating conditions | Condenser side rating conditions |
|---|---|---|
| Air-source commercial heat pump water heater | Evaporator entering air conditions: Dry bulb: 80.6 °F ± 1 °F Wet bulb: 71.2 °F ± 1 °F |
Entering water temperature: 70 °F ± 1 °F. Vary water flow rate (if needed) to achieve the outlet water temperature as specified in section 8.7.2 of ANSI/ASHRAE 118.1-2012. |
| If the required outlet water temperature as specified in section 8.7.2 of ANSI/ASHRAE 118.1-2012 is not met even after varying the flow rate, then change the condenser entering water temperature to 110 °F ± 1 °F. Vary flow rate to achieve the conditions in section 8.7.2 of ANSI/ASHRAE 118.1-2012. | ||
| Direct geo-exchange commercial heat pump water heater | Evaporator refrigerant temperature: 32 °F ± 1 °F | Entering water temperature: 110 °F ± 1 °F. |
| Indoor water-source commercial heat pump water heater | Evaporator entering water temperature: 68 °F ± 1 °F | Entering water temperature: 110 °F ± 1 °F. |
| Ground water-source commercial heat pump water heater | Evaporator entering water temperature: 50 °F ± 1 °F | Entering water temperature: 110 °F ± 1 °F. |
| Ground-source closed-loop commercial heat pump water heater | Evaporator entering water temperature: 32 °F ± 1 °F | Entering water temperature: 110 °F ± 1 °F. |
5.2.1. For air-source CHPWHs:
5.2.1.1. Set the supply water temperature to 70 °F ± 1 °F. The water pressure must not exceed the maximum working pressure rating for the equipment under test.
5.2.1.2. Use the provisions in section 8.7.1 of ANSI/ASHRAE 118.1-2012 to set the tank thermostat for CHPWHs equipped with an integral storage tank.
5.2.1.3. Initiate operation at the rated pump flow rate and measure the outlet water temperature. If the outlet water temperature is maintained at 120 °F ± 5 °F with no variation in excess of 2 °F over a three-minute period, as required by section 8.7.2 of ANSI/ASHRAE 118.1-2012, skip to section 5.3 of this appendix.
5.2.1.4. If the outlet water temperature condition as specified in section 8.7.2 of ANSI/ASHRAE 118.1-2012 is not achieved, adjust the water flow rate over the range of the pump's capacity. If, after varying the water flow rate, the outlet water temperature is maintained at 120 °F ± 5 °F with no variation in excess of 2 °F over a three-minute period, as required by section 8.7.2 of ANSI/ASHRAE 118.1-2012, skip to section 5.3 of this appendix.
5.2.1.5. If, after adjusting the water flow rate within the range that is achievable by the pump, the outlet water temperature condition as specified in section 8.7.2 of ANSI/ASHRAE 118.1-2012 is still not achieved, then change the supply water temperature to 110 °F ± 1 °F and repeat the instructions from sections 5.2.1.2 and 5.2.1.4 of this appendix.
5.2.1. 6. If the outlet water temperature condition cannot be met, then a test procedure waiver is necessary to specify an alternative set of test conditions.
5.2.2. For direct geo-exchange, indoor water-source, ground-source closed-loop, and ground water-source CHPWHs use the following steps:
5.2.2.1. Set the condenser supply water temperature to 110 °F ± 1 °F. The water pressure must not exceed the maximum working pressure rating for the equipment under test.
5.2.2.2. Use the provisions in section 8.7.1 of ANSI/ASHRAE 118.1-2012 to set the tank thermostat for CHPWHs equipped with an integral storage tank.
5.2.2.3. Follow the steps specified in section 8.7.2 of ANSI/ASHRAE 118.1-2012 to obtain an outlet water temperature of 120 °F ± 5 °F with no variation in excess of 2 °F over a three-minute period.
5.3. Conduct the test as per section 9.1.1, “Full Input Rating,” of ANSI/ASHRAE 118.1-2012. The flow rate, “FR,” referred to in section 9.1.1 of ANSI/ASHRAE 118.1-2012 is the flow rate of water through the CHPWH expressed in gallons per minute obtained after following the steps in section 5.2 of this appendix. Use the evaporator side rating conditions specified in section 4.6 of this appendix to conduct the test as per section 9.1.1 of ANSI/ASHRAE 118.1-2012.
5.4. Calculate the COPh of the CHPWH according to section 10.3.1 of the ANSI/ASHRAE 118.1-2012 for the “Full Capacity Test Method.” For all calculations, time differences must be expressed in minutes.
[81 FR 79346, Nov. 10, 2016]
70 FR 60415, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for commercial ice makers, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
Automatic commercial ice maker means a factory-made assembly (not necessarily shipped in 1 package) that—
(1) Consists of a condensing unit and ice-making section operating as an integrated unit, with means for making and harvesting ice; and
(2) May include means for storing ice, dispensing ice, or storing and dispensing ice.
Baffle means a partition (usually made of flat material like cardboard, plastic, or sheet metal) that reduces or prevents recirculation of warm air from an ice maker's air outlet to its air inlet—or, for remote condensers, from the condenser's air outlet to its inlet.
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Batch type ice maker means an ice maker having alternate freezing and harvesting periods.
Condenser water use means the total amount of water used by the condensing unit (if water-cooled), stated in gallons per 100 pounds (gal/100 lb) of ice, in multiples of 1.
Continuous type ice maker means an ice maker that continually freezes and harvests ice at the same time.
Energy use means the total energy consumed, stated in kilowatt hours per one-hundred pounds (kWh/100 lb) of ice, in multiples of 0.01. For remote condensing (but not remote compressor) automatic commercial ice makers and remote condensing and remote compressor automatic commercial ice makers, total energy consumed shall include the energy use of the ice-making mechanism, the compressor, and the remote condenser or condensing unit.
Harvest rate means the amount of ice (at 32 degrees F) in pounds produced per 24 hours.
Ice hardness factor means the latent heat capacity of harvested ice, in British thermal units per pound of ice (Btu/lb), divided by 144 Btu/lb, expressed as a percent.
Ice-making head means automatic commercial ice makers that do not contain integral storage bins, but are generally designed to accommodate a variety of bin capacities. Storage bins entail additional energy use not included in the reported energy consumption figures for these units.
Portable automatic commercial ice maker means an automatic commercial ice maker that does not have a means to connect to a water supply line and has one or more reservoirs that are manually supplied with water.
Potable water use means the amount of potable water used in making ice, which is equal to the sum of the ice harvested, dump or purge water, and the harvest water, expressed in gal/100 lb, in multiples of 0.1, and excludes any condenser water use.
Refrigerated storage automatic commercial ice maker means an automatic commercial ice maker that has a refrigeration system that actively refrigerates the self-contained ice storage bin.
Remote compressor means a type of automatic commercial ice maker in which the ice-making mechanism and compressor are in separate sections.
Remote condensing means a type of automatic commercial ice maker in which the ice-making mechanism and condenser or condensing unit are in separate sections.
Self-contained means a type of automatic commercial ice maker in which the ice-making mechanism and storage compartment are in an integral cabinet.
[70 FR 60415, Oct. 18, 2005, as amended at 71 FR 71371, Dec. 8, 2006; 76 FR 12503, Mar. 7, 2011; 77 FR 1613, Jan. 11, 2012; 87 FR 65899, Nov. 1, 2022]
Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the U.S. Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202)-586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the following sources:
(a) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Blvd., Suite 500, Arlington, VA 22201; (703) 524-8800; ahri@ahrinet.org; www.ahrinet.org.
(1) AHRI Standard 810 (I-P)-2016 with Addendum 1, Performance Rating of Automatic Commercial Ice-Makers, January 2018; IBR approved for § 431.134.
(2) [Reserved]
(b) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc., 1791 Tullie Circle NE, Atlanta, GA 30329; (404) 636-8400; ashrae@ashrae.org; www.ashrae.org.
(1) ANSI/ASHRAE Standard 29-2015, Method of Testing Automatic Ice Makers, approved April 30, 2015; IBR approved for § 431.134.
(2) [Reserved]
[87 FR 65900, Nov. 1, 2022]
On or after October 27, 2023, any representations, including certifications of compliance for automatic commercial ice makers, made with respect to the energy use or efficiency of automatic commercial ice makers must be made in accordance with the results of testing pursuant to this section. Prior to October 27, 2023, any representations with respect to energy use or efficiency of automatic commercial ice makers must be made either in accordance with the results of testing pursuant to this section or with the results of testing pursuant to this section as it appeared in 10 CFR 431.134 in the 10 CFR parts 200-499 edition revised as of January 1, 2022.
(a) Scope. This section provides the test procedures for measuring the harvest rate in pounds of ice per 24 hours (lb/24 h), energy use in kilowatt hours per 100 pounds of ice (kWh/100 lb), and the condenser water use in gallons per 100 pounds of ice (gal/100 lb) of automatic commercial ice makers with capacities up to 4,000 lb/24 h. This section also provides voluntary test procedures for measuring the potable water use in gallons per 100 pounds of ice (gal/100 lb).
(b) Testing and calculations. Measure the harvest rate, the energy use, the condenser water use, and, to the extent elected, the potable water use of each covered automatic commercial ice maker by conducting the test procedures set forth in AHRI Standard 810 (I-P)-2016 with Addendum 1, section 3, “Definitions,” section 4, “Test Requirements,” and section 5.2, “Standard Ratings” (incorporated by reference, see § 431.133), and according to the provisions of this section. Use ANSI/ASHRAE Standard 29-2015 (incorporated by reference, see § 431.133) referenced by AHRI Standard 810 (I-P)-2016 with Addendum 1 for all automatic commercial ice makers, except as noted in paragraphs (c) through (k) of this section. If any provision of the referenced test procedures conflicts with the requirements in this section or the definitions in § 431.132, the requirements in this section and the definitions in § 431.132 control.
(c) Test setup and equipment configurations —
(1) Baffles. Conduct testing without baffles unless the baffle either is a part of the automatic commercial ice maker or shipped with the automatic commercial ice maker to be installed according to the manufacturer's installation instructions.
(2) Clearances. Install all automatic commercial ice makers for testing according to the manufacturer's specified minimum rear clearance requirements, or with 3 feet of clearance from the rear of the automatic commercial ice maker, whichever is less, from the chamber wall. All other sides of the automatic commercial ice maker and all sides of the remote condenser, if applicable, shall have clearances according to section 6.5 of ANSI/ASHRAE Standard 29-2015.
(3) Purge settings. Test automatic commercial ice makers equipped with automatic purge water control using a fixed purge water setting that is described in the manufacturer's written instructions shipped with the unit as being appropriate for water of normal, typical, or average hardness. Purge water settings described in the instructions as suitable for use only with water that has higher or lower than normal hardness (such as distilled water or reverse osmosis water) must not be used for testing.
(4) Ambient conditions measurement —
(i) Ambient temperature sensors. Measure all ambient temperatures according to section 6.4 of ANSI/ASHRAE Standard 29-2015, except as provided in paragraph (c)(4)(iv) of this section, with unweighted temperature sensors.
(ii) Ambient relative humidity measurement. Except as provided in paragraph (c)(4)(iv) of this section, ambient relative humidity shall be measured at the same location(s) used to confirm ambient dry bulb temperature, or as close as the test setup permits. Ambient relative humidity shall be measured with an instrument accuracy of ±2.0 percent.
(iii) Ambient conditions sensors shielding. Ambient temperature and relative humidity sensors may be shielded if the ambient test conditions cannot be maintained within the specified tolerances because of warm discharge air from the condenser exhaust affecting the ambient measurements. If shields are used, the shields must not inhibit recirculation of the warm discharge air into the condenser or automatic commercial ice maker inlet.
(iv) Alternate ambient conditions measurement location. For automatic commercial ice makers in which warm air discharge from the condenser exhaust affects the ambient conditions as measured 1 foot in front of the air inlet, or automatic commercial ice makers in which the air inlet is located in the rear of the automatic commercial ice maker and the manufacturer's specified minimum rear clearance is less than or equal to 1 foot, the ambient temperature and relative humidity may instead be measured 1 foot from the cabinet, centered with respect to the sides of the cabinet, for any side of the automatic commercial ice maker cabinet with no warm air discharge or air inlet.
(5) Collection container for batch type automatic commercial ice makers with harvest rates less than or equal to 50 lb/24 h. Use an ice collection container as specified in section 5.5.2(a) of ANSI/ASHRAE Standard 29-2015, except that the water retention weight of the container is no more than 4.0 percent of that of the smallest batch of ice for which the container is used.
(d) Test conditions —
(1) Relative humidity. Maintain an average minimum ambient relative humidity of 30.0 percent throughout testing.
(2) Inlet water pressure. Except for portable automatic commercial ice makers, the inlet water pressure when water is flowing into the automatic commercial ice maker shall be within the allowable range within 5 seconds of opening the water supply valve.
(e) Stabilization —
(1) Percent difference calculation. Calculate the percent difference in the ice production rate between two cycles or samples using the following equation, where A and B are the harvest rates, in lb/24 h (for batch type ice makers) or lb/15 mins (for continuous type ice makers), of any cycles or samples used to determine stability:
(2) Automatic commercial ice makers with harvest rates greater than 50lb/24 h. The three or more consecutive cycles or samples used to calculate harvest rate, energy use, condenser water use, and potable water use, must meet the stability criteria in section 7.1.1 of ANSI/ASHRAE Standard 29-2015.
(3) Automatic commercial ice makers with harvest rates less than or equal to 50 lb/24 h. The three or more consecutive cycles or samples used to calculate harvest rate, energy use, condenser water use, and potable water use, must meet the stability criteria in section 7.1.1 of ANSI/ASHRAE Standard 29-2015, except that the weights of the samples (for continuous type automatic commercial ice makers (ACIMs)) or 24-hour calculated ice production (for batch type ACIMs) must not vary by more than ±4 percent, and the 25 g (for continuous type ACIMs) and 1 kg (for batch type ACIMs) criteria do not apply.
(f) Calculations. The harvest rate, energy use, condenser water use, and potable water use must be calculated by averaging the values for the three calculated samples for each respective reported metric as specified in section 9 of ANSI/ASHRAE Standard 29-2015. All intermediate calculations prior to the reported value, as applicable, must be performed with unrounded values.
(g) Rounding. Round the reported values as follows: Harvest rate to the nearest 1 lb/24 h for harvest rates above 50 lb/24 h; harvest rate to the nearest 0.1 lb/24 h for harvest rates less than or equal to 50 lb/24 h; condenser water use to the nearest 1 gal/100 lb; and energy use to the nearest 0.01 kWh/100 lb. Round final potable water use value to the nearest 0.1 gal/100 lb.
(h) Continuous type automatic commercial ice makers —
(1) Ice hardness adjustment —
(i) Calorimeter constant. Determine the calorimeter constant according to the requirements in section A1 and A2 of Normative Annex A Method of Calorimetry in ANSI/ASHRAE Standard 29-2015, except that the trials shall be conducted at an ambient air temperature (room temperature) of 70 °F ± 1 °F, with an initial water temperature of 90 °F ± 1 °F. To verify the temperature of the block of pure ice as provided in section A2.e in ANSI/ASHRAE Standard 29-2015, a thermocouple shall be embedded at approximately the geometric center of the interior of the block. Any water that remains on the block of ice shall be wiped off the surface of the block before being placed into the calorimeter.
(ii) Ice hardness factor. Determine the ice hardness factor according to the requirements in section A1 and A3 of Normative Annex A Method of Calorimetry in ANSI/ASHRAE Standard 29-2015, except that the trials shall be conducted at an ambient air temperature (room temperature) of 70 °F ± 1 °F, with an initial water temperature of 90 °F ± 1 °F. The harvested ice used to determine the ice hardness factor shall be produced according to the test methods specified at § 431.134. The ice hardness factor shall be calculated using the equation for ice hardness factor in section 5.2.2 of AHRI Standard 810 (I-P)-2016 with Addendum 1.
(iii) Ice hardness adjustment calculation. Determine the reported energy use and reported condenser water use by multiplying the measured energy use or measured condenser water use by the ice hardness adjustment factor, determined using the ice hardness adjustment factor equation in section 5.2.2 of AHRI Standard 810 (I-P)-2016 with Addendum 1.
(2) [Reserved]
(i) Automatic commercial ice makers with automatic dispensers. Allow for the continuous production and dispensing of ice throughout testing. If an automatic commercial ice maker with an automatic dispenser is not able to continuously produce and dispense ice because of certain mechanisms within the automatic commercial ice maker that prohibit the continuous production and dispensing of ice throughout testing, those mechanisms must be overridden to the minimum extent which allows for the continuous production and dispensing of ice. The automatic commercial ice maker shall have an empty internal storage bin at the beginning of the test period. Collect capacity samples according to the requirements of ANSI/ASHRAE Standard 29-2015, except that the samples shall be collected through continuous use of the dispenser rather than in the internal storage bin. The intercepted ice samples shall be obtained from a container in an external ice bin that is filled one-half full of ice and is connected to the outlet of the ice dispenser through the minimal length of conduit that can be used.
(j) Portable automatic commercial ice makers. Sections 5.4, 5.6, 6.2, and 6.3 of ANSI/ASHRAE Standard 29-2015 do not apply. Ensure that the ice storage bin is empty prior to the initial potable water reservoir fill. Fill an external container with water to be supplied to the portable automatic commercial ice maker water reservoir. Establish an initial water temperature of 70 °F ± 1.0 °F. Verify the initial water temperature by inserting a temperature sensor into approximately the geometric center of the water in the external container. Immediately after establishing the initial water temperature, fill the ice maker water reservoir to the maximum level of potable water as specified by the manufacturer. After the potable water reservoir is filled, operate the portable automatic commercial ice maker to produce ice into the ice storage bin until the bin is one-half full. One-half full for the purposes of testing portable automatic commercial ice makers means that half of the vertical dimension of the ice storage bin, based on the maximum ice fill level within the ice storage bin, is filled with ice. Once the ice storage bin is one-half full, conduct testing according to section 7 of ANSI/ASHRAE Standard 29-2015. The potable water use is equal to the sum of the weight of ice and any corresponding melt water collected for the capacity test as specified in section 7.2 of ANSI/ASHRAE Standard 29-2015.
(k) Self-contained refrigerated storage automatic commercial ice makers. For door openings, the door shall be in the fully open position, which means opening the ice storage compartment door to an angle of not less than 75 degrees from the closed position (or the maximum extent possible, if that is less than 75 degrees), for 10.0 ± 1.0 seconds to collect the sample. Conduct door openings only for ice sample collection and returning the empty ice collection container to the ice storage compartment (i.e., conduct two separate door openings, one for removing the collection container to collect the ice and one for replacing the collection container after collecting the ice).
[87 FR 65900, Nov. 1, 2022]
(a) All basic models of commercial ice makers must be tested for performance using the applicable DOE test procedure in § 431.134, be compliant with the applicable standards set forth in paragraphs (b) through (d) of this section, and be certified to the Department of Energy under 10 CFR part 429 of this chapter.
(b) Each cube type automatic commercial ice maker with capacities between 50 and 2,500 pounds per 24-hour period manufactured on or after January 1, 2010 and before January 28, 2018, shall meet the following standard levels:
| Equipment type | Type of cooling | Harvest rate lb ice/24 hours |
Maximum energy use kWh/100 lb ice |
Maximum condenser water use 1 gal/100 lb ice |
|---|---|---|---|---|
| Ice-Making Head | Water | <500 | 7.8-0.0055H 2 | 200-0.022H. |
| Ice-Making Head | Water | ≥500 and <1,436 | 5.58-0.0011H | 200-0.022H. |
| Ice-Making Head | Water | ≥1,436 | 4.0 | 200-0.022H. |
| Ice-Making Head | Air | <450 | 10.26-0.0086H | Not Applicable. |
| Ice-Making Head | Air | ≥450 | 6.89-0.0011H | Not Applicable. |
| Remote Condensing (but not remote compressor) | Air | <1,000 | 8.85-0.0038H | Not Applicable. |
| Remote Condensing (but not remote compressor) | Air | ≥1,000 | 5.1 | Not Applicable. |
| Remote Condensing and Remote Compressor | Air | <934 | 8.85-0.0038H | Not Applicable. |
| Remote Condensing (but not remote compressor) | Air | ≥934 | 5.3 | Not Applicable. |
| Self-Contained | Water | <200 | 11.40-0.019H | 191-0.0315H. |
| Self-Contained | Water | ≥200 | 7.6 | 191-0.0315H. |
| Self-Contained | Air | <175 | 18.0-0.0469H | Not Applicable. |
| Self-Contained | Air | ≥175 | 9.8 | Not Applicable. |
| 1 Water use is for the condenser only and does not include potable water used to make ice. | ||||
| 2 H = harvest rate in pounds per 24 hours, indicating the water or energy use for a given harvest rate. | ||||
| Source: 42 U.S.C. 6313(d). | ||||
(c) Each batch type automatic commercial ice maker with capacities between 50 and 4,000 pounds per 24-hour period manufactured on or after January 28, 2018, shall meet the following standard levels:
| Equipment type | Type of cooling | Harvest rate lb ice/24 hours |
Maximum energy use kilowatt-hours (kWh)/100 lb ice 1 |
Maximum condenser water use gal/100 lb ice 2 |
|---|---|---|---|---|
| Ice-Making Head | Water | < 300 | 6.88-0.0055H | 200-0.022H. |
| Ice-Making Head | Water | ≥300 and <850 | 5.80-0.00191H | 200-0.022H. |
| Ice-Making Head | Water | ≥850 and <1,500 | 4.42-0.00028H | 200-0.022H. |
| Ice-Making Head | Water | ≥1,500 and <2,500 | 4.0 | 200-0.022H. |
| Ice-Making Head | Water | ≥2,500 and <4,000 | 4.0 | 145. |
| Ice-Making Head | Air | < 300 | 10-0.01233H | NA. |
| Ice-Making Head | Air | ≥ 300 and < 800 | 7.05-0.0025H | NA. |
| Ice-Making Head | Air | ≥ 800 and < 1,500 | 5.55-0.00063H | NA. |
| Ice-Making Head | Air | ≥ 1500 and < 4,000 | 4.61 | NA. |
| Remote Condensing (but not remote compressor) | Air | < 988 | 7.97-0.00342H | NA. |
| Remote Condensing (but not remote compressor) | Air | ≥ 988 and < 4,000 | 4.59 | NA. |
| Remote Condensing and Remote Compressor | Air | < 930 | 7.97-0.00342H | NA. |
| Remote Condensing and Remote Compressor | Air | ≥ 930 and < 4,000 | 4.79 | NA. |
| Self-Contained | Water | < 200 | 9.5-0.019H | 191-0.0315H. |
| Self-Contained | Water | ≥ 200 and < 2,500 | 5.7 | 191-0.0315H. |
| Self-Contained | Water | ≥ 2,500 and < 4,000 | 5.7 | 112. |
| Self-Contained | Air | < 110 | 14.79-0.0469H | NA. |
| Self-Contained | Air | ≥ 110 and < 200 | 12.42-0.02533H | NA. |
| Self-Contained | Air | ≥ 200 and < 4,000 | 7.35 | NA. |
| 1 H = harvest rate in pounds per 24 hours, indicating the water or energy use for a given harvest rate. Source: 42 U.S.C. 6313(d). | ||||
| 2 Water use is for the condenser only and does not include potable water used to make ice. | ||||
(d) Each continuous type automatic commercial ice maker with capacities between 50 and 4,000 pounds per 24-hour period manufactured on or after January 28, 2018, shall meet the following standard levels:
| Equipment type | Type of cooling | Harvest rate lb ice/24 hours |
Maximum energy use kWh/100 lb ice 1 |
Maximum condenser water use gal/100 lb ice 2 |
|---|---|---|---|---|
| Ice-Making Head | Water | <801 | 6.48-0.00267H | 180-0.0198H. |
| Ice-Making Head | Water | ≥801 and <2,500 | 4.34 | 180-0.0198H. |
| Ice-Making Head | Water | ≥2,500 and <4,000 | 4.34 | 130.5. |
| Ice-Making Head | Air | <310 | 9.19-0.00629H | NA. |
| Ice-Making Head | Air | ≥310 and <820 | 8.23-0.0032H | NA. |
| Ice-Making Head | Air | ≥820 and <4,000 | 5.61 | NA. |
| Remote Condensing (but not remote compressor) | Air | <800 | 9.7-0.0058H | NA. |
| Remote Condensing (but not remote compressor) | Air | ≥800 and <4,000 | 5.06 | NA. |
| Remote Condensing and Remote Compressor | Air | <800 | 9.9-0.0058H | NA. |
| ≥800 and <4,000 | 5.26 | NA. | ||
| Self-Contained | Water | <900 | 7.6-0.00302H | 153-0.0252H. |
| Self-Contained | Water | ≥900 and <2,500 | 4.88 | 153-0.0252H. |
| Self-Contained | Water | ≥2,500 and <4,000 | 4.88 | 90. |
| Self-Contained | Air | <200 | 14.22-0.03H | NA. |
| Self-Contained | Air | ≥200 and <700 | 9.47-0.00624H | NA. |
| Self-Contained | Air | ≥700 and <4,000 | 5.1 | NA. |
| 1 H = harvest rate in pounds per 24 hours, indicating the water or energy use for a given harvest rate. Source: 42 U.S.C. 6313(d). | ||||
| 2 Water use is for the condenser only and does not include potable water used to make ice. | ||||
[80 FR 4754, Jan. 28, 2015]
70 FR 60416, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for commercial clothes washers, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
AEER means active-mode energy efficiency ratio, in pounds per kilowatt-hour per cycle (lbs/kWh/cycle), as determined in section 4.8 of appendix J to subpart B of part 430 (when using appendix J).
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Commercial clothes washer means a soft-mounted front-loading or soft-mounted top-loading clothes washer that—
(1) Has a clothes container compartment that—
(i) For horizontal-axis clothes washers, is not more than 3.5 cubic feet; and
(ii) For vertical-axis clothes washers, is not more than 4.0 cubic feet; and
(2) Is designed for use in—
(i) Applications in which the occupants of more than one household will be using the clothes washer, such as multi-family housing common areas and coin laundries; or
(ii) Other commercial applications.
IWF means integrated water factor, in gallons per cubic feet per cycle (gal/cu ft/cycle), as determined in section 4.2.12 of appendix J2 to subpart B of part 430 (when using appendix J2).
MEFJ2 means modified energy factor, in cu ft/kWh/cycle, as determined in section 4.5 of appendix J2 to subpart B of part 430 (when using appendix J2).
WER means water efficiency ratio, in pounds per gallon per cycle (lbs/gal/cycle), as determined in section 4.7 of appendix J to subpart B of part 430 (when using appendix J).
[87 FR 33405, June 1, 2022]
The test procedures for clothes washers in appendix J2 to subpart B of part 430 must be used to determine compliance with the energy conservation standards at § 431.156(b).
[87 FR 33405, June 1, 2022]
(a) Each commercial clothes washer manufactured on or after January 8, 2013, and before January 1, 2018, shall have a modified energy factor no less than and a water factor no greater than:
| Equipment class | Modified energy factor (MEF), cu. ft./kWh/cycle |
Water factor (WF), gal./cu. ft./cycle |
|---|---|---|
| Top-Loading | 1.60 | 8.5 |
| Front-Loading | 2.00 | 5.5 |
(b) Each commercial clothes washer manufactured on or after January 1, 2018 shall have a modified energy factor no less than and an integrated water factor no greater than:
| Equipment class | Modified energy factor (MEFJ2), cu. ft./kWh/cycle |
Integrated Water factor (IWF), gal./cu. ft./cycle |
|---|---|---|
| Top-Loading | 1.35 | 8.8 |
| Front-Loading | 2.00 | 4.1 |
[76 FR 69123, Nov. 8, 2011, as amended at 79 FR 74541, Dec. 15, 2014; 81 FR 20529, Apr. 8, 2016]
86 FR 46590, Aug. 19, 2021, unless otherwise noted.
This subpart contains provisions regarding fans and blowers, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317. This subpart does not cover “ceiling fans” as that term is defined and addressed in part 430 this chapter, nor does it cover “furnace fans” as that term is defined and addressed in part 430 of this chapter.
Air circulating axial panel fan means an axial housed air circulating fan head without a cylindrical housing or box housing that is mounted on a panel, orifice plate or ring.
Air circulating fan means a fan that has no provision for connection to ducting or separation of the fan inlet from its outlet using a pressure boundary, operates against zero external static pressure loss, and is not a jet fan.
Air circulating fan discharge area means the area of a circle having a diameter equal to the blade tip diameter.
Air circulating fan outlet area means the gross inside area measured at the plane of the outlet opening.
Air-cooled steam condenser means a device for rejecting heat to the atmosphere through the indirect condensing of steam inside air-cooled finned tubes.
Axial inline fan means a fan with an axial impeller and a cylindrical housing with or without turning vanes.
Axial panel fans means an axial fan, without cylindrical housing, that includes a panel, orifice plate, or ring with brackets for mounting through a wall, ceiling, or other structure that separates the fan's inlet from its outlet.
Basic model, with respect to fans and blowers, means all units of fans and blowers manufactured by one manufacturer, having the same primary energy source, and having essentially identical electrical, physical, and functional (e.g., aerodynamic) characteristics that affect energy consumption. In addition:
(1) All variations of blade pitches of an adjustable-pitch axial fan may be considered a single basic model; and
(2) All variations of impeller widths and impeller diameters of a given full-width impeller and full-diameter impeller centrifugal fan may be considered a single basic model.
Box fan means an axial housed air circulating fan head without a cylindrical housing that is mounted on a panel, orifice plate or ring and is mounted in a box housing.
Centrifugal housed fan means a fan with a centrifugal or mixed flow impeller in which airflow exits into a housing that is generally scroll-shaped to direct the air through a single fan outlet. A centrifugal housed fan does not include a radial impeller.
Centrifugal inline fan means a fan with a centrifugal or mixed flow impeller in which airflow enters axially at the fan inlet and the housing redirects radial airflow from the impeller to exit the fan in an axial direction.
Centrifugal unhoused fan means a fan with a centrifugal or mixed flow impeller in which airflow enters through a panel and discharges into free space. Inlets and outlets are not ducted. This fan type also includes fans designed for use in fan arrays that have partition walls separating the fan from other fans in the array.
Cross-flow fan means a fan or blower with a housing that creates an airflow path through the impeller in a direction at right angles to its axis of rotation and with airflow both entering and exiting the impeller at its periphery. Inlets and outlets can optionally be ducted.
Cylindrical air circulating fan means an axial housed air circulating fan head with a cylindrical housing that is not a Positive Pressure Ventilator as defined in AMCA 240-15 (incorporated by reference, see § 431.173).
Evaporative field erected closed-circuit cooling tower means a structure which rejects heat to the atmosphere through the indirect cooling of a process fluid stream to a lower temperature by partial evaporation of an external recirculating water flow.
Evaporative field erected open-circuit cooling tower means a structure which rejects heat to the atmosphere through the direct cooling of a water stream to a lower temperature by partial evaporation.
Fan or blower means a rotary bladed machine used to convert electrical or mechanical power to air power, with an energy output limited to 25 kilojoule (kJ)/kilogram (kg) of air. It consists of an impeller, a shaft and bearings and/or driver to support the impeller, as well as a structure or housing. A fan or blower may include a transmission, driver, and/or motor controller.
Fan static air power means the static power delivered to air by the fan or blower; it is proportional to the product of the fan airflow rate, the fan static pressure and the compressibility coefficient and is calculated in accordance with section 7.8.1 of AMCA 210-16 (incorporated by reference, see § 431.173), using fan static pressure instead of fan total pressure.
Fan total air power means the total power delivered to air by the fan or blower; it is proportional to the product of the fan airflow rate, the fan total pressure and the compressibility coefficient and is calculated in accordance with section 7.8.1 of AMCA 210-16 (incorporated by reference, see § 431.173).
Field erected air-cooled (dry) cooler means a structure which rejects heat to the atmosphere from a fluid, either liquid, gas or a mixture thereof, flowing through an air-cooled internal coil.
Field erected evaporative condenser means a structure which rejects heat to the atmosphere through the indirect condensing of a refrigerant in an internal coil by partial evaporation of an external recirculating water flow.
Full-diameter impeller means maximum impeller diameter with which a given fan or blower basic model is distributed in commerce.
Full-width impeller means the maximum impeller width with which a given fan or blower basic model is distributed in commerce.
Housed air circulating fan head means an air circulating fan with an axial or centrifugal impeller, and a housing.
Housed centrifugal air circulating fan means a housed air circulating fan head with a centrifugal or radial impeller in which airflow exits into a housing that is generally scroll shaped to direct the air through a single, narrow fan outlet.
Induced flow fan means a type of laboratory exhaust fan with a nozzle and windband; the fan's outlet airflow is greater than the inlet airflow due to induced airflow. All airflow entering the inlet exits through the nozzle. Airflow exiting the windband includes the nozzle airflow plus the induced airflow.
Jet fan means a fan designed and marketed specifically for producing a high velocity air jet in a space to increase its air momentum. Jet fans are rated using thrust. Inlets and outlets are not ducted but may include acoustic silencers.
Packaged air-cooled (dry) cooler means a device which rejects heat to the atmosphere from a fluid, either liquid, gas or a mixture thereof, flowing through an air-cooled internal coil.
Packaged evaporative closed-circuit cooling tower means a device which rejects heat to the atmosphere through the indirect cooling of a process fluid stream in an internal coil to a lower temperature by partial evaporation of an external recirculating water flow.
Packaged evaporative condenser means a device which rejects heat to the atmosphere through the indirect condensing of a refrigerant in an internal coil by partial evaporation of an external recirculating water flow.
Packaged evaporative open-circuit cooling tower means a device which rejects heat to the atmosphere through the direct cooling of a water stream to a lower temperature by partial evaporation.
Power roof ventilator means a fan with an internal driver and a housing to prevent precipitation from entering the building. It has a base designed to fit over a roof or wall opening, usually by means of a roof curb.
Radial-housed fan means a fan with a radial impeller in which airflow exits into a housing that is generally scroll-shaped to direct the air through a single fan outlet. Inlets and outlets can optionally be ducted.
Safety Fan means:
(1) A reversible axial fan in cylindrical housing that is designed and marketed for use in ducted tunnel ventilation that will reverse operation under emergency ventilation conditions;
(2) A fan for use in explosive atmospheres tested and marked according to the English version of ISO 80079-36:2016 (incorporated by reference, see § 431.173);
(3) An electric-motor-driven-Positive Pressure Ventilator as defined in AMCA 240-15 (incorporated by reference, see § 431.173);
(4) A fan bearing a listing for “Power Ventilators for Smoke Control Systems” in compliance with UL 705 (incorporated by reference, see § 431.173); or
(5) A laboratory exhaust fan designed and marketed specifically for exhausting contaminated air vertically away from a building using a high-velocity discharge.
Unhoused air circulating fan head means an air circulating fan without a housing, having an axial impeller with a ratio of fan-blade span (in inches) to maximum rate of rotation (in revolutions per minute) less than or equal to 0.06. The impeller may or may not be guarded.
[88 FR 27389, May 1, 2023, as amended at 88 FR 53375, Aug. 8, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Ave. SW, EE-5B, Washington, DC 20585, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email: fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section.
(b) AMCA. Air Movement and Control Association International, Inc., 30 West University Drive, Arlington Heights, IL 60004-1893; (847) 394-0150; www.amca.org.
(1) ANSI/AMCA Standard 210-16 (“AMCA 210-16”), Laboratory Methods of Testing Fans for Certified Aerodynamic Performance Rating, ANSI-approved August 26, 2016; IBR approved for § 431.172; appendix A to this subpart. (Co-published as ASHRAE 51-16).
(2) ANSI/AMCA Standard 214-21 (“AMCA 214-21”), Test Procedure for Calculating Fan Energy Index (FEI) for Commercial and Industrial Fans and Blowers, ANSI-approved March 1, 2021; IBR approved for § 431.174; appendix A to this subpart.
(3) ANSI/AMCA Standard 230-23 (“AMCA 230-23”), Laboratory Methods of Testing Air Circulating Fans for Rating and Certification, ANSI-approved February 10, 2023. IBR approved for appendix B to this subpart.
(4) ANSI/AMCA Standard 240-15 (“AMCA 240-15”), Laboratory Methods of Testing Positive Pressure Ventilators for Aerodynamic Performance Rating, ANSI-approved May 9, 2015; IBR approved for § 431.172.
(c) ISO. International Organization for Standardization, Chemin de Blandonnet 8, CP 401, 1214 Vernier, Geneva, Switzerland; www.iso.org.
(1) ISO 5801:2017(E) (“ISO 5801:2017”), Fans—Performance testing using standardized airways, Third Edition, approved September 2017; IBR approved for appendix A to this subpart.
(2) ISO 80079-36:2016, Explosive atmospheres—Part 36: Non-electrical equipment for explosive atmospheres—Basic method and requirements, Edition 1.0, February 2016; IBR approved for § 431.172.
(d) UL. Underwriters Laboratories, 333 Pfingsten Road, Northbrook, Illinois, 60062; www.shopulstandards.com.
(1) UL 705, Standard for Safety for Power Ventilators, Edition 7, July 19, 2017 (including revisions through August 19, 2022); IBR approved for § 431.172.
(2) [Reserved].
[88 FR 27390, May 1, 2023, as amended at 88 FR 53375, Aug. 8, 2023]
(a) Scope for fans and blowers other than air circulating fans. A fan or blower, other than an air circulating fan is subject to the test procedure in this section if it meets the following criteria:
(1) Is a centrifugal housed fan; radial housed fan; centrifugal inline fan; centrifugal unhoused fan; centrifugal power roof ventilator exhaust fan; centrifugal power roof ventilator supply fan; axial inline fan; axial panel fan; or axial power roof ventilator fan;
(2) Is not:
(i) A radial housed unshrouded fan with blade diameter at tip less than 30 inches or a blade width of less than 3 inches;
(ii) A safety fan;
(iii) An induced flow fan;
(iv) A jet fan;
(v) A cross-flow fan;
(vi) A fan manufactured exclusively to be powered by internal combustion engines;
(vii) A fan that create a vacuum of 30 inches water gauge or greater;
(viii) A fan that is designed and marketed to operate at or above 482 degrees Fahrenheit (250 degrees Celsius); or
(ix) A fan and blower embedded in the equipment listed in paragraph (a)(3) of this section;
(3) Is not an embedded fan subject to the following exclusions:
(i) The test procedure in this section does not apply to fans or blowers that are embedded in:
(A) Single phase central air conditioners and heat pumps rated with a certified cooling capacity less than 65,000 British thermal units per hour (“Btu/h”) cooling capacity, that are subject to DOE's energy conservation standard at 10 CFR 430.32(c);
(B) Three phase, air-cooled, small commercial packaged air-conditioning and heating equipment rated with a certified cooling capacity less than 65,000 Btu/h cooling capacity, that are subject to DOE's energy conservation standard at § 431.97(b);
(C) Transport refrigeration (i.e., Trailer refrigeration, Self-powered truck refrigeration, Vehicle-powered truck refrigeration, Marine/Rail container refrigerant);
(D) Vacuum cleaners;
(E) Heat Rejection Equipment: Packaged evaporative open-circuit cooling towers; Evaporative field-erected open-circuit cooling towers; Packaged evaporative closed-circuit cooling towers; Evaporative field-erected closed-circuit cooling towers; Packaged evaporative condensers; Field-erected evaporative condensers; Packaged air-cooled (dry) coolers; Field-erected air-cooled (dry) cooler; Air-cooled steam condensers; Hybrid (water saving) versions of all of the previously listed equipment that contain both evaporative and air-cooled heat exchange sections;
(F) Air curtains; and
(G) Direct expansion-dedicated outdoor air system that are subject to any of DOE's test procedures in appendix B to subpart F of this part.
(ii) The test procedure in this section does not apply to supply or condenser fans or blowers that are embedded in:
(A) Air-cooled commercial package air conditioners and heat pumps (“CUAC,” “CUHP”) with a certified cooling capacity between 5.5 ton (65,000 Btu/h) and 63.5 ton (760,000 Btu/h) that are subject to DOE's energy conservation standard at § 431.97(b);
(B) Water-cooled and evaporatively-cooled commercial air conditioners that are subject to DOE's energy conservation standard at § 431.97(b);
(C) Water-source heat pumps that are subject to DOE's energy conservation standard at § 431.97(b);
(D) Single package vertical air conditioners and heat pumps that are subject to DOE's energy conservation standard at § 431.97(d);
(E) Packaged terminal air conditioners (“PTAC”) and packaged terminal heat pumps (PTHP) that are subject to DOE's energy conservation standard at § 431.97(c);
(F) Computer room air conditioners that are subject to DOE's energy conservation standard at § 431.97(e); and
(G) Variable refrigerant flow multi-split air conditioners and heat pumps that are subject to DOE's energy conservation standard at § 431.97(f); and
(4) In addition, the test procedure is only applicable to fan or blower duty points with the following characteristics, measured or calculated in accordance with the test procedure set forth in appendix A of this subpart:
(i)
(A) Fan shaft input power equal to or greater than 1 horsepower; or
(B) Fan electrical power equal to or greater than 0.89 kW; and
(ii)
(A) Fan static air power equal to or less than 150 horsepower for fans using a static pressure basis fan energy index (“FEI”) in accordance with the required test configuration listed in table 7.1 of AMCA 214-21 (incorporated by reference, see § 431.173); or
(B) Fan total air power equal to or less than 150 horsepower for fans using a total pressure basis FEI in accordance with the required test configuration listed in table 7.1 of AMCA 214-21;
(b) Scope for air circulating fans. The test procedure in this section applies to all air circulating fans with input power greater than or equal to 125W at maximum speed.
(c) Testing and calculations for fans and blowers other than air circulating fans. Determine the FEI, the fan electrical power (“FEP”), and fan shaft power (as applicable) at each duty point, as specified by the manufacturer, using the test procedure set forth in appendix A of this subpart.
(d) Testing and calculations for air circulating fan. Determine the air circulating fan efficacy in cubic feet per minute per watt at maximum speed using the test procedure set forth in appendix B to this subpart.
[88 FR 27391, May 1, 2023, as amended at 88 FR 53375, Aug. 8, 2023]
After October 30, 2023, any representations made with respect to energy use or efficiency of fans and blowers subject to testing pursuant to § 431.174 must be made in accordance with this appendix. Any optional representations of fan energy index in the optional test configuration listed in table 7.1 of AMCA 214-21 (FEIoptional) must be accompanied by a representation of fan energy index in the required test configuration listed in table 7.1 of AMCA 214-21 (FEI).
0. Incorporation by Reference
In § 431.173, DOE incorporated by reference the entire standard for AMCA 210-16, AMCA 214-21, and ISO 5801:2017; however, only enumerated provisions of those documents are applicable as follows. In cases where there is a conflict, the language of this appendix takes precedence over those documents.
0.1 AMCA 210-16:
(a) Section 3, “Definitions/Units of Measure/Symbols”;
(b) Section 4, “Instruments and Methods of Measurement” ;
(c) Section 5, “Test Setups and Equipment”;
(d) Section 6, “Observation and Conduct of Test”;
(e) Section 7, “Calculations” excluding Section 7.9.2, “Conversion to other rotational speeds and air densities with compressible flow” and Section 7.9.3, “Conversion formulae for new densities and new rotational speeds”;
0.2. AMCA 214-21:
(a) Section 2, “References (Normative),” as referenced in section 2.2 of this appendix;
(b) Section 3, “Definitions,” as referenced in section 1 of this appendix;
(c) Section 4, “Calculation of the FEI for a Single Duty Point,” as referenced in section 2.6 of this appendix;
(d) Section 5, “Reference Fan Electrical Power (FEPref),” as referenced in section 2.6 of this appendix;
(e) Section 6.1, “Wire-to-Air Testing at the Required Duty Point,” as referenced in section 2.2 of this appendix;
(f) Section 6.2, “Calculated Ratings Based on Wire-to-Air Testing,” as referenced in section 2.2 of this appendix;
(g) Section 6.3, “Bare Shaft Fans,” as referenced in section 2.2 of this appendix;
(h) Section 6.4, “Fans with Polyphase Regulated Motor”, excluding Section 6.4.1.4, “Requirements for the VFD, if included” and Section 6.4.2.4, “Combined motor-VFD efficiency” as referenced in section 2.2 of this appendix;
(i) Section 7, “Testing,” as referenced in sections 2.2 and 2.3 of this appendix;
(j) Section 8, “Rating Development”, excluding Section 8.2.2, “Separate Fan and Motor Tests” and Section 8.3, “Appurtenances” as referenced in section 2.2 of this appendix;
(k) Annex D, “Motor Performance Constants (Normative),” as referenced in section 2.2 of this appendix;
(l) Annex E, “Calculation Methods for Fans Tested Shaft-to-Air,” as referenced in section 2.2 of this appendix;
(m) Annex G, “Wire-to-Air Measurement—Calculation to Other Speeds and Densities (Normative),” as referenced in section 2.2 of this appendix;
(n) Annex J, “Other data and calculations to be retained,” as referenced in section 2.2 of this appendix; and
(o) Annex K, “Proportionality and Dimensional Requirements (Normative),” as referenced in section 2.2 of this appendix.
0.3. ISO 5801:2017:
(a) Section 3, “Terms and Definitions”;
(b) Section 4, “Symbols, Abbreviated Terms and Subscripts”;
(c) Section 5, “General”;
(d) Section 6, “Test Configurations”;
(e) Section 7, “Carrying out the Test”;
(f) Section 8, “Airways for Duct Configuration”;
(g) Section 9, “Standardized Test Chambers”;
(h) Section 10, “Various Component Parts for a Laboratory Setup”;
(i) Section 11, “Standard Test Configurations”;
(j) Section 12, “Measurements”;
(k) Section 13, “Reference Conditions”;
(l) Section 15, “Calculations”;
(m) Section 16, “Fan Characteristic Curves”; and
(n) Section 17, “Uncertainty Analysis”.
1. Definitions
The definitions applicable to this appendix are defined in § 431.172 and in section 3, “Definitions,” of AMCA 214-21. In cases where there is a conflict, the definitions in § 431.172 take precedence over AMCA 214-21.
2. Test Procedure for Fans and Blowers Other Than Air Circulating Fans
2.1. General.
This section describes the test procedure for fans and blowers other than air circulating fans. In cases where there is a conflict, the provisions in this appendix take precedence over AMCA 214-21. Where AMCA 214-21 refers to Annex A, “Polyphase Regulated Motor Efficiencies (Normative),” of AMCA 214-21, Table 5 of § 431.25 or the currently applicable standards in § 431.25 must be used instead.
2.2. Testing
2.2.1. General.
The fan electrical power (FEPact) in kilowatts must be determined at every duty point specified by the manufacturer in accordance with one of the test methods listed in table 1, and the following sections of AMCA 214-21: Section 2, “References (Normative)”; Section 7, “Testing,” including the provisions of AMCA 210-16 and ISO 5801:2017 as referenced by Section 7 and implicated by sections 2.2.2 and 2.2.3 of this appendix; Section 8.1, “Laboratory Measurement Only” (as applicable); and Annex J, “Other data and calculations to be retained.”
| Driver | Motor
controller present? |
Transmission
configuration? |
Test method | Applicable section(s) of AMCA 214-21 |
|---|---|---|---|---|
| Electric motor | Yes or No | Any | Wire-to-air | 6.1 “Wire-to-Air Testing at the Required Duty Point”. |
| Electric motor | Yes or No | Any | Calculation based on Wire-to-air testing | 6.2 “Calculated Ratings Based on Wire to Air Testing” (references Section 8.2.3, “Calculation to other speeds and densities for wire-to-air testing,” and Annex G, “Wire-to-Air Measurement—Calculation to Other Speeds and Densities (Normative)”). |
| Regulated polyphase motor | No | Direct drive, V-belt drive, flexible coupling or synchronous belt drive | Shaft-to-air | 6.4 “Fans with Polyphase Regulated Motors,” (references Annex D, “Motor Performance Constants (Normative)”) *. |
| None or non-electric | No | None | Shaft-to-air | Section 6.3, “Bare Shaft Fans”. |
| Regulated polyphase motor | No | Direct drive, V-belt drive, flexible coupling or synchronous belt drive | Calculation based on Shaft-to-air testing | Section 8.2.1, “Fan laws and other calculation methods for shaft-to-air testing”(references Annex D, “Motor Performance Constants (Normative),” Annex E, “Calculation Methods for Fans Tested Shaft-to-Air,” and Annex K, “Proportionality and Dimensional Requirements (Normative)”). |
| None or non-electric | No | None | Calculation based on Shaft-to-air testing | Section 8.2.1, “Fan laws and other calculation methods for shaft-to-air testing” (references Annex E, “Calculation Methods for Fans Tested Shaft-to-Air,” and Annex K, “Proportionality and Dimensional Requirements (Normative)”). |
| * Excluding Section 6.4.1.4, “Requirements for the VFD, if included” and Section 6.4.2.4, “Combined motor-VFD efficiency.” | ||||
Testing must be performed in accordance with the required test configuration listed in Table 7.1 of AMCA 214-21. The following values must be determined in accordance with this appendix at each duty point specified by the manufacturer: fan airflow in cubic feet per minute; fan air density; fan total pressure in inches of water gauge for fans using a total pressure basis FEI in accordance with Table 7.1 of AMCA 214-21; fan static pressure in inches of water gauge for fans using a static pressure basis FEI in accordance with Table 7.1 of AMCA 214-21; fan speed in revolutions per minute; and fan shaft input power in horsepower for fans tested in accordance with sections 6.3 or 6.4 of AMCA 214-21.
In addition, if applying the equations in Section E.2 of Annex E of AMCA 214-21 for compressible flows, the compressibility coefficients must be included in the equations as applicable.
All measurements must be recorded at the resolution of the test instrumentation and calculations must be rounded to the number of significant digits present at the resolution of the test instrumentation.
In cases where there is a conflict, the provisions in AMCA 214-21 take precedence over AMCA 210-16 and ISO 5801:2017. In addition, the provisions in this appendix apply.
2.2.2 Power Roof Ventilators
Centrifugal Power Roof Ventilators that are both supply and exhaust must be tested in both supply and exhaust configurations as listed in table 7.1 of AMCA 214-21.
2.2.3 Embedded Fans
Embedded fans that are not manufactured in a standalone configuration must be tested in a standalone configuration. If some components of the bare shaft fan are not removable without causing irreversible damage to the equipment into which the fan is embedded, testing must be performed using additional fan components, except for the fan impeller, that are geometrically identical to that of the fan embedded inside the larger piece of equipment for testing.
2.3. Power Supply
Any wire-to-air testing must be conducted at the supply frequency, phase, and voltages specified in this section. The frequency and voltage must be selected in accordance with section 7.8. of AMCA 214-21. Fans and blowers rated for operation for single- or multi-phase power supply must be tested with single- or multi-phase electricity, respectively. Fans and blowers, capable of operating with single- and multi-phase power supply, must be tested using multi-phase electricity.
2.4. Stability Conditions.
The following conditions must be met to establish system stability prior to collecting test data:
(a) Barometric pressure, dry bulb temperature and wet bulb temperature in the general test area must be captured at least every five seconds after the run-in period is completed and the ambient air density calculated from these values shall not vary by more than ±1 percent during verification of fan speed and fan input power stability.
(b) After the fan has been run-in, record the fan speed in rpm and the input power (in horsepower or watts) at least every 5 seconds for at least three 60-second intervals. Readings shall be made simultaneously. Repeat these measurements over 60-second intervals until:
(1) The average fan speed from the last 60-second interval varies by less than the absolute value of 1 percent or 1 rpm, whichever is greater, when compared to the average fan speed measured during the previous 60-second test interval;
(2) The average input power from the last 60-second interval by reaction dynamometer, torque meter or calibrated motor must be ±4 percent, or the average input power by electrical meter must be ±2 percent of the mean or 1 watt, whichever is greater, compared to the average input power measured during the previous 60-second test interval; and
(3) The slopes of a linear fit trendline calculated from the individual data collected for fan speed and input power during at least three 60-second sampling intervals include both positive and negative values (e.g., two positive and one negative slope value or one positive and two negative slope values). If three positive or three negative slopes are determined in succession, additional sampling intervals are required until slopes from three successive sampling intervals include both positive and negative values.
2.5. Sampling Intervals for Testing.
A test measurement must meet the following conditions:
(a) The sampling interval over which average test values are determined shall not exceed 60 seconds;
(b) The average fan speed from the most recent 60-second interval varies by less than the absolute value of 1 percent or 1 rpm, whichever is greater, when compared to the average fan speed measured during the previous 60-second test interval; and
(c) the average input power from the last 60-second interval by reaction dynamometer, torque meter or calibrated motor must be ±4 percent, or the average input power by electrical meter must be ±2 percent of the mean or 1 watt, whichever is greater, compared to the average input power measured during the previous 60-second test interval.
2.6. FEI calculation
The FEI must be determined at every duty point in accordance with Section 4, “Calculation of the FEI for a single duty point,” and Section 5, “Reference Fan Electrical Power (FEPref)” of AMCA 214-21. In addition, the FEI must be rounded to the nearest hundredths place; FEP must be rounded to three significant figures; and all measurements must be recorded at the resolution of the test instrument.
[88 FR 27391, May 1, 2023, as amended at 88 FR 53375, Aug. 8, 2023]
After October 30, 2023, any representations made with respect to energy use or efficiency of air circulating fans subject to testing pursuant to § 431.174 must be made in accordance with this appendix. Any optional representations of air circulating fan efficacy at speeds less than the air circulating fan's maximum speed must be accompanied by a representation of the air circulating fan efficacy at maximum speed.
0. Incorporation by Reference
In § 431.173, DOE incorporated by reference the entire standard for AMCA 230-23; however, only enumerated provisions of those documents are applicable as follows. In cases where there is a conflict, the language of this appendix takes precedence over those documents.
0.1 AMCA 230-23:
(a) Section 4, “Definitions/Units of Measurement/Symbols,”;
(b) Section 5, “Instruments and Methods of Measurement,”;
(c) Section 6, “Equipment and Setup,”;
(d) Section 7, “Observations and Conduct of Test,”;
(e) Section 8, “Calculations,” excluding equations 8.5 and 8.6; and
(f) Section 9, “Report and Results of Test,”
1. Definitions
The definitions applicable to this appendix are defined in § 431.172 and in Section 4, “Definitions/Units of Measurement/Symbols,” of AMCA 230-23. In cases where there is a conflict, the definitions in § 431.172 take precedence over AMCA 230-23.
2. Test Procedure for Air Circulating Fans
2.1. General
This section describes the test procedure for air circulating fans.
2.2. Testing
2.2.1. General
The air circulating fan efficacy (Eƒƒcirc) in cubic feet per minute (“CFM”) per watt (“W”) (“CFM/W”) at maximum speed must be determined in accordance with the applicable sections of AMCA 230-23 as listed in section 0.1 of this appendix. In addition, testing must be conducted in accordance with the provisions in sections 2.3 through 2.5 of this appendix. Optional testing speeds lower than maximum speed is permitted. Speeds less than maximum speeds must be expressed at a percentage of maximum speed (e.g., 50 percent) and the air circulating fan efficacy at lower speed must include the speed percentage in its subscript (e.g., Eƒƒcirc,50).
All measurements must be recorded at the resolution of the test instrumentation and calculations must be rounded to the number of significant digits of the resolution of the test instrumentation.
2.3. Air circulating fans without motors
Air circulating fans distributed in commerce without an electric motor must be tested using an electric motor as recommended in the manufacturer's catalogs or distributed in commerce with the air circulating fan. If more than one motor is available in manufacturer's catalogs or distributed in commerce with the air circulating fan, testing must be conducted using the least efficient motor capable of running the fan at the fan's maximum allowable speed.
2.4. Power Supply.
The test must be conducted at the frequency, phase, and voltages specified in this section.
2.4.1. Frequency.
Air circulating fans rated for operation with only 60 Hz power supply must be tested with 60 Hz electricity. Air circulating fans capable of operating with 50 Hz and 60 Hz electricity must be tested with 60 Hz electricity.
2.4.2. Phase.
Air circulating fans rated for operation for single- or multi-phase power supply must be tested with single- or multi-phase power electricity, respectively. Air circulating fans, capable of operating with single- and multi-phase power supply, must be tested using multi-phase electricity.
2.4.3. Voltage.
Select the supply voltage as follows:
(a) For air circulating fans tested with single-phase electricity, the supply voltage must be:
(1) 120 V if the air circulating fan's minimum rated voltage is 120 V or the lowest rated voltage range contains 120 V,
(2) 240 V if the air circulating fan's minimum rated voltage is 240 V or the lowest rated voltage range contains 240 V, or
(3) The air circulating fan's minimum rated voltage (if a voltage range is not given) or the mean of the lowest rated voltage range, in all other cases.
(b) For air circulating fans tested with multi-phase electricity, the supply voltage must be
(1) 240 V if the air circulating fan's minimum rated voltage is 240 V or the lowest rated voltage range contains 240 V, or
(2) The air circulating fan's minimum rated voltage (if a voltage range is not given) or the mean of the lowest rated voltage range, in all other cases.
2.5. Stability Conditions.
In addition to the test requirements specified in sections 7.1 and 7.3 of AMCA 230-23, the following conditions must be met to establish system stability prior to collecting test data:
(a) Test voltage shall be captured at least every five seconds and shall not vary by more than ±1 percent during each test. Barometric pressure, dry bulb temperature and wet bulb temperature in the general test area for calculation of air density must be captured at least every five seconds and the calculated ambient air density shall not vary by more than ±1 percent during each test.
(b) After a run-in time of at least 15 minutes, record the fan speed in rpm, the input power in watts, and load differential in pound-force for at least 3 120-second intervals. Repeat these measurements over additional 120-second intervals until:
(1) The average fan speed of the last 120-second interval varies by less than the absolute value of 1 percent or 1 rpm, whichever is greater, when compared to the average fan speed measured during the previous 120-second test interval;
(2) The average input power of the last 120-second interval varies by less than the absolute value of 1 percent or 1 watt, whichever is greater, compared to the average input power measured during the previous 120-second test interval;
(3) The average load differential of the last 120-second interval varies by less than the absolute value of 1 percent compared to the average load differential during the previous 120-second test interval; and
(4) The slopes of a linear fit trendline calculated from the individual data collected for fan speed, input power, and load differential during at least three 120-second intervals include both positive and negative values (e.g., two positive and one negative slope value or one positive and two negative slope values). If three positive or three negative slopes are determined in succession, additional sampling intervals are required until slopes from three successive 120-second intervals include both positive and negative values.
2.6. Calculation of Ambient Air Density.
For any references to ambient air density, ρ0, in AMCA 230-23, calculate ρ0, expressed in kg/m3 when using SI units or lbm/ft3 when using I-P units, as follows:
where pb is the measured barometric pressure of the air, Td0 is the measured dry-bulb temperature of the air, pp is the partial vapor pressure, R is the gas constant, which are all determined according to section 8.2 of AMCA 230-23.
[88 FR 27393, May 1, 2023, as amended at 88 FR 53376, Aug. 8, 2023]
70 FR 60416, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for distribution transformers, pursuant to Parts B and C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6317.
[71 FR 24995, Apr. 27, 2006]
The following definitions apply for purposes of this subpart:
Autotransformer means a transformer that:
(1) Has one physical winding that consists of a series winding part and a common winding part;
(2) Has no isolation between its primary and secondary circuits; and
(3) During step-down operation, has a primary voltage that is equal to the total of the series and common winding voltages, and a secondary voltage that is equal to the common winding voltage.
Auxiliary device means a localized component of a distribution transformer that is a circuit breaker, switch, fuse, or surge/lightning arrester.
Basic model means a group of models of distribution transformers manufactured by a single manufacturer, that have the same insulation type (i.e., liquid-immersed or dry-type), have the same number of phases (i.e., single or three), have the same standard kVA rating, and do not have any differentiating electrical, physical or functional features that affect energy consumption. Differences in voltage and differences in basic impulse insulation level (BIL) rating are examples of differentiating electrical features that affect energy consumption.
Distribution transformer means a transformer that—
(1) Has an input line voltage of 34.5 kV or less;
(2) Has an output line voltage of 600 V or less;
(3) Is rated for operation at a frequency of 60 Hz; and
(4) Has a capacity of 10 kVA to 5000 kVA for liquid-immersed units and 15 kVA to 5000 kVA for dry-type units; but
(5) The term “distribution transformer” does not include a transformer that is an—
(i) Autotransformer;
(ii) Drive (isolation) transformer;
(iii) Grounding transformer;
(iv) Machine-tool (control) transformer;
(v) Nonventilated transformer;
(vi) Rectifier transformer;
(vii) Regulating transformer;
(viii) Sealed transformer;
(ix) Special-impedance transformer;
(x) Testing transformer;
(xi) Transformer with tap range of 20 percent or more;
(xii) Uninterruptible power supply transformer; or
(xiii) Welding transformer.
Drive (isolation) transformer means a transformer that:
(1) Isolates an electric motor from the line;
(2) Accommodates the added loads of drive-created harmonics;
(3) Is designed to withstand the additional mechanical stresses resulting from an alternating current adjustable frequency motor drive or a direct current motor drive; and
(4) Has a rated output voltage that is neither “208Y/120” nor “480Y/277”.
Efficiency means the ratio of the useful power output to the total power input.
Excitation current or no-load current means the current that flows in any winding used to excite the transformer when all other windings are open-circuited.
Grounding transformer means a three-phase transformer intended primarily to provide a neutral point for system-grounding purposes, either by means of:
(1) A grounded wye primary winding and a delta secondary winding; or
(2) A transformer with its primary winding in a zig-zag winding arrangement, and with no secondary winding.
Liquid-immersed distribution transformer means a distribution transformer in which the core and coil assembly is immersed in an insulating liquid.
Load loss means, for a distribution transformer, those losses incident to a specified load carried by the transformer, including losses in the windings as well as stray losses in the conducting parts of the transformer.
Low-voltage dry-type distribution transformer means a distribution transformer that has an input voltage of 600 volts or less and has the core and coil assembly immersed in a gaseous or dry-compound insulating medium.
Machine-tool (control) transformer means a transformer that is equipped with a fuse or other over-current protection device, and is generally used for the operation of a solenoid, contactor, relay, portable tool, or localized lighting.
Medium-voltage dry-type distribution transformer means a distribution transformer in which the core and coil assembly is immersed in a gaseous or dry-compound insulating medium, and which has a rated primary voltage between 601 V and 34.5 kV.
Mining distribution transformer means a medium-voltage dry-type distribution transformer that is built only for installation in an underground mine or surface mine, inside equipment for use in an underground mine or surface mine, on-board equipment for use in an underground mine or surface mine, or for equipment used for digging, drilling, or tunneling underground or above ground, and that has a nameplate which identifies the transformer as being for this use only.
No-load loss means those losses that are incident to the excitation of the transformer.
Nonventilated transformer means a dry-type transformer constructed so as to prevent external air circulation through the coils of the transformer while operating at zero gauge pressure.
Per-unit load means the fraction of rated load.
Phase angle means the angle between two phasors, where the two phasors represent progressions of periodic waves of either:
(1) Two voltages;
(2) Two currents; or
(3) A voltage and a current of an alternating current circuit.
Phase angle correction means the adjustment (correction) of measurement data to negate the effects of phase angle error.
Phase angle error means incorrect displacement of the phase angle, introduced by the components of the test equipment.
Rectifier transformer means a transformer that operates at the fundamental frequency of an alternating-current system and that is designed to have one or more output windings connected to a rectifier.
Reference temperature means the temperature at which the transformer losses are determined, and to which such losses are corrected if testing is done at a different point. (Reference temperature values are specified in the test method in appendix A to this subpart.)
Regulating transformer means a transformer that varies the voltage, the phase angle, or both voltage and phase angle, of an output circuit and compensates for fluctuation of load and input voltage, phase angle or both voltage and phase angle.
Sealed transformer means a dry-type transformer designed to remain hermetically sealed under specified conditions of temperature and pressure.
Special-impedance transformer means a transformer built to operate at an impedance outside of the normal impedance range for that transformer's kVA rating. The normal impedance range for each kVA rating for liquid-immersed and dry-type transformers is shown in Tables 1 and 2, respectively.
| Single-phase transformers | Three-phase transformers | ||
|---|---|---|---|
| kVA | Impedance
(%) |
kVA | Impedance
(%) |
| 10 <= kVA < 50 | 1.0-4.5 | 15 <= kVA < 75 | 1.0-4.5 |
| 50 <= kVA < 250 | 1.5-4.5 | 75 <= kVA < 112.5 | 1.0-5.0 |
| 250 <= kVA < 500 | 1.5-6.0 | 112.5 <= kVA < 500 | 1.2-6.0 |
| 500 <= kVA < 667 | 1.5-7.0 | 500 <= kVA < 750 | 1.5-7.0 |
| 667 <= kVA <= 833 | 5.0-7.5 | 750 <= kVA <= 5000 | 5.0-7.5 |
| Single-phase transformers | Three-phase transformers | ||
|---|---|---|---|
| kVA | Impedance
(%) |
kVA | Impedance
(%) |
| 10 <= kVA < 50 | 1.0-4.5 | 15 <= kVA < 75 | 1.0-4.5 |
| 50 <= kVA < 250 | 1.5-4.5 | 75 <= kVA < 112.5 | 1.0-5.0 |
| 250 <= kVA < 500 | 1.5-6.0 | 112.5 <= kVA < 500 | 1.2-6.0 |
| 500 <= kVA < 667 | 1.5-7.0 | 500 <= kVA < 750 | 1.5-7.0 |
| 667 <= kVA <= 833 | 5.0-7.5 | 750 <= kVA <= 5000 | 5.0-7.5 |
Submersible distribution transformer means a liquid-immersed distribution transformer, so constructed as to be operable when fully or partially submerged in water including the following features—
(1) Has sealed-tank construction; and
(2) Has the tank, cover, and all external appurtenances made of corrosion-resistant material or with appropriate corrosion resistant surface treatment to induce the components surface to be corrosion resistant.
Temperature correction means the mathematical correction(s) of measurement data, obtained when a transformer is tested at a temperature that is different from the reference temperature, to the value(s) that would have been obtained if the transformer had been tested at the reference temperature.
Terminal means a conducting element of a distribution transformer providing electrical connection to an external conductor that is not part of the transformer.
Test current means the current of the electrical power supplied to the transformer under test.
Test frequency means the frequency of the electrical power supplied to the transformer under test.
Test voltage means the voltage of the electrical power supplied to the transformer under test.
Testing transformer means a transformer used in a circuit to produce a specific voltage or current for the purpose of testing electrical equipment.
Total loss means the sum of the no-load loss and the load loss for a transformer.
Transformer means a device consisting of 2 or more coils of insulated wire that transfers alternating current by electromagnetic induction from 1 coil to another to change the original voltage or current value.
Transformer with tap range of 20 percent or more means a transformer with multiple voltage taps, each capable of operating at full, rated capacity (kVA), whose range, defined as the difference between the highest voltage tap and the lowest voltage tap, is 20 percent or more of the highest voltage tap.
Uninterruptible power supply transformer means a transformer that is used within an uninterruptible power system, which in turn supplies power to loads that are sensitive to power failure, power sages, over voltage, switching transients, line notice, and other power quality factors. It does not include distribution transformers at the input, output, or by-pass of an uninterruptible power system.
Waveform correction means the adjustment(s) (mathematical correction(s)) of measurement data obtained with a test voltage that is non-sinusoidal, to a value(s) that would have been obtained with a sinusoidal voltage.
Welding transformer means a transformer designed for use in arc welding equipment or resistance welding equipment.
[70 FR 60416, Oct. 18, 2005, as amended at 71 FR 24995, Apr. 27, 2006; 71 FR 60662, Oct. 16, 2006; 72 FR 58239, Oct. 12, 2007; 78 FR 23433, Apr. 18, 2013; 86 FR 51252, Sept. 14, 2021; 89 FR 30039, Apr. 22, 2024; 90 FR 6795, Jan. 21, 2025]
The test procedure for measuring the energy efficiency of distribution transformers for purposes of EPCA is specified in appendix A to this subpart. The test procedure specified in appendix A to this subpart applies only to distribution transformers subject to energy conservation standards at § 431.196.
[86 FR 51252, Sept. 14, 2021]
(a) Low-Voltage Dry-Type Distribution Transformers.
(1) The efficiency of a low-voltage, dry-type distribution transformer manufactured on or after January 1, 2007, but before January 1, 2016, shall be no less than that required for the applicable kVA rating in the table below. Low-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | % | kVA | % |
| 15 | 97.7 | 15 | 97.0 |
| 25 | 98.0 | 30 | 97.5 |
| 37.5 | 98.2 | 45 | 97.7 |
| 50 | 98.3 | 75 | 98.0 |
| 75 | 98.5 | 112.5 | 98.2 |
| 100 | 98.6 | 150 | 98.3 |
| 167 | 98.7 | 225 | 98.5 |
| 250 | 98.8 | 300 | 98.6 |
| 333 | 98.9 | 500 | 98.7 |
| 750 | 98.8 | ||
| 1000 | 98.9 | ||
All efficiency values are at 35 percent per-unit load.
(2) The efficiency of a low-voltage, dry-type distribution transformer manufactured on or after January 1, 2016, but before April 23, 2029, shall be no less than that required for the applicable kVA rating in the following table. Low-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | kVA | ||
| 15 | 97.70 | 15 | 97.89 |
| 25 | 98.00 | 30 | 98.23 |
| 37.5 | 98.20 | 45 | 98.40 |
| 50 | 98.30 | 75 | 98.60 |
| 75 | 98.50 | 112.5 | 98.74 |
| 100 | 98.60 | 150 | 98.83 |
| 167 | 98.70 | 225 | 98.94 |
| 250 | 98.80 | 300 | 99.02 |
| 333 | 98.90 | 500 | 99.14 |
| 750 | 99.23 | ||
| 1000 | 99.28 | ||
| Note: All efficiency values are at 35 percent of nameplate-rated load, determined according to the DOE Test Method for Measuring the Energy Consumption of Distribution Transformers under appendix A to this subpart K. | |||
(3) The efficiency of a low-voltage dry-type distribution transformer manufactured on or after April 23, 2029, shall be no less than that required for their kVA rating in the following table. Low-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | Efficiency
(%) |
kVA | Efficiency
(%) |
| 15 | 98.39 | 15 | 98.31 |
| 25 | 98.60 | 30 | 98.58 |
| 37.5 | 98.74 | 45 | 98.72 |
| 50 | 98.81 | 75 | 98.88 |
| 75 | 98.95 | 112.5 | 98.99 |
| 100 | 99.02 | 150 | 99.06 |
| 167 | 99.09 | 225 | 99.15 |
| 250 | 99.16 | 300 | 99.22 |
| 333 | 99.23 | 500 | 99.31 |
| 750 | 99.38 | ||
| 1000 | 99.42 | ||
| Note: All efficiency values are at 35 percent of nameplate-rated load, determined according to the DOE Test Method for Measuring the Energy Consumption of Distribution Transformers under appendix A to this subpart K. | |||
(b) Liquid-Immersed Distribution Transformers.
(1) The efficiency of a liquid-immersed distribution transformer manufactured on or after January 1, 2010, but before January 1, 2016, shall be no less than that required for their kVA rating in the table below. Liquid-immersed distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | Efficiency (%) |
kVA | Efficiency (%) |
| 10 | 98.62 | 15 | 98.36 |
| 15 | 98.76 | 30 | 98.62 |
| 25 | 98.91 | 45 | 98.76 |
| 37.5 | 99.01 | 75 | 98.91 |
| 50 | 99.08 | 112.5 | 99.01 |
| 75 | 99.17 | 150 | 99.08 |
| 100 | 99.23 | 225 | 99.17 |
| 167 | 99.25 | 300 | 99.23 |
| 250 | 99.32 | 500 | 99.25 |
| 333 | 99.36 | 750 | 99.32 |
| 500 | 99.42 | 1000 | 99.36 |
| 667 | 99.46 | 1500 | 99.42 |
| 833 | 99.49 | 2000 | 99.46 |
| 2500 | 99.49 | ||
All efficiency values are at 50 percent per-unit load.
(2) The efficiency of a liquid-immersed distribution transformer, including submersible distribution transformers, manufactured on or after January 1, 2016, but before April 23, 2029, shall be no less than that required for their kVA rating in the following table. Liquid-immersed distribution transformers, including submersible distribution transformers, with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | Efficiency
(%) |
kVA | Efficiency
(%) |
| 10 | 98.70 | 15 | 98.65 |
| 15 | 98.82 | 30 | 98.83 |
| 25 | 98.95 | 45 | 98.92 |
| 37.5 | 99.05 | 75 | 99.03 |
| 50 | 99.11 | 112.5 | 99.11 |
| 75 | 99.19 | 150 | 99.16 |
| 100 | 99.25 | 225 | 99.23 |
| 167 | 99.33 | 300 | 99.27 |
| 250 | 99.39 | 500 | 99.35 |
| 333 | 99.43 | 750 | 99.40 |
| 500 | 99.49 | 1000 | 99.43 |
| 667 | 99.52 | 1500 | 99.48 |
| 833 | 99.55 | 2000 | 99.51 |
| 2500 | 99.53 | ||
| Note: All efficiency values are at 50 percent of nameplate-rated load, determined according to the DOE Test—Procedure, appendix A to this subpart K. | |||
(3) The efficiency of a liquid-immersed distribution transformer, that is not a submersible distribution transformer, manufactured on or after April 23, 2029, shall be no less than that required for their kVA rating in the following table. Liquid-immersed distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | Efficiency
(%) |
kVA | Efficiency
(%) |
| 10 | 98.77 | 15 | 98.92 |
| 15 | 98.88 | 30 | 99.06 |
| 25 | 99.00 | 45 | 99.14 |
| 37.5 | 99.10 | 75 | 99.22 |
| 50 | 99.15 | 112.5 | 99.29 |
| 75 | 99.23 | 150 | 99.33 |
| 100 | 99.29 | 225 | 99.38 |
| 167 | 99.46 | 300 | 99.42 |
| 250 | 99.51 | 500 | 99.38 |
| 333 | 99.54 | 750 | 99.43 |
| 500 | 99.59 | 1000 | 99.46 |
| 667 | 99.62 | 1500 | 99.51 |
| 833 | 99.64 | 2000 | 99.53 |
| 2500 | 99.55 | ||
| 3750 | 99.54 | ||
| 5000 | 99.53 | ||
| Note: All efficiency values are at 50 percent of nameplate-rated load, determined according to the DOE Test Method for Measuring the Energy Consumption of Distribution Transformers under appendix A to this subpart K. | |||
(4) The efficiency of a submersible distribution transformer, manufactured on or after April 23, 2029, shall be no less than that required for their kVA rating in the following table. Submersible distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||
|---|---|---|---|
| kVA | Efficiency
(%) |
kVA | Efficiency
(%) |
| 10 | 98.70 | 15 | 98.65 |
| 15 | 98.82 | 30 | 98.83 |
| 25 | 98.95 | 45 | 98.92 |
| 37.5 | 99.05 | 75 | 99.03 |
| 50 | 99.11 | 112.5 | 99.11 |
| 75 | 99.19 | 150 | 99.16 |
| 100 | 99.25 | 225 | 99.23 |
| 167 | 99.33 | 300 | 99.27 |
| 250 | 99.39 | 500 | 99.35 |
| 333 | 99.43 | 750 | 99.40 |
| 500 | 99.49 | 1000 | 99.43 |
| 667 | 99.52 | 1500 | 99.48 |
| 833 | 99.55 | 2000 | 99.51 |
| 2500 | 99.53 | ||
| Note: All efficiency values are at 50 percent of nameplate-rated load, determined according to the DOE Test—Procedure, appendix A to this subpart K. | |||
(c) Medium-Voltage Dry-Type Distribution Transformers.
(1) The efficiency of a medium-voltage dry-type distribution transformer manufactured on or after January 1, 2010, but before January 1, 2016, shall be no less than that required for their kVA and BIL rating in the table below. Medium-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| Single-phase | Three-phase | ||||||
|---|---|---|---|---|---|---|---|
| kVA | BIL* | kVA | BIL | ||||
| 20-45 kV | 46-95 kV | ≥96 kV | 20-45 kV | 46-95 kV | ≥96 kV | ||
| Efficiency (%) |
Efficiency (%) |
Efficiency (%) |
Efficiency (%) |
Efficiency (%) |
Efficiency (%) |
||
| 15 | 98.10 | 97.86 | 15 | 97.50 | 97.18 | ||
| 25 | 98.33 | 98.12 | 30 | 97.90 | 97.63 | ||
| 37.5 | 98.49 | 98.30 | 45 | 98.10 | 97.86 | ||
| 50 | 98.60 | 98.42 | 75 | 98.33 | 98.12 | ||
| 75 | 98.73 | 98.57 | 98.53 | 112.5 | 98.49 | 98.30 | |
| 100 | 98.82 | 98.67 | 98.63 | 150 | 98.60 | 98.42 | |
| 167 | 98.96 | 98.83 | 98.80 | 225 | 98.73 | 98.57 | 98.53 |
| 250 | 99.07 | 98.95 | 98.91 | 300 | 98.82 | 98.67 | 98.63 |
| 333 | 99.14 | 99.03 | 98.99 | 500 | 98.96 | 98.83 | 98.80 |
| 500 | 99.22 | 99.12 | 99.09 | 750 | 99.07 | 98.95 | 98.91 |
| 667 | 99.27 | 99.18 | 99.15 | 1000 | 99.14 | 99.03 | 98.99 |
| 833 | 99.31 | 99.23 | 99.20 | 1500 | 99.22 | 99.12 | 99.09 |
| 2000 | 99.27 | 99.18 | 99.15 | ||||
| 2500 | 99.31 | 99.23 | 99.20 | ||||
| * BIL means basic impulse insulation level. | |||||||
All efficiency values are at 50 percent per-unit load.
(2) The efficiency of a medium-voltage dry-type distribution transformer manufactured on or after January 1, 2016, but before April 23, 2029, shall be no less than that required for their kVA and BIL rating in the following table. Medium-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| kVA | Single-phase | kVA | Three-phase | ||||
|---|---|---|---|---|---|---|---|
| BIL 1 | BIL | ||||||
| 20-45 kV | 46-95 kV | ≥96 kV | 20-45 kV | 46-95 kV | ≥96 kV | ||
| Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
||
| 15 | 98.10 | 97.86 | 15 | 97.50 | 97.18 | ||
| 25 | 98.33 | 98.12 | 30 | 97.90 | 97.63 | ||
| 37.5 | 98.49 | 98.30 | 45 | 98.10 | 97.86 | ||
| 50 | 98.60 | 98.42 | 75 | 98.33 | 98.13 | ||
| 75 | 98.73 | 98.57 | 98.53 | 112.5 | 98.52 | 98.36 | |
| 100 | 98.82 | 98.67 | 98.63 | 150 | 98.65 | 98.51 | |
| 167 | 98.96 | 98.83 | 98.80 | 225 | 98.82 | 98.69 | 98.57 |
| 250 | 99.07 | 98.95 | 98.91 | 300 | 98.93 | 98.81 | 98.69 |
| 333 | 99.14 | 99.03 | 98.99 | 500 | 99.09 | 98.99 | 98.89 |
| 500 | 99.22 | 99.12 | 99.09 | 750 | 99.21 | 99.12 | 99.02 |
| 667 | 99.27 | 99.18 | 99.15 | 1000 | 99.28 | 99.20 | 99.11 |
| 833 | 99.31 | 99.23 | 99.20 | 1500 | 99.37 | 99.30 | 99.21 |
| 2000 | 99.43 | 99.36 | 99.28 | ||||
| 2500 | 99.47 | 99.41 | 99.33 | ||||
| 1 BIL means basic impulse insulation level. | |||||||
| Note: All efficiency values are at 50 percent of nameplate rated load, determined according to the DOE Test Method for Measuring the Energy Consumption of Distribution Transformers under appendix A to this subpart K. | |||||||
(3) The efficiency of a medium-voltage dry-type distribution transformer manufactured on or after April 23, 2029, shall be no less than that required for their kVA and BIL rating in the following table. Medium-voltage dry-type distribution transformers with kVA ratings not appearing in the table shall have their minimum efficiency level determined by linear interpolation of the kVA and efficiency values immediately above and below that kVA rating.
| kVA | Single-phase | kVA | Three-phase | ||||
|---|---|---|---|---|---|---|---|
| BIL 1 | BIL | ||||||
| 20-45 kV | 46-95 kV | ≥96 kV | 20-45 kV | 46-95 kV | ≥96 kV | ||
| Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
Efficiency
(%) |
||
| 15 | 98.29 | 98.07 | 15 | 97.75 | 97.46 | ||
| 25 | 98.50 | 98.31 | 30 | 98.11 | 97.87 | ||
| 37.5 | 98.64 | 98.47 | 45 | 98.29 | 98.07 | ||
| 50 | 98.74 | 98.58 | 75 | 98.50 | 98.32 | ||
| 75 | 98.86 | 98.71 | 98.68 | 112.5 | 98.67 | 98.52 | |
| 100 | 98.94 | 98.80 | 98.77 | 150 | 98.79 | 98.66 | |
| 167 | 99.06 | 98.95 | 98.92 | 225 | 98.94 | 98.82 | 98.71 |
| 250 | 99.16 | 99.06 | 99.02 | 300 | 99.04 | 98.93 | 98.82 |
| 333 | 99.23 | 99.13 | 99.09 | 500 | 99.18 | 99.09 | 99.00 |
| 500 | 99.30 | 99.21 | 99.18 | 750 | 99.29 | 99.21 | 99.12 |
| 667 | 99.34 | 99.26 | 99.24 | 1000 | 99.35 | 99.28 | 99.20 |
| 833 | 99.38 | 99.31 | 99.28 | 1500 | 99.43 | 99.37 | 99.29 |
| 2000 | 99.49 | 99.42 | 99.35 | ||||
| 2500 | 99.52 | 99.47 | 99.40 | ||||
| 3750 | 99.50 | 99.44 | 99.40 | ||||
| 5000 | 99.48 | 99.43 | 99.39 | ||||
| 1 BIL means basic impulse insulation level/ | |||||||
| Note: All efficiency values are at 50 percent of nameplate rated load, determined according to the DOE Test Method for Measuring the Energy Consumption of Distribution Transformers under appendix A to this subpart K. | |||||||
(d) Mining Distribution Transformers. [Reserved]
(e) Severability. The provisions of paragraphs (a) through (d) of this section are separate and severable from one another. Should a court of competent jurisdiction hold any provision(s) of this section to be stayed or invalid, such action shall not affect any other provision of this section.
[78 FR 23433, Apr. 18, 2013, as amended at 86 FR 51252, Sept. 14, 2021; 89 FR 30040, Apr. 22, 2024]
71 FR 24997, Apr. 27, 2006, unless otherwise noted.
1.0 Definitions.
The definitions contained in §§ 431.2 and 431.192 are applicable to this appendix A.
2.0 Per-Unit Load, Reference Temperature, and Accuracy Requirements.
2.1 Per-Unit Load
In conducting the test procedure in this appendix for the purpose of:
(a) Certification to an energy conservation standard, the applicable per-unit load in Table 2.1 must be used; or
(b) Making voluntary representations as provided in section 7.0 at an additional per-unit load, select the per-unit load of interest.
| Distribution transformer category | Per-unit load (percent) |
|---|---|
| Liquid-immersed | 50 |
| Medium-voltage dry-type | 50 |
| Low-voltage dry-type | 35 |
2.2 Reference Temperature
In conducting the test procedure in this appendix for the purpose of:
(a) Certification to an energy conservation standard, the applicable reference temperature in Table 2.2 must be used; or
(b) Making voluntary representations as provided in section 7.0 at an additional reference temperature, select the reference temperature of interest.
| Distribution transformer category | Reference temperature |
|---|---|
| Liquid-immersed | 20 °C for no-load loss. 55 °C for load loss. |
| Medium-voltage dry-type | 20 °C for no-load loss. 75 °C for load loss. |
| Low-voltage dry-type | 20 °C for no-load loss. 75 °C for load loss. |
2.3 Accuracy Requirements
(a) Equipment and methods for loss measurement must be sufficiently accurate that measurement error will be limited to the values shown in Table 2.3.
| Measured quantity |
Test system accuracy |
|---|---|
| Power Losses | ±3.0%. |
| Voltage | ±0.5%. |
| Current | ±0.5%. |
| Resistance | ±0.5%. |
| Temperature | ±1.5 °C for liquid-immersed distribution transformers, and ±2.0 °C for low-voltage dry-type and medium-voltage dry-type distribution transformers. |
(b) Only instrument transformers meeting the 0.3 metering accuracy class, or better, may be used under this test method.
3.0 Resistance Measurements
3.1 General Considerations
(a) Measure or establish the winding temperature at the time of the winding resistance measurement.
(b) Measure the direct current resistance (Rdc) of transformer windings by one of the methods outlined in section 3.3. The methods of section 3.5 must be used to correct load losses to the applicable reference temperature from the temperature at which they are measured. Observe precautions while taking measurements, such as those in section 3.4, in order to maintain measurement uncertainty limits specified in Table 2.1.
(c) Measure the direct current resistance (Rdc) of transformer windings by one of the methods outlined in section 3.3. The methods of section 3.5 must be used to correct load losses to the applicable reference temperature from the temperature at which they are measured. Observe precautions while taking measurements, such as those in section 3.4, in order to maintain measurement uncertainty limits specified in Table 2.3 of this appendix.
3.2 Temperature Determination of Windings and Pre-conditions for Resistance Measurement.
Make temperature measurements in protected areas where the air temperature is stable and there are no drafts. Determine the winding temperature (Tdc) for liquid-immersed and dry-type distribution transformers by the methods described in sections 3.2.1 and 3.2.2, respectively.
3.2.1 Liquid-Immersed Distribution Transformers.
3.2.1.1 Methods
Record the winding temperature (Tdc) of liquid-immersed transformers as the average of either of the following:
(a) The measurements from two temperature sensing devices (for example, thermocouples) applied to the outside of the transformer tank and thermally insulated from the surrounding environment, with one located at the level of the insulating liquid and the other located near the tank bottom or at the lower radiator header if applicable; or
(b) The measurements from two temperature sensing devices immersed in the insulating liquid, with one located directly above the winding and other located directly below the winding.
3.2.1.2 Conditions
Make this determination under either of the following conditions:
(a) The windings have been under insulating liquid with no excitation and no current in the windings for four hours before the dc resistance is measured; or
(b) The temperature of the insulating liquid has stabilized, and the difference between the top and bottom temperature does not exceed 5 °C. The temperature of the insulating liquid is considered stable if the top liquid temperature does not vary more than 2 °C in a 1-h period.
3.2.2 Dry-Type Distribution Transformers.
Record the winding temperature (Tdc) of dry-type transformers as one of the following:
(a) For ventilated dry-type units, use the average of readings of four or more thermometers, thermocouples, or other suitable temperature sensors inserted within the coils. Place the sensing points of the measuring devices as close as possible to the winding conductors; or
(b) For sealed units, such as epoxy-coated or epoxy-encapsulated units, use the average of four or more temperature sensors located on the enclosure and/or cover, as close to different parts of the winding assemblies as possible; or
(c) For ventilated units or sealed units, use the ambient temperature of the test area, only if the following conditions are met:
(1) All internal temperatures measured by the internal temperature sensors must not differ from the test area ambient temperature by more than 2 °C. Enclosure surface temperatures for sealed units must not differ from the test area ambient temperature by more than 2 °C.
(2) Test area ambient temperature must not have changed by more than 3 °C for 3 hours before the test.
(3) Neither voltage nor current has been applied to the unit under test for 24 hours. In addition, increase this initial 24-hour period by any added amount of time necessary for the temperature of the transformer windings to stabilize at the level of the ambient temperature. However, this additional amount of time need not exceed 24 hours (i.e., after 48 hours, the transformer windings can be assumed to have stabilized at the level of the ambient temperature. Any stabilization time beyond 48 hours is optional).
3.3 Resistance Measurement Methods.
Make resistance measurements using either the resistance bridge method (section 3.3.1), the voltmeter-ammeter method (section 3.3.2) or resistance meters (section 3.3.3). In each instance when this appendix is used to test more than one unit of a basic model to determine the efficiency of that basic model, the resistance of the units being tested may be determined from making resistance measurements on only one of the units.
3.3.1 Resistance Bridge Methods.
If the resistance bridge method is selected, use either the Wheatstone or Kelvin bridge circuit (or the equivalent of either).
3.3.1.1 Wheatstone Bridge
(a) This bridge is best suited for measuring resistances larger than ten ohms. A schematic diagram of a Wheatstone bridge with a representative transformer under test is shown in Figure 3.1.
Where:
Rdc is the resistance of the transformer winding being measured,
Rs is a standard resistor having the resistance Rs,
Ra, Rb are two precision resistors with resistance values Ra and Rb , respectively; at least one resistor must have a provision for resistance adjustment,
Rt is a resistor for reducing the time constant of the circuit,
D is a null detector, which may be either a micro ammeter or microvoltmeter or equivalent instrument for observing that no signal is present when the bridge is balanced, and
Vdc is a source of dc voltage for supplying the power to the Wheatstone Bridge.
(b) In the measurement process, turn on the source (Vdc), and adjust the resistance ratio (Ra/Rb) to produce zero signal at the detector (D). Determine the winding resistance by using equation 3-1 as follows:
3.3.1.2 Kelvin Bridge
(a) This bridge separates the resistance of the connecting conductors to the transformer winding being measured from the resistance of the winding, and therefore is best suited for measuring resistances of ten ohms and smaller. A schematic diagram of a Kelvin bridge with a representative transformer under test is shown in Figure 3.2.
(b) The Kelvin Bridge has seven of the same type of components as in the Wheatstone Bridge. It has two more resistors than the Wheatstone bridge, Ra1 and Rb1. At least one of these resistors must have adjustable resistance. In the measurement process, the source is turned on, two resistance ratios (Ra/Rb) and (Ra1/Rb1) are adjusted to be equal, and then the two ratios are adjusted together to balance the bridge producing zero signal at the detector. Determine the winding resistance by using equation 3-2 as follows:
as with the Wheatstone bridge, with an additional condition that:
(c) The Kelvin bridge provides two sets of leads, current-carrying and voltage-sensing, to the transformer terminals and the standard resistor, thus eliminating voltage drops from the measurement in the current-carrying leads as represented by Rd.
3.3.2 Voltmeter-Ammeter Method.
(a) Employ the voltmeter-ammeter method only if the test current is limited to 15 percent of the winding current. Connect the transformer winding under test to the circuit shown in Figure 3.3 of this appendix.
Where:
A is an ammeter or a voltmeter-shunt combination for measuring the current (Imdc) in the transformer winding,
V is a voltmeter with sensitivity in the millivolt range for measuring the voltage (Vmdc) applied to the transformer winding,
Rdc is the resistance of the transformer winding being measured,
Rt is a resistor for reducing the time constant of the circuit, and
Vdc is a source of dc voltage for supplying power to the measuring circuit.
(b) To perform the measurement, turn on the source to produce current no larger than 15 percent of the rated current for the winding. Wait until the current and voltage readings have stabilized and then take a minimum of four readings of voltage and current. Voltage and current readings must be taken simultaneously for each of the readings. Calculate the average voltage and average current using the readings. Determine the winding resistance Rdc by using equation 3-4 as follows:
Where:
Vmdc is the average voltage measured by the voltmeter V; and
Imdc is the average current measured by the ammeter (A).
(c) As shown in Figure 3.3, separate current and voltage leads must be brought to the transformer terminals. (This eliminates the errors due to lead and contact resistance.)
3.3.3 Resistance Meters.
Resistance meters may be based on voltmeter-ammeter, or resistance bridge, or some other operating principle. Any meter used to measure a transformer's winding resistance must have specifications for resistance range, current range, and ability to measure highly inductive resistors that cover the characteristics of the transformer being tested. Also, the meter's specifications for accuracy must meet the applicable criteria of Table 2.3 in section 2.3 of this appendix.
3.4 Precautions in Measuring Winding Resistance.
3.4.1 Required actions.
The following requirements must be observed when making resistance measurements:
(a) Use separate current and voltage leads when measuring small (<10 ohms) resistance.
(b) Use null detectors in bridge circuits, and measuring instruments in voltmeter-ammeter circuits, that have sensitivity and resolution sufficient to enable observation of at least 0.1 percent change in the measured resistance.
(c) Maintain the dc test current at or below 15 percent of the rated winding current.
(d) Inclusion of a stabilizing resistor Rt (see section 3.4.2) will require higher source voltage.
(e) Disconnect the null detector (if a bridge circuit is used) and voltmeter from the circuit before the current is switched off, and switch off current by a suitable insulated switch.
(f) Keep the polarity of the core magnetization constant during all resistance measurements.
(g) For single-phase windings, measure the resistance from terminal to terminal. The total winding resistance is the terminal-to-terminal measurement. For series-parallel windings, the total winding resistance is the sum of the series terminal-to-terminal section measurements.
(h) For wye windings, measure the resistance from terminal to terminal or from terminal to neutral. For the total winding resistance, the resistance of the lead from the neutral connection to the neutral bushing may be excluded. For terminal-to-terminal measurements, the total resistance reported is the sum of the three measurements divided by two.
(i) For delta windings, measure resistance from terminal to terminal with the delta closed or from terminal to terminal with the delta open to obtain the individual phase readings. The total winding resistance is the sum of the three-phase readings if the delta is open. If the delta is closed, the total winding resistance is the sum of the three phase-to-phase readings times 1.5.
3.4.2 Guideline for Time Constant.
(a) The following guideline is suggested for the tester as a means to facilitate the measurement of resistance in accordance with the accuracy requirements of section 2.3:
(b) The accurate reading of resistance Rdc may be facilitated by shortening the time constant. This is done by introducing a resistor Rt in series with the winding under test in both the bridge and voltmeter-ammeter circuits as shown in Figures 3.1 to 3.3. The relationship for the time constant is:
Where:
Tc is the time constant in seconds,
Ltc is the total magnetizing and leakage inductance of the winding under test, in henries, and
Rtc is the total resistance in ohms, consisting of Rt in series with the winding resistance Rdc and the resistance Rs of the standard resistor in the bridge circuit.
(c) Because Rtc is in the denominator of the expression for the time constant, increasing the resistance Rtc will decrease the time constant. If the time constant in a given test circuit is too long for the resistance readings to be stable, then a higher resistance can be substituted for the existing Rtc, and successive replacements can be made until adequate stability is reached.
3.5 Conversion of Resistance Measurements.
(a) Resistance measurements must be corrected from the temperature at which the winding resistance measurements were made, to the reference temperature.
(b) Correct the measured resistance to the resistance at the reference temperature using equation 3-6 as follows:
Where:
Rts is the resistance at the reference temperature, Ts,
Rdc is the measured resistance at temperature, Tdc,
Ts is the reference temperature in °C,
Tdc is the temperature at which resistance was measured in °C, and
Tk is 234.5 °C for copper or 225 °C for aluminum.
4.0 Loss Measurement
4.1 General Considerations.
The efficiency of a transformer is computed from the total transformer losses, which are determined from the measured value of the no-load loss and load loss power components. Each of these two power loss components is measured separately using test sets that are identical, except that shorting straps are added for the load-loss test. The measured quantities need correction for instrumentation losses and may need corrections for known phase angle errors in measuring equipment and for the waveform distortion in the test voltage. Any power loss not measured at the applicable reference temperature must be adjusted to that reference temperature. The measured load loss must also be adjusted to a specified output loading level if not measured at the specified output loading level. Test all distribution transformers using a sinusoidal waveform (k = 1). Measure losses with the transformer energized by a 60 Hz supply.
4.2 Measurement of Power Losses.
4.2.1 No-Load Loss.
Measure the no-load loss and apply corrections as described in section 4.4, using the appropriate test set as described in section 4.3.
4.2.2 Load Loss.
Measure the load loss and apply corrections as described in section 4.5, using the appropriate test set as described in section 4.3.
4.3 Test Sets.
(a) The same test set may be used for both the no-load loss and load loss measurements provided the range of the test set encompasses the test requirements of both tests. Calibrate the test set to national standards to meet the tolerances in Table 2.3 in section 2.3 of this appendix. In addition, the wattmeter, current measuring system and voltage measuring system must be calibrated separately if the overall test set calibration is outside the tolerance as specified in section 2.3 or the individual phase angle error exceeds the values specified in section 4.5.3.
(b) A test set based on the wattmeter-voltmeter-ammeter principle may be used to measure the power loss and the applied voltage and current of a transformer where the transformer's test current and voltage are within the measurement capability of the measuring instruments. Current and voltage transformers, known collectively as instrument transformers, or other scaling devices such as resistive or capacitive dividers for voltage, may be used in the above circumstance, and must be used together with instruments to measure current, voltage, or power where the current or voltage of the transformer under test exceeds the measurement capability of such instruments. Thus, a test set may include a combination of measuring instruments and instrument transformers (or other scaling devices), so long as the current or voltage of the transformer under test does not exceed the measurement capability of any of the instruments.
(c) Both load loss and no-load loss measurements must be made from terminal to terminal.
4.3.1 Single-Phase Test Sets.
Use these for testing single-phase distribution transformers.
4.3.1.1 Without Instrument Transformers.
(a) A single-phase test set without an instrument transformer is shown in Figure 4.1.
Where:
W is a wattmeter used to measure Pnm and Plm, the no-load and load loss power, respectively,
Vrms is a true root-mean-square (rms) voltmeter used to measure Vr(nm) and Vlm, the rms test voltages in no-load and load loss measurements, respectively,
Vav is an average sensing voltmeter, calibrated to indicate rms voltage for sinusoidal waveforms and used to measure Va(nm), the average voltage in no-load loss measurements,
A is an rms ammeter used to measure test current, especially Ilm, the load loss current, and
(SC) is a conductor for providing a short-circuit across the output windings for the load loss measurements.
(b) Either the primary or the secondary winding can be connected to the test set. However, more compatible voltage and current levels for the measuring instruments are available if for no-load loss measurements the secondary (low voltage) winding is connected to the test set, and for load loss measurements the primary winding is connected to the test set. Use the average-sensing voltmeter, Vav, only in no-load loss measurements.
4.3.1.2 With Instrument Transformers.
A single-phase test set with instrument transformers is shown in Figure 4.2. This circuit has the same four measuring instruments as that in Figure 4.1. The current and voltage transformers, designated as (CT) and (VT), respectively, are added.
4.3.2 Three-Phase Test Sets.
Use these for testing three-phase distribution transformers. Use in a four-wire, three-wattmeter test circuit.
4.3.2.1 Without Instrument Transformers.
(a) A three-phase test set without instrument transformers is shown in Figure 4.3. This test set is essentially the same circuit shown in Figure 4.1 repeated three times, and the instruments are individual devices as shown. As an alternative, the entire instrumentation system of a three-phase test set without transformers may consist of a multi-function analyzer.
(b) Either group of windings, the primary or the secondary, can be connected in wye or delta configuration. If both groups of windings are connected in the wye configuration for the no-load test, the neutral of the winding connected to the test set must be connected to the neutral of the source to provide a return path for the neutral current.
(c) In the no-load loss measurement, the voltage on the winding must be measured. Therefore a provision must be made to switch the voltmeters for line-to-neutral measurements for wye-connected windings and for line-to-line measurements for delta-connected windings.
4.3.2.2 With Instrument Transformers.
A three-phase test set with instrument transformers is shown in Figure 4.4. This test set is essentially the same circuit shown in Figure 4.2 repeated three times. Provision must be made to switch the voltmeters for line-to-neutral and line-to-line measurements as in section 4.3.2.1. The voltage sensors (“coils”) of the wattmeters must always be connected in the line-to-neutral configuration.
4.3.2.3 Test Set Neutrals.
If the power source in the test circuit is wye-connected, ground the neutral. If the power source in the test circuit is delta-connected, use a grounding transformer to obtain neutral and ground for the test.
4.4 No-Load Losses: Measurement and Calculations.
4.4.1 General Considerations.
Measurement corrections are permitted but not required for instrumentation losses and for losses from auxiliary devices. Measurement corrections are required:
(a) When the waveform of the applied voltage is non-sinusoidal; and
(b) When the core temperature or liquid temperature is outside the 20 °C ±10 °C range.
4.4.2 No-Load Loss Test.
(a) The purpose of the no-load loss test is to measure no-load losses at a specified excitation voltage and a specified frequency. The no-load loss determination must be based on a sine-wave voltage corrected to the reference temperature. Connect either of the transformer windings, primary or secondary, to the appropriate test set of Figures 4.1 to 4.4, giving consideration to section 4.4.2(a)(2). Leave the unconnected winding(s) open circuited. Apply the rated voltage at rated frequency, as measured by the average-sensing voltmeter, to the transformer. Take the readings of the wattmeter(s) and the average-sensing and true rms voltmeters. Observe the following precautions:
(1) Voltmeter connections. When correcting to a sine-wave basis using the average-voltmeter method, the voltmeter connections must be such that the waveform applied to the voltmeters is the same as the waveform across the energized windings.
(2) Energized windings. Energize either the high voltage or the low voltage winding of the transformer under test.
(3) Voltage and frequency. The no-load loss test must be conducted with rated voltage impressed across the transformer terminals using a voltage source at a frequency equal to the rated frequency of the transformer under test.
(b) Adjust the voltage to the specified value as indicated by the average-sensing voltmeter. Record the values of rms voltage, rms current, electrical power, and average voltage as close to simultaneously as possible. For a three-phase transformer, take all of the readings on one phase before proceeding to the next, and record the average of the three rms voltmeter readings as the rms voltage value.
When the tester uses a power supply that is not synchronized with an electric utility grid, such as a dc/ac motor-generator set, check the frequency and maintain it within ±0.5 percent of the rated frequency of the transformer under test. A power source that is directly connected to, or synchronized with, an electric utility grid need not be monitored for frequency.
4.4.3 Corrections.
4.4.3.1 Correction for Instrumentation Losses.
Measured losses attributable to the voltmeters and wattmeter voltage circuit, and to voltage transformers if they are used, may be deducted from the total no-load losses measured during testing.
4.4.3.2 Correction for Non-Sinusoidal Applied Voltage.
(a) The measured value of no-load loss must be corrected to a sinusoidal voltage, except when waveform distortion in the test voltage causes the magnitude of the correction to be less than 1 percent. In such a case, no correction is required.
(b) To make a correction where the distortion requires a correction of 5 percent or less, use equation 4-1. If the distortion requires a correction to be greater than 5 percent, improve the test voltage and re-test. Repeat until the distortion requires a correction of 5 percent or less.
(c) Determine the no-load losses of the transformer corrected for sine-wave basis from the measured value by using equation 4-1 as follows:
Where:
Pncl is the no-load loss corrected to a sine-wave basis at the temperature (Tnm) at which no-load loss is measured,
Pnm is the measured no-load loss at temperature Tnm,
P1 is the per unit hysteresis loss,
P2 is the per unit eddy-current loss,
P1 + P2 = 1,
Vr(nm) is the test voltage measured by rms voltmeter, and
Va(nm) is the test voltage measured by average-voltage voltmeter.
(d) The two loss components (P1 and P2) are assumed equal in value, each assigned a value of 0.5 per unit, unless the actual measurement-based values of hysteresis and eddy-current losses are available (in per unit form), in which case the actual measurements apply.
4.4.3.3 Correction of No-Load Loss to Reference Temperature.
After correcting the measured no-load loss for waveform distortion, correct the loss to the reference temperature. For both certification to energy conservation standards and voluntary representations, if the correction to reference temperature is applied, then the core temperature of the transformer during no-load loss measurement (Tnm) must be determined within ±10 °C of the true average core temperature. For certification to energy conservation standards only, if the no-load loss measurements were made between 10 °C and 30 °C, this correction is not required. Correct the no-load loss to the reference temperature by using equation 4-2 as follows:
Where:
Pnc is the no-load losses corrected for waveform distortion and then to the reference temperature;
Pnc1 is the no-load losses, corrected for waveform distortion, at temperature Tnm;
Tnm is the core temperature during the measurement of no-load losses; and
Tnr is the reference temperature.
4.5 Load Losses: Measurement and Calculations.
4.5.1 General Considerations.
(a) The load losses of a transformer are those losses incident to a specified load carried by the transformer. Load losses consist of ohmic loss in the windings due to the load current and stray losses due to the eddy currents induced by the leakage flux in the windings, core clamps, magnetic shields, tank walls, and other conducting parts. The ohmic loss of a transformer varies directly with temperature, whereas the stray losses vary inversely with temperature.
(b) For a transformer with a tap changer, conduct the test at the rated current and rated-voltage tap position. For a transformer that has a configuration of windings which allows for more than one nominal rated voltage, determine its load losses either in the winding configuration in which the highest losses occur or in each winding configuration in which the transformer can operate.
4.5.2 Tests for Measuring Load Losses.
(a) Connect the transformer with either the high-voltage or low-voltage windings to the appropriate test set. Then short-circuit the winding that was not connected to the test set. Apply a voltage at the rated frequency (of the transformer under test) to the connected windings to produce the rated current in the transformer. Take the readings of the wattmeter(s), the ammeters(s), and rms voltmeter(s).
(b) Regardless of the test set selected, the following preparatory requirements must be satisfied for accurate test results:
(1) Determine the temperature of the windings using the applicable method in section 3.2.1 or section 3.2.2.
(2) The conductors used to short-circuit the windings must have a cross-sectional area equal to, or greater than, the corresponding transformer leads, or, if the tester uses a different method to short-circuit the windings, the losses in the short-circuiting conductor assembly must be less than 10 percent of the transformer's load losses.
(3) When the tester uses a power supply that is not synchronized with an electric utility grid, such as a dc/ac motor-generator set, follow the provisions of the “Note” in section 4.4.2.
4.5.3 Corrections.
4.5.3.1 Correction for Losses from Instrumentation and Auxiliary Devices.
4.5.3.1.1 Instrumentation Losses.
Measured losses attributable to the voltmeters, wattmeter voltage circuit and short-circuiting conductor (SC), and to the voltage transformers if they are used, may be deducted from the total load losses measured during testing.
4.5.3.1.2 Losses from Auxiliary Devices.
Measured losses attributable to auxiliary devices (e.g., circuit breakers, fuses, switches) installed in the transformer, if any, that are not part of the winding and core assembly, may be excluded from load losses measured during testing. To exclude these losses, either (1) measure transformer losses without the auxiliary devices by removing or by-passing them, or (2) measure transformer losses with the auxiliary devices connected, determine the losses associated with the auxiliary devices, and deduct these losses from the load losses measured during testing.
4.5.3.2 Correction for Phase Angle Errors.
(a) Corrections for phase angle errors are not required if the instrumentation is calibrated over the entire range of power factors and phase angle errors. Otherwise, determine whether to correct for phase angle errors from the magnitude of the normalized per unit correction, βn, obtained by using equation 4-3 as follows:
(b) The correction must be applied if βn is outside the limits of ±0.01. If βn is within the limits of ±0.01, the correction is permitted but not required.
(c) If the correction for phase angle errors is to be applied, first examine the total system phase angle (βw−βv + βc). Where the total system phase angle is equal to or less than ±12 milliradians (±41 minutes), use either equation 4-4 or 4-5 to correct the measured load loss power for phase angle errors, and where the total system phase angle exceeds ±12 milliradians (±41 minutes) use equation 4-5, as follows:
(d) The symbols in this section (4.5.3.2) have the following meanings:
Plc1 is the corrected wattmeter reading for phase angle errors,
Plm is the actual wattmeter reading,
Vlm is the measured voltage at the transformer winding,
Ilm is the measured rms current in the transformer winding,
is the measured phase angle between Vlm and Ilm,
βw is the phase angle error (in radians) of the wattmeter; the error is positive if the phase angle between the voltage and current phasors as sensed by the wattmeter is smaller than the true phase angle, thus effectively increasing the measured power,
βv is the phase angle error (in radians) of the voltage transformer; the error is positive if the secondary voltage leads the primary voltage, and
βc is the phase angle error (in radians) of the current transformer; the error is positive if the secondary current leads the primary current.
(e) The instrumentation phase angle errors used in the correction equations must be specific for the test conditions involved.
4.5.3.3 Temperature Correction of Load Loss.
(a) When the measurement of load loss is made at a temperature Tlm that is different from the reference temperature, use the procedure summarized in the equations 4-6 to 4-10 to correct the measured load loss to the reference temperature. The symbols used in these equations are defined at the end of this section.
(b) Calculate the ohmic loss (Pe) by using equation 4-6 as follows:
(c) Obtain the stray loss by subtracting the calculated ohmic loss from the measured load loss, by using equation 4-7 as follows:
(d) Correct the ohmic and stray losses to the reference temperature for the load loss by using equations 4-8 and 4-9, respectively, as follows:
(e) Add the ohmic and stray losses, corrected to the reference temperature, to give the load loss, Plc2, at the reference temperature, by using equation 4-10 as follows:
(f) The symbols in this section (4.5.3.3) have the following meanings:
Ilm(p) is the primary current in amperes,
Ilm(s) is the secondary current in amperes,
Pe is the ohmic loss in the transformer in watts at the temperature Tlm,
Pe(p) is the ohmic loss in watts in the primary winding at the temperature Tlm,
Pe(s) is the ohmic loss in watts in the secondary winding at the temperature Tlm,
Per is the ohmic loss in watts corrected to the reference temperature,
Plc1 is the measured load loss in watts, corrected for phase angle error, at the temperature Tlm,
Plc2 is the load loss at the reference temperature,
Ps is the stray loss in watts at the temperature Tlm,
Psr is the stray loss in watts corrected to the reference temperature,
Rdc(p) is the measured dc primary winding resistance in ohms,
Rdc(s) is the measured dc secondary winding resistance in ohms,
Tk is the critical temperature in degrees Celsius for the material of the transformer windings. Where copper is used in both primary and secondary windings, Tk is 234.5 °C; where aluminum is used in both primary and secondary windings, Tk is 225 °C; where both copper and aluminum are used in the same transformer, the value of 229 °C is used for Tk,
Tk(p) is the critical temperature in degrees Celsius for the material of the primary winding: 234.5 °C if copper and 225 °C if aluminum,
Tk(s) is the critical temperature in degrees Celsius for the material of the secondary winding: 234.5 °C if copper and 225 °C if aluminum,
Tlm is the temperature in degrees Celsius at which the load loss is measured,
Tlr is the reference temperature for the load loss in degrees Celsius,
Tdc is the temperature in degrees Celsius at which the resistance values are measured, and
N1/N2 is the ratio of the number of turns in the primary winding (N1) to the number of turns in the secondary winding (N2); for a primary winding with taps, N1 is the number of turns used when the voltage applied to the primary winding is the rated primary voltage.
5.0 Determining the Efficiency Value of the Transformer
This section presents the equations to use in determining the efficiency value of the transformer at the required reference conditions and at the specified loading level. The details of measurements are described in sections 3.0 and 4.0. For a transformer that has a configuration of windings which allows for more than one nominal rated voltage, determine its efficiency either at the voltage at which the highest losses occur or at each voltage at which the transformer is rated to operate.
5.1 Output Loading Level Adjustment.
If the per-unit load selected in section 2.1 is different from the per-unit load at which the load loss power measurements were made, then adjust the corrected load loss power, Plc2, by using equation 5-1 as follows:
Where:
Plc is the adjusted load loss power to the per-unit load;
Plc2 is as calculated in section 4.5.3.3;
Por is the rated transformer apparent power (name plate);
Pos is the adjusted rated transformer apparent power, where Pos = PorL; and
L is the per-unit load, e.g., if the per-unit load is 50 percent then “L” is 0.5.
5.2 Total Loss Power Calculation.
Calculate the corrected total loss power by using equation 5-2 as follows:
Where:
Pts is the corrected total loss power adjusted for the transformer output loading specified by the standard,
Pnc is as calculated in section 4.4.3.3, and
Plc is as calculated in section 5.1.
5.3 Energy Efficiency Calculation.
Calculate efficiency (η) in percent at specified energy efficiency load level, Pos, by using equation 5-3 as follows:
Where:
Pos is as described and calculated in section 5.1, and
Pts is as described and calculated in section 5.2.
5.4 Significant Figures in Power Loss and Efficiency Data.
In measured and calculated data, retain enough significant figures to provide at least 1 percent resolution in power loss data and 0.01 percent resolution in efficiency data.
6.0 Test Equipment Calibration and Certification.
Maintain and calibrate test equipment and measuring instruments, maintain calibration records, and perform other test and measurement quality assurance procedures according to the following sections. The calibration of the test set must confirm the accuracy of the test set to that specified in section 2.3, Table 2.3 of this appendix.
6.1 Test Equipment.
The party performing the tests must control, calibrate, and maintain measuring and test equipment, whether or not it owns the equipment, has the equipment on loan, or the equipment is provided by another party. Equipment must be used in a manner which assures that measurement uncertainty is known and is consistent with the required measurement capability.
6.2 Calibration and Certification.
The party performing the tests must:
(a) Identify the measurements to be made, the accuracy required (section 2.3) and select the appropriate measurement and test equipment;
(b) At prescribed intervals, or prior to use, identify, check and calibrate, if needed, all measuring and test equipment systems or devices that affect test accuracy, against certified equipment having a known valid relationship to nationally recognized standards; where no such standards exist, the basis used for calibration must be documented;
(c) Establish, document and maintain calibration procedures, including details of equipment type, identification number, location, frequency of checks, check method, acceptance criteria and action to be taken when results are unsatisfactory;
(d) Ensure that the measuring and test equipment is capable of the accuracy and precision necessary, taking into account the voltage, current and power factor of the transformer under test;
(e) Identify measuring and test equipment with a suitable indicator or approved identification record to show the calibration status;
(f) Maintain calibration records for measuring and test equipment;
(g) Assess and document the validity of previous test results when measuring and test equipment is found to be out of calibration;
(h) Ensure that the environmental conditions are suitable for the calibrations, measurements and tests being carried out;
(i) Ensure that the handling, preservation and storage of measuring and test equipment is such that the accuracy and fitness for use is maintained; and
(j) Safeguard measuring and test facilities, including both test hardware and test software, from adjustments which would invalidate the calibration setting.
7.0 Test Procedure for Voluntary Representations
Follow sections 1.0 through 6.0 of this appendix using the per-unit load and/or reference temperature of interest for voluntary representations of efficiency, and corresponding values of load loss and no-load loss at additional per-unit load and/or reference temperature. Representations made at a per-unit load and/or reference temperature other than those required to comply with the energy conservation standards at § 431.196 must be in addition to, and not in place of, a representation at the required DOE settings for per-unit load and reference temperature. As a best practice, the additional settings of per-unit load and reference temperature should be provided with the voluntary representations.
[71 FR 24999, Apr. 27, 2006; 71 FR 60662, Oct. 16, 2006; 86 FR 51252, Sept. 14, 2021]
70 FR 60417, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for illuminated exit signs, pursuant to Part B of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6309.
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Face means an illuminated side of an illuminated exit sign.
Illuminated exit sign means a sign that—
(1) Is designed to be permanently fixed in place to identify an exit; and
(2) Consists of an electrically powered integral light source that—
(i) Illuminates the legend “EXIT” and any directional indicators; and
(ii) Provides contrast between the legend, any directional indicators, and the background.
Input power demand means the amount of power required to continuously illuminate an exit sign model, measured in watts (W). For exit sign models with rechargeable batteries, input power demand shall be measured with batteries at full charge.
[70 FR 60417, Oct. 18, 2005, as amended at 71 FR 71372, Dec. 8, 2006; 76 FR 12504, Mar. 7, 2011]
(a) General. The Department incorporates by reference the following test procedures into subpart L of part 431. The Director of the Federal Register has approved the material listed in paragraph (b) of this section for incorporation by reference in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. Any subsequent amendment to this material by the standard-setting organization will not affect the DOE test procedures unless and until DOE amends its test procedures. The Department incorporates the material as it exists on the date of the approval by the Federal Register and a notice of any change in the material will be published in the Federal Register.
(b) Test procedure incorporated by reference. Environmental Protection Agency “ENERGY STAR Program Requirements for Exit Signs,” Version 2.0 issued January 1, 1999.
(c) Availability of reference —
(1) Inspection of test procedure. The test procedure incorporated by reference are available for inspection at:
(i) National Archives and Records Administration (NARA). For information on the availability of this material at NARA, call (202) 741-6030, or go to: http://www.archives.gov/federal_register/code_of_federal_regulations/ibr_locations.html.
(ii) U.S. Department of Energy, Forrestal Building, Room 1J-018 (Resource Room of the Building Technologies Program), 1000 Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9127, between 9 a.m. and 4 p.m., Monday through Friday, except Federal holidays.
(2) Obtaining copies of the standard. Copies of the Environmental Protection Agency “ENERGY STAR Program Requirements for Exit Signs,” Version 2.0, may be obtained from the Environmental Protection Agency, Ariel Rios Building, 1200 Pennsylvania Avenue, NW., Washington, DC 20460, (202) 272-0167 or athttp://www.epa.gov.
[71 FR 71373, Dec. 8, 2006]
(a) Scope. This section provides the test procedure for measuring, pursuant to EPCA, the input power demand of illuminated exit signs. For purposes of this part 431 and EPCA, the test procedure for measuring the input power demand of illuminated exit signs shall be the test procedure specified in § 431.203(b).
(b) Testing and Calculations. Determine the energy efficiency of each covered product by conducting the test procedure, set forth in the Environmental Protection Agency's “ENERGY STAR Program Requirements for Exit Signs,” Version 2.0, section 4 (Test Criteria), “Conditions for testing” and “Input power measurement.” (Incorporated by reference, see § 431.203)
[71 FR 71373, Dec. 8, 2006]
An illuminated exit sign manufactured on or after January 1, 2006, shall have an input power demand of 5 watts or less per face.
70 FR 60417, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for traffic signal modules and pedestrian modules, pursuant to Part B of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6309.
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Maximum wattage means the power consumed by the module after being operated for 60 minutes while mounted in a temperature testing chamber so that the lensed portion of the module is outside the chamber, all portions of the module behind the lens are within the chamber at a temperature of 74 °C and the air temperature in front of the lens is maintained at a minimum of 49 °C.
Nominal wattage means the power consumed by the module when it is operated within a chamber at a temperature of 25 °C after the signal has been operated for 60 minutes.
Pedestrian module means a light signal used to convey movement information to pedestrians.
Traffic signal module means a standard 8-inch (200 mm) or 12-inch (300 mm) traffic signal indication that—
(1) Consists of a light source, a lens, and all other parts necessary for operation; and
(2) Communicates movement messages to drivers through red, amber, and green colors.
[70 FR 60417, Oct. 18, 2005, as amended at 71 FR 71373, Dec. 8, 2006; 76 FR 12504, Mar. 7, 2011]
(a) General. The Department incorporates by reference the following test procedures into subpart M of part 431. The Director of the Federal Register has approved the material listed in paragraph (b) of this section for incorporation by reference in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. Any subsequent amendment to this material by the standard-setting organization will not affect the DOE test procedures unless and until DOE amends its test procedures. The Department incorporates the material as it exists on the date of the approval by the Federal Register and a notice of any change in the material will be published in the Federal Register.
(b) List of test procedures incorporated by reference.
(1) Environmental Protection Agency, “ENERGY STAR Program Requirements for Traffic Signals,” Version 1.1 issued February 4, 2003.
(2) Institute of Transportation Engineers (ITE), “Vehicle Traffic Control Signal Heads: Light Emitting Diode (LED) Circular Signal Supplement,” June 27, 2005.
(c) Availability of references —
(1) Inspection of test procedures. The test procedures incorporated by reference are available for inspection at:
(i) National Archives and Records Administration (NARA). For information on the availability of this material at NARA, call (202) 741-6030, or go to: http://www.archives.gov/federal_register/code_of_federal_regulations/ibr_locations.html.
(ii) U.S. Department of Energy, Forrestal Building, Room 1J-018 (Resource Room of the Building Technologies Program), 1000 Independence Avenue, SW., Washington, DC 20585-0121, (202) 586-9127, between 9 a.m. and 4 p.m., Monday through Friday, except Federal holidays.
(2) Obtaining copies of standards. Standards incorporated by reference may be obtained from the following sources:
(i) Copies of the Environmental Protection Agency “ENERGY STAR Program Requirements for Traffic Signals,” Version 1.1, may be obtained from the Environmental Protection Agency, Ariel Rios Building, 1200 Pennsylvania Avenue, NW., Washington, DC 20460, (202) 272-0167 or at http://www.epa.gov.
(ii) Institute of Transportation Engineers, 1099 14th Street, NW., Suite 300 West, Washington, DC 20005-3438, (202) 289-0222, or ite_staff@ite.org.
[71 FR 71373, Dec. 8, 2006]
(a) Scope. This section provides the test procedures for measuring, pursuant to EPCA, the maximum wattage and nominal wattage of traffic signal modules and pedestrian modules. For purposes of 10 CFR part 431 and EPCA, the test procedures for measuring the maximum wattage and nominal wattage of traffic signal modules and pedestrian modules shall be the test procedures specified in § 431.223(b).
(b) Testing and Calculations. Determine the nominal wattage and maximum wattage of each covered traffic signal module or pedestrian module by conducting the test procedure set forth in Environmental Protection Agency, “ENERGY STAR Program Requirements for Traffic Signals,” Version 1.1, section 1, “Definitions,” and section 4, “Test Criteria.” (Incorporated by reference, see § 431.223) Use a wattmeter having an accuracy of ±1% to measure the nominal wattage and maximum wattage of a red and green traffic signal module, and a pedestrian module when conducting the photometric and colormetric tests as specified by the testing procedures in VTCSH 2005.
[71 FR 71373, Dec. 8, 2006]
Any traffic signal module or pedestrian module manufactured on or after January 1, 2006, shall meet both of the following requirements:
(a) Have a nominal wattage and maximum wattage no greater than:
| Maximum wattage (at 74 °C) |
Nominal wattage (at 25 °C) |
|
|---|---|---|
| Traffic Signal Module Type: | ||
| 12″ Red Ball | 17 | 11 |
| 8″ Red Ball | 13 | 8 |
| 12″ Red Arrow | 12 | 9 |
| 12″ Green Ball | 15 | 15 |
| 8″ Green Ball | 12 | 12 |
| 12″ Green Arrow | 11 | 11 |
| Pedestrian Module Type: | ||
| Combination Walking Man/Hand | 16 | 13 |
| Walking Man | 12 | 9 |
| Orange Hand | 16 | 13 |
(b) Be installed with compatible, electrically connected signal control interface devices and conflict monitoring systems.
[70 FR 60417, Oct. 18, 2005, as amended at 71 FR 71374, Dec. 8, 2006]
70 FR 60418, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for unit heaters, pursuant to Part B of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6309.
Automatic flue damper means a device installed in the flue outlet or in the inlet of or upstream of the draft control device of an individual, automatically operated, fossil fuel-fired appliance that is designed to automatically open the flue outlet during appliance operation and to automatically close the flue outlet when the appliance is in a standby condition.
Automatic vent damper means a device intended for installation in the venting system of an individual, automatically operated, fossil fuel-fired appliance either in the outlet or downstream of the appliance draft control device, which is designed to automatically open the venting system when the appliance is in operation and to automatically close off the venting system when the appliance is in a standby or shutdown condition.
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Intermittent ignition device means an ignition device in which the ignition source is automatically shut off when the appliance is in an off or standby condition.
Power venting means a venting system that uses a separate fan, either integral to the appliance or attached to the vent pipe, to convey products of combustion and excess or dilution air through the vent pipe.
Unit heater means a self-contained fan-type heater designed to be installed within the heated space; however, the term does not include a warm air furnace.
Warm air furnace means commercial warm air furnace as defined in § 431.72.
[70 FR 60418, Oct. 18, 2005, as amended at 71 FR 71374, Dec. 8, 2006; 76 FR 12504, Mar. 7, 2011]
A unit heater manufactured on or after August 8, 2008, shall:
(a) Be equipped with an intermittent ignition device; and
(b) Have power venting or an automatic flue damper. An automatic vent damper is an acceptable alternative to an automatic flue damper for those unit heaters where combustion air is drawn from the conditioned space.
[70 FR 60418, Oct. 18, 2005, as amended at 71 FR 71374, Dec. 8, 2006]
70 FR 60418, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for commercial prerinse spray valves, pursuant to section 135 of the Energy Policy Act of 2005, Pub. L. 109-58.
As used in this subpart:
Basic model means all spray settings of a given class manufactured by one manufacturer, which have essentially identical physical and functional (or hydraulic) characteristics that affect water consumption or water efficiency.
Commercial prerinse spray valve means a handheld device that has a release-to-close valve and is suitable for removing food residue from food service items before cleaning them in commercial dishwashing or ware washing equipment. DOE may determine that a device is suitable for removing food residue from food service items before cleaning them in commercial dishwashing or ware washing equipment based on any or all of the following:
(1) Equipment design and representations (for example, whether equipment is represented as being capable of rinsing dishes as compared to equipment that is represented exclusively for washing walls and floors or animal washing);
(2) Channels of marketing and sales (for example, whether equipment is marketed or sold through outlets that market or sell to food service entities);
(3) Actual sales (including whether the end-users are restaurants or commercial or institutional kitchens, even if those sales are indirectly through an entity such as a distributor).
Spray force means the amount of force exerted onto the spray disc, measured in ounce-force (ozf).
[80 FR 81453, Dec. 30, 2015, as amended at 87 FR 13909, Mar. 11, 2022]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the U.S. Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved material is available for inspection at the DOE and at the National Archives and Records Administration (NARA). Contact DOE at: The U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 6th Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, or Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the source(s) in the following paragraph(s) of this section.
(b) ASTM. ASTM, International, 100 Barr Harbor Drive, P.O. Box C700, West Conshohocken, PA 19428-2959, (610) 832-9585, or go to www.astm.org.
(1) ASTM F2324-13 (R2019) (“ASTM F2324”),”Standard Test Method for Prerinse Spray Valves”, Approved May 1, 2019; IBR approved for § 431.264.
(2) [Reserved]
[87 FR 13910, Mar. 11, 2022]
(a) Scope. This section provides the test procedure to measure the flow rate and spray force of a commercial prerinse spray valve.
(b) Testing and calculations for a unit with a single spray setting —
(1) Flow rate.
(i) Test each unit in accordance with the requirements of Sections 6.1 through 6.9 (Apparatus) (except 6.4 and 6.7), 9.1 through 9.4 (Preparation of Apparatus), and 10.1 through 10.2.5 (Procedure) of ASTM F2324, (incorporated by reference, see § 431.263). Precatory language in ASTM F2324 is to be treated as mandatory for the purpose of testing. In Section 9.1 of ASTM F2324, the second instance of “prerinse spray valve” refers to the spring-style deck-mounted prerinse unit defined in Section 6.8. In lieu of using manufacturer installation instructions or packaging, always connect the commercial prerinse spray valve to the flex tubing for testing. Normalize the weight of the water to calculate flow rate using Equation 1 to this paragraph, where Wwater is the weight normalized to a 1 minute time period, W1 is the weight of the water in the carboy at the conclusion of the flow rate test, and t1 is the total recorded time of the flow rate test.
(ii) Perform calculations in accordance with Section 11.3.1 (Calculation and Report) of ASTM F2324. Record the water temperature ( °F) and dynamic water pressure (psi) once at the start for each run of the test. Record the time (min), the normalized weight of water in the carboy (lb) and the resulting flow rate (gpm) once at the end of each run of the test. Record flow rate measurements of time (min) and weight (lb) at the resolutions of the test instrumentation. Perform three runs on each unit, as specified in Section 10.2.5 of ASTM F2324, but disregard any references to Annex A1. Then, for each unit, calculate the mean of the three flow rate values determined from each run. Round the final value for flow rate to two decimal places and record that value.
(2) Spray force. Test each unit in accordance with the test requirements specified in Sections 6.2 and 6.4 through 6.9 (Apparatus), 9.1 through 9.5.3.2 (Preparation of Apparatus), and 10.3.1 through 10.3.8 (Procedure) of ASTM F2324. In Section 9.1 of ASTM F2324, the second instance of “prerinse spray valve” refers to the spring-style deck-mounted prerinse unit defined in Section 6.8. In lieu of using manufacturer installation instructions or packaging, always connect the commercial prerinse spray valve to the flex tubing for testing. Record the water temperature ( °F) and dynamic water pressure (psi) once at the start for each run of the test. In order to calculate the mean spray force value for the unit under test, there are two measurements per run and there are three runs per test. For each run of the test, record a minimum of two spray force measurements and calculate the mean of the measurements over the 15-second time period of stabilized flow during spray force testing. Record the time (min) once at the end of each run of the test. Record spray force measurements at the resolution of the test instrumentation. Conduct three runs on each unit, as specified in Section 10.3.8 of ASTM F2324, but disregard any references to Annex A1. Ensure the unit has been stabilized separately during each run. Then for each unit, calculate and record the mean of the spray force values determined from each run. Round the final value for spray force to one decimal place.
(c) Testing and calculations for a unit with multiple spray settings. If a unit has multiple user-selectable spray settings, or includes multiple spray faces that can be installed, for each possible spray setting or spray face:
(1) Measure both the flow rate and spray force according to paragraphs (b)(1) and (2) of this section (including calculating the mean flow rate and mean spray force) for each spray setting; and
(2) Record the mean flow rate for each spray setting, rounded to two decimal places. Record the mean spray force for each spray setting, rounded to one decimal place.
(d) Test procedure for voluntary representations. Follow paragraph (b)(1) or (2) or (c) of this section, as applicable, using test water pressure(s) of interest for voluntary representations of flow rate. Representations made at a water pressure other than the required test water pressure cannot replace a representation at the required test water pressure specified in Section 9.1 of ASTM F2324. Any voluntary representation of flow rate made pursuant to this paragraph shall specify the water pressure associated with the represented flow rate.
[80 FR 81453, Dec. 30, 2015, as amended at 87 FR 13910, Mar. 11, 2022]
(a) Commercial prerinse spray valves manufactured on or after January 1, 2006 and before January 28, 2019, shall have a flow rate of not more than 1.6 gallons per minute. For the purposes of this standard, a commercial prerinse spray valve is a handheld device designed and marketed for use with commercial dishwashing and ware washing equipment that sprays water on dishes, flatware, and other food service items for the purpose of removing food residue before cleaning the items.
(b) Commercial prerinse spray valves manufactured on or after January 28, 2019 shall have a flow rate that does not exceed the following:
| Product class (spray force in ounce-force, ozf) |
Flow rate (gallons per minute, gpm) |
|---|---|
| Product Class 1 (≤5.0 ozf) | 1.00 |
| Product Class 2 (>5.0 ozf and ≤8.0 ozf) | 1.20 |
| Product Class 3 (>8.0 ozf) | 1.28 |
(1) For the purposes of this standard, the definition of commercial prerinse spray valve in § 431.262 applies.
(2) [Reserved]
[81 FR 4801, Jan. 27, 2016]
70 FR 60418, Oct. 18, 2005, unless otherwise noted.
This subpart contains energy conservation requirements for mercury vapor lamp ballasts, pursuant to section 135 of the Energy Policy Act of 2005, Pub. L. 109-58.
Ballast means a device used with an electric discharge lamp to obtain necessary circuit conditions (voltage, current, and waveform) for starting and operating.
High intensity discharge lamp means an electric-discharge lamp in which—
(1) The light-producing arc is stabilized by the arc tube wall temperature; and
(2) The arc tube wall loading is in excess of 3 Watts/cm2, including such lamps that are mercury vapor, metal halide, and high-pressure sodium lamps.
Mercury vapor lamp means a high intensity discharge lamp, including clear, phosphor-coated, and self-ballasted screw base lamps, in which the major portion of the light is produced by radiation from mercury typically operating at a partial vapor pressure in excess of 100,000 Pa (approximately 1 atm).
Mercury vapor lamp ballast means a device that is designed and marketed to start and operate mercury vapor lamps intended for general illumination by providing the necessary voltage and current.
Specialty application mercury vapor lamp ballast means a mercury vapor lamp ballast that—
(1) Is designed and marketed for operation of mercury vapor lamps used in quality inspection, industrial processing, or scientific use, including fluorescent microscopy and ultraviolet curing; and
(2) In the case of a specialty application mercury vapor lamp ballast, the label of which—
(i) Provides that the specialty application mercury vapor lamp ballast is ‘For specialty applications only, not for general illumination’; and
(ii) Specifies the specific applications for which the ballast is designed.
[74 FR 12074, Mar. 23, 2009]
Mercury vapor lamp ballasts, other than specialty application mercury vapor lamp ballasts, shall not be manufactured or imported after January 1, 2008.
[74 FR 12074, Mar. 23, 2009]
71 FR 71375, Dec. 8, 2006, unless otherwise noted.
This subpart specifies test procedures and energy conservation standards for certain commercial refrigerated bottled or canned beverage vending machines, pursuant to part A of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6309. The regulatory provisions of §§ 430.33 and 430.34 and subparts D and E of part 430 of this chapter are applicable to refrigerated bottled or canned beverage vending machines.
[80 FR 45792, July 31, 2015]
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency.
Bottled or canned beverage means a beverage in a sealed container.
Class A means a refrigerated bottled or canned beverage vending machine that is not a combination vending machine and in which 25 percent or more of the surface area on the front side of the beverage vending machine is transparent.
Class B means a refrigerated bottled or canned beverage vending machine that is not considered to be Class A and is not a combination vending machine.
Combination A means a combination vending machine where 25 percent or more of the surface area on the front side of the beverage vending machine is transparent.
Combination B means a combination vending machine that is not considered to be Combination A.
Combination vending machine means a bottled or canned beverage vending machine containing two or more compartments separated by a solid partition, that may or may not share a product delivery chute, in which at least one compartment is designed to be refrigerated, as demonstrated by the presence of temperature controls, and at least one compartment is not.
Refrigerated bottled or canned beverage vending machine means a commercial refrigerator (as defined at § 431.62) that cools bottled or canned beverages and dispenses the bottled or canned beverages on payment.
Transparent means greater than or equal to 45 percent light transmittance, as determined in accordance with ASTM E 1084-86 (Reapproved 2009), (incorporated by reference, see § 431.293) at normal incidence and in the intended direction of viewing.
V means the refrigerated volume (ft3) of the refrigerated bottled or canned beverage vending machine, as measured by Appendix C of ANSI/ASHRAE 32.1 (incorporated by reference, see § 431.293).
[71 FR 71375, Dec. 8, 2006, as amended at 74 FR 44967, Aug. 31, 2009; 76 FR 12504, Mar. 7, 2011; 80 FR 45792, July 31, 2015; 81 FR 1112, Jan. 8, 2016]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Ave. SW, EE-5B, Washington, DC 20585, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section:
(b) AHAM. Association of Home Appliance Manufacturers, 1111 19th Street NW, Suite 402, Washington, DC 20036; (202) 872-5955; www.aham.org.
(1) AHAM HRF-1-2016, Energy and Internal Volume of Refrigerating Appliances, copyright 2016; IBR approved for appendix B to this subpart.
(2) [Reserved]
(c) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc., 1791 Tullie Circle NE, Atlanta, GA 30329; (404) 636-8400; www.ashrae.org.
(1) ANSI/ASHRAE Standard 32.1-2022 (ANSI/ASHRAE 32.1), Methods of Testing for Rating Refrigerated Vending Machines for Sealed Beverages, approved December 30, 2022; IBR approved for § 431.292 and appendix B to this subpart.
(2) [Reserved]
(d) ASTM. ASTM International, 100 Barr Harbor Drive, P.O. Box C700, West Conshohocken, PA 19428-2959; (877) 909-2786; www.astm.org.
(1) ASTM E 1084-86 (Reapproved 2009), Standard Test Method for Solar Transmittance (Terrestrial) of Sheet Materials Using Sunlight, approved April 1, 2009; IBR approved for § 431.292.
(2) [Reserved]
[88 FR 28400, May 4, 2023]
(a) Scope. This section provides test procedures for measuring, pursuant to EPCA, the energy consumption of refrigerated bottled or canned beverage vending machines.
(b) Testing and Calculations. Determine the daily energy consumption of each covered refrigerated bottled or canned beverage vending machine by conducting the appropriate test procedure set forth in appendix A or B to this subpart.
[71 FR 71375, Dec. 8, 2006, as amended at 80 FR 45793, July 31, 2015]
(a) Each refrigerated bottled or canned beverage vending machine manufactured on or after August 31, 2012 and before January 8, 2019, shall have a daily energy consumption (in kilowatt hours per day), when measured in accordance with the DOE test procedure at § 431.294, that does not exceed the following:
| Equipment class | Maximum daily energy consumption (kilowatt hours per day) |
|---|---|
| Class A | 0.055 × V † + 2.56. |
| Class B | 0.073 × V † + 3.16. |
| Combination Vending Machines | [Reserved]. |
| † “V” is the representative value of refrigerated volume (ft3) of the BVM model, as calculated pursuant to 10 CFR 429.52(a)(3). | |
(b) Each refrigerated bottled or canned beverage vending machine manufactured on or after January 8, 2019, shall have a daily energy consumption (in kilowatt hours per day), when measured in accordance with the DOE test procedure at § 431.294, that does not exceed the following:
| Equipment class | Maximum daily energy consumption (kilowatt hours per day) |
|---|---|
| Class A | 0.052 × V † + 2.43. |
| Class B | 0.052 × V † + 2.20. |
| Combination A | 0.086 × V † + 2.66. |
| Combination B | 0.111 × V † + 2.04. |
| † “V” is the representative value of refrigerated volume (ft3) of the BVM model, as calculated pursuant to 10 CFR 429.52(a)(3). | |
[81 FR 1113, Jan. 8, 2016]
Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standards for refrigerated bottled or canned beverage vending machines at 10 CFR 431.296, revised as of January 1, 2023. Specifically, before October 31, 2023, representations must be based upon results generated either under this appendix as codified on June 5, 2023, or under 10 CFR part 431, subpart Q, appendix B, revised as of January 1, 2023. Any representations made on or after October 31, 2023, must be made based upon results generated using this appendix as codified on June 5, 2023.
0. Incorporation by Reference
DOE incorporated by reference in § 431.293 the entire standard for AHAM HRF-1-2016 and ANSI/ASHRAE Standard 32.1-2022; however, only enumerated provisions of those documents are applicable to this appendix as follows:
0.1. AHAM HRF-1-2016
(a) Section 4, “Method for Computing Refrigerated Volume of Refrigerators, Refrigerator-Freezer, Wine Chillers, and Freezers” as referenced in section 3.1 of this appendix.
(b) Reserved.
0.2. ANSI/ASHRAE Standard 32.1-2022
(a) Section 3, “Definitions,” as referenced in section 1 of this appendix.
(b) Section 4, “Instruments,” as referenced in section 2 of this appendix.
(c) Section 5, “Vending Machine Capacity,” and Normative Appendix C, “Measurement of Volume,” as referenced in sections 2 and 3.1 of this appendix.
(d) Section 6, “Test Conditions,” as referenced in section 2 of this appendix.
(e) Section 7.1, “Test Procedures—General Requirements” (except Section 7.1.2, “Functionality,” and Section 7.1.5.1, “Beverage Temperature Test Packages”), and Section 7.2, “Energy Consumption Test,” (except Section 7.2.2.6), as referenced in sections 1 and 2 of this appendix.
1. General. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over ANSI/ASHRAE Standard 32.1-2022.
1.1 Definitions. In addition to the definitions specified in Section 3, “Definitions,” of ANSI/ASHRAE Standard 32.1-2022, the following definitions are also applicable to this appendix.
Accessory low power mode means a state in which a beverage vending machine's lighting and/or other energy-using systems are in low power mode, but that is not a refrigeration low power mode. Functions that may constitute an accessory low power mode may include, for example, dimming or turning off lights, but does not include adjustment of the refrigeration system to elevate the temperature of the refrigerated compartment(s).
External accessory standby mode means the mode of operation in which any external, integral customer display signs, lighting, or digital screens are connected to main power; do not produce the intended illumination, display, or interaction functionality; and can be switched into another mode automatically with only a remote user-generated or an internal signal.
Low power mode means a state in which a beverage vending machine's lighting, refrigeration, and/or other energy-using systems are automatically adjusted (without user intervention) such that they consume less energy than they consume in an active vending environment.
Lowest application product temperature means either:
(a) For units that operate only at temperatures above the integrated average temperature specified in Table 1 of ANSI/ASHRAE Standard 32.1-2022, the lowest integrated average temperature a given basic model is capable of maintaining so as to comply with the temperature stabilization requirements specified in section 7.2.2.2 of ANSI/ASHRAE Standard 32.1-2022; or
(b) For units that operate only at temperatures below the integrated average temperature specified in Table 1 of ANSI/ASHRAE Standard 32.1-2022, the highest integrated average temperature a given basic model is capable of maintaining so as to comply with the temperature stabilization requirements specified in section 7.2.2.2 of ANSI/ASHRAE Standard 32.1-2022.
Refrigeration low power mode means a state in which a beverage vending machine's refrigeration system is in low power mode because of elevation of the temperature of the refrigerated compartment(s). To qualify as low power mode, the unit must satisfy the requirements described in section 2.3.2.1 of this appendix.
1.2 [Reserved]
2. Test Procedure. Conduct testing according to section 4, “Instruments”; section 5, “Vendible Capacity”; section 6, “Test Conditions”; section 7.1, “Test Procedures—General Requirements” (except Section 7.1.2 “Functionality” and section 7.1.5.1 “Beverage Temperature Test Packages”); and section 7.2, “Energy Consumption Test” (except section 7.2.2.6) of ANSI/ASHRAE Standard 32.1-2022, except as described in the following sections.
2.1. Lowest Application Product Temperature. If a refrigerated bottled or canned beverage vending machine is not capable of maintaining an integrated average temperature of 36 °F (±1 °F) during the 24-hour test period, the unit must be tested at the lowest application product temperature, as defined in section 1.1 of this appendix.
2.2. Equipment Installation and Test Setup. Except as provided in this section 2.2 of this appendix, the test procedure for energy consumption of refrigerated bottled or canned beverage vending machines shall be conducted in accordance with the methods specified in sections 7.1 through 7.2.2.7 under “Test Procedures” of ANSI/ASHRAE Standard 32.1-2022.
2.2.1. Equipment Loading. Configure refrigerated bottled or canned beverage vending machines to hold the maximum number of standard products.
2.2.1.1. Non-Beverage Shelves. Any shelves within the refrigerated compartment(s) for non-beverage merchandise only shall not be loaded for testing.
2.2.1.2. Standard Products. The standard product shall be standard 12-ounce aluminum beverage cans filled with a liquid with a density of 1.0 grams per milliliter (“g/mL”) ±0.1 g/mL at 36 °F. For product storage racks that are not capable of vending 12-ounce cans, but are capable of vending 20-ounce bottles, the standard product shall be 20-ounce plastic bottles filled with a liquid with a density of 1.0 g/mL ±0.1 g/mL at 36 °F. For product storage racks that are not capable of vending 12-ounce cans or 20-ounce bottles, the standard product shall be the packaging and contents specified by the manufacturer in product literature as the standard product (i.e., the specific merchandise the refrigerated bottled or canned beverage vending machine is designed to vend).
2.2.1.3. Standard Test Packages. A standard test package is a standard product, as specified in section 2.2.1.2 of this appendix, altered to include a temperature-measuring instrument at its center of mass.
2.2.2. Sensor Placement. The integrated average temperature of next-to-vend beverages shall be measured in standard test packages in the next-to-vend product locations specified in section 7.1.5.2 of ANSI/ASHRAE Standard 32.1-2022. Do not run the thermocouple wire and other measurement apparatus through the dispensing door; the thermocouple wire and other measurement apparatus must be configured and sealed so as to minimize air flow between the interior refrigerated volume and the ambient room air. If a manufacturer chooses to employ a method other than routing thermocouple and sensor wires through the door gasket and ensuring the gasket is compressed around the wire to ensure a good seal, then it must maintain a record of the method used in the data underlying that basic model's certification pursuant to 10 CFR 429.71.
2.2.3. Vending Mode Test Period. The vending mode test period begins after temperature stabilization has been achieved, as described in section 7.2.2.2 of ANSI/ASHRAE Standard 32.1-2022 and continues for 18 hours for equipment with an accessory low power mode or for 24 hours for equipment without an accessory low power mode. For the vending mode test period, equipment with energy-saving features that cannot be disabled shall have those features set to the most energy-consuming settings, except for as specified in section 2.2.4 of this appendix. In addition, all energy management systems shall be disabled. Provide, if necessary, any physical stimuli or other input to the machine needed to prevent automatic activation of low power modes during the vending mode test period.
2.2.4. Accessory Low Power Mode Test Period. For equipment with an accessory low power mode, the accessory low power mode may be engaged for 6 hours, beginning 18 hours after the temperature stabilization requirements established in section 7.2.2.2 of ANSI/ASHRAE Standard 32.1-2022 have been achieved, and continuing until the end of the 24-hour test period. During the accessory low power mode test, operate the refrigerated bottled or canned beverage vending machine with the lowest energy-consuming lighting and control settings that constitute an accessory low power mode. The specification and tolerances for integrated average temperature in Table 2 of ANSI/ASHRAE Standard 32.1-2022 still apply, and any refrigeration low power mode must not be engaged. Provide, if necessary, any physical stimuli or other input to the machine needed to prevent automatic activation of refrigeration low power modes during the accessory low power mode test period.
2.2.5. Accessories. Unless specified otherwise in this appendix or ANSI/ASHRAE Standard 32.1-2022, all standard components that would be used during normal operation of the basic model in the field and are necessary to provide sufficient functionality for cooling and vending products in field installations (i.e., product inventory, temperature management, product merchandising (including, e.g., lighting or signage), product selection, and product transport and delivery) shall be in place during testing and shall be set to the maximum energy-consuming setting if manually adjustable. Components not necessary for the inventory, temperature management, product merchandising (e.g., lighting or signage), product selection, or product transport and delivery shall be de-energized. If systems not required for the primary functionality of the machine as stated in this section cannot be de-energized without preventing the operation of the machine, then they shall be placed in the lowest energy-consuming state. Components with controls that are permanently operational and cannot be adjusted by the machine operator shall be operated in their normal setting and consistent with the requirements of sections 2.2.3 and 2.2.4 of this appendix. The specific components and accessories listed in the subsequent sections shall be operated as stated during the test, except when controlled as part of a low power mode during the low power mode test period.
2.2.5.1. Payment Mechanisms. Refrigerated bottled or canned beverage vending machines shall be tested with no payment mechanism in place, the payment mechanism in place but de-energized, or the payment mechanism in place but set to the lowest energy-consuming state, if it cannot be de-energized. A default payment mechanism energy consumption value of 0.20 kWh/day shall be added to the primary rated energy consumption per day, as noted in section 2.3 of this appendix.
2.2.5.2. Internal Lighting. All lighting that is contained within or is part of the internal physical boundary of the refrigerated bottled or canned beverage vending machine, as established by the top, bottom, and side panels of the equipment, shall be placed in its maximum energy-consuming state.
2.2.5.3. External Customer Display Signs, Lights, and Digital Screens. All external customer display signs, lights, and digital screens that are independent from the refrigeration or vending performance of the refrigerated bottled or canned beverage vending machine must be disconnected, disabled, or otherwise de-energized for the duration of testing. Customer display signs, lighting, and digital screens that are integrated into the beverage vending machine cabinet or controls such that they cannot be de-energized without disabling the refrigeration or vending functions of the refrigerated bottled or canned beverage vending machine or modifying the circuitry must be placed in external accessory standby mode, if available, or their lowest energy-consuming state. Digital displays that also serve a vending or money processing function must be placed in the lowest energy-consuming state that still allows the money processing feature to function.
2.2.5.4. Anti-sweat or Other Electric Resistance Heaters. Anti-sweat or other electric resistance heaters must be operational during the entirety of the test procedure. Units with a user-selectable setting must have the heaters energized and set to the most energy-consumptive position. Units featuring an automatic, non-user-adjustable controller that turns on or off based on environmental conditions must be operating in the automatic state. Units that are not shipped with a controller from the point of manufacture, but are intended to be used with a controller, must be equipped with an appropriate controller when tested.
2.2.5.5. Condensate Pan Heaters and Pumps. All electric resistance condensate heaters and condensate pumps must be installed and operational during the test. Prior to the start of the test, including the 24-hour period used to determine temperature stabilization prior to the start of the test period, as described in section 7.2.2.2 of ANSI/ASHRAE Standard 32.1-2022, the condensate pan must be dry. For the duration of the test, including the 24-hour time period necessary for temperature stabilization, allow any condensate moisture generated to accumulate in the pan. Do not manually add or remove water from the condensate pan at any time during the test. Any automatic controls that initiate the operation of the condensate pan heater or pump based on water level or ambient conditions must be enabled and operated in the automatic setting.
2.2.5.6. Illuminated Temperature Displays. All illuminated temperature displays must be energized and operated during the test the same way they would be energized and operated during normal field operation, as recommended in manufacturer product literature, including manuals.
2.2.5.7. Condenser Filters. Remove any nonpermanent filters provided to prevent particulates from blocking a model's condenser coil.
2.2.5.8. Security Covers. Remove any devices used to secure the model from theft or tampering.
2.2.5.9. General Purpose Outlets. During the test, do not connect any external load to any general purpose outlets available on a unit.
2.2.5.10. Crankcase Heaters and Other Electric Resistance Heaters for Cold Weather. Crankcase heaters and other electric resistance heaters for cold weather must be operational during the test. If a control system, such as a thermostat or electronic controller, is used to modulate the operation of the heater, it must be activated during the test and operated in accordance with the manufacturer's instructions.
2.2.5.11. Refrigerant Leak Mitigation Controls. Any refrigerant leak mitigation controls that are independent from the refrigeration or vending performance of the refrigerated bottled or canned beverage vending machine must be disconnected, disabled, or otherwise de-energized for the duration of testing. Refrigerant leak mitigation controls that are integrated into the refrigerated bottled or canned beverage vending machine cabinet or controls such that they cannot be de-energized without disabling the refrigeration or vending functions of the refrigerated bottled or canned beverage vending machine or modifying the circuitry must be placed in external accessory standby mode, if available, or their lowest energy-consuming state.
2.3. Determination of Daily Energy Consumption. The daily energy consumption shall be equal to the primary rated energy consumption per day (ED), in kWh, determined in accordance with the calculation procedure in section 7.2.3.1, “Calculation of Daily Energy Consumption,” of ANSI/ASHRAE Standard 32.1-2022 plus the default payment mechanism energy consumption value from section 2.2.5.1 of this appendix, if applicable. In section 7.2.3.1 of ANSI/ASHRAE Standard 32.1-2022, the energy consumed during the test shall be the energy measured during the vending mode test period and accessory low power mode test period, as specified in sections 2.2.3 and 2.2.4 of this appendix, as applicable.
2.3.1. Refrigeration Low Power Mode. For refrigerated bottled or canned beverage vending machines with a refrigeration low power mode, multiply the value determined in section 2.3 of this appendix by 0.97 to determine the daily energy consumption of the unit tested. For refrigerated bottled or canned beverage vending machines without a refrigeration low power mode, the value determined in section 2.3 of this appendix is the daily energy consumption of the unit tested.
2.3.1.1. Refrigeration Low Power Mode Validation Test Method. This test method is not required for the certification of refrigerated bottled or canned beverage vending machines. To verify the existence of a refrigeration low power mode, initiate the refrigeration low power mode in accordance with manufacturer instructions contained in product literature and manuals, after completion of the 6-hour low power mode test period. Continue recording all the data specified in section 7.2.2.3 of ANSI/ASHRAE Standard 32.1-2022 until existence of a refrigeration low power mode has been confirmed or denied. The refrigerated bottled or canned beverage vending machine shall be deemed to have a refrigeration low power mode if either:
(a) The following three requirements have been satisfied:
(1) The instantaneous average next-to-vend beverage temperature must reach at least 4 °F above the integrated average temperature or lowest application product temperature, as applicable, within 6 hours.
(2) The instantaneous average next-to-vend beverage temperature must be maintained at least 4 °F above the integrated average temperature or lowest application product temperature, as applicable, for at least 1 hour.
(3) After the instantaneous average next-to-vend beverage temperature is maintained at or above 4 °F above the integrated average temperature or lowest application product temperature, as applicable, for at least 1 hour, the refrigerated beverage vending machine must return to the specified integrated average temperature or lowest application product temperature, as applicable, automatically without direct physical intervention.
(b) The compressor does not cycle on for the entire 6-hour period, in which case the instantaneous average beverage temperature does not have to reach 4 °F above the integrated average temperature or lowest application product temperature, as applicable, but, the equipment must still automatically return to the integrated average temperature or lowest application product temperature, as applicable, after the 6-hour period without direct physical intervention.
2.3.2. Calculations and Rounding. In all cases, the daily energy consumption must be calculated with raw measured values and the final result rounded to units of 0.01 kWh/day.
3. Determination of Refrigeration Volume and Surface Area.
3.1. Refrigerated Volume. Determine the “refrigerated volume” of refrigerated bottled or canned beverage vending machines in accordance with section 5.3, “Refrigerated Volume,” and Appendix C, “Measurement of Volume,” of ANSI/ASHRAE Standard 32.1-2022 including the referenced methodology in section 4, “Method for Computing Refrigerated Volume of Refrigerators, Refrigerator-Freezer, Wine Chillers, and Freezers,” of AHAM HRF-1-2016. For combination vending machines, the “refrigerated volume” does not include any non-refrigerated compartment(s).
3.2. Determination of Surface Area. (Note: This section is not required for the certification of refrigerated bottled or canned beverage vending machines.) Determine the surface area of each beverage vending machine as the length multiplied by the height of outermost surface of the beverage vending machine cabinet, measured from edge to edge excluding any legs or other protrusions that extend beyond the dimensions of the primary cabinet. Determine the transparent and non-transparent areas on each side of a beverage vending machine as the total surface area of material that is transparent or is not transparent, respectively.
[88 FR 28400, May 4, 2023]
74 FR 12074, Mar. 23, 2009, unless otherwise noted.
This subpart contains energy conservation requirements for walk-in coolers and walk-in freezers, pursuant to Part C of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
Adaptive defrost means a factory-installed defrost control system that reduces defrost frequency by initiating defrosts or adjusting the number of defrosts per day in response to operating conditions (e.g., moisture levels in the refrigerated space, measurements that represent coil frost load) rather than initiating defrost strictly based on compressor run time or clock time.
Attached split system means a matched pair refrigeration system which is designed to be installed with the evaporator entirely inside the walk-in enclosure and the condenser entirely outside the walk-in enclosure, and the evaporator and condenser are permanently connected with structural members extending through the walk-in wall.
Basic model means all components of a given type of walk-in cooler or walk-in freezer (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency; and
(1) With respect to panels, which do not have any differing features or characteristics that affect U-factor.
(2) [Reserved]
CO2 unit cooler means a unit cooler that includes a nameplate listing only CO2 as an approved refrigerant.
Dedicated condensing unit means a positive displacement condensing unit that is part of a refrigeration system (as defined in this section) and is an assembly that
(1) Includes 1 or more compressors, a condenser, and one refrigeration circuit; and
(2) Is designed to serve one refrigerated load.
Dedicated condensing refrigeration system means one of the following:
(1) A dedicated condensing unit;
(2) A single-package dedicated system; or
(3) A matched refrigeration system.
Detachable single-packaged dedicated system means a system consisting of a dedicated condensing unit and an insulated evaporator section in which the evaporator section is designed to be installed external to the walk-in enclosure and circulating air through the enclosure wall, and the condensing unit is designed to be installed either attached to the evaporator section or mounted remotely with a set of refrigerant lines connecting the two components.
Display door means a door that:
(1) Is designed for product display; or
(2) Has 75 percent or more of its surface area composed of glass or another transparent material.
Display panel means a panel that is entirely or partially comprised of glass, a transparent material, or both and is used for display purposes.
Door means an assembly installed in an opening on an interior or exterior wall that is used to allow access or close off the opening and that is movable in a sliding, pivoting, hinged, or revolving manner of movement. For walk-in coolers and walk-in freezers, a door includes the frame (including mullions), the door leaf or multiple leaves (including glass) within the frame, and any other elements that form the assembly or part of its connection to the wall.
Door leaf means the pivoting, rolling, sliding, or swinging portion of a door.
Door surface area means the product of the height and width of a walk-in door measured external to the walk-in. The height and width dimensions shall be perpendicular to each other and parallel to the wall or panel of the walk-in to which the door is affixed. The height and width measurements shall extend to the edge of the frame and frame flange (as applicable) to which the door is affixed. For sliding doors, the height and width measurements shall include the track; however, the width (for horizontal sliding doors) or the height (for vertical sliding doors) shall be truncated to the external width or height of the door leaf or leaves and its frame or casings. The surface area of a display door is represented as Add and the surface area of a non-display door is represented as And.
Ducted fan coil unit means an assembly, including means for forced air circulation capable of moving air against both internal and non-zero external flow resistance, and elements by which heat is transferred from air to refrigerant to cool the air, with provision for ducted installation.
Ducted multi-circuit single-packaged dedicated system means a ducted single-packaged dedicated system or a ducted single-packaged dedicated system (as defined in this section) that contains two or more refrigeration circuits that refrigerate a single stream of circulated air.
Ducted single-packaged dedicated system means a refrigeration system (as defined in this section) that is a single-packaged assembly designed for use with ducts, that includes one or more compressors, a condenser, a means for forced circulation of refrigerated air, and elements by which heat is transferred from air to refrigerant.
Envelope means—
(1) The portion of a walk-in cooler or walk-in freezer that isolates the interior, refrigerated environment from the ambient, external environment; and
(2) All energy-consuming components of the walk-in cooler or walk-in freezer that are not part of its refrigeration system.
Freight door means a door that is not a display door and is equal to or larger than 4 feet wide and 8 feet tall.
High-temperature refrigeration system means a refrigeration system which is not designed to operate below 45 °F.
Indoor dedicated condensing refrigeration system means a dedicated condensing refrigeration system designated by the manufacturer for indoor use or for which there is no designation regarding the use location.
K-factor means the thermal conductivity of a material.
Manufacturer of a walk-in cooler or walk-in freezer means any person who:
(1) Manufactures a component of a walk-in cooler or walk-in freezer that affects energy consumption, including, but not limited to, refrigeration, doors, lights, windows, or walls; or
(2) Manufactures or assembles the complete walk-in cooler or walk-in freezer.
Matched condensing unit means a dedicated condensing unit that is distributed in commerce with one or more unit cooler(s) specified by the condensing unit manufacturer.
Matched refrigeration system (also called “matched-pair”) means a refrigeration system including the matched condensing unit and the one or more unit coolers with which it is distributed in commerce.
Multi-circuit single-packaged dedicated system means a single-packaged dedicated system or a ducted single-packaged dedicated system (as defined in this section) that contains two or more refrigeration circuits that refrigerate a single stream of circulated air.
Non-display door means a door that is not a display door.
Outdoor dedicated condensing refrigeration system means a dedicated condensing refrigeration system designated by the manufacturer for outdoor use.
Panel means a construction component that is not a door and is used to construct the envelope of the walk-in, i.e., elements that separate the interior refrigerated environment of the walk-in from the exterior.
Passage door means a door that is not a freight or display door.
Refrigerated means held at a temperature at or below 55 degrees Fahrenheit using a refrigeration system.
Refrigerated storage space means a space held at refrigerated (as defined in this section) temperatures.
Refrigeration system means the mechanism (including all controls and other components integral to the system's operation) used to create the refrigerated environment in the interior of a walk-in cooler or walk-in freezer, consisting of:
(1) A dedicated condensing refrigeration system (as defined in this section); or
(2) A unit cooler.
Single-packaged dedicated system means a refrigeration system (as defined in this section) that is a single-package assembly that includes one or more compressors, a condenser, a means for forced circulation of refrigerated air, and elements by which heat is transferred from air to refrigerant, without any element external to the system imposing resistance to flow of the refrigerated air.
U-factor means the heat transmission in a unit time through a unit area of a specimen or product and its boundary air films, induced by a unit temperature difference between the environments on each side.
Unit cooler means an assembly, including means for forced air circulation and elements by which heat is transferred from air to refrigerant, thus cooling the air, without any element external to the cooler imposing air resistance.
Walk-in cooler and walk-in freezer means an enclosed storage space including, but not limited to, panels, doors, and refrigeration system, refrigerated to temperatures, respectively, above, and at or below 32 degrees Fahrenheit that can be walked into, and has a total chilled storage area of less than 3,000 square feet; however, the terms do not include products designed and marketed exclusively for medical, scientific, or research purposes.
Walk-in process cooling refrigeration system means a refrigeration system that is capable of rapidly cooling food or other substances from one temperature to another. The basic model of such a system must satisfy one of the following three conditions:
(1) Be distributed in commerce with an insulated enclosure consisting of panels and door(s) such that the assembled product has a refrigerating capacity of at least 100 Btu/h per cubic foot of enclosed internal volume;
(2) Be a unit cooler having an evaporator coil that is at least four-and-one-half (4.5) feet in height and whose height is at least one-and-one-half (1.5) times the width. The height of the evaporator coil is measured perpendicular to the tubes and is also the fin height, while its width is the finned length parallel to the tubes, as illustrated in Figure 1; or
(3) Be a dedicated condensing unit that is distributed in commerce exclusively with a unit cooler meeting description (2) or with an evaporator that is not a unit cooler, i.e., an evaporator that is not distributed or installed as part of a package including one or more fans.
[74 FR 12074, Mar. 23, 2009, as amended at 76 FR 12504, Mar. 7, 2011; 76 FR 21604, Apr. 15, 2011; 76 FR 33631, June 9, 2011; 79 FR 32123, June 3, 2014; 81 FR 95801, Dec. 28, 2016; 88 FR 28838, May 4, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the U.S. Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the sources in the following paragraphs of this section.
(b) AHRI. Air-Conditioning, Heating, and Refrigeration Institute, 2111 Wilson Boulevard, Suite 500, Arlington, VA 22201; (703) 600-0366; www.ahrinet.org.
(1) ANSI/AHRI Standard 420-2008 (“AHRI 420-2008”), Performance Rating of Forced-Circulation Free-Delivery Unit Coolers for Refrigeration, Copyright 2008; IBR approved for appendix C to subpart R.
(2) AHRI Standard 1250P (I-P)-2009 (“AHRI 1250-2009”), Standard for Performance Rating of Walk-in Coolers and Freezers, (including Errata sheet dated December 2015), copyright 2009, except Table 15 and Table 16; IBR approved for appendix C to subpart R.
(3) AHRI Standard 1250 (“AHRI 1250-2020”), Standard for Performance Rating of Walk-in Coolers and Freezers, copyright 2020; IBR approved for appendix C1 to subpart R.
(c) ASHRAE. American Society of Heating, Refrigerating and Air-Conditioning Engineers, 180 Technology Parkway, Peachtree Corners, GA 30092; (404) 636-8400; www.ashrae.org.
(1) ANSI/ASHRAE Standard 16-2016 (“ANSI/ASHRAE 16”), Method of Testing for Rating Room Air Conditioners, Packaged Terminal Air Conditioners, and Packaged Terminal Heat Pumps for Cooling and Heating Capacity, ANSI-approved November 1, 2016; IBR approved for appendix C1 to subpart R.
(2) ANSI/ASHRAE Standard 23.1-2010 (“ASHRAE 23.1-2010”), Methods of Testing for Rating the Performance of Positive Displacement Refrigerant Compressors and Condensing Units that Operate at Subcritical Temperatures of the Refrigerant, ANSI-approved January 28, 2010; IBR approved for appendices C and C1 to subpart R.
(3) ANSI/ASHRAE Standard 37-2009 (“ANSI/ASHRAE 37”), Methods of Testing for Rating Electrically Driven Unitary Air-Conditioning and Heat Pump Equipment, ASHRAE-approved June 24, 2009; IBR approved for appendices C and C1 to subpart R.
(4) ANSI/ASHRAE Standard 41.1-2013 (“ANSI/ASHRAE 41.1”), Standard Method for Temperature Measurement, ANSI-approved January 30, 2013; IBR approved for appendix C1 to subpart R.
(5) ANSI/ASHRAE Standard 41.3-2014 (“ANSI/ASHRAE 41.3”), Standard Methods for Pressure Measurement, ANSI-approved July 3, 2014; IBR approved for appendix C1 to subpart R.
(6) ANSI/ASHRAE Standard 41.6-2014 (“ANSI/ASHRAE 41.6”), Standard Method for Humidity Measurement, ANSI-approved July 3, 2014; IBR approved for appendix C1 to subpart R.
(7) ANSI/ASHRAE Standard 41.10-2013 (“ANSI/ASHRAE 41.10”), Standard Methods for Refrigerant Mass Flow Measurement Using Flowmeters, ANSI-approved June 27, 2013; IBR approved for appendix C1 to subpart R.
(d) ASTM. ASTM, International, 100 Barr Harbor Drive, West Conshohocken, PA 19428-2959; (610) 832-9500; www.astm.org.
(1) ASTM C518-17, Standard Test Method for Steady-State Thermal Transmission Properties by Means of the Heat Flow Meter Apparatus, approved May 1, 2017; IBR approved for appendix B to subpart R.
(2) ASTM C1199-14, Standard Test Method for Measuring the Steady-State Thermal Transmittance of Fenestration Systems Using Hot Box Methods, approved February 1, 2014; IBR approved for appendix A to subpart R.
(e) NFRC. National Fenestration Rating Council, 6305 Ivy Lane, Ste. 140, Greenbelt, MD 20770; (301) 589-1776; www.nfrc.org/.
(1) NFRC 102-2020 [E0A0] (“NFRC 102-2020”), Procedure for Measuring the Steady-State Thermal Transmittance of Fenestration Systems, copyright 2013; IBR approved for appendix A to subpart R.
(2) [Reserved]
[88 FR 28838, May 4, 2023]
(a) Scope. This section provides test procedures for measuring, pursuant to EPCA, the energy consumption of walk-in coolers and walk-in freezers.
(b) Testing and calculations. Determine the energy efficiency and/or energy consumption of the specified walk-in cooler and walk-in freezer components by conducting the appropriate test procedure as follows:
(1) Display panels. Determine the energy use of walk-in cooler and walk-in freezer display panels by conducting the test procedure set forth in appendix A to this subpart.
(2) Display doors and non-display doors. Determine the energy use of walk-in cooler and walk-in freezer display doors and non-display doors by conducting the test procedure set forth in appendix A to this subpart.
(3) Non-display panels and non-display doors. Determine the R-value of insulation of walk-in cooler and walk-in freezer non-display panels and non-display doors by conducting the test procedure set forth in appendix B to this subpart.
(4) Refrigeration systems. Determine the AWEF and net capacity of walk-in cooler and walk-in freezer refrigeration systems by conducting the test procedures set forth in appendix C or C1 to this subpart, as applicable. Refer to the notes at the beginning of those appendices to determine the applicable appendix to use for testing.
(i) For unit coolers: follow the general testing provisions in sections 3.1 and 3.2, and the equipment-specific provisions in section 3.3 of appendix C or sections 4.5 through 4.8 of appendix C1.
(ii) For dedicated condensing units: follow the general testing provisions in sections 3.1 and 3.2, and the product-specific provisions in section 3.4 of appendix C or sections 4.5 through 4.8 of appendix C1.
(iii) For single-packaged dedicated systems: follow the general testing provisions in sections 3.1 and 3.2, and the product-specific provisions in section 3.3 of appendix C or sections 4.5 through 4.8 of appendix C1.
[74 FR 12074, Mar. 23, 2009, as amended at 76 FR 21605, Apr. 15, 2011; 76 FR 33631, June 9, 2011; 76 FR 65365, Oct. 21, 2011; 79 FR 27412, May 13, 2014; 79 FR 32123, June 3, 2014; 81 FR 95802, Dec. 28, 2016; 88 FR 28839, May 4, 2023]
(a) Panel nameplate—
(1) Required information. The permanent nameplate of a walk-in cooler or walk-in freezer panel for which standards are prescribed in § 431.306 must be marked clearly with the following information:
(i) The panel brand or manufacturer; and
(ii) One of the following statements, as appropriate:
(A) “This panel is designed and certified for use in walk-in cooler applications.”
(B) “This panel is designed and certified for use in walk-in freezer applications.”
(C) “This panel is designed and certified for use in walk-in cooler and walk-in freezer applications.”
(2) Display of required information. All orientation, spacing, type sizes, typefaces, and line widths to display this required information must be the same as or similar to the display of the other performance data included on the panel's permanent nameplate. The permanent nameplate must be visible unless the panel is assembled into a completed walk-in.
(b) Door nameplate—
(1) Required information. The permanent nameplate of a walk-in cooler or walk-in freezer door for which standards are prescribed in § 431.306 must be marked clearly with the following information:
(i) The door brand or manufacturer; and
(ii) One of the following statements, as appropriate:
(A) “This door is designed and certified for use in walk-in cooler applications.”
(B) “This door is designed and certified for use in walk-in freezer applications.”
(C) “This door is designed and certified for use in walk-in cooler and walk-in freezer applications.”
(2) Display of required information. All orientation, spacing, type sizes, typefaces, and line widths to display this required information must be the same as or similar to the display of the other performance data included on the door's permanent nameplate. The permanent nameplate must be visible unless the door is assembled into a completed walk-in.
(c) Refrigeration system nameplate—
(1) Required information. The permanent nameplate of a walk-in cooler or walk-in freezer refrigeration system for which standards are prescribed in § 431.306 must be marked clearly with the following information:
(i) The refrigeration system brand or manufacturer;
(ii) The refrigeration system model number;
(iii) The date of manufacture of the refrigeration system (if the date of manufacture is embedded in the unit's serial number, then the manufacturer of the refrigeration system must retain any relevant records to discern the date from the serial number);
(iv) If the refrigeration system is a dedicated condensing refrigeration system, and is not designated for outdoor use, the statement, “Indoor use only” (for a matched pair this must appear on the condensing unit); and
(v) One of the following statements, as appropriate:
(A) “This refrigeration system is designed and certified for use in walk-in cooler applications.”
(B) “This refrigeration system is designed and certified for use in walk-in freezer applications.”
(C) “This refrigeration system is designed and certified for use in walk-in cooler and walk-in freezer applications.”
(2) Process cooling refrigeration systems. The permanent nameplate of a process cooling refrigeration system (as defined in § 431.302) must be marked clearly with the statement, “This refrigeration system is designed for use exclusively in walk-in cooler and walk-in freezer process cooling refrigeration applications.”
(3) Display of required information. All orientation, spacing, type sizes, typefaces, and line widths to display this required information must be the same as or similar to the display of the other performance data included on the refrigeration system's permanent nameplate. The model number must be in one of the following forms: “Model ______” or “Model number ______” or “Model No. ______.” The permanent nameplate must be visible unless the refrigeration system is assembled into a completed walk-in.
(d) A manufacturer may not mark the nameplate of a component with the required information if the manufacturer has not submitted a certification of compliance for the relevant model.
(e) Disclosure of efficiency information in marketing materials. Each catalog that lists the component and all materials used to market the component must include:
(1) For panels—The R-value in the form “R-value____.”
(2) For doors—The energy consumption in the form “EC____kWh/day.”
(3) For those refrigeration system for which standards are prescribed—The AWEF in the form “AWEF ____.”
(4) The information that must appear on a walk-in cooler or walk-in freezer component's permanent nameplate pursuant to paragraphs (a)-(c) of this section must also be prominently displayed in each catalog that lists the component and all materials used to market the component.
[81 FR 95802, Dec. 28, 2016, as amended at 89 FR 82071, Oct. 9, 2024; 90 FR 43384, Sept. 9, 2025]
(a) Each walk-in cooler or walk-in freezer manufactured on or after January 1, 2009, shall—
(1) Have automatic door closers that firmly close all walk-in doors that have been closed to within 1 inch of full closure, except that this paragraph shall not apply to doors wider than 3 feet 9 inches or taller than 7 feet;
(2) Have strip doors, spring hinged doors, or other method of minimizing infiltration when doors are open;
(3) Contain wall, ceiling, and door insulation of at least R-25 for coolers and R-32 for freezers, except that this paragraph shall not apply to:
(i) Glazed portions of doors not to structural members and
(ii) A walk-in cooler or walk-in freezer component if the component manufacturer has demonstrated to the satisfaction of the Secretary in a manner consistent with applicable requirements that the component reduces energy consumption at least as much as if such insulation requirements of subparagraph (a)(3) were to apply.
(4) Contain floor insulation of at least R-28 for freezers;
(5) For evaporator fan motors of under 1 horsepower and less than 460 volts, use—
(i) Electronically commutated motors (brushless direct current motors); or
(ii) 3-phase motors;
(6) For condenser fan motors of under 1 horsepower, use—
(i) Electronically commutated motors (brushless direct current motors);
(ii) Permanent split capacitor-type motors; or
(iii) 3-phase motors; and
(7) For all interior lights, use light sources with an efficacy of 40 lumens per watt or more, including ballast losses (if any), except that light sources with an efficacy of 40 lumens per watt or less, including ballast losses (if any), may be used in conjunction with a timer or device that turns off the lights within 15 minutes of when the walk-in cooler or walk-in freezer is not occupied by people.
(b) Each walk-in cooler or walk-in freezer with transparent reach-in doors manufactured on or after January 1, 2009, shall also meet the following specifications:
(1) Transparent reach-in doors for walk-in freezers and windows in walk-in freezer doors shall be of triple-pane glass with either heat-reflective treated glass or gas fill.
(2) Transparent reach-in doors for walk-in coolers and windows in walk-in cooler doors shall be—
(i) Double-pane glass with heat-reflective treated glass and gas fill; or
(ii) Triple-pane glass with either heat-reflective treated glass or gas fill.
(3) If the walk-in cooler or walk-in freezer has an antisweat heater without antisweat heat controls, the walk-in cooler and walk-in freezer shall have a total door rail, glass, and frame heater power draw of not more than 7.1 watts per square foot of door opening (for freezers) and 3.0 watts per square foot of door opening (for coolers).
(4) If the walk-in cooler or walk-in freezer has an antisweat heater with antisweat heat controls, and the total door rail, glass, and frame heater power draw is more than 7.1 watts per square foot of door opening (for freezers) and 3.0 watts per square foot of door opening (for coolers), the antisweat heat controls shall reduce the energy use of the antisweat heater in a quantity corresponding to the relative humidity in the air outside the door or to the condensation on the inner glass pane.
(c) Walk-in cooler and freezer display doors. All walk-in cooler and walk-in freezer display doors manufactured starting June 5, 2017, must satisfy the following standards:
| Class descriptor | Class | Equations for maximum energy consumption (kWh/day) * |
|---|---|---|
| Display Door, Medium Temperature | DD.M | 0.04 × Add + 0.41. |
| Display Door, Low Temperature | DD.L | 0.15 × Add + 0.29. |
| *Add represents the surface area of the display door. | ||
(d) Walk-in cooler and freezer non-display doors. All walk-in cooler and walk-in freezer non-display doors manufactured starting on June 5, 2017, must satisfy the following standards:
| Class descriptor | Class | Equations for maximum energy consumption (kWh/day) * |
|---|---|---|
| Passage door, Medium Temperature | PD.M | 0.05 × And + 1.7. |
| Passage Door, Low Temperature | PD.L | 0.14 × And + 4.8. |
| Freight Door, Medium Temperature | FD.M | 0.04 × And + 1.9. |
| Freight Door, Low Temperature | FD.L | 0.12 × And + 5.6. |
| *And represents the surface area of the non-display door. | ||
(e) Walk-in cooler refrigeration systems. All walk-in cooler and walk-in freezer refrigeration systems manufactured starting on the dates listed in the table, except for walk-in process cooling refrigeration systems (as defined in § 431.302), must satisfy the following standards:
| Equipment class | Minimum AWEF (Btu/W-h)* |
Compliance date: equipment manufactured starting on . . . |
|---|---|---|
| Dedicated Condensing System—Medium, Indoor | 5.61 | June 5, 2017. |
| Dedicated Condensing System—Medium, Outdoor | 7.60 | |
| Dedicated Condensing System—Low, Indoor with a Net Capacity (qnet) of: | ||
| < 6,500 Btu/h | 9.091 × 10 −5 × qnet + 1.81 | July 10, 2020. |
| ≥ 6,500 Btu/h | 2.40 | |
| Dedicated Condensing System—Low, Outdoor with a Net Capacity (qnet) of: | ||
| < 6,500 Btu/h | 6.522 × 10−5 × qnet + 2.73 | |
| ≥ 6,500 Btu/h | 3.15 | |
| Unit Cooler—Medium | 9.00 | |
| Unit Cooler—Low with a Net Capacity (qnet) of: | ||
| < 15,500 Btu/h | 1.575 × 10 −5 × qnet + 3.91 | |
| ≥ 15,500 Btu/h | 4.15 | |
| * Where qnet is net capacity as determined in accordance with § 431.304 and certified in accordance with 10 CFR part 429. | ||
[74 FR 12074, Mar. 23, 2009, as amended at 78 FR 62993, Oct. 23, 2013; 79 FR 32123, June 3, 2014; 80 FR 69838, Nov. 12, 2015; 82 FR 31885, July 10, 2017]
Prior to October 31, 2023, representations with respect to the energy use of envelope components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with the applicable provisions of 10 CFR part 431, subpart R, appendix A, revised as of January 1, 2022. Beginning October 31, 2023, representations with respect to energy use of envelope components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.303 the entire standard for ASTM C1199-14 and NFRC 102-2020. However, certain enumerated provisions of these standards, as set forth in sections 0.1 and 0.2 of this appendix are inapplicable. To the extent that there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
0.1 ASTM C1199-14
(a) Section 1 Scope, is inapplicable,
(b) Section 4 Significance and Use is inapplicable,
(c) Section 7.3 Test Conditions, is inapplicable,
(d) Section 10 Report, is inapplicable, and
(e) Section 11 Precision and Bias, is inapplicable.
0.2 NFRC 102-2020
(a) Section 1 Scope, is inapplicable,
(b) Section 4 Significance and Use, is inapplicable,
(c) Section 7.3 Test Conditions, is inapplicable,
(d) Section 10 Report, is inapplicable,
(e) Section 11 Precision and Bias, is inapplicable,
(f) Annex A3 Standard Test Method for Determining the Thermal Transmittance of Tubular Daylighting Devices, is inapplicable, and
(g) Annex A5 Tables and Figures, is inapplicable.
1. General. The following sections of this appendix provide additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by NFRC 102-2020, followed by ASTM C1199-14. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE. Material is incorporated as it exists on the date of the approval, and a notification of any change in the incorporation will be published in the Federal Register.
2. Scope
This appendix covers the test requirements used to measure the energy consumption of the components that make up the envelope of a walk-in cooler or walk-in freezer.
3. Definitions
The definitions contained in § 431.302 are applicable to this appendix.
4. Additional Definitions
4.1 Automatic door opener/closer means a device or control system that “automatically” opens and closes doors without direct user contact, such as a motion sensor that senses when a forklift is approaching the entrance to a door and opens it, and then closes the door after the forklift has passed.
4.2 Percent time off (PTO) means the percent of time that an electrical device is assumed to be off.
4.3 Rated power means the input power of an electricity-consuming device as specified on the device's nameplate. If the device does not have a nameplate or such nameplate does not list the device's input power, then the rated power must be determined from the device's product data sheet, literature, or installation instructions that come with the device or are available online.
4.4 Rating conditions means, unless explicitly stated otherwise, all conditions shown in table A.1 of this appendix.
| Internal Temperatures (cooled space within the envelope) | |
| Cooler Dry-Bulb Temperature | 35 °F |
| Freezer Dry-Bulb Temperature | −10 °F |
| External Temperatures (space external to the envelope) | |
| Freezer and Cooler Dry-Bulb Temperatures | 75 °F |
5. Test Methods and Measurements
5.1 U-Factor Test of Doors and Display Panels
Determine the U-factor of the entire door or display panel, including the frame, in accordance with the specified sections of NFRC 102-2020 and ASTM C1199-14 at the temperature conditions listed in table A.1 of this appendix.
5.2 Required Test Measurements
5.2.1 For display doors and display panels, thermal transmittance, Udd or Udp, respectively, shall be the standardized thermal transmittance, UST, determined per section 5.1 of this appendix.
5.2.2 For non-display doors, thermal transmittance, Und, shall be the standardized thermal transmittance, UST, determined per section 5.1 of this appendix.
5.2.3 Projected area of the test specimen, As, in ft2, as referenced in ASTM C1199-14.
6. Calculations
6.1 Display Panels
6.1.1 Determine the U-factor of the display panel in accordance with section 5.1 of this appendix, in units of Btu/(h-ft2- °F).
6.1.2 Calculate the temperature differential, ΔTdp, °F, for the display panel, as follows:
Where:
TDB,ext,dp = dry-bulb air external temperature, °F, as prescribed in table A.1 of this appendix; and
TDB,int,dp = dry-bulb air temperature internal to the cooler or freezer, °F, as prescribed in table A.1 of this appendix.
6.1.3 Calculate the conduction load through the display panel, Qcond-dp, Btu/h, as follows:
Where:
As = projected area of the test specimen (same as the test specimen aperture in the surround panel) or the area used to determine the U-factor in section 5.1 of this appendix, ft2;
ΔTdp = temperature differential between refrigerated and adjacent zones, °F; and
Udp = thermal transmittance, U-factor, of the display panel in accordance with section 5.1 of this appendix, Btu/(h-ft2- °F).
6.1.4 Calculate the total daily energy consumption, Edp, kWh/day, as follows:
Where:
Qcond,dp = the conduction load through the display panel, Btu/h; and
EER = Energy Efficiency Ratio of walk-in (cooler or freezer), Btu/W-h. For coolers, use EER = 12.4 Btu/W-h. For freezers, use EER = 6.3 Btu/W-h.
6.2 Display Doors
6.2.1 Conduction Through Display Doors
6.2.1.1 Determine the U-factor of the display door in accordance with section 5.1 of this appendix, in units of Btu/(h-ft2- °F).
6.2.1.2 Calculate the temperature differential, ΔTdd, °F, for the display door as follows:
Where:
TDB,ext,dd = dry-bulb air temperature external to the display door, °F, as prescribed in table A.1 of this appendix; and
TDB,int,dd = dry-bulb air temperature internal to the display door, °F, as prescribed in table A.1 of this appendix.
6.2.1.3 Calculate the conduction load through the display doors, Qcond,dd, Btu/h, as follows:
Where:
As = projected area of the test specimen (same as the test specimen aperture in the surround panel) or the area used to determine the U-factor in section 5.1 of this appendix, ft2;
ΔTdd = temperature differential between refrigerated and adjacent zones, °F; and
Udd = thermal transmittance, U-factor of the door, in accordance with section 5.1 of this appendix, Btu/(h-ft2- °F).
6.2.1.4 Calculate the total daily energy consumption due to conduction thermal load, Edd,thermal, kWh/day, as follows:
Where:
Qcond,dd = the conduction load through the display door, Btu/h; and
EER = EER of walk-in (cooler or freezer), Btu/W-h. For coolers, use EER = 12.4 Btu/(W-h). For freezers, use EER = 6.3 Btu/(W-h).
6.2.2 Direct Energy Consumption of Electrical Component(s) of Display Doors
Electrical components associated with display doors could include but are not limited to: heater wire (for anti-sweat or anti-freeze application); lights; door motors; control system units; and sensors.
6.2.2.1 Select the required value for percent time off (PTO) for each type of electricity-consuming device per table A.2 of this appendix, PTOt (%).
| Device | Temperature
condition |
Controls, timer, or other auto-shut-off system | Percent time
off value (%) |
|---|---|---|---|
| Lights | All | Without
With |
25
50 |
| Anti-sweat heaters | All
Coolers Freezers |
Without
With With |
0
75 50 |
| Door motors | All | 97 | |
| All other electricity-consuming devices | All | Without
With |
0
25 |
6.2.2.2 Calculate the power usage for each type of electricity-consuming device, Pdd,comp,u,t, kWh/day, as follows:
Where:
u = the index for each of type of electricity-consuming device located on either (1) the interior facing side of the display door or within the inside portion of the display door, (2) the exterior facing side of the display door, or (3) any combination of (1) and (2). For purposes of this calculation, the interior index is represented by u = int and the exterior index is represented by u = ext. If the electrical component is both on the interior and exterior side of the display door then use u = int. For anti-sweat heaters sited anywhere in the display door, 75 percent of the total power is be attributed to u = int and 25 percent of the total power is attributed to u = ext;
t = index for each type of electricity-consuming device with identical rated power;
Prated,u,t = rated input power of each component, of type t, kW;
PTOu,t = percent time off, for device of type t, %; and
nu,t = number of devices at the rated input power of type t, unitless.
6.2.2.3 Calculate the total electrical energy consumption for interior and exterior power, Pdd,tot,int (kWh/day) and Pdd,tot,ext (kWh/day), respectively, as follows:
Where:
t = index for each type of electricity-consuming device with identical rated input power;
Pdd,comp,int,t = the energy usage for an electricity-consuming device sited on the interior facing side of or in the display door, of type t, kWh/day; and
Pdd,comp,ext,t = the energy usage for an electricity-consuming device sited on the external facing side of the display door, of type t, kWh/day.
6.2.2.4 Calculate the total electrical energy consumption, Pdd,tot, (kWh/day), as follows:
Where:
Pdd,tot,int = the total interior electrical energy usage for the display door, kWh/day; and
Pdd,tot,ext = the total exterior electrical energy usage for the display door, kWh/day.
6.2.3 Total Indirect Electricity Consumption Due to Electrical Devices
Calculate the additional refrigeration energy consumption due to thermal output from electrical components sited inside the display door, Cdd,load, kWh/day, as follows:
Where:
Pdd,tot,int = The total internal electrical energy consumption due for the display door, kWh/day; and
EER = EER of walk-in cooler or walk-in freezer, Btu/W-h. For coolers, use EER = 12.4 Btu/(W-h). For freezers, use EER = 6.3 Btu/(W-h).
6.2.4 Total Display Door Energy Consumption
Calculate the total energy, Edd,tot, kWh/day,
Where:
Edd,thermal = the total daily energy consumption due to thermal load for the display door, kWh/day;
Pdd,tot = the total electrical load, kWh/day; and
Cdd,load = additional refrigeration load due to thermal output from electrical components contained within the display door, kWh/day.
6.3 Non-Display Doors
6.3.1 Conduction Through Non-Display Doors
6.3.1.1 Determine the U-factor of the non-display door in accordance with section 5.1 of this appendix, in units of Btu/(h-ft2- °F).
6.3.1.2 Calculate the temperature differential of the non-display door, ΔTnd, °F, as follows:
Where:
TDB,ext,nd = dry-bulb air external temperature, °F, as prescribed by table A.1 of this appendix; and
TDB,int,nd = dry-bulb air internal temperature, °F, as prescribed by table A.1 of this appendix. If the component spans both cooler and freezer spaces, the freezer temperature must be used.
6.3.1.3 Calculate the conduction load through the non-display door: Qcond,nd, Btu/h,
Where:
As = projected area of the test specimen (same as the test specimen aperture in the surround panel) or the area used to determine the U-factor in section 5.1 of this appendix, ft2;
ΔTnd = temperature differential across the non-display door, °F; and
Und = thermal transmittance, U-factor of the door, in accordance with section 5.1 of this appendix, Btu/(h-ft2- °F).
6.3.1.4 Calculate the total daily energy consumption due to thermal load, End,thermal, kWh/day, as follows:
Where:
Qcond,nd = the conduction load through the non-display door, Btu/h; and
EER = EER of walk-in (cooler or freezer), Btu/W-h. For coolers, use EER = 12.4 Btu/(W-h). For freezers, use EER = 6.3 Btu/(W-h).
6.3.2 Direct Energy Consumption of Electrical Components of Non-Display Doors
Electrical components associated with non-display doors comprise could include, but are not limited to: heater wire (for anti-sweat or anti-freeze application), lights, door motors, control system units, and sensors.
6.3.2.1 Select the required value for percent time off for each type of electricity-consuming device per table A.2 of this appendix, PTOt (%).
6.3.2.2 Calculate the power usage for each type of electricity-consuming device, Pnd,comp,u,t, kWh/day, as follows:
Where:
u = the index for each of type of electricity-consuming device located on either (1) the interior facing side of the non-display door or within the inside portion of the non-display door, (2) the exterior facing side of the non-display door, or (3) any combination of (1) and (2). For purposes of this calculation, the interior index is represented by u = int and the exterior index is represented by u = ext. If the electrical component is both on the interior and exterior side of the non-display door then use u = int. For anti-sweat heaters sited anywhere in the non-display door, 75 percent of the total power is be attributed to u = int and 25 percent of the total power is attributed to u = ext;
t = index for each type of electricity-consuming device with identical rated input power;
Prated,u,t = rated input power of each component, of type t, kW;
PTOu,t = percent time off, for device of type t, %; and
nu,t = number of devices at the rated input power of type t, unitless.
6.3.2.3 Calculate the total electrical energy consumption for interior and exterior power, Pnd,tot,int, kWh/day, and Pnd,tot,ext, kWh/day, respectively, as follows:
Where:
t = index for each type of electricity-consuming device with identical rated input power;
Pnd,comp,int,t = the energy usage for an electricity-consuming device sited on the internal facing side or internal to the non-display door, of type t, kWh/day; and
Pnd,comp,ext,t = the energy usage for an electricity-consuming device sited on the external facing side of the non-display door, of type t, kWh/day. For anti-sweat heaters,
6.3.2.4 Calculate the total electrical energy consumption, Pnd,tot, kWh/day, as follows:
Where:
Pnd,tot,int = the total interior electrical energy usage for the non-display door, of type t, kWh/day; and
Pnd,tot,ext = the total exterior electrical energy usage for the non-display door, of type t, kWh/day.
6.3.3 Total Indirect Electricity Consumption Due to Electrical Devices
Calculate the additional refrigeration energy consumption due to thermal output from electrical components associated with the non-display door, Cnd,load, kWh/day, as follows:
Where:
Pnd,tot,int = the total interior electrical energy consumption for the non-display door, kWh/day; and
EER = EER of walk-in cooler or freezer, Btu/W-h. For coolers, use EER = 12.4 Btu/(W-h). For freezers, use EER = 6.3 Btu/(W-h).
6.3.4 Total Non-Display Door Energy Consumption
Calculate the total energy, End,tot, kWh/day, as follows:
Where:
End,thermal = the total daily energy consumption due to thermal load for the non-display door, kWh/day;
Pnd,tot = the total electrical energy consumption, kWh/day; and
Cnd,load = additional refrigeration load due to thermal output from electrical components contained on the inside face of the non-display door, kWh/day.
[88 FR 28839, May 4, 2023, as amended at 88 FR 73216, Oct. 25, 2023]
Prior to October 31, 2023, representations with respect to the R-value for insulation of envelope components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with the applicable provisions of 10 CFR part 431, subpart R, appendix B, revised as of January 1, 2022. Beginning October 31, 2023, representations with respect to R-value for insulation of envelope components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.303 the entire standard for ASTM C518-17. However, certain enumerated provisions of ASTM C518-17, as set forth in paragraph 0.1 of this appendix, are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
0.1 ASTM C518-17
(a) Section 1 Scope, is inapplicable,
(b) Section 4 Significance and Use, is inapplicable,
(c) Section 7.3 Specimen Conditioning, is inapplicable,
(d) Section 9 Report, is inapplicable,
(e) Section 10 Precision and Bias, is inapplicable,
(f) Section 11 Keywords, is inapplicable,
(g) Annex A2 Equipment Error Analysis, is inapplicable,
(h) Appendix X1 is inapplicable,
(i) Appendix X2 Response of Heat Flux Transducers, is inapplicable, and
(j) Appendix X3 Proven Performance of a Heat Flow Apparatus, is inapplicable.
0.2 [Reserved]
1. General
The following sections of this appendix provide additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by ASTM C518-17. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE. Material is incorporated as it exists on the date of the approval, and a notification of any change in the incorporation will be published in the Federal Register.
2. Scope
This appendix covers the test requirements used to measure the R-value of non-display panels and non-display doors of a walk-in cooler or walk-in freezer.
3. Definitions
The definitions contained in § 431.302 apply to this appendix.
4. Additional Definitions
4.1 Edge region means a region of the envelope component that is wide enough to encompass any framing members. If the envelope component contains framing members (e.g., a wood frame) then the width of the edge region must be as wide as any framing member plus an additional 2 in. ± 0.25 in.
5. Test Methods, Measurements, and Calculations
5.1 General. Foam shall be tested after it is produced in its final chemical form. For foam produced inside of an envelope component (“foam-in-place”), “final chemical form” means the foam is cured as intended and ready for use as a finished envelope component. For foam produced as board stock (e.g., polystyrene), “final chemical form” means after extrusion and ready for assembly into an envelope component or after assembly into an envelope component. Foam must not include any structural members or non-foam materials during testing in accordance with ASTM C518-17. When preparing the specimen for test, a high-speed bandsaw or a meat slicer are two types of recommended cutting tools. Hot wire cutters or other heated tools shall not be used for cutting foam test specimens.
5.2 Specimen Preparation
5.2.1 Determining the thickness around the perimeter of the envelope component, tp. The full thickness of an envelope component around the perimeter, which may include facers on one or both sides, shall be determined as follows:
5.2.1.1 At least 8 thickness measurements shall be taken around the perimeter of the envelope component, at least 2 inches from the edge region, and avoiding any regions with hardware or fixtures.
5.2.1.2 The average of the thickness measurements taken around the perimeter of the envelope component shall be the thickness around the perimeter of the envelope component, tp.
5.2.1.3 Measure and record the width, wp, and height, hp, of the envelope component. The surface area of the envelope component, Ap, shall be determined as follows:
Where:
wp = width of the envelope component, in.; and
hp = height of the envelope component, in.
5.2.2. Removing the sample from the envelope component.
5.2.2.1. Determine the center of the envelope component relative to its height and its width.
5.2.2.2. Cut a sample from the envelope component that is at least the length and width dimensions of the heat flow meter, and where the marked center of the sample is at least 3 inches from any cut edge.
5.2.2.3. If the center of the envelope component contains any non-foam components (excluding facers), additional samples may be cut adjacent to the previous cut that is at least the length and width dimensions of the heat flow meter and is greater than 12 inches from the edge region.
5.2.3. Determining the thickness at the center of the envelope component, tc. The full thickness of an envelope component at the center, which may include facers on one or both sides, shall be determined as follows:
5.2.3.1. At least 2 thickness measurements shall be taken in each quadrant of the cut sample removed from the envelope component per section 5.2.2 of this appendix, for a total of at least 8 measurements.
5.2.3.2. The average of the thickness measurements of the cut sample removed from the envelope component shall be the overall thickness of the cut sample, tc.
5.2.3.3. Measure and record the width and height of the cut sample removed from the envelope component. The surface area of the cut sample removed from the envelope component, Ac., shall be determined as follows:
Where:
wc = width of the cut sample removed from the envelope component, in.; and
hc = height of the cut sample removed from the envelope component, in.
5.2.4. Determining the total thickness of the foam within the envelope component, tfoam. The average total thickness of the foam sample, without facers, shall be determined as follows:
5.2.4.1. Remove the facers on the envelope component sample, while minimally disturbing the foam.
5.2.4.2. Measure the thickness of each facer in 4 locations for a total of 4 measurements if 1 facer is removed, and a total of 8 measurements if 2 facers are removed. The average of all facer measurements shall be the thickness of the facers, tfacers, in.
5.2.4.3. The average total thickness of the foam, tfoam, in., shall be determined as follows:
Where:
tc = the average thickness of the center of the envelope component, in., as determined per sections 5.2.3.1 and 5.2.3.2 of this appendix;
Ac = the surface area of the center of the envelope component, in2., as determined per section 5.2.3.3 of this appendix;
tp = the average thickness of the perimeter of the envelope component, in., as determined per sections 5.2.1.1 and 5.2.1.2 of this appendix;
Ap = the average thickness of the center of the envelope component, in2, as determined per section 5.2.1.3 of this appendix;
tfacers = the average thickness of the facers of the envelope component, in., as determined per section 5.2.4.2 of this appendix.
5.2.5. Cutting, measuring, and determining parallelism and flatness of a 1-inch-thick specimen for test from the center of the cut envelope component sample.
5.2.5.1. Cut a 1 ± 0.1-inch-thick specimen from the center of the cut envelope sample. The 1-inch-thick test specimen shall be cut from the point that is equidistant from both edges of the sample (i.e., shall be cut from the center point that would be directly between the interior and exterior space of the walk-in).
5.2.5.2. Document through measurement or photographs with measurement indicators that the specimen was taken from the center of the sample.
5.2.5.3 After the 1-inch specimen has been cut, and prior to testing, place the specimen on a flat surface and allow gravity to determine the specimen's position on the surface. This will be side 1.
5.2.5.4 To determine the flatness of side 1, take at least nine height measurements at equidistant positions on the specimen (i.e., the specimen would be divided into 9 regions and height measurements taken at the center of each of these nine regions). Contact with the measurement indicator shall not indent the foam surface. From the height measurements taken, determine the least squares plane for side 1. For each measurement location, calculate the theoretical height from the least squares plane for side 1. Then, calculate the difference between the measured height and the theoretical least squares plane height at each location. The maximum difference minus the minimum difference out of the nine measurement locations is the flatness of side 1. For side 1 of the specimen to be considered flat, this shall be less than or equal to 0.03 inches.
5.2.5.5 To determine the flatness of side 2, turn the specimen over and allow gravity to determine the specimen's position on the surface. Repeat section 5.2.5.4 to determine the flatness of side 2.
5.2.5.6 To determine the parallelism of the specimen for side 1, calculate the theoretical height of the least squares plane at the furthest corners (i.e., at points (0,0), (0,12), (12,0), and (12,12)) of the 12-inch by 12-inch test specimen. The difference between the maximum theoretical height and the minimum theoretical height shall be less than or equal to 0.03 inches for each side in order for side 1 to be considered parallel.
5.2.5.7 To determine the parallelism of the specimen for side 2, repeat section 5.2.5.6 of this appendix.
5.2.5.8 The average thickness of the test specimen, L, shall be 1 ± 0.1-inches determined using a minimum of 18 thickness measurements (i.e., a minimum of 9 measurements on side 1 of the specimen and a minimum of 9 on side 2 of the specimen). This average thickness shall be used to determine the thermal conductivity, or K-factor.
5.3 K-factor Test. Determine the thermal conductivity, or K-factor, of the 1-inch-thick specimen in accordance with the specified sections of ASTM C518-17. Testing must be completed within 24 hours of the specimen being cut for testing per section 5.2.5 of this appendix.
5.3.1 Test Conditions.
5.3.1.1 For freezer envelope components, the K-factor of the specimen shall be determined at an average specimen temperature of 20 ± 1 degrees Fahrenheit.
5.3.1.2 For cooler envelope components, the K-factor of the specimen shall be determined at an average specimen temperature of 55 ± 1 degrees Fahrenheit.
5.4 R-value Calculation.
5.4.1 For envelope components consisting of one homogeneous layer of insulation, calculate the R-value, h-ft2- °F/Btu, as follows:
Where:
tfoam = the total thickness of the foam, in., as determined in section 5.2.4 of this appendix; and
λ = K-factor, Btu-in/(h-ft2- °F), as determined in section 5.3 of this appendix.
5.4.2 For envelope components consisting of two or more layers of dissimilar insulating materials (excluding facers or protective skins), determine the K-factor of each material as described in sections 5.1 through 5.3 of this appendix. For an envelope component with N layers of insulating material, the overall R-value shall be calculated as follows:
Where:
ti is the thickness of the ith material that appears in the envelope component, inches, as determined in section 5.2.4 of this appendix;
λi is the k-factor of the ith material, Btu-in/(h-ft2- °F), as determined in section 5.3 of this appendix; and
N is the total number of material layers that appears in the envelope component.
5.4.3 K-factor test results from a test sample 1 ± 0.1-inches in thickness may be used to determine the R-value of envelope components with various foam thicknesses as long as the foam throughout the panel depth is of the same final chemical form and the test was completed at the same test conditions that the other envelope components would be used at. For example, a K-factor test result conducted at cooler conditions cannot be used to determine R-value of a freezer envelope component.
[88 FR 28843, May 4, 2023, as amended at 88 FR 73217, Oct. 25, 2023]
Prior to October 31, 2023, representations with respect to the energy use of refrigeration components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with the applicable provisions of 10 CFR part 431, subpart R, appendix C, revised as of January 1, 2022. Beginning October 31, 2023, representations with respect to energy use of refrigeration components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with this appendix.
For any amended standards for walk-in coolers and freezers published after January 1, 2022, manufacturers must use the results of testing under appendix C1 to this subpart to determine compliance. Representations related to energy consumption must be made in accordance with appendix C1 when determining compliance with the relevant standard. Manufacturers may also use appendix C1 to certify compliance with any amended standards prior to the applicable compliance date for those standards.
1.0 Scope
This appendix covers the test requirements used to determine the net capacity and the AWEF of the refrigeration system of a walk-in cooler or walk-in freezer.
2.0 Definitions
The definitions contained in § 431.302 and AHRI 1250-2009 (incorporated by reference; see § 431.303) apply to this appendix. When definitions contained in the standards DOE has incorporated by reference are in conflict or when they conflict with this section, the hierarchy of precedence shall be in the following order: § 431.302, AHRI 1250-2009, and then either AHRI 420-2008 (incorporated by reference; see § 431.303) for unit coolers or ASHRAE 23.1-2010 (incorporated by reference; see § 431.303) for dedicated condensing units.
The term “unit cooler” used in AHRI 1250-2009, AHRI 420-2008, and this subpart shall be considered to address both “unit coolers” and “ducted fan coil units,” as appropriate.
3.0 Test Methods, Measurements, and Calculations
Determine the Annual Walk-in Energy Factor (AWEF) and net capacity of walk-in cooler and walk-in freezer refrigeration systems by conducting the test procedure set forth in AHRI 1250-2009 (incorporated by reference; see § 431.303), with the modifications to that test procedure provided in this section. When standards that are incorporated by reference are in conflict or when they conflict with this section, the hierarchy of precedence shall be in the following order: § 431.302, AHRI 1250-2009, and then either AHRI 420-2008 (incorporated by reference; see § 431.303) or ASHRAE 23.1-2010 (incorporated by reference; see § 431.303).
3.1. General modifications: Test Conditions and Tolerances.
When conducting testing in accordance with AHRI 1250-2009 (incorporated by reference; see § 431.303), the following modifications must be made.
3.1.1. In Table 1, Instrumentation Accuracy, refrigerant temperature measurements shall have an accuracy of ±0.5 °F for unit cooler in/out. When testing high-temperature refrigeration systems, measurements used to determine temperature or water vapor content of the air (i.e., wet-bulb or dew point) shall be accurate to within ±0.25 °F; all other temperature measurements shall be accurate to within ±1.0 °F.
3.1.2. In Table 2, Test Operating and Test Condition Tolerances for Steady-State Test, electrical power frequency shall have a Test Condition Tolerance of 1 percent.
3.1.3. In Table 2, the Test Operating Tolerances and Test Condition Tolerances for Air Leaving Temperatures shall be deleted.
3.1.4. In Tables 2 through 14, the Test Condition Outdoor Wet Bulb Temperature requirement and its associated tolerance apply only to units with evaporative cooling.
3.1.5. Tables 15 and 16 shall be modified to read as follows:
| Test description |
Unit cooler air entering dry-bulb, °F |
Unit cooler air entering relative humidity, % |
Saturated suction temp, °F |
Liquid inlet saturation temp, °F | Liquid inlet subcooling temp, °F | Compressor capacity |
Test objective |
|---|---|---|---|---|---|---|---|
| Off Cycle Fan Power | 35 | <50 | — | — | — | Compressor Off | Measure fan input power during compressor off cycle. |
| Refrigeration Capacity Suction A | 35 | <50 | 25 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Refrigeration Capacity Suction B | 35 | <50 | 20 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Note: Superheat to be set according to equipment specification in equipment or installation manual. If no superheat specification is given, a default superheat value of 6.5 °F shall be used. The superheat setting used in the test shall be reported as part of the standard rating. | |||||||
| Test description |
Unit cooler air entering dry-bulb, °F |
Unit cooler air entering relative humidity, % |
Saturated suction temp, °F |
Liquid inlet saturation temp, °F | Liquid inlet subcooling temp, °F | Compressor capacity |
Test objective |
|---|---|---|---|---|---|---|---|
| Off Cycle Fan Power | −10 | <50 | — | — | — | Compressor Off | Measure fan input power during compressor off cycle. |
| Refrigeration Capacity Suction A | −10 | <50 | −20 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Refrigeration Capacity Suction B | −10 | <50 | −26 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Defrost | −10 | Various | — | — | — | Compressor Off | Test according to Appendix C Section C11. |
| Note: Superheat to be set according to equipment specification in equipment or installation manual. If no superheat specification is given, a default superheat value of 6.5 °F shall be used. The superheat setting used in the test shall be reported as part of the standard rating. | |||||||
3.1.6. Test Operating Conditions for CO2 Unit Coolers
For medium-temperature CO2 unit coolers, conduct tests using the test conditions specified in table C.1 of this appendix. For low-temperature CO2 unit coolers, conduct tests using the test conditions specified in table C.2 of this appendix.
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Suction
dew point temp, °F |
Liquid
inlet bubble point temperature °F |
Liquid
inlet subcooling, °F |
Compressor
capacity |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle Power | 35 | <50 | Compressor Off | Measure fan input power during compressor off-cycle. | |||
| Refrigeration Capacity, Ambient Condition A | 35 | <50 | 25 | 38 | 5 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Notes: | |||||||
| 1 Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
| Test description | Unit
cooler air entering dry-bulb, °F |
Unit
cooler air entering relative humidity, % |
Suction
dew point temp, °F |
Liquid inlet bubble point temperature
°F |
Liquid
inlet subcooling, °F |
Compressor
capacity |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle Power | −10 | <50 | Compressor Off | Measure fan input power during compressor off cycle. | |||
| Refrigeration Capacity, Ambient Condition A | −10 | <50 | −20 | 38 | 5 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Defrost | −10 | <50 | Compressor Off | Test according to Appendix C Section C11 of AHRI 1250-2009. | |||
| 1. Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
3.1.7. Test Operating Conditions for High-Temperature Unit Coolers
For high-temperature cooler unit coolers, conduct tests using the test conditions specified in table C.3 of this appendix.
| Test description | Unit
cooler air entering dry-bulb, °F |
Unit
cooler air entering relative humidity, % 1 |
Suction
dew point temp, °F 2 3 |
Liquid inlet bubble point temperature
°F |
Liquid
inlet subcooling, °F |
Compressor
capacity |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle | 55 | 55 | 105 | 9 | Compressor Off | Measure fan input power. | |
| Refrigeration Capacity Suction A | 55 | 55 | 38 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler. |
| Notes: | |||||||
| 1 The test condition tolerance (maximum permissible variation of the average value of the measurement from the specified test condition) for relative humidity is 3%. | |||||||
| 2 Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
| 3 Suction Dew Point shall be measured at the Unit Cooler Exit. | |||||||
3.2. General Modifications: Methods of Testing
When conducting testing in accordance with appendix C of AHRI 1250-2009 (incorporated by reference; see § 431.303), the following modifications must be made.
3.2.1. Refrigerant Temperature Measurements
In AHRI 1250-2009 appendix C, section C3.1.6, any refrigerant temperature measurements entering and leaving the unit cooler may use sheathed sensors immersed in the flowing refrigerant instead of thermometer wells. When testing a condensing unit alone, measure refrigerant liquid temperature leaving the condensing unit using thermometer wells as described in AHRI 1250-2009 appendix C, section C3.1.6 or sheathed sensors immersed in the flowing refrigerant. For all of these cases, if the refrigerant tube outer diameter is less than 1⁄2 inch, the refrigerant temperature may be measured using the average of two temperature measuring instruments with a minimum accuracy of ±0.5 °F placed on opposite sides of the refrigerant tube surface—resulting in a total of up to 8 temperature measurement devices used for the DX Dual Instrumentation method. In this case, the refrigerant tube shall be insulated with 1-inch thick insulation from a point 6 inches upstream of the measurement location to a point 6 inches downstream of the measurement location. Also, to comply with this requirement, the unit cooler entering measurement location may be moved to a location 6 inches upstream of the expansion device and, when testing a condensing unit alone, the entering and leaving measurement locations may be moved to locations 6 inches from the respective service valves.
3.2.2. It is not necessary to perform composition analysis of refrigerant (appendix C, section C3.3.6) or refrigerant oil concentration testing (appendix C, section C3.4.6).
3.2.3. Subcooling at Refrigerant Mass Flow Meter
In appendix C, section C3.4.5 of AHRI 1250-2009 (incorporated by reference; see § 431.303), and in section 7.1.2 of ASHRAE 23.1-2010 (incorporated by reference; see § 431.303) when verifying subcooling at the mass flow meters, only the sight glass and a temperature sensor located on the tube surface under the insulation are required. Subcooling shall be verified to be within the 3 °F requirement downstream of flow meters located in the same chamber as a condensing unit under test and upstream of flow meters located in the same chamber as a unit cooler under test, rather than always downstream as indicated in AHRI 1250-2009, section C3.4.5 or always upstream as indicated in section 7.1.2 of ASHRAE 23.1-2010. If the subcooling is less than 3 °F, cool the line between the condensing unit outlet and this location to achieve the required subcooling. When providing such cooling while testing a matched pair, (a) set up the line-cooling system and also set up apparatus to heat the liquid line between the mass flow meters and the unit cooler, (b) when the system has achieved steady state without activation of the heating and cooling systems, measure the liquid temperature entering the expansion valve for a period of at least 30 minutes, (c) activate the cooling system to provide the required subcooling at the mass flow meters, (d) if necessary, apply heat such that the temperature entering the expansion valve is within 0.50F of the temperature measured during step (b), and (e) proceed with measurements once condition (d) has been verified.
3.2.4. In appendix C, section C3.5, regarding unit cooler fan power measurements, for a given motor winding configuration, the total power input shall be measured at the highest nameplate voltage. For three-phase power, voltage imbalances shall be no more than 2 percent from phase to phase.
3.2.5. In the test setup (appendix C, section C8.3), the liquid line and suction line shall be constructed of pipes of the manufacturer-specified size. The pipe lines shall be insulated with a minimum total thermal resistance equivalent to 1⁄2-inch thick insulation having a flat-surface R-Value of 3.7 ft2- °F-hr/Btu per inch or greater. Flow meters need not be insulated but must not be in contact with the floor. The lengths of the connected liquid line and suction line shall be 25 feet ± 3 inches, not including the requisite flow meters, each. Of this length, no more than 15 feet shall be in the conditioned space. Where there are multiple branches of piping, the maximum length of piping applies to each branch individually as opposed to the total length of the piping.
3.2.6. Installation Instructions
Manufacturer installation instructions refer to the instructions that are applied to the unit (i.e., as a label) or that come packaged with the unit. Online installation instructions are acceptable only if the version number or date of publication is referenced on the unit label or in the documents that are packaged with the unit.
3.2.6.1 Installation Instruction Hierarchy when available installation instructions are in conflict
3.2.6.1.1 If a manufacturer installation instruction provided on the label(s) applied to the unit conflicts with the manufacturer installation instructions that are shipped with the unit, the instructions on the unit's label take precedence.
3.2.6.1.2 Manufacturer installation instructions provided in any documents that are packaged with the unit take precedence over any manufacturer installation instructions provided online.
3.2.6.2 For testing of attached split systems, the manufacturer installation instructions for the dedicated condensing unit shall take precedence over the manufacturer installation instructions for the unit cooler.
3.2.6.3 Unit setup shall be in accordance with the manufacturer installation instructions (laboratory installation instructions shall not be used).
3.2.6.4 Achieving test conditions shall always take precedence over installation instructions.
3.2.7. Refrigerant Charging and Adjustment of Superheat and Subcooling.
All dedicated condensing systems (dedicated condensing units tested alone, matched pairs, and single packaged dedicated systems) that use flooding of the condenser for head pressure control during low-ambient-temperature conditions shall be charged, and superheat and/or subcooling shall be set, at Refrigeration C test conditions unless otherwise specified in the installation instructions.
If after being charged at Refrigeration C condition the unit under test does not operate at the Refrigeration A condition due to high pressure cut out, refrigerant shall be removed in increments of 4 ounces or 5 percent of the test unit's receiver capacity, whichever quantity is larger, until the unit operates at the Refrigeration A condition. All tests shall be run at this final refrigerant charge. If less than 0 °F of subcooling is measured for the refrigerant leaving the condensing unit when testing at B or C condition, calculate the refrigerant-enthalpy-based capacity (i.e., when using the DX dual instrumentation, the DX calibrated box, or single-packaged unit refrigerant enthalpy method) assuming that the refrigerant is at saturated liquid conditions at the condensing unit exit.
All dedicated condensing systems that do not use a flooded condenser design shall be charged at Refrigeration A test conditions unless otherwise specified in the installation instructions.
If the installation instructions give a specified range for superheat, sub-cooling, or refrigerant pressure, the average of the range shall be used as the refrigerant charging parameter target and the test condition tolerance shall be ±50 percent of the range. Perform charging of near-azeotropic and zeotropic refrigerants only with refrigerant in the liquid state. Once the correct refrigerant charge is determined, all tests shall run until completion without further modification.
3.2.7.1. When charging or adjusting superheat/subcooling, use all pertinent instructions contained in the installation instructions to achieve charging parameters within the tolerances. However, in the event of conflicting charging information between installation instructions, follow the installation instruction hierarchy listed in section 3.2.6. of this appendix. Conflicting information is defined as multiple conditions given for charge adjustment where all conditions specified cannot be met. In the event of conflicting information within the same set of charging instructions (e.g., the installation instructions shipped with the dedicated condensing unit), follow the hierarchy in table C.4 of this section for priority. Unless the installation instructions specify a different charging tolerance, the tolerances identified in table C.4 of this section shall be used.
| Priority | Fixed orifice | Expansion valve | ||
|---|---|---|---|---|
| Parameter with installation
instruction target |
Tolerance | Parameter with installation
instruction target |
Tolerance | |
| 1 | Superheat | ±2.0 °F | Subcooling | 10% of the Target Value; No less than ±0.5 °F, No more than ±2.0 °F. |
| 2 | High Side Pressure or Saturation Temperature | ±4.0 psi or ±1.0 °F | High Side Pressure or Saturation Temperature | ±4.0 psi or ±1.0 °F. |
| 3 | Low Side Pressure or Saturation Temperature | ±2.0 psi or ±0.8 °F | Superheat | ±2.0 °F. |
| 4 | Low Side Temperature | ±2.0 °F | Low Side Pressure or Saturation Temperature | ±2.0 psi or ±0.8 °F. |
| 5 | High Side Temperature | ±2.0 °F | Approach Temperature | ±1.0 °F. |
| 6 | Charge Weight | ±2.0 oz | Charge Weight | 0.5% or 1.0 oz, whichever is greater. |
3.2.7.2. Dedicated Condensing Unit. If the Dedicated Condensing Unit includes a receiver and the subcooling target leaving the condensing unit provided in installation instructions cannot be met without fully filling the receiver, the subcooling target shall be ignored. Likewise, if the Dedicated Condensing unit does not include a receiver and the subcooling target leaving the condensing unit cannot be met without the unit cycling off on high pressure, the subcooling target can be ignored. Also, if no instructions for charging or for setting subcooling leaving the condensing unit are provided in the installation instructions, the refrigeration system shall be set up with a charge quantity and/or exit subcooling such that the unit operates during testing without shutdown (e.g., on a high-pressure switch) and operation of the unit is otherwise consistent with the requirements of the test procedure of this appendix and the installation instructions.
3.2.8. Chamber Conditioning using the Unit Under Test.
In appendix C, section C6.2 of AHRI 1250-2009, for applicable system configurations (matched pairs, single-packaged refrigeration systems, and standalone unit coolers), the unit under test may be used to aid in achieving the required test chamber conditions prior to beginning any steady state test. However, the unit under test must be inspected and confirmed to be free from frost before initiating steady state testing.
3.3. Matched systems, single-package dedicated systems, and unit coolers tested alone: Use the test method in AHRI 1250-2009 (incorporated by reference; see § 431.303), appendix C as the method of test for matched refrigeration systems, single-package dedicated systems, or unit coolers tested alone, with the following modifications:
3.3.1. For unit coolers tested alone, use test procedures described in AHRI 1250-2009 for testing unit coolers for use in mix-match system ratings, except that for the test conditions in tables 15 and 16 of this appendix, use the Suction A saturation condition test points only. Also, for unit coolers tested alone, other than high-temperature unit coolers, use the calculations in section 7.9 of AHRI 1250-2009 to determine AWEF and net capacity described in AHRI 1250-2009 for unit coolers matched to parallel rack systems.
3.3.2. In appendix C, section C.13, the version of AHRI Standard 420 used for test methods, requirements, and procedures shall be AHRI 420-2008 (incorporated by reference; see § 431.303).
3.3.3. Evaporator Fan Power.
3.3.3.1. Ducted Evaporator Air.
For ducted fan coil units with ducted evaporator air, or that can be installed with or without ducted evaporator air: Connect ductwork on both the inlet and outlet connections and determine external static pressure as described in ASHRAE 37 (incorporated by reference; see § 431.303), sections 6.4 and 6.5. Use pressure measurement instrumentation as described in ASHRAE 37, section 5.3.2. Test at the fan speed specified in manufacturer installation instructions—if there is more than one fan speed setting and the installation instructions do not specify which speed to use, test at the highest speed. Conduct tests with the external static pressure equal to 50 percent of the maximum external static pressure allowed by the manufacturer for system installation within a tolerance of −0.00/+0.05 in. wc. Set the external static pressure by symmetrically restricting the outlet of the test duct. Alternatively, if using the indoor air enthalpy method to measure capacity, set external static pressure by adjusting the fan of the airflow measurement apparatus. In case of conflict, these requirements for setting evaporator airflow take precedence over airflow values specified in manufacturer installation instructions or product literature.
3.3.3.2. Unit Coolers or Single-Packaged Systems that are not High-Temperature Refrigeration Systems.
Use appendix C, section C10 of AHRI 1250-2009 for off-cycle evaporator fan testing, with the exception that evaporator fan controls using periodic stir cycles shall be adjusted so that the greater of a 50 percent duty cycle (rather than a 25 percent duty cycle) or the manufacturer default is used for measuring off-cycle fan energy. For adjustable-speed controls, the greater of 50 percent fan speed (rather than 25 percent fan speed) or the manufacturer's default fan speed shall be used for measuring off-cycle fan energy. Also, a two-speed or multi-speed fan control may be used as the qualifying evaporator fan control. For such a control, a fan speed no less than 50 percent of the speed used in the maximum capacity tests shall be used for measuring off-cycle fan energy.
3.3.3.3. High-Temperature Refrigeration Systems.
3.3.3.3.1. The evaporator fan power consumption shall be measured in accordance with the requirements in section C3.5 of AHRI 1250-2009. This measurement shall be made with the fan operating at full speed, either measuring unit cooler or total system power input upon the completion of the steady state test when the compressor and the condenser fan of the walk-in system are turned off, or by submetered measurement of the evaporator fan power during the steady state test.
Section C3.5 of AHRI 1250-2009 is revised to read:
Evaporator Fan Power Measurement.
The following shall be measured and recorded during a fan power test.
EFcomp,on Total electrical power input to fan motor(s) of Unit Cooler, W
FS Fan speed(s), rpm
N Number of motors
Pb Barometric pressure, in. Hg
Tdb Dry-bulb temperature of air at inlet, °F
Twb Wet-bulb temperature of air at inlet, °F
V Voltage of each phase
For a given motor winding configuration, the total power input shall be measured at the highest nameplate voltage. For three-phase power, voltage imbalance shall be no more than 2%.
3.3.3.3.2. Evaporator fan power for the off-cycle is equal to the on-cycle evaporator fan power with a run time of 10 percent of the off-cycle time.
EFcomp,off = 0.1 × EFcomp,on
3.3.4. Use appendix C, section C11 of AHRI 1250-2009 (incorporated by reference, see § 431.303) for defrost testing. The Frost Load Condition Defrost Test (C11.1.1) is optional.
3.3.4.1. If the frost load condition defrost test is performed:
3.3.4.1.1 Operate the unit cooler at the dry coil conditions as specified in appendix C, section C11.1 to obtain dry coil defrost energy, DFd, in W-h.
3.3.4.1.2 Operate the unit cooler at the frost load conditions as specified in appendix C, sections C11.1 and C11.1.1 to obtain frosted coil defrost energy, DFf, in W-h.
3.3.4.1.3 The number of defrosts per day, NDF, shall be calculated from the time interval between successive defrosts from the start of one defrost to the start of the next defrost at the frost load conditions.
3.3.4.1.4 Use appendix C, equations C13 and C14 in section C11.3 to calculate, respectively, the daily average defrost energy, DF, in W-h and the daily contribution of the load attributed to defrost QDF in Btu.
3.3.4.1.5 The defrost adequacy requirements in appendix C, section C11.3 shall apply.
3.3.4.2 If the frost load test is not performed:
3.3.4.2.1 Operate the unit cooler at the dry coil conditions as specified in appendix C, section C11.1 to obtain dry coil defrost energy, DFd, in W-h.
3.3.4.2.2 The frost load defrost energy, DFf, in W-h shall be equal to 1.05 multiplied by the dry coil energy consumption, DFd, measured using the dry coil condition test in appendix C, section C11.1.
3.3.4.2.3 The number of defrosts per day NDF used in subsequent calculations shall be 4.
3.3.4.2.4 Use appendix C, equation C13 in section C11.3 to calculate the daily average defrost energy, DF, in W-h.
3.3.4.2.5 The daily contribution of the load attributed to defrost QDF in Btu shall be calculated as follows:
Where:
DFd = the defrost energy, in W-h, measured at the dry coil condition
3.3.5. If a unit has adaptive defrost, use appendix C, section C11.2 of AHRI 1250-2009 as follows:
3.3.5.1. When testing to certify to the energy conservation standards in § 431.306, do not perform the optional test for adaptive or demand defrost in appendix C, section C11.2.
3.3.5.2. When determining the represented value of the calculated benefit for the inclusion of adaptive defrost, conduct the optional test for adaptive or demand defrost in appendix C, section C11.2 to establish the maximum time interval allowed between dry coil defrosts. If this time is greater than 24 hours, set its value to 24 hours. Then, calculate NDF (the number of defrosts per day) by averaging the time in hours between successive defrosts for the dry coil condition with the time in hours between successive defrosts for the frosted coil condition, and dividing 24 by this average time. (The time between successive defrosts for the frosted coil condition is found as specified in section 3.3.4 of this appendix C of AHRI 1250-2009: That is, if the optional frosted coil test was performed, the time between successive defrosts for the frosted coil condition is found by performing the frosted coil test as specified in section 3.3.4.1 of this appendix; and if the optional frosted coil test was not performed, the time between successive defrosts for the frosted coil condition shall be set to 4 as specified in section 3.3.4.2. of this appendix) Use this new value of NDF in subsequent calculations.
3.3.6. For matched refrigeration systems and single-package dedicated systems, calculate the AWEF using the calculations in AHRI 1250-2009 (incorporated by reference; see § 431.303), section 7.4, 7.5, 7.6, or 7.7, as applicable.
3.3.7. Calculations for Unit Coolers Tested Alone.
3.3.7.1. Unit Coolers that are not High-Temperature Unit Coolers.
Calculate the AWEF and net capacity using the calculations in AHRI 1250-2009, section 7.9.
3.3.7.2 High-Temperature Unit Coolers.
Calculate AWEF on the basis that walk-in box load is equal to half of the system net capacity, without variation according to high and low load periods, and with EER set according to tested evaporator capacity, as follows:
The net capacity, q̇mix,evap, is determined from the test data for the unit cooler at the 38 °F suction dewpoint.
Where:
Where:
ḂL is the non-equipment-related box load;
LF is the load factor; and
Other symbols are as defined in section 8 of AHRI 1250-2009.
3.3.7.3. If the unit cooler has variable-speed evaporator fans that vary fan speed in response to load, then:
3.3.7.3.1. When testing to certify compliance with the energy conservation standards in § 431.306, fans shall operate at full speed during on-cycle operation. Do not conduct the calculations in AHRI 1250-2009, section 7.9.3. Instead, use AHRI 1250-2009, section 7.9.2 to determine the system's AWEF.
3.3.7.3.2. When calculating the benefit for the inclusion of variable-speed evaporator fans that modulate fan speed in response to load for the purpose of making representations of efficiency, use AHRI 1250-2009, section 7.9.3 to determine the system AWEF.
3.4. Dedicated condensing units that are not matched for testing and are not single-package dedicated systems
3.4.1. Refer to appendix C, section C.12 of AHRI 1250-2009 (incorporated by reference; see § 431.303), for the method of test for dedicated condensing units. The version of ASHRAE Standard 23 used for test methods, requirements, and procedures shall be ANSI/ASHRAE Standard 23.1-2010 (incorporated by reference; see § 431.303). When applying this test method, use the applicable test method modifications listed in sections 3.1 and 3.2 of this appendix. For the test conditions in AHRI 1250-2009, Tables 11, 12, 13, and 14, use the Suction A condition test points only.
3.4.2. Calculate the AWEF and net capacity for dedicated condensing units using the calculations in AHRI 1250-2009 (incorporated by reference; see § 431.303) section 7.8. Use the following modifications to the calculations in lieu of unit cooler test data:
3.4.2.1. For calculating enthalpy leaving the unit cooler to calculate gross capacity,
(a) the saturated refrigerant temperature (dew point) at the unit cooler coil exit, Tevap, shall be 25 °F for medium-temperature systems (coolers) and −20 °F for low-temperature systems (freezers), and
(b) the refrigerant temperature at the unit cooler exit shall be 35 °F for medium-temperature systems (coolers) and −14 °F for low-temperature systems (freezers). For calculating gross capacity, the measured enthalpy at the condensing unit exit shall be used as the enthalpy entering the unit cooler. The temperature measurement requirements of appendix C, section C3.1.6 of AHRI 1250-2009 and modified by section 3.2.1 of this appendix shall apply only to the condensing unit exit rather than to the unit cooler inlet and outlet, and they shall be applied for two measurements when using the DX Dual Instrumentation test method.
3.4.2.2. The on-cycle evaporator fan power in watts, EFcomp,on, shall be calculated as follows:
For medium-temperature systems (coolers), EFcomp,on = 0.013 × qmix,cd
For low-temperature systems (freezers), EFcomp,on = 0.016 × qmix,cd
Where:
qmix,cd is the gross cooling capacity of the system in Btu/h, found by a single test at the Capacity A, Suction A condition for outdoor units and the Suction A condition for indoor units.
3.4.2.3. The off-cycle evaporator fan power in watts, EFcomp,off, shall be calculated as follows:
EFcomp,off = 0.2 × EFcomp,on
Where:
EFcomp,on is the on-cycle evaporator fan power in watts.
3.4.2.4. The daily defrost energy use in watt-hours, DF, shall be calculated as follows:
For medium-temperature systems (coolers), DF = 0
For low-temperature systems (freezers), DF = 8.5 × 10−3 × qmix,cd1.27 × NDF
Where:
qmix,cd is the gross cooling capacity of the system in Btu/h, found by a single test at the Capacity A, Suction A condition for outdoor units and the Suction A condition for indoor units, and
NDF is the number of defrosts per day, equal to 4.
3.4.2.5. The daily defrost heat load contribution in Btu, QDF, shall be calculated as follows:
For medium-temperature systems (coolers), QDF = 0
For low-temperature systems (freezers), QDF = 0.95 × DF × 3.412
Where:
DF is the daily defrost energy use in watt-hours.
3.5 Hot Gas Defrost Refrigeration Systems
For all hot gas defrost refrigeration systems, remove the hot gas defrost mechanical components and disconnect all such components from electrical power.
3.5.1 Hot Gas Defrost Dedicated Condensing Units Tested Alone: Test these units as described in section 3.4 of this appendix for electric defrost dedicated condensing units that are not matched for testing and are not single-package dedicated systems.
3.5.2 Hot Gas Defrost Matched Systems and Single-package Dedicated Systems: Test these units as described in section 3.3 of this appendix for electric defrost matched systems and single-package dedicated systems, but do not conduct defrost tests as described in sections 3.3.4 and 3.3.5 of this appendix. Calculate daily defrost energy use as described in section 3.4.2.4 of this appendix. Calculate daily defrost heat contribution as described in section 3.4.2.5 of this appendix.
3.5.3 Hot Gas Defrost Unit Coolers Tested Alone: Test these units as described in section 3.3 of this appendix for electric defrost unit coolers tested alone, but do not conduct defrost tests as described in sections 3.3.4 and 3.3.5 of this appendix. Calculate average defrost heat load Q̇DF, expressed in Btu/h, as follows:
[81 FR 95803, Dec. 28, 2016, as amended at 86 FR 16035, Mar. 26, 2021; 88 FR 28845, May 4, 2023; 88 FR 73217, Oct. 25, 2023]
Prior to October 31, 2023, representations with respect to the energy use of refrigeration components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with the applicable provisions for 10 CFR part 431, subpart R, appendix C, revised as of January 1, 2022. Beginning October 31, 2023, representations with respect to energy use of refrigeration components of walk-in coolers and walk-in freezers, including compliance certifications, must be based on testing conducted in accordance with appendix C to this subpart.
For any amended standards for walk-in coolers and walk-in freezers published after January 1, 2022, manufacturers must use the results of testing under this appendix to determine compliance. Representations related to energy consumption must be made in accordance with this appendix when determining compliance with the relevant standard. Manufacturers may also use this appendix to certify compliance with any amended standards prior to the applicable compliance date for those standards.
0. Incorporation by Reference
DOE incorporated by reference in § 431.303, the entire standard for AHRI 1250-2020, ANSI/ASHRAE 16, ANSI/ASHRAE 23.1-2010, ANSI/ASHRAE 37, ANSI/ASHRAE 41.1, ANSI/ASHRAE 41.3, ANSI/ASHRAE 41.6, and ANSI/ASHRAE 41.10. However, certain enumerated provisions of these standards, as set forth in sections 0.1 through 0.8 of this appendix are inapplicable. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control. To the extent there is a conflict between the terms or provisions of AHRI 1250-2020, ANSI/ASHRAE 16, ANSI/ASHRAE 23.1-2010, ANSI/ASHRAE 37, ANSI/ASHRAE 41.1, ANSI/ASHRAE 41.3, ANSI/ASHRAE 41.6, and ANSI/ASHRAE 41.10, the AHRI 1250-2020 provisions control.
0.1 AHRI 1250-2020
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 9 Minimum Data Requirements for Published Rating, is inapplicable
(d) Section 10 Marking and Nameplate Data, is inapplicable
(e) Section 11 Conformance Conditions, is inapplicable
0.2 ANSI/ASHRAE 16
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Normative Appendices E-M, are inapplicable
(e) Informative Appendices N-R, are inapplicable
0.3 ANSI/ASHRAE 23.1-2010
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
0.4 ANSI/ASHRAE 37
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Informative Appendix A Classifications of Unitary Air-conditioners and Heat Pumps, is inapplicable.
0.5 ANSI/ASHRAE 41.1
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Section 9 Test Report, is inapplicable
(e) Informative Appendices A-C, are inapplicable
0.6 ANSI/ASHRAE 41.3
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Section 6 Instrument Types (informative), is inapplicable
(e) Section 8 Test Report, is inapplicable
(f) Informative Annexes A-D, are inapplicable
0.7 ANSI/ASHRAE 41.6
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Section 9 Test Report, is inapplicable
(e) Informative Appendices A-D, are inapplicable
0.8 ANSI/ASHRAE 41.10
(a) Section 1 Purpose, is inapplicable
(b) Section 2 Scope, is inapplicable
(c) Section 4 Classifications, is inapplicable
(d) Section 10 Test Report, is inapplicable
(e) Informative Annexes A-D, are inapplicable
1. Scope
This appendix covers the test requirements used to determine the net capacity and the AWEF2 of the refrigeration system of a walk-in cooler or walk-in freezer.
2. Definitions
2.1. Applicable Definitions
The definitions contained in § 431.302, AHRI 1250-2020, ANSI/ASHRAE 37, and ANSI/ASHRAE 16 apply to this appendix. When definitions in standards incorporated by reference are in conflict or when they conflict with this section, the hierarchy of precedence shall be in the following order: § 431.302, AHRI 1250-2020, and then either ANSI/ASHRAE 37 or ANSI/ASHRAE 16.
The term “unit cooler” used in AHRI 1250-2020 and this subpart shall be considered to address both “unit coolers” and “ducted fan coil units,” as appropriate.
2.2. Additional Definitions
2.2.1. Digital Compressor means a compressor that uses mechanical means for disengaging active compression on a cyclic basis to provide a reduced average refrigerant flow rate in response to a control system input signal.
2.2.2. Displacement Ratio, applicable to staged positive displacement compressor systems, means the swept volume rate, e.g. in cubic centimeters per second, of a given stage, divided by the swept volume rate at full capacity.
2.2.3. Duty Cycle, applicable to digital compressors, means the fraction of time that the compressor is engaged and actively compressing refrigerant.
2.2.4. Maximum Speed, applicable to variable-speed compressors, means the maximum speed at which the compressor will operate under the control of the dedicated condensing system control system for extended periods of time, i.e. not including short-duration boost-mode operation.
2.2.5. Minimum Speed, applicable to variable-speed compressors, means the minimum compressor speed at which the compressor will operate under the control of the dedicated condensing system control system.
2.2.6. Multiple-Capacity, applicable for describing a refrigeration system, indicates that it has three or more stages (levels) of capacity.
2.2.7. Speed Ratio, applicable to variable-speed compressors, means the ratio of operating speed to the maximum speed.
3. Test Methods, Measurements, and Calculations
Determine the Annual Walk-in Energy Factor (AWEF2) and net capacity of walk-in cooler and walk-in freezer refrigeration systems by conducting the test procedure set forth in AHRI 1250-2020, with the modifications to that test procedure provided in this section. However, certain sections of AHRI 1250-2020, ANSI/ASHRAE 37, and ANSI/ASHRAE 16 are not applicable, as set forth in sections 0.1, 0.2, and 0.3 of this appendix. Round AWEF2 measurements to the nearest 0.01 Btu/Wh. Round net capacity measurements as indicated in table 1 of this appendix.
| Net capacity range, Btu/h | Rounding
multiple, Btu/h |
|---|---|
| <20,000 | 100 |
| ≥20,000 and <38,000 | 200 |
| ≥38,000 and <65,000 | 500 |
| ≥65,000 | 1,000 |
The following sections of this appendix provide additional instructions for testing. In cases where there is a conflict, the language of this appendix takes highest precedence, followed by AHRI 1250-2020, then ANSI/ASHRAE 37 or ANSI/ASHRAE 16. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE. Material is incorporated as it exists on the date of the approval, and a notification of any change in the incorporation will be published in the Federal Register.
3.1. Instrumentation Accuracy and Test Tolerances
Use measuring instruments as described in section 4.1 of AHRI 1250-2020, with the following additional requirement.
3.1.1. Electrical Energy Input measured in Wh with a minimum accuracy of ±0.5% of reading (for Off-Cycle tests per footnote 5 of Table C3 in section C3.6.2 of AHRI 1250-2020).
3.2. Test Operating Conditions
Test conditions used to determine AWEF2 shall be as specified in Tables 4 through 17 of AHRI 1250-2020. Tables 7 and 11 of AHRI 1250-2020, labeled to apply to variable-speed outdoor matched-pair refrigeration systems, shall also be used for testing variable-capacity single-packaged outdoor refrigeration systems, and also for testing multiple-capacity matched-pair or single-packaged outdoor refrigeration systems. Test conditions used to determine AWEF2 for refrigeration systems not specifically identified in AHRI 1250-2020 are as enumerated in sections 3.5.1 through 3.5.6 of this appendix.
3.2.1 Test Operating Conditions for High-Temperature Refrigeration Systems
For fixed-capacity high-temperature matched-pair or single-packaged refrigeration systems with indoor condensing units, conduct tests using the test conditions specified in table 2 of this appendix. For fixed-capacity high-temperature matched-pair or single-packaged refrigeration systems with outdoor condensing units, conduct tests using the test conditions specified in table 3 of this appendix. For high-temperature unit coolers tested alone, conduct tests using the test conditions specified in table 4 of this appendix.
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % 1 |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F |
Compressor
status |
Test objective |
|---|---|---|---|---|---|---|
| Off-Cycle Power | 55 | 55 | Compressor Off | Measure total input wattage during compressor off-cycle, (E |
||
| Refrigeration Capacity A | 55 | 55 | 90 | 3 75, 4 65 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler, input power, and EER at Test Condition. |
| Notes: | ||||||
| 1 The test condition tolerance (maximum permissible variation of the average value of the measurement from the specified test condition) for relative humidity is 3%. | ||||||
| 2 Measure off-cycle power as described in sections C3 and C4.2 of AHRI 1250-2020. | ||||||
| 3 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | ||||||
| 4 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | ||||||
| Test
description |
Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % 1 |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F |
Compressor
status |
Test objective |
|---|---|---|---|---|---|---|
| Refrigeration Capacity A | 55 | 55 | 95 | 3 75, 4 68 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler, input power, and EER at Test Condition. |
| Off-Cycle Power, Capacity A | 55 | 55 | 95 | 3 75, 4 68 | Compressor Off | Measure total input wattage during compressor off-cycle, ( E |
| Refrigeration Capacity B | 55 | 55 | 59 | 3 54, 4 46 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler and system input power at moderate condition. |
| Off-Cycle Power, Capacity B | 55 | 55 | 59 | 3 54, 4 46 | Compressor Off | Measure total input wattage during compressor off-cycle, (E |
| Refrigeration Capacity C | 55 | 55 | 35 | 3 34, 4 29 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler and system input power at cold condition. |
| Off-Cycle Power, Capacity C | 55 | 55 | 35 | 3 34, 4 29 | Compressor Off | Measure total input wattage during compressor off-cycle, (E |
| Notes: | ||||||
| 1 The test condition tolerance (maximum permissible variation of the average value of the measurement from the specified test condition) for relative humidity is 3%. | ||||||
| 2 Measure off-cycle power as described in sections C3 and C4.2 of AHRI 1250-2020. | ||||||
| 3 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | ||||||
| 4 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | ||||||
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % 1 |
Suction
dew point temp, °F 3 4 |
Liquid inlet
bubble point temperature, °F |
Liquid inlet
subcooling, °F |
Compressor
status |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle | 55 | 55 | 105 | 9 | Compressor Off | Measure unit cooler input wattage during compressor off-cycle, E |
|
| Refrigeration Capacity | 55 | 55 | 38 | 105 | 9 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler, input power, and EER at Test Condition. |
| Notes: | |||||||
| 1 The test condition tolerance (maximum permissible variation of the average value of the measurement from the specified test condition) for relative humidity is 3%. | |||||||
| 2 Measure off-cycle power as described in sections C3 and C4.2 of AHRI 1250-2020. | |||||||
| 3 Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
| 4 Suction Dew Point shall be measured at the Unit Cooler Exit. | |||||||
3.2.2 Test Operating Conditions for CO2 Unit Coolers
For medium-temperature CO2 Unit Coolers, conduct tests using the test conditions specified in table 5 of this appendix. For low-temperature CO2 Unit Coolers, conduct tests using the test conditions specified in table 6 of this appendix.
| Test title | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Suction
dew point temp,3 °F |
Liquid inlet
bubble point temperature, °F |
Liquid inlet
subcooling, °F |
Compressor
operating mode |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle Power | 35 | <50 | Compressor Off | Measure unit cooler input wattage during compressor off-cycle, E |
|||
| Refrigeration Capacity, Ambient Condition A | 35 | <50 | 25 | 38 | 5 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler, q |
| Notes: | |||||||
| 1 Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
| 2 Measure off-cycle power as described in sections C3 and C4.2 of AHRI 1250-2020. | |||||||
| 3 Suction Dew Point shall be measured at the Unit Cooler Exit conditions. | |||||||
| Test title | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Suction
dew point temp,2 °F |
Liquid inlet
bubble point temperature, °F |
Liquid inlet
subcooling, °F |
Compressor
operating mode |
Test objective |
|---|---|---|---|---|---|---|---|
| Off-Cycle Power | −10 | <50 | Compressor Off | Measure unit cooler input wattage during compressor off-cycle, E |
|||
| Refrigeration Capacity, Ambient Condition A | −10 | <50 | −20 | 38 | 5 | Compressor On | Determine Net Refrigeration Capacity of Unit Cooler, q |
| Defrost | −10 | <50 | Compressor Off | Test according to Appendix C Section C10 of AHRI 1250-2020, D |
|||
| Notes: | |||||||
| 1 Superheat shall be set as indicated in the installation instructions. If no superheat specification is given a default superheat value of 6.5 °F shall be used. | |||||||
| 2 Measure off-cycle power as described in sections C3 and C4.2 of AHRI 1250-2020. | |||||||
| 3 Suction Dew Point shall be measured at the Unit Cooler Exit conditions. | |||||||
3.2.3 Test Operating Conditions for Two-Capacity Condensing Units Tested Alone
For two-capacity medium-temperature outdoor condensing units tested alone, conduct tests using the test conditions specified in table 7 of this appendix. For two-capacity medium-temperature indoor condensing units tested alone, conduct tests using the test conditions specified in table 8 of this appendix. For two-capacity low-temperature outdoor condensing units tested alone, conduct tests using the test conditions specified in table 9 of this appendix. For two-capacity low-temperature indoor condensing units tested alone, conduct tests using the test conditions specified in table 10 of this appendix.
| Test description | Suction
dew point, °F |
Return gas, °F | Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | 24 | 41 | 95 | 75 | Low Capacity, k=1. |
| Capacity, Condition A, High Capacity | 23 | 41 | 95 | 75 | High Capacity, k=2. |
| Off-Cycle, Condition A | 95 | 75 | Off. | ||
| Capacity, Condition B, Low Capacity | 24 | 41 | 59 | 54 | Low Capacity, k=1. |
| Capacity, Condition B, High Capacity | 23 | 59 | 54 | High Capacity, k=2. | |
| Off-Cycle, Condition B | 59 | 54 | Off. | ||
| Capacity, Condition C, Low Capacity | 24 | 41 | 35 | 34 | Low Capacity, k=1. |
| Capacity, Condition C, High Capacity | 23 | 41 | 35 | 34 | High Capacity, k=2. |
| Off-Cycle, Condition C | 35 | 34 | Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test description | Suction
dew point, °F |
Return gas, °F | Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | 24 | 41 | 90 | 75 | Low Capacity, k=1. |
| Capacity, Condition A, High Capacity | 23 | 41 | 90 | 75 | High Capacity, k=2. |
| Off-Cycle, Condition A | 90 | 75 | Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test title | Suction
dew point, °F |
Return gas,
°F |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor operating mode |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | −22 | 5 | 95 | 75 | Low Capacity, k=1. |
| Capacity, Condition A, High Capacity | −22 | 5 | 95 | 75 | High Capacity, k=2. |
| Off-Cycle, Condition A | 95 | 75 | Compressor Off. | ||
| Capacity, Condition B, Low Capacity | −22 | 5 | 59 | 54 | Low Capacity, k=1. |
| Capacity, Condition B, High Capacity | −22 | 5 | 59 | 54 | High Capacity, k=2. |
| Off-Cycle, Condition B | 59 | 54 | Compressor Off. | ||
| Capacity, Condition C, Low Capacity | −22 | 5 | 35 | 34 | Low Capacity, k=1. |
| Capacity, Condition C, High Capacity | −22 | 5 | 35 | 34 | High Capacity, k=2. |
| Off-Cycle, Condition C | 35 | 34 | Compressor Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test title | Suction
dew point, °F |
Return gas, °F | Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor operating mode |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | −22 | 5 | 90 | 75 | Low Capacity, k=1. |
| Capacity, Condition A, High Capacity | −22 | 5 | 90 | 75 | High Capacity, k=2. |
| Off-Cycle, Condition A | 90 | 75 | Compressor Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
3.2.4 Test Operating Conditions for Variable- or Multiple-Capacity Condensing Units Tested Alone
For variable-capacity or multiple-capacity outdoor medium-temperature condensing units tested alone, conduct tests using the test conditions specified in table 11 of this appendix. For variable-capacity or multiple-capacity indoor medium-temperature condensing units tested alone, conduct tests using the test conditions specified in table 12 of this appendix. For variable-capacity or multiple-capacity outdoor low-temperature condensing units tested alone, conduct tests using the test conditions specified in table 13 of this appendix. For variable-capacity or multiple-capacity indoor low-temperature condensing units tested alone, conduct tests using the test conditions specified in table 14 of this appendix.
| Test description | Suction
dew point, °F |
Return gas, °F | Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | 24 | 41 | 95 | 75 | Minimum Capacity, k=1. |
| Capacity, Condition A, Intermediate Capacity | 24 | 41 | 95 | 75 | Intermediate Capacity, k=i. |
| Capacity, Condition A, Maximum Capacity | 23 | 41 | 95 | 75 | Maximum Capacity, k=2 |
| Off-Cycle, Condition A | 95 | 75 | Off. | ||
| Capacity, Condition B, Minimum Capacity | 24 | 41 | 59 | 54 | Minimum Capacity, k=1. |
| Capacity, Condition B, Intermediate Capacity | 24 | 41 | 59 | 54 | Intermediate Capacity, k=i. |
| Capacity, Condition B, Maximum Capacity | 23 | 41 | 59 | 54 | Maximum Capacity, k=2. |
| Off-Cycle, Condition B | 59 | 54 | Off. | ||
| Capacity, Condition C, Minimum Capacity | 24 | 41 | 35 | 34 | Minimum Capacity, k=1. |
| Capacity, Condition C, Intermediate Capacity | 24 | 41 | 35 | 34 | Intermediate Capacity, k=i. |
| Capacity, Condition C, Maximum Capacity | 23 | 41 | 35 | 34 | Maximum Capacity, k=2. |
| Off-Cycle, Condition C | 35 | 34 | Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test description | Suction
dew point, °F |
Return gas, °F | Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | 24 | 41 | 90 | 75 | Minimum Capacity, k=1. |
| Capacity, Condition A, Intermediate Capacity | 24 | 41 | 90 | 75 | Intermediate Capacity, k=i. |
| Capacity, Condition A, Maximum Capacity | 23 | 41 | 90 | 75 | Maximum Capacity, k=2. |
| Off-Cycle, Condition A | 90 | 75 | Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test title | Suction
dew point, °F |
Return gas,
°F |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor operating mode |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | −22 | 5 | 95 | 75 | Minimum Capacity, k=1. |
| Capacity, Condition A, Intermediate Capacity | −22 | 5 | 95 | 75 | Intermediate Capacity, k=i. |
| Capacity, Condition A, Maximum Capacity | −22 | 5 | 95 | 75 | Maximum Capacity, k=2. |
| Off-Cycle, Condition A | 95 | 75 | Compressor Off. | ||
| Capacity, Condition B, Minimum Capacity | −22 | 5 | 59 | 54 | Minimum Capacity, k=1. |
| Capacity, Condition B, Intermediate Capacity | −22 | 5 | 59 | 54 | Intermediate Capacity, k=i. |
| Capacity, Condition B, Maximum Capacity | −22 | 5 | 59 | 54 | Maximum Capacity, k=2. |
| Off-Cycle, Condition B | 59 | 54 | Compressor Off. | ||
| Capacity, Condition C, Minimum Capacity | −22 | 5 | 35 | 34 | Minimum Capacity, k=1. |
| Capacity, Condition C, Intermediate Capacity | −22 | 5 | 35 | 34 | Intermediate Capacity, k=i. |
| Capacity, Condition C, Maximum Capacity | −22 | 5 | 35 | 34 | Maximum Capacity, k=2. |
| Off-Cycle, Condition C | 35 | 34 | Compressor Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| Test title | Suction
dew point, °F |
Return gas,
°F |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F 1 |
Compressor operating mode |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | −22 | 5 | 90 | 75 | Minimum Capacity, k=1. |
| Capacity, Condition A, Intermediate Capacity | −22 | 5 | 90 | 75 | Intermediate Capacity, k=i. |
| Capacity, Condition A, Maximum Capacity | −22 | 5 | 90 | 75 | Maximum Capacity, k=2. |
| Off-Cycle, Condition A | 90 | 75 | Compressor Off. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
3.2.5 Test Operating Conditions for Two-Capacity Indoor Matched-Pair or Single-Packaged Refrigeration Systems
For two-capacity indoor medium-temperature matched-pair or single-packaged refrigeration systems, conduct tests using the test conditions specified in table 15 of this appendix. For two-capacity indoor low-temperature matched-pair or single-packaged refrigeration systems, conduct tests using the test conditions specified in table 16 of this appendix.
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | 35 | <50 | 90 | 1 75, 2 65 | Low Capacity. |
| Capacity, Condition A, High Capacity | 35 | <50 | 90 | 1 75, 2 65 | High Capacity. |
| Off-Cycle, Condition A | 35 | <50 | 90 | 1 75, 2 65 | Off. |
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| 2 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | |||||
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Condenser
air entering dry-bulb, °F |
Maximum
condenser air entering wet-bulb, °F |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Low Capacity | −10 | <50 | 90 | 1 75, 2 65 | Low Capacity. |
| Capacity, Condition A, High Capacity | −10 | <50 | 90 | 1 75, 2 65 | High Capacity. |
| Off-Cycle, Condition A | −10 | <50 | 90 | 1 75, 2 65 | Off. |
| Defrost | −10 | <50 | System Dependent. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| 2 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | |||||
3.2.6 Test Conditions for Variable- or Multiple-Capacity Indoor Matched Pair or Single-Packaged Refrigeration Systems
For variable- or multiple-capacity indoor medium-temperature matched-pair or single-packaged refrigeration systems, conduct tests using the test conditions specified in table 17 of this appendix. For variable- or multiple-capacity indoor low-temperature matched-pair or single-packaged refrigeration systems, conduct tests using the test conditions specified in table 18 of this appendix.
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Condenser
air entering dry-bulb, °F |
Condenser
air entering wet-bulb, °F |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | 35 | <50 | 90 | 1 75, 2 65 | Minimum Capacity. |
| Capacity, Condition A, Intermediate Capacity | 35 | <50 | 90 | 1 75, 2 65 | Intermediate Capacity. |
| Capacity, Condition A, High Capacity | 35 | <50 | 90 | 1 75, 1 65 | Maximum Capacity. |
| Off-Cycle, Condition A | 35 | <50 | 90 | 1 75, 2 65 | Off. |
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| 2 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | |||||
| Test description | Unit cooler
air entering dry-bulb, °F |
Unit cooler
air entering relative humidity, % |
Condenser
air entering dry-bulb, °F |
Maximum condenser
air entering wet-bulb, °F |
Compressor status |
|---|---|---|---|---|---|
| Capacity, Condition A, Minimum Capacity | −10 | <50 | 90 | 1 75, 2 65 | Minimum Capacity. |
| Capacity, Condition A, Intermediate Capacity | −10 | <50 | 90 | 1 75, 2 65 | Intermediate Capacity. |
| Capacity, Condition A, Maximum Capacity | −10 | <50 | 90 | 1 75, 2 65 | Maximum Capacity. |
| Off-Cycle, Condition A | −10 | <50 | 90 | 1 75, 2 65 | Off. |
| Defrost | −10 | <50 | System Dependent. | ||
| Notes: | |||||
| 1 Required only for evaporative condensing units (e.g., incorporates a slinger ring). | |||||
| 2 Maximum allowable value for Single-Packaged Systems that do not use evaporative Dedicated Condensing Units, where all or part of the equipment is located in the outdoor room. | |||||
3.3 Calculation for Walk-in Box Load
3.3.1 For medium- and low-temperature refrigeration systems with indoor condensing units, calculate walk-in box loads for high and low load periods as a function of net capacity as described in section 6.2.1 of AHRI 1250-2020.
3.3.2 For medium- and low-temperature refrigeration systems with outdoor condensing units, calculate walk-in box loads for high and low load periods as a function of net capacity and outdoor temperature as described in section 6.2.2 of AHRI 1250-2020.
3.3.3 For high-temperature refrigeration systems, calculate walk-in box load as follows.
ḂL = 0.5 · q̇ss,A
Where q̇ss,A is the measured net capacity for Test Condition A.
3.4 Calculation for Annual Walk-in Energy Factor (AWEF2)
Calculations used to determine AWEF2 based on performance data obtained for testing shall be as specified in section 7 of AHRI 1250-2020 with modifications as indicated in sections 3.4.7 through 3.4.10 of this appendix. Calculations used to determine AWEF2 for refrigeration systems not specifically identified in sections 7.1.1 through 7.1.6 of AHRI 1250-2020 are enumerated in sections 3.4.1 through 3.4.6 and 3.4.11 through 3.4.14 of this appendix.
3.4.1 Two-Capacity Condensing Units Tested Alone, Indoor
3.4.1.1 Unit Cooler Power
Calculate maximum-capacity unit cooler power during the compressor on period ĖFcomp,on, in Watts, using Equation 130 of AHRI 1250-2020 for medium-temperature refrigeration systems and using Equation 173 of AHRI 1250-2020 for low-temperature refrigeration systems.
Calculate unit cooler power during the compressor off period ĖFcomp,off, in Watts, as 20 percent of the maximum-capacity unit cooler power during the compressor on period.
3.4.1.2 Defrost
For freezer refrigeration systems, calculate defrost heat contribution Q̇DF in Btu/h and the defrost average power consumption ḊF in W as a function of steady-state maximum gross refrigeration capacity Q̇grossk=2, as specified in section C10.2.2 of Appendix C of AHRI 1250-2020.
3.4.1.3 Net Capacity
Calculate steady-state maximum net capacity, q̇ssk=2, and minimum net capacity, q̇ssk=1 as follows:
q̇ssk=2 = Q̇grossk=2 − 3412 · ĖFcomp,on
q̇ssk=1 = Q̇grossk=1 − 3412 · 0.2 · ĖFcomp,on
Where:
Q̇grossk=2 and Q̇grossk=1 represent gross refrigeration capacity at maximum and minimum capacity, respectively.
3.4.1.4 Calculate average power input during the low load period as follows.
If the low load period box load, BL̇L, plus defrost heat contribution, Q̇DF (only applicable for freezers), is less than the minimum net capacity q̇ssk=1:
Where:
Ėssk=1 is the steady state condensing unit power input for minimum-capacity operation.
Ėcu,off is the condensing unit off-cycle power input, measured as described in section C3.5 of AHRI 1250-2020.
If the low load period box load, BL̇L, plus defrost heat contribution, Q̇DF, (only applicable for freezers) is greater than the minimum net capacity q̇ssk=1:
3.4.1.5 Calculate average power input during the high load period as follows.
3.4.1.6 Calculate the AWEF2 as follows:
3.4.2 Variable-Capacity or Multistage Condensing Units Tested Alone, Indoor
3.4.2.1 Unit Cooler Power
Calculate maximum-capacity unit cooler power during the compressor on period ĖFcomp,on as described in section 3.4.1.1 of this appendix.
Calculate unit cooler power during the compressor off period ĖFcomp,off, in Watts, as 20 percent of the maximum-capacity unit cooler power during the compressor on period.
3.4.2.2 Defrost
Calculate Defrost parameters as described in section 4.4.1.2 of this appendix.
3.4.2.3 Net Capacity
Calculate steady-state maximum net capacity, q̇ssk=2, intermediate net capacity, q̇ssk=i, and minimum net capacity, q̇ssk=1 as follows:
q̇ssk=2 = Q̇grossk=2 − 3412 · ĖFcomp,on
q̇ssk=2 = Q̇grossk=2 − 3412 · Kf · ĖFcomp,on
q̇ssk=1 = Q̇grossk=1 − 3412 · 0.2 · ĖFcomp,on
Where:
Q̇grossk=2, Q̇grossk=i, Q̇gross,k=1, and represent gross refrigeration capacity at maximum, intermediate, and minimum capacity, respectively.
Kf is the unit cooler power coefficient for intermediate capacity operation, set equal to 0.2 to represent low-speed fan operation if the Duty Cycle for a Digital Compressor, the Speed Ratio for a Variable-Speed Compressor, or the Displacement Ratio for a Multi-Stage Compressor at Intermediate Capacity is 65% or less, and otherwise set equal to 1.0.
3.4.2.4 Calculate average power input during the low load period as follows.
If the low load period box load, BL̇L, plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the minimum net capacity q̇ssk=1:
Where Ėcu,off, in W, is the condensing unit off-mode power consumption, measured as described in section C3.5 of AHRI 1250-2020.
If the low load period box load BL̇L plus defrost heat contribution Q̇DF (only applicable for freezers) is greater than the minimum net capacity q̇ssk=1 and less than the intermediate net capacity q̇ssk=i:
Where:
EERk=1 is the minimum-capacity energy efficiency ratio, equal to q̇ssk=1 divided by Ėssk=1 + 0.2 · ĖFcomp,on; and
EERk=i is the intermediate-capacity energy efficiency ratio, equal to q̇ssk=i divided by Ėssk=i + Kf · ĖFcomp,on.
3.4.2.5 Calculate average power input during the high load period as follows:
If the high load period box load, BL̇H, plus defrost heat contribution, Q̇DF (only applicable for freezers), is greater than the minimum net capacity q̇ssk=1 and less than the intermediate net capacity q̇ssk=i:
If the high load period box load, BL̇H, plus defrost heat contribution, Q̇DF (only applicable for freezers), is greater than the intermediate net capacity, q̇ssk=i, and less than the maximum net capacity, q̇ssk=2:
Where:
EERk=2 is the maximum-capacity energy efficiency ratio, equal to q̇ssk=2 divided by Ėssk=2 + ĖFcomp,on
3.4.2.6 Calculate the AWEF2 as follows.
3.4.3 Two-Capacity Condensing Units Tested Alone, Outdoor
3.4.3.1 Unit Cooler Power
Calculate maximum-capacity unit cooler power during the compressor on period ĖFcomp,on, in Watts, using Equation 153 of AHRI 1250-2020 for medium-temperature refrigeration systems and using Equation 196 of AHRI 1250-2020 for low-temperature refrigeration systems.
Calculate unit cooler power during the compressor off period ĖFcomp,off, in Watts, as 20 percent of the maximum-capacity unit cooler power during the compressor on period.
3.4.3.2 Defrost
Calculate Defrost parameters as described in section 3.4.1.2 of this appendix.
3.4.3.3 Condensing Unit Off-Cycle Power
Calculate Condensing Unit Off-Cycle Power for temperature tj as follows.
Where Ėcu,off,A and Ėcu,off,C are the Condensing Unit off-cycle power measurements for test conditions A and C, respectively, measured as described in section C3.5 of AHRI 1250-2020. If tj is greater than 35 °F and less than 59 °F, use Equation 157 of AHRI 1250-2020, and if tj is greater than or equal to 59 °F and less than 95 °F, use Equation 159 of AHRI 1250-2020.
3.4.3.4 Net Capacity and Condensing Unit Power Input
Calculate steady-state maximum net capacity, q̇ssk=2(tj), and minimum net capacity, q̇ssk=1(tj), and corresponding condensing unit power input levels Ėssk=2(tj) and Ėssk=1(tj) as a function of outdoor temperature tj as follows:
If tj ≤ 59 °F:
If 59 °F < tj:
Where:
The capacity level k can equal 1 or 2;
Q̇gross,Xk=2 and Q̇gross,Xk=1 represent gross refrigeration capacity at maximum and minimum capacity, respectively, for test condition X, which can take on values A, B, or C;
Ėss,Xk=2 and Ėss,Xk=1 represent condensing unit power input at maximum and minimum capacity, respectively for test condition X.
3.4.3.5 Calculate average power input during the low load period as follows.
Calculate the temperature, tIL, in the following equation which the low load period box load, BL̇L(tj), plus defrost heat contribution, Q̇DF (only applicable for freezers), is less than the minimum net capacity, q̇ssk=1(tj), by solving the following equation for tIL:
BL̇L (tIL) + Q̇DF = q̇ssk=1(tIL)
For tj < tIL:
Where Ėcu,off(tj), in W, is the condensing unit off-mode power consumption for temperature tj, determined as indicated in section 3.4.3.3 of this appendix.
For tj ≥ tIL:
3.4.3.6 Calculate average power input during the high load period as follows.
Calculate the temperature, tIH, in the following equation which the high load period box load, BL̇H(tj), plus defrost heat contribution, Q̇DF (only applicable for freezers), is less than the minimum net capacity, q̇ssk=1(tj) , by solving the following equation for tIH:
BL̇H (tIH) + Q̇DF = q̇ssk=1(tIH)
Calculate the temperature, tIIH, in the following equation which the high load period box load BL̇H(tj) plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the maximum net capacity q̇ssk=2(tj), by solving the following equation for tIIH:
BL̇H (tIIH) + Q̇DF = q̇ssk=1(tIIH)
For tj < tIH:
For tIH ≤ tj < tIIH:
For tIIH ≤ tj:
ĖH (tj) = (Ėssk=2(tj) + ĖFcomp,on)
3.4.3.7 Calculate the AWEF2 as follows:
3.4.4 Variable-Capacity or Multistage Condensing Units Tested Alone, Outdoor
3.4.4.1 Unit Cooler Power
Calculate maximum-capacity unit cooler power during the compressor on period ĖFcomp,on as described in section 3.4.1.1 of this appendix.
Calculate unit cooler power during the compressor off period ĖFcomp,on, in Watts, as 20 percent of the maximum-capacity unit cooler power during the compressor on period.
3.4.4.2 Defrost
Calculate Defrost parameters as described in section 3.4.1.2 of this appendix.
3.4.4.3 Condensing Unit Off-Cycle Power
Calculate Condensing Unit Off-Cycle Power for temperature, tj, as described in section 3.4.3.3 of this appendix.
3.4.4.4 Net Capacity and Condensing Unit Power Input
Calculate steady-state maximum net capacity, q̇ssk=2(tj), intermediate net capacity, q̇ssk=i(tj) , and minimum net capacity, q̇ssk=1(tj), and corresponding condensing unit power input levels Ėssk=2(tj), Ėssk=i(tj), Ėssk=1(tj) and as a function of outdoor temperature, tj, as follows:
If tj ≤ 59 °F:
If 59 °F < tj:
Where:
The capacity level k can equal 1, i, or 2;
Q̇gross,Xk=2, Q̇gross,Xk=i and Q̇gross,Xk=1 represent gross refrigeration capacity at maximum, intermediate, and minimum capacity, respectively, for test condition X, which can take on values A, B, or C;
Ėss,Xk=2 and Ėss,Xk=1 represent condensing unit power input at maximum and minimum capacity, respectively for test condition X; and
Kf is the unit cooler power coefficient for intermediate capacity operation, set equal to 0.2 to represent low-speed fan operation if the Duty Cycle for a Digital Compressor, the Speed Ratio for a Variable-Speed Compressor, or the Displacement Ratio for a Multi-Stage Compressor at Intermediate Capacity is 65% or less, and otherwise set equal to 1.0.
3.4.4.5 Calculate average power input during the low load period as follows.
Calculate the temperature, tIL, in the following equation which the low load period box load BL̇L(tj) plus defrost heat contribution, Q̇DF (only applicable for freezers), is less than the minimum net capacity, q̇ssk=1(tj), by solving the following equation for tIL:
BL̇L (tIL) + Q̇DF = q̇ssk=1(tIL)
Calculate the temperature, tVL, in the following equation which the low load period box load, BL̇L(tj), plus defrost heat contribution, Q̇DF (only applicable for freezers), is less than the intermediate net capacity, q̇ssk=i(tj), by solving the following equation for tVL:
BL̇L (tVL) + Q̇DF = q̇ssk=i(tVL)
For tj < tIL:
Where, Ėcu,off(tj) in W, is the condensing unit off-mode power consumption for temperature, tj, determined as indicated in section 3.4.3.3 of this appendix.
For tIL ≤ tj < tVL:
For tVL ≤ tj:
Where:
EERk=2(tj) is the minimum-capacity energy efficiency ratio, equal to q̇ssk=1(tj) divided by Ėssk=1(tj) + 0.2 ĖFcomp,on;
EERk=i(tj) is the intermediate-capacity energy efficiency ratio, equal to q̇ssk=i(tj) divided by Ėssk=i(tj) + Kf · ĖFcomp,on; and
EERk=2(tj) is the maximum-capacity energy efficiency ratio, equal to q̇ssk=2(tj) divided by Ėssk=2(tj) + ĖFcomp,on
3.4.4.6 Calculate average power input during the high load period as follows.
Calculate the temperature tVH in the following equation which the high load period box load BL̇H(tj) plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the intermediate net capacity q̇ssk=i(tj), by solving the following equation for tVH:
BL̇H (tVH) + Q̇DF = q̇ssk=i(tVH)
Calculate the temperature tIIH in the following equation which the high load period box load BL̇H(tj) plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the maximum net capacity q̇ssk=2(tj), by solving the following equation for tIIH:
BL̇H (tIIH) + Q̇DF = q̇ssk=2(tIIH)
For tj < tVH:
For tVH ≤ tj < tIIH:
For tIIH ≤ tj:
ĖH (tj) = (Ėssk=2 (tj) + ĖFcomp,on)
3.4.4.7 Calculate the AWEF2 as follows:
3.4.5 Two-Capacity Indoor Matched Pairs or Single-Packaged Refrigeration Systems Other Than High-Temperature
3.4.5.1 Defrost
For freezer refrigeration systems, defrost heat contribution Q̇DF in Btu/h and the defrost average power consumption ḊF in W shall be as measured in accordance with section C10.2.1 of Appendix C of AHRI 1250-2020.
3.4.5.2 Calculate average power input during the low load period as follows.
If the low load period box load BL̇L plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the minimum net capacity q̇ssk=1:
Where:
q̇ssk=1 and Ėssk=1 are the steady state refrigeration system minimum net capacity, in Btu/h, and associated refrigeration system power input, in W, respectively, for minimum-capacity operation, measured as described in AHRI 1250-2020.
ĖFcomp,off and Ėcu,off, both in W, are the unit cooler and condensing unit, respectively, off-mode power consumption, measured as described in section C3.5 of AHRI 1250-2020.
If the low load period box load BL̇L plus defrost heat contribution Q̇DF (only applicable for freezers) is greater than the minimum net capacity q̇ssk=1:
Where q̇ssk=2 and Ėssk=2 are the steady state refrigeration system maximum net capacity, in Btu/h, and associated refrigeration system power input, in W, respectively, for maximum-capacity operation, measured as described in AHRI 1250-2020.
3.4.5.3 Calculate average power input during the high load period as follows.
3.4.5.4 Calculate the AWEF2 as follows:
3.4.6 Variable-Capacity or Multistage Indoor Matched Pairs or Single-Packaged Refrigeration Systems Other Than High-Temperature
3.4.6.1 Defrost
For freezer refrigeration systems, defrost heat contribution Q̇DF in Btu/h and the defrost average power consumption ḊF in W shall be as measured in accordance with section C10.2.1 of Appendix C of AHRI 1250-2020.
3.4.6.2 Calculate average power input during the low load period as follows.
If the low load period box load BL̇L plus defrost heat contribution Q̇DF (only applicable for freezers) is less than the minimum net capacity q̇ssk=1:
Where:
q̇ssk=1 and Ėssk=1 are the steady state refrigeration system minimum net capacity, in Btu/h, and associated refrigeration system power input, in W, respectively, for minimum-capacity operation, measured as described in AHRI 1250-2020; and
ĖFcomp,off and Ėcu,off, both in W, are the unit cooler and condensing unit, respectively, off-mode power consumption, measured as described in section C3.5 of AHRI 1250-2020.
If the low load period box load BL̇L plus defrost heat contribution Q̇DF (only applicable for freezers) is greater than the minimum net capacity and less than the intermediate net capacity q̇ssk=i:
Where:
EERk=1 is the minimum-capacity energy efficiency ratio, equal to q̇ssk=1divided by Ėssk=1;
q̇ssk=i and Ėssk=i are the steady state refrigeration system intermediate net capacity, in Btu/h, and associated refrigeration system power input, in W, respectively, for intermediate-capacity operation, measured as described in AHRI 1250-2020.
EERk=i is the intermediate-capacity energy efficiency ratio, equal to q̇ssk=i divided by Ėssk=i.
3.4.6.3 Calculate average power input during the high load period as follows.
If the high load period box load BL̇H plus defrost heat contribution Q̇DF (only applicable for freezers) is greater than the minimum net capacity q̇ssk=1 and less than the intermediate net capacity q̇ssk=i:
If the high load period box load BL̇H plus defrost heat contribution Q̇DF (only applicable for freezers) is greater than the intermediate net capacity q̇ssk=i and less than the maximum net capacity q̇ssk=2:
Where:
q̇ssk=2 and Ėssk=2 are the steady state refrigeration system maximum net capacity, in Btu/h, and associated refrigeration system power input, in W, respectively, for maximum-capacity operation, measured as described in AHRI 1250-2020; and
EERk=2 is the maximum-capacity energy efficiency ratio, equal to q̇ssk=2 divided by Ėssk=2.
3.4.6.4 Calculate the AWEF2 as follows.
3.4.7 Variable-Capacity or Multistage Outdoor Matched Pairs or Single-Packaged Refrigeration Systems Other Than High-Temperature
Calculate AWEF2 as described in section 7.6 of AHRI 1250-2020, with the following revisions.
3.4.7.1 Condensing Unit Off-Cycle Power
Calculate condensing unit off-cycle power for temperature tj as indicated in section 3.4.3.3 of this appendix. Replace the constant value ĖCU,off in Equations 55 and 70 of AHRI 1250-2020 with the values ĖCU,off(tj), which vary with outdoor temperature tj.
3.4.7.2 Unit Cooler Off-Cycle Power
Set unit cooler Off-Cycle power ĖFcomp,off equal to the average of the unit cooler off-cycle power measurements made for test conditions A, B, and C.
3.4.7.3 Average Power During the Low Load Period
Calculate average power for intermediate-capacity compressor operation during the low load period Ėss,Lk=v(tj) as described in section 7.6 of AHRI 1250-2020, except that, instead of calculating intermediate-capacity compressor EER using Equation 77 of AHRI 1250-2020, calculate EER as follows.
For tj < tVL:
For tVL ≤ tj:
Where:
EERk=1(tj) is the minimum-capacity energy efficiency ratio, equal to q̇ssk=1(tj) divided by Ėssk=1(tj);
EERk=i(tj) is the intermediate-capacity energy efficiency ratio, equal to q̇ssk=i (tj) divided by Ėssk=i(tj); and
EERk=2(tj) is the maximum-capacity energy efficiency ratio, equal to q̇ssk=2(tj) divided by Ėssk=2(tj)
3.4.7.4 Average Power During the High Load Period
Calculate average power for intermediate-capacity compressor operation during the high load period Ėss,Hk=v(tj) as described in section 7.6 of AHRI 1250-2020, except that, instead of calculating intermediate-capacity compressor EER using Equation 61 of AHRI 1250-2020, calculate EER as follows:
For tj < tVH:
For tVH ≤ tj:
3.4.8 Two-Capacity Outdoor Matched Pairs or Single-Packaged Refrigeration Systems Other Than High-Temperature
Calculate AWEF2 as described in section 7.5 of AHRI 1250-2020, with the following revisions for Condensing Unit Off-Cycle Power and Unit Cooler Off-Cycle Power. Calculate condensing unit off-cycle power for temperature tj as indicated in section 3.4.3.3 of this appendix. Replace the constant value ĖCU,off in Equations 13 and 29 of AHRI 1250-2020 with the values ĖCU,off(tj), which vary with outdoor temperature tj. Set unit cooler Off-Cycle power ĖFcomp,off equal to the average of the unit cooler off-cycle power measurements made for test conditions A, B, and C.
3.4.9 Single-Capacity Outdoor Matched Pairs or Single-Packaged Refrigeration Systems Other Than High-Temperature
Calculate AWEF2 as described in section 7.4 of AHRI 1250-2020, with the following revision for Condensing Unit Off-Cycle Power and Unit Cooler Off-cycle Power. Calculate condensing unit off-cycle power for temperature tj as indicated in section 3.4.3.3 of this appendix. Replace the constant value ĖCU,off in Equations 13 of AHRI 1250-2020 with the values ĖCU,off(tj), which vary with outdoor temperature tj. Set unit cooler Off-Cycle power ĖFcomp,off equal to the average of the unit cooler off-cycle power measurements made for test conditions A, B, and C.
3.4.10 Single-Capacity Condensing Units, Outdoor
Calculate AWEF2 as described in section 7.9 of AHRI 1250-2020, with the following revision for Condensing Unit Off-Cycle Power. Calculate condensing unit off-cycle power for temperature tj as indicated in section 3.4.3.3 of this appendix rather than as indicated in Equations 157, 159, 202, and 204 of AHRI 1250-2020.
3.4.11 High-Temperature Matched Pairs or Single-Packaged Refrigeration Systems, Indoor
3.4.11.1 Calculate Load Factor LF as follows:
Where:
ḂL , in Btu/h is the non-equipment-related box load calculated as described in section 3.3.3 of this appendix;
ĖFcomp,off , in W, is the unit cooler off-cycle power consumption, equal to 0.1 times the unit cooler on-cycle power consumption; and
q̇ss,A, in Btu/h is the measured net capacity for test condition A.
3.4.11.2 Calculate the AWEF2 as follows:
Where:
Ėss,A , in W, is the measured system power input for test condition A; and
Ėcu,off , in W, is the condensing unit off-cycle power consumption, measured as described in section C3.5 of AHRI 1250-2020.
3.4.12 High-Temperature Matched Pairs or Single-Packaged Refrigeration Systems, Outdoor
3.4.12.1 Calculate Load Factor LF(tj) for outdoor temperature tj as follows:
Where:
ḂL , in Btu/h, is the non-equipment-related box load calculated as described in section 3.3.3 of this appendix;
ĖFcomp,off , in W, is the unit cooler off-cycle power consumption, equal to 0.1 times the unit cooler on-cycle power consumption; and
q̇ss(tj), in Btu/h, is the net capacity for outdoor temperature tj, calculated as described in section 7.4.2 of AHRI 1250-2020.
3.4.12.2 Calculate the AWEF2 as follows:
Where:
Ėss (tj, in W, is the system power input for temperature tj, calculated as described in section 7.4.2 of AHRI 1250-2020;
Ėcu,off (tj, in W, is the condensing unit off-cycle power consumption for temperature tj, determined as indicated in section 3.4.3.3 of this appendix; and
nj are the hours for temperature bin j.
3.4.13 High-Temperature Unit Coolers Tested Alone
3.4.13.1 Calculate Refrigeration System Power Input as follows:
Where:
q̇mix,evap, in W, is the net evaporator capacity, measured as described in AHRI 1250-2020;
ĖFcomp,on , in W, is the unit cooler on-cycle power consumption; and
EER, in W, equals
3.4.13.2 Calculate the load factor LF as follows:
Where:
ḂL , in Btu/h, is the non-equipment-related box load calculated as described in section 3.3.3 of this appendix; and
ĖFcomp,off , in W, is the unit cooler off-cycle power consumption, equal to 0.1 times the unit cooler on-cycle power consumption.
3.4.13.3 Calculate AWEF2 as follows:
3.4.14 CO2 Unit Coolers Tested Alone
Calculate AWEF2 for CO2 Unit Coolers Tested Alone using the calculations specified in in section 7.8 of AHRI 1250-2020 for calculation of AWEF2 for Unit Cooler Tested Alone.
3.5 Test Method
Test the Refrigeration System in accordance with AHRI 1250-2020 to determine refrigeration capacity and power input for the specified test conditions, with revisions and additions as described in this section.
3.5.1 Chamber Conditioning Using the Unit Under Test
In Appendix C, section C5.2.2 of AHRI 1250-2020, for applicable system configurations (matched pairs, single-packaged refrigeration systems, and standalone unit coolers), the unit under test may be used to aid in achieving the required test chamber conditions prior to beginning any steady state test. However, the unit under test must be inspected and confirmed to be free from frost before initiating steady state testing.
3.5.2 General Modification: Methods of Testing
3.5.2.1 Refrigerant Temperature Measurements
When testing a condensing unit alone, measure refrigerant liquid temperature leaving the condensing unit, and the refrigerant vapor temperature entering the condensing unit as required in section C7.5.1.1.2 of Appendix C of AHRI 1250-2020 using the same measurement approach specified for the unit cooler in section C3.1.3 of Appendix C of AHRI 1250-2020. In all cases in which thermometer wells or immersed sheathed sensors are prescribed, if the refrigerant tube outer diameter is less than 1⁄2 inch, the refrigerant temperature may be measured using the average of two temperature measuring instruments with a minimum accuracy of ±0.5 °F placed on opposite sides of the refrigerant tube surface—resulting in a total of up to 8 temperature measurement devices used for the DX Dual Instrumentation method. In this case, the refrigerant tube shall be insulated with 1-inch thick insulation from a point 6 inches upstream of the measurement location to a point 6 inches downstream of the measurement location. Also, to comply with this requirement, the unit cooler/evaporator entering measurement location may be moved to a location 6 inches upstream of the expansion device and, when testing a condensing unit alone, the entering and leaving measurement locations may be moved to locations 6 inches from the respective service valves.
3.5.2.2 Mass Flow Meter Location
When using the DX Dual Instrumentation test method of AHRI 1250-2020, applicable for unit coolers, dedicated condensing units, and matched pairs, the second mass flow meter may be installed in the suction line as shown in Figure C1 of AHRI 1250-2020.
3.5.2.3 Subcooling at Refrigerant Mass Flow Meter
In section C3.4.5 of Appendix C of AHRI 1250-2020, when verifying subcooling at the mass flow meters, only the sight glass and a temperature sensor located on the tube surface under the insulation are required. Subcooling shall be verified to be within the 3 °F requirement downstream of flow meters located in the same chamber as a condensing unit under test and upstream of flow meters located in the same chamber as a unit cooler under test, rather than always downstream as indicated in AHRI 1250-2009, section C3.4.5. If the subcooling is less than 3 °F when testing a unit cooler, dedicated condensing unit, or matched pair (not a single-packaged system), cool the line between the condensing unit outlet and this location to achieve the required subcooling. When providing such cooling while testing a matched pair (a) set up the line-cooling system and also set up apparatus to heat the liquid line between the mass flow meters and the unit cooler, (b) when the system has achieved steady state without activation of the heating and cooling systems, measure the liquid temperature entering the expansion valve for a period of at least 30 minutes, (c) activate the cooling system to provide the required subcooling at the mass flow meters, (d) if necessary, apply heat such that the temperature entering the expansion valve is within 0.5 °F of the temperature measured during step (b), and (e) proceed with measurements once condition (d) has been verified.
3.5.2.4 Installation Instructions
Manufacturer installation instructions or installation instructions described in this section refer to the instructions that come packaged with or appear on the labels applied to the unit. This does not include online manuals.
Installation Instruction Hierarchy: If a given installation instruction provided on the label(s) applied to the unit conflicts with the installation instructions that are shipped with the unit, the label takes precedence. For testing of matched pairs, the installation instructions for the dedicated condensing unit shall take precedence. Setup shall be in accordance with the field installation instructions (laboratory installation instructions shall not be used). Achieving test conditions shall always take precedence over installation instructions.
3.5.2.5. Refrigerant Charging and Adjustment of Superheat and Subcooling.
All dedicated condensing systems (dedicated condensing units tested alone, matched pairs, and single packaged dedicated systems) that use flooding of the condenser for head pressure control during low-ambient-temperature conditions shall be charged, and superheat and/or subcooling shall be set, at Refrigeration C test conditions unless otherwise specified in the installation instructions.
If after being charged at Refrigeration C condition the unit under test does not operate at the Refrigeration A condition due to high pressure cut out, refrigerant shall be removed in increments of 4 ounces or 5 percent of the test unit's receiver capacity, whichever quantity is larger, until the unit operates at the Refrigeration A condition. All tests shall be run at this final refrigerant charge. If less than 0 °F of subcooling is measured for the refrigerant leaving the condensing unit when testing at B or C condition, calculate the refrigerant-enthalpy-based capacity (i.e., when using the DX dual instrumentation, the DX calibrated box, or single-packaged unit refrigerant enthalpy method) assuming that the refrigerant is at saturated liquid conditions at the condensing unit exit.
All dedicated condensing systems that do not use a flooded condenser design shall be charged at Refrigeration A test conditions unless otherwise specified in the installation instructions.
If the installation instructions give a specified range for superheat, sub-cooling, or refrigerant pressure, the average of the range shall be used as the refrigerant charging parameter target and the test condition tolerance shall be ±50 percent of the range. Perform charging of near-azeotropic and zeotropic refrigerants only with refrigerant in the liquid state. Once the correct refrigerant charge is determined, all tests shall run until completion without further modification.
3.5.2.5.1. When charging or adjusting superheat/subcooling, use all pertinent instructions contained in the installation instructions to achieve charging parameters within the tolerances. However, in the event of conflicting charging information between installation instructions, follow the installation instruction hierarchy listed in section 3.5.2.4. Conflicting information is defined as multiple conditions given for charge adjustment where all conditions specified cannot be met. In the event of conflicting information within the same set of charging instructions (e.g., the installation instructions shipped with the dedicated condensing unit), follow the hierarchy in Table 19 for priority. Unless the installation instructions specify a different charging tolerance, the tolerances identified in table 19 of this appendix shall be used.
| Priority | Fixed orifice | Expansion Valve | ||
|---|---|---|---|---|
| Parameter with installation
instruction target |
Tolerance | Parameter with installation
instruction target |
Tolerance | |
| 1 | Superheat | ±2.0 °F | Subcooling | 10% of the Target Value; No less than ±0.5 °F, No more than ±2.0 °F |
| 2 | High Side Pressure or Saturation Temperature* | ±4.0 psi or ±1.0 °F | High Side Pressure or Saturation Temperature* | ±4.0 psi or
±1.0 °F |
| 3 | Low Side Pressure or Saturation Temperature* | ±2.0 psi or ±0.8 °F | Superheat | ±2.0 °F |
| 4 | Low Side Temperature | ±2.0 °F | Low Side Pressure or Saturation Temperature * | ±2.0 psi or
±0.8 °F |
| 5 | High Side Temperature | ±2.0 °F | Approach Temperature | ±1.0 °F |
| 6 | Charge Weight | ±2.0 oz | Charge Weight | 0.5% or 1.0 oz, whichever is greater |
| * Saturation temperature can refer to either bubble or dew point calculated based on a measured pressure, or a coil temperature measurement, as specified by the installation instructions. | ||||
3.5.2.5.2. Dedicated Condensing Unit.
If the Dedicated Condensing Unit includes a receiver and the subcooling target leaving the condensing unit provided in installation instructions cannot be met without fully filling the receiver, the subcooling target shall be ignored. Likewise, if the Dedicated Condensing unit does not include a receiver and the subcooling target leaving the condensing unit cannot be met without the unit cycling off on high pressure, the subcooling target can be ignored. Also, if no instructions for charging or for setting subcooling leaving the condensing unit are provided in the installation instructions, the refrigeration system shall be set up with a charge quantity and/or exit subcooling such that the unit operates during testing without shutdown (e.g., on a high-pressure switch) and operation of the unit is otherwise consistent with the requirements of the test procedure of this appendix and the installation instructions.
3.5.2.5.3. Unit Cooler. Use the shipped expansion device for testing. Otherwise, use the expansion device specified in the installation instructions. If the installation instructions specify multiple options for the expansion device, any specified expansion device may be used. The supplied expansion device shall be adjusted until either the superheat target is met, or the device reaches the end of its adjustable range. In the event the device reaches the end of its adjustable range and the super heat target is not met, test with the adjustment at the end of its range providing the closest match to the superheat target, and the test condition tolerance for super heat target shall be ignored. The measured superheat is not subject to a test operating tolerance. However, if the evaporator exit condition is used to determine capacity using the DX dual instrumentation method or the refrigerant enthalpy method, individual superheat value measurements may not be equal to or less than zero. If this occurs, or if the operating tolerances of measurements affected by expansion device fluctuation are exceeded, the expansion device shall be replaced, operated at an average superheat value higher than the target, or both, in order to avoid individual superheat value measurements less than zero and/or to meet the required operating tolerances.
3.5.2.5.4. Single-Packaged Unit. Unless otherwise directed by the installation instructions, install one or more refrigerant line pressure gauges during the setup of the unit, located depending on the parameters used to verify or set charge, as described in this section:
3.5.2.5.4.1. Install a pressure gauge in the liquid line if charging is on the basis of subcooling, or high side pressure or corresponding saturation or dew point temperature.
3.5.2.5.4.2. Install a pressure gauge in the suction line if charging is on the basis of superheat, or low side pressure or corresponding saturation or dew point temperature. Install this gauge as close to the evaporator as allowable by the installation instructions and the physical constraints of the unit. Use methods for installing pressure gauge(s) at the required location(s) as indicated in the installation instructions if specified.
3.5.2.5.4.3. If the installation instructions indicate that refrigerant line pressure gauges should not be installed and the unit fails to operate due to high-pressure or low-pressure compressor cut off, then a charging port shall be installed, and the unit shall be evacuated of refrigerant and charged to the nameplate charge.
3.5.2.6 Ducted Units
For systems with ducted evaporator air, or that can be installed with or without ducted evaporator air: Connect ductwork on both the inlet and outlet connections and determine external static pressure (ESP) as described in sections 6.4 and 6.5 of ANSI/ASHRAE 37. Use pressure measurement instrumentation as described in section 5.3.2 of ANSI/ASHRAE 37. Test at the fan speed specified in the installation instructions—if there is more than one fan speed setting and the installation instructions do not specify which speed to use, test at the highest speed. Conduct tests with the ESP equal to 50% of the maximum ESP allowed in the installation instructions, within a tolerance of −0.00/+0.05 inches of water column. If the installation instructions do not provide the maximum ESP, the ESP shall be set for testing such that the air volume rate is 2⁄3 of the air volume rate measured when the ESP is 0.00 inches of water column within a tolerance of −0.00/+0.05 inches of water column.
If testing using either the indoor or outdoor air enthalpy method to measure the air volume rate, adjust the airflow measurement apparatus fan to set the external static pressure—otherwise, set the external static pressure by symmetrically restricting the outlet of the test duct. In case of conflict, these requirements for setting airflow take precedence over airflow values specified in manufacturer installation instructions or product literature.
3.5.2.7. Two-Speed or Multiple-Speed Evaporator Fans. Two-Speed or Multiple-Speed evaporator fans shall be considered to meet the qualifying control requirements of section C4.2 of Appendix C of AHRI 1250-2020 for measuring off-cycle fan energy if they use a fan speed no less than 50% of the speed used in the maximum capacity tests.
3.5.2.8. Defrost
Use section C10.2.1 of Appendix C of AHRI 1250-2020 for defrost testing. The Test Room Conditioning Equipment requirement of section C10.2.1.1 of Appendix C of AHRI 1250-2020 does not apply.
3.5.2.8.1 Adaptive Defrost
When testing to certify compliance to the energy conservation standards, use NDF = 4, as instructed in section C10.2.1.7 or C10.2.2.1 of AHRI 1250-2020. When determining the represented value of the calculated benefit for the inclusion of adaptive defrost, use NDF = 2.5, as instructed in section C10.2.1.7 or C10.2.2.1 of AHRI 1250-2020.
3.5.2.8.2 Hot Gas Defrost
When testing to certify compliance to the energy conservation standards, remove the hot gas defrost mechanical components and disconnect all such components from electrical power. Test the units as if they are electric defrost units, but do not conduct the defrost tests described in section C10.2.1 of AHRI 1250-2020. Use the defrost heat and power consumption values as described in section C10.2.2 of AHRI 1250-2020 for the AWEF2 calculations.
3.5.2.9 Dedicated condensing units that are not matched for testing and are not single-packaged dedicated systems.
The temperature measurement requirements of sections C3.1.3 and C4.1.3.1 appendix C of AHRI 1250-2020 shall apply only to the condensing unit exit rather than to the unit cooler inlet and outlet, and they shall be applied for two measurements when using the DX Dual Instrumentation test method.
3.5.2.10. Single-packaged dedicated systems
Use the test method in section C9 of appendix C of AHRI 1250-2020 (including the applicable provisions of ASHRAE 16-2016, ASHRAE 23.1-2010, ASHRAE 37-2009, and ASHRAE 41.6-2014, as referenced in section C9.1 of AHRI 1250-2020) as the method of test for single-packaged dedicated systems, with modifications as described in this section. Use two test methods listed in table 20 of this appendix to calculate the net capacity and power consumption. The test method listed with a lower “Hierarchy Number” and that has “Primary” as an allowable use in table 20 of this appendix shall be considered the primary measurement and used as the net capacity.
| Hierarchy number | Method of test | Test hierarchy |
|---|---|---|
| 1 | Balanced Ambient Indoor Calorimeter | Primary. |
| 2 | Indoor Air Enthalpy | Primary or Secondary. |
| 3 | Indoor Room Calorimeter | Primary or Secondary. |
| 4 | Calibrated Box | Primary or Secondary. |
| 5 | Balanced Ambient Outdoor Calorimeter | Secondary. |
| 6 | Outdoor Air Enthalpy | Secondary. |
| 7 | Outdoor Room Calorimeter | Secondary. |
| 8 | Single-Packaged Refrigerant Enthalpy 1 | Secondary. |
| 9 | Compressor Calibration | Secondary. |
| Notes: | ||
| 1 See description of the single-packaged refrigerant enthalpy method in section 3.5.2.10.1 of this appendix. | ||
3.5.2.10.1 Single-Packaged Refrigerant Enthalpy Method
The single-packaged refrigerant enthalpy method shall follow the test procedure of the DX Calibrated Box method in AHRI 1250-2020, appendix C, section C8 for refrigerant-side measurements with the following modifications:
3.5.2.10.1.1 Air-side measurements shall follow the requirements of the primary single-packaged method listed in table 20 of this appendix. The air-side measurements and refrigerant-side measurements shall be collected over the same intervals.
3.5.2.10.1.2 A preliminary test at Test Rating Condition A is required using the primary method prior to any modification necessary to install the refrigerant-side measuring instruments. Install surface mount temperature sensors on the evaporator and condenser coils at locations not affected by liquid subcooling or vapor superheat (i.e., near the midpoint of the coil at a return bend), entering and leaving the compressor, and entering the expansion device. These temperature sensors shall be included in the regularly recorded data.
3.5.2.10.1.3 After the preliminary test is completed, the refrigerant shall be removed from the equipment and the refrigerant-side measuring instruments shall be installed. The equipment shall then be evacuated and recharged with refrigerant. Once the equipment is operating at Test Condition A, the refrigerant charge shall be adjusted until, as compared to the average values from the preliminary test, the following conditions are achieved:
(a) Each on-coil temperature sensor indicates a reading that is within ±1.0 °F of the measurement in the initial test,
(b) The temperatures of the refrigerant entering and leaving the compressor are within ±4 °F, and
(c) The refrigerant temperature entering the expansion device is within ±1 °F.
3.5.2.10.1.4 Once these conditions have been achieved over an interval of at least 10 minutes, refrigerant charging equipment shall be removed and the official tests shall be conducted.
3.5.2.10.1.5 The lengths of liquid line to be added shall be 5 feet maximum, not including the requisite flow meter. This maximum length applies to each circuit separately.
3.5.2.10.1.6 Use section C9.2 of appendix C of AHRI 1250-2020 for allowable refrigeration capacity heat balance. Calculate the single-packaged refrigerant enthalpy (secondary) method test net capacity
Q̇net,secondary as follows: Q̇net,secondary = Q̇ref-3.412·ĖFcomp,on−Q̇sploss
Where:
Q̇ref is the gross capacity;
ĖFcomp,on is the evaporator compartment on-cycle power, including evaporator fan power; and
Q̇sploss is a duct loss calculation applied to the evaporator compartment of the single-packaged systems, which is calculated as indicated in the following equation.
Q̇sploss = UAcond × (Tevapside − Tcondside) + UAamb × (Tevapside − Tamb)
Where:
UAcond and UAamb are, for the condenser/evaporator partition and the evaporator compartment walls exposed to ambient air, respectively, the product of the overall heat transfer coefficient and surface area of the unit as manufactured, i.e. without external insulation that might have been added during the test. The areas shall be calculated based on measurements, and the thermal resistance values shall be based on insulation thickness and insulation material;
Tevapside is the air temperature in the evaporator compartment—the measured evaporator air inlet temperature may be used;
Tcondside is the air temperature in the condenser compartment—the measured chamber ambient temperature may be used, or a measurement may be made using a temperature sensor placed inside the condenser box at least 6 inches distant from any part of the refrigeration system; and
Tamb is the air temperature outside the single-packaged system.
3.5.2.10.1.7 For multi-circuit single-packaged systems utilizing the single-packaged refrigerant enthalpy method, apply the test method separately for each circuit and sum the separately-calculated refrigerant-side gross refrigeration capacities.
3.5.2.10.2 Calibrated Box Test Procedure
3.5.2.10.2.1 Measurements. Refer to section C3 of AHRI 1250-2020 (including the applicable provisions of ASHRAE 41.1-2013, ASHRAE 41.3-2014, and ASHRAE 41.10-2013, as referenced in section C3 of AHRI 1250-2020) for requirements of air-side and refrigerant-side measurements.
3.5.2.10.2.2 Apparatus setup for Calibrated Box Calibration and Test. Refer to section C5 of AHRI 1250-2020 and section C8 of AHRI 1250-2020 for specific test setup.
3.5.2.10.2.3 The calibrated box shall be installed in a temperature-controlled enclosure in which the temperature can be maintained at a constant level. When using the calibrated box method for Single-Packaged Dedicated Systems, the enclosure air temperature shall be maintained such that the condenser air entering conditions are as specified for the test.
3.5.2.10.2. The temperature-controlled enclosure shall be of a size that will provide clearances of not less than 18 in at all sides, top and bottom, except that clearance of any one surface may be reduced to not less than 5.5 inches.
3.5.2.10.2.5 The heat leakage of the calibrated box shall be noted in the test report.
3.5.2.10.2.6 Refrigerant lines within the calibrated box shall be well insulated to avoid appreciable heat loss or gain.
3.5.2.10.2.7 Instruments for measuring the temperature around the outside of the calibrated box to represent the enclosure temperature Ten shall be located at the center of each wall, ceiling, and floor. Exception: in the case where a clearance around the outside of the calibrated box, as indicated in section 3.5.2.10.2.4 of this appendix, is reduced to less than 18 inches, the number of temperature measuring devices on the outside of that surface shall be increased to six, which shall be treated as a single temperature to be averaged with the temperature of each of the other five surfaces. The six temperature measuring instruments shall be located at the center of six rectangular sections of equal area. If the refrigeration system is mounted at the location that would cover the center of the face on which it is mounted, up to four temperature measurements shall be used on that face to represent its temperature. Each sensor shall be aligned with the center of the face's nearest outer edge and centered on the distance between that edge and the single-packaged unit (this is illustrated in figure C5 of this section when using surface temperature sensors), and they shall be treated as a single temperature to be averaged with the temperature of each of the other five surfaces. However, any of these sensors shall be omitted if either
(a) the distance between the outer edge and the single-packaged unit is less than one foot or
(b) if the sensor location would be within two feet of any of the foot square surfaces discussed in section 3.5.2.10.2.8 of this appendix representing a warm discharge air impingement area. In this case, the remaining sensors shall be used to represent the average temperature for the surface.
3.5.2.10.2.8 One of the following two approaches shall be used for the box external temperature measurement. Box calibration and system capacity measurement shall both be done using the same one of these approaches. 1: Air temperature sensors. Each temperature sensor shall be at a distance of 6 inches from the calibrated box. If the clearance from a surface of the box (allowed for one surface only) is less than 12 inches, the temperature measuring instruments shall be located midway between the outer wall of the calibrated box and the adjacent surface. 2: Surface temperature sensors. Surface temperature sensors shall be mounted on the calibrated box surfaces to represent the enclosure temperature, Ten.
3.5.2.10.2.9 Additional surface temperature sensors may be used to measure external hot spots during refrigeration system testing. If this is done, two temperature sensors shall be used to measure the average temperature of the calibrated box surface covered by the condensing section—they shall be located centered on equal-area rectangles comprising the covered calibrated box surface whose common sides span the short dimension of this surface. Additional surface temperature sensors may be used to measure box surfaces on which warm condenser discharge air impinges. A pattern of square surfaces measuring one foot square shall be mapped out to represent the hot spot upon which the warm condenser air impinges. One temperature sensor shall be used to measure surface temperature at the center of each square (see figure C5 of this section). A drawing showing this pattern and identifying the surface temperature sensors shall be provided in the test report. The average surface temperature of the overall calibrated box outer surface during testing shall be calculated as follows.
Where:
Ai is the surface area of the ith of the six calibrated box surfaces;
Ti is the average temperature measured for the ith surface;
Aj is half of the surface area of the calibrated box covered by the condensing section;
T'j is the jth of the two temperature measurements underneath the condensing section;
T1 is the average temperature of the four or fewer measurements representing the temperature of the face on which the single-packaged system is mounted, prior to adjustments associated with hot spots based on measurements Tj and/or Tk;
Ak is the area of the kth of n 1-square-foot surfaces used to measure the condenser discharge impingement area hot spot; and,
T” k is the kth of the n temperature measurements of the condenser discharge impingement area hot spot.
Figure C5: Illustration of Layout of Surface Temperature Sensors on Face of Calibrated Box on which Single-Packaged Dedicated System is Mounted when Using Section 3.5.2.10.2.7 of Appendix C to this Part.3.5.2.10.2.10 Heating means inside the calibrated box shall be shielded or installed in a manner to avoid radiation to the Single-Packaged Dedicated System, the temperature measuring instruments, and to the walls of the box. The heating means shall be constructed to avoid stratification of temperature, and suitable means shall be provided for distributing the temperature uniformly.
3.5.2.10.2.11 The average air dry-bulb temperature in the calibrated box during Single-Packaged Dedicated System tests and calibrated box heat leakage tests shall be the average of eight temperatures measured at the corners of the box at a distance of 2 inches to 4 inches from the walls. The instruments shall be shielded from any cold or warm surfaces except that they shall not be shielded from the adjacent walls of the box. The Single-Packaged Dedicated System under test shall be mounted such that the temperature instruments are not in the direct air stream from the discharge of the Single-Packaged Dedicated System.
3.5.2.10.2.12 Calibration of the Calibrated Box. Calibration of the Calibrated Box shall occur prior to installation of the Single-Packaged Dedicated System. This shall be done either
(a) prior to cutting the opening needed to install the Single-Packaged Dedicated System, or
(b) with an insulating panel with the same thickness and thermal resistance as the box wall installed in the opening intended for the Single-Packaged Dedicated System installation. Care shall be taken to avoid thermal shorts in the location of the opening either during calibration or during subsequent installation of the Single-Packaged Dedicated System. A calibration test shall be made for air movements comparable to those expected for Single-Packaged Dedicated System capacity measurement, i.e., with air volume flow rate within 10 percent of the air volume flow rate of the Single-Packaged Dedicated System evaporator.
3.5.2.10.2.13 The heat input shall be adjusted to maintain an average box temperature not less than 25.0 °F above the test enclosure temperature.
3.5.2.10.2.14 The average dry-bulb temperature inside the calibrated box shall not vary more than 1.0 °F over the course of the calibration test.
3.5.2.10.2.15 A calibration test shall be the average of 11 consecutive hourly readings when the box has reached a steady-state temperature condition.
3.5.2.10.2.16 The box temperature shall be the average of all readings after a steady-state temperature condition has been reached.
3.5.2.10.2.17 The calibrated box has reached a steady-state temperature condition when: The average box temperature is not less than 25 °F above the test enclosure temperature. Temperature variations do not exceed 5.0 °F between temperature measuring stations. Temperatures do not vary by more than 2 °F at any one temperature- measuring station.
3.5.2.10.2.18 Data to be Measured and Recorded. Refer to Table C5 in section C6.2 of AHRI 1250-2020 for the required data that need to measured and recorded.
3.5.2.10.2.19 Refrigeration Capacity Calculation.
The heat leakage coefficient of the calibrated box is calculated by
For each Dry Rating Condition, calculate the Net Capacity:
q̇ss = Kcb (Ten−Tcb) + 3.412 × Ėc
3.5.2.10.3 Detachable single-packaged systems shall be tested as single-packaged dedicated refrigeration systems.
3.5.2.11 Variable-Capacity and Multiple-Capacity Dedicated Condensing Refrigeration Systems
3.5.2.11.1 Manufacturer-Provided Equipment Overrides
Where needed, the manufacturer must provide a means for overriding the controls of the test unit so that the compressor(s) operates at the specified speed or capacity and the indoor blower operates at the speed consistent with the compressor operating level as would occur without override.
3.5.2.11.2 Compressor Operating Levels
For variable-capacity and multiple-capacity compressor systems, the minimum capacity for testing shall be the minimum capacity that the system control would operate the compressor in normal operation. Likewise, the maximum capacity for testing shall be the maximum capacity that the system control would operate the compressor in normal operation. For variable-speed compressor systems, the intermediate speed for testing shall be the average of the minimum and maximum speeds. For digital compressor systems, the intermediate duty cycle shall be the average of the minimum and maximum duty cycles. For multiple-capacity compressor systems with three capacity levels, the intermediate operating level for testing shall be the middle capacity level. For multiple-capacity compressor systems with more than three capacity levels, the intermediate operating level for testing shall be the level whose displacement ratio is closest to the average of the maximum and minimum displacement ratios.
3.5.2.11.3 Refrigeration Systems with Digital Compressor(s)
Use the test methods described in section 3.5.2.10.1 of this appendix as the secondary method of test for refrigeration systems with digital compressor(s) with modifications as described in this section. The Test Operating tolerance for refrigerant mass flow rate and suction pressure in Table 2 of AHRI 1250-2020 shall be ignored. Temperature and pressure measurements used to calculate shall be recorded at a frequency of once per second or faster and based on average values measured over the 30-minute test period.
3.5.2.11.3.1 For Matched pair (not including single-packaged systems) and Dedicated Condensing Unit refrigeration systems, the preliminary test in sections 3.5.2.10.1.2 and 3.5.2.10.1.3 of this appendix is not required. The liquid line and suction line shall be 25 feet ± 3 inches, not including the requisite flow meters. Also, the term in the equation to calculate net capacity shall be set equal to zero.
3.5.2.11.3.2 For Dedicated Condensing Unit refrigeration systems, the primary capacity measurement method shall be balanced ambient outdoor calorimeter, outdoor air enthalpy, or outdoor room calorimeter.
[88 FR 28843, May 4, 2023, as amended at 88 FR 73217, Oct. 25, 2023; 90 FR 6795, Jan. 21, 2025]
74 FR 12075, Mar. 23, 2009, unless otherwise noted.
This subpart contains energy conservation requirements for metal halide lamp ballasts and fixtures, pursuant to Part A of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6309.
[75 FR 10966, Mar. 9, 2010]
Active mode means the condition in which an energy-using product:
(1) Is connected to a main power source;
(2) Has been activated; and
(3) Provides one or more main functions.
Ballast means a device used with an electric discharge lamp to obtain necessary circuit conditions (voltage, current, and waveform) for starting and operating.
Ballast efficiency means, in the case of a high intensity discharge fixture, the efficiency of a lamp and ballast combination, expressed as a percentage, and calculated in accordance with the following formula: Efficiency = Pout/Pin where:
(1) Pout equals the measured operating lamp wattage; and
(2) Pin equals the measured operating input wattage.
(3) The lamp, and the capacitor when the capacitor is provided, shall constitute a nominal system in accordance with the ANSI C78.43-2017 (incorporated by reference; see § 431.323);
(4) For ballasts with a frequency of 60 Hz, Pin and Pout shall be measured after lamps have been stabilized according to Section 4.4 of ANSI C82.6-2015 (incorporated by reference; see § 431.323) using a wattmeter with accuracy specified in Section 4.5 of ANSI C82.6-2015; and
(5) For ballasts with a frequency greater than 60 Hz, Pin and Pout shall have a basic accuracy of ±0.5 percent at the higher of either 3 times the output operating frequency of the ballast or 2.4 kHz.
Basic model means all units of a given type of covered product (or class thereof) manufactured by one manufacturer, having the same primary energy source, and which have essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency, and are rated to operate a given lamp type and wattage.
Ceramic metal halide lamp means a metal halide lamp with an arc tube made of ceramic materials.
Electronic ballast means a device that uses semiconductors as the primary means to control lamp starting and operation.
General lighting application means lighting that provides an interior or exterior area with overall illumination.
High-frequency electronic metal halide ballast means an electronic ballast that operates a lamp at an output frequency of 1000 Hz or greater.
Metal halide ballast means a ballast used to start and operate metal halide lamps.
Metal halide lamp means a high intensity discharge lamp in which the major portion of the light is produced by radiation of metal halides and their products of dissociation, possibly in combination with metallic vapors.
Metal halide lamp fixture means a light fixture for general lighting application designed to be operated with a metal halide lamp and a ballast for a metal halide lamp.
Nonpulse-start electronic ballast means an electronic ballast with a starting method other than pulse-start.
Off mode means the condition in which an energy-using product:
(1) Is connected to a main power source; and
(2) Is not providing any standby or active mode function.
PLC control signal means a power line carrier (PLC) signal that is supplied to the ballast using the input ballast wiring for the purpose of controlling the ballast and putting the ballast in standby mode.
Probe-start metal halide ballast means a ballast that starts a probe-start metal halide lamp that contains a third starting electrode (probe) in the arc tube, and does not generally contain an igniter but instead starts lamps with high ballast open circuit voltage.
Pulse-start metal halide ballast means an electronic or electromagnetic ballast that starts a pulse-start metal halide lamp with high voltage pulses, where lamps shall be started by the ballast first providing a high voltage pulse for ionization of the gas to produce a glow discharge and then power to sustain the discharge through the glow-to-arc transition.
Quartz metal halide lamp means a metal halide lamp with an arc tube made of quartz materials.
Reference lamp is a metal halide lamp that meets the operating conditions of a reference lamp as defined by ANSI C82.9-2016 (incorporated by reference; see § 431.323).
Standby mode means the condition in which an energy-using product:
(1) Is connected to a main power source; and
(2) Offers one or more of the following user-oriented or protective functions:
(i) To facilitate the activation or deactivation of other functions (including active mode) by remote switch (including remote control), internal sensor, or timer;
(ii) Continuous functions, including information or status displays (including clocks) or sensor-based functions.
[74 FR 12075, Mar. 23, 2009, as amended at 75 FR 10966, Mar. 9, 2010; 74 FR 12074, Mar. 23, 2009; 79 FR 7843, Feb. 10, 2014; 87 FR 37699, June 24, 2022]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the U.S. Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, email: fr.inspection@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html. The material may be obtained from the sources in the following paragraphs of this section.
(b) ANSI. American National Standards Institute, 25 W. 43rd Street, 4th Floor, New York, NY 10036; 212-642-4900; www.ansi.org.
(1) ANSI C78.43-2017, American National Standard for Electric Lamps—Single-Ended Metal Halide Lamps, approved December 21, 2017; IBR approved for § 431.324.
(2) ANSI C78.44-2016, American National Standard for Electric Lamps—Double-Ended Metal Halide Lamps, approved July 1, 2016; IBR approved for § 431.324.
(3) ANSI C82.6-2015 (R2020), American National Standard for Lamp Ballasts—Ballasts for High-Intensity Discharge Lamps—Methods of Measurement, approved March 30, 2020; IBR approved for §§ 431.322; 431.324.
(4) ANSI C82.9-2016, American National Standard for Lamp Ballasts—High Intensity Discharge and Low-Pressure Sodium Lamps—Definitions, approved July 12, 2016; IBR approved for §§ 431.322; 431.324.
(c) IEC. International Electrotechnical Commission, 3 rue de Varembé, 1st Floor, P.O. Box 131, CH—1211 Geneva 20—Switzerland, +41 22 919 02 11, or go to webstore.iec.ch/home.
(1) IEC 63103, Lighting Equipment—Non-active Mode Power Measurement, Edition 1.0, dated 2020-07; IBR approved for § 431.324.
(2) [Reserved]
(d) NFPA. National Fire Protection Association, 11 Tracy Drive, Avon, MA 02322, 1-800-344-3555, or go to http://www.nfpa.org;
(1) NFPA 70-2002 (“NFPA 70”), National Electrical Code 2002 Edition, IBR approved for § 431.326;
(2) [Reserved]
(e) UL. Underwriters Laboratories, Inc., COMM 2000, 1414 Brook Drive, Downers Grove, IL 60515, 1-888-853-3503, or go to http://www.ul.com.
(1) UL 1029 (ANSI/UL 1029-2007) (“UL 1029”), Standard for Safety High-Intensity-Discharge Lamp Ballasts, 5th edition, May 25, 1994, which consists of pages dated May 25, 1994, September 28, 1995, August 3, 1998, February 7, 2001 and December 11, 2007, IBR approved for § 431.326.
(2) [Reserved]
[74 FR 12075, Mar. 23, 2009, as amended at 75 FR 10966, Mar. 9, 2010; 87 FR 37699, June 24, 2022]
(a) Scope. This section provides test procedures for measuring, pursuant to EPCA, the energy efficiency of metal halide lamp ballasts. After July 25, 2022, and prior to December 21, 2022, any representations with respect to energy use or efficiency of metal halide lamp fixtures must be in accordance with the results of testing pursuant to this section or the test procedures as they appeared in 10 CFR 431.324 as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2022. On or after December 21, 2022, any representations, including certifications of compliance for metal halide lamp fixtures subject to any energy conservation standard, made with respect to the energy use or efficiency of metal halide lamp fixtures must be made in accordance with the results of testing pursuant to this section.
(b) Active mode procedure —
(1) General instructions. Specifications in referenced standards that are recommended, that “shall” or “should” be met, or that are not otherwise explicitly optional, are mandatory. In cases where there is a conflict between any industry standard(s) and this section, the language of the test procedure in this section takes precedence over the industry standard(s).
(2) Test conditions and setup.
(i) The power supply, ballast conditions, lamp position, and instrumentation must all conform to the requirements specified in Section 4.0 of ANSI C82.6-2015 (R2020) (incorporated by reference; see § 431.323).
(ii) Airflow in the room for the testing period must be ≤0.5 meters/second.
(iii) Test circuits must be in accordance with the circuit connections specified in Section 6.3 of ANSI C82.6-2015 (R2020).
(iv) For ballasts designed to operate lamps rated less than 150 W that have 120 V as an available input voltage, testing must be performed at 120 V. For ballasts designed to operate lamps rated less than 150 W that do not have 120 V as an available voltage, testing must be performed at the highest available input voltage. For ballasts designed to operate lamps rated greater than or equal to 150 W that have 277 V as an available input voltage, testing must be conducted at 277 V. For ballasts designed to operate lamps rated greater than or equal to 150 W that do not have 277 V as an available input voltage, testing must be conducted at the highest available input voltage.
(v) Operate dimming ballasts at maximum input power.
(vi) Select the metal halide lamp for testing as follows:
(A) The metal halide lamp used for testing must meet the specifications of a reference lamp as defined by ANSI C82.9-2016 and the rated values of the corresponding lamp data sheet as specified in ANSI C78.43-2017 (both incorporated by reference; see § 431.323) for single-ended lamps and ANSI C78.44-2016 (incorporated by reference; see § 431.323) for double-ended lamps.
(B) Ballasts designated with ANSI codes corresponding to more than one lamp must be tested with the lamp having the highest nominal lamp wattage as specified in ANSI C78.43-2017 or ANSI C78.44-2016, as applicable.
(C) Ballasts designated with ANSI codes corresponding to both ceramic metal halide lamps (code beginning with “C”) and quartz metal halide lamps (code beginning with “M”) of the same nominal lamp wattage must be tested with the quartz metal halide lamp.
(3) Test method —
(i) Stabilization criteria —
(A) General instruction. Lamp must be seasoned as prescribed in Section 4.4.1 of ANSI C82.6-2015 (R2020).
(B) Basic stabilization method. Lamps using the basic stabilization method must be stabilized in accordance with Section 4.4.2 of ANSI C82.6-2015 (R2020). Stabilization is reached when the lamp's electrical characteristics vary by no more than 3-percent in three consecutive 10- to 15-minute intervals measured after the minimum burning time of 30 minutes.
(C) Alternative stabilization method. In cases where switching from the reference ballast to test ballast without extinguishing the lamp is impossible, such as for low-frequency electronic ballasts, the alternative stabilization method must be used. Lamps using the alternative stabilization method must be stabilized in accordance with Section 4.4.3 of ANSI C82.6-2015 (R2020).
(ii) Test measurements.
(A) The ballast input power during operating conditions must be measured in accordance with the methods specified in Sections 6.1 and 6.8 of ANSI C82.6-2015 (R2020).
(B) The ballast output (lamp) power during operating conditions must be measured in accordance with the methods specified in Sections 6.2 and 6.10 of ANSI C82.6-2015 (R2020).
(C) For ballasts with a frequency of 60 Hz, the ballast input and output power shall be measured after lamps have been stabilized according to Section 4.4 of ANSI C82.6-2015 (R2020) using a wattmeter with accuracy specified in Section 4.5 of ANSI C82.6-2015 (R2020); and
(D) For ballasts with a frequency greater than 60 Hz, the ballast input and output power shall have a basic accuracy of ±0.5 percent at the higher of either 3 times the output operating frequency of the ballast or 2.4 kHz.
(iii) Calculations.
(A) To determine the percent efficiency of the ballast under test, divide the measured ballast output (lamp) power, as measured in paragraph (b)(3)(ii) of this section, by the measured ballast input power, as measured in paragraph (b)(3)(ii) of this section. Calculate percent efficiency to three significant figures.
(B) [Reserved]
(c) Standby mode procedure —
(1) General instructions. Measure standby mode energy consumption only for a ballast that is capable of operating in standby mode. Specifications in referenced standards that are recommended, that “shall” or “should” be met, or that are not otherwise explicitly optional, are mandatory. When there is a conflict, the language of the test procedure in this section takes precedence over IEC 63103 (incorporated by reference; see § 431.323).
(2) Test conditions and setup.
(i) Establish and maintain test conditions and setup in accordance with paragraph (b)(2) of this section.
(ii) Connect each ballast to a lamp as specified in paragraph (b)(2)(vi) of this section. Note: ballast operation with a reference lamp is not required.
(3) Test method and measurement.
(i) Turn on all of the lamps at full light output. If any lamp is not functional, replace the lamp and repeat the test procedure. If the ballast will not operate any lamps, replace the unit under test.
(ii) Send a signal to the ballast instructing it to have zero light output using the appropriate ballast communication protocol or system for the ballast being tested.
(iii) Stabilize the ballast prior to measurement using one of the methods as specified in Section 5.4 of IEC 63103.
(iv) Measure the standby mode energy consumption in watts using one of the methods as specified in Section 5.4 of IEC 63103.
[87 FR 37699, June 24, 2022]
(a) Except as provided in paragraph (b) of this section, each metal halide lamp fixture manufactured on or after January 1, 2009, and designed to be operated with lamps rated greater than or equal to 150 watts but less than or equal to 500 watts shall contain—
(1) A pulse-start metal halide ballast with a minimum ballast efficiency of 88 percent;
(2) A magnetic probe-start ballast with a minimum ballast efficiency of 94 percent; or
(3) A nonpulse-start electronic ballast with either a minimum ballast efficiency of 92 percent for wattages greater than 250 watts; or a minimum ballast efficiency of 90 percent for wattages less than or equal to 250 watts.
(b) The standards described in paragraph (a) of this section do not apply to—
(1) Metal halide lamp fixtures with regulated lag ballasts;
(2) Metal halide lamp fixtures that use electronic ballasts that operate at 480 volts; or
(3) Metal halide lamp fixtures that;
(i) Are rated only for 150 watt lamps;
(ii) Are rated for use in wet locations; as specified by the National Fire Protection Association in NFPA 70 (incorporated by reference; see § 431.323); and
(iii) Contain a ballast that is rated to operate at ambient air temperatures above 50 °C, as specified in UL 1029, (incorporated by reference; see § 431.323).
(c) Except when the requirements of paragraph (a) of this section are more stringent (i.e., require a larger minimum efficiency value) or as provided by paragraph (e) of this section, each metal halide lamp fixture manufactured on or after February 10, 2017, must contain a metal halide ballast with an efficiency not less than the value determined from the appropriate equation in the following table:
| Designed to be operated with lamps of the following rated lamp wattage |
Tested input voltage‡‡ |
Minimum standard equation‡‡ % |
|---|---|---|
| ≥50 W and ≤100 W | Tested at 480 V | (1/(1 + 1.24 × P^(−0.351))) − 0.020†† |
| ≥50 W and ≤100 W | All others | 1/(1 + 1.24 × P^(−0.351)) |
| >100 W and <150† W | Tested at 480 V | (1/(1 + 1.24 × P^(−0.351))) − 0.020 |
| >100 W and <150† W | All others | 1/(1 + 1.24 × P^(−0.351)) |
| ≥150 ‡ W and ≤250 W | Tested at 480 V | 0.880 |
| ≥150 ‡ W and ≤250 W | All others | For ≥150 W and ≤200 W: 0.880 |
| For >200 W and ≤250 W: 1/(1 + 0.876 × P^(−0.351)) | ||
| >250 W and ≤500 W | Tested at 480 V | For >250 and <265 W: 0.880 |
| For ≥265 W and ≤500 W: (1/(1 + 0.876 × P^(−0.351)) − 0.010 | ||
| >250 W and ≤500 W | All others | 1/(1 + 0.876 × P^(−0.351)) |
| >500 W and ≤1000 W | Tested at 480 V | For >500 W and ≤750 W: 0.900 |
| For >750 W and ≤1000 W: 0.000104 × P + 0.822 | ||
| For >500 W and ≤1000 W: may not utilize a probe-start ballast | ||
| >500 W and ≤1000 W | All others | For >500 W and ≤750 W: 0.910 |
| For >750 W and ≤1000 W: 0.000104 × P + 0.832 | ||
| For >500 W and ≤1000 W: may not utilize a probe-start ballast | ||
| † Includes 150 W fixtures specified in paragraph (b)(3) of this section, that are fixtures rated only for 150 W lamps; rated for use in wet locations, as specified by the NFPA 70 (incorporated by reference, see § 431.323), section 410.4(A); and containing a ballast that is rated to operate at ambient air temperatures above 50 °C, as specified by UL 1029 (incorporated by reference, see § 431.323). | ||
| ‡ Excludes 150 W fixtures specified in paragraph (b)(3) of this section, that are fixtures rated only for 150 W lamps; rated for use in wet locations, as specified by the NFPA 70, section 410.4(A); and containing a ballast that is rated to operate at ambient air temperatures above 50 °C, as specified by UL 1029. | ||
| †† P is defined as the rated wattage of the lamp the fixture is designed to operate. | ||
| ‡‡ Tested input voltage is specified in 10 CFR 431.324. | ||
(d) Except as provided in paragraph (e) of this section, metal halide lamp fixtures manufactured on or after February 10, 2017, that operate lamps with rated wattage >500 W to ≤1000 W must not contain a probe-start metal halide ballast.
(e) The standards described in paragraphs (c) and (d) of this section do not apply to—
(1) Metal halide lamp fixtures with regulated-lag ballasts;
(2) Metal halide lamp fixtures that use electronic ballasts that operate at 480 volts; and
(3) Metal halide lamp fixtures that use high-frequency electronic ballasts.
[74 FR 12075, Mar. 23, 2009, as amended at 79 FR 7844, Feb. 10, 2014]
81 FR 79998, Nov. 15, 2016, unless otherwise noted.
This subpart contains and energy conservation requirements for compressors, pursuant to Part A-1 of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
The following definitions are applicable to this subpart, including appendix A. In cases where there is a conflict, the language of the definitions adopted in this section take precedence over any descriptions or definitions found in any other source, including in ISO Standard 1217:2009(E), “Displacement compressors—Acceptance tests,” as amended through Amendment 1:2016(E), “Calculation of isentropic efficiency and relationship with specific energy” (incorporated by reference, see § 431.343). In cases where definitions reference design intent, DOE will consider all relevant information, including marketing materials, labels and certifications, and equipment design, to determine design intent.
Actual volume flow rate means the volume flow rate of air, compressed and delivered at the standard discharge point, referred to conditions of total temperature, total pressure and composition prevailing at the standard inlet point, and as determined in accordance with the test procedures prescribed in § 431.344.
Air compressor means a compressor designed to compress air that has an inlet open to the atmosphere or other source of air, and is made up of one or more compression elements (bare compressors), driver(s), mechanical equipment to drive the compression elements, and any ancillary equipment.
Air-cooled compressor means a compressor that utilizes air to cool both the compressed air and, if present, any auxiliary substance used to facilitate compression, and that is not a liquid-cooled compressor.
Ancillary equipment means any equipment distributed in commerce with an air compressor but that is not a bare compressor, driver, or mechanical equipment. Ancillary equipment is considered to be part of a given air compressor, regardless of whether the ancillary equipment is physically attached to the bare compressor, driver, or mechanical equipment at the time when the air compressor is distributed in commerce.
Auxiliary substance means any substance deliberately introduced into a compression process to aid in compression of a gas by any of the following: Lubricating, sealing mechanical clearances, or absorbing heat.
Bare compressor means the compression element and auxiliary devices (e.g., inlet and outlet valves, seals, lubrication system, and gas flow paths) required for performing the gas compression process, but does not include any of the following:
(1) The driver;
(2) Speed-adjusting gear(s);
(3) Gas processing apparatuses and piping; and
(4) Compressor equipment packaging and mounting facilities and enclosures.
Basic model means all units of a class of compressors manufactured by one manufacturer, having the same primary energy source, the same compressor motor nominal horsepower, and essentially identical electrical, physical, and functional (or pneumatic) characteristics that affect energy consumption and energy efficiency.
Brushless electric motor means a machine that converts electrical power into rotational mechanical power without use of sliding electrical contacts.
Compressor means a machine or apparatus that converts different types of energy into the potential energy of gas pressure for displacement and compression of gaseous media to any higher pressure values above atmospheric pressure and has a pressure ratio at full-load operating pressure greater than 1.3.
Compressor motor nominal horsepower means the motor horsepower of the electric motor, as determined in accordance with the applicable procedures in subparts B and X of this part, with which the rated air compressor is distributed in commerce.
Driver means the machine providing mechanical input to drive a bare compressor directly or through the use of mechanical equipment.
Fixed-speed compressor means an air compressor that is not capable of adjusting the speed of the driver continuously over the driver operating speed range in response to incremental changes in the required compressor flow rate.
Full-load actual volume flow rate means the actual volume flow rate of the compressor at the full-load operating pressure.
Liquid-cooled compressor means a compressor that utilizes liquid coolant provided by an external system to cool both the compressed air and, if present, any auxiliary substance used to facilitate compression.
Lubricant-free compressor means a compressor that does not introduce any auxiliary substance into the compression chamber at any time during operation.
Lubricated compressor means a compressor that introduces an auxiliary substance into the compression chamber during compression.
Maximum full-flow operating pressure means the maximum discharge pressure at which the compressor is capable of operating, as determined in accordance with the test procedure prescribed in § 431.344.
Mechanical equipment means any component of an air compressor that transfers energy from the driver to the bare compressor.
Package isentropic efficiency means the ratio of power required for an ideal isentropic compression process to the actual packaged compressor power input used at a given load point, as determined in accordance with the test procedures prescribed in § 431.344.
Package specific power means the compressor power input at a given load point, divided by the actual volume flow rate at the same load point, as determined in accordance with the test procedures prescribed in § 431.344.
Positive displacement compressor means a compressor in which the admission and diminution of successive volumes of the gaseous medium are performed periodically by forced expansion and diminution of a closed space(s) in a working chamber(s) by means of displacement of a moving member(s) or by displacement and forced discharge of the gaseous medium into the high-pressure area.
Pressure ratio at full-load operating pressure means the ratio of discharge pressure to inlet pressure, determined at full-load operating pressure in accordance with the test procedures prescribed in § 431.344.
Reciprocating compressor means a positive displacement compressor in which gas admission and diminution of its successive volumes are performed cyclically by straight-line alternating movements of a moving member(s) in a compression chamber(s).
Rotary compressor means a positive displacement compressor in which gas admission and diminution of its successive volumes or its forced discharge are performed cyclically by rotation of one or several rotors in a compressor casing.
Rotor means a compression element that rotates continually in a single direction about a single shaft or axis.
Variable-speed compressor means an air compressor that is capable of adjusting the speed of the driver continuously over the driver operating speed range in response to incremental changes in the required compressor actual volume flow rate.
Water-injected lubricated compressor means a lubricated compressor that uses injected water as an auxiliary substance.
[82 FR 1101, Jan. 4, 2017, as amended at 85 FR 1591, Jan. 10, 2020; 90 FR 5555, Jan. 17, 2025]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Avenue SW, EE-5B, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email: fr.inspection@nara.gov. The material may be obtained from the sources in paragraphs (b) and (c) of this section:
(b) IEC. International Electrotechnical Commission Central Office, 3, rue de Varembé, Case Postale 131, CH-1211 GENEVA 20, Switzerland; + 41 22 919 02 11; webstore.iec.ch.
(1) IEC 60584-1:2013, Thermocouples—Part 1: EMF specifications and tolerances, editions 3.0, August 2013; IBR approved for appendix A to this subpart.
(2) IEC 60584-3:2021, Thermocouples—Part 3: Extension and compensating cables—Tolerances and identification system, edition 3.0, February 2021; IBR approved for appendix A to this subpart.
(c) ISO. International Organization for Standardization, Chemin de Blandonnet 8, CP 401, 1214 Vernier, Geneva, Switzerland +41 22 749 01 11, www.iso.org.
(1) ISO 1217:2009(E), Displacement compressors—Acceptance tests, fourth edition, July 1, 2009; IBR approved for appendix A to this subpart.
(2) ISO 1217:2009/Amd.1:2016(E), Displacement compressors—Acceptance tests (fourth edition, July 1, 2009), AMENDMENT 1: Calculation of isentropic efficiency and relationship with specific energy, April 15, 2016; IBR approved for appendix A to this subpart.
(3) ISO 5167-1:2022(E), Measurement of fluid flow by means of pressure differential devices inserted in circular cross-section conduits running full—Part 1: General principles and requirements, third edition, June 2022; IBR approved for appendix A to this subpart.
(4) ISO 9300:2022(E), Measurement of gas flow by means of critical flow nozzles, third edition, June 2022; IBR approved for appendix A to this subpart.
[90 FR 5555, Jan. 17, 2025]
(a) Scope. This section is a test procedure that is applicable to a compressor that meets the following criteria:
(1) Is an air compressor;
(2) Is a rotary compressor;
(3) Is not a liquid ring compressor;
(4) Is driven by a brushless electric motor;
(5) Is a lubricated compressor;
(6) Has a full-load operating pressure greater than or equal to 75 pounds per square inch gauge (psig) and less than or equal to 200 psig;
(7) Is not designed and tested to the requirements of the American Petroleum Institute Standard 619, “Rotary-Type Positive-Displacement Compressors for Petroleum, Petrochemical, and Natural Gas Industries;”
(8) Has full-load actual volume flow rate greater than or equal to 35 cubic feet per minute (cfm), or is distributed in commerce with a compressor motor nominal horsepower greater than or equal to 10 horsepower (hp); and
(9) Has a full-load actual volume flow rate less than or equal to 1,250 cfm, or is distributed in commerce with a compressor motor nominal horsepower less than or equal to 200 hp.
(b) Testing and calculations. Determine the applicable full-load package isentropic efficiency (ηisen,FL), part-load package isentropic efficiency (ηisen,PL), package specific power, maximum full-flow operating pressure, full-load operating pressure, full-load actual volume flow rate, and pressure ratio at full-load operating pressure using the test procedure set forth in appendix A of this subpart.
[82 FR 1102, Jan. 4, 2017]
(a) Each compressor that is manufactured starting on January 10, 2025 and that:
(1) Is an air compressor,
(2) Is a rotary compressor,
(3) Is not a liquid ring compressor,
(4) Is driven by a brushless electric motor,
(5) Is a lubricated compressor,
(6) Has a full-load operating pressure greater than or equal to 75 pounds per square inch gauge (psig) and less than or equal to 200 psig,
(7) Is not designed and tested to the requirements of The American Petroleum Institute standard 619, “Rotary-Type Positive-Displacement Compressors for Petroleum, Petrochemical, and Natural Gas Industries,”
(8) Has full-load actual volume flow rate greater than or equal to 35 cubic feet per minute (cfm), or is distributed in commerce with a compressor motor nominal horsepower greater than or equal to 10 horsepower (hp),
(9) Has a full-load actual volume flow rate less than or equal to 1,250 cfm, or is distributed in commerce with a compressor motor nominal horsepower less than or equal to 200 hp,
(10) Is driven by a three-phase electric motor,
(11) Is manufactured alone or as a component of another piece of equipment; and
(12) Is in one of the equipment classes listed in the Table 1, must have a full-load package isentropic efficiency or part-load package isentropic efficiency that is not less than the appropriate “Minimum Package Isentropic Efficiency” value listed in Table 1 of this section.
| Equipment class | Minimum package isentropic efficiency | ηRegr (package isentropic efficiency reference curve) |
d (percentage loss reduction) |
|---|---|---|---|
| Rotary, lubricated, air-cooled, fixed-speed compressor | ηRegr + (1 − ηRegr) * (d/100) | −0.00928 * ln2 (.4719 * V1) + 0.13911 * ln(.4719 * V1) + 0.27110 | −15 |
| Rotary, lubricated, air-cooled, variable-speed compressor | ηRegr + (1 − ηRegr) * (d/100) | −0.01549 * ln2 (.4719 * V1) + 0.21573 * ln(.4719 * V1) + 0.00905 | −10 |
| Rotary, lubricated, liquid-cooled, fixed-speed compressor | .02349 + ηRegr + (1 − ηRegr) * (d/100) | −0.00928 * ln2 (.4719 * V1) + 0.13911 * ln(.4719 * V1) + 0.27110 | −15 |
| Rotary, lubricated, liquid-cooled, variable-speed compressor | .02349 + ηRegr + (1 − ηRegr) * (d/100) | −0.01549 * ln2 (.4719 * V1) + 0.21573 * ln(.4719 * V1) + 0.00905 | −15 |
(b) Instructions for the use of Table 1 of this section:
(1) To determine the standard level a compressor must meet, the correct equipment class must be identified. The descriptions are in the first column (“Equipment Class”); definitions for these descriptions are found in § 431.342.
(2) The second column (“Minimum Package Isentropic Efficiency”) contains the applicable energy conservation standard level, provided in terms of package isentropic efficiency.
(3) For “Fixed-speed compressor” equipment classes, the relevant Package Isentropic Efficiency is Full-load Package Isentropic Efficiency. For “Variable-speed compressor” equipment classes, the relevant Package Isentropic Efficiency is Part-load Package Isentropic Efficiency. Both Full- and Part-load Package Isentropic Efficiency are determined in accordance with the test procedure in § 431.344.
(4) The second column (“Minimum Package Isentropic Efficiency”) references the third column (“ηRegr”), also a function of full-load actual volume flow rate, and the fourth column (“d”). The equations are provided separately to maintain consistency with the language of the preamble and analysis.
(5) The second and third columns contain the term V1, which denotes compressor full-load actual volume flow rate, given in terms of cubic feet per minute (“cfm”) and determined in accordance with the test procedure in § 431.344.
[85 FR 1591, Jan. 10, 2020]
Prior to July 16, 2025, any representations made with respect to the energy use or efficiency of compressors must be based on testing conducted in accordance with:
(a) The applicable provisions of this appendix as they appeared in this subpart T of part 431 as of January 1, 2023; or
(b) This appendix.
Beginning July 16, 2025, representations with respect to energy use or efficiency of compressors, including compliance certifications, must be based on testing conducted in accordance with this appendix.
1. Incorporation by Reference
DOE incorporated by reference in § 431.343, the entire standard for: IEC 60584-1:2013, IEC 60584-3:2021, ISO 1217:2009(E), ISO 1217:2009/Amd.1:2016(E), ISO 5167-1:2022, and ISO 9300:2022; however, only enumerated provisions of ISO 1217:2009(E) and ISO 1217:2009/Amd.1:2016(E) are applicable to this appendix as listed in section 1. To the extent there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
1.1 ISO 1217:2009(E)
1.1.1 Section 2, Normative references;
1.1.2 Section 3, Terms and definitions;
1.1.3 Section 4, Symbols;
1.1.4 Section 5, Measuring equipment, methods and accuracy (excluding 5.1, 5.5, 5.7, and 5.8);
1.1.5 Section 6, Test procedures: the introductory text to Section 6.2, Test arrangements, paragraphs 6.2(g) and 6.2(h), and Table 1—Maximum deviations from specified values and fluctuations from average readings of this appendix;
1.1.6 Annex B (normative), Simplified acceptance test for bare displacement compressors, Section B.4.5 Comparison with specified values;
1.1.7 Annex C (normative), Simplified acceptance test for electrically driven packaged displacement compressors (excluding C.1.2, C.2.1, C.3, C.4.2.2, C.4.3.1, and C.4.5).
1.2 ISO 1217:2009/Amd.1:2016(E)
1.2.1 Section 3.5.1: isentropic power;
1.2.2 Section 3.6.1: isentropic efficiency;
1.2.3 Annex H (informative), Isentropic efficiency and its relation to specific energy requirement, sections H.2, Symbols and subscripts, and H.3, Derivation of isentropic power.
2. Measurements, Test Conditions, and Equipment Configuration
2.1. Measurement Equipment.
2.1.1. For the purposes of measuring air compressor performance, the equipment necessary to measure volume flow rate, inlet and discharge pressure, temperature, condensate, and packaged compressor power input must comply with the equipment and accuracy requirements specified in sections 5.2, 5.3, 5.4, 5.6, and 5.9 of ISO 1217:2009(E), (including the applicable provisions of IEC 60584-1 and IEC 60584-3, as referenced in section 5.3 of ISO 1217:2009(E) and the applicable provisions of ISO 5167-1 and ISO 9300, as referenced in section 5.6 of ISO 1217:2009(E)) and sections C.2.3 and C.2.4 of Annex C to ISO 1217:2009(E).
2.1.2. Electrical measurement equipment must be capable of measuring true root mean square (RMS) current, true RMS voltage, and real power up to the 40th harmonic of fundamental supply source frequency.
2.1.3. Any instruments used to measure a particular parameter specified in section 2.1.1 of this appendix must have a combined accuracy of ±2.0 percent of the measured value at the fundamental supply source frequency, where combined accuracy is the square root of the sum of the squares of individual instrument accuracies.
2.1.4. Any instruments used to directly measure the density of air must have an accuracy of ±1.0 percent of the measured value.
2.1.5. Any pressure measurement equipment used in a calculation of another variable (e.g.,actual volume flow rate) must also meet all accuracy and measurement requirements of section 5.2 of ISO 1217:2009(E).
2.1.6. Any temperature measurement equipment used in a calculation of another variable (e.g.,actual volume flow rate) must also meet all accuracy and measurement requirements of section 5.3 of ISO 1217:2009(E).
2.1.7. Where ISO 1217:2009(E) refers to “corrected volume flow rate,” the term is deemed synonymous with the term “actual volume flow rate,” as defined in section 3.4.1 of ISO 1217:2009(E).
2.2. Test Conditions and Configuration of Unit Under Test
2.2.1. For both fixed-speed and variable-speed compressors, conduct testing in accordance with the test conditions, unit configuration, and specifications of section 6.2 paragraphs (g) and (h) of ISO 1217:2009(E) and sections C.1.1, C.2.2, C.2.3, C.2.4, C.4.1, C.4.2.1, C.4.2.3, and C.4.3.2 of Annex C to ISO 1217:2009(E).
2.2.2. The power supply must:
(a) Maintain the voltage greater than or equal to 95 percent and less than or equal to 110 percent of the rated value of the motor,
(b) Maintain the frequency within ±5 percent of the rated value of the motor,
(c) Maintain the voltage unbalance of the power supply within ±3 percent of the rated values of the motor, and
(d) Maintain total harmonic distortion below 12 percent throughout the test.
2.2.3. Ambient Conditions. The ambient air temperature must be greater than or equal to 68 °F and less than or equal to 90 °F for the duration of testing. There are no ambient condition requirements for inlet pressure or relative humidity.
2.2.4. All equipment indicated in table 1 of this appendix must be present and installed for all tests specified in this appendix. If the compressor is distributed in commerce without an item from table 1 of this appendix, the manufacturer must provide an appropriate item to be installed for the test. Additional ancillary equipment may be installed for the test, if distributed in commerce with the compressor, but this additional ancillary equipment is not required. If any of the equipment listed in table 2 of this appendix is distributed in commerce with units of the compressor basic model, it must be present and installed for all tests specified in this appendix.
| Equipment | Fixed-speed rotary air compressors | Variable-speed
rotary air compressors |
|---|---|---|
| Driver | Yes | Yes. |
| Bare compressors | Yes | Yes. |
| Inlet filter | Yes | Yes. |
| Inlet valve | Yes | Yes. |
| Minimum pressure check valve/backflow check valve | Yes | Yes. |
| Lubricant separator | Yes | Yes. |
| Air piping | Yes | Yes. |
| Lubricant piping | Yes | Yes. |
| Lubricant filter | Yes | Yes. |
| Lubricant cooler | Yes | Yes. |
| Thermostatic valve | Yes | Yes. |
| Electrical switchgear or frequency converter for the driver | Yes | Not applicable.* |
| Device to control the speed of the driver (e.g., variable speed drive) | Not applicable ** | Yes. |
| Compressed air cooler(s) | Yes | Yes. |
| Pressure switch, pressure transducer, or similar pressure control device | Yes | Yes. |
| Moisture separator and drain | Yes | Yes. |
| * This category is not applicable to variable-speed rotary air compressors. | ||
| ** This category is not applicable to fixed-speed rotary air compressors. | ||
| Equipment | Fixed-speed rotary air compressors | Variable-speed rotary air compressors |
|---|---|---|
| Cooling fan(s) and motors | Yes | Yes. |
| Mechanical equipment | Yes | Yes. |
| Lubricant pump | Yes | Yes. |
| Interstage cooler | Yes | Yes. |
| Electronic or electrical controls and user interface | Yes | Yes. |
| All protective and safety devices | Yes | Yes. |
2.2.5. The inlet of the compressor under test must be open to the atmosphere and take in ambient air for all tests specified in this appendix.
2.2.6. The compressor under test must be set up according to all manufacturer instructions for normal operation (e.g., verify lubricant level, connect all loose electrical connections, close off bottom of unit to floor, cover forklift holes).
2.2.7. The piping connected to the discharge orifice of the compressor must be of a diameter at least equal to that of the compressor discharge orifice to which it is connected. The piping must be straight with a length of at least 6 inches.
2.2.8. Transducers used to record compressor discharge pressure must be located on the discharge piping between 2 inches and 6 inches, inclusive, from the discharge orifice of the compressor. The pressure tap for transducers must be located at the highest point of the pipe's cross section.
3. Determination of Package Isentropic Efficiency, Package Specific Power, and Pressure Ratio at Full-Load Operating Pressure
3.1 Data Collection and Analysis.
3.1.1. Stabilization. Record data at each load point under steady-state conditions. Steady-state conditions are achieved when a set of two consecutive readings taken at least 10 seconds apart and no more than 60 seconds apart are within the maximum permissible fluctuation from the average (of the two consecutive readings), as specified in table 1 of ISO 1217:2009(E) for—
(a) Discharge pressure;
(b) Temperature at the nozzle or orifice plate, measured per section 5.3 of ISO 1217:2009(E); and
(c) Differential pressure over the nozzle or orifice plate, measured per section 5.2 of ISO 1217:2009(E).
3.1.2. Data Sampling and Frequency. At each load point, record a minimum set of 16 unique readings, collected over a minimum time of 15 minutes. Each consecutive reading must be no more than 60 seconds apart, and not less than 10 seconds apart. All readings at each load point must be within the maximum permissible fluctuation from average specified in table 1 of ISO 1217:2009(E) for—
(a) Discharge pressure;
(b) Temperature at the nozzle or orifice plate, measured per section 5.3 of ISO 1217:2009(E); and
(c) Differential pressure over the nozzle or orifice plate, measured per section 5.2 of ISO 1217:2009(E).
If one or more readings do not meet the requirements, then all previous readings must be disregarded and a new set of at least 16 new unique readings must be collected over a minimum time of 15 minutes. Average the readings to determine the value of each parameter to be used in subsequent calculations.
3.1.3. Calculations and Rounding. Perform all calculations using raw measured values. Round the final result for package isentropic efficiency to the thousandth (i.e., 0.001), for package specific power in kilowatts per 100 cubic feet per minute to the nearest hundredth (i.e., 0.01), for pressure ratio at full-load operating pressure to the nearest tenth (i.e., 0.1), for full-load actual volume flow rate in cubic feet per minute to the nearest tenth (i.e., 0.1), and for full-load operating pressure in pounds per square inch gauge (psig) to the nearest integer (i.e., 1). All terms and quantities refer to values determined in accordance with the procedures set forth in this appendix for the tested unit.
3.2. Full-Load Operating Pressure and Full-Load Actual Volume Flow Rate
Determine the full-load operating pressure and full-load actual volume flow rate (referenced throughout this appendix) in accordance with the procedures prescribed in section 4 of this appendix.
3.3. Full-Load Package Isentropic Efficiency for Fixed- and Variable-Speed Air Compressors
Use this test method to test fixed-speed air compressors and variable-speed air compressors.
3.3.1. Test unit at full-load operating pressure and full-load volume flow rate according to the requirements established in sections 2, 3.1, and 3.2 of this appendix. Measure volume flow rate and calculate actual volume flow rate in accordance with section C.4.2.1 of Annex C to ISO 1217:2009(E) with no corrections made for shaft speed. Measure discharge gauge pressure and packaged compressor power input. Measured discharge gauge pressure and calculated actual volume flow rate must be within the deviation limits for discharge pressure and volume flow rate specified in tables C.1 and C.2 of Annex C to ISO 1217:2009(E), where full-load operating pressure and full-load actual volume flow rate (as determined in section 4 of this appendix) are the targeted values.
3.3.2. Calculate the package isentropic efficiency at full-load operating pressure and full-load actual volume flow rate (full-load package isentropic efficiency, ηisen,FL) using the equation for isentropic efficiency in section 3.6.1 of ISO 1217:2009(E) as modified by ISO 1217:2009/Amd.1:2016(E). For Pisen, use the isentropic power required for compression at full-load operating pressure and full-load actual volume flow rate, as determined in section 3.3.2.1 of this appendix. For Preal, use the real packaged compressor power input at full-load operating pressure and full-load actual volume flow rate, as determined in section 3.3.2.2 of this appendix.
3.3.2.1. Calculate the isentropic power required for compression at full-load operating pressure and full-load actual volume flow rate using equation (H.6) of Annex H to ISO 1217:2009/Amd.1:2016(E). For qV1, use the actual volume flow rate (cubic meters per second) calculated in section 3.3.1 of this appendix. For p1, use 100 kPa. For p2, use the sum of
(a) 100 kPa, and
(b) The measured discharge gauge pressure (Pa) from section 3.3.1 of this appendix. For K, use the isentropic exponent (ratio of specific heats) of air, which, for the purposes of this test procedure, is 1.400.
3.3.2.2. Calculate real packaged compressor power input at full-load operating pressure and full-load actual volume flow rate using the following equation:
Preal,100% = K5 · K6 · PPR,100%
Where:
K5 = correction factor for inlet pressure, as determined in section C.4.3.2 of Annex C to ISO 1217:2009(E). For calculations of this variable use a value of 100 kPa for contractual inlet pressure;
K6 = correction factor for pressure ratio, as determined in section B.4.5 of Annex B to ISO 1217:2009(E). For calculations of this variable use a value of 1.400 for isentropic exponent, and for contractual pressure ratio, use the ratio of
(a) The sum of 100 kPa and the measured discharge gauge pressure (kPa) from section 3.3.1 of this appendix, to
(b) 100 kPa; and
PPR,100% = packaged compressor power input reading at full-load operating pressure and full-load actual volume flow rate measured in section 3.3.1 of this appendix (W).
3.4. Part-Load Package Isentropic Efficiency for Variable-Speed Air Compressors
Use this test method to test variable-speed air compressors.
3.4.1. Test unit at two load points:
(a) Full-load operating pressure and 70 percent of full-load actual volume flow rate and
(b) Full-load operating pressure and 40 percent of full-load actual volume flow rate, according to the requirements established in sections 2, 3.1, and 3.2 of this appendix. To reach each specified load point, adjust the speed of the driver and the backpressure of the system. For each load point, measure volume flow rate and calculate actual volume flow rate in accordance with section C.4.2.1 of Annex C to ISO 1217:2009(E), with no corrections made for shaft speed. For each load point, measure discharge gauge pressure and packaged compressor power input. Measured discharge gauge pressure and calculated actual volume flow rate must be within the deviation limits for discharge pressure and volume flow rate specified in tables C.1 and C.2 of Annex C to ISO 1217:2009(E).
3.4.2. For variable-speed compressors, calculate the part-load package isentropic efficiency using the following equation:
ηisen,PL = ω40% × ηisen,40% + ω70% × ηisen,70% + ω100% × ηisen,100%
Where:
ηisen,PL = part-load package isentropic efficiency for a variable-speed compressor;
ηisen,100% = package isentropic efficiency at full-load operating pressure and 100 percent of full-load actual volume flow rate, as determined in section 3.3.2 of this appendix;
ηisen,70% = package isentropic efficiency at full-load operating pressure and 70 percent of full-load actual volume flow rate, as determined in section 3.4.3 of this appendix;
ηisen,40% = package isentropic efficiency at full-load operating pressure and 40 percent of full-load actual volume flow rate, as determined in section 3.4.4 of this appendix;
ω40% = weighting at 40 percent of full-load actual volume flow rate and is 0.25;
ω70% = weighting at 70 percent of full-load actual volume flow rate and is 0.50; and
ω100% = weighting at 100 percent of full-load actual volume flow rate and is 0.25.
3.4.3. Calculate package isentropic efficiency at full-load operating pressure and 70 percent of full-load actual volume flow rate using the equation for isentropic efficiency in section 3.6.1 of ISO 1217:2009(E) as modified by ISO 1217:2009/Amd.1:2016(E). For Pisen, use the isentropic power required for compression at full-load operating pressure and 70 percent of full-load actual volume flow rate, as determined in section 3.4.3.1 of this appendix. For Preal, use the real packaged compressor power input at full-load operating pressure and 70 percent of full-load actual volume flow rate, as determined in section 3.4.3.2 of this appendix.
3.4.3.1. Calculate the isentropic power required for compression at full-load operating pressure and 70 percent of full-load actual volume flow rate using equation (H.6) of Annex H to ISO 1217:2009/Amd.1:2016(E). For qV1, use actual volume flow rate (cubic meters per second) at full-load operating pressure and 70 percent of full-load actual volume flow rate, as calculated in section 3.4.1 of this appendix. For p1, use 100 kPa. For p2, use the sum of
(a) 100 kPa, and
(b) Discharge gauge pressure (Pa) at full-load operating pressure and 70 percent of full-load actual volume flow rate, as calculated in section 3.4.1 of this appendix. For K, use the isentropic exponent (ratio of specific heats) of air, which, for the purposes of this test procedure, is 1.400.
3.4.3.2. Calculate real packaged compressor power input at full-load operating pressure and 70 percent of full-load actual volume flow rate using the following equation:
Preal,70% = K5 · K6 · PPR,70%
Where:
K5 = correction factor for inlet pressure, as determined in section C.4.3.2 of Annex C to ISO 1217:2009(E). For calculations of this variable use a value of 100 kPa for contractual inlet pressure;
K6 = correction factor for pressure ratio, as determined in section B.4.5 of Annex B to ISO 1217:2009(E). For calculations of this variable use a value of 1.400 for isentropic exponent, and for contractual pressure ratio, use the ratio of
(a) The sum of 100 kPa and the measured discharge gauge pressure (kPa) from the test at 70 percent of full-load actual volume flow rate in section 3.4.1 of this appendix, to
(b) 100 kPa; and
PPR,70% = packaged compressor power input reading at full-load operating pressure and 70 percent of full-load actual volume flow rate, as measured in section 3.4.1 of this appendix (W).
3.4.4. Calculate package isentropic efficiency at full-load operating pressure and 40 percent of full-load actual volume flow rate using the equation for isentropic efficiency in section 3.6.1 of ISO 1217:2009(E) as modified by ISO 1217:2009/Amd.1:2016(E). For Pisen, use the isentropic power required for compression at full-load operating pressure and 40 percent of full-load actual volume flow rate, as determined in section 3.4.4.1 of this appendix. For Preal, use the real packaged compressor power input at full-load operating pressure and 40 percent of full-load actual volume flow rate, as determined in section 3.4.4.2 of this appendix.
3.4.4.1. Calculate the isentropic power required for compression at full-load operating pressure and 40 percent of full-load actual volume flow rate using equation (H.6) of Annex H to ISO 1217:2009/Amd.1:2016(E). For qV1, use actual volume flow rate (cubic meters per second) at full-load operating pressure and 40 percent of full-load actual volume flow rate, as calculated in section 3.4.1 of this appendix. For p1, use 100 kPa. For p2, use the sum of
(a) 100 kPa, and
(b) Discharge gauge pressure (Pa) at full-load operating pressure and 40 percent of full-load actual volume flow rate, as calculated in section 3.4.1 of this appendix. For K, use the isentropic exponent (ratio of specific heats) of air, which, for the purposes of this test procedure, is 1.400.
3.4.4.2. Calculate real packaged compressor power input at full-load operating pressure and 40 percent of full-load actual volume flow rate using the following equation:
Preal,40% = K5 · K6 · PPR,40%
Where:
K5 = correction factor for inlet pressure, as determined in section C.4.3.2 of Annex C to ISO 1217:2009(E). For calculations of this variable use a value of 100 kPa for contractual inlet pressure;
K6 = correction factor for pressure ratio, as determined in section B.4.5 of Annex B to ISO 1217:2009(E). For calculations of this variable use a value of 1.400 for isentropic exponent, and for contractual pressure ratio, use the ratio of
(a) The sum of 100 kPa and the measured discharge gauge pressure (kPa) from the test at 40 percent of full-load actual volume flow rate in section 3.4.1 of this appendix, to
(b) 100 kPa; and
PPR,40% = packaged compressor power input reading at full-load operating pressure and 40 percent of full-load actual volume flow rate, as measured in section 3.4.1 of this appendix (W).
3.5. Determination of Package Specific Power
For both fixed and variable-speed air compressors, determine the package specific power, at any load point, using the equation for specific energy consumption in section C.4.4 of Annex C to ISO 1217:2009(E) and other values measured pursuant to this appendix, with no correction for shaft speed. Calculate PPcorr in section C.4.4 of Annex C to ISO 1217:2009(E) using the following equation:
PPcorr = K5 · K6 · PPR
Where:
K5 = correction factor for inlet pressure, as determined in section C.4.3.2 of Annex C to ISO 1217:2009(E). For calculations of this variable use a value of 100 kPa for contractual inlet pressure;
K6 = correction factor for pressure ratio, as determined in section B.4.5 of Annex B to ISO 1217:2009(E). For calculations of this variable use a value of 1.400 for isentropic exponent, and for contractual pressure ratio, use the ratio of
(a) The sum of 100 kPa and the measured discharge gauge pressure (kPa) from the test used to determine the package specific power, to
(b) 100 kPa; and
PPR = packaged compressor power input reading (W), as determined in section C.2.4 of Annex C to ISO 1217:2009(E).
3.6. Determination of Pressure Ratio at Full-Load Operating Pressure
Pressure ratio at full-load operating pressure, as defined in § 431.342, is calculated using the following equation:
Where:
PR = pressure ratio at full-load operating pressure;
P1 = 100 kPa; and
PFL = full-load operating pressure, determined in section 4.3.4 of this appendix (Pa gauge).
4. Method To Determine Maximum Full-Flow Operating Pressure, Full-Load Operating Pressure, and Full-Load Actual Volume Flow Rate
4.1. Principal Strategy
The principal strategy of this method is to incrementally increase discharge pressure by 2 psig relative to a starting point, and identify the maximum full-flow operating pressure at which the compressor is capable of operating. The maximum discharge pressure achieved is the maximum full-flow operating pressure. The full-load operating pressure and full-load actual volume flow rate are determined based on the maximum full-flow operating pressure.
4.2. Pre-test Instructions
4.2.1. Safety. For the method presented in section 4.3.1 of this appendix, only test discharge pressure within the safe operating range of the compressor, as specified by the manufacturer in the installation and operation manual shipped with the unit. Make no changes to safety limits or equipment. Do not violate any manufacturer-provided motor operational guidelines for normal use, including any restriction on instantaneous and continuous input power draw and output shaft power (e.g., electrical rating and service factor limits).
4.2.2. Adjustment of Discharge Pressure
4.2.2.1. If the air compressor is not equipped, as distributed in commerce by the manufacturer, with any mechanism to adjust the maximum discharge pressure output limit, proceed to section 4.2.3 of this appendix.
4.2.2.2. If the air compressor is equipped, as distributed in commerce by the manufacturer, with any mechanism to adjust the maximum discharge pressure output limit, then adjust this mechanism to the maximum pressure allowed, according to the manufacturer's operating instructions for these mechanisms. Mechanisms to adjust discharge pressure may include, but are not limited to, onboard digital or analog controls, and user-adjustable inlet valves.
4.2.3. Driver speed. If the unit under test is a variable-speed compressor, maintain maximum driver speed throughout the test. If the unit under test is a fixed-speed compressor with a multi-speed driver, maintain driver speed at the maximum speed throughout the test.
4.2.4. Measurements and Tolerances
4.2.4.1. Recording. Record data by electronic means such that the requirements of section 4.2.4.5 of this appendix are met.
4.2.4.2. Discharge Pressure. Measure discharge pressure in accordance with section 5.2 of ISO 1217:2009(E). Express compressor discharge pressure in psig in reference to ambient conditions, and record it to the nearest integer. Specify targeted discharge pressure points in integer values only. The maximum allowable measured deviation from the targeted discharge pressure at each tested point is ±1 psig.
4.2.4.3. Actual Volume Flow Rate. Measure actual volume flow rate in accordance with section C.4.2.1 of Annex C to ISO 1217:2009(E) (where it is called “corrected volume flow rate”) with no corrections made for shaft speed. Express compressor actual volume flow rate in cubic feet per minute at inlet conditions (cfm).
4.2.4.4. Stabilization. Record data at each tested load point under steady-state conditions, as determined in section 3.1.1 of this appendix.
4.2.4.5. Data Sampling and Frequency. At each load point, record a set of at least of two readings, collected at a minimum of 10 seconds apart. All readings at each load point must be within the maximum permissible fluctuation from the average (of the two consecutive readings), as specified in 3.1.2 of this appendix. Average the measurements to determine the value of each parameter to be used in subsequent calculations.
4.2.5 Adjusting System Backpressure. Set up the unit under test so that backpressure on the unit can be adjusted (e.g., by valves) incrementally, causing the measured discharge pressure to change, until the compressor is in an unloaded condition.
4.2.6 Unloaded Condition. A unit is considered to be in an unloaded condition if capacity controls on the unit automatically reduce the actual volume flow rate from the compressor (e.g., shutting the motor off, or unloading by adjusting valves).
4.3. Test Instructions
4.3.1. Adjust the backpressure of the system so the measured discharge pressure is 90 percent of the expected maximum full-flow operating pressure, rounded to the nearest integer, in psig. If the expected maximum full-flow operating pressure is not known, then adjust the backpressure of the system so that the measured discharge pressure is 65 psig. Allow the unit to remain at this setting for 15 minutes to allow the unit to thermally stabilize. Then measure and record discharge pressure and actual volume flow rate at the starting pressure.
4.3.2. Adjust the backpressure of the system to increase the discharge pressure by 2 psig from the previous value, allow the unit to remain at this setting for a minimum of 2 minutes, and proceed to section 4.3.3 of this appendix.
4.3.3. If the unit is now in an unloaded condition, end the test and proceed to section 4.3.4 of this appendix. If the unit is not in an unloaded condition, measure discharge pressure and actual volume flow rate, and repeat section 4.3.2 of this appendix.
4.3.4. Of the discharge pressures recorded under stabilized conditions in sections 4.3.1 through 4.3.3 of this appendix, identify the largest. This is the maximum full-flow operating pressure. Determine the full-load operating pressure as a self-declared value greater than or equal to the lesser of (A) 90 percent of the maximum full-flow operating pressure, or (B) 10 psig less than the maximum full-flow operating pressure.
4.3.5 The full-load actual volume flow rate is the actual volume flow rate measured at the full-load operating pressure. If the self-declared full-load operating pressure falls on a previously tested value of discharge pressure, then use the previously measured actual volume flow rate as the full-load actual volume flow rate. If the self-declared full-load operating pressure does not fall on a previously tested value of discharge pressure, then adjust the backpressure of the system to the self-declared full-load operating pressure and allow the unit to remain at this setting for a minimum of 2 minutes. The measured actual volume flow rate at this setting is the full-load actual volume flow rate.
[90 FR 5555, Jan. 17, 2025]
69 FR 61941, Oct. 21, 2004, unless otherwise noted. Redesignated at 70 FR 60416, Oct. 18, 2005.
This subpart describes violations of EPCA's energy conservation requirements, specific procedures we will follow in pursuing alleged non-compliance of an electric motor with an applicable energy conservation standard or labeling requirement, and general procedures for enforcement action, largely drawn directly from EPCA, that apply to electric motors.
[76 FR 12505, Mar. 7, 2011]
(a) Each of the following is a prohibited act under sections 332 and 345 of the Act:
(1) Distribution in commerce by a manufacturer or private labeler of any “new covered equipment” which is not labeled in accordance with an applicable labeling rule prescribed in accordance with Section 344 of the Act, and in this part;
(2) Removal from any “new covered equipment” or rendering illegible, by a manufacturer, distributor, retailer, or private labeler, of any label required under this part to be provided with such covered equipment;
(3) Failure to permit access to, or copying of records required to be supplied under the Act and this part, or failure to make reports or provide other information required to be supplied under the Act and this part;
(4) Advertisement of an electric motor or motors, by a manufacturer, distributor, retailer, or private labeler, in a catalog from which the equipment may be purchased, without including in the catalog all information as required by § 431.31(b)(1), provided, however, that this shall not apply to an advertisement of an electric motor in a catalog if distribution of the catalog began before the effective date of the labeling rule applicable to that motor;
(5) Failure of a manufacturer to supply at his expense a reasonable number of units of covered equipment to a test laboratory designated by the Secretary;
(6) Failure of a manufacturer to permit a representative designated by the Secretary to observe any testing required by the Act and this part, and to inspect the results of such testing; and
(7) Distribution in commerce by a manufacturer or private labeler of any new covered equipment which is not in compliance with an applicable energy efficiency standard prescribed under the Act and this part.
(b) In accordance with sections 333 and 345 of the Act, any person who knowingly violates any provision of paragraph (a) of this section may be subject to assessment of a civil penalty of no more than $575 for each violation.
(c) For purposes of this section:
(1) The term “new covered equipment” means covered equipment the title of which has not passed to a purchaser who buys such product for purposes other than:
(i) Reselling it; or
(ii) Leasing it for a period in excess of one year; and
(2) The term “knowingly” means:
(i) Having actual knowledge; or
(ii) Presumed to have knowledge deemed to be possessed by a reasonable person who acts in the circumstances, including knowledge obtainable upon the exercise of due care.
[69 FR 61941, Oct. 21, 2004. Redesignated at 70 FR 60416, Oct. 18, 2005, as amended at 79 FR 19, Jan. 2, 2014; 81 FR 41794, June 28, 2016; 81 FR 96351, Dec. 30, 2016; 83 FR 1291, Jan. 11, 2018; 83 FR 66083, Dec. 26, 2018; 85 FR 830, Jan. 8, 2020; 86 FR 2955, Jan. 14, 2021; 87 FR 1063, Jan. 10, 2022; 88 FR 2193, Jan. 13, 2023; 89 FR 1028, Jan. 9, 2024; 89 FR 105406, Dec. 27, 2024]
(a) Test notice. Upon receiving information in writing, concerning the energy performance of a particular electric motor sold by a particular manufacturer or private labeler, which indicates that the electric motor may not be in compliance with the applicable energy efficiency standard, or upon undertaking to ascertain the accuracy of the efficiency rating on the nameplate or in marketing materials for an electric motor, disclosed pursuant to subpart B of this part, the Secretary may conduct testing of that electric motor under this subpart by means of a test notice addressed to the manufacturer in accordance with the following requirements:
(1) The test notice procedure will only be followed after the Secretary or his/her designated representative has examined the underlying test data (or, where appropriate, data as to use of an alternative efficiency determination method) provided by the manufacturer and after the manufacturer has been offered the opportunity to meet with the Department to verify, as applicable, compliance with the applicable efficiency standard, or the accuracy of labeling information, or both. In addition, where compliance of a basic model was certified based on an AEDM, the Department shall have the discretion to pursue the provisions of § 431.17(a)(4)(iii) prior to invoking the test notice procedure. A representative designated by the Secretary shall be permitted to observe any re-verification procedures undertaken pursuant to this subpart, and to inspect the results of such reverification.
(2) The test notice will be signed by the Secretary or his/her designee. The test notice will be mailed or delivered by the Department to the plant manager or other responsible official, as designated by the manufacturer.
(3) The test notice will specify the model or basic model to be selected for testing, the method of selecting the test sample, the date and time at which testing shall be initiated, the date by which testing is scheduled to be completed and the facility at which testing will be conducted. The test notice may also provide for situations in which the specified basic model is unavailable for testing, and may include alternative basic models.
(4) The Secretary may require in the test notice that the manufacturer of an electric motor shall ship at his expense a reasonable number of units of a basic model specified in such test notice to a testing laboratory designated by the Secretary. The number of units of a basic model specified in a test notice shall not exceed 20.
(5) Within five working days of the time the units are selected, the manufacturer shall ship the specified test units of a basic model to the testing laboratory.
(b) Testing laboratory. Whenever the Department conducts enforcement testing at a designated laboratory in accordance with a test notice under this section, the resulting test data shall constitute official test data for that basic model. Such test data will be used by the Department to make a determination of compliance or noncompliance if a sufficient number of tests have been conducted to satisfy the requirements of appendix A of this subpart.
(c) Sampling. The determination that a manufacturer's basic model complies with its labeled efficiency, or the applicable energy efficiency standard, shall be based on the testing conducted in accordance with the statistical sampling procedures set forth in appendix A of this subpart and the test procedures set forth in appendix B to subpart B of this part.
(d) Test unit selection. A Department inspector shall select a batch, a batch sample, and test units from the batch sample in accordance with the provisions of this paragraph and the conditions specified in the test notice.
(1) The batch may be subdivided by the Department utilizing criteria specified in the test notice.
(2) A batch sample of up to 20 units will then be randomly selected from one or more subdivided groups within the batch. The manufacturer shall keep on hand all units in the batch sample until such time as the basic model is determined to be in compliance or non-compliance.
(3) Individual test units comprising the test sample shall be randomly selected from the batch sample.
(4) All random selection shall be achieved by sequentially numbering all of the units in a batch sample and then using a table of random numbers to select the units to be tested.
(e) Test unit preparation.
(1) Prior to and during the testing, a test unit selected in accordance with paragraph (d) of this section shall not be prepared, modified, or adjusted in any manner unless such preparation, modification, or adjustment is allowed by the applicable Department of Energy test procedure. One test shall be conducted for each test unit in accordance with the applicable test procedures prescribed in appendix B to subpart B of this part.
(2) No quality control, testing, or assembly procedures shall be performed on a test unit, or any parts and sub-assemblies thereof, that is not performed during the production and assembly of all other units included in the basic model.
(3) A test unit shall be considered defective if such unit is inoperative or is found to be in noncompliance due to failure of the unit to operate according to the manufacturer's design and operating instructions. Defective units, including those damaged due to shipping or handling, shall be reported immediately to the Department. The Department shall authorize testing of an additional unit on a case-by-case basis.
(4)
(i) Non-standard endshields or flanges. For purposes of DOE-initiated testing of electric motors with non-standard endshields or flanges, the Department will have the discretion to determine whether the lab should test a general purpose electric motor of equivalent electrical design and enclosure rather than replacing the nonstandard flange or endshield.
(ii) Partial electric motors. For purposes of DOE-initiated testing, the Department has the discretion to determine whether the lab should test a general purpose electric motor of equivalent electrical design and enclosure rather than machining and attaching an endshield.
(f) Testing at manufacturer's option.
(1) If a manufacturer's basic model is determined to be in noncompliance with the applicable energy performance standard at the conclusion of Department testing in accordance with the sampling plan specified in appendix A of this subpart, the manufacturer may request that the Department conduct additional testing of the basic model according to procedures set forth in appendix A of this subpart.
(2) All units tested under this paragraph shall be selected and tested in accordance with the provisions given in paragraphs (a) through (e) of this section.
(3) The manufacturer shall bear the cost of all testing conducted under this paragraph.
(4) The manufacturer shall cease distribution of the basic model tested under the provisions of this paragraph from the time the manufacturer elects to exercise the option provided in this paragraph until the basic model is determined to be in compliance. The Department may seek civil penalties for all units distributed during such period.
(5) If the additional testing results in a determination of compliance, a notice of allowance to resume distribution shall be issued by the Department.
[69 FR 61941, Oct. 21, 2004. Redesignated at 70 FR 60416, Oct. 18, 2005, as amended at 78 FR 75995, Dec. 13, 2013]
(a) In the event that a model of an electric motor is determined non-compliant by the Department in accordance with § 431.192 or if a manufacturer or private labeler determines a model of an electric motor to be in noncompliance, then the manufacturer or private labeler shall:
(1) Immediately cease distribution in commerce of the basic model.
(2) Give immediate written notification of the determination of noncompliance, to all persons to whom the manufacturer has distributed units of the basic model manufactured since the date of the last determination of compliance.
(3) Pursuant to a request made by the Secretary, provide the Department within 30 days of the request, records, reports, and other documentation pertaining to the acquisition, ordering, storage, shipment, or sale of a basic model determined to be in noncompliance.
(4) The manufacturer may modify the non-compliant basic model in such manner as to make it comply with the applicable performance standard. Such modified basic model shall then be treated as a new basic model and must be certified in accordance with the provisions of this subpart; except that in addition to satisfying all requirements of this subpart, the manufacturer shall also maintain records that demonstrate that modifications have been made to all units of the new basic model prior to distribution in commerce.
(b) If a basic model is not properly certified in accordance with the requirements of this subpart, the Secretary may seek, among other remedies, injunctive action to prohibit distribution in commerce of such basic model.
If the Secretary determines that a basic model of any covered equipment does not comply with an applicable energy conservation standard:
(a) The Secretary will notify the manufacturer, private labeler, or any other person as required, of this finding and of the Secretary's intent to seek a judicial order restraining further distribution in commerce of units of such a basic model unless the manufacturer, private labeler or other person as required, delivers, within 15 calendar days, a satisfactory statement to the Secretary, of the steps the manufacturer, private labeler or other person will take to insure that the noncompliant basic model will no longer be distributed in commerce. The Secretary will monitor the implementation of such statement.
(b) If the manufacturer, private labeler or any other person as required, fails to stop distribution of the noncompliant basic model, the Secretary may seek to restrain such violation in accordance with sections 334 and 345 of the Act.
(c) The Secretary will determine whether the facts of the case warrant the assessment of civil penalties for knowing violations in accordance with sections 333 and 345 of the Act.
(a) Under sections 333(d) and 345 of the Act, before issuing an order assessing a civil penalty against any person, the Secretary must provide to such a person a notice of the proposed penalty. Such notice must inform the person that such person can choose (in writing within 30 days after receipt of the notice) to have the procedures of paragraph (c) of this section (in lieu of those in paragraph (b) of this section) apply with respect to such assessment.
(b)
(1) Unless a person elects, within 30 calendar days after receipt of a notice under paragraph (a) of this section, to have paragraph (c) of this section apply with respect to the civil penalty under paragraph (a), the Secretary will assess the penalty, by order, after providing an opportunity for an agency hearing under 5 U.S.C. 554, before an administrative law judge appointed under 5 U.S.C. 3105, and making a determination of violation on the record. Such assessment order will include the administrative law judge's findings and the basis for such assessment.
(2) Any person against whom the Secretary assesses a penalty under this paragraph may, within 60 calendar days after the date of the order assessing such penalty, initiate action in the United States Court of Appeals for the appropriate judicial circuit for judicial review of such order in accordance with 5 U.S.C. chapter 7. The court will have jurisdiction to enter a judgment affirming, modifying, or setting aside in whole or in part, the order of the Secretary, or the court may remand the proceeding to the Secretary for such further action as the court may direct.
(c)
(1) In the case of any civil penalty with respect to which the procedures of this paragraph have been elected, the Secretary will promptly assess such penalty, by order, after the date of the receipt of the notice under paragraph (a) of this section of the proposed penalty.
(2) If the person has not paid the civil penalty within 60 calendar days after the assessment has been made under paragraph (c)(1) of this section, the Secretary will institute an action in the appropriate District Court of the United States for an order affirming the assessment of the civil penalty. The court will have authority to review de novo the law and the facts involved and jurisdiction to enter a judgment enforcing, modifying, and enforcing as so modified, or setting aside in whole or in part, such assessment.
(3) Any election to have this paragraph apply can only be revoked with the consent of the Secretary.
(d) If any person fails to pay an assessment of a civil penalty after it has become a final and unappealable order under paragraph (b) of this section, or after the appropriate District Court has entered final judgment in favor of the Secretary under paragraph (c) of this section, the Secretary will institute an action to recover the amount of such penalty in any appropriate District Court of the United States. In such action, the validity and appropriateness of such final assessment order or judgment will not be subject to review.
(e)
(1) In accordance with the provisions of sections 333(d)(5)(A) and 345 of the Act and notwithstanding the provisions of title 28, United States Code, or Section 502(c) of the Department of Energy Organization Act, the General Counsel of the Department of Energy (or any attorney or attorneys within DOE designated by the Secretary) will represent the Secretary, and will supervise, conduct, and argue any civil litigation to which paragraph (c) of this section applies (including any related collection action under paragraph (d) of this section) in a court of the United States or in any other court, except the Supreme Court of the United States. However, the Secretary or the General Counsel will consult with the Attorney General concerning such litigation and the Attorney General will provide, on request, such assistance in the conduct of such litigation as may be appropriate.
(2) In accordance with the provisions of sections 333(d)(5)(B) and 345 of the Act, and subject to the provisions of Section 502(c) of the Department of Energy Organization Act, the Secretary will be represented by the Attorney General, or the Solicitor General, as appropriate, in actions under this section, except to the extent provided in paragraph (e)(1) of this section.
(3) In accordance with the provisions of Section 333(d)(5)(c) and 345 of the Act, Section 402(d) of the Department of Energy Organization Act will not apply with respect to the function of the Secretary under this section.
Step 1. The first sample size (n1) must be five or more units.
Step 2. Compute the mean (X̄1 of the measured energy performance of the n1 units in the first sample as follows:
where Xi is the measured full-load efficiency of unit i.
Step 3. Compute the sample standard deviation (S1) of the measured full-load efficiency of the n1 units in the first sample as follows:
Step 4. Compute the standard error (SE(X̄1)) of the mean full-load efficiency of the first sample as follows:
Step 5. Compute the lower control limit (LCL1) for the mean of the first sample using RE as the desired mean as follows:
where: RE is the applicable EPCA nominal full-load efficiency when the test is to determine compliance with the applicable statutory standard, or is the labeled nominal full-load efficiency when the test is to determine compliance with the labeled efficiency value, and t is the 2.5th percentile of a t-distribution for a sample size of n1, which yields a 97.5 percent confidence level for a one-tailed t-test.
Step 6. Compare the mean of the first sample (X̄1) with the lower control limit (LCL1) to determine one of the following:
(i) If the mean of the first sample is below the lower control limit, then the basic model is in non-compliance and testing is at an end.
(ii) If the mean is equal to or greater than the lower control limit, no final determination of compliance or non-compliance can be made; proceed to Step 7.
Step 7. Determine the recommended sample size (n) as follows:
where S1, RE and t have the values used in Steps 3 and 5, respectively. The factor
is based on a 20 percent tolerance in the total power loss at full-load and fixed output power.
Given the value of n, determine one of the following:
(i) If the value of n is less than or equal to n1 and if the mean energy efficiency of the first sample (X̄1) is equal to or greater than the lower control limit (LCL1), the basic model is in compliance and testing is at an end.
(ii) If the value of n is greater than n1, the basic model is in non-compliance. The size of a second sample n2 is determined to be the smallest integer equal to or greater than the difference n−n1. If the value of n2 so calculated is greater than 20−n1, set n2 equal to 20−n1.
Step 8. Compute the combined (X̄2) mean of the measured energy performance of the n1 and n2 units of the combined first and second samples as follows:
Step 9. Compute the standard error (SE(X̄2)) of the mean full-load efficiency of the n1 and n2 units in the combined first and second samples as follows:
(Note that S1 is the value obtained above in Step 3.)
Step 10. Set the lower control limit (LCL2) to,
where t has the value obtained in Step 5, and compare the combined sample mean (X̄2) to the lower control limit (LCL2) to find one of the following:
(i) If the mean of the combined sample (X̄2) is less than the lower control limit (LCL2), the basic model is in non-compliance and testing is at an end.
(ii) If the mean of the combined sample (X̄2) is equal to or greater than the lower control limit (LCL2), the basic model is in compliance and testing is at an end.
Manufacturer-Option Testing
If a determination of non-compliance is made in Steps 6, 7 or 10, of this appendix A, the manufacturer may request that additional testing be conducted, in accordance with the following procedures.
Step A. The manufacturer requests that an additional number, n3, of units be tested, with n3 chosen such that n1 + n2 + n3 does not exceed 20.
Step B. Compute the mean full-load efficiency, standard error, and lower control limit of the new combined sample in accordance with the procedures prescribed in Steps 8, 9, and 10, of this appendix A.
Step C. Compare the mean performance of the new combined sample to the lower control limit (LCL2) to determine one of the following:
(a) If the new combined sample mean is equal to or greater than the lower control limit, the basic model is in compliance and testing is at an end.
(b) If the new combined sample mean is less than the lower control limit and the value of n1 + n2 + n3 is less than 20, the manufacturer may request that additional units be tested. The total of all units tested may not exceed 20. Steps A, B, and C are then repeated.
(c) Otherwise, the basic model is determined to be in non-compliance.
69 FR 61941, Oct. 21, 2004, unless otherwise noted. Redesignated at 70 FR 60417, Oct. 18, 2005.
(a) General information. This section provides a means for seeking waivers of the test procedure requirements of this part for basic models that meet the requirements of paragraph (a)(1) of this section. In granting a waiver or interim waiver, DOE will not change the energy use or efficiency metric that the manufacturer must use to certify compliance with the applicable energy conservation standard and to make representations about the energy use or efficiency of the covered equipment. The granting of a waiver or interim waiver by DOE does not exempt such basic models from any other regulatory requirement contained in this part or the certification and compliance requirements of 10 CFR part 429 and specifies an alternative method for testing the basic model(s) addressed in the waiver.
(1) Any interested person may submit a petition to waive for a particular basic model the requirements of any uniform test method contained in this part, upon the grounds that either the basic model contains one or more design characteristics that prevent testing of the basic model according to the prescribed test procedures or cause the prescribed test procedures to evaluate the basic model in a manner so unrepresentative of its true energy or water consumption characteristics as to provide materially inaccurate comparative data.
(2) Manufacturers of basic model(s) subject to a waiver or interim waiver are responsible for complying with the other requirements of this part and with the requirements of 10 CFR part 429 regardless of the person that originally submitted the petition for waiver and/or interim waiver. The filing of a petition for waiver and/or interim waiver shall not constitute grounds for noncompliance with any requirements of this part.
(3) All correspondence regarding waivers and interim waivers must be submitted to DOE either electronically to AS_Waiver_Requests@ee.doe.gov (preferred method of transmittal) or by mail to U.S. Department of Energy, Building Technologies Program, Test Procedure Waiver, 1000 Independence Avenue SW., Mailstop EE-5B, Washington, DC 20585-0121.
(b) Petition content and publication.
(1) Each petition for interim waiver and waiver must:
(i) Identify the particular basic model(s) for which a waiver is requested, each brand name under which the identified basic model(s) will be distributed in commerce, the design characteristic(s) constituting the grounds for the petition, and the specific requirements sought to be waived, and must discuss in detail the need for the requested waiver;
(ii) Identify manufacturers of all other basic models distributed in commerce in the United States and known to the petitioner to incorporate design characteristic(s) similar to those found in the basic model that is the subject of the petition;
(iii) Include any alternate test procedures known to the petitioner to evaluate the performance of the equipment type in a manner representative of the energy and/or water consumption characteristics of the basic model; and
(iv) Be signed by the petitioner or an authorized representative. In accordance with the provisions set forth in 10 CFR 1004.11, any request for confidential treatment of any information contained in a petition or in supporting documentation must be accompanied by a copy of the petition, application or supporting documentation from which the information claimed to be confidential has been deleted. DOE will publish in the Federal Register the petition and supporting documents from which confidential information, as determined by DOE, has been deleted in accordance with 10 CFR 1004.11 and will solicit comments, data and information with respect to the determination of the petition.
(2) In addition to the requirements in paragraph (b)(1) of this section, each petition for interim waiver must reference the related petition for waiver, demonstrate likely success of the petition for waiver, and address what economic hardship and/or competitive disadvantage is likely to result absent a favorable determination on the petition for interim waiver.
(c) Notification to other manufacturers.
(1) Each petitioner for interim waiver must, upon publication of a grant of an interim waiver in the Federal Register, notify in writing all known manufacturers of domestically marketed basic models of the same equipment class (as specified in the relevant subpart of 10 CFR part 431), and of other equipment classes known to the petitioner to use the technology or have the characteristic at issue in the waiver. The notice must include a statement that DOE has published the interim waiver and petition for waiver in the Federal Register and the date the petition for waiver was published. The notice must also include a statement that DOE will receive and consider timely written comments on the petition for waiver. Within five working days, each petitioner must file with DOE a statement certifying the names and addresses of each person to whom a notice of the petition for waiver has been sent.
(2) If a petitioner does not request an interim waiver and notification has not been provided pursuant to paragraph (c)(1) of this section, each petitioner, after filing a petition for waiver with DOE, and after the petition for waiver has been published in the Federal Register, must, within five working days of such publication, notify in writing all known manufacturers of domestically marketed basic models of the same equipment class (as listed in the relevant subpart of 10 CFR part 431), and of other equipment classes known to the petitioner to use the technology or have the characteristic at issue in the waiver. The notice must include a statement that DOE has published the petition in the Federal Register and the date the petition for waiver was published. Within five working days of the publication of the petition in the Federal Register, each petitioner must file with DOE a statement certifying the names and addresses of each person to whom a notice of the petition for waiver has been sent.
(d) Public comment and rebuttal.
(1) Any person submitting written comments to DOE with respect to an interim waiver must also send a copy of the comments to the petitioner by the deadline specified in the notice.
(2) Any person submitting written comments to DOE with respect to a petition for waiver must also send a copy of such comments to the petitioner.
(3) A petitioner may, within 10 working days of the close of the comment period specified in the Federal Register, submit a rebuttal statement to DOE. A petitioner may rebut more than one comment in a single rebuttal statement.
(e) Provisions specific to interim waivers.
(1) DOE will post a petition for interim waiver on its website within 5 business days of receipt of a complete petition. DOE will make best efforts to review a petition for interim waiver within 90 business days of receipt of a complete petition.
(2) A petition for interim waiver that does not meet the content requirements of paragraph (b) of this section will be considered incomplete. DOE will notify the petitioner of an incomplete petition via email.
(3) DOE will grant an interim waiver from the test procedure requirements if it appears likely that the petition for waiver will be granted and/or if DOE determines that it would be desirable for public policy reasons to grant immediate relief pending a determination on the petition for waiver. Notice of DOE's determination on the petition for interim waiver will be published in the Federal Register.
(f) Provisions specific to waivers —
(1) Disposition of application. The petitioner shall be notified in writing as soon as practicable of the disposition of each petition for waiver. DOE shall issue a decision on the petition as soon as is practicable following receipt and review of the Petition for Waiver and other applicable documents, including, but not limited to, comments and rebuttal statements.
(2) Criteria for granting. DOE will grant a waiver from the test procedure requirements if DOE determines either that the basic model(s) for which the waiver was requested contains a design characteristic that prevents testing of the basic model according to the prescribed test procedures, or that the prescribed test procedures evaluate the basic model in a manner so unrepresentative of its true energy or water consumption characteristics as to provide materially inaccurate comparative data. DOE may grant a waiver subject to conditions, which may include adherence to alternate test procedures specified by DOE. DOE will promptly publish in the Federal Register notice of each waiver granted or denied, and any limiting conditions of each waiver granted.
(g) Extension to additional basic models. A petitioner may request that DOE extend the scope of a waiver or an interim waiver to include additional basic models employing the same technology as the basic model(s) set forth in the original petition. The petition for extension must identify the particular basic model(s) for which a waiver extension is requested, each brand name under which the identified basic model(s) will be distributed in commerce, and documentation supporting the claim that the additional basic models employ the same technology as the basic model(s) set forth in the original petition. DOE will publish any such extension in the Federal Register.
(h) Duration.
(1) Within one year of issuance of an interim waiver, DOE will either:
(i) Publish in the Federal Register a final determination on the petition for waiver; or
(ii) Publish in the Federal Register a new or amended test procedure that addresses the issues presented in the waiver.
(2) When DOE publishes a decision and order on a petition for waiver in the Federal Register pursuant to paragraph (f) of this section, the interim waiver will terminate upon the date specified in the decision and order, in accordance with paragraph (i) of this section.
(3) When DOE amends the test procedure to address the issues presented in a waiver, the waiver or interim waiver will automatically terminate on the date on which use of that test procedure is required to demonstrate compliance.
(4) When DOE publishes a decision and order in the Federal Register to modify a waiver pursuant to paragraph (k) of this section, the existing waiver will terminate upon the date specified in the decision and order, in accordance with paragraph (i) of this section.
(i) Compliance certification and representations.
(1) If the interim waiver test procedure methodology is different than the decision and order test procedure methodology, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on either of the two methodologies until 180-360 days after the publication date of the decision and order, as specified by DOE in the decision and order. Thereafter, certification reports and any representations must be based on the decision and order test procedure methodology, unless otherwise specified by DOE. Once a manufacturer uses the decision and order test procedure methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the decision and order test procedure methodology while the waiver is valid.
(2) When DOE publishes a new or amended test procedure, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on the testing methodology of an applicable waiver or interim waiver, or the new or amended test procedure until the date on which use of such test procedure is required to demonstrate compliance, unless otherwise specified by DOE in the test procedure final rule. Thereafter, certification reports and any representations must be based on the test procedure final rule methodology. Once a manufacturer uses the test procedure final rule methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the test procedure final rule methodology.
(3) If DOE publishes a decision and order modifying an existing waiver, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on either of the two methodologies until 180-360 days after the publication date of the decision and order modifying the waiver, as specified by DOE in the decision and order. Thereafter, certification reports and any representations must be based on the modified test procedure methodology unless otherwise specified by DOE. Once a manufacturer uses the modified test procedure methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the modified test procedure methodology while the modified waiver is valid.
(j) Petition for waiver required of other manufactures. Any manufacturer of a basic model employing a technology or characteristic for which a waiver was granted for another basic model and that results in the need for a waiver (as specified by DOE in a published decision and order in the Federal Register) must petition for and be granted a waiver for that basic model. Manufacturers may also submit a request for interim waiver pursuant to the requirements of this section.
(k) Rescission or modification.
(1) DOE may rescind or modify a waiver or interim waiver at any time upon DOE's determination that the factual basis underlying the petition for waiver or interim waiver is incorrect, upon a determination that the results from the alternate test procedure are unrepresentative of the basic model(s)' true energy consumption characteristics, or for other appropriate reason. Waivers and interim waivers are conditioned upon the validity of statements, representations, and documents provided by the requestor; any evidence that the original grant of a waiver or interim waiver was based upon inaccurate information will weigh against continuation of the waiver. DOE's decision will specify the basis for its determination and, in the case of a modification, will also specify the change to the authorized test procedure.
(2) A person may request that DOE rescind or modify a waiver or interim waiver issued to that person if the person discovers an error in the information provided to DOE as part of its petition, determines that the waiver is no longer needed, or for other appropriate reasons. In a request for rescission, the requestor must provide a statement explaining why it is requesting rescission. In a request for modification, the requestor must explain the need for modification to the authorized test procedure and detail the modifications needed and the corresponding impact on measured energy consumption.
(3) DOE will publish a proposed rescission or modification (DOE-initiated or at the request of the original requestor) in the Federal Register for public comment. A requestor may, within 10 working days of the close of the comment period specified in the proposed rescission or modification published in the Federal Register, submit a rebuttal statement to DOE. A requestor may rebut more than one comment in a single rebuttal statement.
(4) DOE will publish its decision in the Federal Register. DOE's determination will be based on relevant information contained in the record and any comments received.
(5) After the effective date of a rescission, any basic model(s) previously subject to a waiver must be tested and certified using the applicable DOE test procedure in 10 CFR part 431.
(l) Revision of regulation. As soon as practicable after the granting of any waiver, DOE will publish in the Federal Register a notice of proposed rulemaking to amend its regulations so as to eliminate any need for the continuation of such waiver. As soon thereafter as practicable, DOE will publish in the Federal Register a final rule.
(m) To exhaust administrative remedies, any person aggrieved by an action under this section must file an appeal with the DOE's Office of Hearings and Appeals as provided in 10 CFR part 1003, subpart C.
[79 FR 26601, May 9, 2014, as amended at 85 FR 79820, Dec. 11, 2020; 86 FR 70960, Dec. 14, 2021]
Beginning on the effective date of such standard, an energy conservation standard set forth in this part for a commercial HVAC & WH product supersedes any State or local regulation concerning the energy efficiency or energy use of that product, except as provided for in Section 345(b)(2)(B)-(D) of the Act.
(a) Manufacturers of electric motors must establish, maintain and retain records of the following:
(1) The test data for all testing conducted pursuant to this part;
(2) The development, substantiation, application, and subsequent verification of any AEDM used under this part;
(3) Any written certification received from a certification program, including a certificate or conformity, relied on under the provisions of this part;
(b) You must organize such records and index them so that they are readily accessible for review. The records must include the supporting test data associated with tests performed on any test units to satisfy the requirements of this part (except tests performed by DOE).
(c) For each basic model, you must retain all such records for a period of two years from the date that production of all units of that basic model has ceased. You must retain records in a form allowing ready access to DOE, upon request.
[76 FR 12505, Mar. 7, 2011]
(a) Under sections 331 and 345 of the Act, any person importing an electric motor into the United States must comply with the provisions of the Act and of this part, and is subject to the remedies of this part.
(b) Any electric motor offered for importation in violation of the Act and of this part will be refused admission into the customs territory of the United States under rules issued by the Secretary of the Treasury, except that the Secretary of the Treasury may, by such rules, authorize the importation of such electric motor upon such terms and conditions (including the furnishing of a bond) as may appear to the Secretary of the Treasury appropriate to ensure that such electric motor will not violate the Act and this part, or will be exported or abandoned to the United States.
[76 FR 12505, Mar. 7, 2011]
Under Sections 330 and 345 of the Act, this part does not apply to any electric motor if:
(a) Such electric motor is manufactured, sold, or held for sale for export from the United States (or such electric motor was imported for export), unless such electric motor is, in fact, distributed in commerce for use in the United States; and,
(b) Such electric motor, when distributed in commerce, or any container in which it is enclosed when so distributed, bears a stamp or label stating that such electric motor is intended for export.
[76 FR 12505, Mar. 7, 2011]
Pursuant to sections 329(a) and 345 of the Act, for purposes of carrying out this part, the Secretary or the Secretary's designee, may sign and issue subpoenas for the attendance and testimony of witnesses and the production of relevant books, records, papers, and other documents, and administer the oaths. Witnesses summoned under the provisions of this section shall be paid the same fees and mileage as are paid to witnesses in the courts of the United States. In case of contumacy by, or refusal to obey a subpoena served upon any persons subject to this part, the Secretary may seek an order from the District Court of the United States for any District in which such person is found or resides or transacts business requiring such person to appear and give testimony, or to appear and produce documents. Failure to obey such order is punishable by such court as a contempt thereof.
[76 FR 12505, Mar. 7, 2011]
Pursuant to the provisions of 10 CFR 1004.11, any manufacturer or private labeler of electric motors submitting information or data which they believe to be confidential and exempt from public disclosure should submit one complete copy, and 15 copies from which the information believed to be confidential has been deleted. In accordance with the procedures established at 10 CFR 1004.11, the Department shall make its own determination with regard to any claim that information submitted be exempt from public disclosure.
[76 FR 12505, Mar. 7, 2011]
This section concerns State regulations providing for any energy conservation standard, or water conservation standard (in the case of commercial prerinse spray valves or commercial clothes washers), or other requirement with respect to the energy efficiency, energy use, or water use (in the case of commercial prerinse spray valves or commercial clothes washers), for any covered equipment other than an electric motor or commercial HVAC and WH product. Any such regulation that contains a standard or requirement that is not identical to a Federal standard in effect under this subpart is preempted by that standard, except as provided for in sections 327(b) and (c) and 345(a)(10), (e), (f) and (g) of the Act.
[75 FR 675, Jan. 5, 2010, as amended at 78 FR 62993, Oct. 23, 2013]
69 FR 61941, Oct. 21, 2004, unless otherwise noted. Redesignated at 70 FR 60417, Oct. 18, 2005.
(a) The regulations in this subpart prescribe the procedures to be followed in connection with petitions requesting a rule that a State regulation prescribing an energy conservation standard or other requirement respecting energy use or energy efficiency of a type (or class) of covered equipment not be preempted.
(b) The regulations in this subpart also prescribe the procedures to be followed in connection with petitions to withdraw a rule exempting a State regulation prescribing an energy conservation standard or other requirement respecting energy use or energy efficiency of a type (or class) of covered equipment.
(a) Criteria for exemption from preemption. Upon petition by a State which has prescribed an energy conservation standard or other requirement for a type or class of covered equipment for which a Federal energy conservation standard is applicable, the Secretary shall prescribe a rule that such standard not be preempted if he/she determines that the State has established by a preponderance of evidence that such requirement is needed to meet unusual and compelling State or local energy interests. For the purposes of this regulation, the term “unusual and compelling State or local energy interests” means interests which are substantially different in nature or magnitude from those prevailing in the U.S. generally, and are such that when evaluated within the context of the State's energy plan and forecast, the costs, benefits, burdens, and reliability of energy savings resulting from the State regulation make such regulation preferable or necessary when measured against the costs, benefits, burdens, and reliability of alternative approaches to energy savings or production, including reliance on reasonably predictable market-induced improvements in efficiency of all equipment subject to the State regulation. The Secretary may not prescribe such a rule if he finds that interested persons have established, by a preponderance of the evidence, that the State's regulation will significantly burden manufacturing, marketing, distribution, sale or servicing of the covered equipment on a national basis. In determining whether to make such a finding, the Secretary shall evaluate all relevant factors including: The extent to which the State regulation will increase manufacturing or distribution costs of manufacturers, distributors, and others; the extent to which the State regulation will disadvantage smaller manufacturers, distributors, or dealers or lessen competition in the sale of the covered equipment in the State; the extent to which the State regulation would cause a burden to manufacturers to redesign and produce the covered equipment type (or class), taking into consideration the extent to which the regulation would result in a reduction in the current models, or in the projected availability of models, that could be shipped on the effective date of the regulation to the State and within the U.S., or in the current or projected sales volume of the covered equipment type (or class) in the State and the U.S.; and the extent to which the State regulation is likely to contribute significantly to a proliferation of State commercial and industrial equipment efficiency requirements and the cumulative impact such requirements would have. The Secretary may not prescribe such a rule if he/she finds that such a rule will result in the unavailability in the State of any covered equipment (or class) of performance characteristics (including reliability), features, sizes, capacities, and volumes that are substantially the same as those generally available in the State at the time of the Secretary's finding. The failure of some classes (or types) to meet this criterion shall not affect the Secretary's determination of whether to prescribe a rule for other classes (or types).
(1) Requirements of petition for exemption from preemption. A petition from a State for a rule for exemption from preemption shall include the information listed in paragraphs (a)(1)(i) through (a)(1)(vi) of this section. A petition for a rule and correspondence relating to such petition shall be available for public review except for confidential or proprietary information submitted in accordance with the Department of Energy's Freedom of Information Regulations set forth in 10 CFR part 1004.
(i) The name, address, and telephone number of the petitioner;
(ii) A copy of the State standard for which a rule exempting such standard is sought;
(iii) A copy of the State's energy plan and forecast;
(iv) Specification of each type or class of covered equipment for which a rule exempting a standard is sought;
(v) Other information, if any, believed to be pertinent by the petitioner; and
(vi) Such other information as the Secretary may require.
(b) Criteria for exemption from preemption when energy emergency conditions exist within State. Upon petition by a State which has prescribed an energy conservation standard or other requirement for a type or class of covered equipment for which a Federal energy conservation standard is applicable, the Secretary may prescribe a rule, effective upon publication in the Federal Register, that such regulation not be preempted if he determines that in addition to meeting the requirements of paragraph (a) of this Section the State has established that: an energy emergency condition exists within the State that imperils the health, safety, and welfare of its residents because of the inability of the State or utilities within the State to provide adequate quantities of gas or electric energy to its residents at less than prohibitive costs; and cannot be substantially alleviated by the importation of energy or the use of interconnection agreements; and the State regulation is necessary to alleviate substantially such condition.
(1) Requirements of petition for exemption from preemption when energy emergency conditions exist within a State. A petition from a State for a rule for exemption from preemption when energy emergency conditions exist within a State shall include the information listed in paragraphs (a)(1)(i) through (a)(1)(vi) of this section. A petition shall also include the information prescribed in paragraphs (b)(1)(i) through (b)(1)(iv) of this section, and shall be available for public review except for confidential or proprietary information submitted in accordance with the Department of Energy's Freedom of Information Regulations set forth in 10 CFR part 1004:
(i) A description of the energy emergency condition which exists within the State, including causes and impacts.
(ii) A description of emergency response actions taken by the State and utilities within the State to alleviate the emergency condition;
(iii) An analysis of why the emergency condition cannot be alleviated substantially by importation of energy or the use of interconnection agreements;
(iv) An analysis of how the State standard can alleviate substantially such emergency condition.
(c) Criteria for withdrawal of a rule exempting a State standard. Any person subject to a State standard which, by rule, has been exempted from Federal preemption and which prescribes an energy conservation standard or other requirement for a type or class of covered equipment, when the Federal energy conservation standard for such equipment subsequently is amended, may petition the Secretary requesting that the exemption rule be withdrawn. The Secretary shall consider such petition in accordance with the requirements of paragraph (a) of this section, except that the burden shall be on the petitioner to demonstrate that the exemption rule received by the State should be withdrawn as a result of the amendment to the Federal standard. The Secretary shall withdraw such rule if he determines that the petitioner has shown the rule should be withdrawn.
(1) Requirements of petition to withdraw a rule exempting a State standard. A petition for a rule to withdraw a rule exempting a State standard shall include the information prescribed in paragraphs (c)(1)(i) through (c)(1)(vii) of this section, and shall be available for public review, except for confidential or proprietary information submitted in accordance with the Department of Energy's Freedom of Information Regulations set forth in 10 CFR part 1004:
(i) The name, address and telephone number of the petitioner;
(ii) A statement of the interest of the petitioner for which a rule withdrawing an exemption is sought;
(iii) A copy of the State standard for which a rule withdrawing an exemption is sought;
(iv) Specification of each type or class of covered equipment for which a rule withdrawing an exemption is sought;
(v) A discussion of the factors contained in paragraph (a) of this section;
(vi) Such other information, if any, believed to be pertinent by the petitioner; and
(vii) Such other information as the Secretary may require.
(2) [Reserved]
(a) Service. All documents required to be served under this subpart shall, if mailed, be served by first class mail. Service upon a person's duly authorized representative shall constitute service upon that person.
(b) Obligation to supply information. A person or State submitting a petition is under a continuing obligation to provide any new or newly discovered information relevant to that petition. Such information includes, but is not limited to, information regarding any other petition or request for action subsequently submitted by that person or State.
(c) The same or related matters. A person or State submitting a petition or other request for action shall state whether to the best knowledge of that petitioner the same or related issue, act, or transaction has been or presently is being considered or investigated by any State agency, department, or instrumentality.
(d) Computation of time.
(1) Computing any period of time prescribed by or allowed under this subpart, the day of the action from which the designated period of time begins to run is not to be included. If the last day of the period is Saturday, or Sunday, or Federal legal holiday, the period runs until the end of the next day that is neither a Saturday, or Sunday or Federal legal holiday.
(2) Saturdays, Sundays, and intervening Federal legal holidays shall be excluded from the computation of time when the period of time allowed or prescribed is 7 days or less.
(3) When a submission is required to be made within a prescribed time, DOE may grant an extension of time upon good cause shown.
(4) Documents received after regular business hours are deemed to have been submitted on the next regular business day. Regular business hours for the DOE's National Office, Washington, DC, are 8:30 a.m. to 4:30 p.m.
(5) DOE reserves the right to refuse to accept, and not to consider, untimely submissions.
(e) Filing of petitions.
(1) A petition for a rule shall be submitted in triplicate to: The Assistant Secretary for Energy Efficiency and Renewable Energy, U.S. Department of Energy, Section 327 Petitions, Building Technologies, EE-2J, Forrestal Building,1000 Independence Avenue, SW., Washington, DC 20585.
(2) A petition may be submitted on behalf of more than one person. A joint petition shall indicate each person participating in the submission. A joint petition shall provide the information required by § 431.212 for each person on whose behalf the petition is submitted.
(3) All petitions shall be signed by the person(s) submitting the petition or by a duly authorized representative. If submitted by a duly authorized representative, the petition shall certify this authorization.
(4) A petition for a rule to withdraw a rule exempting a State regulation, all supporting documents, and all future submissions shall be served on each State agency, department, or instrumentality whose regulation the petitioner seeks to supersede. The petition shall contain a certification of this service which states the name and mailing address of the served parties, and the date of service.
(f) Acceptance for filing.
(1) Within 15 days of the receipt of a petition, the Secretary will either accept it for filing or reject it, and the petitioner will be so notified in writing. The Secretary will serve a copy of this notification on each other party served by the petitioner. Only such petitions which conform to the requirements of this subpart and which contain sufficient information for the purposes of a substantive decision will be accepted for filing. Petitions which do not so conform will be rejected and an explanation provided to petitioner in writing.
(2) For purposes of the Act and this subpart, a petition is deemed to be filed on the date it is accepted for filing.
(g) Docket. A petition accepted for filing will be assigned an appropriate docket designation. Petitioner shall use the docket designation in all subsequent submissions.
(a) Promptly after receipt of a petition and its acceptance for filing, notice of such petition shall be published in the Federal Register. The notice shall set forth the availability for public review of all data and information available, and shall solicit comments, data and information with respect to the determination on the petition. Except as may otherwise be specified, the period for public comment shall be 60 days after the notice appears in the Federal Register.
(b) In addition to the material required under paragraph (a) of this section, each notice shall contain a summary of the State regulation at issue and the petitioner's reasons for the rule sought.
DOE may consolidate any or all matters at issue in two or more proceedings docketed where there exist common parties, common questions of fact and law, and where such consolidation would expedite or simplify consideration of the issues. Consolidation shall not affect the right of any party to raise issues that could have been raised if consolidation had not occurred.
The Secretary may hold a public hearing, and publish notice in the Federal Register of the date and location of the hearing, when he determines that such a hearing is necessary and likely to result in a timely and effective resolution of the issues. A transcript shall be kept of any such hearing.
(a) After the submission of public comments under § 431.213(a), the Secretary shall prescribe a final rule or deny the petition within 6 months after the date the petition is filed.
(b) The final rule issued by the Secretary or a determination by the Secretary to deny the petition shall include a written statement setting forth his findings and conclusions, and the reasons and basis therefor. A copy of the Secretary's decision shall be sent to the petitioner and the affected State agency. The Secretary shall publish in the Federal Register a notice of the final rule granting or denying the petition and the reasons and basis therefor.
(c) If the Secretary finds that he cannot issue a final rule within the 6-month period pursuant to paragraph (a) of this section, he shall publish a notice in the Federal Register extending such period to a date certain, but no longer than one year after the date on which the petition was filed. Such notice shall include the reasons for the delay.
(a) A final rule exempting a State standard from Federal preemption will be effective:
(1) Upon publication in the Federal Register if the Secretary determines that such rule is needed to meet an “energy emergency condition” within the State;
(2) Three years after such rule is published in the Federal Register; or
(3) Five years after such rule is published in the Federal Register if the Secretary determines that such additional time is necessary due to the burdens of retooling, redesign or distribution.
(b) A final rule withdrawing a rule exempting a State standard will be effective upon publication in the Federal Register.
(a) Any petitioner whose petition for a rule has been denied may request reconsideration within 30 days of denial. The request shall contain a statement of facts and reasons supporting reconsideration and shall be submitted in writing to the Secretary.
(b) The denial of a petition will be reconsidered only where it is alleged and demonstrated that the denial was based on error in law or fact and that evidence of the error is found in the record of the proceedings.
(c) If the Secretary fails to take action on the request for reconsideration within 30 days, the request is deemed denied, and the petitioner may seek such judicial review as may be appropriate and available.
(d) A petitioner has not exhausted other administrative remedies until a request for reconsideration has been filed and acted upon or deemed denied.
(a) A decision to prescribe a rule that a State energy conservation standard or other requirement not be preempted is final on the date the rule is issued, i.e., signed by the Secretary. A decision to prescribe such a rule has no effect on other regulations of covered equipment of any other State.
(b) A decision to prescribe a rule withdrawing a rule exempting a State standard or other requirement is final on the date the rule is issued, i.e., signed by the Secretary. A decision to deny such a petition is final on the day a denial of a request for reconsideration is issued, i.e., signed by the Secretary.
74 FR 32072, July 7, 2009, unless otherwise noted.
This subpart contains definitions, test procedures, and energy conservation requirements for small electric motors, pursuant to Part A-1 of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317. This subpart does not cover “electric motors,” which are addressed in subpart B of this part. This subpart does not cover electric motors that are “dedicated-purpose pool pump motors,” which are addressed in subpart Z of this part.
[77 FR 26638, May 4, 2012, as amended at 86 FR 40774, July 29, 2021]
The following definitions are applicable to this subpart:
Alternative efficiency determination method, or AEDM, means, with respect to a small electric motor, a method of calculating the total power loss and average full-load efficiency.
Average full-load efficiency means the arithmetic mean of the full-load efficiencies of a population of small electric motors of duplicate design, where the full-load efficiency of each motor in the population is the ratio (expressed as a percentage) of the motor's useful power output to its total power input when the motor is operated at its full rated load, rated voltage, and rated frequency.
Basic model means, with respect to a small electric motor, all units of a given type of small electric motor (or class thereof) manufactured by a single manufacturer, and which have the same rating, have electrical characteristics that are essentially identical, and do not have any differing physical or functional characteristics that affect energy consumption or efficiency. For the purpose of this definition, “rating” means a combination of the small electric motor's group (i.e., capacitor-start, capacitor-run; capacitor-start, induction-run; or polyphase), horsepower rating (or standard kilowatt equivalent), and number of poles with respect to which § 431.446 prescribes nominal full load efficiency standards.
Breakdown torque means the maximum torque that the motor will develop with rated voltage and frequency applied without an abrupt drop in speed. The breakdown torque is the local maximum of the torque-speed plot of the motor, closest to the synchronous speed of the motor, determined in accordance with NEMA MG 1-2016 (incorporated by reference, see § 431.443).
CSA means Canadian Standards Association.
DOE or the Department means the U.S. Department of Energy.
EPCA means the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6291-6317.
IEC means International Electrotechnical Commission.
IEEE means Institute of Electrical and Electronics Engineers, Inc.
NEMA means National Electrical Manufacturers Association.
Rated frequency means 60 hertz.
Rated load (or full load, full rated load, or rated full load) means the rated output power of a small electric motor.
Rated output power means the mechanical output power that corresponds to the small electric motor's breakdown torque as specified in NEMA MG 1-2016 Table 10-5 (incorporated by reference, see § 431.443) for single-phase motors or 140 percent of the breakdown torque values specified in NEMA MG 1-2016 Table 10-5 for polyphase motors. For purposes of this definition, NEMA MG 1-2016 Table 10-5 is applied regardless of whether elements of NEMA MG 1-2016 Table 10-5 are identified as for small or medium motors.
Rated voltage means the input voltage of a small electric motor used when making representations of the performance characteristics of a given small electric motor and selected by the motor's manufacturer to be used for testing the motor's efficiency.
Small electric motor means a NEMA general purpose alternating current single-speed induction motor, built in a two-digit frame number series in accordance with NEMA Standards Publication MG1-1987, including IEC metric equivalent motors.
[74 FR 32072, July 7, 2009, as amended at 77 FR 26638, May 4, 2012; 86 FR 23, Jan. 4, 2021]
(a) General. Certain material is incorporated by reference into subpart X of part 431 with the approval of the Director of the Federal Register under 5 U.S.C. 552(a) and 1 CFR part 51. Material is incorporated as it exists on the date of the approval, and a notification of any change in the material will be published in the Federal Register. Standards can be obtained from the sources below. All approved material is available for inspection at U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-2945, or go to http://www1.eere.energy.gov/buildings/appliance_standards/. It is also available at the National Archives and Records Administration (NARA). For information on the availability of this material at NARA, email: fedreg.legal@nara.gov, or go to: www.archives.gov/federal-register/cfr/ibr-locations.html.
(b) CAN/CSA. Canadian Standards Association, Sales Department, 5060 Spectrum Way, Suite 100, Mississauga, Ontario, L4W 5N6, Canada, 1-800-463-6727, or go to http://www.shopcsa.ca/onlinestore/welcome.asp.
(1) CSA C747-09 (“CSA C747”), Energy efficiency test methods for small motors, October 2009, IBR approved for §§ 431.444; 431.447.
(2) CSA C390-10, Test methods, marking requirements, and energy efficiency levels for three-phase induction motors, March 2010, IBR approved for §§ 431.444; 431.447.
(c) IEC. International Electrotechnical Commission, 3 rue de Varembé, 1st Floor, P.O. Box 131, CH—1211 Geneva 20—Switzerland, +41 22 919 02 11, or go to https://webstore.iec.ch/home.
(1) IEC 60034-1, Edition 12.0 2010-02, (“IEC 60034-1:2010”), Rotating electrical machines—Part 1: Rating and performance, IBR approved for §§ 431.444.
(2) IEC 60034-2-1:2014, Edition 2.0 2014-06, (“IEC 60034-2-1:2014”), Rotating electrical machines—Part 2-1: Standard methods for determining losses and efficiency from tests (excluding machines for traction vehicles), IBR approved for §§ 431.444, and 431.447.
(3) IEC 60051-1:2016, Edition 6.0 2016-02, (“IEC 60051-1:2016), Direct acting indicating analogue electrical measuring instruments and their accessories—Part 1: Definitions and general requirements common to all parts, IBR approved for §§ 431.444.
(d) IEEE. Institute of Electrical and Electronics Engineers, Inc., 445 Hoes Lane, P.O. Box 1331, Piscataway, NJ 08855-1331, 1-800-678-IEEE (4333), or go to http://www.ieee.org/web/publications/home/index.html.
(1) IEEE 112TM-2017 (“IEEE 112-2017”), IEEE Standard Test Procedure for Polyphase Induction Motors and Generators, approved December 6, 2017, IBR approved for §§ 431.444, and 431.447.
(2) IEEE Std 114-2010, Test Procedure for Single-Phase Induction Motors, approved September 30, 2010, IBR approved for §§ 431.444; 431.447.
(e) NEMA. National Electrical Manufacturers Association, 1300 North 17th Street, Suite 900, Arlington, Virginia 22209, +1 703 841 3200, or go to https://www.nema.org.
(1) NEMA MG 1-2016, American National Standard for Motors and Generators, ANSI approved June 1, 2018, IBR approved for § 431.442.
(2) [Reserved]
[74 FR 32072, July 7, 2009, as amended at 77 FR 26638, May 4, 2012; 86 FR 23, Jan. 4, 2021]
(a) Scope. Pursuant to section 346(b)(1) of EPCA, this section provides the test procedures for measuring the full-load efficiency of small electric motors pursuant to EPCA. (42 U.S.C. 6317(b)(1)) For purposes of this part 431 and EPCA, the test procedures for measuring the efficiency of small electric motors shall be the test procedures specified in paragraph (b) of this section.
(b) Testing and Calculations. Determine the full-load efficiency of a small electric motor using one of the test methods listed in this paragraphs (b)(1) through (4) of this section.
(1) Incorporation by reference: In § 431.443, DOE incorporated by reference the entire standard for CSA C747-09, CSA C390-10, IEC 60034-1:2010, IEC 60034-2-1:2014, IEC 60051-1:2016, IEEE 112-2017, and IEEE 114-2010 into this section; however, only enumerated provisions of those documents referenced in this section are applicable as follows:
(i) CSA C747-09:
(A) Section 1.6 “Scope” as specified in paragraphs (b)(2)(ii) and (b)(3)(ii) of this section;
(B) Section 3 “Definitions” as specified in paragraphs (b)(2)(ii) and (b)(3)(ii) of this section;
(C) Section 5 “General test requirements” as specified in paragraphs (b)(2)(ii) and (b)(3)(ii) of this section; and
(D) Section 6 “Test method” as specified in paragraphs (b)(2)(ii) and (b)(3)(ii) of this section.
(ii) CSA C390-10:
(A) Section 1.3, “Scope” as specified in paragraph (b)(4)(ii) of this section;
(B) Section 3.1, “Definitions” as specified in paragraph (b)(4)(ii) of this section;
(C) Section 5, “General test requirements—Measurements” as specified in paragraph (b)(4)(ii) of this section;
(D) Section 7, “Test method” as specified in paragraph (b)(4)(ii) of this section;
(E) Table 1, “Resistance measurement time delay” as specified in paragraph (b)(4)(ii) of this section;
(F) Annex B, “Linear regression analysis” as specified in paragraph (b)(4)(ii) of this section; and
(G) Annex C, “Procedure for correction of dynamometer torque readings” as specified in paragraph (b)(4)(ii) of this section.
(iii) IEC 60034-1:2010:
(A) Section 7.2 as specified in paragraphs (b)(2)(iii), (b)(3)(iii), and (b)(4)(iii) of this section;
(B) Section 8.6.2.3.3 as specified in paragraphs (b)(2)(iii), (b)(3)(iii), and (b)(4)(iii) of this section; and
(C) Table 5 as specified in paragraphs (b)(2)(iii), (b)(3)(iii), and (b)(4)(iii) of this section.
(iv) IEC 60034-2-1:2014:
(A) Method 2-1-1A as specified in paragraphs (b)(2)(iii) and (b)(3)(iii) of this section;
(B) Method 2-1-1B as specified in paragraph (b)(4)(iii) of this section;
(C) Section 3 “Terms and definitions” as specified in paragraphs (b)(2)(iii), (b)(3)(iii), and (b)(4)(iii) of this section;
(D) Section 4 “Symbols and abbreviations” as specified in paragraphs (b)(2)(iii), (b)(3)(iii), (b)(4)(iii) of this section;
(E) Section 5 “Basic requirements” as specified in paragraphs (b)(2)(iii), (b)(3)(iii), and (b)(4)(iii) of this section;
(F) Section 6.1.2 “Method 2-1-1A—Direct measurement of input and output” (except Section 6.1.2.2, “Test Procedure”) as specified in paragraphs (b)(2)(iii) and (b)(3)(iii) of this section;
(G) Section 6.1.3 “Method 2-1-1B—Summations of losses, additional load losses according to the method of residual losses” as specified in paragraph (b)(4)(iii) of this section; and
(H) Annex D, “Test report template for 2-1-1B” as specified in paragraph (b)(4)(iii) of this section.
(v) IEC 60051-1:2016:
(A) Section 5.2 as specified in paragraphs (b)(2)(iii), (b)(3)(iii) and (b)(4)(iii), of this section; and
(B) [Reserved]
(vi) IEEE 112-2017:
(A) Test Method A as specified in paragraph (b)(3)(i) of this section;
(B) Test Method B as specified in paragraph (b)(4)(i) of this section;
(C) Section 3, “General” as specified in paragraphs (b)(3)(i) and (b)(4)(i) of this section;
(D) Section 4, “Measurements” as specified in paragraphs (b)(3)(i) and (b)(4)(i) of this section;
(E) Section 5, “Machine losses and tests for losses” as specified in paragraphs (b)(3)(i) and (b)(4)(i) of this section;
(F) Section 6.1, “General” as specified in paragraphs (b)(3)(i) and (b)(4)(i) of this section;
(G) Section 6.3, “Efficiency test method A—Input-output” as specified in paragraph (b)(3)(i) of this section;
(H) Section 6.4, “Efficiency test method B—Input-output” as specified in paragraph (b)(4)(i) of this section;
(I) Section 9.2, “Form A—Method A” as specified in paragraph (b)(3)(i) of this section;
(J) Section 9.3, “Form A2—Method A calculations” as specified in paragraph (b)(3)(i) of this section;
(K) Section 9.4, “Form B—Method B” as specified in paragraph (b)(4)(i) of this section; and
(L) Section 9.5, “Form B2—Method B calculations” as specified in paragraph (b)(4)(i) of this section.
(vii) IEEE 114-2010:
(A) Section 3.2, “Test with load” as specified in paragraph (b)(2)(i) of this section;
(B) Section 4, “Testing Facilities as specified in paragraph (b)(2)(i) of this section;
(C) Section 5, “Measurements” as specified in paragraph (b)(2)(i) of this section;
(D) Section 6, “General” as specified in paragraph (b)(2)(i) of this section;
(E) Section 7, “Type of loss” as specified in paragraph (b)(2)(i) of this section;
(F) Section 8, “Efficiency and Power Factor” as specified in paragraph (b)(2)(i) of this section;
(G) Section 10 “Temperature Tests” as specified in paragraph (b)(2)(i) of this section;
(H) Annex A, Section A.3 “Determination of Motor Efficiency” as specified in paragraph (b)(2)(i) of this section; and
(I) Annex A, Section A.4 “Explanatory notes for form 3, test data” as specified in paragraph (b)(2)(i) of this section.
(viii) In cases where there is a conflict, the language of this appendix takes precedence over those documents. Any subsequent amendment to a referenced document by the standard-setting organization will not affect the test procedure in this appendix, unless and until the test procedure is amended by DOE.
(2) Single-phase small electric motors. For single-phase small electric motors, use one of the following methods:
(i) IEEE 114-2010, Section 3.2, “Test with load”, Section 4, “Testing Facilities, Section 5, “Measurements”, Section 6, “General”, Section 7, “Type of loss”, Section 8, “Efficiency and Power Factor”; Section 10 “Temperature Tests”, Annex A, Section A.3 “Determination of Motor Efficiency”, Annex A, Section A.4 “Explanatory notes for form 3, test data”;
(ii) CSA C747-09, Section 1.6 “Scope”, Section 3 “Definitions”, Section 5, “General test requirements”, and Section 6 “Test method”;
(iii) IEC 60034-2-1:2014 Method 2-1-1A, Section 3 “Terms and definitions”, Section 4 “Symbols and abbreviations”, Section 5 “Basic requirements”, and Section 6.1.2 “Method 2-1-1A—Direct measurement of input and output” (except Section 6.1.2.2, “Test Procedure”). The supply voltage shall be in accordance with section 7.2 of IEC 60034-1:2010 (incorporated by reference, see § 431.443). The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in section 8.6.2.3.3 of IEC 60034-1:2010, using the shortest possible time instead of the time interval specified in Table 5 therein, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with section 5.2 of IEC 60051-1:2016 (incorporated by reference, see § 431.443).
(A) Additional IEC 60034-2-1:2014 Method 2-1-1A Torque Measurement Instructions.
If using IEC 60034-2-1:2014 Method 2-1-1A to measure motor performance, follow the instructions in paragraph (b)(2)(iii)(B) of this section, instead of section 6.1.2.2 of IEC 60034-2-1:2014;
(B) Couple the machine under test to a load machine. Measure torque using an in-line, shaft-coupled, rotating torque transducer or stationary, stator reaction torque transducer. Operate the machine under test at the rated load until thermal equilibrium is achieved (rate of change 1 K or less per half hour). Record U, I, Pel, n, T, θc.
(3) Polyphase small electric motors of less than or equal to 1 horsepower (0.75 kW). For polyphase small electric motors with 1 horsepower or less, use one of the following methods:
(i) IEEE 112-2017 Test Method A, Section 3, “General”, Section 4, “Measurements”, Section 5, “Machine losses and tests for losses”, Section 6.1, “General”, Section 6.3, “Efficiency test method A—Input-output”, Section 9.2, “Form A—Method A”, and Section 9.3, “Form A2—Method A calculations”;
(ii) CSA C747-09, Section 1.6 “Scope”, Section 3 “Definitions”, Section 5, “General test requirements”, and Section 6 “Test method”;
(iii) IEC 60034-2-1:2014 Method 2-1-1A, Section 3 “Terms and definitions”, Section 4 “Symbols and abbreviations”, Section 5 “Basic requirements”, and Section 6.1.2 “Method 2-1-1A—Direct measurement of input and output” (except Section 6.1.2.2, “Test Procedure”). The supply voltage shall be in accordance with section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in section 8.6.2.3.3 of IEC 60034-1:2010 using the shortest possible time instead of the time interval specified in Table 5 therein, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with section 5.2 of IEC 60051-1:2016.
(A) Additional IEC 60034-2-1:2014 Method 2-1-1A Torque Measurement Instructions.
If using IEC 60034-2-1:2014 Method 2-1-1A to measure motor performance, follow the instructions in paragraph (b)(3)(iii)(B) of this section, instead of section 6.1.2.2 of IEC 60034-2-1:2014;
(B) Couple the machine under test to load machine. Measure torque using an in-line shaft-coupled, rotating torque transducer or stationary, stator reaction torque transducer. Operate the machine under test at the rated load until thermal equilibrium is achieved (rate of change 1 K or less per half hour). Record U, I, Pel, n, T, θc.
(4) Polyphase small electric motors of greater than 1 horsepower (0.75 kW). For polyphase small electric motors exceeding 1 horsepower, use one of the following methods:
(i) IEEE 112-2017 Test Method B, Section 3, “General”; Section 4, “Measurements”; Section 5, “Machine losses and tests for losses”, Section 6.1, “General”, Section 6.4, “Efficiency test method B—Input-output with loss segregation”, Section 9.4, “Form B—Method B”, and Section 9.5, “Form B2—Method B calculations”; or
(ii) CSA C390-10, Section 1.3, “Scope”, Section 3.1, “Definitions”, Section 5, “General test requirements—Measurements”, Section 7, “Test method”, Table 1, “Resistance measurement time delay, Annex B, “Linear regression analysis”, and Annex C, “Procedure for correction of dynamometer torque readings”; or
(iii) IEC 60034-2-1:2014 Method 2-1-1B Section 3 “Terms and definitions”, Section 4 “Symbols and abbreviations”, Section 5 “Basic requirements”, Section 6.1.3 “Method 2-1-1B—Summation of losses, additional load losses according to the method of residual losses.”, and Annex D, “Test report template for 2-1-1B. The supply voltage shall be in accordance with section 7.2 of IEC 60034-1:2010. The measured resistance at the end of the thermal test shall be determined in a similar way to the extrapolation procedure described in section 8.6.2.3.3 of IEC 60034-1:2010 using the shortest possible time instead of the time interval specified in Table 5 therein, and extrapolating to zero. The measuring instruments for electrical quantities shall have the equivalent of an accuracy class of 0,2 in case of a direct test and 0,5 in case of an indirect test in accordance with section 5.2 of IEC 60051-1:2016.
[86 FR 23, Jan. 4, 2021]
(a) Scope. When a party determines the energy efficiency of a small electric motor to comply with an obligation imposed on it by or pursuant to Part A-1 of Title III of EPCA, 42 U.S.C. 6311-6317, this section applies.
(b) Provisions applicable to all small electric motors —
(1) General requirements. The average full-load efficiency of each basic model of small electric motor must be determined either by testing in accordance with § 431.444 of this subpart, or by application of an alternative efficiency determination method (AEDM) that meets the requirements of paragraphs (a)(2) and (3) of this section, provided, however, that an AEDM may be used to determine the average full-load efficiency of one or more of a manufacturer's basic models only if the average full-load efficiency of at least five of its other basic models is determined through testing.
(2) Alternative efficiency determination method. An AEDM applied to a basic model must be:
(i) Derived from a mathematical model that represents the mechanical and electrical characteristics of that basic model, and
(ii) Based on engineering or statistical analysis, computer simulation or modeling, or other analytic evaluation of performance data.
(3) Substantiation of an alternative efficiency determination method. Before an AEDM is used, its accuracy and reliability must be substantiated as follows:
(i) The AEDM must be applied to at least five basic models that have been tested in accordance with § 431.444; and
(ii) The predicted total power loss for each such basic model, calculated by applying the AEDM, must be within plus or minus 10 percent of the mean total power loss determined from the testing of that basic model.
(4) Subsequent verification of an AEDM.
(i) Each manufacturer that has used an AEDM under this section shall have available for inspection by the Department of Energy records showing the method or methods used; the mathematical model, the engineering or statistical analysis, computer simulation or modeling, and other analytic evaluation of performance data on which the AEDM is based; complete test data, product information, and related information that the manufacturer has generated or acquired pursuant to paragraph (a)(3) of this section; and the calculations used to determine the efficiency and total power losses of each basic model to which the AEDM was applied.
(ii) If requested by the Department, the manufacturer shall conduct simulations to predict the performance of particular basic models of small electric motors specified by the Department, analyses of previous simulations conducted by the manufacturer, sample testing of basic models selected by the Department, or a combination of the foregoing.
(5) Use of a certification program.
(i) A manufacturer may use a certification program, that DOE has classified as nationally recognized under § 431.447, to certify the average full-load efficiency of a basic model of small electric motor, and issue a certificate of conformity for the small electric motor.
(ii) For each basic model for which a certification program is not used as described in paragraph (b)(5)(i) of this section, any testing of a motor to determine its energy efficiency must be carried out in accordance with paragraph (c) of this section.
(c) Additional testing requirements applicable when a certification program is not used —
(1) Selection of basic models for testing.
(i) Basic models must be selected for testing in accordance with the following criteria:
(A) Two of the basic models must be among the five basic models that have the highest unit volumes of production by the manufacturer in the prior year, or during the prior 12 calendar month period beginning in 2015, whichever is later, and comply with the standards set forth in § 431.446;
(B) The basic models should be of different horsepowers without duplication;
(C) At least one basic model should be selected from each of the frame number series for which the manufacturer is seeking compliance; and
(D) Each basic model should have the lowest average full-load efficiency among the basic models with the same rating (“rating” as used here has the same meaning as it has in the definition of “basic model”).
(ii) In any instance where it is impossible for a manufacturer to select basic models for testing in accordance with all of these criteria, the criteria shall be given priority in the order in which they are listed. Within the limits imposed by the criteria, basic models shall be selected randomly.
(2) Selection of units for testing within a basic model. For each basic model selected for testing,[1] a sample of units shall be selected at random and tested. The sample shall be comprised of production units of the basic model, or units that are representative of such production units. The sample size shall be no fewer than five units, except when fewer than five units of a basic model would be produced over a reasonable period of time (approximately 180 days). In such cases, each unit produced shall be tested.
(3) Applying results of testing. When applying the test results to determine whether a motor complies with the required average efficiency level:
The average full-load efficiency of the sample, X̄ which is defined by
where Xi is the measured full-load efficiency of unit i and n is the number of units tested, shall satisfy the condition:
where RE is the required average full-load efficiency.
[74 FR 32072, July 7, 2009, as amended at 77 FR 26638, May 4, 2012]
(a) Each small electric motor manufactured (alone or as a component of another piece of non-covered equipment) after March 9, 2015, or in the case of a small electric motor which requires listing or certification by a nationally recognized safety testing laboratory, after March 9, 2017, shall have an average full load efficiency of not less than the following:
| Motor horsepower/standard kilowatt equivalent | Average full load efficiency | ||
|---|---|---|---|
| Polyphase | |||
| Open motors (number of poles) | |||
| 6 | 4 | 2 | |
| 0.25/0.18 | 67.5 | 69.5 | 65.6 |
| 0.33/0.25 | 71.4 | 73.4 | 69.5 |
| 0.5/0.37 | 75.3 | 78.2 | 73.4 |
| 0.75/0.55 | 81.7 | 81.1 | 76.8 |
| 1/0.75 | 82.5 | 83.5 | 77.0 |
| 1.5/1.1 | 83.8 | 86.5 | 84.0 |
| 2/1.5 | N/A | 86.5 | 85.5 |
| 3/2.2 | N/A | 86.9 | 85.5 |
| Motor horsepower/standard kilowatt equivalent | Average full load efficiency | ||
|---|---|---|---|
| Capacitor-start capacitor-run and capacitor-start induction-run | |||
| Open motors (number of poles) | |||
| 6 | 4 | 2 | |
| 0.25/0.18 | 62.2 | 68.5 | 66.6 |
| 0.33/0.25 | 66.6 | 72.4 | 70.5 |
| 0.5/0.37 | 76.2 | 76.2 | 72.4 |
| 0.75/0.55 | 80.2 | 81.8 | 76.2 |
| 1/0.75 | 81.1 | 82.6 | 80.4 |
| 1.5/1.1 | N/A | 83.8 | 81.5 |
| 2/1.5 | N/A | 84.5 | 82.9 |
| 3/2.2 | N/A | N/A | 84.1 |
(b) For purposes of determining the required minimum average full load efficiency of an electric motor that has a horsepower or kilowatt rating between two horsepower or two kilowatt ratings listed in any table of efficiency standards in paragraph (a) of this section, each such motor shall be deemed to have a listed horsepower or kilowatt rating, determined as follows:
(1) A horsepower at or above the midpoint between the two consecutive horsepower ratings shall be rounded up to the higher of the two horsepower ratings;
(2) A horsepower below the midpoint between the two consecutive horsepower ratings shall be rounded down to the lower of the two horsepower ratings; or
(3) A kilowatt rating shall be directly converted from kilowatts to horsepower using the formula 1 kilowatt = (1/0.746) hp, without calculating beyond three significant decimal places, and the resulting horsepower shall be rounded in accordance with paragraphs (b)(1) or (b)(2) of this section, whichever applies.
[75 FR 10947, Mar. 9, 2010; 75 FR 17036, Apr. 5, 2010]
(a) Petition. For a certification program to be classified by the Department of Energy as being nationally recognized in the United States (“nationally recognized”), the organization operating the program must submit a petition to the Department requesting such classification, in accordance with paragraph (c) of this section and § 431.448. The petition must demonstrate that the program meets the criteria in paragraph (b) of this section.
(b) Evaluation criteria. For a certification program to be classified by the Department as nationally recognized, it must meet the following criteria:
(1) It must have satisfactory standards and procedures for conducting and administering a certification system, including periodic follow up activities to assure that basic models of small electric motors continue to conform to the efficiency levels for which they were certified, and for granting a certificate of conformity.
(2) It must be independent of small electric motor manufacturers, importers, distributors, private labelers or vendors. It cannot be affiliated with, have financial ties with, be controlled by, or be under common control with any such entity.
(3) It must be qualified to operate a certification system in a highly competent manner.
(4) It must be expert in the content and application of the test procedures and methodologies in IEEE 112-2017 Test Method A, IEEE 112-2017 Test Method B, IEEE 114-2010, IEC 60034-2-1:2014 Method 2-1-1A, IEC 60034-2-1:2014 Method 2-1-1B, CSA C390-10, or CSA C747-09 (incorporated by reference, see § 431.443) or similar procedures and methodologies for determining the energy efficiency of small electric motors. It must have satisfactory criteria and procedures for the selection and sampling of electric motors tested for energy efficiency.
(c) Petition format. Each petition requesting classification as a nationally recognized certification program must contain a narrative statement as to why the program meets the criteria listed in paragraph (b) of this section, must be signed on behalf of the organization operating the program by an authorized representative, and must be accompanied by documentation that supports the narrative statement. The following provides additional guidance as to the specific criteria:
(1) Standards and procedures. A copy of the standards and procedures for operating a certification system and for granting a certificate of conformity should accompany the petition.
(2) Independent status. The petitioning organization should identify and describe any relationship, direct or indirect, that it or the certification program has with an electric motor manufacturer, importer, distributor, private labeler, vendor, trade association or other such entity, as well as any other relationship it believes might appear to create a conflict of interest for the certification program in operating a certification system for determining the compliance of small electric motors with the applicable energy efficiency standards. It should explain why it believes such relationship would not compromise its independence in operating a certification program.
(3) Qualifications to operate a certification system. Experience in operating a certification system should be discussed and substantiated by supporting documents. Of particular relevance would be documentary evidence that establishes experience in the application of guidelines contained in the ISO/IEC Guide 65, General requirements for bodies operating product certification systems, ISO/IEC Guide 27, Guidelines for corrective action to be taken by a certification body in the event of either misapplication of its mark of conformity to a product, or products which bear the mark of the certification body being found to subject persons or property to risk, and ISO/IEC Guide 28, General rules for a model third-party certification system for products, as well as experience in overseeing compliance with the guidelines contained in the ISO/IEC Guide 25, General requirements for the competence of calibration and testing laboratories.
(4) Expertise in small electric motor test procedures. The petition should set forth the program's experience, as applicable, with the test procedures and methodologies in, IEEE 112-2017 Test Method A, IEEE 112-2017 Test Method B, IEEE 114-2010, IEC 60034-2-1:2014 Method 2-1-1A, IEC 60034-2-1:2014 Method 2-1-1B, CSA C390-10, and CSA C747-09 (incorporated by reference, see § 431.443) and with similar procedures and methodologies. This part of the petition should include items such as, but not limited to, a description of prior projects and qualifications of staff members. Of particular relevance would be documentary evidence that establishes experience in applying guidelines contained in the ISO/IEC Guide 25, General Requirements for the Competence of Calibration and Testing Laboratories to energy efficiency testing for electric motors.
(5) The ISO/IEC Guides referenced in paragraphs (c)(3) and (c)(4) of this section are not incorporated by reference, but are for information and guidance only. International Organization for Standardization (ISO), 1, ch. de la Voie-Creuse, CP 56, CH-1211 Geneva 20, Switzerland/International Electrotechnical Commission, 3, rue de Varembé, P.O. Box 131, CH-1211 Geneva 20, Switzerland.
(d) Disposition. The Department will evaluate the petition in accordance with § 431.448, and will determine whether the applicant meets the criteria in paragraph (b) of this section for classification as a nationally recognized certification program.
[77 FR 26639, May 4, 2012, as amended at 86 FR 25, Jan. 4, 2021]
(a) Filing of petition. Any petition submitted to the Department pursuant to § 431.447(a), shall be entitled “Petition for Recognition” (“Petition”) and must be submitted, in triplicate to the Assistant Secretary for Energy Efficiency and Renewable Energy, U.S. Department of Energy, Forrestal Building, 1000 Independence Avenue SW., Washington, DC 20585-0121. In accordance with the provisions set forth in 10 CFR 1004.11, any request for confidential treatment of any information contained in such a Petition or in supporting documentation must be accompanied by a copy of the Petition or supporting documentation from which the information claimed to be confidential has been deleted.
(b) Public notice and solicitation of comments. DOE shall publish in the Federal Register the Petition from which confidential information, as determined by DOE, has been deleted in accordance with 10 CFR 1004.11 and shall solicit comments, data and information on whether the Petition should be granted. The Department shall also make available for inspection and copying the Petition's supporting documentation from which confidential information, as determined by DOE, has been deleted in accordance with 10 CFR 1004.11. Any person submitting written comments to DOE with respect to a Petition shall also send a copy of such comments to the petitioner.
(c) Responsive statement by the petitioner. A petitioner may, within 10 working days of receipt of a copy of any comments submitted in accordance with paragraph (b) of this section, respond to such comments in a written statement submitted to the Assistant Secretary for Energy Efficiency and Renewable Energy. A petitioner may address more than one set of comments in a single responsive statement.
(d) Public announcement of interim determination and solicitation of comments. The Assistant Secretary for Energy Efficiency and Renewable Energy shall issue an interim determination on the Petition as soon as is practicable following receipt and review of the Petition and other applicable documents, including, but not limited to, comments and responses to comments. The petitioner shall be notified in writing of the interim determination. DOE shall also publish in the Federal Register the interim determination and shall solicit comments, data and information with respect to that interim determination. Written comments and responsive statements may be submitted as provided in paragraphs (b) and (c) of this section.
(e) Public announcement of final determination. The Assistant Secretary for Energy Efficiency and Renewable Energy shall, as soon as practicable, following receipt and review of comments and responsive statements on the interim determination publish in the Federal Register a notice of final determination on the Petition.
(f) Additional information. The Department may, at any time during the recognition process, request additional relevant information or conduct an investigation concerning the Petition. The Department's determination on a Petition may be based solely on the Petition and supporting documents, or may also be based on such additional information as the Department deems appropriate.
(g) Withdrawal of recognition —
(1) Withdrawal by the Department. If the Department believes that a certification program that has been recognized under § 431.447 is failing to meet the criteria of paragraph (b) of the section under which it is recognized, the Department will so advise such entity and request that it take appropriate corrective action. The Department will give the entity an opportunity to respond. If after receiving such response, or no response, the Department believes satisfactory corrective action has not been made, the Department will withdraw its recognition from that entity.
(2) Voluntary withdrawal. A certification program may withdraw itself from recognition by the Department by advising the Department in writing of such withdrawal. It must also advise those that use it (for a certification organization, the manufacturers) of such withdrawal.
(3) Notice of withdrawal of recognition. The Department will publish in the Federal Register a notice of any withdrawal of recognition that occurs pursuant to this paragraph (g).
[77 FR 26639, May 4, 2012]
81 FR 4145, Jan. 25, 2016, unless otherwise noted.
This subpart contains definitions, test procedures, and energy conservation requirements for pumps, pursuant to Part A-1 of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317.
The following definitions are applicable to this subpart, including appendices A, B, and C. In cases where definitions reference design intent, DOE will consider marketing materials, labels and certifications, and equipment design to determine design intent.
Adaptive pressure control means a pressure control that senses the head requirements in the system in which it is installed and adjusts the pump control curve accordingly.
Bare pump means a pump excluding mechanical equipment, driver, and controls.
Basic model means all units of a given class of pump manufactured by one manufacturer, having the same primary energy source, and having essentially identical electrical, physical, and functional (or hydraulic) characteristics that affect energy consumption, energy efficiency, water consumption, or water efficiency; and, in addition, for pumps that are subject to the test procedures specified in § 431.464(a), the following provisions also apply:
(1) All variations in numbers of stages of bare RSV and ST pumps must be considered a single basic model;
(2) Pump models for which the bare pump differs in impeller diameter and/or impeller trim, may be considered a single basic model; and
(3) Pump models for which the bare pump differs in number of stages and/or impeller diameter and which are sold with motors (or motors and controls) of varying horsepower may only be considered a single basic model if:
(i) For ESCC, ESFM, IL, and RSV pumps, each motor offered in the basic model has a nominal full load motor efficiency rated at the Federal minimum (see the applicable table at § 431.25) or the same number of bands above the Federal minimum for each respective motor horsepower (see table 3 of appendix A to this subpart); or for pumps sold with inverter-only synchronous electric motors, any number of bands above the Federal minimum for each respective motor horsepower provided that the rating is based on the lowest number of bands; or
(ii) For ST pumps, each motor offered in the basic model has a full load motor efficiency at the default nominal full load submersible motor efficiency shown in table 2 of appendix A to subpart Y of this part or the same number of bands above the default nominal full load submersible motor efficiency for each respective motor horsepower (see table 3 of appendix A to this subpart) or for inverter-only synchronous electric motors, any number of bands above the default nominal full load submersible motor efficiency provided the rating is based on the lowest number of bands.
Basket strainer means a perforated or otherwise porous receptacle, mounted within a housing on the suction side of a pump, that prevents solid debris from entering a pump. The basket strainer receptacle is capable of passing spherical solids of 1 mm in diameter, and can be removed by hand or using only simple tools (e.g., screwdriver, pliers, open-ended wrench).
Best efficiency point (BEP) means the pump hydraulic power operating point (consisting of both flow and head conditions) that results in the maximum efficiency.
Bowl means a casing in which the impeller rotates, and that directs flow axially to the next stage or the discharge column.
Bowl diameter means the maximum dimension of an imaginary straight line passing through and in the plane of the circular shape of the bowl of the bare pump that is perpendicular to the pump shaft and that intersects the outermost circular shape of the bowl of the bare pump at both of its ends.
Circulator-less-volute means a circulator pump distributed in commerce without a volute and for which a paired volute is also distributed in commerce. Whether a paired volute is distributed in commerce will be determined based on published data, marketing literature, and other publicly available information.
Circulator pump means is a pump that is either a wet rotor circulator pumps; a dry rotor, two-piece circulator pump; or a dry rotor, three-piece circulator pump. A circulator pump may be distributed in commerce with or without a volute.
Clean water pump means a pump that is designed for use in pumping water with a maximum non-absorbent free solid content of 0.016 pounds per cubic foot, and with a maximum dissolved solid content of 3.1 pounds per cubic foot, provided that the total gas content of the water does not exceed the saturation volume, and disregarding any additives necessary to prevent the water from freezing at a minimum of 14 °F.
Close-coupled pump means a pump in which the driver's bearings are designed to absorb the pump's axial load.
Continuous control means a control that adjusts the speed of the pump driver continuously over the driver operating speed range in response to incremental changes in the required pump flow, head, or power output.
Control means any device that can be used to operate the driver. Examples include, but are not limited to, continuous or non-continuous controls, schedule-based controls, on/off switches, and float switches.
Dedicated-purpose pool pump comprises self-priming pool filter pumps, non-self-priming pool filter pumps, waterfall pumps, pressure cleaner booster pumps, integral sand-filter pool pumps, integral-cartridge filter pool pumps, storable electric spa pumps, and rigid electric spa pumps.
Dedicated-purpose pool pump motor total horsepower means the product of the dedicated-purpose pool pump nominal motor horsepower and the dedicated-purpose pool pump service factor of a motor used on a dedicated-purpose pool pump based on the maximum continuous duty motor power output rating allowable for the motor's nameplate ambient rating and insulation class. (Dedicated-purpose pool pump motor total horsepower is also referred to in the industry as service factor horsepower or motor capacity.)
Dedicated-purpose pool pump service factor means a multiplier applied to the rated horsepower of a pump motor to indicate the percent above nameplate horsepower at which the motor can operate continuously without exceeding its allowable insulation class temperature limit.
Designed and marketed means that the equipment is designed to fulfill the indicated application and, when distributed in commerce, is designated and marketed for that application, with the designation on the packaging and any publicly available documents (e.g., product literature, catalogs, and packaging labels).
Driver means the machine providing mechanical input to drive a bare pump directly or through the use of mechanical equipment. Examples include, but are not limited to, an electric motor, internal combustion engine, or gas/steam turbine.
Dry rotor pump means a pump in which the motor rotor is not immersed in the pumped fluid.
Dry rotor, three-piece circulator pump means:
(1) A single stage, rotodynamic, single-axis flow, mechanically-coupled, dry rotor pump that:
(i) Has a rated hydraulic power less than or equal to 5 hp at the best efficiency point at full impeller diameter,
(ii) Is distributed in commerce with a horizontal motor, and
(iii) Discharges the pumped liquid through a volute in a plane perpendicular to the shaft.
(2) Examples include, but are not limited to, pumps generally referred to in industry as CP3.
Dry rotor, two-piece circulator pump means:
(1) A single stage, rotodynamic, single-axis flow, close-coupled, dry rotor pump that:
(i) Has a rated hydraulic power less than or equal to 5 hp at best efficiency point at full impeller diameter,
(ii) Is distributed in commerce with a horizontal motor, and
(iii) Discharges the pumped liquid through a volute in a plane perpendicular to the shaft.
(2) Examples include, but are not limited to, pumps generally referred to in industry as CP2.
End-suction close-coupled (ESCC) pump means a close-coupled, dry rotor, end-suction pump that has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and that is not a dedicated-purpose pool pump.
End-suction frame mounted/own bearings (ESFM) pump means a mechanically-coupled, dry rotor, end-suction pump that has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and that is not a dedicated-purpose pool pump.
End-suction pump means a single-stage, rotodynamic pump in which the liquid enters the bare pump in a direction parallel to the impeller shaft and on the side opposite the bare pump's driver-end. The liquid is discharged in a plane perpendicular to the shaft.
External input signal control means a variable speed drive that adjusts the speed of the driver in response to an input signal from an external logic and/or user interface.
Fire pump means a pump that is compliant with NFPA 20-2016 (incorporated by reference, see § 431.463), “Standard for the Installation of Stationary Pumps for Fire Protection,” and is either:
(1) UL listed under ANSI/UL 448-2013 (incorporated by reference, see § 431.463), “Standard for Safety Centrifugal Stationary Pumps for Fire-Protection Service,” or
(2) FM Global (FM) approved under the January 2015 edition of FM Class Number 1319, “Approval Standard for Centrifugal Fire Pumps (Horizontal, End Suction Type),” (incorporated by reference, see § 431.463).
Freeze protection control means a pool pump control that, at a certain ambient temperature, turns on the dedicated-purpose pool pump to circulate water for a period of time to prevent the pool and water in plumbing from freezing.
Full impeller diameter means the maximum diameter impeller with which a given pump basic model is distributed in commerce.
Header pump means a circulator pump distributed in commerce without a volute and for which a paired volute is not distributed in commerce. Whether a paired volute is distributed in commerce will be determined based on published data, marketing literature, and other publicly available information.
Horizontal motor means a motor, for which the motor shaft position when functioning under operating conditions specified in manufacturer literature, includes a horizontal position.
In-line (IL) pump means a pump that is either a twin head pump or a single-stage, single-axis flow, dry rotor, rotodynamic pump that has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter, in which liquid is discharged in a plane perpendicular to the shaft. Such pumps do not include circulator pumps.
Integral means a part of the device that cannot be removed without compromising the device's function or destroying the physical integrity of the unit.
Integral cartridge-filter pool pump means a pump that requires a removable cartridge filter, installed on the suction side of the pump, for operation; and the cartridge filter cannot be bypassed.
Integral sand-filter pool pump means a pump distributed in commerce with a sand filter that cannot be bypassed.
Magnet driven pump means a pump in which the bare pump is isolated from the motor via a containment shell and torque is transmitted from the motor to the bare pump via magnetic force. The motor shaft is not physically coupled to the impeller or impeller shaft.
Manual speed control means a control (variable speed drive and user interface) that adjusts the speed of the driver based on manual user input.
Mechanical equipment means any component of a pump that transfers energy from the driver to the bare pump.
Mechanically-coupled pump means a pump in which bearings external to the driver are designed to absorb the pump's axial load.
Multi-speed dedicated-purpose pool pump means a dedicated-purpose pool pump that is capable of operating at more than two discrete, pre-determined operating speeds separated by speed increments greater than 100 rpm, where the lowest speed is less than or equal to half of the maximum operating speed and greater than zero, and must be distributed in commerce with an on-board pool pump control (i.e., variable speed drive and user interface or programmable switch) that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times.
Non-continuous control means a control that adjusts the speed of a driver to one of a discrete number of non-continuous preset operating speeds, and does not respond to incremental reductions in the required pump flow, head, or power output.
Non-self-priming pool filter pump means a pool filter pump that is not certified under NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) to be self-priming and is not capable of re-priming to a vertical lift of at least 5.0 feet with a true priming time less than or equal to 10.0 minutes, when tested in accordance with section F of appendix B or C of this subpart, and is not a waterfall pump.
On-demand circulator pump means a circulator pump that is distributed in commerce with an integral control that:
(1) Initiates water circulation based on receiving a signal from the action of a user [of a fixture or appliance] or sensing the presence of a user of a fixture and cannot initiate water circulation based on other inputs, such as water temperature or a pre-set schedule.
(2) Automatically terminates water circulation once hot water has reached the pump or desired fixture.
(3) Does not allow the pump to operate when the temperature in the pipe exceeds 104 °F or for more than 5 minutes continuously.
Pool filter pump means an end suction pump that:
(1) Either:
(i) Includes an integrated basket strainer; or
(ii) Does not include an integrated basket strainer, but requires a basket strainer for operation, as stated in manufacturer literature provided with the pump; and
(2) May be distributed in commerce connected to, or packaged with, a sand filter, removable cartridge filter, or other filtration accessory, so long as the filtration accessory are connected with consumer-removable connections that allow the filtration accessory to be bypassed.
Pool pump timer means a pool pump control that automatically turns off a dedicated-purpose pool pump after a run-time of no longer than 10 hours.
Pressure cleaner booster pump means an end suction, dry rotor pump designed and marketed for pressure-side pool cleaner applications, and which may be UL listed under ANSI/UL 1081-2016 (incorporated by reference, see § 431.463).
Pressure control means a control (variable speed drive and integrated logic) that automatically adjusts the speed of the driver in response to pressure.
Prime-assist pump means a pump that:
(1) Is designed to lift liquid that originates below the centerline of the pump inlet;
(2) Requires no manual intervention to prime or re-prime from a dry-start condition; and
(3) Includes a device, such as a vacuum pump or air compressor and venturi eductor, to remove air from the suction line in order to automatically perform the prime or re-prime function at any point during the pump's operating cycle.
Pump means equipment designed to move liquids (which may include entrained gases, free solids, and totally dissolved solids) by physical or mechanical action and includes a bare pump and, if included by the manufacturer at the time of sale, mechanical equipment, driver, and controls.
Radially-split, multi-stage, horizontal, diffuser casing (RSH) pump means a horizontal, multi-stage, dry rotor, rotodynamic pump:
(1) That has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and at the number of stages required for testing;
(2) In which liquid is discharged in a plane perpendicular to the impeller shaft;
(3) For which each stage (or bowl) consists of an impeller and diffuser; and
(4) For which no external part of such a pump is designed to be submerged in the pumped liquid.
Radially-split, multi-stage, horizontal, end-suction diffuser casing (RSHES) pump means a RSH pump in which the liquid enters the bare pump in a direction parallel to the impeller shaft and on the side opposite the bare pump's driver-end.
Radially-split, multi-stage, horizontal, in-line diffuser casing (RSHIL) pump means a single-axis flow RSH pump in which the liquid enters the pump in a plane perpendicular to the impeller shaft.
Radially-split, multi-stage, vertical, diffuser casing (RSV) pump means a vertically suspended, multi-stage, single-axis flow, dry rotor, rotodynamic pump:
(1) That has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and at the number of stages required for testing;
(2) In which liquid is discharged in a plane perpendicular to the impeller shaft;
(3) For which each stage (or bowl) consists of an impeller and diffuser; and
(4) For which no external part of such a pump is designed to be submerged in the pumped liquid.
Removable cartridge filter means a filter component with fixed dimensions that captures and removes suspended particles from water flowing through the unit. The removable cartridge filter is not capable of passing spherical solids of 1 mm in diameter or greater, and can be removed from the filter housing by hand or using only simple tools (e.g., screwdrivers, pliers, open-ended wrench).
Rigid electric spa pump means an end suction pump that does not contain an integrated basket strainer or require a basket strainer for operation as stated in manufacturer literature provided with the pump and that meets the following three criteria:
(1) Is assembled with four through bolts that hold the motor rear endplate, rear bearing, rotor, front bearing, front endplate, and the bare pump together as an integral unit;
(2) Is constructed with buttress threads at the inlet and discharge of the bare pump; and
(3) Uses a casing or volute and connections constructed of a non-metallic material.
Rotodynamic pump means a pump in which energy is continuously imparted to the pumped fluid by means of a rotating impeller, propeller, or rotor.
Sand filter means a device designed to filter water through sand or an alternate sand-type media.
Self-priming pool filter pump means a pool filter pump that is certified under NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) to be self-priming or is capable of re-priming to a vertical lift of at least 5.0 feet with a true priming time less than or equal to 10.0 minutes, when tested in accordance with section F of appendix B or C of this subpart, and is not a waterfall pump.
Self-priming pump means a pump that either is a self-priming pool filter pump or a pump that:
(1) Is designed to lift liquid that originates below the centerline of the pump inlet;
(2) Contains at least one internal recirculation passage; and
(3) Requires a manual filling of the pump casing prior to initial start-up, but is able to re-prime after the initial start-up without the use of external vacuum sources, manual filling, or a foot valve.
Single axis flow pump means a pump in which the liquid inlet of the bare pump is on the same axis as the liquid discharge of the bare pump.
Single-speed dedicated-purpose pool pump means a dedicated-purpose pool pump that is capable of operating at only one speed.
Small vertical in-line (SVIL) pump means a small vertical twin-head pump or a single stage, single-axis flow, dry rotor, rotodynamic pump that:
(1) Has a shaft input power less than 1 horsepower at its BEP at full impeller diameter; and
(2) In which liquid is discharged in a plane perpendicular to the shaft; and
(3) Is not a circulator pump.
Small vertical twin-head pump means a dry rotor, single-axis flow, rotodynamic pump that contains two equivalent impeller assemblies, each of which:
(1) Contains an impeller, impeller shaft (or motor shaft in the case of close-coupled pumps), shaft seal or packing, driver (if present), and mechanical equipment (if present); and
(2) Has a shaft input power that is less than or equal to 1 hp at BEP and full impeller diameter; and
(3) Has the same primary energy source (if sold with a driver) and the same electrical, physical, and functional characteristics that affect energy consumption or energy efficiency; and
(4) Is mounted in its own volute; and
(5) Discharges liquid through its volute and the common discharge in a plane perpendicular to the impeller shaft.
Storable electric spa pump means a pump that is distributed in commerce with one or more of the following:
(1) An integral heater; and
(2) An integral air pump.
Submersible pump means a pump that is designed to be operated with the motor and bare pump fully submerged in the pumped liquid.
Submersible turbine (ST) pump means a single-stage or multi-stage, dry rotor, rotodynamic pump that is designed to be operated with the motor and stage(s) fully submerged in the pumped liquid; that has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and at the number of stages required for testing; and in which each stage of this pump consists of an impeller and diffuser, and liquid enters and exits each stage of the bare pump in a direction parallel to the impeller shaft.
Temperature control means a control (variable speed drive and integrated logic) that automatically adjusts the speed of the driver continuously over the driver operating speed range in response to temperature.
Twin head pump means a dry rotor, single-axis flow, rotodynamic pump that contains two impeller assemblies, which both share a common casing, inlet, and discharge, and each of which
(1) Contains an impeller, impeller shaft (or motor shaft in the case of close-coupled pumps), shaft seal or packing, driver (if present), and mechanical equipment (if present);
(2) Has a shaft input power that is greater than or equal to 1 hp and less than or equal to 200 hp at best efficiency point (BEP) and full impeller diameter;
(3) Has the same primary energy source (if sold with a driver) and the same electrical, physical, and functional characteristics that affect energy consumption or energy efficiency;
(4) Is mounted in its own volute; and
(5) Discharges liquid through its volute and the common discharge in a plane perpendicular to the impeller shaft.
Two-speed dedicated-purpose pool pump means a dedicated-purpose pool pump that is capable of operating at only two different pre-determined operating speeds, where the low operating speed is less than or equal to half of the maximum operating speed and greater than zero, and must be distributed in commerce either:
(1) With a pool pump control (e.g., variable speed drive and user interface or switch) that is capable of changing the speed in response to user preferences; or
(2) Without a pool pump control that has the capability to change speed in response to user preferences, but is unable to operate without the presence of such a pool pump control.
Variable-speed dedicated-purpose pool pump means a dedicated-purpose pool pump that is capable of operating at a variety of user-determined speeds, where all the speeds are separated by at most 100 rpm increments over the operating range and the lowest operating speed is less than or equal to one-third of the maximum operating speed and greater than zero. Such a pump must include a variable speed drive and be distributed in commerce either:
(1) With a user interface that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times; or
(2) Without a user interface that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times, but is unable to operate without the presence of a user interface.
Variable speed drive means equipment capable of varying the speed of the motor.
Vertical turbine (VT) pump means a vertically suspended, single-stage or multi-stage, dry rotor, single inlet, rotodynamic pump:
(1) That has a shaft input power greater than or equal to 1 hp and less than or equal to 200 hp at BEP and full impeller diameter and at the number of stages required for testing;
(2) For which the pump driver is not designed to be submerged in the pumped liquid;
(3) That has a single pressure containing boundary (i.e., is single casing), which may consist of, but is not limited, to bowls, columns, and discharge heads; and
(4) That discharges liquid through the same casing in which the impeller shaft is contained.
Waterfall pump means a pool filter pump with a certified maximum head less than or equal to 30.0 feet, and a maximum speed less than or equal to 1,800 rpm.
Wet rotor circulator pump means a single stage, rotodynamic, close-coupled, wet rotor pump. Examples include, but are not limited to, pumps generally referred to in industry as CP1.
[81 FR 4145, Jan. 25, 2016, as amended at 82 FR 5742, Jan. 18, 2017; 82 FR 36920, Aug. 7, 2017; 87 FR 57298, Sept. 19, 2022; 88 FR 17975, Mar. 24, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, DOE must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, Sixth Floor, 950 L'Enfant Plaza SW, Washington, DC 20024, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email fr.inspection@nara.gov. The material may be obtained from the following sources:
(b) ASME. American Society of Mechanical Engineers, Two Park Avenue, New York, NY 10016-5990; (800) 843-2763; www.asme.org.
(1) ASME MFC-3M-2004 (Reaffirmed 2017) (“ASME MFC-3M-2004”), Measurement of Fluid Flow in Pipes Using Orifice, Nozzle, and Venturi, Issued January 1, 2004; IBR approved for appendix A to this subpart.
(2) ANSI/ASME MFC-5M-1985 (Reaffirmed 2006) (“ASME MFC-5M-1985”), Measurement of Liquid Flow in Closed Conduits Using Transit-Time Ultrasonic Flowmeters, Issued July 15, 1985; IBR approved for appendix A to this subpart.
(3) ASME MFC-8M-2001 (Reaffirmed 2011) (“ASME MFC-8M-2001”), Fluid Flow in Closed Conduits: Connections for Pressure Signal Transmissions Between Primary and Secondary Devices, Issued September 1, 2001; IBR approved for appendix A to this subpart.
(4) ASME MFC-12M-2006 (Reaffirmed 2014) (“ASME MFC-12M-2006”), Measurement of Fluid Flow in Closed Conduits Using Multiport Averaging Pitot Primary Elements, Issued October 9, 2006; IBR approved for appendix A to this subpart.
(5) ASME MFC-16-2014, Measurement of Liquid Flow in Closed Conduits with Electromagnetic Flowmeters, Issued March 14, 2014; IBR approved for appendix A to this subpart.
(6) ASME MFC-22-2007 (Reaffirmed 2014) (“ASME MFC-22-2007”), Measurement of Liquid by Turbine Flowmeters, Issued April 14, 2008; IBR approved for appendix A to this subpart.
(c) AWWA. American Water Works Association, Headquarters, 6666 W Quincy Ave, Denver, CO 80235; (303) 794-7711; www.awwa.org.
(1) ANSI/AWWA E103-2015 (“AWWA E103-2015”), Horizontal and Vertical Line-Shaft Pumps, approved 7, 2015; IBR approved for appendix A to this subpart.
(2) [Reserved]
(d) CSA. Canadian Standards Association, 5060 Spectrum Way, Suite 100, Mississauga, Ontario, L4W 5N6, Canada; (800) 463-6727; www.csagroup.org.
(1) CSA C390-10 Test methods, marking requirements, and energy efficiency levels for three-phase induction motors, Updated March 2010; IBR approved for appendix A to this subpart.
(2) CSA C747-2009 (Reaffirmed 2014) (“CSA C747-2009 (RA 2014)”), Energy efficiency test methods for small motors, CSA reaffirmed 2014; IBR approved for appendices B and C to this subpart, as follows:
(i) Section 1, “Scope”;
(ii) Section 3, “Definitions”;
(iii) Section 5, “General Test Requirements”; and
(iv) Section 6, “Test Method.”
(e) FM. FM Global, 1151 Boston-Providence Turnpike, P.O. Box 9102, Norwood, MA 02062; (781) 762-4300; www.fmglobal.com.
(1) FM Class Number 1319, Approval Standard for Centrifugal Fire Pumps (Horizontal, End Suction Type), January 2015; IBR approved for § 431.462.
(2) [Reserved]
(f) HI. Hydraulic Institute, 300 Interpace Parkway, 3rd Floor, Parsippany, NJ 07054-4406; 973-267-9700; www.Pumps.org.
(1) ANSI/HI 9.6.1-2017 (“HI 9.6.1-2017”) “Rotodynamic Pumps—Guideline for NPSH Margin, ANSI-approved January 6, 2017; IBR approved for appendix A to this subpart.
(2) ANSI/HI 9.6.6-2016 (“HI 9.6.6-2016”) “Rotodynamic Pumps for Pump Piping, ANSI-approved March 23, 2016; IBR approved for appendix A to this subpart.
(3) ANSI/HI 9.8-2018 (“HI 9.8-2018”) “Rotodynamic Pumps for Pump Intake Design, ANSI-approved January 8, 2018; IBR approved for appendix A to this subpart.
(4) ANSI/HI 14.1-14.2-2019 (“HI 14.1-14.2-2019”) “Rotodynamic Pumps for Nomenclature and Definitions, ANSI-approved April 9, 2019; IBR approved for appendix A to this subpart.
(5) HI 40.6-2014 (“HI 40.6-2014-B”), Methods for Rotodynamic Pump Efficiency Testing, copyright 2014, IBR approved for appendices B and C to this subpart, excluding the following:
(i) Section 40.6.4.1 “Vertically suspended pumps”;
(ii) Section 40.6.4.2 “Submersible pumps”;
(iii) Section 40.6.5.3 “Test report”;
(iv) Section 40.6.5.5 “Test conditions”;
(v) Section 40.6.5.5.2 “Speed of rotation during test”;
(vi) Section 40.6.6.1 “Translation of test results to rated speed of rotation”;
(vii) Appendix A “Test arrangements (normative)”: A.7 “Testing at temperatures exceeding 30 °C (86 °F)”; and
(viii) Appendix B, “Reporting of test results (normative)”).
(6) HI 40.6-2021, Hydraulic Institute Standard for Methods for Rotodynamic Pump Efficiency Testing, approved February 17, 2021; IBR approved for appendices A and D to this subpart.
(7) HI 41.5-2022, Hydraulic Institute Program Guideline for Circulator Pump Energy Rating Program, approved June 16, 2022; IBR approved for appendix D to this subpart.
(8) HI Engineering Data Book, Second Edition copyright 1990; IBR approved for appendix A to this subpart.
(g) IEEE. Institute of Electrical and Electronics Engineers, Inc., 45 Hoes Lane, P.O. Box 1331, Piscataway, NJ 08855-1331; (732) 981-0060; www.ieee.org.
(1) IEEE 112-2017, IEEE Standard Test Procedure for Polyphase Induction Motors and Generators, published February 14, 2018; IBR approved for appendix A to this subpart.
(2) IEEE 113-1985, IEEE Guide: Test Procedures for Direct-Current Machines,” copyright 1985, IBR approved for appendices B and C to this subpart, as follows:
(i) Section 3, Electrical Measurements and Power Sources for all Test Procedures:
(A) Section 3.1, “Instrument Selection Factors”;
(B) Section 3.4 “Power Measurement”; and
(C) Section 3.5 “Power Sources”;
(ii) Section 4, Preliminary Tests:
(A) Section 4.1, Reference Conditions, Section 4.1.2, “Ambient Air”; and
(B) Section 4.1, Reference Conditions, Section 4.1.4 “Direction of Rotation”; and
(iii) Section 5, Performance Determination:
(A) Section 5.4, Efficiency, Section 5.4.1, “Reference Conditions”; and
(B) Section 5.4.3, Direct Measurements of Input and Output, Section 5.4.3.2 “Dynomometer or Torquemeter Method.”
(3) IEEE 114-2010 (“IEEE 114-2010-A”), IEEE Standard Test Procedure for Single-Phase Induction Motors, published December 23, 2010; IBR approved for appendix A to this subpart.
(4) IEEE 114-2010 (“IEEE 114-2010”), “IEEE Standard Test Procedure for Single-Phase Induction Motors,” approved September 30, 2010, IBR approved for appendices B and C to this subpart, as follows:
(i) Section 3, “General tests”, Section 3.2, “Tests with load”;
(ii) Section 4 “Testing facilities”; and
(iii) Section 5, “Measurements”:
(A) Section 5.2 “Mechanical measurements”;
(B) Section 5.3 “Temperature measurements”; and
(iv) Section 6 “Tests.”
(h) ISO. International Organization for Standardization, Chemin de Blandonnet 8, CP 401, 1214 Vernier, Geneva, Switzerland, +41 22 749 01 11. www.iso.org.
(1) ISO 1438:2017(E) (“ISO 1438:2017”), Hydrometry—Open channel flow measurement using thin-plate weirs, Third edition, April 2017; IBR approved for appendix A to this subpart.
(2) ISO 2186:2007(E) (“ISO 2186:2007”), Fluid flow in closed conduits—Connections for pressure signal transmissions between primary and secondary elements, Second edition, March 1, 2007; IBR approved for appendix A to this subpart.
(3) ISO 2715:2017(E) (“ISO 2715:2017”), Liquid hydrocarbons—Volumetric measurement by turbine flowmeter, Second edition, November 1, 2017; IBR approved for appendix A to this subpart.
(4) ISO 3354:2008(E) (“ISO 3354:2008”), Measurement of clean water flow in closed conduits—Velocity-area method using current-meters in full conduits and under regular flow conditions, Third edition, July 15, 2008; IBR approved for appendix A to this subpart.
(5) ISO 3966:2020(E) (“ISO 3966:2020”), Measurement of fluid flow in closed conduits—Velocity area method using Pitot static tubes, Third edition, July 27, 2020; IBR approved for appendix A to this subpart.
(6) ISO 5167-1:2003(E) (“ISO 5167-1:2003”), Measurement of fluid flow by means of pressure differential devices inserted in circular cross-section conduits running full—Part 1: General principles and requirements, Second edition, March 1, 2003; IBR approved for appendix A to this subpart.
(7) ISO 5198:1987(E) (“ISO 5198:1987”), Centrifugal, mixed flow and axial pumps—Code for hydraulic performance tests—Precision class, First edition, July 1, 1987; IBR approved for appendix A to this subpart.
(8) ISO 6416:2017(E) (“ISO 6416:2017”), Hydrometry—Measurement of discharge by the ultrasonic transit time (time of flight) method, Fourth edition, October 2017; IBR approved for appendix A to this subpart.
(9) ISO 20456:2017(E) (“ISO 20456:2017”), Measurement of fluid flow in closed conduits—Guidance for the use of electromagnetic flowmeters for conductive liquids, First edition, September 2017; IBR approved for appendix A to this subpart.
(i) NFPA. National Fire Protection Association, 1 Batterymarch Park, Quincy, MA 02169-7471; (617) 770-3000; www.nfpa.org.
(1) NFPA 20 (“NFPA 20-2016”), Standard for the Installation of Stationary Pumps for Fire Protection, 2016 Edition, approved June 15, 2015, IBR approved for § 431.462.
(2) [Reserved]
(j) NSF. NSF International, 789 N. Dixboro Road, Ann Arbor, MI 48105; (743) 769-8010; www.nsf.org.
(1) NSF/ANSI 50-2015, Equipment for Swimming Pools, Spas, Hot Tubs and Other Recreational Water Facilities, Annex C, normative Test methods for the evaluation of centrifugal pumps, Section C.3, Self-priming capability, ANSI-approved January 26, 2015; IBR approved for § 431.462 and appendices B and C to this subpart.
(2) [Reserved]
(k) UL. UL, 333 Pfingsten Road, Northbrook, IL 60062; (847) 272-8800; www.ul.com.
(1) UL 448 (“ANSI/UL 448-2013”), Standard for Safety Centrifugal Stationary Pumps for Fire-Protection Service, 10th Edition, June 8, 2007, including revisions through July 12, 2013; IBR approved for § 431.462.
(2) UL 1081 (“ANSI/UL 1081-2016”), Standard for Swimming Pool Pumps, Filters, and Chlorinators, 7th Edition, ANSI-approved October 21, 2016; IBR approved for § 431.462.
[88 FR 17976, Mar. 24, 2023, as amended at 88 FR 24471, Apr. 21, 2023]
(a) General pumps —
(1) Scope. This paragraph (a) provides the test procedures for determining the constant and variable load pump energy index for:
(i) The following categories of clean water pumps that have the characteristics listed in paragraph (a)(1)(iii) of this section.
(A) End suction close-coupled (ESCC);
(B) End suction frame mounted/own bearings (ESFM);
(C) In-line (IL);
(D) Radially split, multi-stage, vertical, in-line casing diffuser (RSV); and
(E) Submersible turbine (ST) pumps.
(ii) The additional following categories of clean water pumps that have the characteristics listed in paragraph (a)(1)(iii) of this section:
(A) Radially-split, multi-stage, horizontal, end-suction diffuser casing (RSHES);
(B) Radially-split, multi-stage, horizontal, in-line diffuser casing (RSHIL);
(C) Small vertical in-line (SVIL); and
(D) Vertical Turbine (VT).
(iii) Pump characteristics:
(A) Flow rate of 25 gpm or greater at BEP and full impeller diameter;
(B) Maximum head of 459 feet at BEP and full impeller diameter and the number of stages required for testing (see section 1.2.2 of appendix A of this subpart);
(C) Design temperature range wholly or partially in the range of 15 to 250 °F;
(D) Designed to operate with either:
(1) A 2- or 4- or 6-pole induction motor, or
(2) A non-induction motor with a speed of rotation operating range that includes speeds of rotation between 2,880 and 4,320 revolutions per minute (rpm) and/or 1,440 and 2,160 rpm and/or 960 and 1,439 revolutions per minute, and in each case, the driver and impeller must rotate at the same speed;
(E) For ST, and VT pumps, a 6-inch or smaller bowl diameter; and
(F) For ESCC, and ESFM pumps, a specific speed less than or equal to 5,000 when calculated using U.S. customary units.
(2) Testing and calculations. Determine the applicable constant load pump energy index (PEICL) or variable load pump energy index (PEIVL) using the test procedure set forth in appendix A of this subpart.
(b) Dedicated-purpose pool pumps —
(1) Scope. This paragraph (b) provides the test procedures for determining the weighted energy factor (WEF), rated hydraulic horsepower, dedicated-purpose pool pump nominal motor horsepower, dedicated-purpose pool pump motor total horsepower, dedicated-purpose pool pump service factor, and other pump performance parameters for:
(i) The following varieties of dedicated-purpose pool pumps:
(A) Self-priming pool filter pumps;
(B) Non-self-priming pool filter pumps;
(C) Waterfall pumps; and
(D) Pressure cleaner booster pumps;
(ii) Served by single-phase or polyphase input power;
(iii) Except for:
(A) Submersible pumps; and
(B) Self-priming and non-self-priming pool filter pumps with hydraulic output power greater than or equal to 2.5 horsepower.
(2) Testing and calculations. Determine the weighted energy factor (WEF) using the test procedure set forth in appendix B or appendix C of this subpart, as applicable.
(c) Circulator pumps —
(1) Scope. This paragraph (c) provides the test procedures for determining the circulator energy index for circulator pumps that are also clean water pumps, including on-demand circulator pumps and circulators-less-volute, and excluding submersible pumps and header pumps.
(2) Testing and calculations. Determine the circulator energy index (CEI) using the test procedure set forth in appendix D of this subpart Y.
[82 FR 36923, Aug. 7, 2017, as amended at 87 FR 57299, Sept. 19, 2022; 88 FR 17978, Mar. 24, 2023]
(a) For the purposes of paragraph (b) of this section, “PEICL” means the constant load pump energy index and “PEIVL” means the variable load pump energy index, both as determined in accordance with the test procedure in § 431.464. For the purposes of paragraph (c) of this section, “BEP” means the best efficiency point as determined in accordance with the test procedure in § 431.464.
(b) Each pump that is manufactured starting on January 27, 2020 and that:
(1) Is in one of the equipment classes listed in the table in paragraph (b)(4) of this section;
(2) Meets the definition of a clean water pump in § 431.462;
(3) Is not listed in paragraph (c) of this section; and
(4) Conforms to the characteristics listed in paragraph (d) of this section must have a PEICL or PEIVL rating of not more than 1.00 using the appropriate C-value in the table in this paragraph (b)(4):
| Equipment class 1 | Maximum PEI 2 | C-value 3 |
|---|---|---|
| ESCC.1800.CL | 1.00 | 128.47 |
| ESCC.3600.CL | 1.00 | 130.42 |
| ESCC.1800.VL | 1.00 | 128.47 |
| ESCC.3600.VL | 1.00 | 130.42 |
| ESFM.1800.CL | 1.00 | 128.85 |
| ESFM.3600.CL | 1.00 | 130.99 |
| ESFM.1800.VL | 1.00 | 128.85 |
| ESFM.3600.VL | 1.00 | 130.99 |
| IL.1800.CL | 1.00 | 129.30 |
| IL.3600.CL | 1.00 | 133.84 |
| IL.1800.VL | 1.00 | 129.30 |
| IL.3600.VL | 1.00 | 133.84 |
| RSV.1800.CL | 1.00 | 129.63 |
| RSV.3600.CL | 1.00 | 133.20 |
| RSV.1800.VL | 1.00 | 129.63 |
| RSV.3600.VL | 1.00 | 133.20 |
| ST.1800.CL | 1.00 | 138.78 |
| ST.3600.CL | 1.00 | 134.85 |
| ST.1800.VL | 1.00 | 138.78 |
| ST.3600.VL | 1.00 | 134.85 |
| 1 Equipment class designations consist of a combination (in sequential order separated by periods) of: (1) An equipment family (ESCC = end suction close-coupled, ESFM = end suction frame mounted/own bearing, IL = in-line, RSV = radially split, multi-stage, vertical, in-line diffuser casing, ST = submersible turbine; all as defined in § 431.462); (2) nominal speed of rotation (1800 = 1800 rpm, 3600 = 3600 rpm); and (3) an operating mode (CL = constant load, VL = variable load). Determination of the operating mode is determined using the test procedure in appendix A to this subpart. | ||
| 2 For equipment classes ending in .CL, the relevant PEI is PEICL. For equipment classes ending in .VL, the relevant PEI is PEIVL. | ||
| 3 The C-values shown in this table must be used in the equation for PERSTD when calculating PEICL or PEIVL, as described in section II.B of appendix A to this subpart. | ||
(c) The energy efficiency standards in paragraph (b) of this section do not apply to the following pumps:
(1) Fire pumps;
(2) Self-priming pumps;
(3) Prime-assist pumps;
(4) Magnet driven pumps;
(5) Pumps designed to be used in a nuclear facility subject to 10 CFR part 50, “Domestic Licensing of Production and Utilization Facilities”;
(6) Pumps meeting the design and construction requirements set forth in Military Specification MIL-P-17639F, “Pumps, Centrifugal, Miscellaneous Service, Naval Shipboard Use” (as amended); MIL-P-17881D, “Pumps, Centrifugal, Boiler Feed, (Multi-Stage)” (as amended); MIL-P-17840C, “Pumps, Centrifugal, Close-Coupled, Navy Standard (For Surface Ship Application)” (as amended); MIL-P-18682D, “Pump, Centrifugal, Main Condenser Circulating, Naval Shipboard” (as amended); MIL-P-18472G, “Pumps, Centrifugal, Condensate, Feed Booster, Waste Heat Boiler, And Distilling Plant” (as amended). Military specifications and standards are available for review at http://everyspec.com/MIL-SPECS.
(d) The energy conservation standards in paragraph (b) of this section apply only to pumps that have the following characteristics:
(1) Flow rate of 25 gpm or greater at BEP at full impeller diameter;
(2) Maximum head of 459 feet at BEP at full impeller diameter and the number of stages required for testing;
(3) Design temperature range from 14 to 248 °F;
(4) Designed to operate with either:
(i) A 2- or 4-pole induction motor; or
(ii) A non-induction motor with a speed of rotation operating range that includes speeds of rotation between 2,880 and 4,320 revolutions per minute and/or 1,440 and 2,160 revolutions per minute; and
(iii) In either case, the driver and impeller must rotate at the same speed;
(5) For ST pumps, a 6-inch or smaller bowl diameter; and
(6) For ESCC and ESFM pumps, specific speed less than or equal to 5,000 when calculated using U.S. customary units.
(e) For the purposes of paragraph (f) of this section, “WEF” means the weighted energy factor and “hhp” means the rated hydraulic horsepower, as determined in accordance with the test procedure in § 431.464(b) and applicable sampling plans in § 429.59 of this chapter.
(f) Each dedicated-purpose pool pump that is not a submersible pump and is manufactured starting on July 19, 2021 must have a WEF rating that is not less than the value calculated from the following table:
| Equipment class | Minimum allowable WEF score [kgal/kWh] |
Minimum allowable WEF score [kgal/kWh] |
|
|---|---|---|---|
| Dedicated-purpose pool pump variety |
hhp Applicability | Motor phase | |
| Self-priming pool filter pumps | 0.711 hp ≤hhp <2.5 hp | Single | WEF = −2.30 * ln (hhp) + 6.59. |
| Self-priming pool filter pumps | hhp <0.711 hp | Single | WEF = 5.55, for hhp ≤0.13 hp −1.30 * ln (hhp) + 2.90, for hhp >0.13 hp. |
| Non-self-priming pool filter pumps | hhp <2.5 hp | Any | WEF = 4.60, for hhp ≤0.13 hp −0.85 * ln (hhp) + 2.87, for hhp >0.13 hp. |
| Pressure cleaner booster pumps | Any | Any | WEF = 0.42. |
(g) Each integral cartridge filter pool pump and integral sand filter pool pump that is manufactured starting on July 19, 2021 must be distributed in commerce with a pool pump timer that is either integral to the pump or a separate component that is shipped with the pump.
(h) For all dedicated-purpose pool pumps distributed in commerce with freeze protection controls, the pump must be shipped with freeze protection disabled or with the following default, user-adjustable settings:
(1) The default dry-bulb air temperature setting is no greater than 40 °F;
(2) The default run time setting shall be no greater than 1 hour (before the temperature is rechecked); and
(3) The default motor speed shall not be more than 1⁄2 of the maximum available speed.
(i) Each circulator pump that is manufactured starting on May 22, 2028 and that meets the criteria in paragraphs (i)(1) through (i)(2) of this section must have a circulator energy index (“CEI”) rating (as determined in accordance with the test procedure in § 431.464(c)(2)) of not more than 1.00 using the instructions in paragraph (i)(3) of this section and with a control mode as specified in paragraph (i)(4) of this section:
(1) Is a clean water pump as defined in § 431.462.
(2) Is not a submersible pump or a header pump, each as defined in § 431.462.
(3) The relationships in this paragraph (i)(3) are necessary to calculate maximum CEI.
(i) Calculate CEI according to the following equation:
Equation 1 to Paragraph (i)(3)(i)
Where:
CEI = the circulator energy index (dimensionless);
CER = the circulator energy rating (hp), determined in accordance with section 6 of appendix D to subpart Y of part 431; and
CERSTD = the CER for a circulator pump that is minimally compliant with DOE's energy conservation standards with the same hydraulic horsepower as the rated pump (hp), determined in accordance with paragraph (i)(3)(ii) of this section.
(ii) Calculate CERSTD according to the following equation:
Equation 2 to Paragraph (i)(3)(ii)
Where:
CERSTD = the CER for a circulator pump that is minimally compliant with DOE's energy conservation standards with the same hydraulic horsepower as the rated pump (hp);
i = the index variable of the summation notation used to express CERSTD (dimensionless) as described in the table 3 to paragraph (i)(3)(ii), in which i is expressed as a percentage of circulator pump flow at best efficiency point, determined in accordance with the test procedure in § 431.464(c)(2);
ωi = the weighting factor (dimensionless) at each corresponding test point, i, as described in table 3 to paragraph (i)(3)(ii); and Piin,STD = the reference power input to the circulator pump driver (hp) at test point i, calculated using the equations and method specified in paragraph (i)(3)(iii) of this section.
| I
(%) |
Corresponding
ωi |
|---|---|
| 25 | .25 |
| 50 | .25 |
| 75 | .25 |
| 100 | .25 |
(iii) Calculate Piin,STD according to the following equation:
Equation 3 to Paragraph (i)(3)(iii)
Where:
Piin,STD = the reference power input to the circulator pump driver at test point i (hp);
Pu,i = circulator pump basic model rated hydraulic horsepower (hp) determined in accordance with 10 CFR 429.59(a)(2)(i);
αi = part-load efficiency factor (dimensionless) at each test point i as described in table 4 to paragraph (i)(3)(iii); and
ηWTW,100% = reference circulator pump wire-to-water efficiency at best efficiency point (%) at the applicable energy conservation standard level, as described in table 5 to paragraph (i)(3)(iii) as a function of circulator pump basic model rated hydraulic horsepower at 100% BEP flow, Pu,100%.
| I
(%) |
Corresponding
αi |
|---|---|
| 25 | 0.4843 |
| 50 | 0.7736 |
| 75 | 0.9417 |
| 100 | 1 |
| Pu,100 % | ηWTW,100 % |
|---|---|
| <1 | 10*ln(Pu,100 % + 0.001141) + 67.78. |
| ≥1 | 67.79%. |
(4) A circulator pump subject to energy conservation standards as described in this paragraph (i) must achieve the maximum CEI as described in paragraph (i)(3)(i) of this section and in accordance with the test procedure in § 431.464(c)(2) in the least consumptive control mode in which it is capable of operating.
[81 FR 4431, Jan. 26, 2016, as amended at 82 FR 5742, Jan. 18, 2017; 89 FR 44536, May 20, 2024]
(a) General pumps. For the pumps described in § 431.464(a), the following requirements apply to units manufactured on the same date that compliance is required with any applicable standards prescribed in § 431.465.
(1) Pump nameplate —
(i) Required information. The permanent nameplate must be marked clearly with the following information:
(A) For bare pumps and pumps sold with electric motors but not continuous or non-continuous controls, the rated pump energy index—constant load (PEICL), and for pumps sold with motors and continuous or non-continuous controls, the rated pump energy index—variable load (PEIVL);
(B) The bare pump model number; and
(C) If transferred directly to an end-user, the unit's impeller diameter, as distributed in commerce. Otherwise, a space must be provided for the impeller diameter to be filled in.
(ii) Display of required information. All orientation, spacing, type sizes, typefaces, and line widths to display this required information must be the same as or similar to the display of the other performance data on the pump's permanent nameplate. The PEICL or PEIVL, as appropriate to a given pump model, must be identified in the form “PEICL ________” or “PEIVL ________.” The model number must be in one of the following forms: “Model ________” or “Model number ________” or “Model No. ________.” The unit's impeller diameter must be in the form “Imp. Dia. ________(in.).”
(2) Disclosure of efficiency information in marketing materials.
(i) The same information that must appear on a pump's permanent nameplate pursuant to paragraph (a)(1)(i) of this section, must also be prominently displayed:
(A) On each page of a catalog that lists the pump; and
(B) In other materials used to market the pump.
(ii) [Reserved]
(b) Dedicated-purpose pool pumps. For the pumps described in § 431.464(b), the following requirements apply on the same date that compliance is required with any applicable standards prescribed in § 431.465.
(1) Pump nameplate —
(i) Required information. The permanent nameplate must be marked clearly with the following information:
(A) The weighted energy factor (WEF); and
(B) The dedicated-purpose pool pump motor total horsepower.
(ii) Display of required information. All orientation, spacing, type sizes, typefaces, and line widths to display this required information must be the same as or similar to the display of the other performance data on the pump's permanent nameplate.
(A) The WEF must be identified in the form “WEF ________.”
(B) The dedicated-purpose pool pump motor total horsepower must be identified in one of the following forms: “Dedicated-purpose pool pump motor total horsepower __________,” “DPPP motor total horsepower __________,” “motor total horsepower __________,” “motor THP __________,” or “THP __________.”
(2) [Reserved]
[82 FR 36923, Aug. 7, 2017]
Note: Prior to September 20, 2023, representations with respect to the energy use or efficiency (including compliance certifications) of pumps specified in § 431.464(a)(1)(i), excluding pumps listed in § 431.464(a)(1)(iv), must be based on testing conducted in accordance with the applicable provisions of this appendix as they appeared in the January 1, 2022 edition of the Code of Federal Regulations of subpart Y of part 431 in 10 CFR parts 200 through 499.
On or after September 20, 2023, representations with respect to the energy use or efficiency (including compliance certifications) of pumps specified in § 431.464(a)(1)(i), excluding pumps listed in § 431.464(a)(1)(iv), must be based on testing conducted in accordance with the applicable provisions of this appendix.
Any representations with respect to the energy use or efficiency of pumps specified in § 431.464(a)(1)(ii), excluding pumps listed in § 431.464(a)(1)(iv), made on or after September 20, 2023 must be made in accordance with the results of testing pursuant to this appendix. Manufacturers must use the results of testing under this appendix to determine compliance with any energy conservation standards established for pumps specified in § 431.464(a)(1)(ii), excluding pumps listed in § 431.464(a)(1)(iv), that are published after January 1, 2022.
I. Test Procedure for Pumps
0. Incorporation by Reference.
DOE incorporated by reference in § 431.463 the entire standard for HI 40.6-2021, HI 9.6.1-2017, HI 9.6.6-2016, HI 9.8-2018, HI 14.1-14.2-2019, the HI Engineering Data Book, ASME MFC-5M-1985, ASME MFC-3M-2004, ASME MFC-8M-2001, ASME MFC-12M-2006, ASME MFC-16-2014, ASME MFC-22-2007, AWWA E103-2015, CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, ISO 1438:2017, ISO 2186:2007, ISO 2715:2017, ISO 3354:2008, ISO 3966:2020, ISO 5167-1:2003, ISO 5198:1987, ISO 6416:2017, and ISO 20456:2017; however, certain enumerated provisions of HI 40.6-2021, as follows are inapplicable. To the extent that there is a conflict between the terms or provisions of a referenced industry standard and the CFR, the CFR provisions control.
0.1 HI 40.6-2021
(a) Section 40.6.1 Scope
(b) Section 40.6.5.3 Test report
(c) Appendix B Reporting of test results (informative)
(d) Appendix E Testing Circulator Pumps (normative)
(e) Appendix G DOE Compared to HI 40.6 Nomenclature
0.2 [Reserved]
A. General. To determine the constant load pump energy index (PEICL) for bare pumps and pumps sold with electric motors or the variable load pump energy index (PEIVL) for pumps sold with electric motors and continuous or non-continuous controls, perform testing in accordance with HI 40.6-2021, except section 40.6.5.3, “Test report”, including the applicable provisions of HI 9.6.1-2017, HI 9.6.6-2016, HI 9.8-2018, HI 14.1-14.2-2019, the HI Engineering Data Book, ASME MFC-3M-2004, ASME MFC-5M-1985, ASME MFC-8M-2001, ASME MFC-12M-2006, ASME MFC-16-2014, ASME MFC-22-2007, AWWA E103-2015, CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, ISO 1438:2017, ISO 2186:2007, ISO 2715:2017, ISO 3354:2008, ISO 3966:2020, ISO 5167-1:2003, ISO 5198:1987, ISO 6416:2017, and ISO 20456:2017, as referenced in HI 40.6, with the modifications and additions as noted throughout the provisions below. Where HI 40.6-2021 refers to “pump,” the term refers to the “bare pump,” as defined in § 431.462. Also, for the purposes of applying this appendix, the term “volume per unit time,” as defined in section 40.6.2, “Terms and definitions,” of HI 40.6-2021 shall be deemed to be synonymous with the term “flow rate” used throughout that standard and this appendix. In addition, the specifications in section 40.6.4.1 of HI 40.6-2021, “Vertically suspended pumps,” do not apply to ST pumps and the performance of ST bare pumps considers bowl performance only. However, the specifications in the first paragraph of section 40.6.4.1 of HI 40.6-2021 (including the applicable provisions of HI 14.1-14.2-2019, the HI Engineering Data Book, and AWWA E103-2015, as referenced in section 40.6.4.1 of HI 40.6), “Vertically suspended pumps,” do apply to VT pumps and the performance of VT bare pumps considers bowl performance only.
A.1 Scope. Section II of this appendix applies to all pumps and describes how to calculate the pump energy index (section II.A) based on the pump energy rating for the minimally-compliant reference pump (PERSTD; section II.B) and the constant load pump energy rating (PERCL) or variable load pump energy rating (PERVL) determined in accordance with one of sections III through VII of this appendix, based on the configuration in which the pump is distributed in commerce and the applicable testing method specified in sections III through VII and as described in Table 1 of this appendix.
| Pump configuration | Pump sub-configuration | Applicable test methods |
|---|---|---|
| Bare Pump | Bare Pump OR Pump + Single-Phase Induction Motor (Excluding SVIL) OR Pump + Driver Other Than Electric Motor | Section III: Test Procedure for Bare Pumps. |
| Pump + Motor OR Pump + Motor + Controls other than continuous or non-continuous controls (e.g., ON/OFF switches) | Pump + Motor Listed at § 431.25(g) OR SVIL Pump + Motor Covered by DOE's Test Procedure and/or Energy Conservation Standards * OR Pump + Submersible Motor | Section IV: Testing-Based Approach for Pumps Sold with Motors OR Section V: Calculation-Based Approach for Pumps Sold with Motors. |
| Pump (Including SVIL) + Motor Not Covered by DOE's Motor Energy Conservation Standards (Except Submersible Motors) ** OR Pump (Other than SVIL) + Single-Phase Induction Motor (if Section III is not used) | Section IV: Testing-Based Approach for Pumps Sold with Motors. | |
| Pump + Motor + Continuous Controls OR Pump + Motor + Non-Continuous Controls OR Pump + Inverter-Only Synchronous Electric Motor *** (With or Without Controls) | Pump + Motor Listed at § 431.25(g) + Continuous Control OR SVIL Pump + Motor Covered by DOE's Test Procedure and/or Energy Conservation Standards * + Continuous Control OR Pump + Submersible Motor + Continuous Control OR Pump + Inverter-Only Synchronous Electric Motor *** (With or Without Continuous Control) | Section VI: Testing-Based Approach for Pumps Sold with Motors and Controls OR Section VII: Calculation-Based Approach for Pumps Sold with Motors Controls. |
| Pump + Motor Listed at § 431.25(g) + Non-Continuous Control OR SVIL Pump + Motor Covered by DOE's Test Procedure and/or Energy Conservation Standards * + Non-Continuous Control OR Pump + Submersible Motor + Non-Continuous Control | Section VI: Testing-Based Approach for Pumps Sold with Motors and Controls. | |
| Pump (Including SVIL) + Motor Not Covered by DOE's Motor Test Procedure and/or Energy Conservation Standards ** (Except Submersible Motors) + Continuous or Non-Continuous Controls OR Pump (Other than SVIL) + Single-Phase Induction Motor + Continuous or Non-Continuous Controls (if Section III is not used) | Section VI: Testing-Based Approach for Pumps Sold with Motors and Controls. | |
| * All references to “Motor Covered by DOE's Motor Test Procedure and/or Energy Conservation Standards” refer to those listed at § 431.446 of this chapter or those for Small Non-Small Electric Motor Electric Motors (SNEMs) at Subpart B to Part 431, including motors of such varieties that are less than 0.25 hp. | ||
| ** All references to “Motor Not Covered by DOE's Test Procedure and/or Motor Energy Conservation Standards” refer to motors not listed at § 431.25 of this chapter or, for SVIL, not listed at either § 431.446 of this chapter or in Subpart B to Part 431 (excluding motors of such varieties that are less than 0.25 hp). | ||
| *** All references to “Inverter-Only Synchronous Electric Motor” refer to inverter-only electric motors that are synchronous electric motors, both as defined in subpart B to Part 431. | ||
A.2 Section III of this appendix addresses the test procedure applicable to bare pumps. This test procedure also applies to pumps sold with drivers other than motors and ESCC, ESFM, IL, RSHES, RSHIL, RSV, ST, and VT pumps sold with single-phase induction motors.
A.3 Section IV of this appendix addresses the testing-based approach for pumps sold with motors, which applies to all pumps sold with electric motors, except for pumps sold with inverter-only synchronous electric motors, but including pumps sold with single-phase induction motors. This test procedure also applies to pumps sold with controls other than continuous or non-continuous controls (e.g., on/off switches).
A.4 Section V of this appendix addresses the calculation-based approach for pumps sold with motors, which applies to:
A.4.1 Pumps sold with polyphase electric motors regulated by DOE's energy conservation standards for electric motors at § 431.25(g), and
A.4.2 SVIL pumps sold with small electric motors regulated by DOE's energy conservation standards at § 431.446 or sold with SNEMs regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part but including motors of such varieties that are less than 0.25 hp, and
A.4.3 Pumps sold with submersible motors.
A.5 Section VI of this appendix addresses the testing-based approach for pumps sold with motors and controls, which applies to all pumps sold with electric motors (including single-phase induction motors) and continuous or non-continuous controls and to pumps sold with inverter-only synchronous electric motors with or without controls.
A.6 Section VII of this appendix discusses the calculation-based approach for pumps sold with motors and controls, which applies to:
A.6.1 Pumps sold with polyphase electric motors regulated by DOE's energy conservation standards for electric motors at § 431.25(g) and continuous controls and
A.6.2 Pumps sold with inverter-only synchronous electric motors regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part,
A.6.3 SVIL pumps sold with small electric motors regulated by DOE's energy conservation standards at § 431.446 (but including motors of such varieties that are less than 0.25 hp) and continuous controls or with SNEMs regulated by DOE's test procedure and/or energy conservation standards at subpart B of this part (but including motors of such varieties that are less than 0.25 hp) and continuous controls, and
A.6.4 Pumps sold with submersible motors and continuous controls.
B. Measurement Equipment.
B.1 Instrument Accuracy. For the purposes of measuring pump power input, driver power input to the motor or controls, and pump power output, the equipment specified in HI 40.6-2021 Appendix C (including the applicable provisions of ASME MFC-5M-1985, ASME MFC-3M-2004, ASME MFC-8M-2001, ASME MFC-12M-2006, ASME MFC-16-2014, ASME MFC-22-2007, CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, ISO 1438:2017, ISO 2186:2007, ISO 2715:2017, ISO 3354:2008, ISO 3966:2020, ISO 5167-1:2003, ISO 5198:1987, ISO 6416:2017, and ISO 20456:2017, as referenced in Appendix C of HI 40.6) necessary to measure head, speed of rotation, flow rate, temperature, torque, and electrical power must be used and must comply with the stated accuracy requirements in HI 40.6-2021 Table 40.6.3.2.3 except as noted in sections III.B, IV.B, V.B, VI.B, and VII.B of this appendix. When more than one instrument is used to measure a given parameter, the combined accuracy, calculated as the root sum of squares of individual instrument accuracies, must meet the specified accuracy requirements.
B. 2 Calibration. Calibration requirements for instrumentation are specified in Appendix D of HI 40.6-2021.
C. Test Conditions. Conduct testing at full impeller diameter in accordance with the test conditions, stabilization requirements, and specifications of HI 40.6-2021 Section 40.6.3, “Pump efficiency testing;” Section 40.6.4, “Considerations when determining the efficiency of certain pumps” including the applicable provisions of HI 14.1-14.2-2019, the HI Engineering Data Book, and AWWA E103-2015, as referenced in section 40.6.4 of HI 40.6; section 40.6.5.4 (including appendix A), “Test arrangements,” including the applicable provisions of HI 9.6.1-2017, HI 9.6.6-2016, HI 9.8-2018, HI Engineering Data Book, and AWWA E103-2015 as referenced in appendix A of HI 40.6; and section 40.6.5.5, “Test conditions” including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6-2021. For ST pumps, head measurements must be based on the bowl assembly total head as described in section A.5 of 40.6-2021, including the applicable provisions of the HI Engineering Data Book and AWWA E103-2015 as referenced in ins section A.5 of HI 40.6-2021, and the pump power input or driver power input, as applicable, must be based on the measured input power to the driver or bare pump, respectively; section 40.6.4.1, “Vertically suspended pumps,” does not apply to ST pumps.
C. 1 Nominal Speed of Rotation. Determine the nominal speed of rotation based on the range of speeds of rotation at which the pump is designed to operate, in accordance with sections I.C.1.1, I.C.1.2, and I.C.1.3 of this appendix, as applicable. When determining the range of speeds at which the pump is designed to operate, DOE will refer to published data, marketing literature, and other publicly-available information about the pump model and motor, as applicable.
C. 1.1 For pumps sold without motors, select the nominal speed of rotation based on the speed for which the pump is designed.
C. 1.1.1 For bare pumps designed for speeds of rotation including 2,880 to 4,320 revolutions per minute (rpm), the nominal speed of rotation shall be 3,600 rpm.
C. 1.1.2 For bare pumps designed for speeds of rotation including 1,440 to 2,160 rpm, the nominal speed of rotation shall be 1,800 rpm.
C. 1.1.3 For bare pumps designed for speeds of rotation including 960 to 1,439 rpm, the nominal speed of rotation shall be 1,200 rpm.
C. 1.2 For pumps sold with induction motors, select the appropriate nominal speed of rotation.
C. 1.2.1 For pumps sold with 6-pole induction motors, the nominal speed of rotation shall be 1,200 rpm.
C. 1.2.2 For pumps sold with 4-pole induction motors, the nominal speed of rotation shall be 1,800 rpm.
C. 1.2.3 For pumps sold with 2-pole induction motors, the nominal speed of rotation shall be 3,600 rpm.
C. 1.3 For pumps sold with non-induction motors, select the appropriate nominal speed of rotation.
C. 1.3.1 Where the operating range of the pump and motor includes speeds of rotation between 2,880 and 4,320 rpm, the nominal speed of rotation shall be 3,600 rpm.
C. 1.3.2 Where the operating range of the pump and motor includes speeds of rotation between 1,440 and 2,160 rpm, the nominal speed of rotation shall be 1,800 rpm.
C. 1.3.3 Where the operating range of the pump and motor includes speeds of rotation between 960 and 1,439, the nominal speed of rotation shall be 1,200 rpm.
C. 2 Multi-Stage Pumps. Perform testing on the pump with three stages for RSH and RSV pumps, and nine stages for ST and VT pumps. If the basic model of pump being tested is only available with fewer than the required number of stages, test the pump with the maximum number of stages with which the basic model is distributed in commerce in the United States. If the basic model of pump being tested is only available with greater than the required number of stages, test the pump with the lowest number of stages with which the basic model is distributed in commerce in the United States. If the basic model of pump being tested is available with both fewer and greater than the required number of stages, but not the required number of stages, test the pump with the number of stages closest to the required number of stages. If both the next lower and next higher number of stages are equivalently close to the required number of stages, test the pump with the next higher number of stages.
C. 3 Twin-Head Pumps. For twin-head pumps, perform testing on an equivalent single impeller IL or SVIL pump as applicable, constructed by incorporating one of the driver and impeller assemblies of the twin-head pump being rated into an adequate IL-style or SVIL-style, single impeller volute and casing. An adequate IL-style or SVIL-style, single impeller volute and casing means a volute and casing for which any physical and functional characteristics that affect energy consumption and energy efficiency are the same as their corresponding characteristics for a single impeller in the twin-head pump volute and casing.
D. Data Collection and Analysis.
D. 1 Damping Devices. Use of damping devices, as described in section 40.6.3.2.2 of HI 40.6-2021, are only permitted to integrate up to the data collection interval used during testing.
D. 2 Stabilization. Record data at any tested load point only under stabilized conditions, as defined in HI 40.6-2021 section 40.6.5.5.1, including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6, where a minimum of two measurements are used to determine stabilization.
D. 3 Calculations and Rounding. Normalize all measured data to the nominal speed of rotation of 3,600 or 1,800 or 1,200 rpm based on the nominal speed of rotation selected for the pump in section I.C.1 of this appendix, in accordance with the procedures specified in section 40.6.6.1.1 of HI 40.6-2021. Except for the “expected BEP flow rate,” all terms and quantities refer to values determined in accordance with the procedures set forth in this appendix for the rated pump. Perform all calculations using raw measured values without rounding. Round PERCL and PERVL to three significant digits, and round PEICL, and PEIVL values, as applicable, to the hundredths place (i.e., 0.01).
D. 4 Pumps with BEP at Run Out. Test pumps for which the expected BEP corresponds to a volume rate of flow that is within 20 percent of the expected maximum flow rate at which the pump is designed to operate continuously or safely (i.e., pumps with BEP at run-out) in accordance with the test procedure specified in this appendix, but with the following exceptions:
D. 4.1 Use the following seven flow points—40, 50, 60, 70, 80, 90, and 100 percent of the expected maximum flow rate for determination of BEP in sections III.D, IV.D, V.D, VI.D, and VII.D of this appendix instead of the flow points specified in those sections.
D. 4.2 Use flow points of 60, 70, 80, 90, and 100 percent of the expected maximum flow rate of the pump to determine pump power input or driver power input instead of the flow points of 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate specified in sections III.E.1.1, IV.E.1, V.E.1.1, VI.E.1, and VII.E.1.1 of this appendix.
D. 4.3 To determine PERCL in sections III.E, IV.E, and V.E and to determine PERSTD in section II.B, use load points of 65, 90, and 100 percent of the BEP flow rate determined with the modified flow points specified in this section I.D.4 of this appendix instead of 75, 100, and 110 percent of BEP flow. In section II.B.1.1, where alpha values are specified for the load points 75, 100, and 110 percent of BEP flow rate, instead apply the alpha values to the load points of 65, 90, and 100 percent of the BEP flow rate determined with the modified flow points specified in this section I.D.4 of this appendix. However, in sections II.B.1.1.1 and II.B.1.1.1.1 of this appendix, use 100 percent of the BEP flow rate as specified to determine ηpump,STD and Ns as specified. To determine motor sizing for bare pumps in sections II.B.1.2.1.1 and III.E.1.2.1.1 of this appendix, use a load point of 100 percent of the BEP flow rate instead of 120 percent.
II. Calculation of the Pump Energy Index
A. Determine the PEI of each tested pump based on the configuration in which it is sold, as follows:
A.
1. For pumps rated as bare pumps or pumps sold with motors (other than inverter-only synchronous electric motors), determine the PEICL using the following equation:
Where:
PEICL = the pump energy index for a constant load (hp),
PERCL = the pump energy rating for a constant load (hp), determined in accordance with either section III (for bare pumps; ESCC, ESFM, IL, RSHES, RSHIL, RSV, ST or VT pumps sold with single-phase induction motors; and pumps sold with drivers other than electric motors), section IV (for pumps sold with motors and rated using the testing-based approach), or section V (for pumps sold with motors and rated using the calculation-based approach) of this appendix, and
PERSTD = the PERCL for a pump that is minimally compliant with DOE's energy conservation standards with the same flow and specific speed characteristics as the tested pump (hp), as determined in accordance with section II.B of this appendix.
A. 2 For pumps rated as pumps sold with motors and continuous controls or non-continuous controls (including pumps sold with inverter-only synchronous electric motors with or without controls), determine the PEIVL using the following equation:
PEIVL = the pump energy index for a variable load (hp),
PERVL = the pump energy rating for a variable load (hp), determined in accordance with section VI (for pumps sold with motors and continuous or non-continuous controls rated using the testing-based approach) or section VII of this appendix (for pumps sold with motors and continuous controls rated using the calculation-based approach), and
PERSTD = the PERCL for a pump that is minimally compliant with DOE's energy conservation standards with the same flow and specific speed characteristics as the tested pump (hp), as determined in accordance with section II.B of this appendix.
B. Determine the pump energy rating for the minimally compliant reference pump (PERSTD), according to the following equation:
Where:
PERSTD = the PERCL for a pump that is minimally compliant with DOE's energy conservation standards with the same flow and specific speed characteristics as the tested pump (hp),
ωi = 0.3333,
Piin,m = calculated driver power input to the motor at load point i for the minimally compliant pump (hp), calculated in accordance with section II.B.1of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
B.
1. Determine the driver power input at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
Piin,m = driver power input to the motor at load point i (hp),
Pi = pump power input to the bare pump at load point i (hp), calculated in accordance with section II.B.1.1 of this appendix,
Li = the part load motor losses at load point i (hp), calculated in accordance with section II.B.1.2 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
B.1.1. Determine the pump power input to the minimally compliant pump at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
Pi = pump power input to the bare pump at load point i (hp),
αi = 0.947 for 75 percent of the BEP flow rate, 1.000 for 100 percent of the BEP flow rate, and 0.985 for 110 percent of the BEP flow rate;
Pu,i = the pump power output at load point i of the tested pump (hp), as determined in accordance with section II.B.1.1.2 of this appendix;
ηpump,STD = the minimally compliant pump efficiency (%), calculated in accordance with section II.B.1.1.1 of this appendix; and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
B.1.1.1 Calculate the minimally compliant pump efficiency based on the following equation:
ηpump,STD = −0.8500 × ln(Q100≠)2 −0.3800 × ln(Ns) × ln(Q100≠) − 11.480 × ln(Ns)2 + 17.800 × ln(Q100≠) + 179.80 × ln(Ns) − (C + 555.60
Where:
ηpump,STD = minimally compliant pump efficiency (%),
Q100≠ = the BEP flow rate of the tested pump at full impeller and nominal speed of rotation (gpm),
Ns = specific speed of the tested pump determined in accordance with section II.B.1.1.1.1 of this appendix, and
C = the appropriate C-value for the category and nominal speed of rotation of the tested pump, as listed at § 431.466.
B.1.1.1.1 Determine the specific speed of the rated pump using the following equation:
Where:
Ns = specific speed,
nsp = the nominal speed of rotation (rpm),
Q'100% = the measured BEP flow rate of the tested pump at full impeller and nominal speed of rotation (gpm),
H100% = pump total head at 100 percent of the BEP flow rate of the tested pump at full impeller and nominal speed of rotation (ft), and
S = the number of stages with which the pump is being rated
B.1.1.2 Determine the pump power output at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate using the following equation:
Where:
Pu,i = the measured pump power output at load point i of the tested pump (hp),
Qi = the measured flow rate at load point i of the tested pump (gpm),
Hi = pump total head at load point i of the tested pump (ft),
SG = the specific gravity of water at specified test conditions, which is equivalent to 1.00, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
B.1.2 Determine the motor part load losses at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Li = Lfull × yi
Where:
Li = part load motor losses at load point i (hp),
Lfull = motor losses at full load (hp), as determined in accordance with section II.B.1.2.1 of this appendix,
yi = part load loss factor at load point i determined in accordance with section II.B.1.2.2 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
B.1.2.1 Determine the full load motor losses using the appropriate motor efficiency value and horsepower as shown in the following equation:
Where:
Lfull = motor losses at full load (hp),
MotorHP = the motor horsepower as determined in accordance with section II.B.1.2.1.1 of this appendix (hp), and
ηmotor,full = the default nominal full load motor efficiency as determined in accordance with section II.B.1.2.1.2 of this appendix (%).
B.1.2.1.1 Determine the motor horsepower as follows:
• For bare pumps other than ST pumps, the motor horsepower is determined as the horsepower rating listed in Table 2 of this appendix that is either equivalent to, or the next highest horsepower greater than, the pump power input to the bare pump at 120 percent of the BEP flow rate of the tested pump.
• For ST bare pumps, the motor horsepower is determined as the horsepower rating listed in Table 2 of this appendix that, is either equivalent to, or the next highest horsepower greater than, the pump power input to the bare pump at 120 percent of the BEP flow rate of the tested pump divided by a service factor of 1.15.
• For pumps sold with motors, pumps sold with motors and continuous controls, or pumps sold with motors and non-continuous controls, the motor horsepower is the rated horsepower of the motor with which the pump is being tested.
B. 1.2.1.2 Determine the default nominal full load motor efficiency as described in section II.B.1.2.1.2.1 of this appendix for ESCC, ESFM, IL, RSHES, RSHIL, RSV, and VT pumps; section II.B.1.2.1.2.2 of this appendix for ST pumps; and section II.B.1.2.1.2.3 for SVIL pumps.
B. 1.2.1.2.1. For ESCC, ESFM, IL, RSHES, RSHIL, RSV, and VT pumps, the default nominal full load motor efficiency is the minimum of the nominal full load motor efficiency standards (open or enclosed) from the table containing the current energy conservation standards for NEMA Design B motors at § 431.25, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section II.B.1.2.1.1 of this appendix.
B. 1.2.1.2.2. For ST pumps, prior to the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load motor efficiency is the default nominal full load submersible motor efficiency listed in table 2 of this appendix, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section II.B.1.2.1.1 of this appendix. Starting on the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load motor efficiency shall be the minimum of any nominal full load motor efficiency standard from the table containing energy conservation standards for submersible motors in subpart B of this part, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section II.B.1.2.1.1 of this appendix.
B. 1.2.1.2.3. For SVIL pumps, the default nominal full load motor efficiency is the minimum full load motor efficiency standard from the tables containing the current energy conservation standards for polyphase or CSCR/CSIR small electric motors at § 431.446, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section II.B.1.2.1.1 of this appendix, or for SVIL pumps sold with motors less than 0.25 hp, the default nominal full load motor efficiency is 58.3% for 6-pole, 64.6% for 4-pole, and 61.7% for 2-pole motors.
B. 1.2.2 Determine the part load loss factor at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
yi = the part load loss factor at load point i,
Pi = pump power input to the bare pump at load point i (hp),
MotorHP = the motor horsepower (hp), as determined in accordance with section II.B.1.2.1.1 of this appendix,
III. Test Procedure for Bare Pumps
A. Scope. This section III applies only to:
A. 1 Bare pumps,
A.2 Pumps sold with drivers other than electric motors, and
A.3 ESCC, ESFM, IL, RSHES, RSHIL, RSV, ST, and VT pumps sold with single-phase induction motors.
B. Measurement Equipment. The requirements regarding measurement equipment presented in section I.B of this appendix apply to this section III. In addition, when testing pumps using a calibrated motor, electrical measurement equipment shall meet the requirements of section C.4.3 of HI 40.6-2021 (including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3 of HI 40.6), and motor power input shall be determined according to section 40.6.3.2.3 of HI 40.6-2021 and meet the requirements in Table 40.6.3.2.3 of HI 40.6-2021.
C. Test Conditions. The requirements regarding test conditions presented in section I.C of this appendix apply to this section III. In addition, when testing pumps using a calibrated motor, the conditions in section C.4.3.1 of HI 40.6-2021 shall be met, including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3.1 of HI 40.6-2021.
D. Testing BEP for the Pump. Determine the best efficiency point (BEP) of the pump as follows:
D.
1. Adjust the flow by throttling the pump without changing the speed of rotation of the pump and conduct the test at a minimum of the following seven flow points: 40, 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate of the pump at the nominal speed of rotation, as specified in section 40.6.5.5.1 of HI 40.6-2021, including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6-2021.
D.
2. Determine the BEP flow rate as the flow rate at the operating point of maximum pump efficiency on the pump efficiency curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021, where the pump efficiency is the ratio of the pump power output divided by the pump power input, as specified in Table 40.6.2 of HI 40.6-2021, disregarding the calculations provided in section 40.6.6.2 of HI 40.6-2021.
E. Calculating the Constant Load Pump Energy Rating. Determine the PERCL of each tested pump using the following equation:
Where:
PERCL = the pump energy rating for a constant load (hp),
ωi = 0.3333,
Piin,m = calculated driver power input to the motor at load point i (hp), as determined in accordance with section III.E.1 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1 Determine the driver power input at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
Piin,m = driver power input to the motor at load point i (hp),
Pi = pump power input to the bare pump at load point i (hp), as determined in section III.E.1.1 of this appendix,
Li = the part load motor losses at load point i (hp), as determined in accordance with section III.E.1.2 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1.1 Determine the pump power input at 75, 100, 110, and 120 percent of the BEP flow rate by employing a least squares regression to determine a linear relationship between the pump power input at the nominal speed of rotation of the pump and the measured flow rate at the following load points: 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate. Use the linear relationship to determine the pump power input at the nominal speed of rotation for the load points of 75, 100, 110, and 120 percent of the BEP flow rate.
E. 1.2 Determine the motor part load losses at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Li = Lfull × yi
Where:
Li = motor losses at load point i (hp),
Lfull = motor losses at full load (hp), as determined in accordance with section III.E.1.2.1 of this appendix,
yi = loss factor at load point i as determined in accordance with section III.E.1.2.2 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1.2.1 Determine the full load motor losses using the appropriate motor efficiency value and horsepower as shown in the following equation:
Where:
Lfull = motor losses at full load (hp);
MotorHP = the motor horsepower (hp), as determined in accordance with section II.E.1.2.1.1 of this appendix, and
ηmotor,full = the default nominal full load motor efficiency (%), as determined in accordance with section III.E.1.2.1.2 of this appendix.
E. 1.2.1.1 Determine the motor horsepower as follows:
• For bare pumps other than ST pumps, determine the motor horsepower by selecting the horsepower rating listed in Table 2 of this appendix that is either equivalent to, or the next highest horsepower greater than, the pump power input to the bare pump at 120 percent of the BEP flow rate of the tested pump.
• For ST bare pumps, determine the motor horsepower by selecting the horsepower rating listed in Table 2 of this appendix that, is either equivalent to, or the next highest horsepower greater than, the pump power input to the bare pump at 120 percent of the BEP flow rate of the tested pump divided by a service factor of 1.15.
• For pumps sold with motors, pumps sold with motors and continuous controls, or pumps sold with motors and non-continuous controls, the motor horsepower is the rated horsepower of the motor with which the pump is being tested.
E. 1.2.1.2 Determine the default nominal full load motor efficiency as described in section III.E.1.2.1.2.1 of this appendix for ESCC, ESFM, IL, RSHES, RSHIL, RSV, and VT pumps; or section III.E.1.2.1.2.2. of this appendix for ST pumps; or section III.E.1.2.1.2.3 of this appendix for SVIL pumps.
E. 1.2.1.2.1. For ESCC, ESFM, IL, RSHES, RSHIL, RSV, and VT pumps, the default nominal full load motor efficiency is the minimum of the nominal full load motor efficiency standards (open or enclosed) from the table containing the current energy conservation standards for NEMA Design B motors at § 431.25, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section III.E.1.2.1.1 of this appendix.
E. 1.2.1.2.2. For ST pumps, prior to the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load motor efficiency is the default nominal full load submersible motor efficiency listed in table 2 of this appendix, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section III.E.1.2.1.1 of this appendix. Starting on the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load motor efficiency is the minimum of any nominal full load motor efficiency standard from the table containing energy conservation standards for submersible motors in subpart B of this part, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in accordance with section III.E.1.2.1.1 of this appendix.
E. 1.2.1.2.3. For SVIL pumps, the default nominal full load motor efficiency is the minimum full load motor efficiency standard from the tables containing the current energy conservation standards for polyphase or CSCR/CSIR small electric motors at § 431.446, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower determined in section III.E.1.2.1.1 of this appendix, or for SVIL pumps sold with motors less than 0.25 hp, the default nominal full load motor efficiency is 58.3% for 6-pole, 64.6% for 4-pole, and 61.7% for 2-pole motors.
E. 1.2.2 Determine the loss factor at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
yi = the part load loss factor at load point i,
Pi = pump power input to the bare pump at load point i (hp), as determined in accordance with section III.E.1.1 of this appendix,
MotorHP = as determined in accordance with section III.E.1.2.1 of this appendix (hp),
IV. Testing-Based Approach for Pumps Sold With Motors
A. Scope. This section IV applies only to pumps sold with electric motors (excluding pumps sold with inverter-only synchronous electric motors regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part), including single-phase induction motors.
B. Measurement Equipment. The requirements regarding measurement equipment presented in section I.B of this appendix apply to this section IV. In addition, when testing pumps using a calibrated motor, electrical measurement equipment shall meet the requirements of section C.4.3 of HI 40.6-2021 (including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3 of HI 40.6), and motor power input shall be determined according to section 40.6.3.2.3 of HI 40.6-2021 and meet the requirements in Table 40.6.3.2.3 of HI 40.6-2021.
C. Test Conditions. The requirements regarding test conditions presented in section I.C of this appendix apply to this section IV. In addition, when testing pumps using a calibrated motor, the conditions in section C.4.3.1 of HI 40.6-2021, including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in Section C.4.3.1 of HI 40.6, shall be met.
D. Testing BEP for the Pump. Determine the best efficiency point (BEP) of the pump as follows:
D.
1. Adjust the flow by throttling the pump without changing the speed of rotation of the pump and conduct the test at a minimum of the following seven flow points: 40, 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate of the pump at the nominal speed of rotation, as specified in section 40.6.5.5.1 of HI 40.6-2021, including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6-2021.
D. 2 Determine the BEP flow rate as the flow rate at the operating point of maximum overall efficiency on the pump efficiency curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021, where the overall efficiency is the ratio of the pump power output divided by the driver power input, as specified in Table 40.6.2 of HI 40.6-2021, disregarding the calculations provided in section 40.6.6.2 of HI 40.6-2021.
E. Calculating the Constant Load Pump Energy Rating. Determine the PERCL of each tested pump using the following equation:
Where:
PERCL = the pump energy rating for a constant load (hp),
ωi = 0.3333,
Piin = measured driver power input to the motor at load point i (hp) for the tested pump as determined in accordance with section IV.E.1 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1 Determine the driver power input at 75, 100, and 110 percent of the BEP flow rate by employing a least squares regression to determine a linear relationship between the driver power input at the nominal speed of rotation of the pump and the measured flow rate at the following load points: 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate. Use the linear relationship to determine the driver power input at the nominal speed of rotation for the load points of 75, 100, and 110 percent of the BEP flow rate.
V. Calculation-Based Approach for Pumps Sold With Motors
A. Scope. This section V can only be used in lieu of the test method in section IV of this appendix to calculate the index for pumps sold with motors listed in section V.A.1, V.A.2, or V.A.3 of this appendix.
A. 1 Pumps sold with motors subject to DOE's energy conservation standards for polyphase electric motors at § 431.25(g),
A.2 SVIL pumps sold with small electric motors regulated by DOE's energy conservation standards at § 431.446 or with SNEMs regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part but including motors of such varieties that are less than 0.25 hp, and
A.3. Pumps sold with submersible motors.
A.4. Pumps sold with motors not listed in sections V.A.1, V.A.2, or V.A.3 of this appendix cannot use this section V and must apply the test method in section IV of this appendix.
B. Measurement Equipment. The requirements regarding measurement equipment presented in section I.B of this appendix apply to this section V. In addition, when testing pumps using a calibrated motor, electrical measurement equipment shall meet the requirements of section C.4.3 of HI 40.6-2021 (including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3 of HI 40.6), and motor power input shall be determined according to section 40.6.3.2.3 of HI 40.6-2021 and meet the requirements in Table 40.6.3.2.3 of HI 40.6-2021.
C. Test Conditions. The requirements regarding test conditions presented in section I.C of this appendix apply to this section V. In addition, when testing pumps using a calibrated motor, the conditions in section C.4.3.1 of HI 40.6-2021, including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3.1 of HI 40.6-2021 shall be met.
D. Testing BEP for the Pump. Determine the best efficiency point (BEP) of the pump as follows:
D.
1. Adjust the flow by throttling the pump without changing the speed of rotation of the pump and conduct the test at a minimum of the following seven flow points: 40, 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate of the pump at the nominal speed of rotation, as specified in section 40.6.5.5.1 of HI 40.6-2021, including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6-2021.
D.2. Determine the BEP flow rate as the flow rate at the operating point of maximum pump efficiency on the pump efficiency curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021, where the pump efficiency is the ratio of the pump power output divided by the pump power input, as specified in Table 40.6.2 of HI 40.6-2021, disregarding the calculations provided in section 40.6.6.2.
E. Calculating the Constant Load Pump Energy Rating. Determine the PERCL of each tested pump using the following equation:
Where:
PERCL = the pump energy rating for a constant load (hp),
ωi = 0.3333,
Piin,m = calculated driver power input to the motor at load point i for the tested pump as determined in accordance with section V.E.1 of this appendix (hp), and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1 Determine the driver power input at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
Piin,m = driver power input to the motor at load point i (hp),
Pi = pump power input to the bare pump at load point i, as determined in section V.E.1.1 of this appendix (hp),
Li = the part load motor losses at load point i as determined in accordance with section V.E.1.2 of this appendix (hp), and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1.1 Determine the pump power input at 75, 100, and 110 percent of the BEP flow rate by employing a least squares regression to determine a linear relationship between the pump power input at the nominal speed of rotation of the pump and the measured flow rate at the following load points: 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate. Use the linear relationship to determine the pump power input at the nominal speed of rotation for the load points of 75, 100, and 110 percent of the BEP flow rate.
E. 1.2 Determine the motor part load losses at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Li = Lfull × Yi
Where:
Li = motor losses at load point i (hp),
Lfull = motor losses at full load as determined in accordance with section V.E.1.2.1 of this appendix (hp),
yi = part load loss factor at load point i as determined in accordance with section V.E.1.2.2 of this appendix, and
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate.
E. 1.2.1 Determine the full load motor losses using the appropriate motor efficiency value and horsepower as shown in the following equation:
Where:
Lfull = motor losses at full load (hp),
MotorHP = the horsepower of the motor with which the pump model is being tested (hp), and
ηmotor,full = the represented nominal full load motor efficiency (i.e., nameplate/DOE-certified value) or default nominal full load submersible motor efficiency as determined in accordance with section V.E.1.2.1.1 of this appendix (%).
E. 1.2.1.1 For pumps sold with motors other than submersible motors, determine the represented nominal full load motor efficiency as described in section V.E.1.2.1.1.1 of this appendix. For pumps sold with submersible motors, determine the default nominal full load submersible motor efficiency as described in section V.E.1.2.1.1.2 of this appendix.
E. 1.2.1.1.1 For pumps sold with motors other than submersible motors, the represented nominal full load motor efficiency is that of the motor with which the given pump model is being tested, as determined in accordance with the DOE test procedure for electric motors at § 431.16 or, for SVIL, the DOE test procedure for small electric motors at § 431.444, or the DOE test procedure for SNEMs in subpart B to this part, as applicable (including for motors less than 0.25 hp), and if available, applicable representation procedures in 10 CFR part 429 and this part.
E. 1.2.1.1.2 For pumps sold with submersible motors, prior to the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load submersible motor efficiency is that listed in table 2 of this appendix, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower of the pump being tested, or if a test procedure for submersible motors is provided in subpart B to this part, the represented nominal full load motor efficiency of the motor with which the given pump model is being tested, as determined in accordance with the applicable test procedure in subpart B to this part and applicable representation procedures in 10 CFR part 429 and this part, may be used instead. Starting on the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load submersible motor efficiency may no longer be used. Instead, the represented nominal full load motor efficiency of the motor with which the given pump model is being tested, as determined in accordance with the applicable test procedure in subpart B of this part and applicable representation procedures in 10 CFR part 429 and this part, must be used.
E. 1.2.2 Determine the loss factor at each load point corresponding to 75, 100, or 110 percent of the BEP flow rate as follows:
Where:
yi = the part load loss factor at load point i,
Pi = the pump power input to the bare pump at load point i as determined in accordance with section V.E.1.1 of this appendix (hp),
MotorHP = the horsepower of the motor with which the pump model is being tested (hp),
i = load point corresponding to 75, 100, or 110 percent of the BEP flow rate, and
in the equation in this section V.E.1.2.2. of this appendix to calculate the part load loss factor at each load point
VI. Testing-Based Approach for Pumps Sold with Motors and Controls
A. Scope. This section VI applies only to pumps sold with electric motors, including single-phase induction motors, and continuous or non-continuous controls, as well as to pumps sold with inverter-only synchronous electric motors that are regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part (with or without controls). For the purposes of this section VI, all references to “driver input power” in this section VI or HI 40.6-2021 refer to the input power to the continuous or non-continuous controls.
B. Measurement Equipment. The requirements regarding measurement equipment presented in section I.B of this appendix apply to this section VI. In addition, when testing pumps using a calibrated motor, electrical measurement equipment shall meet the requirements of section C.4.3 of HI 40.6-2021 (including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3 of HI 40.6), and motor power input shall be determined according to section 40.6.3.2.3 of HI 40.6-2021 and meet the requirements in Table 40.6.3.2.3 of HI 40.6-2021.
C. Test Conditions. The requirements regarding test conditions presented in section I.C of this appendix apply to this section VI. In addition, when testing pumps using a calibrated motor, the conditions in section C.4.3.1 of HI 40.6-2021, including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3.1 of HI 40.6, shall be met.
D. Testing BEP for the Pump. Determine the best efficiency point (BEP) of the pump as follows:
D.
1. Adjust the flow by throttling the pump without changing the speed of rotation of the pump and conduct the test at a minimum of the following seven flow points: 40, 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate of the pump at the nominal speed of rotation, as specified in section 40.6.5.5.1 of HI 40.6-2021, including the applicable provisions of HI 9.6.1-2017 as referenced in section 40.6.5.5.1 of HI 40.6-2021.
D. 2 Determine the BEP flow rate as the flow rate at the operating point of maximum overall efficiency on the pump efficiency curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021, where the overall efficiency is the ratio of the pump power output divided by the driver power input, as specified in Table 40.6.2 of HI 40.6-2021, disregarding the calculations provided in section 40.6.6.2 of HI 40.6-2021.
E. Calculating the Variable Load Pump Energy Rating. Determine the PERVL of each tested pump using the following equation:
Where:
PERVL = the pump energy rating for a variable load (hp);
ωi = 0.25;
Piin,c = the normalized driver power input to continuous or non-continuous controls at load point i for the tested pump as determined in accordance with section VI.E.1 of this appendix; and
i = load point corresponding 25, 50, 75, or 100 percent of the BEP flow rate.
E.
1. Determine the driver power input at 100 percent of the measured BEP flow rate of the tested pump by employing a least squares regression to determine a linear relationship between the measured driver power input at the nominal speed of rotation of the pump and the measured flow rate, using the following load points: 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate. Use the linear relationship to determine the driver power input at the nominal speed of rotation for the load point of 100 percent of the measured BEP flow rate of the tested pump.
E.2 Determine the driver power input at 25, 50, and 75 percent of the BEP flow rate by measuring the driver power input at the load points defined by:
(1) Those flow rates, and
(2) The associated head points calculated according to the following reference system curve equation:
Where:
Hi = pump total head at load point i (ft),
H100≠ = pump total head at 100 percent of the BEP flow rate and nominal speed of rotation (ft),
Qi = flow rate at load point i (gpm),
Q100≠ = flow rate at 100 percent of the BEP flow rate and nominal speed of rotation (gpm), and
i = load point corresponding to 25, 50, or 75 percent of the measured BEP flow rate of the tested pump.
E.2.1. For pumps sold with motors and continuous controls, the specific head and flow points must be achieved within 10 percent of the calculated values and the measured driver power input must be corrected to the exact intended head and flow conditions using the following equation:
Where:
Piin,c = the corrected driver power input to the continuous or non-continuous controls at load point i (hp),
Hsp,i = the specified total system head at load point i based on the reference system curve (ft),
HM,j = the measured total system head at load point j (ft),
Qsp,i = the specified total system flow rate at load point i based on the reference system curve (gpm),
QM,j = the measured total system flow rate at load point j (gpm),
PM,jin,c = the measured normalized driver power input to the continuous or non-continuous controls at load point j (hp),
i = specified load point at 25, 50, 75, or 100 percent of BEP flow, and
j = measured load point corresponding to specified load point i.
E. 2.2. For pumps sold with motors and non-continuous controls, the head associated with each of the specified flow points shall be no lower than 10 percent below that defined by the reference system curve equation in section VI.E.2 of this appendix. Only the measured flow points must be achieved within 10 percent of the calculated values. Correct for flow and head as described in section VI.E.2.1, except do not correct measured head values that are higher than the reference system curve at the same flow rate; only correct flow rate and head values lower than the reference system curve at the same flow rate. For head values higher than the system curve, use the measured head points directly to calculate PEIVL.
VII. Calculation-Based Approach for Pumps Sold With Motors and Controls
A. Scope. This section VII can only be used in lieu of the test method in section VI of this appendix to calculate the index for pumps listed in sections VII.A.1, VII.A.2, VII.A.3, and VII.A.4 of this appendix.
A.
1. Pumps sold with motors regulated by DOE's energy conservation standards for polyphase NEMA Design B electric motors at § 431.25(g) and continuous controls,
A.2. Pumps sold with inverter-only synchronous electric motors regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part,
A.3. SVIL pumps sold with small electric motors regulated by DOE's energy conservation standards at § 431.446 or with SNEMs regulated by DOE's test procedure and/or energy conservation standards in subpart B of this part (but including motors of such varieties that are less than 0.25 hp) and continuous controls,
A.4. Pumps sold with submersible motors and continuous controls, and
A.5. Pumps sold with motors not listed in sections VII.A.1, VII.A.2, VII.A.3, and VII.A.4 of this appendix and pumps sold without continuous controls, including pumps sold with non-continuous controls, cannot use this section and must apply the test method in section VI of this appendix.
B. Measurement Equipment. The requirements regarding measurement equipment presented in section I.B of this appendix apply to this section VII. In addition, when testing pumps using a calibrated motor, electrical measurement equipment shall meet the requirements of section C.4.3 of HI 40.6-2021 (including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3 of HI 40.6), and motor power input shall be determined according to section 40.6.3.2.3 of HI 40.6-2021 and meet the requirements in Table 40.6.3.2.3 of HI 40.6-2021.
C. Test Conditions. The requirements regarding test conditions presented in section I.C of this appendix apply to this section VII. In addition, when testing pumps using a calibrated motor, the conditions in section C.4.3.1 of HI 40.6-2021, including the applicable provisions of CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, as referenced in section C.4.3.1 of HI 40.6-2021 shall be met.
D. Testing BEP for the Pump. Determine the best efficiency point (BEP) of the pump as follows:
D.
1. Adjust the flow by throttling the pump without changing the speed of rotation of the pump and conduct the test at a minimum of the following seven flow points: 40, 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate of the pump at the nominal speed of rotation, as specified in HI 40.6-2021, except section 40.6.5.3, and appendix B, including the applicable provisions of HI 9.6.1-2017, HI 9.6.6-2016, HI 9.8-2018, HI 14.1-14.2-2019, the HI Engineering Data Book, ASME MFC-3M-2004, ASME MFC-5M-1985, ASME MFC-8M-2001, ASME MFC-12M-2006, ASME MFC-16-2014, ASME MFC-22-2007, AWWA E103-2015, CSA C390-10, IEEE 112-2017, IEEE 114-2010-A, ISO 1438:2017, ISO 2186:2007, ISO 2715:2017, ISO 3354:2008, ISO 3966:2020, ISO 5167-1:2003, ISO 5198:1987, ISO 6416:2017, and ISO 20456:2017, as referenced in HI 40.6-2021.
D.2. Determine the BEP flow rate as the flow rate at the operating point of maximum pump efficiency on the pump efficiency curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021, where the pump efficiency is the ratio of the pump power output divided by the pump power input, as specified in Table 40.6.2 of HI 40.6-2021, disregarding the calculations provided in section 40.6.6.2.
E. Calculating the Variable Load Pump Energy Rating. Determine the PERVL of each tested pump using the following equation:
Where:
PERVL = the pump energy rating for a variable load (hp);
ωi = 0.25;
Piin,c = the calculated driver power input to the continuous or non-continuous controls at load point i for the tested pump as determined in accordance with section VII.E.1 of this appendix; and
i = load point corresponding to 25, 50, 75, or 100 percent of the BEP flow rate.
E. 1 Determine the driver power input at each load point corresponding to 25, 50, 75, or 100 percent of the BEP flow rate as follows:
Where:
Piin,c = driver power input at to the continuous or non-continuous controls at load point i (hp),
Pi = pump power input to the bare pump at load point i as determined in accordance with section VII.E.1.1 of this appendix (hp),
Li = the part load motor and control losses at load point i as determined in accordance with section VII.E.1.2 of this appendix (hp), and
i = load point corresponding to 25, 50, 75, or 100 percent of the BEP flow rate.
E. 1.1 Determine the pump power input at 100 percent of the measured BEP flow rate of the tested pump by employing a least squares regression to determine a linear relationship between the measured pump power input at the nominal speed of rotation and the measured flow rate at the following load points: 60, 75, 90, 100, 110, and 120 percent of the expected BEP flow rate. Use the linear relationship to determine the pump power input at the nominal speed of rotation for the load point of 100 percent of the BEP flow rate.
E. 1.1.1 Determine the pump power input at 25, 50, and 75 percent of the BEP flow rate based on the measured pump power input at 100 percent of the BEP flow rate and using with the following equation:
Where:
Pi = pump power input at load point i (hp);
P100% = pump power input at 100 percent of the BEP flow rate and nominal speed of rotation (hp);
Qi = flow rate at load point i (gpm);
Q100% = flow rate at 100 percent of the BEP flow rate and nominal speed of rotation (gpm); and
i = load point corresponding to 25, 50, or 75 percent of the measured BEP flow rate of the tested pump.
E. 1.2 Calculate the motor and control part load losses at each load point corresponding to 25, 50, 75, and 100 percent of the BEP flow rate as follows:
Li = Lfull × zi
Where:
Li = motor and control losses at load point i (hp),
Lfull = motor losses at full load or, for inverter-only synchronous electric motors, motor + inverter losses at full load, as determined in accordance with section VII.E.1.2.1 of this appendix (hp),
zi = part load loss factor at load point i as determined in accordance with section VII.E.1.2.2 of this appendix, and
i = load point corresponding to 25, 50, 75, or 100 percent of the BEP flow rate.
E. 1.2.1 Determine the full load motor losses using the appropriate motor efficiency value and horsepower as shown in the following equation:
Where:
Lfull = motor losses at full load (hp), or for inverter-only synchronous electric motors, motor + inverter losses at full load,
MotorHP = the horsepower of the motor with which the pump model is being tested (hp), and
ηmotor,full = the represented nominal full load motor efficiency (i.e., nameplate/DOE-certified value) or the represented nominal full load motor + inverter efficiency or the default nominal full load submersible motor efficiency as determined in accordance with section VII.E.1.2.1.1 of this appendix (%).
E. 1.2.1.1 For pumps sold with motors other than inverter-only synchronous electric motors or submersible motors, determine the represented nominal full load motor efficiency as described in section VII.E.1.2.1.1.1 of this appendix. For pumps sold with inverter-only synchronous electric motors, determine the represented nominal full load motor + inverter efficiency as described in section VII.E.1.2.1.1.2 of this appendix. For pumps sold with submersible motors, determine the default nominal full load submersible motor efficiency as described in section VII.E.1.2.1.1.3 of this appendix.
E. 1.2.1.1.1 For pumps sold with motors other than inverter-only synchronous electric motors or submersible motors, the represented nominal full load motor efficiency is that of the motor with which the given pump model is being tested, as determined in accordance with the DOE test procedure for electric motors at § 431.16 or, for SVIL, the DOE test procedure for small electric motors at § 431.444 or the DOE test procedure for SNEMs in subpart B of this part, as applicable (including for motors less than 0.25 hp), and, if available, applicable representation procedures in 10 CFR part 429 and this part.
E. 1.2.1.1.2 For pumps sold with inverter-only synchronous electric motors, the represented nominal full load motor + inverter efficiency is that of the motor with which the given pump model is being tested, as determined in accordance with the DOE test procedure for inverter-only synchronous electric motors in subpart B of this part, and, if available, applicable representation procedures in 10 CFR part 429 and this part.
E. 1.2.1.1.3 For pumps sold with submersible motors, prior to the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load submersible motor efficiency is that listed in table 2 of this appendix, with the number of poles relevant to the speed at which the pump is being tested (see section I.C.1 of this appendix) and the motor horsepower of the pump being tested, or if a test procedure for submersible motors is provided in subpart B of this part, the represented nominal full load motor efficiency of the motor with which the given pump model is being tested, as determined in accordance with the applicable test procedure in subpart B of this part and applicable representation procedures in 10 CFR part 429 and this part, may be used instead. Starting on the compliance date of any energy conservation standards for submersible motors in subpart B of this part, the default nominal full load submersible motor efficiency may no longer be used and instead the represented nominal full load motor efficiency of the motor with which the given pump model is being tested, as determined in accordance with the applicable test procedure in subpart B of this part and applicable representation procedures in 10 CFR part 429 and this part, must be used instead.
E. 1.2.2 For load points corresponding to 25, 50, 75, and 100 percent of the BEP flow rate, determine the part load loss factor at each load point as follows:
Where:
z i = the motor and control part load loss factor at load point i,
a,b,c = coefficients listed in either Table 4 of this appendix for induction motors or Table 5 of this appendix for inverter-only synchronous electric motors, based on the horsepower of the motor with which the pump is being tested,
Pi = the pump power input to the bare pump at load point i, as determined in accordance with section VII.E.1.1 of this appendix (hp),
MotorHP = the horsepower of the motor with which the pump is being tested (hp),
| Motor horsepower
(hp) |
Default nominal full load submersible motor efficiency | ||
|---|---|---|---|
| 2 poles | 4 poles | 6 poles | |
| 1 | 55 | 68 | 64 |
| 1.5 | 66 | 70 | 72 |
| 2 | 68 | 70 | 74 |
| 3 | 70 | 75.5 | 75.5 |
| 5 | 74 | 75.5 | 75.5 |
| 7.5 | 68 | 74 | 72 |
| 10 | 70 | 74 | 72 |
| 15 | 72 | 75.5 | 74 |
| 20 | 72 | 77 | 74 |
| 25 | 74 | 78.5 | 77 |
| 30 | 77 | 80 | 78.5 |
| 40 | 78.5 | 81.5 | 81.5 |
| 50 | 80 | 82.5 | 81.5 |
| 60 | 81.5 | 84 | 82.5 |
| 75 | 81.5 | 85.5 | 82.5 |
| 100 | 81.5 | 84 | 82.5 |
| 125 | 84 | 84 | 82.5 |
| 150 | 84 | 85.5 | 85.5 |
| 200 | 85.5 | 86.5 | 85.5 |
| 250 | 86.5 | 86.5 | 85.5 |
| Nominal full load motor efficiency* |
|---|
| 50.5 |
| 52.5 |
| 55.0 |
| 57.5 |
| 59.5 |
| 62.0 |
| 64.0 |
| 66.0 |
| 68.0 |
| 70.0 |
| 72.0 |
| 74.0 |
| 75.5 |
| 77.0 |
| 78.5 |
| 80.0 |
| 81.5 |
| 82.5 |
| 84.0 |
| 85.5 |
| 86.5 |
| 87.5 |
| 88.5 |
| 89.5 |
| 90.2 |
| 91.0 |
| 91.7 |
| 92.4 |
| 93.0 |
| 93.6 |
| 94.1 |
| 94.5 |
| 95.0 |
| 95.4 |
| 95.8 |
| 96.2 |
| 96.5 |
| 96.8 |
| 97.1 |
| 97.4 |
| 97.6 |
| 97.8 |
| 98.0 |
| 98.2 |
| 98.4 |
| 98.5 |
| 98.6 |
| 98.7 |
| 98.8 |
| 98.9 |
| 99.0 |
| * Note: Each consecutive incremental value of nominal efficiency represents one band. |
| Motor horsepower
(hp) |
Coefficients for induction motor and control part load loss factor
(zi) |
||
|---|---|---|---|
| a | b | c | |
| ≤5 | −0.4658 | 1.4965 | 0.5303 |
| >5 and ≤20 | −1.3198 | 2.9551 | 0.1052 |
| >20 and ≤50 | −1.5122 | 3.0777 | 0.1847 |
| >50 and ≤100 | −0.6629 | 2.1452 | 0.1952 |
| >100 | −0.7583 | 2.4538 | 0.2233 |
| Motor horsepower
(hp) |
Coefficients for induction motor and control part load loss factor
(zi) |
||
|---|---|---|---|
| a | b | c | |
| ≤5 | −0.0898 | 1.0251 | 0.0667 |
| >5 and ≤20 | −0.1591 | 1.1683 | −0.0085 |
| >20 and ≤50 | −0.4071 | 1.4028 | 0.0055 |
| >50 and ≤100 | −0.3341 | 1.3377 | −0.0023 |
| >100 | −0.0749 | 1.0864 | −0.0096 |
[81 FR 4145, Jan. 25, 2016, as amended at 82 FR 36924, Aug. 7, 2017; 88 FR 17978, Mar. 24, 2023; 88 FR 24471, Apr. 21, 2023; 90 FR 6795, Jan. 21, 2025]
On February 5, 2018 but before July 19, 2021, any representations made with respect to the energy use or efficiency of dedicated-purpose pool pumps subject to testing pursuant to 10 CFR 431.464(b) must be made in accordance with the results of testing pursuant to this appendix. Any optional representations of energy factor (EF) must be accompanied by a representation of weighted energy factor (WEF).
I. Test Procedure for Dedicated-Purpose Pool Pumps
A. General
A. 1 Test Method. To determine the weighted energy factor (WEF) for dedicated-purpose pool pumps, perform “wire-to-water” testing in accordance with HI 40.6-2014-B, except section 40.6.4.1, “Vertically suspended pumps”; section 40.6.4.2, “Submersible pumps”; section 40.6.5.3, “Test report”; section 40.6.5.5, “Test conditions”; section 40.6.5.5.2, “Speed of rotation during testing”; section 40.6.6.1, “Translation of test results to rated speed of rotation”; section 40.6.6.2, “Pump efficiency”; section 40.6.6.3, “Performance curve”; section A.7, “Testing at temperatures exceeding 30 °C (86 °F)”; and appendix B, “Reporting of test results”; (incorporated by reference, see § 431.463) with the modifications and additions as noted throughout the provisions below. Do not use the test points specified in section 40.6.5.5.1, “Test procedure” of HI 40.6-2014-B and instead use those test points specified in section D.3 of this appendix for the applicable dedicated-purpose pool pump variety and speed configuration. When determining overall efficiency, best efficiency point, or other applicable pump energy performance information, section 40.6.5.5.1, “Test procedure”; section 40.6.6.2, “Pump efficiency”; and section 40.6.6.3, “Performance curve” must be used, as applicable. For the purposes of applying this appendix, the term “volume per unit time,” as defined in section 40.6.2, “Terms and definitions,” of HI 40.6-2014-B shall be deemed to be synonymous with the term “flow rate” used throughout that standard and this appendix.
A.
2. Calculations and Rounding. All terms and quantities refer to values determined in accordance with the procedures set forth in this appendix for the rated pump. Perform all calculations using raw measured values without rounding. Round WEF, EF, maximum head, vertical lift, and true priming time values to the tenths place (i.e., 0.1) and rated hydraulic horsepower to the thousandths place (i.e., 0.001). Round all other reported values to the hundredths place unless otherwise specified.
B. Measurement Equipment
B. 1 For the purposes of measuring flow rate, speed of rotation, temperature, and pump power output, the equipment specified in HI 40.6-2014-B Appendix C (incorporated by reference, see § 431.463) necessary to measure head, speed of rotation, flow rate, and temperature must be used and must comply with the stated accuracy requirements in HI 40.6-2014-B Table 40.6.3.2.3, except as specified in section B.1.1 and B.1.2 of this appendix. When more than one instrument is used to measure a given parameter, the combined accuracy, calculated as the root sum of squares of individual instrument accuracies, must meet the specified accuracy requirements.
B. 1.1 Electrical measurement equipment for determining the driver power input to the motor or controls must be capable of measuring true root mean squared (RMS) current, true RMS voltage, and real power up to the 40th harmonic of fundamental supply source frequency, and have a combined accuracy of ±2.0 percent of the measured value at the fundamental supply source frequency.
B. 1.2 Instruments for measuring distance (e.g., height above the reference plane or water level) must be accurate to and have a resolution of at least ±0.1 inch.
B. 2 Calibration. Calibration requirements for instrumentation are specified in appendix D of HI 40.6-2014-B (incorporated by reference, see § 431.463). Historical calibration data may be used to justify time periods up to three times longer than those specified in table D.1 of HI 40.6-2014-B provided the supporting historical data shows maintenance of calibration of the given instrument up to the selected extended calibration interval on at least two unique occasions, based on the interval specified in HI 40.6-2014-B.
C. Test Conditions and Tolerances
C. 1 Pump Specifications. Conduct testing at full impeller diameter in accordance with the test conditions, stabilization requirements, and specifications of HI 40.6-2014-B section 40.6.3, “Pump efficiency testing”; section 40.6.4, “Considerations when determining the efficiency of a pump”; section 40.6.5.4 (including appendix A), “Test arrangements”; and section 40.6.5.5, “Test conditions” (incorporated by reference, see § 431.463).
C. 2 Power Supply Requirements. The following conditions also apply to the mains power supplied to the DPPP motor or controls, if any:
(1) Maintain the voltage within ±5 percent of the rated value of the motor,
(2) Maintain the frequency within ±1 percent of the rated value of the motor,
(3) Maintain the voltage unbalance of the power supply within ±3 percent of the value with which the motor was rated, and
(4) Maintain total harmonic distortion below 12 percent throughout the test.
C. 3 Test Conditions. Testing must be carried out with water that is between 50 and 107 °F with less than or equal to 15 nephelometric turbidity units (NTU).
C. 4 Tolerances. For waterfall pumps, multi-speed self-priming and non-self-priming pool filter pumps, and variable-speed self-priming and non-self-priming pool filter pumps all measured load points must be within ±2.5 percent of the specified head value and comply with any specified flow values or thresholds. For all other dedicated-purpose pool pumps, all measured load points must be within the greater of ±2.5 percent of the specified flow rate values or ±0.5 gpm and comply with any specified head values or thresholds.
D. Data Collection and Stabilization
D. 1 Damping Devices. Use of damping devices, as described in section 40.6.3.2.2 of HI 40.6-2014-B (incorporated by reference, see § 431.463), are only permitted to integrate up to the data collection interval used during testing.
D. 2 Stabilization. Record data at any tested load point only under stabilized conditions, as defined in HI 40.6-2014-B section 40.6.5.5.1 (incorporated by reference, see § 431.463), where a minimum of two measurements are used to determine stabilization.
D. 3 Test Points. Measure the flow rate in gpm, pump total head in ft, the driver power input in W, and the speed of rotation in rpm at each load point specified in Table 1 of this appendix for each DPPP variety and speed configuration:
| DPPP varieties | Speed configuration(s) | Number of load points (n) |
Load point (i) |
Test points | ||
|---|---|---|---|---|---|---|
| Flow rate (Q) (GPM) |
Head (H) (ft) |
Speed (rpm) |
||||
| Self-Priming Pool Filter Pumps And Non-Self-Priming Pool Filter Pumps | Single-speed dedicated-purpose pool pumps and all self-priming and non-self-priming pool filter pumps not meeting the definition of two-*, multi-, or variable-speed dedicated-purpose pool pump | 1 | High | Qhigh (gpm) = Qmax__speed@C ** | H = 0.0082 × Qhigh 2 | Maximum speed |
| Two-speed dedicated-purpose pool pumps * | 2 | Low | Qlow (gpm) = Flow rate associated with specified head and speed that is not below: • 31.1 gpm if rated hydraulic horsepower is >0.75 or • 24.7 gpm if rated hydraulic horsepower is ≤0.75 |
H = 0.0082 × Qlow 2 | Lowest speed capable of meeting the specified flow and head values, if any ***. | |
| High | Qhigh (gpm) = Qmax__speed@C ** | H = 0.0082 × Qhigh 2 | Maximum speed. | |||
| Multi-speed and variable-speed dedicated-purpose pool pumps | 2 | Low | Qlow (gpm) = • If rated hydraulic horsepower is >0.75, then Qlow ≥ 31.1 gpm • If rated hydraulic horsepower is ≤0.75, then Qlow ≥24.7 gpm |
H = 0.0082 × Qlow 2 | Lowest speed capable of meeting the specified flow and head values. | |
| High | Qhigh (gpm) ≥0.8 × Qmax__speed@C ** | H = 0.0082 × Qhigh 2 | Lowest speed capable of meeting the specified flow and head values. | |||
| Waterfall Pumps | Single-speed dedicated-purpose pool pumps | 1 | High | Qlow (gpm) = Flow corresponding to specified head | 17.0 ft | Maximum speed. |
| Pressure Cleaner Booster Pumps | Any | 1 | High | 10.0 gpm | ≥60.0 ft | Lowest speed capable of meeting the specified flow and head values. |
| * In order to apply the test points for two-speed self-priming and non-self-priming pool filter pumps, self-priming pool filter pumps that are greater than or equal to 0.711 rated hydraulic horsepower that are two-speed dedicated-purpose pool pumps must also be distributed in commerce either: (1) With a pool pump control (variable speed drive and user interface or switch) that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times or (2) without a pool pump control that has such capability, but without which the pump is unable to operate. Two-speed self-priming pool filter pumps greater than or equal to 0.711 rated hydraulic horsepower that do not meet these requirements must be tested using the load point for single-speed self-priming or non-self-priming pool filter pumps, as appropriate. | ||||||
| ** Qmax__speed@C = Flow at max speed on curve C (gpm) | ||||||
| *** If a two-speed pump has a low speed that results in a flow rate below the specified values, the low speed of that pump shall not be tested. | ||||||
E. Calculations
E. 1 Determination of Weighted Energy Factor. Determine the WEF as a ratio of the measured flow and driver power input to the dedicated-purpose pool pump in accordance with the following equation:
Where:
WEF = Weighted Energy Factor in kgal/kWh;
wi = weighting factor at each load point i, as specified in section E.2 of this appendix;
Qi = flow at each load point i, in gpm;
Pi = driver power input to the motor (or controls, if present) at each load point i, in watts;
i = load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix; and
n = number of load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix.
E. 2 Weights. When determining WEF, apply the weights specified in Table 2 of this appendix for the applicable load points, DPPP varieties, and speed configurations:
| DPPP varieties | Speed configuration(s) | Load point(s) i | |
|---|---|---|---|
| Low flow | High flow | ||
| Self-Priming Pool Filter Pumps and Non-Self-Priming Pool Filter Pumps | Single-speed dedicated-purpose pool pumps and all self-priming and non-self-priming pool filter pumps not meeting the definition of two-,* multi-, or variable-speed dedicated-purpose pool pump | 1.0 | |
| Two-speed dedicated-purpose pool pumps * | 0.80 | 0.20 | |
| Multi-speed and variable-speed dedicated-purpose pool pumps | 0.80 | 0.20 | |
| Waterfall Pumps | Single-speed dedicated-purpose pool pumps | 1.0 | |
| Pressure Cleaner Booster Pump | Any | 1.0 | |
| * In order to apply the test points for two-speed self-priming and non-self-priming pool filter pumps, self-priming pool filter pumps that are greater than or equal to 0.711 rated hydraulic horsepower that are two-speed dedicated-purpose pool pumps must also be distributed in commerce either: (1) With a pool pump control (variable speed drive and user interface or switch) that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times or (2) without a pool pump control that has such capability, but without which the pump is unable to operate. Two-speed self-priming pool filter pumps greater than or equal to 0.711 rated hydraulic horsepower that do not meet these requirements must be tested using the load point for single-speed self-priming or non-self-priming pool filter pumps, as appropriate. | |||
E. 3 Determination of Horsepower and True Power Factor Metrics
E. 3.1 Determine the pump power output at any load point i using the following equation:
Where:
Pu,i = the measured pump power output at load point i of the tested pump, in hp;
Qi = the measured flow rate at load point i of the tested pump, in gpm;
Hi = pump total head at load point i of the tested pump, in ft; and
SG = the specific gravity of water at specified test conditions, which is equivalent to 1.00.
E. 3.1.1 Determine the rated hydraulic horsepower as the pump power output measured on the reference curve at maximum rotating speed and full impeller diameter for the rated pump.
E. 3.2 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, determine the dedicated-purpose pool pump nominal motor horsepower as the product of the measured full load speed and torque, adjusted to the appropriate units, as shown in the following equation:
Where:
Pnm = the dedicated-purpose pool pump nominal total horsepower at full load, in hp;
T = output torque at full load, in lb-ft; and
n = the motor speed at full load, in rpm.
Full-load speed and torque shall be determined based on the maximum continuous duty motor power output rating allowable for the motor's nameplate ambient rating and insulation class.
E. 3.2.1 For single-phase AC motors, determine the measured speed and torque at full load according to either section E.3.2.1.1 or E.3.2.1.2 of this appendix.
E. 3.2.1.1 Use the procedures in section 3.2, “Tests with load”; section 4 “Testing facilities”; section 5.2 “Mechanical measurements”; section 5.3 “Temperature measurements”; and section 6 “Tests” of IEEE 114-2010 (incorporated by reference, see § 431.463), or
E. 3.2.1.2 Use the applicable procedures in section 5, “General test requirements” and section 6, “Tests” of CSA C747-2009 (RA 2014); except in section 6.4(b) the conversion factor shall be 5252, only measurements at full load are required in section 6.5, and section 6.6 shall be disregarded (incorporated by reference, see § 431.463).
E. 3.2.2 For DC motors, determine the measured speed and torque at full load according to either section E.3.2.2.1 or E.3.2.2.2 of this appendix.
E. 3.2.2.1 Use the procedures in section 3.1, “Instrument Selection Factors”; section 3.4 “Power Measurement”: Section 3.5 “Power Sources”; section 4.1.2 “Ambient Air”; section 4.1.4 “Direction of Rotation”; section 5.4.1 “Reference Conditions”; and section 5.4.3.2 “Dynomometer or Torquemeter Method” of IEEE 113-1985 (incorporated by reference, see § 431.463), or
E. 3.2.2.2 Use the applicable procedures in section 5, “General test requirements” and section 6, “Tests” of CSA C747-2009 (RA 2014); except in section 6.4(b) the conversion factor shall be 5252, only measurements at full load are required in section 6.5, and section 6.6 shall be disregarded (incorporated by reference, see § 431.463).
E. 3.3 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, the dedicated-purpose pool pump service factor is equal to 1.0.
E. 3.4 Determine the dedicated-purpose pool pump motor total horsepower according to section E.3.4.1 of this appendix for dedicated-purpose pool pumps with single-phase AC motors or DC motors and section E.3.4.2 of this appendix for dedicated-purpose pool pumps with polyphase AC motors.
E. 3.4.1 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, determine the dedicated-purpose pool pump motor total horsepower as the product of the dedicated-purpose pool pump nominal motor horsepower, determined in accordance with section E.3.2 of this appendix, and the dedicated-purpose pool pump service factor, determined in accordance with section E.3.3 of this appendix.
E. 3.4.2 For dedicated-purpose pool pumps with polyphase AC induction motors, determine the dedicated-purpose pool pump motor total horsepower as the product of the rated nominal motor horsepower and the rated service factor of the motor.
E. 3.5 Determine the true power factor at each applicable load point specified in Table 1 of this appendix for each DPPP variety and speed configuration as a ratio of driver power input to the motor (or controls, if present) (Pi), in watts, divided by the product of the voltage in volts and the current in amps at each load point i, as shown in the following equation:
Where:
PFi = true power factor at each load point i, dimensionless;
Pi = driver power input to the motor (or controls, if present) at each load point i, in watts;
Vi = voltage at each load point i, in volts;
Ii = current at each load point i, in amps; and
i = load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix.
E. 4 Determination of Maximum Head. Determine the maximum head for self-priming pool filter pumps, non-self-priming pool filter pumps, and waterfall pumps by measuring the head at maximum speed and the minimum flow rate at which the pump is designed to operate continuously or safely, where the minimum flow rate is assumed to be zero unless stated otherwise in the manufacturer literature.
F. Determination of Self-Priming Capability
F. 1 Test Method. Determine the vertical lift and true priming time of non-self-priming pool filter pumps and self-priming pool filter pumps that are not already certified as self-priming under NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) by testing such pumps pursuant to section C.3 of appendix C of NSF/ANSI 50-2015, except for the modifications and exceptions listed in the following sections F.1.1 through F.1.5 of this appendix:
F. 1.1 Where section C.3.2, “Apparatus,” and section C.3.4, “Self-priming capability test method,” of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) state that the “suction line must be essentially as shown in annex C, figure C.1;” the phrase “essentially as shown in Annex C, figure C.1” means:
• The centerline of the pump impeller shaft is situated a vertical distance equivalent to the specified vertical lift (VL), calculated in accordance with section F.1.1.1. of this appendix, above the water level of a water tank of sufficient volume as to maintain a constant water surface level for the duration of the test;
• The pump draws water from the water tank with a riser pipe that extends below the water level a distance of at least 3 times the riser pipe diameter (i.e., 3 pipe diameters);
• The suction inlet of the pump is at least 5 pipe diameters from any obstructions, 90° bends, valves, or fittings; and
• The riser pipe is of the same pipe diameter as the pump suction inlet.
F. 1.1.1 The vertical lift (VL) must be normalized to 5.0 feet at an atmospheric pressure of 14.7 psia and a water density of 62.4 lb/ft3 in accordance with the following equation:
Where:
VL = vertical lift of the test apparatus from the waterline to the centerline of the pump impeller shaft, in ft;
ρtest = density of test fluid, in lb/ft3; and
Pabs,test = absolute barometric pressure of test apparatus location at centerline of pump impeller shaft, in psia.
F. 1.2 The equipment accuracy requirements specified in section B, “Measurement Equipment,” of this appendix also apply to this section F, as applicable.
F. 1.2.1 All measurements of head (gauge pressure), flow, and water temperature must be taken at the pump suction inlet and all head measurements must be normalized back to the centerline of the pump impeller shaft in accordance with section A.3.1.3.1 of HI 40.6-2014-B (incorporated by reference, see § 431.463).
F. 1.3 All tests must be conducted with clear water that meets the requirements adopted in section C.3 of this appendix.
F. 1.4 In section C.3.4, “Self-priming capability test method,” of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463), “the elapsed time to steady discharge gauge reading or full discharge flow” is determined when the changes in head and flow, respectively, are within the tolerance values specified in table 40.6.3.2.2, “Permissible amplitude of fluctuation as a percentage of mean value of quantity being measured at any test point,” of HI 40.6-2014-B (incorporated by reference, see § 431.463). The measured priming time (MPT) is determined as the point in time when the stabilized load point is first achieved, not when stabilization is determined. In addition, the true priming time (TPT) is equivalent to the MPT.
F. 1.5 The maximum true priming time for each test run must not exceed 10.0 minutes. Disregard section C.3.5 of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463).
G. Optional Testing and Calculations
G. 1 Energy Factor. When making representations regarding the EF of dedicated-purpose pool pumps, determine EF on one of four system curves (A, B, C, or D) and at any given speed (s) according to the following equation:
Where:
EFX,s = the energy factor on system curve X at speed s in gal/Wh;
X = one of four possible system curves (A, B, C, or D), as defined in section G.1.1 of this appendix;
s = the tested speed, in rpm;
QX,s = flow rate measured on system curve X at speed s in gpm; and
PX,s = driver power input to the motor (or controls, if present) on system curve X at speed s in watts.
G. 1.1 System Curves. The energy factor may be determined at any speed (s) and on any of the four system curves A, B, C, and/or D specified in the Table 3:
| System curve | System curve equation * |
|---|---|
| A | H = 0.0167 × Q2 |
| B | H = 0.0500 × Q2 |
| C | H = 0.0082 × Q2 |
| D | H = 0.0044 × Q2 |
| * In the above table, Q refers to the flow rate in gpm and H refers to head in ft. | |
G. 2 Replacement Dedicated-Purpose Pool Pump Motors. To determine the WEF for replacement DPPP motors, test each replacement DPPP motor paired with each dedicated-purpose pool pump bare pump for which the replacement DPPP motor is advertised to be paired, as stated in the manufacturer's literature for that replacement DPPP motor model, according to the testing and calculations described in sections A, B, C, D, and E of this appendix. Alternatively, each replacement DPPP motor may be tested with the most consumptive dedicated-purpose pool pump bare pump for which it is advertised to be paired, as stated in the manufacturer's literature for that replacement DPPP motor model. If a replacement DPPP motor is not advertised to be paired with any specific dedicated-purpose pool pump bare pumps, test with the most consumptive dedicated-purpose pool pump bare pump available.
[82 FR 36924, Aug. 7, 2017]
Any representations made on or after July 19, 2021, with respect to the energy use or efficiency of dedicated-purpose pool pumps subject to testing pursuant to 10 CFR 431.464(b) must be made in accordance with the results of testing pursuant to this appendix.
I. Test Procedure for Dedicated-Purpose Pool Pumps
A. General
A. 1 Test Method. To determine the weighted energy factor (WEF) for dedicated-purpose pool pumps, perform “wire-to-water” testing in accordance with HI 40.6-2014-B, except section 40.6.4.1, “Vertically suspended pumps”; section 40.6.4.2, “Submersible pumps”; section 40.6.5.3, “Test report”; section 40.6.5.5, “Test conditions”; section 40.6.5.5.2, “Speed of rotation during testing”; section 40.6.6.1, “Translation of test results to rated speed of rotation”; section 40.6.6.2, “Pump efficiency”; section 40.6.6.3, “Performance curve”; section A.7, “Testing at temperatures exceeding 30 °C (86 °F)”; and appendix B, “Reporting of test results”; (incorporated by reference, see § 431.463) with the modifications and additions as noted throughout the provisions below. Do not use the test points specified in section 40.6.5.5.1, “Test procedure” of HI 40.6-2014-B and instead use those test points specified in section D.3 of this appendix for the applicable dedicated-purpose pool pump variety and speed configuration. When determining overall efficiency, best efficiency point, or other applicable pump energy performance information, section 40.6.5.5.1, “Test procedure”; section 40.6.6.2, “Pump efficiency”; and section 40.6.6.3, “Performance curve” must be used, as applicable. For the purposes of applying this appendix, the term “volume per unit time,” as defined in section 40.6.2, “Terms and definitions,” of HI 40.6-2014-B shall be deemed to be synonymous with the term “flow rate” used throughout that standard and this appendix .
A. 2 Calculations and Rounding. All terms and quantities refer to values determined in accordance with the procedures set forth in this appendix for the rated pump. Perform all calculations using raw measured values without rounding. Round WEF, maximum head, vertical lift, and true priming time values to the tenths place (i.e., 0.1) and rated hydraulic horsepower to the thousandths place (i.e., 0.001). Round all other reported values to the hundredths place unless otherwise specified.
B. Measurement Equipment
B. 1 For the purposes of measuring flow rate, speed of rotation, temperature, and pump power output, the equipment specified in HI 40.6-2014-B Appendix C (incorporated by reference, see § 431.463) necessary to measure head, speed of rotation, flow rate, and temperature must be used and must comply with the stated accuracy requirements in HI 40.6-2014-B Table 40.6.3.2.3, except as specified in sections B.1.1 and B.1.2 of this appendix. When more than one instrument is used to measure a given parameter, the combined accuracy, calculated as the root sum of squares of individual instrument accuracies, must meet the specified accuracy requirements.
B. 1.1 Electrical measurement equipment for determining the driver power input to the motor or controls must be capable of measuring true root mean squared (RMS) current, true RMS voltage, and real power up to the 40th harmonic of fundamental supply source frequency, and have a combined accuracy of ±2.0 percent of the measured value at the fundamental supply source frequency.
B. 1.2 Instruments for measuring distance (e.g., height above the reference plane or water level) must be accurate to and have a resolution of at least ±0.1 inch.
B. 2 Calibration. Calibration requirements for instrumentation are specified in appendix D of HI 40.6-2014-B (incorporated by reference, see § 431.463). Historical calibration data may be used to justify time periods up to three times longer than those specified in table D.1 of HI 40.6-2014-B provided the supporting historical data shows maintenance of calibration of the given instrument up to the selected extended calibration interval on at least two unique occasions, based on the interval specified in HI 40.6-2014-B.
C. Test Conditions and Tolerances
C. 1 Pump Specifications. Conduct testing at full impeller diameter in accordance with the test conditions, stabilization requirements, and specifications of HI 40.6-2014-B section 40.6.3, “Pump efficiency testing”; section 40.6.4, “Considerations when determining the efficiency of a pump”; section 40.6.5.4 (including appendix A), “Test arrangements”; and section 40.6.5.5, “Test conditions” (incorporated by reference, see § 431.463).
C. 2 Power Supply Requirements. The following conditions also apply to the mains power supplied to the DPPP motor or controls, if any:
(1) Maintain the voltage within ±5 percent of the rated value of the motor,
(2) Maintain the frequency within ±1 percent of the rated value of the motor,
(3) Maintain the voltage unbalance of the power supply within ±3 percent of the value with which the motor was rated, and
(4) Maintain total harmonic distortion below 12 percent throughout the test.
C. 3 Test Conditions. Testing must be carried out with water that is between 50 and 107 °F with less than or equal to 15 nephelometric turbidity units (NTU).
C. 4 Tolerances. For waterfall pumps, multi-speed self-priming and non-self-priming pool filter pumps, and variable-speed self-priming and non-self-priming pool filter pumps all measured load points must be within ±2.5 percent of the specified head value and comply with any specified flow values or thresholds. For all other dedicated-purpose pool pumps, all measured load points must be within the greater of ±2.5 percent of the specified flow rate values or ±0.5 gpm and comply with any specified head values or thresholds.
D. Data Collection and Stabilization
D. 1 Damping Devices. Use of damping devices, as described in section 40.6.3.2.2 of HI 40.6-2014-B (incorporated by reference, see § 431.463), are only permitted to integrate up to the data collection interval used during testing.
D. 2 Stabilization. Record data at any tested load point only under stabilized conditions, as defined in HI 40.6-2014-B section 40.6.5.5.1 (incorporated by reference, see § 431.463), where a minimum of two measurements are used to determine stabilization.
D. 3 Test Points. Measure the flow rate in gpm, pump total head in ft, the driver power input in W, and the speed of rotation in rpm at each load point specified in Table 1 of this appendix for each DPPP variety and speed configuration:
| DPPP varieties | Speed configuration(s) | Number of load points (n) |
Load point (i) |
Test points | ||
|---|---|---|---|---|---|---|
| Flow rate (Q) (GPM) |
Head (H) (ft) |
Speed (rpm) |
||||
| Self-Priming Pool Filter Pumps And Non-Self-Priming Pool Filter Pumps | Single-speed dedicated-purpose pool pumps and all self-priming and non-self-priming pool filter pumps not meeting the definition of two-*, multi-, or variable-speed dedicated-purpose pool pump | 1 | High | Qhigh (gpm) = Qmax__speed@C ** | H = 0.0082 × Qhigh 2 | Maximum speed. |
| Two-speed dedicated-purpose pool pumps * | 2 | Low | Qlow (gpm) = Flow rate associated with specified head and speed that is not below: • 31.1 gpm if rated hydraulic horsepower is >0.75 or • 24.7 gpm if rated hydraulic horsepower is ≤0.75 |
H = 0.0082 × Qlow 2 | Lowest speed capable of meeting the specified flow and head values, if any. *** | |
| High | Qhigh (gpm) = Qmax__speed@C ** | H = 0.0082 × Qlow 2 | Maximum speed. | |||
| Multi-speed and variable-speed dedicated-purpose pool pumps | 2 | Low | Qlow (gpm) = • If rated hydraulic horsepower is >0.75, then Qlow ≥31.1 gpm • If rated hydraulic horsepower is ≤0.75, then Qlow ≥24.7 gpm |
H = 0.0082 × Qlow 2 | Lowest speed capable of meeting the specified flow and head values. | |
| High | Qhigh (gpm) ≥0.8 × Qmax__speed@C ** | H = 0.0082 × Qhigh 2 | Lowest speed capable of meeting the specified flow and head values. | |||
| Waterfall Pumps | Single-speed dedicated-purpose pool pumps | 1 | High | Qlow (gpm) = Flow corresponding to specified head | 17.0 ft | Maximum speed. |
| Pressure Cleaner Booster Pumps | Any | 1 | High | 10.0 gpm | ≥60.0 ft | Lowest speed capable of meeting the specified flow and head values. |
| * In order to apply the test points for two-speed self-priming and non-self-priming pool filter pumps, self-priming pool filter pumps that are greater than or equal to 0.711 rated hydraulic horsepower that are two-speed dedicated-purpose pool pumps must also be distributed in commerce either: (1) With a pool pump control (variable speed drive and user interface or switch) that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times or (2) without a pool pump control that has such capability, but without which the pump is unable to operate. Two-speed self-priming pool filter pumps greater than or equal to 0.711 rated hydraulic horsepower that do not meet these requirements must be tested using the load point for single-speed self-priming or non-self-priming pool filter pumps, as appropriate. | ||||||
| ** Qmax__speed@C = Flow at max speed on curve C (gpm). | ||||||
| *** If a two-speed pump has a low speed that results in a flow rate below the specified values, the low speed of that pump shall not be tested. | ||||||
E. Calculations
E. 1 Determination of Weighted Energy Factor. Determine the WEF as a ratio of the measured flow and driver power input to the dedicated-purpose pool pump in accordance with the following equation:
Where:
WEF = Weighted Energy Factor in kgal/kWh;
Wi = weighting factor at each load point i, as specified in section E.2 of this appendix;
Qi = flow at each load point i, in gpm;
Pi = driver power input to the motor (or controls, if present) at each load point i, in watts;
i = load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix; and
n = number of load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix.
E. 2 Weights. When determining WEF, apply the weights specified in Table 2 of this appendix for the applicable load points, DPPP varieties, and speed configurations:
| DPPP varieties | Speed configuration(s) | Load point(s) i |
|
|---|---|---|---|
| Low flow | High flow | ||
| Self-Priming Pool Filter Pumps and Non-Self-Priming Pool Filter Pumps | Single-speed dedicated-purpose pool pumps and all self-priming and non-self-priming pool filter pumps not meeting the definition of two-*, multi-, or variable-speed dedicated-purpose pool pump | 1.0 | |
| Two-speed dedicated-purpose pool pumps * | 0.80 | 0.20 | |
| Multi-speed and variable-speed dedicated-purpose pool pumps | 0.80 | 0.20 | |
| Waterfall Pumps | Single-speed dedicated-purpose pool pumps | 1.0 | |
| Pressure Cleaner Booster Pump | Any | 1.0 | |
| * In order to apply the test points for two-speed self-priming and non-self-priming pool filter pumps, self-priming pool filter pumps that are greater than or equal to 0.711 rated hydraulic horsepower that are two-speed dedicated-purpose pool pumps must also be distributed in commerce either: (1) With a pool pump control (variable speed drive and user interface or switch) that changes the speed in response to pre-programmed user preferences and allows the user to select the duration of each speed and/or the on/off times or (2) without a pool pump control that has such capability, but without which the pump is unable to operate. Two-speed self-priming pool filter pumps greater than or equal to 0.711 rated hydraulic horsepower that do not meet these requirements must be tested using the load point for single-speed self-priming or non-self-priming pool filter pumps, as appropriate. | |||
E. 3 Determination of Horsepower and True Power Factor Metrics
E. 3.1 Determine the pump power output at any load point i using the following equation:
Where:
Pu,i = the measured pump power output at load point i of the tested pump, in hp;
Qi = the measured flow rate at load point i of the tested pump, in gpm;
Hi = pump total head at load point i of the tested pump, in ft; and
SG = the specific gravity of water at specified test conditions, which is equivalent to 1.00.
E. 3.1.1 Determine the rated hydraulic horsepower as the pump power output measured on the reference curve at maximum rotating speed and full impeller diameter for the rated pump.
E. 3.2 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, determine the dedicated-purpose pool pump nominal motor horsepower as the product of the measured full load speed and torque, adjusted to the appropriate units, as shown in the following equation:
Where:
Pnm = the dedicated-purpose pool pump nominal total horsepower at full load, in hp;
T = output torque at full load, in lb-ft; and
n = the motor speed at full load, in rpm.
Full-load speed and torque shall be determined based on the maximum continuous duty motor power output rating allowable for the motor's nameplate ambient rating and insulation class.
E. 3.2.1 For single-phase AC motors, determine the measured speed and torque at full load according to either section E.3.2.1.1 or E.3.2.1.2 of this appendix.
E. 3.2.1.1 Use the procedures in section 3.2, “Tests with load”; section 4 “Testing facilities”; section 5.2 “Mechanical measurements”; section 5.3 “Temperature measurements”; and section 6 “Tests” of IEEE 114-2010 (incorporated by reference, see § 431.463), or
E. 3.2.1.2 Use the applicable procedures in section 5, “General test requirements” and section 6, “Tests” of CSA C747-2009 (RA 2014); except in section 6.4(b) the conversion factor shall be 5252, only measurements at full load are required in section 6.5, and section 6.6 shall be disregarded (incorporated by reference, see § 431.463).
E. 3.2.2 For DC motors, determine the measured speed and torque at full load according to either section E.3.2.2.1 or E.3.2.2.2 of this appendix.
E. 3.2.2.1 Use the procedures in section 3.1, “Instrument Selection Factors”; section 3.4 “Power Measurement”: Section 3.5 “Power Sources”; section 4.1.2 “Ambient Air”; section 4.1.4 “Direction of Rotation”; section 5.4.1 “Reference Conditions”; and section 5.4.3.2 “Dynomometer or Torquemeter Method” of IEEE 113-1985 (incorporated by reference, see § 431.463), or
E. 3.2.2.2 Use the applicable procedures in section 5, “General test requirements” and section 6, “Tests” of CSA C747-2009 (RA 2014); except in section 6.4(b) the conversion factor shall be 5252, only measurements at full load are required in section 6.5, and section 6.6 shall be disregarded (incorporated by reference, see § 431.463).
E. 3.3 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, the dedicated-purpose pool pump service factor is equal to 1.0.
E. 3.4 Determine the dedicated-purpose pool pump motor total horsepower according to section E.3.4.1 of this appendix for dedicated-purpose pool pumps with single-phase AC motors or DC motors and section E.3.4.2 of this appendix for dedicated-purpose pool pumps with polyphase AC motors.
E. 3.4.1 For dedicated-purpose pool pumps with single-phase AC motors or DC motors, determine the dedicated-purpose pool pump motor total horsepower as the product of the dedicated-purpose pool pump nominal motor horsepower, determined in accordance with section E.3.2 of this appendix, and the dedicated-purpose pool pump service factor, determined in accordance with section E.3.3 of this appendix.
E. 3.4.2 For dedicated-purpose pool pumps with polyphase AC induction motors, determine the dedicated-purpose pool pump motor total horsepower as the product of the rated nominal motor horsepower and the rated service factor of the motor.
E. 3.5 Determine the true power factor at each applicable load point specified in Table 1 of this appendix for each DPPP variety and speed configuration as a ratio of driver power input to the motor (or controls, if present) (Pi), in watts, divided by the product of the voltage in volts and the current in amps at each load point i, as shown in the following equation:
Where:
PFi = true power factor at each load point i, dimensionless;
Pi = driver power input to the motor (or controls, if present) at each load point i, in watts;
Vi = voltage at each load point i, in volts;
Ii = current at each load point i, in amps; and
i = load point(s), defined uniquely for each DPPP variety and speed configuration as specified in section D.3 of this appendix.
E. 4 Determination of Maximum Head. Determine the maximum head for self-priming pool filter pumps, non-self-priming pool filter pumps, and waterfall pumps by measuring the head at maximum speed and the minimum flow rate at which the pump is designed to operate continuously or safely, where the minimum flow rate is assumed to be zero unless stated otherwise in the manufacturer literature.
F. Determination of Self-Priming Capability
F. 1 Test Method. Determine the vertical lift and true priming time of non-self-priming pool filter pumps and self-priming pool filter pumps that are not already certified as self-priming under NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) by testing such pumps pursuant to section C.3 of appendix C of NSF/ANSI 50-2015, except for the modifications and exceptions listed in the following sections F.1.1 through F.1.5 of this appendix:
F. 1.1 Where section C.3.2, “Apparatus,” and section C.3.4, “Self-priming capability test method,” of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463) state that the “suction line must be essentially as shown in annex C, figure C.1;” the phrase “essentially as shown in Annex C, figure C.1” means:
(1) The centerline of the pump impeller shaft is situated a vertical distance equivalent to the specified vertical lift (VL), calculated in accordance with section F.1.1.1. of this appendix, above the water level of a water tank of sufficient volume as to maintain a constant water surface level for the duration of the test;
(2) The pump draws water from the water tank with a riser pipe that extends below the water level a distance of at least 3 times the riser pipe diameter (i.e., 3 pipe diameters);
(3) The suction inlet of the pump is at least 5 pipe diameters from any obstructions, 90° bends, valves, or fittings; and
(4) The riser pipe is of the same pipe diameter as the pump suction inlet.
F. 1.1.1 The vertical lift (VL) must be normalized to 5.0 feet at an atmospheric pressure of 14.7 psia and a water density of 62.4 lb/ft3 in accordance with the following equation:
Where:
VL = vertical lift of the test apparatus from the waterline to the centerline of the pump impeller shaft, in ft;
ρtest = density of test fluid, in lb/ft3; and
Pabs,test = absolute barometric pressure of test apparatus location at centerline of pump impeller shaft, in psia.
F. 1.2 The equipment accuracy requirements specified in section B, “Measurement Equipment,” of this appendix also apply to this section F, as applicable.
F. 1.2.1 All measurements of head (gauge pressure), flow, and water temperature must be taken at the pump suction inlet and all head measurements must be normalized back to the centerline of the pump impeller shaft in accordance with section A.3.1.3.1 of HI 40.6-2014-B (incorporated by reference, see § 431.463).
F. 1.3 All tests must be conducted with clear water that meets the requirements adopted in section C.3 of this appendix.
F. 1.4 In section C.3.4, “Self-priming capability test method,” of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463), “the elapsed time to steady discharge gauge reading or full discharge flow” is determined when the changes in head and flow, respectively, are within the tolerance values specified in table 40.6.3.2.2, “Permissible amplitude of fluctuation as a percentage of mean value of quantity being measured at any test point,” of HI 40.6-2014-B (incorporated by reference, see § 431.463). The measured priming time (MPT) is determined as the point in time when the stabilized load point is first achieved, not when stabilization is determined. In addition, the true priming time (TPT) is equivalent to the MPT.
F. 1.5 The maximum true priming time for each test run must not exceed 10.0 minutes. Disregard section C.3.5 of NSF/ANSI 50-2015 (incorporated by reference, see § 431.463).
G. Optional Testing and Calculations
G. 1 Replacement Dedicated-Purpose Pool Pump Motors. To determine the WEF for replacement DPPP motors, test each replacement DPPP motor paired with each dedicated-purpose pool pump bare pump for which the replacement DPPP motor is advertised to be paired, as stated in the manufacturer's literature for that replacement DPPP motor model, according to the testing and calculations described in sections A, B, C, D, and E of this appendix. Alternatively, each replacement DPPP motor may be tested with the most consumptive dedicated-purpose pool pump bare pump for which it is advertised to be paired, as stated in the manufacturer's literature for that replacement DPPP motor model. If a replacement DPPP motor is not advertised to be paired with any specific dedicated-purpose pool pump bare pumps, test with the most consumptive dedicated-purpose pool pump bare pump available.
[82 FR 36924, Aug. 7, 2017]
Beginning March 20, 2023, any representations made with respect to the energy use or efficiency of circulator pumps subject to testing pursuant to 10 CFR 431.464(c) must be made in accordance with the results of testing pursuant to this appendix.
0. Incorporation by Reference
DOE incorporated by reference in § 431.463 the entire standard for HI 40.6-2021 and for HI 41.5-2022. However, not all provisions of HI 40.6-2021 and HI 41.5-2022 apply to this appendix. If there is any conflict between any industry standard and this appendix, follow the language of the test procedure in this appendix, disregarding the conflicting industry standard language.
0.1 Specifically, the following provisions of HI 40.6-2021 are not applicable:
(a) Section 40.6.4—Considerations when determining the efficiency of certain pumps, Section 40.6.4.1—Vertically suspended pumps
(b) Section 40.6.4—Considerations when determining the efficiency of certain pumps, Section 40.6.4.2—Submersible pumps
(c) Section 40.6.5—Test procedures, Section 40.6.5.3—Test report
(d) Section 40.6.5—Test procedures, Section 40.6.5.5—Test conditions, Section 40.6.5.5.2—Speed of rotation during test
(e) Section 40.6.6—Analysis, Section 40.6.6.1—Translation of the test results to the specified speed of rotation
(f) Section 40.6.6—Analysis, Section 40.6.6.1—Translation of the test results to the specified speed of rotation, Section 40.6.6.1.1—Translation of the test results into data based on specified speed of rotation
(g) Appendix B—Reporting of test results
(h) Appendix G—DOE compared to HI 40.6 nomenclature
0.2 Specifically, only the following provisions of HI 41.5-2022 are applicable:
(a) Section 41.5.3.4.1—Determination of CER—Full Speed
(b) Section 41.5.3.4.2—Determination of CER—Pressure Speed Control
(c) Section 41.5.3.4.3—Determination of CER—Temperature Speed Control
(d) Section 41.5.3.4.4.1—Determination of CER—External Input Signal Speed Control Only
(e) Section 41.5.3.4.4.2—Determination of CER—External Input Signal Speed Control Operated With Other Control Methods
(f) Section 41.5.3.4.5—Determination of CER—Manual Speed Control
1. General
To determine the circulator energy index (CEI), testing shall be performed in accordance with HI 40.6-2021, including Appendix E “Testing Circulator Pumps,” with the exceptions noted in section 0.1 of this appendix and the modifications and additions as noted throughout the following provisions. For the purposes of applying this appendix, the term “pump power output,” as defined in section 40.6.2, “Terms and definitions,” of HI 40.6-2021 shall be deemed to be synonymous with the term “hydraulic horsepower” used throughout that standard and this appendix.
2. Scope
2.1 This appendix is applicable to all circulator pumps and describes how to calculate the circulator energy index (CEI; section F) based on the pump energy rating for the minimally compliant reference circulator pump (CERSTD) and the circulator energy rating (CER) determined in accordance with one of the test methods listed in Table I of this appendix based on a control variety with which the circulator pump is distributed in commerce.
| Circulator pump configuration | Control method with which circulator pump is distributed | Test method to be used for testing and calculation of CER |
|---|---|---|
| Circulator Pump + Motor | Circulator pumps at full speed or circulator pumps without pressure, temperature, external input signal, or manual speed control | HI 41.5-2022 Section 41.5.3.4.1. |
| Circulator Pump + Motor + Controls | Circulator pumps with pressure control (including adaptive pressure control) | HI 41.5-2022 Section 41.5.3.4.2. |
| Circulator pumps with temperature control | HI 41.5-2022 Section 41.5.3.4.3. | |
| Circulator pumps with only external input signal control, and which cannot be operated without an external input signal | HI 41.5-2022 Section 41.5.3.4.4.1. | |
| Circulator pumps with external input signal control in addition to other control varieties, or which can be operated without an external input signal | HI 41.5-2022 Section 41.5.3.4.4.2. | |
| Circulator pumps with manual speed control | HI 41.5-2022 Section 41.5.3.4.5. |
2.2 If a given circulator pump model is distributed in commerce with multiple control varieties available, the manufacturer may select a control variety (or varieties) among those available with which to test the circulator pump, including the test method for circulator pumps at full speed or circulator pumps without external input signal, manual, pressure, or temperature controls).
3. Measurement Equipment
For the purposes of measuring flow rate, head, driver power input, and pump power output, the equipment specified in HI 40.6-2021 Appendix C must be used and must comply with the stated accuracy requirements in HI 40.6-2021 Table 40.6.3.2.3. When more than one instrument is used to measure a given parameter, the combined accuracy, calculated as the root sum of squares of individual instrument accuracies, must meet the specified accuracy requirements.
4. Test Conditions
4.1 Pump specifications. Conduct testing in accordance with the test conditions, stabilization requirements, and specifications of HI 40.6-2021 section 40.6.3, “Pump efficiency testing”; section 40.6.4, “Considerations when determining the efficiency of a pump,” including section 40.6.4.4, “Determination of pump overall efficiency”; section 40.6.5.4 (including Appendix A), “Test arrangements”; and section 40.6.5.5, “Test conditions.”
4.2 Twin head circulator pump. To test twin head circulator pumps, one of the two impeller assemblies should be incorporated into an adequate, single impeller volute and casing. An adequate, single impeller volute and casing means a volute and casing for which any physical and functional characteristics that affect energy consumption and energy efficiency are essentially identical to their corresponding characteristics for a single impeller in the twin head circulator pump volute and casing.
4.3 Circulator-less-volute. To determine the CEI for a circulator-less-volute, test each circulator-less-volute with each volute for which the circulator-less-volute is offered for sale or advertised to be paired for that circulator pump model according to the testing and calculations described in the applicable test method listed in Table 1 of this appendix, depending on the variety of control with which the circulator pump model is distributed in commerce. Alternatively, each circulator-less-volute may be tested with the most consumptive volute with which is it offered for sale or advertised to be paired for that circulator pump model.
5. Data Collection and Analysis
5.1 Stabilization. Record data at any test point only under stabilized conditions, as defined in HI 40.6-2021 section 40.6.5.5.1.
5.2 Testing BEP at maximum speed for the circulator pump. Determine the BEP of the circulator pump at maximum speed as specified in Appendix E of HI 40.6-2021 including sections 40.6.5.5.1 and 40.6.6 as modified. Determine the BEP flow rate at maximum speed as the flow rate at the operating point of maximum overall efficiency on the circulator pump curve, as determined in accordance with section 40.6.6.3 of HI 40.6-2021 as modified by Appendix E, where overall efficiency is the ratio of the circulator pump power output divided by the driver power input, as specified in Table 40.6.2.1 of HI 40.6-2021. For the purposes of this test procedure, all references to “driver power input” in this appendix or HI 40.6-2021 shall refer to the input power to the controls, or to the motor if no controls are present.
5.3 Rounding. All terms and quantities refer to values determined in accordance with the procedures set forth in this appendix for the rated circulator pump. Perform all calculations using raw measured values without rounding. Round CER to three significant figures. Round CEI to the hundredths decimal place. Round rated hydraulic horsepower to the less precise of the following two values: three significant figures; the fourth decimal place when expressed in units of horsepower.
6. Calculation of CEI
Determine CEI using the following equation:
Where:
CEI = the circulator energy index (dimensionless);
CER = the circulator energy rating determined in accordance with Table 1 of this appendix (hp); and
CERSTD = the CER for a circulator pump that is minimally compliant with DOE's energy conservation standards with the same hydraulic horsepower as the tested pump, as determined in accordance with the specifications at paragraph (i) of § 431.465.
7. Determination of Additional Circulator Performance Parameters
7.1 To determine flow and head at BEP; pump power output (hydraulic horsepower) and driver power input at load points used in the calculation of CEI, including the rated hydraulic horsepower; and any other reported performance parameters, conduct testing according to section 1 of this appendix.
7.2 Determine the rated hydraulic horsepower as the pump power output measured at BEP and full impeller diameter for the rated pump.
7.3 Determine the true power factor at each applicable load point specified in the applicable test method listed in Table 1 of this appendix for each circulator pump control variety as a ratio of driver power input to the motor (or controls, if present) (Pi), in watts, divided by the product of the true RMS voltage in volts and the true RMS current in amps at each load point i, as shown in the following equation:
Where:
PFi = true power factor at each load point i, dimensionless;
Pi = driver power input to the motor (or controls, if present) at each load point i, in watts;
Vi = true RMS voltage at each load point i, in volts;
Ii = true RMS current at each load point i, in amps; and
i = load point(s), defined uniquely for each circulator pump control variety as specified in the applicable test method listed in Table 1 of this appendix.
[87 FR 57299, Sept. 19, 2022]
86 FR 40774, July 29, 2021, unless otherwise noted.
(a) Purpose. This subpart contains definitions and test procedures requirements for electric motors that are dedicated-purpose pool pump motors, pursuant to Part A-1 of Title III of the Energy Policy and Conservation Act, as amended, 42 U.S.C. 6311-6317. It also identifies materials incorporated by reference in this part. This subpart does not cover other “electric motors,” which are addressed in subpart B of this part, nor does it cover “small electric motors,” which are addressed in subpart X of this part.
(b) Scope. The requirements of this subpart apply to dedicated-purpose pool pump motors, as specified in paragraphs 1.2, 1.3 and 1.4 of UL 1004-10:2022 (incorporated by reference, see § 431.482).
(c) Incorporation by reference. In § 431.482, DOE incorporates by reference entire standards for use in this subpart; however, only the provisions of the document enumerated in an approved section are applicable within § 431.482.
[86 FR 40774, July 29, 2021, as amended at 88 FR 67041, Sept. 28, 2023]
(a) Certain material is incorporated by reference into this subpart with the approval of the Director of the Federal Register in accordance with 5 U.S.C. 552(a) and 1 CFR part 51. To enforce any edition other than that specified in this section, the Department of Energy (DOE) must publish a document in the Federal Register and the material must be available to the public. All approved incorporation by reference (IBR) material is available for inspection at DOE, and at the National Archives and Records Administration (NARA). Contact DOE at: the U.S. Department of Energy, Office of Energy Efficiency and Renewable Energy, Building Technologies Program, 1000 Independence Ave SW, EE-5B, Washington, DC 20585, (202) 586-9127, Buildings@ee.doe.gov, https://www.energy.gov/eere/buildings/building-technologies-office. For information on the availability of this material at NARA, visit www.archives.gov/federal-register/cfr/ibr-locations.html or email fr.inspection@nara.gov. The material may be obtained from the sources in the following paragraphs of this section.
(b) CSA. Canadian Standards Association, Sales Department, 5060 Spectrum Way, Suite 100, Mississauga, Ontario, L4W 5N6, Canada, 1-800-463-6727, or https://www.csagroup.org/store.
(1) CSA C747-09 (Reaffirmed 2014) (“CSA C747-09”), “Energy efficiency test method for small motors” as revised through August 2016, including Update No. 1; IBR approved for § 431.484.
(2) [Reserved]
(c) UL. Underwriters Laboratories, 333 Pfingsten Road, Northbrook, IL 60062, (841) 272-8800, or go to https://www.ul.com.
(1) UL 1004-10 (“UL 1004-10:2022”), Standard for Safety for Pool Pump Motors, Revised First Edition, Dated March 24, 2022; IBR approved for §§ 431.481 and 431.483.
(2) [Reserved]
[86 FR 40774, July 29, 2021, as amended at 88 FR 67041, Sept. 28, 2023; 88 FR 71990, Oct. 19, 2023]
The definitions applicable to this subpart are defined in section 2 “Glossary” of UL 1004-10:2022 (incorporated by reference, see § 431.482). In addition, the following definition applies:
Basic model means all units of dedicated purpose pool pump motors manufactured by a single manufacturer, that are within the same equipment class, have electrical characteristics that are essentially identical, and do not have any differing physical or functional characteristics that affect energy consumption or efficiency.
[88 FR 67041, Sept. 28, 2023]
(a) Scope. Pursuant to section 343(a) of EPCA, this section provides the test procedures for measuring the efficiency of dedicated-purpose pool pump motors. (42 U.S.C. 6314) For purposes of this part and EPCA, the test procedures for measuring the efficiency of dedicated-purpose pool pump motors shall be the test procedure specified in paragraph (b) of this section.
(b) Testing and calculations. At such time as compliance is required with a labeling requirement or an energy conservation standard, the full-load efficiency of each dedicated-purpose pool pump motor model (inclusive of the drive, if the dedicated-purpose pool pump motor model is placed into commerce with a drive, or is unable to operate without the presence of a drive) is determined in accordance with CSA C747-09, Section 1.6 “Scope”, Section 3 “Definitions”, Section 4 “General requirements”, Section 5, “General test requirements”, and Section 6 “Test method” (incorporated by reference, see § 431.482).
(a) For the purpose of paragraphs (b), (c) and (d) of this section, “THP” means dedicated-purpose-pool pump motor total horsepower.
(b) Each dedicated-purpose pool pump motor manufactured starting on September 29, 2025, with a THP less than 0.5 THP, must have a full-load efficiency that is not less than 69 percent.
(c) Each dedicated-purpose pool pump motor manufactured starting on the dates provided in table 1 to this paragraph (c) with a THP greater than or equal to 0.5 THP must be a variable speed control dedicated-purpose pool pump motor, and must follow the requirements in paragraph (d) of this section.
| Equipment class | Compliance date |
|---|---|
| Small-size (0.5 ≤ THP <1.15) | September 28, 2027. |
| Standard-size (1.15 ≤ THP ≤ 5) | September 29, 2025. |
(d) All dedicated-purpose pool pump motors with a THP greater than or equal to 0.5 THP and distributed in commerce with freeze protection controls, must be shipped with freeze protection disabled or with the following user-adjustable settings:
(1) The default dry-bulb air temperature setting is no greater than 40 °F;
(2) The default run time setting shall be no greater than 1 hour (before the temperature is rechecked); and
(3) The default motor speed (in revolutions per minute, or rpm) in freeze protection mode shall not be more than half of the maximum operating speed.
[88 FR 67041, Sept. 28, 2023]