## Thursday December 27, 1979



# Part III 

# Department of Energy

Office of Conservation and Solar Energy

Test Procedures for Central Air Conditioners, Including Heat Pumps

### 76700 Federal Register 

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# I Rules and Regulations

DEPARTMENT OF ENERGY

Office of Conservation and Solar Energy

10 CFR Part 430 Energy Conservation Program for Consumer Products; Test Procedures for Central Air Conditioners, Including Heat Pumps

AGENCY: 

### Department ofEnergy.
ACTION: 

### Final rule.

SUMMARY:

### The**D~partment** 

### ofEnergy amends its test procedures for central airconditioners to include test procedures for heat pumps. and to modify the existing test procedures for otherkinds ofcentral air conditioners. These test procedures are part ofthe energy conservation program for

consumer products established pursuant to the Energy Policy and Conservation Act. Among otherprogram elements. the legislation requires that standard methods oftesting be prescribed for coveredproducts.

EFFECTIVE DATE: 

### January 17. 1980. FOR FURTHER INFORMATION CONTACT:
James A. Smith. U.S. Department ofEnergy.

Office of Conservation and SolarEnergy. Mail Station 2221C. 20 Massachusetts Avenue, N.W.• Washington. D.C. 20585. 202-376-4814. WilliamJ. Dennison, U.S. Department of

Energy. Office of General Counsel. Mail Station 3224. 20 Massachusetts Avenue. N.W •• Washington. D.C. 20585. 202-376- 4100.

SUPPLEMENTARY INFORMATION: 

### A. Background

On October 1. 1977. the Department of Energy (DOE) assumed the authority of the Federal Energy Administration (FEA) for the energy conservation program for consumer products. pursuant to Section 301 ofthe Department ofEnergy Organization Act (DOE Act) (Pub. L. 

### 95-91). The energy conservationprogram for consumer products was establishedby FEA pursuant to Title III. Part Bofthe Energy Policy and Conservation Act (Act) (Pub. L. 94-163).1 Section 323 (42 U.S.C. 6293) ofthe Act requires that standard methods oftesting be prescribed for coveredproducts. Test procedures appear at 10 CFR Part 430. Subpart B.

Test procedures for central air conditioners were originally proposed

1Subsequently. the Act was amended by the National Energy Conservation Policy Act (NECPA] (Pub. L. 95-619). References in this notice to "the Act" or to sections ofthe Act refer to the Energy Policy and Conservation Act as amended by NECPA. 

### by notice issued June 7. 1977 (42 FR 30401. June 14. 1977) and a public hearing on the proposed test procedures

was held on August 4. 1977. Final test procedures for central air conditioners

were prescribed on November 21. 1977 (42 FR 60150. November 25. 1977). DOE proposed to amend the test procedures

on April 6. 1979 (44 

### FR 23468. April 19. 1979) in order to include testing procedures for heat pumps. and solicited public comments on the need to modify any provisions ofthe existing test procedures for other kinds ofcentral air conditioners. A public hearing was held

on June 13. 1979. at which the proposed changes were discussed.


### B. Discussion ofComments

Comments were received from manufacturers. a trade association. and interested individuals. The major issues raised by the comments are discussed below.



### 1. CentralAirConditionerDefinition. One commenter requested clarification ofthe applicability ofthe test procedures to packaged combination units. A packaged combination unit is a central air conditioner and a furnace in

a single cabinet. Although this type of equipment is generally used in commercial applications. either the heating capacity or the cooling capacity ofa given model could fall within the capacity limits set forth in the central air conditioner or furnace definitions in 10 CFR 430.2. If

### both heating and cooling capacities ofa packaged combination unit fall within the defined limits, the unit is accurately characterized as a residential unit and the DOE test procedures are applicable to both the heating and cooling functions. If

### either ofthe functions. however. has a capacity greater than the defined residential limits specified in section 430.2. the unit is most likely to be used in a commercial application andis not covered by the test procedures in either the heating or cooling mode. DOE has modified the definition ofcentral air conditioner in section 430.2 to clarify the treatment ofthese units in today's fmal rule.



### 2. EnergyEfficiencyMeasures. Several comments were concerned with the use ofthe measures ofefficiency identified in the proposed rule. Proposed section 430.22(m)(5) identified the heating seasonal performance factor (HSPF). the cooling seasonal performance factor (CSPF). the seasonal energy efficiency ratio (SEER). and the annualperformance factor (APF) as
measures ofefficiency. The CSPF and the SEER are essentially the same; the CSPF is derived by dividing the SEER (expressed in Btu's/watt-hour) by a conversion factor (3.413 Btu's/watthour) to produce a dimensionless efficiency measure. Commenlers argued against the use ofthe CSPF on the basis ofpresent consumer familiarity with the SEER concept, and the limited. less comprehensible range ofnumerical values ofthe CSPF compared to the SEER. A related comment cautioned that heating efficiency and cooling efficiency should be expressed in the same units

so that they canbe easily compared.

The FederalTrade Commission (FTC) has requested that DOE provide the SEER as a measure ofefficiency for use in the FTC appliance labeling program established by section 324 ofthe Act. DOE has reviewed all comments concerning energy efficiency measures and has made the following changes from the proposed rule:

1. Deletion ofthe CSPF from section 430.22(m) (5) and from the test methodology in Appendix M.

2. Retention ofthe SEER in section 430.22(m)(5) and section 5.1 ofAppendix M as the only measure ofcooling seasonal efficiency.

3. Alteration ofthe method ofthe calculation ofthe HSPF values measured in section 5.2 ofAppendix M to reflect the multiplication ofthe conversion factor of 3.413 Btu's perwalthour to result in the same units as the SEER.

4. Revision ofthe APF calculations in section 5.3 ofAppendix M to replace the CSPF values with the SEER values derived in section 5.1.

Another commenter suggested that DOE prescribe only a national HSPF for comparison purposes. and delete the proposed regional HSPF values. The regional values discussed in the proposed rule are based upon climatic variations among specified geographic regions. DOE maintains that due to wide climatic variations in the United States.

a single average HSPF value would not provide sufficient useful information to
consumers and could be misleading when compared to other heating systems whose efficiency. unlike heat pump efficiency. is not affected by climate. Consequently, DOE has retained the regional HSPF values in section430.22(m)(5) oftoday's final rule.

A final related comment pointed out potential problems concerning representations ofproduct efficiency based upon computations indentified in Appendix Mbut notidentified as "measures ofefficiency" in section 430.22(M)(5). DOE intends only those

measures specifically identified in section 430.22 to be used in representations regarding the energy consumption ofcovered products. but regulation of such representations is a

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matterrelegated to the FederalTrade Commission (FTC) by sections 323(c) and 333(c) ofthe Act.

3. Degradation Coefficient. 

### Determination ofthe degration coefficient (Cd. used to quantify the cycling performance ofcentral air conditioners andheat pumps. is necessary in order to evaluate seasonal performance. Section 2.1 ofproposed Appendix M allowed manufacturers to test (by performing Tests C and D) to determine CD for all basicmodels that they sell or, at manufacturers' option, to

use an assigned value ofCD equal to 0.25. Many comments were received regarding the degradation coefficient. These comments pointed out two general areas ofconcern. The first

concern was the proposed requirement that any manufacturer electing to use the assigned value to rate any model must use the assigned value to rate all models that the manufacturer produces. The second concern was the specified numerical value ofthe assigned degradation coefficient, 0.25.

Nearly all commenters urged that DOE allow actual testing ofcertain models in a product line without prohibiting the use ofthe assigned value

on other models in that same product line. The commenters stated that the proposed requirement would be unduly burdensome since the time required to perform Tests C and D on all models would be considerable and would reduce the level ofeffort that a manufacturer could devote to developing and testing more efficient product designs. Commenters also stated that the testing cost for determining CD would not bejustified for low volume models and on older models which would soon be removed from production, but that sufficient marketing incentive exists to encourge such testing for newer, more efficient models with higher sales volumes. One commenter stated that his company had difficulty meeting the Tests C and D tolerances with certain units and that this difficulty, would, under the proposedrule, prevent him from advertising the higherratings for other models which had been statisfactorily tested for CD'

Some commenters stated that the proposed rule would favor the large manufacturers who hadlarger testing capabilities, but another commenter also objected to any rule which would allow manufacturers an option oftesting certain models for CD and using the assigned value on other models. This objection may have been based upon a
concern that large mannufacturers could test all products in their product lines for CD but could then calculate seasonal efficiency by using the assigned degradation factor of0.25 for all products on which the measured CD was greater than 0.25. DOE is aware that this situation could occur under today's final rule, as it could occur under the previous test procedures for central air conditioners which have beenin effect since January 1, 1978, but DOE has found no evidence ofits occurrence.

Based on its review ofall comments, DOE has determined that manufacturers ofcentral air conditioners and heat pumps should be given the option to choose which models to test for CD' retaining the option to use the assigned CD for all other models. In addition, in the case ofheat pumps, the final rule clarifies that manufacturers will be allowed the option oftesting a model for CD on a unit in the cooling mode and then using the assigned CD for that same unit in the heating mode, and vice versa. However, in the case ofa unit with two compressor speeds, ifthe assigned degradation coefficient is used at one speed, it

### must also be used for the other speed. Sections 2.1, 2.2, and 3.1.3 of Appendix M have been rewritten to reflect these changes.

Many comments were also received expressing concern over the numerical value ofthe assigned degradation coefficient, 0.25. It 

### should be noted that lower degradation coefficients indicate higher seasonal efficiency. Two commenters stated their beliefthat the 0.25 value accuratelyreflects the data presently available; two other commenters urged that the assigned Co should be reduced to 0.15 to reflect lower cyclic losses based on data from a study conducted atPurdue University's Herrick Laboratories under the sponsorship ofthe Air Conditioning and Refrigeration Institute. Another commenter stated that the Herrick data presently available showed only that further investigation is necessary. Both DOE and the National Bureau of Standards (NBS) have carefully considered these comments andDOE has concluded that available data support the assigned 0.25 value for CD' which is only slightly higher than the

mean ofthe CD values currentlyknown to DOE which have been determined by actual testing. Units with good cycling performance can only be identified by testing to determine CD' Setting the assigned value for CD to be slightly higher than the average value will give manufacturers an incentive to test their units to show the actual cycling performance. At the same time, since the assigned value is close to the mean, manufacturers who do not test for cycling performance are unlikely to be severely penalized when they use the assigned value. Consequently, no changes in the assigned value ofCD have beenmade in today's final rule.

4. Cyclic TestProcedures. 

### One commenter disagreed with the "on" and "ofr' timp.s specified in TestD in section 3.1.1.2 ofAppendix M for use in measuring the degradation coefficient. The commenter submitted data showing cycle times for actual field installed units inboth the heating and cooling modes. The data were carefully analyzed byNBS and the results were compared with predictions made by a computerized thermostat model. NBS found that the field results provided insufficient data to conclude thatheat pumps typically operate at longer ontimes than was assumed inDOE cyclic test procedures. Based on a recommendation by NBS, today's final rule relating to cyclic "on" and "ofr' times remains the same as was originally proposed.

Another commenter suggested a new procedure termed "time constant evaluation test" to replace the cyclic tests for determination ofcyclic degradation. The time constant approach is presently under study by NBS. While this method mayhave advantages such as simplified procedures andreduced test time, the tests which thus far have been conducted according to this method raise doubts aboutits ability to measure accurately the cyclic performance degradation for all the different types of air conditioners andheatpumps presently manufactured. The time constant approach to partload performance shows promise but is not yet sufficiently developed to the point where it can be utilized.

5. Evaporator Coils. 

### The proposed rule required that within a family ofbasic models thatuse the same condensing unit, only the condenser-evaporator coil combination expectedto have the largest volume ofretail sales must be tested. Ratings for otherbasic models could, at manufacturers' option, be determined by computer simulation methods which would predict the performance ofotherbasic models consisting ofthe same condensing unit but different evaporatorcoils. The proposedrule specified certain minimum criteria for these computer models and required that any manufacturer who elected to use computer simulation submit to DOE the simulation method used. DOE also solicited comments on the feasibility ofDOE prescribing a computer model for use by all manufacturers who chose not to rate their products by actual testing.

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•
Comments received from manufacturers who had computer models unanimously opposed the idea of sumitting these models to DOE because of their perceived proprietary character. Commenters also expressed doubt that a single DOE prescribed computer model could be specific enough to predict accurate ratings, yet flexible enough to accommodate all manufacturers' products and permit innovative designs. Many commenters requestedthat DOE also allow manufacturers to use graphic and manual engineering calculation procedures to predict performance of condenser-evaporator coil combinations not actually tested.

Manufacturers who produce only evaporator coils expressed concern that builders might be reludant to install split system air conditioners consisting of a condensing unit made by one manufacturer and an evaporator coil made by a different manufacturer, unless the evaporator coil manufacturers could provide the builders with information concerning the energy characteristics of the installed systems. Because the evaporator coil manufacturers typically lack the facilities or resources for testing their coils with significant numbl]rs ofother manufacturers' condensing units, these commenters suggested that the DOE test procedure should apply to only the condensing unit of split system air conditioners, since it 

### accounts for the largest portion of the energy used by the total system.

DOE has carefully considered all of these comments and has concluded that applying the test procedure to condensing units only would require the deletion ofseasonal energy efficiency

.. ratios from the test procedures. This

would be detrimental to consumers, because seasonal ene!'gy efficiency ratios besfapproximate actual energy
use in homes. On.the other hand, DOE is also aware that any requirement that manufacturers test all condenserevaporator coil combinations would be unduly burdensome. DOE has concluded that the use of a computer simulation technique is the most accurate method for establishing rated values for all basic models of split system central air conditioners and heat pumps which are not actually tested. Since graphic and manual engineering calculation procedures perform the same functions

as do computer simulation techniques, DOE has determined that graphic and manual engineering calculation procedures are also acceptable for predicting the performance ofmodels of split system central air conditioners which utilize different evaporator coils. The National Bureau of Standards (NBS) is currently developing a computer simulation technique to predictthe performance of any evaporator coil with any condensing unit ofknown performance characteristics. Ifthis simulation method is shown to be accurate, the program will be made available to all manufacturers for use at their discretion. Although the use of analysis techniques is retained as an option available to manufacturers, whenever measures ofenergy consumption determined by analysis do not agree with measures ofenergy consumption outlined by actual testing, the test results shall prevail.

Consequently section430.23(m) of today's final rule permits ratings of condenser-evaporator coil combinations to be based upon the results of condensermanufacturers' tests ofeach condensing unit with the evaporator coil likely to have the largest sales volume of all coils that the manufacturer matches with that particular condensing unit. The manufacturer may then rate all other condenser-evaporator coil combinations using thatparticular condensing unit with values obtained by using computer simulation or other suitable analysis which incorporates the minimum requirements outlined in section 430.23(5) to predict the performance of other evaporator coils with that condensing unit.

DOE has investigated thoroughly the provision in the proposed rule that requires manufacturers to submit copies of their computer model to DOE ifthey

use a computer simulation technique to rate condenser-evaporator coil combinations different from those that

are actually tested. DOE has concluded that it 

### would be difficult for the Government to examine and certify the accuracy of each individual manufacturer's simulation method. The accuracy of simulation methods usedby

a manufacturer can only be determined by verification testing of actual condenser-evaporator coil combinations and comparison with results predicted by the simulation technique. As further explained in part C.3 ofthe preamble, verification ofthe accuracy ofmeasures ofenergy efficiency reported for labeling ofconsumer products according to today's final rule is the responsibility of the Federal Trade Commission (FTC). The FTC may decide to determine the accuracy ofthese representations by testing certain condenser-evaporator coil combinations that were rated by simulation methods. In such instances the accuracy ofthe manufacturer's simulation methods is ofcritical importance since it is anticipated that the accuracy ofthe representations 

### will bejudged in comparison with the actual test results.

However, DOE must retain some method of substantiating the accuracy of manufacturer's simulation methods in order to preserve the objectivity of the central air conditioner test procedure. Consequently, DOE has revised the final rule to include the requirement that manufacturers who choose to rate certain condenser-evaporator coil combinations ofcentral air conditioners by the use of simulation methods must submit to DOE a written statement which describes the type of simulation method used. In addition, users of simulation methods must, for every family ofbasic models using the same condensing unit, submit to DOE the test results used to establish the rated value(s) ofefficiency for the combination likely to have the highest sales volume, and a comparison ofthese test results with the system efficiency predictedwhen the simulation method is used to determine the efficiency ofthe system with the highest sales volume coil.



### If the ongoing NBS efforts succeed in developing an accurate computer simulation method for predicting the performance ofcondenser-evaporator coil combinations, DOE may use this technique as an initial screening method to determine which manufacturers' simulation methods shall be more closely inspected. Section430.23(m)(8) has been added to require any manufacturer which elects to rate its products by simulation methods to permitrepresentatives ofDOE to inspect those methods to verify their accuracy. DOE anticipates that such inspections will be performed at the manufacturer's site and will involve analytical evaluation ofthe simulation methods used, as well as actual performance of simulations and comparison ofpredicted results with actual test results. Inspections at the manufacturer's site

are expected to be the most convenient and efficient means ofverifying the simulation methods used. DOE will retain the option ofrequiring manufacturers to submit their simulation methods to DOE pursuant to the authority of section 329 ofthe Act ifthis is determined in the future to be necessary, eitherin the case ofa particularmanufacturer orfor all manufacturers which use the simulation option. DOE plans to inspect and verify by actual testing a significant percentage ofmanufacturer's simulation methods eachyear.

After thorough review ofthe comments received from manufacturers

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who produce only evaporator coils, DOE acknowledges the need to provide these manufacturers with a method by which they can make representations ofthe efficiency of split system central air conditioners which use their evaporator coils in combination with other manufacturers' condensing units. DOE agrees that a rule which requires builders or coil manufacturers to test their evaporator coils with the condensing units ofnumerous other manufacturers would beburdensome. However, it

### is equally important that an accurate rating procedure for these split systems be established to ensure that

consumers will be able to determine the estimated cost ofoperation and the efficiency ofthese combinations. DOE has concluded that an analytical method which utilizes computer simulation or other engineering analysis to predict the performance ofthese combinations is the most accurate alternative to testing. The method to predict the performance ofthe condenser-evaporator coil combination must be based upon condensing unit performance data provided by the manufacturer ofthe condensing unit. Today's final rule allows the use of this technique for evaporator coil manufacturers to rate split system combinations using their evaporator coils with another manufacturer's condensing unit. This approach will provide consumers and installers with accurate energy consumption and cost ofoperation information for these systems and will also protect evaporator coil manufacturers. which are typically small businesses. from any competitive disadvantage. It

### is anticipated that regardless ofthe method used to rate the product (testing, computer simulation. or engineering analysis). determination of compliance by the Federal Trade Commission or DOE may require actual testing to substantiate the measures of energy consumption published.

6. DemandDefrost. Many comments
were received concerning both the definition of "demand defrost" in proposed section 1.12 ofAppendix M and the application ofan enhancement factor referenced in section 5.2 of Appendix M to show improved performance for units incorporating this feature. All comments concerning the definition stated that the wording was too prescriptive and would not allow innovative methods to be incorporated into production as new technology is developed. DOE has revised the definition of "demand defrost" in section 1.12 to cover all types ofdemand defrost which initiate the defrost cycle only by measurement of some variable parameter(s) in order to establish a need for defrosting. due to frost build-up on the outdoor coil.

One commenter stated that the energy consumption ofdemand defrost should be measuredby actual testing rather than estimated by assigned factors. DOE is aware that testing is the ideal means by which to evaluate this feature; however, DOE has determined after consultation with NBS that considerably

more research is needed before a methodology canbe developed which adequately accounts for climatic variation. Because available information indicates that demand defrost systems do result in significant energy savings. DOE has determined for the present to evaluate demand defrost improvement by use of an enhancement factor derived from correlation to actual field test results.

Many commenters apparently attributed the proposed 5 percent enhancement factor specified in section 5.2 ofAppendix M directly to seasonal performance improvement. In actuality the 5 percent factor applies to the defrost capacity (QDEF) 

### in section 5.2 which in turn improves the heating seasonal performance factor (HSPF) by approximately 3 percent. Those comments which criticized the enhancement factor provided no data to indicate that demand defrost does not typically use less energy than timetemperature defrost over the course ofa year. Some comments provided detailed analysis and field test results which agreed with the proposed approach and showed that demand defrost does improve the seasonal performance ofa heat pump in the heating mode. Although this improvement does varyby region, analysis shows that in most

areas a 4 percent improvement in the seasonal performance factor is the minimum which would be expected. Based on the information submitted and actual test results. DOE has adjusted the enhancement factor in section 5.2 of Appendix M to 7percent. in order to achieve a resultant effect of4 percent improvement in the HSPF for units which use demand defrost.

7. WaterSource HeatPumps. Two commenters stated that the test methodology proposed to be used for water source heat pumps was not consistent with that used for air source units. Commenters argued that these inconsistencies could give erroneous cost information and encourage sales of

one product over another. After reviewing the comments associated with this issue. and considering the present low sales volume ofwater source heat pumps. DOE has determined not to include a methodology for testing water

source heat pumps in today's final rule. However. it is expected that after further studyby DOE and NBS a test methodology for these products will be proposed as soon as practicable. In today's final rule all sections which referred in the proposed rule to water

source heat pumps have beenreserved.

8. Dual Voltage Units. In section 3 of the proposed rule. DOE required testing ofcentral air conditioners at only one voltage (either 115V or 230V). which

was determined to be the typical residential voltage for a particularbasic model. Some comments specifically requested that the test procedures permit the rating ofcentral air conditioners atvoltages other than 230

or 115 volts by correlative methods or computer simulation. Because voltages other than 230 or 115 are not commonly used in residential applications. DOE foresees no need for specifying test procedures at other voltages.

9. Hours ofOperation. One commenter remarked that the heating and cooling loadhour maps referred to in sections 6.1.3 and 6.2.5 ofproposed Appendix M did not correlate with the actual hours ofoperation which the commenter expected to find in a particular city. The values on the maps
were not designed to represent any particular city. but rather an average of the cities within a region. These average values reflect national variation in climate in sufficient detail for purposes ofthis program. Therefore, today's final rule reflects no changes in the heating and cooling load hours.

10. EstimatedAnnualHeating Costs of HeatPumps. Several commenters expressed concern that the estimated annual heating costs for heat pumps in proposed sections 430.22(m)(1) and 430.22(m)(3) would be overstated by the proposed test procedure. DOE is aware that the sizing calculations made for furnaces and heat pumps typically employ many conservative. "worst case" assumptions. DOE proposed a correction factor of0.77 in the sections mentioned above. The 0.77 value has traditionally been used by industry for estimating actual heating season costs
more accurately. It

### is significant that this same correction factor is used in DOE's furnace test procedures. and its retention here facilitates comparisons between the operating costs ofheat pumps and the operating costs of furnaces. While the actual costs may differ somewhat. the relative operating cost differences between furnaces and heat pumps are accurately developed by the consistent use ofthe 0.77 correction factor. Until further field test data are

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available which establish the need for a change. the testprocedures will continue to use the 0.77 correction factor

..



### 11. SamplingPlan. In addition to the one-sided sampling plan contained in proposed section430.23(m). the notice of proposedrulemaking also solicited comments on an alternate sampling plan inwhich testing would have been performed on only two units ofeach basicmodel required to be tested, with the mean value ofthe test results forming the basis for product ratings. Comments on these two sampling plans

were divided, with some commenters favoring the proposed planbecause of the more reliable results it

### would yield. andwith other commenters favoring the alternate planbecause it might reduce the number ofunits required to be tested. One manufacturer provided data which indicated that with four ofthe six models it

### had tested. testing oftwo units

was sufficient to satisfy the confidence levels required in the one-sided sampling plan.

The Air 

### Conditioning and Refrigeration Institute (ARI) suggested

an alternate sampling plan to be used in conjunction with a future certification/ enforcement program for labeling and efficiency standards. This plan would allow manufacturers to rate their products based upon a minimum ofone test. Under this plan. ARI would modify

an existing industry-supported certification and enforcement program
so that verification ofpublished ratings would be done by testing models selectedunder the following criteria:

(a) selection due to a "for cause" evaluation determined by trade association engineers.

(b) selection based on shipment volume, and

(c) arbitrary selection ofexisting models.

This verification plan as presently formulated does not utilize the statistical confidence levels proposed by DOE. Instead, a negative tolerance of5 percent is allowed on capacity and SEER and ifeither oftwo units tested meets this tolerance, the product's rating is verified. If

### not, three additional units

are tested and the product is then rated at the mean ofthe measured values of the last three units tested.

The alternate program offered by ARI combines testing and enforcement activities into a single program. The DOE enforcement program for use in conjunction with the forthcoming energy efficiency standards for air conditioning equipment is still under development. All comments made which pertain to enforcement and certification are being considered in the development ofthe enforcement program. DOE recognizes the merits ofthe existing industry

. certification programs and will consider incorporating any appropriate portions ofthose programs into DOE's own enforcement planfor the standards program.

DOE has considered all comments received relating to the two sampling plans offered for comment in

### the proposed rule. Since the data which

were received show that the proposed plan utilizing statistical confidence levels will not require significantly more testing than the two-unit plan. DOE has retained the one-sided statistical sampling plan in today's final rule because ofthe increased confidence attributable to values ofenergy consumption measured under this plan.

12. 

### IndustryStandards. Many ofthe comments received indicated that two industry standards referenced in the proposed test procedure have subsequently beenrevised. and consequently commenters urged that the final test procedure reference the latest version ofthese standards. DOE has reviewed both editions ofthe American Society ofHeating, Refrigeration, and Air Conditioning Engineers (ASHRAE) Standard 37 and the Air Conditioning and Refrigeration Institute (ARI) Standard 210. No substantive changes in any sections referenced in the DOE test procedure were found. For this reason, andbecause the latest versions ofthese standards canmore easily be obtained by interestedpersons, today's final rule references the current versions, ASHRAE 37-78 andARI 210-79. As noted below, inpart C.l. ofthis preamble, DOE has consulted with the Attorney General and the Chairman of the FfCregarding DOE's use ofthese industry standards.

13. 

### TestMeasurements and Tolerances. Some comments stated that the dew point measurement specified in section 4.2.2.3 ofproposed AppendixM

was not consistent with wetbulb measurements in otherparts ofthe test procedure. It

### was not the intent to require manufacturers to measure dew point, but simply to impose a tolerance of ±0.5°F on the resultant dew point determination when wet and dry bulb temperatures were required to be measured. DOE has revised Section 4.2.2.3 ofAppendix M to clarify that dew point need not be measured.

Another comment requested a relaxation oftolerances on wet bulb temperature measurements from ±0.3°F to ±0.6°F. No specific reasons were given for the request nor was any substantive information provided. A careful examination revealed that ±0.3°F has been used in ASHRAE Standards for several years and therefore any changes to the proposed rule would not be consistent with past industry practice and would result in less reliable testresults. In

### view ofthese facts, DOE has made no changes in the tolerances allowed for wetbulb measurements in today's final rule.

Other commenters recommended a
more exactrounding procedure for capacity values specified in section 3.1 ofAppendix M. The recommended rounding was 100 Btu/hour for capacities under 20,000 Btu/hour, 200 Btu/hourfor capacitiesbetween 20,000 and 37,800 Btu/hour, and 500 Btu/hour for capacities between 38,000 and 64,500 Btu/hour. DOE agrees that this recommendation promotes greater accuracy without affecting test procedure costs, and therefore DOE has prescribed requirements in Sections 3.1 and 3.2 ofAppendix M which allow a similar rounding offprocedure in today's final rule.

14. 

### Miscellaneous. After careful consideration ofall the comments and further consultation with NBS and FfC, DOE has incorporated into the final rule

some editorial andminor technical changes thatwere not discussed above.
C. Regulations Prescribed

1. 

### TestProcedures. The test procedures for central air conditioners prescribed today are included in Subpart BofPart430 and are substantially the same as those proposed, with the exception ofthe changes discussed above. Appendix M ofSubpartBincorporates inpart the revised Air Conditioning and Refrigeration Institutes Standards 210- 79, 240-77. and 320-76, and the revised American Society ofHeating, Refrigeration, and Air Conditioning Engineers Standard 37-78 to measure the capacities and efficiencies ofcentral air conditioners, including heatpumps. Any subsequent amendment ofthese standardsby the standard-setting organizations will not affect the DOE test procedures, which can only be amended byDOE.

Under the requirements of section 32(c) ofthe Federal Energy Administration Act of 1974 (15 U.S.C. 761 

### etseq.) as amended by section 9 of the FederalEnergy Administration Authorization Act of1977 (Pub. L. 

### 95- 70), DOE is directed to consult with the Attorney General and the Chairman of the FederalTrade Commission concerning the impact on competition of any rules prescribed by DOE which utilize orincorporate anycommercial standards.

DOE has provided copies ofthe proposed test procedures for central air

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### conditioners, which incorporated the above-mentioned commercial standards, to the Attorney General andthe Chairman ofthe FederalTrade Commission for their comments concerning the impact ofsuch standards

on competition. Neither official recommended against the incorporation

or use ofthese commercial standards in the fmal test procedures for central air conditioners. At the request ofthe Attorney General, DOE will monitor manufacturers' costs ofperforming tests according to today's final rule.

2. GeneralProvisions. 

### Today's rulemaking contains definitions of"airsource heatpump," "central air conditioner," "condenser-evaporator coil combination," "condensing unit," "cooling only unit," "evaporator coil," "heatpump," and "water-source heat pump."

3. Application ofTestProcedures. 

### The testprocedures prescribed today contain statistical sampling provisions for any testing required in order to comply with sections 323(c) and 324 of the Act. Section 323(c) provides that, effective 180 days after a test procedure rule applicable to a covered product is prescribed by DOE, no manufacturer, distributor, retailer, orprivate labeler may make any representation in writing

or in any broadcast advertisement respecting the energy consumption or cost ofenergy consumed by that covered product, unless the product has been tested in accordance with the DOE test procedure, and the representation fairly discloses test results. Section 333(c) ofthe Act assigns enforcement responsibility for this provision to the Federal Trade Commission (FTC). The test procedures prescribed today are also applicable to any labeling rules which may be prescribed by the FTC pursuant to section 324 ofthe Act.

As required by section 325 ofthe Act, DOE is currently developing energy efficiency standards for the consumer products covered by the Act. An advance notice ofproposed rulemaking relating to standards for nine types of

consumer products, including central air conditioners other than heat pumps, was published in the Federal Register on January 2, 1979 (44 

### FR 49). An 

### advance notice relating to standards for heat pumps is expected to be published in the

near future, and notices ofproposed rulemaking for standards will be published as soon as practicable.

The test procedure provisions prescribed today, other than the sampling provisions ofsection 430.23(m),

are expected to be used generally for determining compliance with future standards, but the exact method of determining compliance will be decided during the ongoing standard setting process. The sampling provisions of section 430.23 are specifically intended to apply only to testing required pursuant to sections 323(c) and 324 of the Act. Future DOE regulations relating to the selection ofunits for testing to insure compliance with minimum efficiency standards under section 325 may differ substantiallyfrom the approach taken in the sampling provisions ofsection 430.23. One ofthe approaches that will be consideredby the standards program for split-system central air conditioners would require testing ofeach condensing unit with the least efficient evaporator coil that is marketed with that particular condensing unit.

4. Unit Costs of Energy. 

### Under section 323(b)(2) ofthe Act, DOE is required to provide manufacturers with information

on representative average unit costs of energy. This information was provided by notice issuedJune 22, 1979 (44 

### FR 37534. June 27, 1979), and is expected to beupdated periodically.

5. Preemption. 

### Today's rulemaking prescribing fmal test procedures for central air conditioners supersedes any State regulation to the extentrequired by section 327 ofthe Act. Pursuant to section 327, all State regulations which provide for the disclosure ofinformation with respect to any measure ofenergy consumption ofcentral air conditioners,

or which provide for an energy efficiency standard, or other requirement regarding the energy efficiency or energy use ofcentral air conditioners, must now employ test procedures identical to those specified in today's fmal rule.

6. RegulatoryandEnvironmental Review. 

### In accordance with the requirements ofthe National Environmental Policy Act of 1969 (NEPA) (42 USC 4321 etseq.), 

### DOE evaluated the proposed establishment of these test procedures for consumer products to determine ifan environmental assessment (EA) or an environmental impact statement (EIS)

was required. These test procedures will be used only to standardize the measurment ofenergy usage for the subject consumer products. The action ofprescribing these test procedures, by itself, will not result in any environmental impact. Since it was thus clearthat the proposed action was not a major Federal action significantly affecting the quality ofthe human environment, DOE determined that neither an EA nor an EIS was required. The potential environmental impacts that might occur from the application of the test procedures in connection with DOE's minimum efficiency standards program will be evaluatedby that program.

This rule has beenreviewed in accordance with Executive Order 12044 andDOE Order 2030. It

### was determined that this rule was significant in nature but did not have major impacts to manufacturers and consumers (imposing annual economic costs of$100 million or more). (Energy Policy and Conservation Act, Pub. L 94-163, as amendedbyPub. 

### L. 95-619; Department ofEnergy OrganizationAct, Pub. 

### L. 95-91)



### In 

### consideration ofthe foregOing, Part 430 ofChapter

## n ofTitle 10, Code of FederalRegulations, is amended as set forth below, effective January 17, 1980.

Issued

### inWashington, D.C., December 10. 1979. Maxine Savitz, ActingAssistantSecretary, Conservation and SolarEnergy.



### 1. Section430.2 is amendedby deleting the present definitions of "central air conditioner," "condenserevaporator coil combination," "condensingunit" and adding the following new defmitions in appropriate alphabetical order:
§ 430.2 Definitions. 

### * * 

### * * 

### *

"Air-source heat pump" means a "heatpump" which consists ofone or
more assemblies, which utilizes an indoor conditioning coil, compressor(s), and refrigerant-to-outdoor-air heat exchanger to provide airheating, and which may also provide air cooling, dehumidifying, Circulating, and air cleaning. * 

### * * 

### * *

"Central air conditioner" means a
consumer product which is poweredby single phase electric current, which is rated below 65,000 Btu/hour, which is not contained within the same cabinet

as a furnace whose rated capacity is above 225,000 Btu/hour, andwhich is either a "heatpump" or a "cooling only unit". 

### * * * 

### * *



### "Condenser-evaporator coil combination" means a condenSing unit made by one manufacturer and one of several evaporator coils, either manufacturedby the same manufacturer

or anothermanufacturer, intended to be combined with that particular condensing unit. 

### * * * * 

### *

"Condensing unit" means a component ofa central air conditioner which is designed to remove the heat absorbedby the refrigerant and to

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transfer it to the outside erivironinent, andwhich consists ofan outdoor coil, compressor(s). and airmoviIlg device. 

### * * 

### * * *



### "Cooling only unit" means a "central air conditioner" which consists ofan air cooled condensing unit and an evaporator coil. and which is designed to provide air cooling. dehumidifying. circulating. and air cleaning. 

### * * * * 

### *

"Heatpump" means a "central air conditioner" which is eitheran "airsource heat pump" or a "water-source heatpump." 

### * * * * 

### *

"Water-source heatpump" means a "heatpump" which consists ofone assembly which utilizes an indoor conditioning coil with airmoving means, compressor(s). and refrigerant-to-water heat exchanger(s) to provide both air heating and cooling. dehumidifying. circulating. and air cleaning.

2. Section 430.22 is amendedby substituting a new paragraph (m) to read

as follows:
§ 430.22 Test procedures for measures of energy consumption. 

### * * * * 

### *



### (m) Central Air Conditioners. (1) The estimated annual operating cost for cooling only units and air-source heat pumps shall be one ofthe following:

(i) For cooling only units or the cooling portion ofthe estimated annual operating cost for air-source heatpumps which provide both heating and cooling, the product of (A) the quotient ofthe cooling capacity. in Btu's perhour. determined from the steady-state wetcoil test (test A) measured at the highest compressor speed. as described in Section 3.1 ofAppendix M to this subpart. and the average seasonal energy efficiency ratio. in Btu's per watthour. determined from Section 5.1 of Appendix M to this subpart; (B) 

### the representative average use cycle of1000 cooling load hours per year; (C) 

### a conversion factor of .001 kilowatts per watt; and (D) a representative average unit cost ofelectricity in dollars per kilowatt-hour as provided pursuant to Section 323(b)(2) ofthe Act. the resulting product then being rounded offto the nearest dollar per year;

(ii) 

### For heat pumps which provide only heating or the heating portionofthe estimated annual operating cost for central air conditioners which provide both heating and cooling. the product of (Al the quotient ofthe standardized design heating requirement nearest the capacity measured in the High Temperature Test, Qs. 

### (47) in Btu's per hour, determined in Sections 5.2 and 6.2.6 ofAppendix M to this subpart, and the heating seasonal performance factor. in Btu's per watt-hour. calculatedfor heating region IV correspondiIlg to the above mentioned standardized design heating requirement determined from Section 5.2 ofAppendix M to this subpart; (B) the representative average
use cycle of2080 heatingloadhours per year; (C) 

### 0.77. a correction factor described in section 5.2 ofAppendix M to this subpart; (0) 

### a representative average unit cost ofelectricity in: dollars perkilowatt-hour as provided pursuant to Section 323(b)(2) ofthe Act; and (E) 

### a conversion factor of .001 kilowatts per watt; the resulting quotient then being rounded offto the nearest dollar per year; or

(iii) 

### For central air conditioners which provide bothheating and cooling. the quantity determined in paragraph (m)(l)(i) ofthis section added tothe quantity determined in paragraph (m)(l)(ii) ofthis section.

(2) [Reserved] (3) The estimated regional annual operating costs for cooling only units and air-source heatpumps shallbe one ofthe following:

(i) For cooling only units or the cooling portion ofthe estimated annual operating cost for central air conditioners which provide bothheating and cooling, the product of(A) the quotient ofcooling capacity in Btu's per hour determined from the steady-state wet-coil test (test A) measured at the highest compressor speed. and the average seasonal energy efficiency ratio inBtu's perwatt-hour both determined from Section 5.1 ofAppendix M to this subpart; (B) the estimatednumber of local cooling load hours per year determined from Section 6.1.3 of Appendix M to this subpart; (C) 

### a conversion factor of .001 kilowatts per watt; and (D) a representative average unit cost ofelectricity in dollars per kilowatt-hour as prOVided pursuant to Section 323(b)(2) ofthe Act. the resulting product then being rounded offto the nearest dollar peryear.

(ii) 

### For heat pumps which provide only heating or the heating portion ofthe estimated annual operating cost for central air conditioners which provide both heating and cooling, for each applicable standardized design heating requir'ement, the product of (A) the quotient ofthe estimated number of local heating load hours peryear determined from Section 6.2.5 of Appendix M to this subpart. and the heating seasonal performancefactor. in Btu's perwatt-hour, corresponding to the appropriate standardized design heating requirement determined from Section 5.2 ofAppendix Mto this subpart; (B) 0.77, a correcuon factor described in Section 5.2 ofAppendixM to this subpart; (C) 

### the standardized design heating requirement inBtll's per hour determined in Sections 5.2 and 6.2.6 ofAppendixM to this subpart; (D) a representative average unit cost of electricity in dollars perkilowatt-hour

as provided pursuant to Section 323(b)(2) ofthe Act; and (E) 

### a conversion factor of .001 kilowatts per watt, the resulting quotient thenbeing rounded offto the nearest dollar

### pet' year; or

(iii) 

### For central air conditioners which provide bothheating and cooling. the quantity determined inparagraph (m)(3)(i) ofthis section added to each quantity determined inparagraph (m)(3)(ii) ofthis section.

(4) [Reserved] (5) The measure(s) ofefficiency for cooling only units and air-source heat pumps shallbe one ormore ofthe follOwing:

(i) The seasonal energy efficiency ratio for cooling only units and airsource heat pumps which provide cooling shall be the seasonal energy efficiency ratio. inBtu's perwatt-hour, determined according to Section 5.1 of AppendixM to this Subpart. rounded off to the nearest0.05.

(ii) 

### The heating seasonal performance factors for air-source heat pumps shall be the heating seasonal performance factors. in Btu's perwatt-hour. determined according to Section 5.2 of AppendixM to this subpart for each applicable standardized design heating requirement within each climaticregion. rounded offto the nearest 0.05.

(iii) 

### The annual performance factors for air-source heatpumps which provide heating and cooling, shall be the annual performance factors, inBtu's perwatthour. determined according to Section 5.3 ofAppendix M to this subpart for each standardized design heating requirement within each climatic region. rounded offto the nearest 0.05.

(6) [Reserved] (7) Otheruseful measures ofenergy consumption for central air conditioners shallbe those measures of**enf:~'~y** 

### consumption which the Secretary of Energy determines are likely to assist

consumers in making purchasing decisions and which are derived from the application ofAppendix M to this subpart. 

## " " ." 

## " "

3. Section 430.23 is amended by establishing a new paragraph (m) to read as follows:

§ 430.23 Units to be tested. 

### * * 

## " " 

## "

(m)(l) For central air conditioners. each condensing unit shall have a

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### '76'70'7

condenser-evaporator coil combination selected and a sample of sufficient size tested in accordance with applicable provisions of this subpart such that-

(i) Any represented value ofestimated annual operating cost, energy consumption or other measure ofenergy consumption ofthe condenserevaporator coil combination for which

consumers would favor lower values shall be no less than the higher of (AJ the mean ofthe sample or (B) the upper 90 percent confidence limit ofthe true
mean divided by 1.05, and

(ii) 

### Any represented value ofthe energy efficiency or other measure of energy consumption of the condenserevaporator coil combination for which

consumers would favor higher values shall be no greater than the lower of (A) the mean ofthe sample or (B) the lower 90 percent confidence limit ofthe true

mean divided by0.95.

(2) The condenser-evaporator coil combination 1 

### selected for tests pursuant to paragraph (m)(l) shall be that combination manufactured by the condensing unit manufacturer likely to have the largest volume ofretail sales.

For every other condenser-evaporator coil combination manufactured by the

same manufacturer or in

### part by a component manufacturer using that

same condensing unit, either-

(i) 

### A sample of sufficient size shall be tested to insure that the requirements of paragraphs (m)(l)(i) and (m)(l)(ii) are met for such other condenser-evaporator coil combinations, or

(ii) 

### Represented values ofthe

measures ofenergy consumption shall be determined by the use ofcomputer simulation or engineering analysis to determine the energy consuming characteristics of such basic model, as described in paragraph (m)(5) of this section.

(3) Whenever measures ofenergy consumption determined by computer simulation or by engineering analysis do not agree with measures ofenergy consumption determined by actual testing, the values determined by actual testing shall be used to comply with section 323(cl ofthe Act, or to comply with rules prescribed under section 324 ofthe Act.

(4) The sample selected for testing under paragraph (m)(l) ofthis section shall be comprised ofunits which are production units, orrepresentative of production units.

1Components of similar design may be substituted without requiring additional testing if the represented measures ofenergy consumption continue to satisfy the applicable sampling provision. 

### (5) The basis ofthe computer simulation or engineering analysis method referred to in paragraph (m)(2)(ii) ofthis section shall be a representation ofthe mechanical vapor compression refrigeration cycle. The major components in the refrigeration cycle shall be modeled as "fits" to manufacturer performance data or by the use ofgraphic or tabular performance data. Heat transfer characteristics ofcoils may be modeled

as a function offace area, number of rows, fins per inch, refrigerant circuiting. air flow rate and entering air enthalpy. An iterative process shall be used which varies system temperatures and flow rates until the cycle is balanced.

(6) 

### When making representations regarding energy consumption. manufacturers must distinguish which condenser-evaporator coil combinations have been tested to fulfill 

### the sampling requirements for labeling and representations and which units have been rated by computer simulation or engineering analysis. If

### after a period of time (not exceeding one year from introduction ofa new product into the market) a manufacturer discovers that the condenser-evaporator coil combination tested does not have the largest volume ofretail sales he must test the combination which. in fact. does have the largest sales volume and provide that information to the Federal Trade Commission (FTC).

(7) Manufacturers who choose to use computer simulation or engineering analysis for determing measures of energy consumption underparagraphs (m)(2)(ii) and (m)(5) ofthis section must-

(i) submit to DOE a written document which describes the method used to derive such ratings, and describes the procedure used by the manufacturer to verify the accuracy of such ratings; and

(ii) 

### for every family ofbasic models using the same condensing unit, submit to DOE the results from all tests required by section 3 ofAppendix M to this subpart used to establish the rated value(s) for the condenser-evaporator coil combination likely to have the highest sales volume. and a comparison ofthose test results with the values predicted when the simulation method used to rate othermembers ofthe family is used to rate such combination.

(8) 

### Manufacturers who choose to use computer simulation or engineering analysis for determining measures of energy consumption underparagraphs (m)(2)(ii) and (m)(5) ofthis section shall permit representatives ofthe Department ofEnergy to inspect for verification purposes the simulation method ormethods used. This inspection may include conducting simulations to predict the performance ofparticular condenser-evaporator coil combinations specified by DOE. analysis ofprevious simulations conducted by a manufacturer, orboth.
§ 430.24 [Revoked]



### 4. Section 430.24(m) is revoked. 5. Appendix M to Subpart BofPart 430 is amended to read as follows: Appendix M to SubpartB-UniformTest Method for Measuring the Energy Consumption ofCentral AirConditioners


### 1. Definitions



### 1.1 "Annual performance factor"

means the total heating and cooling done by a heat pump in 

### a particular region in one year divided by the total electric power used in one year.

1.2 "ARJ" means Air-Conditioning and Refrigeration Institute.

1.3 "ARl Standard 210-79" means the test standard published in 1979by the ARl and titled "Standard for Unitary Air-Conditioning Equipment".

1.4 "ARI Standard 240-77" means the test standard published in 1977 by the ARI and titled "Standard for Air-Source Unitary Heat Pump Equipment".

1.5 "ARI Standard 320-76" means the test standard published in 1976by the ARJ and titled "Standard for Water-Source Heat Pumps",

1.6 "ASHRAE" means the American Society ofHeating. Refrigeration anli AirConditioning Engineers. Inc.

1.7 "ASHRAE Standard 37-78" means the test standard published by ASHRAE in 1978 and titled "Methods ofTesting for Rating Unitary Air-Conditioning and Heat Pump Equipment."

1.8 "Continuously recorded" means a method ofrecording measurements in intervals no greater than 5 seconds.

1.9 "Cooling load factor (CLF)" means the ratio ofthe total cooling done in a complete cycle ofa specified time period, consisting of

an "on" time and "off' time, to the steadystate cooling done over the same period at constant ambient conditions.

1.10 "Cyclic Test" means a test where the indoor and outdoor conditions are held constant, but the unit is manually turned "on" and "off' for specific time periods to simulate part-load operation.

1.11 "Degradation coefficient (CD)" means the measure ofthe efficiency loss due to the cycling ofthe unit.

1.12 "Demand-defrost control system"

means a system which is designed to perform the defrost function on the outdoor coil ofthe heat pump only when a predetermined degradation ofperformance is measured.

1.13 "Design heating requirement (DHR)" is the amount ofheating required to maintain

a given indoor temperature at a particular outdoor design temperature.

1.14 "Dry-coil test" means a test conducted at a wet-bulb temperature and a dry-bulb temperature such that moisture will not condense on the evaporator coil of the unit.

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1.15 "Heating seasonal performance factor (HSPF)" means the total heating output ofa heat pump during its normal annual usageperiod for heating dividedby the total electric powerinput during the same period.

1.16 "Heating load factor (HLF)" means the ratio ofthe-total heating done in a complete cycle ofa specified time period. consisting ofan "on" time "ofr' time. to the ste!ldy state heating done overthe same period at constant ambient conditions.

1.17 "Latent cooling" means the amount ofcooling in Btu's necessary to remove water vaporfrom the airpassing overthe indoor coil by condensation during a period oftime.

1.18 "Part-load factor (PLF)" means the ratio ofthe cyclic energy efficiency ratio to the steady-state energy efficiency ratio at identical ambient conditions.

1.19 "Seasonal energy efficiency ratio (SEER)" means the total cooling ofa central air conditionerin Btu's during its normal annual usage period for cooling divided by the total electric powerinput in watt-hours during the same period.

1.20 "Sensible cooling" means the amount ofcooling in Btu's performedby a unit over a period oftime. excluding latent cooling.

1.21 "Single package unit" means any central air conditioner in which all the major assemblies are enclosed in one cabinet.

1.22 "Split system" means any central air conditionerin which one ormore ofthe major assemblies are separate from the others.

1.23 "Steady-state test" means a test in which all indoor and outdoor conditions are held constant and the unit is innon-changing operating mode.

1.24 "Temperature bin" means a 5° F increment over a dry-bulb temperature range of65° F through 104° F for the cooling cycle and -25° F through 64° F for the heating cycle.

1.25 "Time-temperature defrost control system" means a system which automatically provides the defrost function at a predetermined time interval wheneverthe outdoortemperature drops below a level where frosting will occur.

1.26 "Testcondition tolerance" means the maximum permissible variation ofthe average ofthe test observations from the standard ordesired test condition as provided in 6.1.1. 6.2.1. 6.2.2. and 6.2.3 ofthis Appendix.

1.27 "Test operating tolerance" means the maximum permiSSible difference between the maximum and the minimum instrument observation during a test as providedin6.1.1. 6.2.1. 6.2.2. and 6.2.3 ofthis Appendix.

1.28 "Wet-coil test" means a test conducted at a wet-bulb temperature and a dry-bulb temperature such that moisture will condense on the test unit evaporatorcoil.
Z. Testing Required

2.1 Testing required for airsource cooling onlyunits with single speedcompressors, two-speedcompressors, two compressors, or cylinder unloading. Two steady state wet coil tests required to be performed, test A and testB. TestA is to be**~onducted** as an outdoor dry bulb temperature of95° F and test Bat 82° F. Test C and D are optional tests to be conducted when cyclic performance parameters are to be measured in order to determine the degradation coefficient,

### ,CO Test C is a steady state dry coil test conducted at an outdoor drybulb temperature of82° F. TestD is a cyclic test also conducted at an outdoor dry bulb temperature of82° F; Inlieu ofconducting tests C andD, an assigned value of0.25 may be used for the degradation coefficient, CD.

2.1.1 Testing required for units with single speedcompressors andsinglespeed condenser fans. Test A and test B shallbe performed according to the test procedures outlined in 4.1 ofthis Appendix. In addition, the cyclic performance shall be evaluated by conducting test C and D according to the requirements outlined in 4.1 ofthis Appendix.

2.1.2 Testing required for units with single speedcompressors andmultiple-speed condenser fans. The test requirements for multiple-speed condenserfan units shallbe the same as described in section 2.1.1 for single speed condensor fan units.

2.1.3 Testing required for units with twospeedcompressors, two compressors, or cylinder unloading. The test requirements for two-speed compressor units, two compressor units, or units with cylinder unloading are the

same as described in 2.1.1 ofthis Appendix except that test A and test B shallbe performed at eachcompressor speed or at each compressor capacity.

2.1.4 Testing required for units with twospeedcompressors, two compressors, or cylinderunloading capable ofvarying the sensible 

### to total(SIT) capacityratio. When a unit employing a two-speed compressor, two compressors, orcylinder unloading provides

a method ofvarying the ratio ofthe sensible cooling capacity to the total cooling capacity. (S/T), the testrequirements are the same as for two-speed compressor units as described in 2.1.3 ofthis Appendix.

2.2 Testing required for airsource.heating onlyunits with single speedcompressors, two-speedcompressors, two compressors, or cylinderunloading. Fourtypes oftests are required to be performed: High Temperature. Cyclic. Frost Accumulation. and Low Temperature. Inlieu ofconducting the Cyclic Test an assigned value of0.25 maybeused for the degradation coefficient, CD.

2.2.1 Testing required for units with single speedcompressors. Units with single speed compressors shallbe subjected respectively to the High TemperatureTest at 47° F described in section 3.2.1.1. the Cyclic Test as described in section 3.2.1.2, theFrost AccumulationTest as describedin section 3.2.1.3. andthe LowTemperatureTest as described in section 3.2.1.4.

2.2.2 Testing required for units with twospeedcompressors, two compressors, or cylinderunloading. With the unit operating: athigh compressors speed (two-speed compressor). withboth compressors in operation (two-compressors). or at the maximum capacity (cylinder unloading): the following tests are required to be performed

on all units; the HighTemperatureTestat 47° F, the Frost AccumulationTest. and the Low TemperatureTest. An additional test (cyclic at 47° F) is required, with the unit operating at the high compressor speed (twospeed compressor). with both compressors in operation (two compressors). or at the maximum capacity (cylinderunloading); 

### if the normal mode ofoperationrequires cycling "on" and "ofr' ofthe compressor(s) at high speed ormaximum capacity.

With the unit operating: at the low compressor speed (two-speed compressor). with the single compressor which normally operates atlowloads (two compressors). or at the low compressor capacity (cylinder unloading); the following tests are required to beperformed on all units: the High Temperature Test at 47° F. the High TemperatureTest at 62° F. andthe Cyclic Test Additional tests, (Frost Accumulation

• Test andLow Temperature Test) are

required, with the unit operating: onlow compressor speed (two-speed compressor). with the single compressor which normally operates atlow loads (two compressors) or at the low compressor capacity (cylinder unloading). ifthe unit's low speed, one compressor orlow capacity performance at andbelow40° F is needed to calculate its seasonal performance.

2.3 Testing required for airsource units whichprovide both heating andcooling. The requirements for units which provide both heating and cooling shallbe the same as the requirements in Section 2.1. and 2.2 ofthis Appendix.

2.4 Testing required for watersource units whichprovidebothheatingandcooling. (Reserved)
3. Testing conditions

3.1 Testing conditionsfor airsource cooling onlyunits with single speed compressors, two-speedcompressors, two compressors orcylinderunloading. The test

room requirement and equipment installation procedures are the same as those specified in sections 11.1 and 11.2 ofASHRAE Standard 37-78. Units designed for bothhorizontal and verticalinstallation shallbe tested inthe orientationin which they are most frequently installed. All tests shallbe performed at the normalresidential voltage and frequency for which the equipment is designed (either 115

or 230 volts and 60 hertz). the testinstallation shallbe designed such that there will be no airflow through the cooling coil due to natural orforced convection while the indoor fan is "ofr·.This shallbe accomplished by installing dampers upstream and downstream ofthe testunitto block the offperiod air flow. Values ofcapacityfor rating purposes
aretobe rounded offto the nearest 100 Btu/ hourfor capacities less than 20.000 Btu/hour; to the nearest 200 Btu/hourfor capacities between 20.000 and 37.999Btu/hour; andto the nearest 500 Btu/hourfor capacities between 36.000 and 64.999 Btu/hour.

The following conditions listedinAR1 Standard 210.79 shall apply to all tests performedin Section 3.1 ofthis Appendix: 5.1.3.4 Cooling Coil Air Quantity. 5.1.3.6 Requirements for Separated Assemblies.
3.1.1 Testing conditionsfor units with single speedcompressors andsingle speed condenser fans. 3.1.1.1 Steadystate wet-coiJperformance tests (TestA and Test B). TestA and testB shallbe performed with the airentering the indoor side ofthe unit having a dry-bulb temperature of80° F and a wet-bulb temperature of87" F. The dry-bulb

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temperature ofthe air entering the outdoor side ofthe unit shallbe 95° Fin test A and 82° F in test B. The temperature ofthe air surrounding the outdoor side ofthe unit in each test shall be the same as the outdoor entering air temperature exceptfor units or sections thereofintended to be installed only indoors, in which case the dry-bulb temperature surrounding that indoor side of the unit shall be 80° F. For those units which reject condensate to the condenser, located in the outdoor side ofthe unit, the outdoorwetbulb temperature surrounding the outdoor side ofthe unit shall be 75° Fin test A and 65° F in test B.



### 3.1.1.2 Steadystate drycoilperformance test{Test C)

### andcyclicdrycoilperformance test{Test D}. Test C and test D shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of80° F and a wet-bulb temperature which does notresult in formation ofcondensate on the indoor coil. (It is recommended that an indoor wet-bulb temperature of57° F or less be used.) The dry-bulb temperature ofthe air entering the outdoor portion ofthe unit shall be 82° F. The outdoor portion ofthe unit shall be subject to the same conditions as the requirements for conducting test Bas stated previously in section 3.1.1.1. Test C shall be conducted with the unit operating steadily. TestD shallbe conducted by cycling the unit "on" and "off" bymanual or automatic operation ofthe normal control circuit oftheunit. Theunit shall cycle with the compressor "on" for 6 minutes and "off" for 24 minutes. The indoor fan shall also cycle "on" and "off", the duration ofthe indoor fan "on" and "ofr' periods being governed by the automatic controls which the manufacturer normally supplies with the unit. The results oftests C andD shall be used to calculate a degradation coefficient, CD by the procedures outlined in 5.1 ofthis Appendix.



### 3.1.2 Testing conditionsfor units with single speedcompressors andmultiple-speed condenser fans. The condenserfan speedto be used in test A shall be that speedwhich normally occurs at an outdoor dry-bulb temperature of95° F. andfor test B. the fan speed shall be that which normally occurs at

an outdoor dry-bulb temperature of82° F. If elected to be performed, tests C andD shall be conducted at the same condenserfan speed as in test B.



### 3.1.3 Testing conditionsfor units with two-speedcompressors, two compressors, or cylinderunloading. The condenserfan speed usedin conducting test A at each compressor speed shall be that which normally occurs at

an outdoor dry-bulb temperature of95° F. For testB. the condenserfan speed at each compressor speed shallbe that which normally occurs at an outdoor dry-bulb temperature of82° F. Ifelected tobe performed. tests C andD shall be conducted at the low compressor speed with the same condenserfan speed as used in testB. For those two-speed units in which the normal mode ofoperation involves cycling the compressor "on" and "off" at high speed, tests C andD shall also be performed with the compressor operating at high speed and at a condenser fan speed that normally

occurs at test A ambient conditions. Units consisting oftwo compressors are subject to the same requirements as those units containing two-speed compressors. except that when operated at high speed. both compressors shall be operating and when operating atlow speed. only the compressor which normally operates at an outdoor drybulb temperature of82° F shall be operating.

Inlieu ofconducting tests C andD. an assigned value of0.25 may be used for the degradation coefficient. CD' at each compressor speed. Ifthe assigned degradation coefficient is used for one compressor speed it must also be used for the other compressor speed.

Inthe case ofunits with cylinder unloading. the loaded and the unloaded conditions correspond to high and low compressor speed on two-speed units respectively.



### 3.1.4 Testing conditionsfor units with two-speedcompressors, two compressors, or cylinder unloading capable ofvarying the sensible to total(SIT) capacityratio. The mode ofoperation selected for controlling the SITratio in the performance oftest A and test Bat each compressor speed shallbe such that itdoes not result in an operating configuration which is not typical ofa normal residential installation. Ifelected to be performed, tests C andD shall be conducted atlow compressor speed (single compressor operating) with the same SITcontrol mode as used in test Bwhen performed at the low compressor speed. Likewise, tests C andD shall also be conducted athigh compressor speed (two compressors operating) and with the same S/ T control mode asin test A whenperformed atthe high compressor speed.

Inthe case ofunits with cylinder unloading, the loaded and unloaded conditions correspond to high and low compressor speed on two-speed units respectively.



### 3.2 Testing conditionsfor airsource heatingonlyunits with single speed compressors, two-speedcompressors, two compressors, orcylinder unloading. The equipment undertest shall be installed according to the requirements ofSection 11.2 ofASHRAE Standard 37-78and Section 5.1.4.5 ofARI Standard 240-77. Test chamber requirements are the same as given in Section 11.1 ofASHRAE Standard 37-78. Units designed for bothhorizontal andvertical installation shallbe tested in the orientation inwhich they aremost often installed. All tests shallbeperformed at the normal residential voltage and frequency for which the equipment is designed (either 115 or230 volts and 60 hertz). Values ofcapacityfor rating purposes are to be rounded offto the nearest 100 Btu/hourfor capacities less than 20,000 Btu/hour; to the nearest 200 Btu/hour for capacities between 20,000 and 37,999 Btu/ hour; and to the nearest 500 Btu/hour for capacitiesbetween 38,000 and 64,999Btu/ hour.



### 3.2.1 Testing conditionsfor units with singlespeedcompressors.

3.2.1.1 High temperature testconditions. The High TemperatureTest at47° F shallbe conducted at anoutdoor dry-bulb temperature of47° F and an outdoorwet-bulb temperature at43° F. The High Temperature Test at 62° F shall be conducted at an outdoor dry-bulb temperature of82° F and an outdoor wet-bulb temperature of56.5° F. For both tests. the dry-bulb air temperature entering and surrounding the indoor portion ofthe unit shall be 70° F and a maximum wet-bulb temperature of80° F. The duration ofthe tests shall be for a minimum of Ih hour.



### 3.2.1.2 Cycling testconditions. The Cycling Test at47° F shallbe conducted at the same dry-bulb and wet-bulb temperature
as the High Temperature Test at 47° F as described in 3.2.1.1. During the Cycling Test, the indoor fan shall cycle "on" and "off", as the compressor cycles "on" and "ofr'. except that the indoor fan cycling times may be delayed due to controls that are normally installed with the unit. The compressor cycling times shall be 6 minutes "On" and 24 minutes "off." The test installation shall be designed such that there will be no airflow through the indoor unit due to natural or forced convection while the indoor fan is "off." This shall be accomplished by installing dampers upstream and downstream ofthe test unit to block the offperiod airflow.



### 3.2.1.3 Frost accumulation testconditions. The dry-bulb temperature and the resultant dew-point temperature ofthe air entering the outdoor portion ofthe unit shallbe 35° F and 30° F respectively. The indoor dry-bulb temperature shall be 70° F and the maximum indoor wet-bulb temperature shall be 60° F. TheFrost AccumulationTest requires that the unit undergo a defrost prior to the actual test. The test then begins at defrost termination and ends at the next defrost termination. Defrost termination occurs when the controls normally installed within the unit

are actuated to cause itto change defrost operation to normal heating operation. During the test. auxiliary resistance heaters shall not be employed during either the heating or defrost portion ofthe test.



### 3.2.1.4 Lowtemperature testconditions. The LowTemperature Test shallbe conducted at a dry-bulb temperature entering the outdoor portion ofthe unit of17° F and a wet-bulb temperature of15° F. The air entering the indoor portion ofthe unit shall have a dry-bulb temperature of70° F and a maximum wet-bulb temperature of60° F.



### 3.2.1.5 Additionaltesting conditions. All tests shallbe conducted atthe indoor-side air quantities specified in Sections 4.1.4.3 and 5.1.4.6 andTable 2 ofARI Standard 240-77. The following conditions listedin ARI Standard 240-77 shall apply to all tests performed in Section 3.2 ofthis Appendix. 

### 5.4.4.4 Outdoor-SideAirQuantity; and 5.1.4.5 RequirementsforSeparated Assemblies. In all tests, the specified dry-bulb temperature entering the outdoorportion of the unit also applies to the air temperature surrounding the outdoorportion ofthe unit. Similarly. models whereportions are intended to be installedindoors shallhave the airtemperature surrounding thatportion ofthe unit the same as the indoor air temperature.



### 3.2.2 Testing conditionsfor units with two-speedcompressors, two compressors or cylinderunloading. The testing conditions for two-speed compressors, two compressors, or cylinderunloading shall

### be the same as those for single speedunits as described in 3.2.1.

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3.3 Testing conditionsfor airsource units whichprovide both heating andcooling. The testing conditions for units which provide botliheating and cooling shall be the same as the requirements in Sections 3.1 and 3.2 of this Appendix.



### 3.4 Testing conditionsfor watersource units whichprovide both heatingandcooling. (Reserved)



### 4.0 Testingprocedures. Measure all electrical inputs as described in the procedures below. All electrical measurements during all "on" and "off' periods shall include auxiliarypower or energy (controls, transformers, crankcase heaters, etc.) delivered to the unit.



### 4.1 Testingproceduresfor airsource cooling only units with single speed compressors, two-speedcompressors, two compressors, orcylinder unloading. All steady:state wet- and dry-coil performance tests on single package units shall simultaneously employ the Air-Enthalpy Method (Section 3 ofASHRAE Standard 37- 78) on the indoor side and one other method consisting ofeither the Air-Enthalpy Method

orthe Compressor Calibration Method (Section 4 ofASHRAE Standard 37-78 on the outdoor side. All steady-state wet- and drycoil performance tests on split systems shall Simultaneously employ the Air-Enthalpy Method orthe Compressor Calibration Method on the indoor side and the AirEnthalpy Method. the Compressor Calibration Method or the Volatile Refrigerant Flow Method (Section 5 of ASHRAE Standard 37-78) on the outside. All cyclic dry-coil performance tests shall employ the Air-Enthalpy Method. indoor side only. The values calculated from the two test methods must agree within 6 percent in order to constitute a valid test. Only the results from the Alr-Enthalpy Method on the indoor side shall be used in the calculations in Section 5.1. Units shallbe installed and testedin such a manner that when operated under steady-state conditions. the cooling coil and condenser coil air flows meet the requirements ofSections 5.1.3.4. 5.1.3.5. and 5.1.3.7 ofARl Standard210.79.



### 4.1.1 Test operotingprocedures. 4.1.1.1 Steady-state wet-coilperformance tests {TestA and TestB}. Steady-state wetcoil performance tests (A and B) shall be conducted in accordance with the conditions described in sections 3.1.1.1. 3.1.2. 3.1.3. 3.1.4. and 3.1.5 ofthis Appendix and the procedures described for cooling tests in Section 11.3 of ASHRAE standard 37-78 and evaluatedin accordance with the cooling-related requirements of Section 12 ofthe ASHRAE Standard 37-78. The test room reconditioning apparatus and the equipment under test shall be operateduntil equilibrium conditions are attained.



### 4.1.1.2 Steady-state andcyclicdry-coil performance tests {Test C

### and Test D}. The steady-state and cyclic dry-coil tests (C and D) shall be conducted as described below in accordance with the conditions described in sections 3.1.1.2. 3.1.2, 3.1.3, 3.1.4. and 3.1.5 of this Appendix. The results shall be evaluated in accordance with the cooling related requirements ofSections 12.1.5.12.1.6.12.1.7. ofASHRAE Standard 37.78. The test room reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained. butnot for less than

one hourbefore data for test C are recorded. For all equipment test methods including the Compressor CalibrationMethod. test C shall be performed with data recorded at 10- minute intervals until four consecutive sets of readings are attained with the tolerance prescribed in Section 11.6 ofASHRAE Standard 37-78. When the Air-Enthalpy Method is used on the outdoor side for test C. the requirements ofthis section shall apply tq both the preliminary test and the regular equipment iest; the requirements of Section 3.6 ofASHRAE Standard 37-78 shall also apply. Immediately after test C is completed the test unit shall be manually cycled "off' and "on" using the time periods from 3.1.1 of this Appendix until steadily repeating ambient conditions are again achieved in both the indoor and outdoor test chambers. butfor not less than 2 complete "off'/"on" cycles. Without a break in the cycling pattern. the unit shall be run through an additional "ofr'/"on" cycle during which the test data required in 5.1 shall be recorded. During this last cycle. which is referred to as the test cycle. the indoor and outdoor test

room ambient conditions shall remain within the tolerances specified in 4.1.3 ofthis Appendix during the cyclic dry-coil tests. all air moving equipment on the condenser side shall cycle "on" and "off' when the compressor cycles "on" and "off'. The indoor air moving equipment shall also cycle "off'

as governed by any automatic controls normally installed with the unit. This last requirement applies to units having an indoor fan time delay. Units not supplied with an indoor fan time delay shall have the indoor air moving equipment cycle "on" and "off' as the compressor cycles "on" and "off."



### 4.1.2 Test instrumentation. The steadystate and cyclic performance tests shall have the same requirements pertaining to instrumentation and data as those specified in Section 10 andTable

## nofASHRAE Standard 37.78. For the cyclic dry-coil performance tests. the dry-bulb temperature ofthe air entering and leaving the cooling coil. orthe difference between these two drybulb temperatures. shall be continuously recorded with instrumentation accurate to within ±0.3·F ofindicated value and have a response time of2.5 seconds orless. Response time in the time required for the instrumentation to obtain 63 percent ofthe final steady-state temperature difference when subjected to a step change in temperature difference of15· F ormore. Electrical measurement devices (watt-hour meters) used during all tests shall be accurate to within ±O.5 percent ofindicatedvalue.



### 4.1.3 Test tolerances. All steady-state wet-and dry-coil performance tests shallbe performedwithin the applicable operating and test condition tolerances specified in Section 11.6 andTable III ofASHRAE Standard 37-78.

4.1.3.1 The indoor and outdoor average dry-bulb temperature for the cyclic dry coil testD shallboth be within 1.0· F ofthe indoor and outdoor average drybulb temperature for the steady-state dry coil test 

### C. respectively.

4.1.3.2 The testcondition and test operating tolerances for conducting testDare stated in 6.1.1 ofthis Appendix. Variation in the test conditions greater than the tolerances prescribed in 6.1.1 ofthis Appendix shall invalidate the test. Itis suggested that an electric resistance heater having a heating capacity approximately equal to the sum of the cooling capacity and compressor and condenser fan power shouldbe installed in the outdoor testroom and cycled "off' and "on" as the unit cycles "on" and "off' respectively to improve control in the outdoor test room. Similarly. an electric resistance heaterhaving a heating capacity approximately equal to the cooling capacity ofthe unit could be installed in the indoor test room. and cycled "on" and "off' as the test unit cycles "on" and "off' to improve indoorroom control.



### 4.2 Testingproceduresfor airsource heating only units with single speed compressors, two-speedcompressors, two compressors. orcylinder unloading.

4.2.1 Test operotingprocedures. All High Temperature Tests. the Cyclic Test. the Frost Accumulation Test. and the lowTemperature test shall have the performance evaluatedby the Air-Enthalpy Method on the indoor side. In addition. the High Temperature Test and the Low Temperature Test shall have a simultaneous test method [as described in 4.1) used as a check. The values calculated from the two methods must agree within 6 percent in order to constitute a valid test. Only the results from the Air-Enthalpy Method on the indoor side shall be used in the calulations in section 5.2.



### 4.2.1.1 Testprocedurefor high temperature test. When the outdoor AirEnthalpy Method is used. the outdoor chamber must not interfere with the normal air circulating pattern during the preliminary test. Itis necessary to determine and adjust for system resistance when the outdoor air measuring apparatus is attached to the outdoor portion ofthe unit. The testroom apparatus and test units must be operated for atleast one hour with at least ¥.l hour at equilibrium and at the specified test conditions prior to starting the test. The High Temperature Test shall then be ;:;onducted for

a minimum of¥.l hour with intermittent data being recorded at lo-minute intervals. For all units. especially those having controls which periodically cause the unit to operate in defrost mode. attention should be given to prevent defrost during the High Temperature Test. Units which have undergone a defrost should operate in the heating mode for at least 10-minutes after defrost termination priorto the start ofthe test. When the outdoorAir-Enthalpy Method is used as a second test then a preliminary testmust be conducted for a minimum of 30 minutes with 4 ormore sets ofdata recorded at 10 minute intervals. all remaining requirements of Section 3.6.1 in the ASHRAE Standard 37-78 shall then apply in conducting the preliminary testfor the outdoor air enthalpy method. For some units. at the ambient condition ofthe test. frost may accumulate on the outdoor coil. Uthe supply air temperature

or the difference between the supply air temperature and the indoor air entering temperature has decreasedby more than 1.5 0 F at the end ofthe test. the unit shall be defrosted and the test restarted. Only the

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results ofthis second High Temperature Test shall be used in the heating seasonal performance calculation in section 5.2. Prior to beginning the High Temperature Test. a unit shall operate in the heatingmode for at least 10 minutes after defrost termination to establish equilibrium conditions for the unit and the room reconditioning apparatus. The High Temperature Test may only begin when the test unit androom conditions are within the test condition tolerances specified in Section 6.2.1 of this Appendix.



### 4.2.1.2 Testproceduresfor the cyclic test. The cyclic test shall follow the High Temperature Test and by cycled "on" and "ofP' as specified ifl 3.2.1.2 until steadily repeating ambient conditions are achieved for both the indoor and outdoor test chambers. but for not less than 2complete "off"/"on" cycles. Without a breakin the cycling pattern. the unit shall be operated through an additional "off'/"on" cycle. during which the required test data shall be recorded. During the last cycle. which is referred to as the test cycle. the indoor and outdoor test room ambient conditions shall remain within the tolerance specified in section 6.2.2. ofthis Appendix. If. prior to the High Temperature Test. the unit underwent a defrost cycle to rid the outdoor coil ofany accumulated frost. then prior to cycling the unit "off' and "on" it should be made to undergo a defrost. After defrost is completed and before starting the cycling process. the unit shall be operated continuously in the heating mode for a least 10 minutes to assure that equilibrium conditions have again been established for the unit and the room conditioning apparatus. Cycling the unit may begin when the test unit androom conditions

are within the High Temperature Test condition tolerances specified in section 6.2.1 ofthis Appendix. Attention should be given to prevent defrost after the cycling process has begun.



### 4.2.1.3 Testproceduresfor thefrost accumulation test. The defrost controls shall be set at the normal settings which most typify those encountered ill Region IV as described in section 6.2.4 and 6.2.5 ofthis Appendix. The test room reconditioning equipment and the unit lh,der test shall be operated for at least lh hour prior to the start ofa "preliminary" test period. The preliminary test period and the test period itselfare to be conducted within the test tolerances given in section 4.2.3.3 ofthis Appendix. In some cases. the preliminary defrost cycle may be manually induced. however. it is important that the normally operating controls govern the defrost termination in all cases. For units containing defrost controls which are likely to cause defrost at intervals less than one hour when the unit is operating at the required test conditions. the preliminary test period shall start at the termination ofa defrost cycle which automatically occurs and shall end at the termination ofthe next automatically occurring defrost cycle. For units containing defrost controls which are likely to cause defrost at intervals'exceeding one hour when operating at the required test condition. the preliminary test period conslsts of "heatingonly" preliminary operation for at least one hour, after which a defrost may be manually or automatically induced. The test period then begins at the termination ofthis defrost cycle and ends at the termination ofthe next automatically occurring defrost cycle. Ifthe unit has not undergone a defrost after 12 hours, then the tests shall be concluded and the results calculated for this 12-hourperiod. For units which turn the indoor fan offduring defrost the indoor supply duct shallbe blocked during all defrost cycles to prevent natural or forced convection through the indoor unit. During defrost. resistance heaters normally installed with the unit shallbe prevented from operating.



### 4.2.1.4 Testproceduresfor the low temperature test. Where applicable, the High Temperature Testpreparation and performance requirements shall also beused in the Low Temperature Test. The testroom reconditioning equipment shall first be operated in a steady-state manner for atleast one-halfhour at equilibrium and at the specified test conditions. The unit shall then undergo a defrost. either automatic or manually induced. Itis important that the unit terminate the defrost sequence by the action ofits own defrost controls. The defrost controls are to remain at the same setting as specified in 4.2.1.3. At a time no earlier than 10 minutes after defrost termination. the test shall start. Test duration is one-halfhour. For all units. defrost should be prevented during the one-halfhour test period.



### 4.2.2 Test instrumentation. 4.2.2.1 Test instrumentationfor thehigh temperature test. The indoor air flow rate shall be determined as described in Section 7.1 through 7.4 ofASHRAE Standard37-78. This requires the construction ofan air receiving chamber and discharge chamber separatedbypartition in which one or more nozzles are located. The receiving chamberis connected to the indoor air discharge side of the test specimen through a short plenum. The exhaust side of the air flow rate measuring device contains an exhaust fan with some means to vary its capacity to obtain the desired external resistance to air flow rate. The exhaust side is then left open to the test room or is ducted through a conditioning apparatus and then back to the test specimen inlet. The static pressure
across the nozzles. the velocity pressure. and the static pressure measurements at the nozzle throat shall be measured with manometers which will result in errors which

are no greater than ±1.0percent ofindicated value and having minimum scale divisions not exceeding 2,0 percent ofthe reading. Static pressure and temperature measurements must be taken at the nozzle throat in order to obtain density ofthe air. The areas ofthe nozzles shall be determined by measuring their diameter with an error no greater than ±0.2percent in four places approximately 45 degrees apart around the nozzle in each oftwo places through the nozzle throat. one at the outlets and the others in the straight section near the radius. The energy usage ofthe compressor. indoor and outdoor fan. and all other equipment components shall be measured with a watthour meter which is accurate to within ±O.5 percent ofthe quantity measured. Measurements ofthe air temperature entering andleaVing the indoor coil or the difference between these two shall be made in accordance with the requirements of ASHRAE Standard41 part 1. These temperatures shallbe continuously recorded with instrumentation having a total system accuracy within ±0.3° F ofindicated value and a response time of2.5 seconds or less. Temperature measurements are to be made upstream ofthe static pressure tap on the inlet and downstream ofthe static pressure taps on the outlet. The indoor and outdoor dry-bulb temperatures shall be continuously recorded with instrumentation which will result in an errorno greater than ±0.3° F of indicated value. The outdoor wet-bulb temperature shallbe continuously recorded. Staticpressure measurements in the ducts and across the unit shall be made in accordance with Section 8 ofASHRAE Standard 37-78 using equipment which will result in an error no greater than ±0.01 inch ofwater. Static pressure measurements shall be made andrecorded at 5 minute intervals. All other data not continuously recorded shall be recorded at 10 minute intervals.



### 4.2.2.2 Test instrumentationfor the cycling test. The air flow rate during the onperiod ofthe Cyclic Test shallbe the same agreed within ±1.percent as the air flow rate measured during the previously conducted High Temperature Test. All other instrumentationrequirements are identical to 4.2.2.1 ofthis Appendix.



### 4.2.2.3 Test instrumentationfor thefrost accumulation test. The air flow rate for the Frost Accumulation Test shall be the same as described in 4.2.2.1. The indoor-side dry-bulb temperature and outdoor-side dry-bulb temperature shall be continuously recorded with instrumentation having a total system accuracy within ±0.3° F ofindicated value. The outdoor dew point temperature shall be determined with an error no greater than ±0.5° F ofindicated value using continuously recording instrumentation. All other data shallbe recorded at 10 minute intervals during the heating cycle. Defrost initiation, termination and complete test cycle time (from defrost termination to defrost termination) shall be recorded. Defrost initiation is defined as the actuation (either automatically or manually) ofthe controls normally installed with the unit which cause it to alter its normal heating operation in order to eliminate possible accumulations of frost on the outdoor coil. Defrost termination

occurs when the controls normally within the unit are actuated to change from defrost operation to normal heating operation. Provisions should bemade so that instrumentation in capable ofrecording the cooling done during defrost as well as the total electrical energy usage during defrost. These data and the continuously recorded data needbe the only data obtained during defrost.



### 4.2.2.4 Test instrumentationfor the low temperature test. Instrumentation for the Low TemperatureTest is identical to that ofthe High Temperature Test described in section 4.2.2.1 ofthis Appendix.



### 4.2.3 Test tolerances. 4.2.3.1 Test tolerancesfor the high temperature test. All tests shall be conducted within the tolerances specified in Section 6.2.1. Variation greater than those given shall

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invalidate the test. The heating capacity results by the indoor AirEnthalpyMethod shall agree within 6 percent ofthe value determined by any other simultaneously conducted capacity testin orderfor the test to be valid.



### 4.2.3.2 Test tolerancesfor the cyclic test. The test condition tolerances andtest operating tolerances for the on-period portion ofthe test cycle are specified in Section 6.2.2. Variation exceeding any specified test tolerance shall invalidate 

### the testresults.



### 4.2.3.3 Test tolerancesfor thefrost accumulation test. Test condition and test operating tolerances for FrostAccumulation Tests are specified in Section 6.2.3. Test operating tolerances during heating applies when the unit is in the heatingmode. except for the first 5minutes after the termination of

a defrost cycle. Testoperating tolerance during defrost applies during a defrost cycle and during the first 5minutes after defrost termination when the unit is operating inthe heatingmode. In determining whetherthe test condition tolerances are met. only the heating portion ofthe test period shallbe usedin calculating the average values. Variations exceeding the tolerances presentedin Section 6.2.3 shallinvalidate the test.



### 4.2.3.4 Test tolerancesfor the low temperature test. During the testperiod for the Low Temperature Test. the operating conditions shallbe within the tolerances specified in Section 6.2.1 ofthis Appendix.



### 4.3 Testingpraceduresfor airsource units whichpravide both heating andcooling. The testing procedures for units which provide bothheating and cooling shall be the

same as those specified in Sections 4.1 and 4.2 ofthis Appendix. Also during the offperiod ofthe dry-coil cooling test (test D). the switch-over valve shallremain in the cooling mode. unless the controls normally supplied with the unit are designed to reverse it. in which case the controls shall operate the valve. During the off-period ofthe cyclic heating test at47· F. the switch-over valve shallremain in the heating mode. unless the controls normally supplied with the unit are designed to reverse it. in which case the controls shall operate the valve.



### 4.4 Testingproceduresfor watersource units whichprovide both heating andcooling. (Reserved)



### 5.0 Calculationsforperformancefactors. 5.1 Calculations of seasonalenergy efficiencyratios (SEER) in air-source units.

The testing data andresults required to calculate the seasonal energy efficiency ratio (SEER) in Btu's perwatt-hour shallinclude the following:

(i) Cooling capacities (Btu/hr) from tests A andB and. ifapplicable. the cooling capacity (Btu/hr) from test C and the total cooling done from testD (Btu·s). 

## Q

..k (95F) 

## Q

..k (82F) Q..,dry QeyCO dry

.

(ii) Electrical powerinput to all components andcontrols (watts) from tests A. B. and ifapplicable the electrical power Input to all components and controls (watts) from test C and the electrical usage (watthour) from test D. 

## E,.k (95F) 

## t

..k (82F) 

### E,.k. dry 

### E.,... dry

(iii) Indoor air flow rate (SCFM) and externalresistance to indoor air flow (inches ofwater).

(iv) Airtemperature (" F) Outdoor dry bulb Outdoor wetbulb Indoor drybulb Indoor wet bulb

.

Where thepooling capacities

# o..k (9qF). from test A. 

## 0..k (82). from test B. and

## 0... dry. from test C. are calculatedusing the equations specified in section 3.7 ofASHRAE Standard 37-78. The total cooling done. QeyCO dry from test D. is calculatedusing equation (1) below.

Units which do not have indoor air circulating fans furnished as part ofthe model shall have their measuredtotal cooling capacities adjusted by subtracting 1250 Btu/ hrper 1.000 CFM ofmeasured indoor airflow and adding to the total steady-state electrical powerinput 365 watts per 1.000 CFM of measured indoor airflow.

Energy effiCiency ratios from tests A. B. and 

### C. EER A• EERs. 

### EER... dry respectively.

are each calculated as the ratio ofthe total cooling capacityinBtu/hrto the total electrical powerinputin watts.

Units which do nothave indoor air circulating fans furnished as part ofthe model shall adjust their total cooling done and energy used in one complete cycle for the effect ofcirculating indoor air equipment power. The value to be used for the circulating indoor airequipment power shall be 1250 Btu/hrper 1.000 CFM ofcirculating indoor air. The energy usage required in one complete cycle required for indoor air circulation is the product ofthe circulating indoor airequipment power and the duration oftime in one cycle that the circulating indoor air equipment is on. The total cooling done shall then be the measured cooling in

one complete cycle minus the energy usage required for indoor aircirculation in one complete cycle. The total electrical energy usage shall be the sum ofthe energy usage required for indoor air circulation in one complete cycle and the energy usedby the re.maining equipment components (compressor(s). outdoor fan. crankcase heater. transformer(s). etc.) in one complete test cycle.

Energy efficiency ratio from tests D. EER""" dry is calculated as the ratio ofthe total cooling done in Btu's to the total electrical en.ergy usage in watt-hours.

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The results of the cyclic and steadystate dry-coil performance**te~ts** shall be used in the following (4) equatlOns:

(1) 60XVXC""xr QCY•. drY [V,,'

### X (1

# +W

..)J

where



### Q",. d,.=Total cooling over a .cycle consisting of one compressor Hoff" penod and one compressor

. "on" period (Btu's). 

### iT=Indoor air flow rate (clm) at the dry-bnlb temperature, humidity ratio, and pressure existing in the region ofmeasurement.

. Cp.=Specific heat at constant pressure of 8!1'- water mixture per pound of dry wr, (Btu/lb-OF).

. . V.'= Specific volume of air-water mIXture at the

. same dry-bnlb temperature, humidity ratio,

and pressure nsed in the determination of the indoor air flow rate (fta/lb). W.=Humidityratio (Ib/lb). and 

## r (hr.-OF), which is described by the equation: (2)



### r = f(time indoorfan off) [T.l(t)

- Ta2 (t)]dt 

## J(time indoor fan on)
where

T.i(t)=Dry bulb temperature of air entering the indoor coil (OF) at time (t). T.,(t)= Dry-bulbtemperature ofairleaving theindoor coil (,F) at time (t). (3) CLF= QcYC.d!:!.. 

### Q

•• dryX

.. where CLF=cooling load factor. Q

.. d,.=Totalsteady-statecoolingcapacityfrom test C (Btu/hr). T=Duration of time (hours) lor one complete

cycle consisting of one compressor "on" time and one compressor "ofi''' time.

The preceding equations are then used in the following equation to calculate a degradation coefficient CD rounded to the nearest .01.



### (4)

where 1 EERcyo.dry EER

... dry 1-CLF

EER".dry=Energy efficiency ratio from test C, (BtU; watt-hr). 5.1.1 Method for caiculating a SEER for units with single-speed compressor and single-speed condenser fans. The seasonal energy efficiency ratio for units employing single-speed compressors and single-speed condenser fans shall be based on the performance of test B and a method outlined in 2.1.1 and 3.1.1 of this Appendix to account for the cyclic performance.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER=PLF(0.5) XEERB
where EERB=Energy efficiency ratio determined from test B as outlined in 2.1.1. PLF(O.5) = Part-load performance factor when cooling load factor=O.5 as determined from the equation: PLF(0.5) 

### = 1-0.5X CD where

CD=Is the degradation coefficient described in 2.1.1 or as calculatedin equation (4) above.

5.1.2 Method for calculating a SEER for units with Single-speed compressors and multi-speed condenser fans. The seasonal energy efficiency ratio (SEER) for units employing single-speed compressors and multi-speed condenser fans shall be based

on the energy efficiency ratio obtained for test B and the method outlined in 2.1.2 of this Appendix to account for the perform-
ance under cyclic conditions. The energy efficiency ratio for test B is obtained with the unit operating with the condenser fan speed which normally occurs at test B ambient conditions.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER=PLF(0.5)

### X EERB
where EERB=energy efficiency ratio determined from test B in2.8 PLF(O.5)=Part-load performance factor as determined from the equation:
PLF(0.5) = 1-0.5X

### 0 D where

CD=The delll'l!.datlon coefficient described in 2.1.2 or as calculatedinequation (4) above. 5.1.3 Method for calculating a SEER for units with two speed compressors or two compressors, or cylinder unloading. The calculation procedure described in this section shall be based on the performance of test A and B at each of the compressor speeds for two-speed compressor units, subject to the conditions on condenser fan speed described in 3.1.3.

Units operating with two compressors shall have the SEER calculated in the same manner as two-speed compressor units. The superscripted index k=l (and the term "low-speed") designates the com- pressor that normally operates at an outdoor dry-bulb temperature of 82° F and k=2 (and the term "high speed") denotes operation with both compressors.

In order to evaluate the steady-state capacity Q

..**~(** 

### T j}, and power input, E••k( Tt}, at temperature T j for each compressor speed, k=l, k=2, the results of tests A and B from 5.1 shall be used in the following equation: Q.8T;)=Q

.. k(95 F) 

# +Q

..

### ~ (82

### !~=~:/ (95 F) [33- (5Xi)]

where

Q

..>(95 F)= Steady-state capacity measured from test A as outlined in 2.1.3. Q">(82 F)= Stef¥ly-state capacity measured from test B as outlinedin2.1.3.

E

..k( Ti } = E

.." (95 F)



# +E

..k (82 F)

- 

### E.," (95 F) [33- (5X .)] 95-82 J
when

E

..'(95 F)=Electrical power inpnt measured USing test A as outlined in2.1.3.

E

..' (82 F)= Electrical power input measured from using test A asoutlined in 2.1.3. The bnilding cooling load BL (T;) for the four cases described in section 5.1.3.1 through 5.1.3.4 shall be obtained from the following equation: BL(T )=(5Xi)-3 XQ!·=' (95 F) I 95-65 1.1
where

Q"

.....(95 F)=Steady-state capacity measured from test A in 2.9 at the high compressor speed.

. The value of the degradation coefficient Ot=l for low compressor speed cycling and 

## ct-· for high speed on/off compressor cycling is determined as described in section 2.1.3, or as calculated above in equation (1). 5.1.3.1 Units operating atlow compressor speed (k= 1) for which the steady-state cooling capacity, (f..-l (T j), is greater than or equal to the building cooling load, BL ( T j), evaluate the following equations:

Xk-I BL(T;} (f..-l( 

### Ti) (1)
where Xk-,=Loa!l factor.

B L(Tj) =Bnlldingcooling load (Btu/hr) attempera- ture (Tj) from section 5.1.3.
Q

... -i(Tj)=Steady-state cooling capacity (Btulhr) at tamperatures (Ti) from section 5.1.3.

(2) Q<;'j}=Xk=lX(f..-l(Tj)X!jJ

where

Q<;;i)

# = ratio of total cooling (Btu) in temperature binjto the number oftemperaturebinhours.
Ui is the fractional number of hours in temperature 

### N binj from 6.1.2.

(3)

where**~~** 

### . ..

"]i{"

# = ratiOofEnergyusage (watt-hr.)m temperature binj to the number oftemperaturebinhours.
PLFk-I=1-Ct- 1 (1-Xk=l).
Where CD the degradation coe.fficient as described in section 2.1.3 or as calculated above in equation (1)

.. 5.1.3.2 When a unit must alternate between high (k=2) and low (k=l) compres- sor speeds to satisfy the building cooling load at a temperature 

### Ti, evaluate the following equations:
(1) Xk-I= Q!,-'(Tj)-BL(Tj) (f..='( T;)_(f..-i( T;) (2) Xk-2=I-Xk-1

(3) Q<;'j)=[Xk-IXQ".;l(T;)

+Xi:-2X

### Q~._2( T;)]

### X~
(4)

### E<Ji)=[Xi:-IXE~.~l(T;) +Xk-2X

### E!;'(Tj)]X~

5.1.3.3 When a unit must cycle on and off at high compressor speed (k=2) in order to satisfy the huilding cooling load at a temperature 

### Ti, evaluate the equa- tions provided in section 5.1.3.1 replacing (k=l) data with the (k=2) data. 5.1.3.4 When a unit operates continuously at high compressor speed (k=2) at an outdoor temperature Ti evaluate the following equations:

(1) Q<;i)=lf..-2 (T i)Xj}

(2) E<J;)

## =E~;'(T;)

# xiJ

## 76714 Federal Register 

# I Vol. 44, No. 249 

# I Thursday, December 27,1979 

# I Rules and Regulations

5.1.3.5 Calculate the SEER in Btu'sj watt-hr. using the values for the terms

and Q(T;) 

## !r
E(T;) 

## lr

as determined at each temperature bin according to the applicable conditions described in sections 5.1.3.1 through 5.1.3.4

as follows: 

# ±Q(T;)
. 1 N SEER

## =""J=,-=--

__ 

# ± E(T;) j=l N

5.1.4 Method for calculating a SEER for units with two speed compressor, two com- pressor or cylinder unloading capable of varying the sensible to total capacity (SjT) ratio. Multi-speed compressor and twospeed compressor units capable of varying the sensible to total capacity ratio (SIT) shall have the seasonal energy efficiency ratio determined as described in section 5.1.3. For such units, the mode of operation selected to determine the steady-st.ate capacities 

### Q

..k(95), 

### Q••k(82), E••k(95), E

..k(82), and power inputs at each com- pressor speed k=l, k=2, for tests A and B. is outlined in section 2.10.



### 5.2 Calculation of Heating Seasonal Performance Factors (HSPF) for AirSource Units. The testing data and results required to calculate the heating seasonal performance factor (HSPF), in Btu's per watt-hI', shall include the following: (i) Hcating capacities (Btu/hI') from the indoor air enthalpy method fOl the High Temperature Tests, and the total heating done (Btu's) for the cyclic and frost accumulation tests.



### Q

•• (47) or Q.3(62). Qs.(17). Qcyc(47). QDEF(35). (ii) Electrical power input to all com- ponents (watts) for the steady state tests, and the electrical usage (watt-hours) for the cyclic and frost accumulation tests



## E

••(47) or 

## E•• (62). 

### E

••(17). Ecyc(47). 

### EDEF(35). (iii) Indoor air flow rate (SCFM) and external resistance to indoor air flow (inches of water). (iv) Air temperature (OF) Outdoor dry bulb Outdoor wet bulb or dew point Indoor dry bulb and Indoor wet bulb. (v) Data as specified in Table II of ASHRAE Standard 37-78. Where the heating capacities 

## Q ••(47)
, 

## Q

.. (62) and 

## Q

.. (17) and the indoor air flow rate are calculated using the equations specified in section 3.8.1 and 7.4 of ASHRAE standard 37-78. The total heating done, QeYc(47) and Q(DEF35) are calculated using the equations below. Units not having an indoor fan as part of the model tested shall add 1250 Btu/hr per 1,000 SCFM of indoor air handled to the measured capacity to obtain the total heating capacity, 

### Q ••(17), 

## Q ••(47) or 

### Q

•• (62), and add 361) wattsper 1,000 SCFM of indoor air handled to the measured power to obtain the total power input, 

## E

••(17), 

## E ••(47)
, or 

## E ••(62), to the unit.

The coefficients of performance (COP) for the High Temperature Tests COP••(62)

or COP••(47), and Low Temperature Test, COP

..(17), are calculated as the ratio of the heating capacity in Btu/hI' to the product of 3.413 and the power inputs to the indoor fan in watts and the power inputs to the remaining equipment com- ponents (including all controls) in watts.

Units which do not have indoor air circulating fans furnished as part of the model shall have their total heating done (Qcyc(47» and energy used Eeyc(47) in one complete cycle adjusted for the effect of circulating indoor air equipment power. For units tested without an indoor fan as part of the model, Qoye(47) shall be increased by a quantity of heat equal to the product of 1250 Btujhr per 1,000 SCFM, the length of the on-period of the test cycle in hours, and the flow rate of indoor air circulated in units of 1,000 SCFM. The total energy usage, E eyo(47), shall be the
sum of the energy usage required for air circulation during the test cycle and the energy used hy the remaining equipment components (including all controls) during the test cycle. Units not having an indoor fan as part ofthe model tested, shall set the energy required for indoor air circulation equal to the quantity given by the product of 365 watts per 1000 SCFM, the length of the on-period of the test cycle in hours, and the rate of indoor air circulated in units of 1000 SCFM.

The cyclic coefficient of performance, COP.yc(47) is calculated as the ratio of the total heating done (Qeyc{47» in Btu's to the product of 3.413 Btu/watt-hour and the totalenergy usage (Eoyc(47» in watt hours. The net heating· capacity, QDEF(35) (Btujhr), is the total net heating done

over the test period (including any credit for the indoor fan heat) divided by the total length of the test period, in hours. For units with "demanddefrost control system", the net heating capacity, QDEF(31), shall be multiplied by an enhancement factor of 1.07 to compensate for improved performance not measured in the Frost Accumulation Test. For units tested without indoor fans, the value determined for QDEF(35) below shall he increased hy a quantity of heat equal to the product of 1250 Btu/hI' per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor air circulating, and the average flow rate of indoor air circulated in units of 1000 SCFM.

The totaJ energy usage, EDEF(35) shall he the sum of the energy usage required for indoor-air circulation during the test period and the energy used hy the remaining equipment components during the test period. Units not having an indoor fan as part of the model tested, shall set the energy required for indoor ail' circulation equal to the quantity given hy the product of 365 watts per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that thel'e was indoor air circulating, and the average flow rate of indoor air circulated in**~mits** of 1000 SCFM.

The actual heating done during the CYClic Test, QCY.(47), shall be determined using the following equation:

(1) 

### 60X'VXC".xr Qcyc(47) = [V"l X (1+

### W

..)] where


### 'iT

=the flow rate during the on-period calculated in

accordance with section 7.4 ofASHRAE Standard 37-78 in CFM. Cp.=Specific heat at constant pressure of air-water mixture per pound of dry air, (Btujlb-OF). Vn'=Specific volume ofair-water mixture at the same dry-bulb temperature, htunidity ratio, and pressure nsed in the determination ofthe indoor air flow rate (ft3jlb). Wn=Humidity ratio (lbjlb). and 

## r (hr-OF), which is described by the equation: 

# f

(time indoor fan off) 

## r= [T a2 (t) (time indoorfan on) where

Ta,(t)=Dry-bulb wmperatnre of air entering the indoor coil 

## e F) at time (t). Ta2(t)=Dry-bulb temperature of air leaving the indoor coil ("F) at time (t). The net heating, QDEF (35) in Btu's done during the test period shall be determined using the following equation:

(2)

where 

### 60X'VXC"axr [V"lX (1+ W,,)]



### 'iT=the average ofthe air flow rate calculated at fOllr
or more time intervals throughout the heating phase of the test using the equation in section 7.4 ofASHRAE Standard 3i-78. Cp.=Specific heat at constant pressnre of air-water mixtnre per pound ofdry air, (Btu/lb-OF). Vn 1=Specific voltune ofair-water mixture at the same dry-bulb temperature, humidity ratio, and pres- snre used in the determination of the indoor air flow rate (ft3jlb). W.=Humidityratio (lb/lb). and 

## r (hr.-OF), which is described by the equation: 

# f (tlme ofnext defrost termination) 

## r= (time ofdefrost termination

where

T.'(t)=Dry·bulb temperature of air entering the indoor coil (OF) at time (t). T.'(t)=Dry-bulb temperatureofairleaving theindoor coil ("F) at time (t).
The cyclic degradation coefficient shall be calculated as follows:

(3)

where 1 COP cyo(47) 

### COP,,(47) 1-HLF

CD=thecyclicdegradationcoefficientrounded to thenearest .01
COP Cyc(41) as dermed above
COP

..(41) as defined above
HLF is the heating load factor calculated as follows:



### HLP QOyo(47) 

## Q

••(47)XT

### Federal Register 

# I Vol. 44, No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations 

## 76715

where

Q,,,(47) as defined above Q,,(47) as defined above

T= Duration of time (hour,) for one complete

cycle consisting ofone. conlpressor "on" time and one cornpressor "off" time.
5.2.1 Calculation of the heating seasonal p('rformance fact.or (HSPF) for air-

source hoat pumps with single "peed compressors. For each climatic region listed in section 6.2.4 ano for design heating requirements equal to both the stl1ndnrdized minimum and maximum design heating requirements defined below, calClllate the HSPF defined

as: HSPF

where

### ~

# j;j BL(T j)
J

[ n· X( T)

.**~N** PLF(X) Ii(Tj)E(Tj)(T j )


# +L: RH(T;)] j N

j=1,2,3, •.•• , n corresponds to thej'b tempera.

ture bm. n=total number of non·zero temperature bins

in the climatic region. T;= (67-5;) is the representative temperature of thej'hbin, (OF)..

. l:=indicated the quantIty followmg the symbol ; is to be summedover all temperature bins. RH(T;)=snpplemenlary resistance heat term at

N temperature T; requiredinthosecases where the heat pump automatically turns off (T;< To") or when it is needed to meet the balanceofthebuilding heatingrequirements

.

### .':'.!=&";,'r:~;'mber ofhoursinthej,h temperature N bin dividedby N=l:. niand is referred to as the "fractionalhours'inj'btemperaturebin". 3.413=is a conversion factor which converts watt hours to Btu. BL(T;)=building load at temperature Tin (Btu/hr).

o(T;)=heat pump low temperature cut-out factor. XL T;)=heat pump heating load factor. PLF(X)=heatpump part load factor.

The quantities BLCT j)
, 6(T j ), X (T j ) , PLF(X) and RH(T;) N

are defined by the following equations:
BUT;)=( 65-T; )(C)(DHR) 65-ToD

where (C)=0.77 is a correction factor which tends to improve the agreement between calculated andmeasuredbuilding loads (DHR)=the minimum and maximum designhea,ting requirement which the heat pump IS Illtely to encounter when installed in a residence, rounded offtothenearest standardized DHR in section 6.26 in Btu/hr where (minimum design heating requirement)

{ . (65-ToD) f . I

Q

..(47) 60 ,or regIons
,



## = II, III, IV, and 

### VI 

### Q

..(47), for region V and
maximum design heating requirement

( . (65- 

### TOD) •

_ 2Q,.,(47) 

### --"-60--' for regIOns 

### I,



### - II, III, IV, and 

### VI
2.2Q,,(47), for region V
where



### ¢,,, (47) is the heat. pnmp capacity measured during the High Temperatme Test @ .170 F
TOD is the outdoor design ten1perature given in section 0.2.4



### 0;**Ti~ToFF** or Q(T i) <1 (3.413)(E( Ti»

and Q(T i) 

### >1 (3,413)(E(T;»

- 1; 

### Ti>T oN and

## Q(T~) >1 (3.413)(E(T;»

-

X(T i)= Q(T;) I Q(T;)?:,BL(T;) 

# I BL (

### Ti)

..

1; 

### Q( Tj )**~BL(** Ti) PLF(X)=I-C D(l-X(Tj»

RH(T i) N
where . n' [BL(T;)-Q(Tj)X(T;)Ii(T i)]

# N

3.413

TOFF=the outdoor temperatnre that the compressor is automatically shut off at (If no such tempera- ture exists, T; is always greater than Toft· and TON.) TON=the outdoor temperatnre that the compressor is automatically turned on (if applicable) if designed for low temperature automatic shutoff. Co=degradation factor determined described in section 5.2 aud 2.2.1.
In using the above equation to calculate HSPF, the heat pump capacity in Btu/hr, 

### Q, and the power in watts, 

## E, shall be obtained as follows:

E(T i)= (Q

..(47)-Q

..(17»

. X(T;-17) 

### Q,,(17)+

## -----::c 3""0"-'--'--...:.
,

(QDEF(35) 

## -Q••(17» Q,,(17) 

# +**1~(T;-17),**

17°F<Ti<45°F

(Ess(47) -E••(17»



### . X(Tj 

### -17) E••(

### 17)**+---....,3:::.,0~-'---'-'** Ti?:,45°F or**Tj~17°F** 

## (EDEF(35)

- 

## E ••(17» 

## E

•• (17)

# +**~(T;-17),**
17°F< Ti <45°F where Q••(47) and 

### E

..(47) and QDEF(35) and 

### E•• (47) and 

## Q

..(17) and 

### E

..(17) are the capacities (in Btu/hr) and powers (in watts), measured during the High Temperature Test, the Frost Accumulation test, and th€. Low Temperature Test, respectively.
Once the maximum and minimum HSPF and operating cost values have heen obtained for each region, the HSPF anrl operating cost shall be determined for each standardized design heating requirement (see section 6.2.6) between the maximum and minimum design heating requirements hy means of interpolation. 5.2.2 Calculation of the heating seasonal performance factor (HSPF) for air

source heat pumps with a two-speed compressor, two compressors, or cylimler unloading. For each climatic region listed in section 6.2.4, anrl for design heating requirements equal to hoth the standardized minimum and maximum design heating requirements defined below, calculate the HSPF defined

as:

### ~!jJ BL(T j) HSPF J

where

1; as defined in 5.2.1 j**~** as defined in 5.2.1
T; as defmed in 5.2.1

and BL(T i) is thE' huilding load at temperature Ti, in Btu/hI', calculated by:

BL(T j )

## =(6~5~**:£~)** X (C) X (DHR)

where (C)=0.77 is a correction factor which tends to improve the agreement between calculated and measuredbuilding loads (DHR)=the minimum and maximum design heating requirement which the heat pump is likely to enconnter when installed in a reSidence, rounded off to the nearest standardized DHR in section 6.2.6 in Btu'sper hour where (minimum design heating requirement)

### Q:~.2)(47)**(65~:OD),** for regions 

### I,



## = II, III, IV, and 

### VI**Q\~.2)(47),** for region V

and (maximum design heating requirement)

.. 60' or regIOns
, 

# {2 Q ' k• 2 (47) (65-ToD) f . I

= 

### II, III, IV and 

### VI

2.2<1,;2(47) for region V

where



### Q

.. (k-2) (47) is the heat pump capacity measured duro ing the high temperature performance test at 47°F, with the unit operating at the high compressor speed or with both compressors in operation, in Btn/hr TOD is the outdoor design temperature given in section fl.2.4 in degrees OF.

## 76716 Federal Register / Vol. 44, 

### No.·249 

# I Thursday. December 27.1979 

# I RUles and Regulations

NOTE: 

### The superscript (k=l) 

### and (k=2) 

### refer to the heat pump operating at low 

### speed or single compressor operation and high speed or two compressor operation respectively.

E(T/) is theheat pumpelectricalenergy usageinthe

N ph temperature bin divided by the total number ofbinhours and is evaluated according to the four possible cases of heat pump operation denoted below in watts. RH(Tj) as defined in 5.2.1 and is evaluated according

N tothe four possible cases ofheat pumpopera- tion denoted below (in watts). 

### Case I.-Units operating at low compressor speed or with a single compressor, i.e., k= 

### 1, for which the building heating load, 

### BL(

### Ti) is 

### less than or equal to the heating capacity, Qk=l( Tj ). 

### BL(Tj )**~Qk-l(** Tj ) E(Tj)_Ek-I(Tj)Xk=l(Ti)l/(T i) 

### !Ii 

# -r- PLFk-l 

### N

RH(Ti) 

## !JJ BL(T j)[I-8'(T j))
N 3.413
Xk=l( Tj ) !lL( T j) Qk=l(Tj)**PLFk-l=I_~=l(I-X~=l)**

{ OJ**Tj~** TOFF
8'(Tj)=

## ~;**TOFF<Tj~** TON

1; 

### T;>T oN



### Case H.-Units alternatingbetweenhigh speed or two compressor operation (1:=2) 

### and low sl?eed or single compressor opera- tion (1:= 1) 

### to satisfy the building heating load at temperature T j • (jk=l( T j)< BL( Ti)

# <(jk=2( Ti)
E<J;}

## =[Ek=l( Tj)Xk=l( T j)


# +Ek=Z( Tj)Xk=Z( Ti)]8'(T j ) 

# ';J.

RH(T i) 

# }J BL(Ti)[l-o'(T i}]

N 3.413
ijc=Z(

### Tj }

- 

### BL(

### Tj ) Xk=l(T i} Qk=2( Ti}_(jk=I(Ti)
Xk=Z(T j}= I-X k=l( Ti)

{OJ Tj-$. TOFF
8'(T j )

## ~; TOFF<T j :::, TON


### 1; Tj>ToN 

### Case lIf.-Units cycling 

### on and 

### oil at high 

### compressor speed or cycling both com- pressors on and olI 

### together (1:=2) in 

### order t() 

### satisfy the buildingheating load at temperature 

### T j •

. 

### Qk-1(T,)<BL(T,)<Qt-i(T,)

B(T,)

## Ek-'(T,)X""(T,)a"(2',)~

N PLFt.l.


### RH(T,)

## ~BL(TI)[I-'''(T,)J N 

### 3.413

XPI(T,) BL(T,) 

### Qt-2(T,)**{O;'** 1'1

### ~Tol'I' 

### 1 . a"(T,)- 

## 2;**2'ol'J'<T,~To.**



## . 1; 2',>2'0.

.Case lV.-Units operating continuously. .athigh compressor speed orwith hoth com- pressors in continuous operation (1:=2) 

### in order 

### to satisfy the building heating load at temperature Ti' 

### BL(T,)

### ~Qt-t(f',) E<;'/)

### =EM(T,)X"-*(T,)3"(T,)

# is

RH(T,) 

### N [BL(T,)-QM(f',)X""(T,)a"(f'/»

# jJ

== 3:413 X""(T,)

### =1.0 0;**T/~** Tol'I' 

### Qt-'(T,>==



### <)M(T,) 

# <I

or (3.413)(FJ.t-I(2',» Et-I(T/)=

## ~;**TOI'I'<f',~f'oN.** ""(T ,)

### = ivt-l('l' ) 

### and V'

, 

### >1

. (3.413)(E""(T,» 

### 1;**T,~ToN** 

### and

. 

### Qa-t(T,) >1

. (3.413)(FJ.t-I(T,»-


### Where in each 01 

### the above cases**X(TI)~heat** pnmpheatingloadfactor. PLF

..heat pnmp part loadfactor (notrequired for

_HandIV.) 8"(TI)**~**heatpumplowtemperatnreCnt-ollt factor. 

## T." as defined in5.2.1. T

..as definedin 6.2.1. CDii-2=the part load del!redatlon factor describedIn section 2.2.1 and 5.2 for the nnit eyeling at

. high compre8!lOl' speed or wiUl both c0mpressors S1mnlljl.noonsly cycling (H applica- ble).

. CD(

....' -thepart load del!redatlon factor describedin

. sectIOn 2.2.1 and 5.2 for the nnit cycling at

. lowcompressor speed orwiththesingle com·**~**tba& IIOI'JIiaIly operatesatlow heating 

# e: 1 

### (4"1) 

### (<)::'(62)-<)::'(4'1»


# + X(T,-47). 

### 15 I**Ti~4()Q** 

### F 

# <1-: 1 

### (17)

### (QtB~(35) - 

### <)::'(17»



# + X (T,-17>. 

### 18 ' 

### 17<'**F~Ti<400** 

### F 

# e.-I (17) 

### (<)::1(47)- <>:,-1(17» 

# + X(T,-17). 30 ' T,<17° 

### F 

# e.-O (17) 

# (e.-a (47)- <>:,-'(17»


# + X(T,-I7). 30 '**T,~45°** 

### F or**Ti~17o.** 

### F 

# e.-' (17)**(0B~(35)-** 

## 0.-2(17»



# + X (TI-17),

. 18 ' 

### 17<'F<T,<45° F

E:;"(47) 

## CE!.-'(62)-N,.-1(

### 47»


# + X(T,-47). 

### 15

. I



### H.;'1(17) 

### (EtB"(35)-e..-' (17)) 

# + X(T,-I7).


### 18 • 

### 17<'**F~Ti<4()Q** 

### F E!,-I(17)
(N,.-l(

### 47)

# -e..-1

### (17» 

# + X(T,-17). 

### 30 • 

### T,<17° F 

# e.:'(17) (E!;-I(47)-E:.-(17)) 

# + . X(T

, 

### -17).
30 '**Ti~45°** 

### F or T,-$.17° 

### F b"!.-·(17) (b'tB,-(35)

- 

### E!;"I(17»

. X(TI-I7). 18 ' 

# +

### Federal Register 

# I Vol. 44, No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations

For each of the six regions specified in section 6.2.5, calculate the heating sC>a8onal performance factors and seasonal operating costs corresponding to the standardized maximum and minimum design heating requirements and for all other standardized design heating requiI'ements (see section 6.2.6) between the maximum and the minimum. 5.3 Calculations of the Actual Represenlatitle Regional Annual Performance Factor8 for Air Source Central Air Conditioners (Heat Pump8) Which Provide Both Heating and Cooling. 5.3.1 Calculation of actual regional annual performance factors (APFA) for a particlliar location and for each standardized design heating requirement.

where (CLH A

# Wi••k(95F) ) 

## + (HLH.1 ) (DHR) (C) (CLH A ) 

### (Q.h95F» (SEER) +(HLH A ) (DHR)(C) (HSPF)

(eLHA) is the aetual cooling load honrs for the particular loeatioll, determined from the
• map in S<'<'tiOll 1i.1.3. (Q..k(95F» is defined in 5.1. (DHR) is defined in 5.2.2. (e) is defined in 5.2.2. (HLlIA) is the actnal h..ating load honrs for the particular loeation determined from the map in seetion 6.2.5. (SEER) is the seasonal energy efficiency ratio dctennined in section 5.1. (IlSPF) is the heating seasonal perfonnallce factors
as delennined in section 5.2 for cQ<·h st.andardized design heating reqnirement within the particular location's region or for the sctnal design healing reqniremcnt i! known. where the particular location'R region is determinerl from the map in section 6.2), and, the standardized design h('ating re- quirements within the region are determined in sections 5.2 and 6.2.6. 5.3.2 Calculation of representative re- gional annnal p('rformanee factors (APFR) for ('aeh r('gion and for each standardized design heating re- quirement.
(CLH R) 

### (Q.l(95F» 

## +(HLHR)(DHR) (C) (CLHR ) 

### (Q.l(95F» SEER 

# +(HLH R)(DHR)(C) HSPF (Q.••(95F)) is defined in 6.1. (DHR) is defined in 6.2.2. (e) is defined in 5.2.2. where

(eLHa) Is tbe representative cooling load hours for each heating load hours region, as determined in section 6.3. (HLHR) is tbe representative heating load bours for each region as determined in section 6.2.5. (SEER) is the seasonal energy elliciency ratio as determinedin section 5.1. (HSPF) is the heating seasonal performance factor as determJned in section 5.2 for each region and for each standardized design heating re- quirementwithin each region.
where the regions are listed in section 6.2.5 and, the standardized design heating re- quirements within the regions are determined in sections 5.2 and 6.2.6. 5.4 Calculation8 of Seasonal Energy Efficiency Ratio for Water Source Units Which Provide Both Heating and Cooling. (Reserved)
5.5 Calculation of Heatillg Seasonal Performance Factor for Water Source Ullits Which Provide Both Heating and Cooling. (Reserved) S.6 Calculation of Anllual Performance Factor FOT Water SOllrce Units Which Provide Both Healing alld Cooling. (Reserved)

BILLING COOE 6450-01-M 

### 76717

### CAS-RM-79-102 COMMENT 02

76718 

### Federal Register 

# I Vol. 44, 

### No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations

6.0 Reference Material

6.1 

### Coolinq reference material

6.1.1 -Test operating and test condition tolerance for cyclic dry-coil tests

Readings, remarks

Outdoor dry-bulb air temperature, Fahrenheit: Entering••••••••••••••••••••• Indoor dry-bulb air

temoerature, Fahrenheit: Entering...••••...•....••..•• 

### Indoor wet-bulb air temperature, Fahrenheit: Entering••••••••••••.•••••••• After the 1st 30 Sec after

comnressor startup. External resistance to 3irflow, inches water•••• Nozzle pressure drops, percent of reading•••••••• Electrical voltage inputs to the test unit, percent. Test operating tolerance (total observed

range)

2.0

2.0

(*)



### 0.05 Test condition tolerance (variation of average from specified test condition)

0.5

0.5

(*)



### 0.02

2.0



## .. 

# ....................... 2.0



### .. 

## ........................

* Shall at no time exceed that value of the wet-bulb temperature which results in the production of condensate by the indoor coil at the dry-bulb temperature existing for the air enterina the indoor portion of the unit. 6.1. 2 

### -Distribution of fractional hours in temperature bins to be used for calculation

of the SEER for 2-speed compressor and 2- compressor units

Bin temperature range (degrees Fahrenheit)

Bin No., j:



### 1••••. 65 to 2••••• 70 to 3••••• 75 to 4••••• 80 to 5

..... 85 to 6••.•• 90 to 7••••. 95 to 8••••• 100 to Representative temperature

bin for (degrees Fahrenheit)

69 ••• 67 74 ..• 72 

### 79 ••• 77 84 ••• 82 89 ••• 87 94 .•• 92 

### 99••• 97

104. 102 Fraction of 

### total temperature bin hours n/N

.214 .231 .216 .161 .104 .052 .018 .004

### Alaska Canal Zone Guam Hawaii Puerto Rico Samoa Virgin Island

- 

### CAS·RM·79·102 COMMENT 02

Federal Register 

# I Vol. 44. No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations 

## 76719

0 Cooling 6,000 6,600 2,300 6,000 6,600 

### 6,000 

### (;.1. 

### 3

Load Hours



### ,. 

# .. Distribution of 1\ctual Cooling Load Hours (CLlI1\) Throughout the Uniled States

### CAS-RM-79-102 COMMENT 02

76720 Federal Register 

# I Vol. 44, No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations

6.2 Beating Reference Material

6.2.1 Test operatins and test condition tolerance for

Steadr-State Hish Temperature Test lat 47·, (S.J·C) or 62·' (16.7·C)]

and Lov Temperature Test rat 17·, (-S.3·C)]

Tut Operatin,. Tolerance

Indoor dry-bulb, 

### ·F

Enterills 2.0 Leavins 2.0

Indoor vet-bulb, 

## ·r

EnterillS 1.0 tesvillS 1.0

Outdoor dry-bulb, 

### ·F

Enterins 2.0 teaving 2.0

Outdoor vet-bulb, ·F

Eneerins 1.0 Leaving 1.0

Extlrnal reliltlnce to air flow, inches of vater .05

Electrical volta,e, 

### % 2.0 te.t**Condition.~** Tolerance



### O.S

0.5

0.3

.02



## * Te.t' Operatins Tol.rlnc. i. the maximum permi••able variation of allY measure-

..

nt. When axpre••ed
., a percentage, tha maximum allowable variation i. the lpecified percenta.e of the averas_ Yalue. 

### ** Telt Condition Tolarance is the

..**xi~um** permi.llble vlriltiOll of the average value of the

.... ur

... nt from the .tlndard or de.ired t ••t conditioll. 6.2.2 test..onerating.. IIDd-taat.-.c.ondU.ioG-**to1a~M-Icrr-** 

## t"--

..n-period portion of. c.y.cl.1c.J)'IrfoDlanca...t.aaU.

Indoor dry-bulb,

Ennrins te.vill&

Indoor vet-bulb,

Enter!.ns teaving

Outdoor dry-bulb,

EnterillS te.vill&

Outdoor vet-bulb,

Enter!.n& teavill& 

### ·F

·F

·F



### ·r

Ext.rnal r••i,t.llce to air-flow, iIIeh.. of vac.r
El.ctrical volta,e, % T ••t Operating Tolerance.. Test Condition (Appl1e. after the l.t 

### 30 Toleraneevv ••c. after compressor acart-up)

2.0



### 1.0

2.0

2.0



## .os

2.0 0.5

0.5

1.0



## * T ••t OperltinS Tol.rallce i. the maximus perai••able variation of any me••ure- "lit. Vbell .xpr•••• d a. a percellta.e, the**maxi~** allowable yeriatLolI ia tbe specified percellca,e of tbe averase yalue. 

### ** Teat Condition Tolerlnce ia tbe

.. xi.us permi•• lble variltion of the ayerase .Ilue of the

.... ur

... nt froe tbe Itandard 

### or de.ired te.t condition.

### CAS-RM-79-102 COMMENT 02

Federal Register 

# I VoL 44, No. 249 

# I Thursday. December 27. 

### 1979 

# I Rwes 

### and Regulations 

## 76721

6.2.1 t

.. t I'IperatiDI aDd t ••1: coDd1Uoo colauDe•• for froat**ec~UODt**.. U

Tetting oper.ti"LTot

.... ne

..(l)
Dul'lDI Keatll1l fUll DetroIt

Int.d", Lem",

IDdoo

.... t-1nalb.

... !nt.rl", Lem",

OIICdo07l dr)'-bulb. 

### ·r

IftculDI Lem", 

# OIIt"_ ".-poiDt. 

### ·r 2.0

1.0

2.0

IDtui", 

# 1.' ",mDI

lauf'IIel tr

.. l.ltaaee to .i

...



# n.... iIlcbe. Df

.. ee.. .05

11eeuwl .",lte.e, I 2.0 10.0 Teot Condition Tolerance(%) tHe.U,na portlOft GIl}

0.5

1.0

0.1

.02

1 teet Oper.dDI '1'oleunee it Cbe

..lIi_ peni

... b1. "artatiot! I'If aD,

...... r

... _to Vlura .spre

... d

.. e per.eDual, tb

...... imum aU"".b1. "ariatio" ia tb•• pecified per

.... Us. of tb.

_ ..... 

# "al.... re.t OperaUna Tol.u"u D

....i", Bucina .ppU•• 

# "".0 tba b.ac plllllp it ill tb. ba.d"s

... d

..... eapt for tb. fint
, al.""C" afc

... Carai".dOD I'1f • dafro.t .,cle. T ••t Operati"s TI'11ar

..... Dod

... Deftro.c .pplie. dIIdlll • tiet

..... t CJCl. aDd d

....ioll tbe fir.t
, al.

... t

.. .ft

... tb. t.rai

... cioD Df • deCnee CJCl. wbn tbe beet puIIII i. operatiq ill tbe baacf,1lI_de.
t teet ConditiOD '1'01

........ b tb

... ,,;.- perai

... bl. ".dadoc of tb

.... use ".1

.. Df th

......

# Ir_

..t fir

... tbe ataDdard or d

..ired t.n .O

..di.tiDO. T

.. t CoaditlOll '1'1'11

...... e applle. _1,

... tb. beet puIIII La opeutiol ill che ".CiDI _de. I 10& applicable dur1lll Oef7lO.' U**~M** iAd_ fo U Dff. 6.2.4 'l1atUbuUcm. I'If fra.Uooal hou

... 1

.. tellll>eratun bille, Meticl 11'1ed 11011

... a"d OIItdoor 4

..11D tempereture for the dUf_t c1Smat1c UBi01ll



# - aes1cm. I It III tv
Beat1ftg Load Boun, BLB 750 1250 1750 2250

OUtdoo

.. D.e51gft Temperacuxtl\ TOD for tbe res10ft 37 27 11 S

Frac:tiDoal Boun: 11ft
, T1 (Op)
j • 1 62 .291 .US .153 .132 2 57 .239 .189 .142 .lll 3 52' .194 .163 .138 .103
4 47 .129 .143 .137 .093
S 42 .081 .112 .135 .100
6 37 .041 .088 .118 .109
7 12 .019 .056 .092 .126
8. 21 .005 .024 .041 .087 9 

### n .001 .008 .021 .055
10 1'7 0 .002 .009 .036
11 12 0 0 .005 .028
12 1 0 0 .002 .013
13 2 0 0 .001 .006 14 

# -, 0 0 0 .002
15 -S 0 0 0 .001
18 -13 0 0 0 0
17 -18 0 0 0 0
18 -%3 0 0 0 0

..PacUic: Cont a.g1ft" V VI

2150 

## I 2750·

-10 

# I
30

.106 .113
.092 .205 .MS .215
.076 .204 ;078 .161
.081 .076
.102 .034
.094 .008
.074 .003
.055 0 .041 0
.038 0
.029 0 .018 0

.010 0
.005 0
.002 0
.001 0

# VI CAS-RM-79-102 COMMENT 02

76722 Federal Register 

# I Vol. 44, 

### No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations



### 6.2.5 Actual heating load hours 

### (lILHA ) and regional heating load hours (IILHy( for 

### the United States

2500



# v**~oo**



### 3500



# III**L---T~-,G~~r-1500**

Regional Heating Load Hours
Region**HL~**



### I 

### II 

### III



## IV

V 

## VI 750 1250 

### 1750 2250 

### 2750 2750 nilS 

### map IS 

### reasolliJlJ.., aCClIrale 

## 'Of most pat1S 

### 01 die Unlled Slilles but is 

### Ilecessaritt h'!Jhtt ,generalIZed. iJrd 

### consequenltt /lol too accurate in mounlainous reglOllS, pilrbCulart( in 

### the 

### Aockies. 

## II

Alaska 3500 HLH Hawaii and

- 0 HLH Territories

### Federal Register 

# I Vol. 44, No. 249 

# I Thursday, December 27, 1979 

# I Rules and Regulations



## 6.2.6 Standard Design Heating Requirements (Btu/hr)

5,000 25,000 50,000 90,000

10,000 30,000 60,000 100,000

15,000 35,000 70,000 110,000

20,000 40,000 80,000 130,000



## 6.3 Representative Cooling Load Hours (CLHR ) for Each Heating Load Hours Region

Region CLHR HLHR

I 

## 2400 750

II 

## 1800 1250

III 

## 1200 1750

IV 800 2250

V 400 2750

VI 200 2750

6.4 Ground Water Temperature Mao (Reserved)

[FR Doc. 79-38293 Filed 12-17-79; 8:45 am)

BILLING CODE 6450-o1-C

U. S. GOVERNMENT PRINTING OFFICE: 1980 0 - 308-101 

## 76723

m