10 CFR Part 430, Subpart B, Appendix A to Subpart B of Part 430 - Uniform Test Method for Measuring the Energy Consumption of Electric Refrigerators and Electric Refrigerator-Freezers

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Appendix A to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Electric Refrigerators and Electric Refrigerator-Freezers
Beginning on September 15, 2014, the test procedures in appendix A must be used to determine compliance with energy conservation standards for refrigerators and refrigerator-freezers. Prior to September 15, 2014, manufacturers may continue to use appendix A1 or may elect to use appendix A early to show compliance with the September 15, 2014 energy conservation standards. Manufacturers must use a single appendix for all representations of energy use of a basic model, including certifications of compliance, and may not use appendix A1 for certain representations and appendix A for other representations.
1. Definitions
Section 3, Definitions, of HRF-1-2008 (incorporated by reference; see § 430.3) applies to this test procedure.
1.1 “Adjusted total volume” means the sum of:
(i) The fresh food compartment volume as defined in HRF-1-2008 (incorporated by reference; see § 430.3) in cubic feet, and
(ii) The product of an adjustment factor and the net freezer compartment volume as defined in HRF-1-2008 in cubic feet.
1.2 “All-refrigerator” means an electric refrigerator that does not include a compartment for the freezing and long time storage of food at temperatures below 32 °F (0.0 °C). It may include a compartment of 0.50 cubic-foot capacity (14.2 liters) or less for the freezing and storage of ice.
1.3 “Anti-sweat heater” means a device incorporated into the design of a refrigerator or refrigerator-freezer to prevent the accumulation of moisture on the exterior or interior surfaces of the cabinet.
1.4 “Anti-sweat heater switch” means a user-controllable switch or user interface which modifies the activation or control of anti-sweat heaters.
1.5“AS/NZS 4474.1:2007” means Australian/New Zealand Standard 4474.1:2007, Performance of household electrical appliances—Refrigerating appliances, Part 1: Energy consumption and performance. Only sections of AS/NZS 4474.1:2007 (incorporated by reference; see § 430.3) specifically referenced in this test procedure are part of this test procedure. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over AS/NZS 4474.1:2007.
1.6 “Automatic defrost” means a system in which the defrost cycle is automatically initiated and terminated, with resumption of normal refrigeration at the conclusion of the defrost operation. The system automatically prevents the permanent formation of frost on all refrigerated surfaces. Nominal refrigerated food temperatures are maintained during the operation of the automatic defrost system.
1.7 “Automatic icemaker” means a device, that can be supplied with water without user intervention, either from a pressurized water supply system or by transfer from a water reservoir located inside the cabinet, that automatically produces, harvests, and stores ice in a storage bin, with means to automatically interrupt the harvesting operation when the ice storage bin is filled to a pre-determined level.
1.8“Complete temperature cycle” means a time period defined based upon the cycling of compartment temperature that starts when the compartment temperature is at a maximum and ends when the compartment temperature returns to an equivalent maximum (within 0.5 °F of the starting temperature), having in the interim fallen to a minimum and subsequently risen again to reach the second maximum. Alternatively, a complete temperature cycle can be defined to start when the compartment temperature is at a minimum and end when the compartment temperature returns to an equivalent minimum (within 0.5 °F of the starting temperature), having in the interim risen to a maximum and subsequently fallen again to reach the second minimum.
1.9 “Cycle” means the period of 24 hours for which the energy use of an electric refrigerator or electric refrigerator-freezer is calculated as though the consumer activated compartment temperature controls were set to maintain the standardized temperatures (see section 3.2).
1.10 “Cycle type” means the set of test conditions having the calculated effect of operating an electric refrigerator or electric refrigerator-freezer for a period of 24 hours, with the consumer activated controls other than those that control compartment temperatures set to establish various operating characteristics.
1.11“Defrost cycle type” means a distinct sequence of control whose function is to remove frost and/or ice from a refrigerated surface. There may be variations in the defrost control sequence such as the number of defrost heaters energized. Each such variation establishes a separate distinct defrost cycle type. However, defrost achieved regularly during the compressor off-cycles by warming of the evaporator without active heat addition, although a form of automatic defrost, does not constitute a unique defrost cycle type for the purposes of identifying the test period in accordance with section 4 of this appendix.
1.12 “Externally vented refrigerator or refrigerator-freezer” means an electric refrigerator or electric refrigerator-freezer that has an enclosed condenser or an enclosed condenser/compressor compartment and a set of air ducts for transferring the exterior air from outside the building envelope into, through, and out of the refrigerator or refrigerator-freezer cabinet; is capable of mixing exterior air with the room air before discharging into, through, and out of the condenser or condenser/compressor compartment; may include thermostatically controlled dampers or controls that mix the exterior and room air at low outdoor temperatures and exclude exterior air when the outdoor air temperature is above 80 °F (26.7 °C) or the room air temperature; and may have a thermostatically actuated exterior air fan.
1.13 “HRF-1-2008” means AHAM Standard 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. Only sections of HRF-1-2008 (incorporated by reference; see § 430.3) specifically referenced in this test procedure are part of this test procedure. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over HRF-1-2008.
1.14“Ice storage bin” means a container in which ice can be stored.
1.15 “Long-time automatic defrost” means an automatic defrost system whose successive defrost cycles are separated by 14 hours or more of compressor operating time.
1.16“Multiple-compressor” refrigerator or refrigerator-freezer means a refrigerator or refrigerator-freezer with more than one compressor.
1.17“Precooling” means operating a refrigeration system before initiation of a defrost cycle to reduce one or more compartment temperatures significantly (more than 0.5 °F) below its minimum during stable operation between defrosts.
1.18“Recovery” means operating a refrigeration system after the conclusion of a defrost cycle to reduce the temperature of one or more compartments to the temperature range that the compartment(s) exhibited during stable operation between defrosts.
1.19 “Separate auxiliary compartment” means a freezer compartment or a fresh food compartment of a refrigerator or refrigerator-freezer having more than two compartments that is not the first freezer compartment or the first fresh food compartment. Access to a separate auxiliary compartment is through a separate exterior door or doors rather than through the door or doors of another compartment. Separate auxiliary compartments may be convertible (e.g., from fresh food to freezer). Separate auxiliary freezer compartments may not be larger than the first freezer compartment and separate auxiliary fresh food compartments may not be larger than the first fresh food compartment, but such size restrictions do not apply to separate auxiliary convertible compartments.
1.20 “Special compartment” means any compartment other than a butter conditioner, without doors directly accessible from the exterior, and with separate temperature control (such as crispers convertible to meat keepers) that is not convertible from fresh food temperature range to freezer temperature range.
1.21 “Stabilization period” means the total period of time during which steady-state conditions are being attained or evaluated.
1.22“Stable operation” means operation after steady-state conditions have been achieved but excluding any events associated with defrost cycles. During stable operation the average rate of change of compartment temperature must not exceed 0.042 °F (0.023 °C) per hour for all compartment temperatures. Such a calculation performed for compartment temperatures at any two times, or for any two periods of time comprising complete cycles, during stable operation must meet this requirement.
(A) If compartment temperatures do not cycle, the relevant calculation shall be the difference between the temperatures at two points in time divided by the difference, in hours, between those points in time.
(B) If compartment temperatures cycle as a result of compressor cycling or other cycling operation of any system component (e.g., a damper, fan, or heater), the relevant calculation shall be the difference between compartment temperature averages evaluated for whole compressor cycles or complete temperature cycles divided by the difference, in hours, between either the starts, ends, or mid-times of the two cycles.
1.23 “Standard cycle” means the cycle type in which the anti-sweat heater control, when provided, is set in the highest energy-consuming position.
1.24“Through-the-door ice/water dispenser” means a device incorporated within the cabinet, but outside the boundary of the refrigerated space, that delivers to the user on demand ice and may also deliver water from within the refrigerated space without opening an exterior door. This definition includes dispensers that are capable of dispensing ice and water or ice only.
1.25 “Variable anti-sweat heater control” means an anti-sweat heater control that varies the average power input of the anti-sweat heater(s) based on operating condition variable(s) and/or ambient condition variable(s).
1.26 “Variable defrost control” means an automatic defrost system in which successive defrost cycles are determined by an operating condition variable or variables other than solely compressor operating time. This includes any electrical or mechanical device performing this function. A control scheme that changes the defrost interval from a fixed length to an extended length (without any intermediate steps) is not considered a variable defrost control. A variable defrost control feature should predict the accumulation of frost on the evaporator and react accordingly. Therefore, the times between defrost should vary with different usage patterns and include a continuum of lengths of time between defrosts as inputs vary.
2. Test Conditions
2.1Ambient Temperature Measurement. Temperature measuring devices shall be shielded so that indicated temperatures are not affected by the operation of the condensing unit or adjacent units.
2.1.1Ambient Temperature. The ambient temperature shall be recorded at points located 3 feet (91.5 cm) above the floor and 10 inches (25.4 cm) from the center of the two sides of the unit under test. The ambient temperature shall be 90.0 ± 1.0 °F (32.2 ± 0.6 °C) during the stabilization period and the test period.
2.1.2Ambient Temperature Gradient. The test room vertical ambient temperature gradient in any foot of vertical distance from 2 inches (5.1 cm) above the floor or supporting platform to a height of 1 foot (30.5 cm) above the top of the unit under test is not to exceed 0.5 °F per foot (0.9 °C per meter). The vertical ambient temperature gradient at locations 10 inches (25.4 cm) out from the centers of the two sides of the unit being tested is to be maintained during the test. To demonstrate that this requirement has been met, test data must include measurements taken using temperature sensors at locations 10 inches (25.4 cm) from the center of the two sides of the unit under test at heights of 2 inches (5.1 cm) and 36 inches (91.4 cm) above the floor or supporting platform and at a height of 1 foot (30.5 cm) above the unit under test.
2.1.3Platform. A platform must be used if the floor temperature is not within 3 °F (1.7 °C) of the measured ambient temperature. If a platform is used, it is to have a solid top with all sides open for air circulation underneath, and its top shall extend at least 1 foot (30.5 cm) beyond each side and front of the unit under test and extend to the wall in the rear.
2.2Operational Conditions. The unit under test shall be installed and its operating conditions maintained in accordance with HRF-1-2008 (incorporated by reference; see § 430.3), sections 5.3.2 through section 5.5.5.5 (excluding section 5.5.5.4). Exceptions and clarifications to the cited sections of HRF-1-2008 are noted in sections 2.3 through 2.8, and 5.1 of this appendix.
2.3 Anti-Sweat Heaters. The anti-sweat heater switch is to be on during one test and off during a second test. In the case of an electric refrigerator-freezer equipped with variable anti-sweat heater control, the standard cycle energy use shall be the result of the calculation described in 6.2.3.
2.4 Conditions for Automatic Defrost Refrigerator-Freezers. For automatic defrost refrigerator-freezers, the freezer compartments shall not be loaded with any frozen food packages during testing. Cylindrical metallic masses of dimensions 1.12 ±0.25 inches (2.9 ±0.6 cm) in diameter and height shall be attached in good thermal contact with each temperature sensor within the refrigerated compartments. All temperature measuring sensor masses shall be supported by low-thermal-conductivity supports in such a manner to ensure that there will be at least 1 inch (2.5 cm) of air space separating the thermal mass from contact with any interior surface or hardware inside the cabinet. In case of interference with hardware at the sensor locations specified in section 5.1, the sensors shall be placed at the nearest adjacent location such that there will be a 1-inch air space separating the sensor mass from the hardware.
2.5 Conditions for All-Refrigerators. There shall be no load in the freezer compartment during the test.
2.6 The cabinet and its refrigerating mechanism shall be assembled and set up in accordance with the printed consumer instructions supplied with the cabinet. Set-up of the refrigerator or refrigerator-freezer shall not deviate from these instructions, unless explicitly required or allowed by this test procedure. Specific required or allowed deviations from such set-up include the following:
(a) Connection of water lines and installation of water filters are not required;
(b) Clearance requirements from surfaces of the product shall be as described in section 2.8 of this appendix;
(c) The electric power supply shall be as described in HRF-1-2008 (incorporated by reference; see § 430.3), section 5.5.1;
(d) Temperature control settings for testing shall be as described in section 3 below. Settings for convertible compartments and other temperature-controllable or special compartments shall be as described in section 2.7 of this appendix;
(e) The product does not need to be anchored or otherwise secured to prevent tipping during energy testing;
(f) All the product's chutes and throats required for the delivery of ice shall be free of packing, covers, or other blockages that may be fitted for shipping or when the icemaker is not in use; and
(g) Ice storage bins shall be emptied of ice.
For cases in which set-up is not clearly defined by this test procedure, manufacturers must submit a petition for a waiver (see section 7).
2.7 Compartments that are convertible (e.g., from fresh food to freezer) shall be operated in the highest energy use position. For the special case of convertible separate auxiliary compartments, this means that the compartment shall be treated as a freezer compartment or a fresh food compartment, depending on which of these represents higher energy use. Special compartments shall be tested with controls set to provide the coldest temperature. However, for special compartments in which temperature control is achieved using the addition of heat (including resistive electric heating, refrigeration system waste heat, or heat from any other source, but excluding the transfer of air from another part of the interior of the product) for any part of the controllable temperature range of that compartment, the product energy use shall be determined by averaging two sets of tests. The first set of tests shall be conducted with such special compartments at their coldest settings, and the second set of tests shall be conducted with such special compartments at their warmest settings. The requirements for the warmest or coldest temperature settings of this section do not apply to features or functions associated with temperature control (such as fast chill compartments) that are initiated manually and terminated automatically within 168 hours.
2.8Rear Clearance.
(a) General. The space between the lowest edge of the rear plane of the cabinet and a vertical surface (the test room wall or simulated wall) shall be the minimum distance in accordance with the manufacturer's instructions, unless other provisions of this section apply. The rear plane shall be considered to be the largest flat surface at the rear of the cabinet, excluding features that protrude beyond this surface, such as brackets or compressors.
(b) Maximum clearance. The clearance shall not be greater than 2 inches (51 mm) from the lowest edge of the rear plane to the vertical surface, unless the provisions of paragraph (c) of this section apply.
(c) If permanent rear spacers or other components that protrude beyond the rear plane extend further than the 2 inch (51 mm) distance, or if the highest edge of the rear plane is in contact with the vertical surface when the unit is positioned with the lowest edge of the rear plane at or further than the 2 inch (51 mm) distance from the vertical surface, the appliance shall be located with the spacers or other components protruding beyond the rear plane, or the highest edge of the rear plane, in contact with the vertical surface.
(d) Rear-mounted condensers. If the product has a flat rear-wall-mounted condenser (i.e., a rear-wall-mounted condenser with all refrigerant tube centerlines within 0.25 inches (6.4 mm) of the condenser plane), and the area of the condenser plane represents at least 25% of the total area of the rear wall of the cabinet, then the spacing to the vertical surface may be measured from the lowest edge of the condenser plane.
2.9 Steady-State Condition. Steady-state conditions exist if the temperature measurements in all measured compartments taken at 4-minute intervals or less during a stabilization period are not changing at a rate greater than 0.042 °F (0.023 °C) per hour as determined by the applicable condition of A or B, described below.
A. The average of the measurements during a 2-hour period if no cycling occurs or during a number of complete repetitive compressor cycles occurring through a period of no less than 2 hours is compared to the average over an equivalent time period with 3 hours elapsing between the two measurement periods.
B. If A above cannot be used, the average of the measurements during a number of complete repetitive compressor cycles occurring through a period of no less than 2 hours and including the last complete cycle before a defrost period (or if no cycling occurs, the average of the measurements during the last 2 hours before a defrost period) are compared to the same averaging period before the following defrost period.
2.10 Exterior Air for Externally Vented Refrigerator or Refrigerator-Freezer. An exterior air source shall be provided with adjustable temperature and pressure capabilities. The exterior air temperature shall be adjustable from 30 ±1 °F (1.7 ±0.6 °C) to 90 ±1 °F (32.2 ±0.6 °C).
2.10.1 Air Duct. The exterior air shall pass from the exterior air source to the test unit through an insulated air duct.
2.10.2 Air Temperature Measurement. The air temperature entering the condenser or condenser/compressor compartment shall be maintained to ±3 °F (1.7 °C) during the stabilization and test periods and shall be measured at the inlet point of the condenser or condenser/compressor compartment (“condenser inlet”). Temperature measurements shall be taken from at least three temperature sensors or one sensor per 4 square inches (25.8 square cm) of the air duct cross-sectional area, whichever is greater, and shall be averaged. For a unit that has a condenser air fan, a minimum of three temperature sensors at the condenser fan discharge shall be required. Temperature sensors shall be arranged to be at the centers of equally divided cross-sectional areas. The exterior air temperature, at its source, shall be measured and maintained to ±1 °F (0.6 °C) during the test period. The temperature measuring devices shall have an error no greater than ±0.5 °F (±0.3 °C). Measurements of the air temperature during the test period shall be taken at regular intervals not to exceed 4 minutes.
2.10.3 Exterior Air Static Pressure. The exterior air static pressure at the inlet point of the unit shall be adjusted to maintain a negative pressure of 0.20″ ±0.05″ water column (62 Pascals ±12.5 Pascals) for all air flow rates supplied to the unit. The pressure sensor shall be located on a straight duct with a distance of at least 7.5 times the diameter of the duct upstream and a distance of at least 3 times the diameter of the duct downstream. There shall be four static pressure taps at 90° angles apart. The four pressures shall be averaged by interconnecting the four pressure taps. The air pressure measuring instrument shall have an error no greater than 0.01” water column (2.5 Pascals).
2.11Refrigerators and Refrigerator-Freezers with Demand-Response Capability. Refrigerators and refrigerator-freezers that have a communication module for demand-response functions that is located within the cabinet shall be tested with the communication module in the configuration set at the factory just before shipping.
3. Test Control Settings
3.1 Model with no User Operable Temperature Control. A test shall be performed to measure the compartment temperatures and energy use. A second test shall be performed with the temperature control electrically short circuited to cause the compressor to run continuously.
3.2 Models with User Operable Temperature Control. Testing shall be performed in accordance with one of the following sections using the following standardized temperatures:
All-Refrigerator: 39 °F (3.9 °C) fresh food compartment temperature;
Refrigerator: 15 °F (−9.4 °C) freezer compartment temperature, 39 °F (3.9 °C) fresh food compartment temperature;
Refrigerator-Freezer: 0 °F (−17.8 °C) freezer compartment temperature, 39 °F (3.9 °C) fresh food compartment temperature.
For the purposes of comparing compartment temperatures with standardized temperatures, as described in sections 3.2.1 and 3.2.2, the freezer compartment temperature shall be as specified in section 5.1.4, and the fresh food compartment temperature shall be as specified in section 5.1.3.
3.2.1A first test shall be performed with all compartment temperature controls set at their median position midway between their warmest and coldest settings. For mechanical control systems, (a) knob detents shall be mechanically defeated if necessary to attain a median setting, and (b) the warmest and coldest settings shall correspond to the positions in which the indicator is aligned with control symbols indicating the warmest and coldest settings. For electronic control systems, the test shall be performed with all compartment temperature controls set at the average of the coldest and warmest settings; if there is no setting equal to this average, the setting closest to the average shall be used. If there are two such settings equally close to the average, the higher of these temperature control settings shall be used. A second test shall be performed with all controls set at their warmest setting or all controls set at their coldest setting (not electrically or mechanically bypassed). For all-refrigerators, this setting shall be the appropriate setting that attempts to achieve compartment temperatures measured during the two tests that bound (i.e., one is above and one is below) the standardized temperature for all-refrigerators. For refrigerators and refrigerator-freezers, the second test shall be conducted with all controls at their coldest setting, unless all compartment temperatures measured during the first part of the test are lower than the standardized temperatures, in which case the second test shall be conducted with all controls at their warmest setting. Refer to Table 1 of this appendix for all-refrigerators or Table 2 of this appendix for refrigerators with freezer compartments and refrigerator-freezers to determine which test results to use in the energy consumption calculation. If any compartment is warmer than its standardized temperature for a test with all controls at their coldest position, the tested unit fails the test and cannot be rated.
Table 1—Temperature Settings for All-Refrigerators
First test Second test Energy calculation based on:
Settings Results Settings Results
Mid Low Warm Low Second Test Only.
High First and Second Tests.
High Cold Low First and Second Tests.
High No Energy Use Rating.
Table 2—Temperature Settings for Refrigerators With Freezer Compartments and Refrigerator-Freezers
First test Second test Energy calculation based on:
Settings Results Settings Results
Notes: Fzr = Freezer Compartment, FF = Fresh Food Compartment.
Fzr Mid Fzr Low Fzr Warm Fzr Low Second Test Only.
FF Mid FF Low FF Warm FF Low.
Fzr Low First and Second Tests.
FF High.
Fzr High First and Second Tests.
FF Low.
Fzr High First and Second Tests.
FF High.
Fzr Low Fzr Cold Fzr Low No Energy Use Rating.
FF High FF Cold FF High.
Fzr Low First and Second Tests.
FF Low.
Fzr High Fzr Cold Fzr High No Energy Use Rating.
FF Low FF Cold FF Low.
Fzr Low First and Second Tests.
FF Low.
Fzr High Fzr Cold Fzr Low First and Second Tests.
FF High FF Cold FF Low.
Fzr Low No Energy Use Rating.
FF High.
Fzr High No Energy Use Rating.
FF Low.
Fzr High No Energy Use Rating.
FF High.
3.2.2 Alternatively, a first test may be performed with all temperature controls set at their warmest setting. If all compartment temperatures are below the appropriate standardized temperatures, then the result of this test alone will be used to determine energy consumption. If this condition is not met, then the unit shall be tested in accordance with 3.2.1.
3.2.3 Temperature Settings for Separate Auxiliary Convertible Compartments. For separate auxiliary convertible compartments tested as freezer compartments, the median setting shall be within 2 °F (1.1 °C) of the standardized temperature, and the warmest setting shall be above 5 °F (−15 °C). For separate auxiliary convertible compartments tested as fresh food compartments, the median setting shall be within 2 °F (1.1 °C) of the standardized temperature, and the coldest setting shall be below 34 °F (1.1 °C). For compartments where control settings are not expressed as particular temperatures, the measured temperature of the convertible compartment rather than the settings shall meet the specified criteria.
3.3Optional Test for Models with Two Compartments and User Operable Controls. As an alternative to section 3.2, perform three tests such that the set of tests meets the “minimum requirements for interpolation” of AS/NZS 4474.1:2007 (incorporated by reference; see § 430.3) appendix M, section M3, paragraphs (a) through (c) and as illustrated in Figure M1. The target temperatures txA and txB defined in section M4(a)(i) of AS/NZ 4474.1:2007 shall be the standardized temperatures defined in section 3.2 of this appendix.
4. Test Period
Tests shall be performed by establishing the conditions set forth in section 2, and using the control settings set forth in section 3.
4.1Non-automatic Defrost. If the model being tested has no automatic defrost system, the test period shall start after steady-state conditions (see section 2.9 of this appendix) have been achieved and be no less than three hours in duration. During the test period, the compressor motor shall complete two or more whole compressor cycles. (A compressor cycle is a complete “on” and a complete “off” period of the motor.) If no “off” cycling occurs, the test period shall be three hours. If fewer than two compressor cycles occur during a 24-hour period, then a single complete compressor cycle may be used.
4.2Automatic Defrost. If the model being tested has an automatic defrost system, the test period shall start after steady-state conditions have been achieved and be from one point during a defrost period to the same point during the next defrost period. If the model being tested has a long-time automatic defrost system, the alternative provisions of section 4.2.1 may be used. If the model being tested has a variable defrost control, the provisions of section 4.2.2 shall apply. If the model is a multiple-compressor product with automatic defrost, the provisions of section 4.2.3 shall apply. If the model being tested has long-time automatic or variable defrost control involving multiple defrost cycle types, such as for a product with a single compressor and two or more evaporators in which the evaporators are defrosted at different frequencies, the provisions of section 4.2.4 shall apply. If the model being tested has multiple defrost cycle types for which compressor run time between defrosts is a fixed time of less than 14 hours for all such cycle types, and for which the compressor run times between defrosts for different defrost cycle types are equal to or multiples of each other, the test period shall be from one point of the defrost cycle type with the longest compressor run time between defrosts to the same point during the next occurrence of this defrost cycle type. For such products not using the procedures of section 4.2.4, energy consumption shall be calculated as described in section 5.2.1.1 of this appendix.
4.2.1 Long-time Automatic Defrost. If the model being tested has a long-time automatic defrost system, the two-part test described in this section may be used. The first part is a stable period of compressor operation that includes no portions of the defrost cycle, such as precooling or recovery, that is otherwise the same as the test for a unit having no defrost provisions (section 4.1). The second part is designed to capture the energy consumed during all of the events occurring with the defrost control sequence that are outside of stable operation.
4.2.1.1Cycling Compressor System. For a system with a cycling compressor, the second part of the test starts at the termination of the last regular compressor “on” cycle. The average temperatures of the fresh food and freezer compartments measured from the termination of the previous compressor “on” cycle to the termination of the last regular compressor “on” cycle must both be within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test. If any compressor cycles occur prior to the defrost heater being energized that cause the average temperature in either compartment to deviate from its average temperature for the first part of the test by more than 0.5 °F (0.3 °C), these compressor cycles are not considered regular compressor cycles and must be included in the second part of the test. As an example, a “precooling” cycle, which is an extended compressor cycle that lowers the temperature(s) of one or both compartments prior to energizing the defrost heater, must be included in the second part of the test. The test period for the second part of the test ends at the termination of the first regular compressor “on” cycle after both compartment temperatures have fully recovered to their stable conditions. The average temperatures of the compartments measured from this termination of the first regular compressor “on” cycle until the termination of the next regular compressor “on” cycle must both be within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test. See Figure 1. Note that Figure 1 illustrates the concepts of precooling and recovery but does not represent all possible defrost cycles.
4.2.1.2 Non-cycling Compressor System. For a system with a non-cycling compressor, the second part of the test starts at a time before defrost during stable operation when the temperatures of both fresh food and freezer compartments are within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test. The second part stops at a time after defrost during stable operation when the temperatures of both compartments are within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test. See Figure 2.
4.2.2 Variable Defrost Control. If the model being tested has a variable defrost control system, the test shall consist of the same two parts as the test for long-time automatic defrost (section 4.2.1).
4.2.3Multiple-compressor Products with Automatic Defrost.
4.2.3.1Measurement Frequency. Measurements of power input, cumulative electric energy consumption (watt-hours or kilowatt-hours), and compartment temperature shall be taken at regular intervals not exceeding one minute.
4.2.3.2Steady-state Condition. Steady state shall be considered to have been attained after 24 hours of operation after the last adjustment of the temperature controls.
4.2.3.3Primary Compressor. If at least one compressor cycles, test periods shall be based on compressor cycles associated with the primary compressor system (these are referred to as “primary compressor cycles”). If the freezer compressor cycles, it shall be the primary compressor system.
4.2.3.4Test Periods. The two-part test described in this section shall be used. The first part is a stable continuous period of compressor operation that includes no defrost cycles or events associated with a defrost cycle, such as precooling or recovery, for any compressor system. The second part is a continuous test period designed to capture the energy consumed during all of the events occurring with the defrost control sequence that are outside of stable operation. The second part of the test shall be conducted separately for each automatic defrost system present.
4.2.3.4.1First Part of Test. If at least one compressor cycles, the test period for the first part of the test shall include a whole number of complete primary compressor cycles comprising at least 24 hours of stable operation, unless a defrost occurs prior to completion of 24 hours of stable operation, in which case the first part of the test shall include a whole number of complete primary compressor cycles comprising at least 18 hours of stable operation. If no compressor cycles, the first part of the test shall comprise at least 24 hours of stable operation, unless a defrost occurs prior to completion of 24 hours of stable operation, in which case the first part of the test shall comprise at least 18 hours of stable operation.
4.2.3.4.2Second Part of Test. (a) If at least one compressor cycles, the test period for the second part of the test starts during stable operation before all portions of the defrost cycle, at the beginning of a complete primary compressor cycle. The test period for the second part of the test ends during stable operation after all portions of the defrost cycle, including recovery, at the termination of a complete primary compressor cycle. The start and stop for the test period shall both occur either when the primary compressor starts or when the primary compressor stops. For each compressor system, the compartment temperature averages for the first and last complete compressor cycles that lie completely within the second part of the test must be within 0.5 °F (0.3 °C) of the average compartment temperature measured for the first part of the test. If any one of the compressor systems is non-cycling, its compartment temperature averages during the first and last complete primary compressor cycles of the second part of the test must be within 0.5 °F (0.3 °C) of the average compartment temperature measured for the first part of the test.
(b) If no compressor cycles, the test period for the second part of the test starts during stable operation before all portions of the defrost cycle, when the compartment temperatures of all compressor systems are within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test. The test period for the second part ends during stable operation after all portions of the defrost cycle, including recovery, when the compartment temperatures of all compressor systems are within 0.5 °F (0.3 °C) of their average temperatures measured for the first part of the test.
4.2.4 Systems with Multiple Defrost Frequencies. This section applies to models with long-time automatic or variable defrost control with multiple defrost cycle types, such as models with single compressors and multiple evaporators in which the evaporators have different defrost frequencies. The two-part method in 4.2.1 shall be used. The second part of the method will be conducted separately for each distinct defrost cycle type.
5. Test Measurements
5.1Temperature Measurements. (a) Temperature measurements shall be made at the locations prescribed in Figures 5.1 and 5.2 of HRF-1-2008 (incorporated by reference; see § 430.3) and shall be accurate to within ±0.5 °F (0.3 °C). No freezer temperature measurements need be taken in an all-refrigerator model.
(b) If the interior arrangements of the unit under test do not conform with those shown in Figure 5.1 and 5.2 of HRF-1-2008, the unit must be tested by relocating the temperature sensors from the locations specified in the figures to avoid interference with hardware or components within the unit, in which case the specific locations used for the temperature sensors shall be noted in the test data records maintained by the manufacturer in accordance with 10 CFR 429.71, and the certification report shall indicate that non-standard sensor locations were used. If any temperature sensor is relocated by any amount from the location prescribed in Figure 5.1 or 5.2 of HRF-1-2008 in order to maintain a minimum 1-inch air space from adjustable shelves or other components that could be relocated by the consumer, this constitutes a relocation of temperature sensors that shall be recorded in the test data and reported in the certification report as described above.
5.1.1Measured Temperature. The measured temperature of a compartment is the average of all sensor temperature readings taken in that compartment at a particular point in time. Measurements shall be taken at regular intervals not to exceed 4 minutes. Measurements for products with multiple-compressor systems shall be taken at regular intervals not to exceed one minute.
5.1.2Compartment Temperature. The compartment temperature for each test period shall be an average of the measured temperatures taken in a compartment during the test period as defined in section 4 of this appendix. For long-time automatic defrost models, compartment temperatures shall be those measured in the first part of the test period specified in section 4.2.1 of this appendix. For models with variable defrost controls, compartment temperatures shall be those measured in the first part of the test period specified in section 4.2.2 of this appendix. For models with automatic defrost that is neither long-time nor variable defrost, the compartment temperature shall be an average of the measured temperatures taken in a compartment during a stable period of compressor operation that (a) includes no defrost cycles or events associated with a defrost cycle, such as precooling or recovery, (b) is no less than three hours in duration, and (c) includes two or more whole compressor cycles. If the compressor does not cycle, the stable period used for the temperature average shall be three hours in duration.
5.1.3 Fresh Food Compartment Temperature. The fresh food compartment temperature shall be calculated as:
Where:
R is the total number of applicable fresh food compartments, which include the first fresh food compartment and any number of separate auxiliary fresh food compartments (including separate auxiliary convertible compartments tested as fresh food compartments in accordance with section 2.7);
TRi is the compartment temperature of fresh food compartment “i” determined in accordance with section 5.1.2; and
VRi is the volume of fresh food compartment “i”.
5.1.4 Freezer Compartment Temperature. The freezer compartment temperature shall be calculated as:
Where:
F is the total number of applicable freezer compartments, which include the first freezer compartment and any number of separate auxiliary freezer compartments (including separate auxiliary convertible compartments tested as freezer compartments in accordance with section 2.7);
TFi is the compartment temperature of freezer compartment “i” determined in accordance with section 5.1.2; and
VFi is the volume of freezer compartment “i”.
5.2 Energy Measurements
5.2.1 Per-Day Energy Consumption. The energy consumption in kilowatt-hours per day, ET, for each test period shall be the energy expended during the test period as specified in section 4 adjusted to a 24-hour period. The adjustment shall be determined as follows.
5.2.1.1 Nonautomatic and Automatic Defrost Models. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:
ET = EP × 1440/T
Where:
ET = test cycle energy expended in kilowatt-hours per day;
EP = energy expended in kilowatt-hours during the test period;
T = length of time of the test period in minutes; and
1440 = conversion factor to adjust to a 24-hour period in minutes per day.
5.2.1.2 Long-time Automatic Defrost. If the two-part test method is used, the energy consumption in kilowatt-hours per day shall be calculated equivalent to:
ET = (1440 × EP1/T1) (EP2 − (EP1 × T2/T1)) × (12/CT)
Where:
ET and 1440 are defined in 5.2.1.1;
EP1 = energy expended in kilowatt-hours during the first part of the test;
EP2 = energy expended in kilowatt-hours during the second part of the test;
T1 and T2 = length of time in minutes of the first and second test parts respectively;
CT = defrost timer run time or compressor run time between defrosts in hours required to cause it to go through a complete cycle, rounded to the nearest tenth of an hour; and
12 = factor to adjust for a 50-percent run time of the compressor in hours per day.
5.2.1.3Variable Defrost Control. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:
ET = (1440 × EP1/T1) (EP2 − (EP1 × T2/T1)) × (12/CT),
Where:
1440 is defined in 5.2.1.1 and EP1, EP2, T1, T2, and 12 are defined in 5.2.1.2;
CT = (CTL × CTM)/(F × (CTM − CTL) CTL);
CTL = the shortest compressor run time between defrosts used in the variable defrost control algorithm (greater than or equal to 6 but less than or equal to 12 hours), or the shortest compressor run time between defrosts observed for the test (if it is shorter than the shortest run time used in the control algorithm and is greater than 6 hours), or 6 hours (if the shortest observed run time is less than 6 hours), in hours rounded to the nearest tenth of an hour;
CTM = maximum compressor run time between defrosts in hours rounded to the nearest tenth of an hour (greater than CTL but not more than 96 hours);
F = ratio of per day energy consumption in excess of the least energy and the maximum difference in per-day energy consumption and is equal to 0.20.
For variable defrost models with no values for CTL and CTM in the algorithm, the default values of 6 and 96 shall be used, respectively.
5.2.1.4Multiple-compressor Products with Automatic Defrost. For multiple-compressor products, the two-part test method in section 4.2.3.4 of this appendix must be used. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:
Where:
1440, EP1, T1, and 12 are defined in 5.2.1.2;
i = a variable that can equal 1, 2, or more that identifies each individual compressor system that has automatic defrost;
D = the total number of compressor systems with automatic defrost;
EP2i = energy expended in kilowatt-hours during the second part of the test for compressor system i;
T2i = length of time in minutes of the second part of the test for compressor system i;
CTi = the compressor run time between defrosts for compressor system i in hours rounded to the nearest tenth of an hour, for long-time automatic defrost control equal to a fixed time in hours, and for variable defrost control equal to
(CTLi × CTMi)/(F × (CTMi − CTLi) CTLi);
Where:
CTLi = for compressor system i, the shortest compressor run time between defrosts used in the variable defrost control algorithm (greater than or equal to 6 but less than or equal to 12 hours), or the shortest compressor run time between defrosts observed for the test (if it is shorter than the shortest run time used in the control algorithm and is greater than 6 hours), or 6 hours (if the shortest observed run time is less than 6 hours), in hours rounded to the nearest tenth of an hour;
CTMi = for compressor system i, the maximum compressor run time between defrosts in hours rounded to the nearest tenth of an hour (greater than CTLi but not more than 96 hours); and
F = default defrost energy consumption factor, equal to 0.20.
For variable defrost models with no values for CTLi and CTMi in the algorithm, the default values of 6 and 96 shall be used, respectively.
5.2.1.5 Long-time or Variable Defrost Control for Systems with Multiple Defrost cycle Types. The energy consumption in kilowatt-hours per day shall be calculated equivalent to:
Where:
1440 is defined in 5.2.1.1 and EP1, T1, and 12 are defined in 5.2.1.2;
i is a variable that can equal 1, 2, or more that identifies the distinct defrost cycle types applicable for the refrigerator or refrigerator-freezer;
EP2i = energy expended in kilowatt-hours during the second part of the test for defrost cycle type i;
T2i = length of time in minutes of the second part of the test for defrost cycle type i;
CTi is the compressor run time between instances of defrost cycle type i, for long-time automatic defrost control equal to a fixed time in hours rounded to the nearest tenth of an hour, and for variable defrost control equal to
(CTLi × CTMi)/(F × (CTMi − CTLi) CTLi);
CTLi = least or shortest compressor run time between instances of defrost cycle type i in hours rounded to the nearest tenth of an hour (CTL for the defrost cycle type with the longest compressor run time between defrosts must be greater than or equal to 6 but less than or equal to 12 hours);
CTMi = maximum compressor run time between instances of defrost cycle type i in hours rounded to the nearest tenth of an hour (greater than CTLi but not more than 96 hours);
For cases in which there are more than one fixed CT value (for long-time defrost models) or more than one CTM and/or CTL value (for variable defrost models) for a given defrost cycle type, an average fixed CT value or average CTM and CTL values shall be selected for this cycle type so that 12 divided by this value or values is the frequency of occurrence of the defrost cycle type in a 24 hour period, assuming 50% compressor run time.
F = default defrost energy consumption factor, equal to 0.20.
For variable defrost models with no values for CT Li and CTMi in the algorithm, the default values of 6 and 96 shall be used, respectively.
D is the total number of distinct defrost cycle types.
5.3Volume Measurements. (a) The unit's total refrigerated volume, VT, shall be measured in accordance with HRF-1-2008 (incorporated by reference; see § 430.3), section 3.30 and sections 4.2 through 4.3. The measured volume shall include all spaces within the insulated volume of each compartment except for the volumes that must be deducted in accordance with section 4.2.2 of HRF-1-2008, and be calculated equivalent to:
VT = VF VFF
Where:
VT = total refrigerated volume in cubic feet,
VF = freezer compartment volume in cubic feet, and
VFF = fresh food compartment volume in cubic feet.
(b) In the case of products with automatic icemakers, the volume occupied by the automatic icemaker, including its ice storage bin, is to be included in the volume measurement.
(c) Total refrigerated volume is determined by physical measurement of the test unit. Measurements and calculations used to determine the total refrigerated volume shall be retained as part of the test records underlying the certification of the basic model in accordance with 10 CFR 429.71.
5.4 Externally Vented Refrigerator or Refrigerator-Freezer Units. All test measurements for the externally vented refrigerator or refrigerator-freezer shall be made in accordance with the requirements of other sections of this appendix, except as modified in this section or other sections expressly applicable to externally vented refrigerators or refrigerator-freezers.
5.4.1 Operability of “Thermostatic” and “Mixing of Air” Controls. Before conducting energy consumption tests, the operability of thermostatic controls that permit the mixing of exterior and ambient air when exterior air temperatures are less than 60 °F (15.6 °C) must be verified. The operability of such controls shall be verified by operating the unit under ambient air temperature of 90 °F (32.2 °C) and exterior air temperature of 45 °F (7.2 °C). If the inlet air entering the condenser or condenser/compressor compartment is maintained at 60 ±3 °F (15.6 ±1.7 °C), energy consumption of the unit shall be measured under 5.4.2.2 and 5.4.2.3. If the inlet air entering the condenser or condenser/compressor compartment is not maintained at 60 ±3 °F (15.6 ±1.7 °C), energy consumption of the unit shall also be measured under 5.4.2.4.
5.4.2 Energy Consumption Tests.
5.4.2.1 Correction Factor Test. To enable calculation of a correction factor, K, two full cycle tests shall be conducted to measure energy consumption of the unit with air mixing controls disabled and the condenser inlet air temperatures set at 90 °F (32.2 °C) and 80 °F (26.7 °C). Both tests shall be conducted with all compartment temperature controls set at the position midway between their warmest and coldest settings and the anti-sweat heater switch off. Record the energy consumptions ec90 and ec80, in kWh/day.
5.4.2.2 Energy Consumption at 90 °F. The unit shall be tested at 90 °F (32.2 °C) exterior air temperature to record the energy consumptions (e90)i in kWh/day. For a given setting of the anti-sweat heater, the value i corresponds to each of the two states of the compartment temperature control positions.
5.4.2.3 Energy Consumption at 60 °F. The unit shall be tested at 60 °F (26.7 °C) exterior air temperature to record the energy consumptions (e60)i in kWh/day. For a given setting of the anti-sweat heater, the value i corresponds to each of the two states of the compartment temperature control positions.
5.4.2.4 Energy Consumption if Mixing Controls do not Operate Properly. If the operability of temperature and mixing controls has not been verified as required under 5.4.1, the unit shall be tested at 50 °F (10.0 °C) and 30 °F (-1.1 °C) exterior air temperatures to record the energy consumptions (e50)i and (e30)i. For a given setting of the anti-sweat heater, the value i corresponds to each of the two states of the compartment temperature control positions.
6. Calculation of Derived Results From Test Measurements
6.1 Adjusted Total Volume.
6.1.1 Electric Refrigerators. The adjusted total volume, VA, for electric refrigerators under test shall be defined as:
VA = (VF × CR) VFF
Where:
VA = adjusted total volume in cubic feet;
VF and VFF are defined in 5.3; and
CR = dimensionless adjustment factor of 1.47 for refrigerators other than all-refrigerators, or 1.0 for all-refrigerators.
6.1.2 Electric Refrigerator-Freezers. The adjusted total volume, VA, for electric refrigerator-freezers under test shall be calculated as follows:
VA = (VF × CRF) VFF
Where:
VF and VFF are defined in 5.3 and VA is defined in 6.1.1, and
CRF = dimensionless adjustment factor of 1.76.
6.2Average Per-Cycle Energy Consumption. The average per-cycle energy consumption for a cycle type, E, is expressed in kilowatt-hours per cycle to the nearest one hundredth (0.01) kilowatt-hour and shall be calculated according to the sections below.
6.2.1All-Refrigerator Models. The average per-cycle energy consumption shall depend upon the temperature attainable in the fresh food compartment as shown below.
6.2.1.1 If the fresh food compartment temperature is always below 39.0 °F (3.9 °C), the average per-cycle energy consumption shall be equivalent to:
E = ET1
Where:
ET is defined in 5.2.1; and
The number 1 indicates the test period during which the highest fresh food compartment temperature is measured.
6.2.1.2 If one of the fresh food compartment temperatures measured for a test period is greater than 39.0 °F (3.9 °C), the average per-cycle energy consumption shall be equivalent to:
E = ET1 ((ET2 − ET1) × (39.0 − TR1)/(TR2 − TR1))
Where:
ET is defined in 5.2.1;
TR = fresh food compartment temperature determined according to 5.1.3 in degrees F;
The numbers 1 and 2 indicate measurements taken during the first and second test period as appropriate; and
39.0 = standardized fresh food compartment temperature in degrees F.
6.2.2Refrigerators and Refrigerator-Freezers. The average per-cycle energy consumption shall be defined in one of the following ways as applicable.
6.2.2.1If the fresh food compartment temperature is at or below 39 °F (3.9 °C) during both tests and the freezer compartment temperature is at or below 15 °F (−9.4 °C) during both tests of a refrigerator or at or below 0 °F (−17.8 °C) during both tests of a refrigerator-freezer, the average per-cycle energy consumption shall be:
E = ET1 IET
Where:
ET is defined in 5.2.1;
IET, expressed in kilowatt-hours per cycle, equals 0 (zero) for products without an automatic icemaker, and equals 0.23 for products with an automatic icemaker; and
The number 1 indicates the test period during which the highest freezer compartment temperature was measured.
6.2.2.2If the conditions of 6.2.2.1 do not exist, the average per-cycle energy consumption shall be defined by the higher of the two values calculated by the following two formulas:
E = ET1 ((ET2 − ET1) × (39.0 − TR1)/(TR2 − TR1)) IET
and
E = ET1 ((ET2 − ET1) × (k − TF1)/(TF2 − TF1)) IET
Where:
ET is defined in 5.2.1;
IET is defined in 6.2.2.1;
TR and the numbers 1 and 2 are defined in 6.2.1.2;
TF = freezer compartment temperature determined according to 5.1.4 in degrees F; 39.0 is the standardized temperature for fresh food compartments in degrees F; and
k is a constant 15.0 for refrigerators or 0.0 for refrigerator-freezers, each being standardized freezer compartment temperatures in degrees F.
6.2.2.3Optional Test for Models with Two Compartments and User Operable Controls. If the procedure of section 3.3 of this appendix is used for setting temperature controls, the average per-cycle energy consumption shall be defined as follows:
E = EX IET
Where:
E is defined in 6.2.1.1;
IET is defined in 6.2.2.1; and
EX is defined and calculated as described in AS/NZS 4474.1:2007 (incorporated by reference; see § 430.3) appendix M, section M4(a). The target temperatures txA and txB defined in section M4(a)(i) of AS/NZS 4474.1:2007 shall be the standardized temperatures defined in section 3.2 of this appendix.
6.2.3 Variable Anti-Sweat Heater Models. The standard cycle energy consumption of an electric refrigerator-freezer with a variable anti-sweat heater control (Estd), expressed in kilowatt-hours per day, shall be calculated equivalent to:
Estd = E (Correction Factor) where E is determined by 6.2.1.1, 6.2.1.2, 6.2.2.1, or 6.2.2.2, whichever is appropriate, with the anti-sweat heater switch in the “off” position or, for a product without an anti-sweat heater switch, the anti-sweat heater in its lowest energy use state.
Correction Factor = (Anti-sweat Heater Power × System-loss Factor) × (24 hrs/1 day) × (1 kW/1000 W)
Where:
Anti-sweat Heater Power = 0.034 * (Heater Watts at 5%RH)
0.211 * (Heater Watts at 15%RH)
0.204 * (Heater Watts at 25%RH)
0.166 * (Heater Watts at 35%RH)
0.126 * (Heater Watts at 45%RH)
0.119 * (Heater Watts at 55%RH)
0.069 * (Heater Watts at 65%RH)
0.047 * (Heater Watts at 75%RH)
0.008 * (Heater Watts at 85%RH)
0.015 * (Heater Watts at 95%RH)
Heater Watts at a specific relative humidity = the nominal watts used by all heaters at that specific relative humidity, 72 °F (22.2 °C) ambient, and DOE reference temperatures of fresh food (FF) average temperature of 39 °F (3.9 °C) and freezer (FZ) average temperature of 0 °F (−17.8 °C).
System-loss Factor = 1.3.
6.3 Externally vented refrigerator or refrigerator-freezers. Per-cycle energy consumption measurements for an externally vented refrigerator or refrigerator-freezer shall be calculated in accordance with the requirements of this appendix, as modified in sections 6.3.1-6.3.7.
6.3.1 Correction Factor. The correction factor, K, shall be calculated as:
K = ec90/ec80
Where:
ec90 and ec80 are measured in section 5.4.2.1.
6.3.2 Combining Test Results of Different Settings of Compartment Temperature Controls. For a given setting of the anti-sweat heater, follow the calculation procedures of 6.2 to combine the test results for energy consumption of the unit at different temperature control settings for each condenser inlet air temperature tested under 5.4.2.2, 5.4.2.3, and 5.4.2.4, where applicable, (e90)i, (e60)i, (e50)i, and (e30)i. The combined values, 90, 60, 50, and 30, where applicable, are expressed in kWh/day.
6.3.3 Energy Consumption Corrections. For a given setting of the anti-sweat heater, adjust the energy consumptions 90, 60, 50, and 30 calculated in 6.3.2 by multiplying the correction factor K to obtain the corrected energy consumptions per day in kWh/day:
E90 = K × 90,
E60 = K × 60,
E50 = K × 50, and
E30 = K × 30
Where:
K is determined under section 6.3.1; and 90, 60, 50, and 30 are determined under section 6.3.2.
6.3.4 Energy Profile Equation. For a given setting of the anti-sweat heater, calculate the energy consumption EX, in kWh/day, at a specific exterior air temperature between 80 °F (26.7 °C) and 60 °F (26.7 °C) using the following equation:
EX = E60 (E90 − E60) × (TX − 60)/30
Where:
TX is the exterior air temperature in °F;
60 is the exterior air temperature in °F for the test of section 5.4.2.3;
30 is the difference between 90 and 60;
E60 and E90 are determined in section 6.3.3.
6.3.5 Energy Consumption at 80 °F (26.7 °C), 75 °F (23.9 °C) and 65 °F (18.3 °C). For a given setting of the anti-sweat heater, calculate the energy consumptions at 80 °F (26.7 °C), 75 °F (23.9 °C) and 65 °F (18.3 °C) exterior air temperatures, E80, E75 and E65, respectively, in kWh/day, using the equation in 6.3.4.
6.3.6 National Average Per-Cycle Energy Consumption. For a given setting of the anti-sweat heater, calculate the national average energy consumption, EN, in kWh/day, using one of the following equations:
EN = 0.523 × E60 0.165 × E65 0.181 × E75 0.131 × E80, for units not tested under section 5.4.2.4; and
EN = 0.257 × E30 0.266 × E50 0.165 × E65 0.181 × E75 0.131 × E80, for units tested under section 5.4.2.4
Where:
E30, E50, and E60 are defined in 6.3.3;
E65, E75, and E80 are defined in 6.3.5;
and
the coefficients 0.523, 0.165, 0.181, 0.131, 0.257 and 0.266 are weather-associated weighting factors.
6.3.7 Regional Average Per-Cycle Energy Consumption. If regional average per-cycle energy consumption is required to be calculated for a given setting of the anti-sweat heater, calculate the regional average per-cycle energy consumption, ER, in kWh/day, for the regions in Figure 3. Use one of the following equations and the coefficients in Table A:
ER = a1 × E60 c × E65 d × E75 e × E80, for a unit that is not required to be tested under section 5.4.2.4; or
ER = a × E30 b × E50 c × E65 d × E75 e × E80, for a unit tested under section 5.4.2.4
Where:
E30, E50, and E60 are defined in section 6.3.3;
E65, E75, and E80 are defined in section 6.3.5; and
a1, a, b, c, d, and e are weather-associated weighting factors for the regions, as specified in Table A.
Table A—Coefficients for Calculating Regional Average per-Cycle Energy Consumption
[Weighting factors]
Regions a1 a b c d e
I 0.282 0.039 0.244 0.194 0.326 0.198
II 0.486 0.194 0.293 0.191 0.193 0.129
III 0.584 0.302 0.282 0.178 0.159 0.079
IV 0.664 0.420 0.244 0.161 0.121 0.055
7. Test Procedure Waivers
To the extent that the procedures contained in this appendix do not provide a means for determining the energy consumption of a refrigerator or refrigerator-freezer, a manufacturer must obtain a waiver under 10 CFR 430.27 to establish an acceptable test procedure for each such product. Such instances could, for example, include situations where the test set-up for a particular refrigerator or refrigerator-freezer basic model is not clearly defined by the provisions of section 2. For details regarding the criteria and procedures for obtaining a waiver, please refer to 10 CFR 430.27.
[75 FR 78851, Dec. 16, 2010, as amended at 76 FR 12502, Mar. 7, 2011; 76 FR 24781, May 2, 2011; 77 FR 3574, Jan. 25, 2012; 79 FR 22349, Apr. 21, 2014; 79 FR 41418, July 16, 2014]

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  • 2015-10-16; vol. 80 # 200 - Friday, October 16, 2015
    1. 80 FR 62441 - Energy Conservation Program for Consumer Products: Test Procedures for Clothes Washers; Correcting Amendments
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      DEPARTMENT OF ENERGY, Office of Energy Efficiency and Renewable Energy
      Final rule; correcting amendments.
      Effective Date: October 16, 2015.
      10 CFR Part 430

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  • 2015-11-27; vol. 80 # 228 - Friday, November 27, 2015
    1. 80 FR 74020 - Energy Conservation Program: Test Procedures for Portable Air Conditioners
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      Supplemental notice of proposed rulemaking.
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      10 CFR Part 429

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