CAS-RM-79-102 COMMENT 02

Thursday 

December 27, 1979 

Part III 

Department of 

Energy 

Office of Conservation and Solar Energy 

Test Procedures for Central Air 

Conditioners, Including Heat Pumps 
CAS-RM-79-102 COMMENT 02

76700 Federal Register I Vol. 44. No. 249 I Thursday. December 27,1979 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 of Energy. 

ACTION: Final rule. 

SUMMARY: The D~partment of Energy 

amends its test procedures for central 

air conditioners to include test 

procedures for heat pumps. and to 

modify the existing test procedures for 

other kinds of central air conditioners. 

These test procedures are part of the 

energy conservation program for 

consumer products established pursuant 

to the Energy Policy and Conservation 

Act. Among other program elements. the 

legislation requires that standard 

methods of testing be prescribed for 

covered products. 

EFFECTIVE DATE: January 17. 1980. 

FOR FURTHER INFORMATION CONTACT: 

James A. Smith. U.S. Department of Energy. 

Office of Conservation and Solar Energy. 

Mail Station 2221C. 20 Massachusetts 

Avenue, N.W .• Washington. D.C. 20585. 

202-376-4814. 

William J. 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 of the 

Department of Energy Organization Act 

(DOE Act) (Pub. L. 95-91). The energy 

conservation program for consumer 

products was established by FEA 

pursuant to Title III. Part B of the Energy 

Policy and Conservation Act (Act) (Pub. 

L. 94-163).1 Section 323 (42 U.S.C. 6293) 

of the Act requires that standard 

methods of testing be prescribed for 

covered products. Test procedures 

appear at 10 CFR Part 430. Subpart B. 

Test procedures for central air 

conditioners were originally proposed 

1 Subsequently. 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 of the 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 of the existing test 

procedures for other kinds of central air 

conditioners. A public hearing was held 

on June 13. 1979. at which the proposed 

changes were discussed. 

B. Discussion of Comments 

Comments were received from 

manufacturers. a trade association. and 

interested individuals. The major issues 

raised by the comments are discussed 

below. 

1. Central Air Conditioner Definition. 

One commenter requested clarification 

of the applicability of the 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 

of a 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 of a 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 

of the 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 and is not 

covered by the test procedures in either 

the heating or cooling mode. DOE has 

modified the definition of central air 

conditioner in section 430.2 to clarify the 

treatment of these units in today's fmal 

rule. 

2. Energy Efficiency Measures. 

Several comments were concerned with 

the use of the measures of efficiency 

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 

annual performance factor (APF) as 

measures of efficiency. 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 of the CSPF on the basis 

of present consumer familiarity with the 

SEER concept, and the limited. less 

comprehensible range of numerical 

values of the 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 can be easily compared. 

The Federal Trade Commission (FTC) 

has requested that DOE provide the 

SEER as a measure of efficiency for use 

in the FTC appliance labeling program 

established by section 324 of the Act. 

DOE has reviewed all comments 

concerning energy efficiency measures 

and has made the following changes 

from the proposed rule: 

1. Deletion of the CSPF from section 

430.22(m) (5) and from the test 

methodology in Appendix M. 

2. Retention of the SEER in section 

430.22(m)(5) and section 5.1 of Appendix 

M as the only measure of cooling 

seasonal efficiency. 

3. Alteration of the method of the 

calculation of the HSPF values 

measured in section 5.2 of Appendix M 

to reflect the multiplication of the 

conversion factor of 3.413 Btu's per walthour to result in the same units as the 

SEER. 

4. Revision of the APF calculations in 

section 5.3 of Appendix 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 

section 430.22(m)(5) of today's final rule. 

A final related comment pointed out 

potential problems concerning 

representations of product efficiency 

based upon computations indentified in 

Appendix M but not identified as 

"measures of efficiency" 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 of covered products. but 

regulation of such representations is a 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44. No. 249 I Thursday. December 27, 1979 I Rules and Regulations 76701 

matter relegated to the Federal Trade 

Commission (FTC) by sections 323(c) 

and 333(c) of the Act. 

3. Degradation Coefficient. 

Determination of the degration 

coefficient (Cd. used to quantify the 

cycling performance of central air 

conditioners and heat pumps. is 

necessary in order to evaluate seasonal 

performance. Section 2.1 of proposed 

Appendix M allowed manufacturers to 

test (by performing Tests C and D) to 

determine CD for all basic models that 

they sell or, at manufacturers' option, to 

use an assigned value of CD equal to 

0.25. Many comments were received 

regarding the degradation coefficient. 

These comments pointed out two 

general areas of concern. 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 of the assigned 

degradation coefficient, 0.25. 

Nearly all commenters urged that 

DOE allow actual testing of certain 

models in a product line without 

prohibiting the use of the 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 of effort 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 be justified 

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 

proposed rule, prevent him from 

advertising the higher ratings for other 

models which had been statisfactorily 

tested for CD' 

Some commenters stated that the 

proposed rule would favor the large 

manufacturers who had larger testing 

capabilities, but another commenter also 

objected to any rule which would allow 

manufacturers an option of testing 

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 of 0.25 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 been in effect 

since January 1, 1978, but DOE has 

found no evidence of its occurrence. 

Based on its review of all comments, 

DOE has determined that manufacturers 

of central 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 of heat pumps, the final rule 

clarifies that manufacturers will be 

allowed the option of testing 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 of a unit with two 

compressor speeds, if the 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 of the assigned degradation 

coefficient, 0.25. It should be noted that 

lower degradation coefficients indicate 

higher seasonal efficiency. Two 

commenters stated their belief that the 

0.25 value accurately reflects 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 at Purdue University's 

Herrick Laboratories under the 

sponsorship of the 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 and DOE 

has concluded that available data 

support the assigned 0.25 value for CD' 

which is only slightly higher than the 

mean of the CD values currently known 

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 of CD 

have been made in today's final rule. 

4. Cyclic Test Procedures. 

One commenter disagreed with the 

"on" and "ofr' timp.s specified in Test D 

in section 3.1.1.2 of Appendix M for use 

in measuring the degradation coefficient. 

The commenter submitted data showing 

cycle times for actual field installed 

units in both the heating and cooling 

modes. The data were carefully 

analyzed by NBS and the results were 

compared with predictions made by a 

computerized thermostat model. NBS 

found that the field results provided 

insufficient data to conclude that heat 

pumps typically operate at longer ontimes than was assumed in DOE 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 of cyclic 

degradation. The time constant 

approach is presently under study by 

NBS. While this method may have 

advantages such as simplified 

procedures and reduced test time, the 

tests which thus far have been 

conducted according to this method 

raise doubts about its ability to measure 

accurately the cyclic performance 

degradation for all the different types of 

air conditioners and heat pumps 

presently manufactured. The time 

constant approach to part load 

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 of basic 

models that use the same condensing 

unit, only the condenser-evaporator coil 

combination expected to have the 

largest volume of retail sales must be 

tested. Ratings for other basic models 

could, at manufacturers' option, be 

determined by computer simulation 

methods which would predict the 

performance of other basic models 

consisting of the same condensing unit 

but different evaporator coils. The 

proposed rule 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 of DOE prescribing a 

computer model for use by all 

manufacturers who chose not to rate 

their products by actual testing. 
CAS-RM-79-102 COMMENT 02

76702 Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 

• 

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 requested that 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 of other 

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 of seasonal 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 of models 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 predict the 

performance of any evaporator coil with 

any condensing unit of known 

performance characteristics. If this 

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 of energy 

consumption determined by analysis do 

not agree with measures of energy 

consumption outlined by actual testing, 

the test results shall prevail. 

Consequently section 430.23(m) of 

today's final rule permits ratings of 

condenser-evaporator coil combinations 

to be based upon the results of 

condenser manufacturers' tests of each 

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 that particular 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 if they 

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 used by 

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 of the preamble, 

verification of the accuracy of measures 

of energy efficiency reported for labeling 

of consumer products according to 

today's final rule is the responsibility of 

the Federal Trade Commission (FTC). 

The FTC may decide to determine the 

accuracy of these representations by 

testing certain condenser-evaporator 

coil combinations that were rated by 

simulation methods. In such instances 

the accuracy of the manufacturer's 

simulation methods is of critical 

importance since it is anticipated that 

the accuracy of the representations will 

be judged 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 of central 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 of basic models using the same 

condensing unit, submit to DOE the test 

results used to establish the rated 

value(s) of efficiency for the 

combination likely to have the highest 

sales volume, and a comparison of these 

test results with the system efficiency 

predicted when the simulation method is 

used to determine the efficiency of the 

system with the highest sales volume 

coil. 

If the ongoing NBS efforts succeed in 

developing an accurate computer 

simulation method for predicting the 

performance of condenser-evaporator 

coil combinations, DOE may use this 

technique as an initial screening method 

to determine which manufacturers' 

simulation methods shall be more 

closely inspected. Section 430.23(m)(8) 

has been added to require any 

manufacturer which elects to rate its 

products by simulation methods to 

permit representatives of DOE 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 of the simulation methods 

used, as well as actual performance of 

simulations and comparison of predicted 

results with actual test results. 

Inspections at the manufacturer's site 

are expected to be the most convenient 

and efficient means of verifying the 

simulation methods used. DOE will 

retain the option of requiring 

manufacturers to submit their simulation 

methods to DOE pursuant to the 

authority of section 329 of the Act if this 

is determined in the future to be 

necessary, either in the case of a 

particular manufacturer or for all 

manufacturers which use the simulation 

option. DOE plans to inspect and verify 

by actual testing a significant 

percentage of manufacturer's simulation 

methods each year. 

After thorough review of the 

comments received from manufacturers 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 76703 

who produce only evaporator coils, DOE 

acknowledges the need to provide these 

manufacturers with a method by which 

they can make representations of the 

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 of numerous other 

manufacturers would be burdensome. 

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 of operation and the 

efficiency of these combinations. DOE 

has concluded that an analytical method 

which utilizes computer simulation or 

other engineering analysis to predict the 

performance of these combinations is 

the most accurate alternative to testing. 

The method to predict the performance 

of the condenser-evaporator coil 

combination must be based upon 

condensing unit performance data 

provided by the manufacturer of the 

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 of operation 

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 of the 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. Demand Defrost. Many comments 

were received concerning both the 

definition of "demand defrost" in 

proposed section 1.12 of Appendix M 

and the application of an 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 of demand 

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 of demand defrost should 

be measured by 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 can be 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 of Appendix 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 of a 

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 of a 

heat pump in the heating mode. 

Although this improvement does vary by 

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 7 percent. in order to 

achieve a resultant effect of 4 percent 

improvement in the HSPF for units 

which use demand defrost. 

7. Water Source Heat Pumps. 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 of water 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 study by 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 been reserved. 

8. Dual Voltage Units. In section 3 of 

the proposed rule. DOE required testing 

of central air conditioners at only one 

voltage (either 115V or 230V). which 

was determined to be the typical 

residential voltage for a particular basic 

model. Some comments specifically 

requested that the test procedures 

permit the rating of central air 

conditioners at voltages 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 of Operation. One 

commenter remarked that the heating 

and cooling load hour maps referred to 

in sections 6.1.3 and 6.2.5 of proposed 

Appendix M did not correlate with the 

actual hours of operation 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 

of this program. Therefore, today's final 

rule reflects no changes in the heating 

and cooling load hours. 

10. Estimated Annual Heating Costs 

of Heat Pumps. 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 of 0.77 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 of heat 

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 of the 0.77 correction 

factor. Until further field test data are 
CAS-RM-79-102 COMMENT 02

7'67'04 Federal Register I Vol. 44. No. 249 I Thursday. December 27. 1979 I Rules and Regulations 

available which establish the need for a 

change. the test procedures will 

continue to use the 0.77 correction 

factor .. 11. Sampling Plan. In addition to the 

one-sided sampling plan contained in 

proposed section 430.23(m). the notice of 

proposed rulemaking also solicited 

comments on an alternate sampling plan 

in which testing would have been 

performed on only two units of each 

basic model required to be tested, with 

the mean value of the test results 

forming the basis for product ratings. 

Comments on these two sampling plans 

were divided, with some commenters 

favoring the proposed plan because of 

the more reliable results it would yield. 

and with other commenters favoring the 

alternate plan because it might reduce 

the number of units required to be 

tested. One manufacturer provided data 

which indicated that with four of the six 

models it had tested. testing of two 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 of one 

test. Under this plan. ARI would modify 

an existing industry-supported 

certification and enforcement program 

so that verification of published ratings 

would be done by testing models 

selected under 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 of existing 

models. 

This verification plan as presently 

formulated does not utilize the 

statistical confidence levels proposed by 

DOE. Instead, a negative tolerance of 5 

percent is allowed on capacity and 

SEER and if either of two 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 of the 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 of the 

enforcement program. DOE recognizes 

the merits of the existing industry . certification programs and will consider 

incorporating any appropriate portions 

of those programs into DOE's own 

enforcement plan for 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 of the increased confidence 

attributable to values of energy 

consumption measured under this plan. 

12. Industry Standards. Many of the 

comments received indicated that two 

industry standards referenced in the 

proposed test procedure have 

subsequently been revised. and 

consequently commenters urged that the 

final test procedure reference the latest 

version of these standards. DOE has 

reviewed both editions of the American 

Society of Heating, 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, 

and because the latest versions of these 

standards can more easily be obtained 

by interested persons, today's final rule 

references the current versions, 

ASHRAE 37-78 and ARI 210-79. As 

noted below, in part C.l. of this 

preamble, DOE has consulted with the 

Attorney General and the Chairman of 

the FfC regarding DOE's use of these 

industry standards. 

13. Test Measurements and 

Tolerances. Some comments stated that 

the dew point measurement specified in 

section 4.2.2.3 of proposed Appendix M 

was not consistent with wet bulb 

measurements in other parts of the 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 of Appendix M to clarify that dew 

point need not be measured. 

Another comment requested a 

relaxation of tolerances 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 test results. In view of these 

facts, DOE has made no changes in the 

tolerances allowed for wet bulb 

measurements in today's final rule. 

Other commenters recommended a 

more exact rounding procedure for 

capacity values specified in section 3.1 

of Appendix M. The recommended 

rounding was 100 Btu/hour for 

capacities under 20,000 Btu/hour, 200 

Btu/hour for capacities between 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 of Appendix M which allow a 

similar rounding off procedure in today's 

final rule. 

14. Miscellaneous. After careful 

consideration of all the comments and 

further consultation with NBS and FfC, 

DOE has incorporated into the final rule 

some editorial and minor technical 

changes that were not discussed above. 

C. Regulations Prescribed 

1. Test Procedures. The test 

procedures for central air conditioners 

prescribed today are included in 

Subpart B of Part 430 and are 

substantially the same as those 

proposed, with the exception of the 

changes discussed above. Appendix M 

of Subpart B incorporates in part the 

revised Air Conditioning and 

Refrigeration Institutes Standards 210-

79, 240-77. and 320-76, and the revised 

American Society of Heating, 

Refrigeration, and Air Conditioning 

Engineers Standard 37-78 to measure 

the capacities and efficiencies of central 

air conditioners, including heat pumps. 

Any subsequent amendment of these 

standards by the standard-setting 

organizations will not affect the DOE 

test procedures, which can only be 

amended by DOE. 

Under the requirements of section 

32(c) of the Federal Energy 

Administration Act of 1974 (15 U.S.C. 

761 et seq.) as amended by section 9 of 

the Federal Energy Administration 

Authorization Act of 1977 (Pub. L. 95-

70), DOE is directed to consult with the 

Attorney General and the Chairman of 

the Federal Trade Commission 

concerning the impact on competition of 

any rules prescribed by DOE which 

utilize or incorporate any commercial 

standards. 

DOE has provided copies of the 

proposed test procedures for central air 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27, 19.19 I Rules and Regulations 76705 

conditioners, which incorporated the 

above-mentioned commercial standards, 

to the Attorney General and the 

Chairman of the Federal Trade 

Commission for their comments 

concerning the impact of such standards 

on competition. Neither official 

recommended against the incorporation 

or use of these commercial standards in 

the fmal test procedures for central air 

conditioners. At the request of the 

Attorney General, DOE will monitor 

manufacturers' costs of performing tests 

according to today's final rule. 

2. General Provisions. Today's 

rulemaking contains definitions of "airsource heat pump," "central air 

conditioner," "condenser-evaporator 

coil combination," "condensing unit," 

"cooling only unit," "evaporator coil," 

"heat pump," and "water-source heat 

pump." 

3. Application of Test Procedures. The 

test procedures 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, or private labeler 

may make any representation in writing 

or in any broadcast advertisement 

respecting the energy consumption or 

cost of energy 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) of the 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 of the Act. 

As required by section 325 of the Act, 

DOE is currently developing energy 

efficiency standards for the consumer 

products covered by the Act. An 

advance notice of proposed 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 of proposed 

rulemaking for standards will be 

published as soon as practicable. 

The test procedure provisions 

prescribed today, other than the 

sampling provisions of section 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 of units for testing to 

insure compliance with minimum 

efficiency standards under section 325 

may differ substantially from the 

approach taken in the sampling 

provisions of section 430.23. One of the 

approaches that will be considered by 

the standards program for split-system 

central air conditioners would require 

testing of each 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) of the Act, DOE is required to 

provide manufacturers with information 

on representative average unit costs of 

energy. This information was provided 

by notice issued June 22, 1979 (44 FR 

37534. June 27, 1979), and is expected to 

be updated periodically. 

5. Preemption. Today's rulemaking 

prescribing fmal test procedures for 

central air conditioners supersedes any 

State regulation to the extent required 

by section 327 of the Act. Pursuant to 

section 327, all State regulations which 

provide for the disclosure of information 

with respect to any measure of energy 

consumption of central air conditioners, 

or which provide for an energy 

efficiency standard, or other 

requirement regarding the energy 

efficiency or energy use of central air 

conditioners, must now employ test 

procedures identical to those specified 

in today's fmal rule. 

6. Regulatory and Environmental 

Review. In accordance with the 

requirements of the National 

Environmental Policy Act of 1969 

(NEPA) (42 USC 4321 et seq.), DOE 

evaluated the proposed establishment of 

these test procedures for consumer 

products to determine if an 

environmental assessment (EA) or an 

environmental impact statement (EIS) 

was required. These test procedures will 

be used only to standardize the 

measurment of energy usage for the 

subject consumer products. The action 

of prescribing these test procedures, by 

itself, will not result in any 

environmental impact. Since it was thus 

clear that the proposed action was not a 

major Federal action significantly 

affecting the quality of the 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 evaluated by that 

program. 

This rule has been reviewed in 

accordance with Executive Order 12044 

and DOE 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 amended by Pub. L. 95-619; 

Department of Energy Organization Act, Pub. 

L. 95-91) 

In consideration of the foregOing, Part 

430 of Chapter n of Title 10, Code of 

Federal Regulations, is amended as set 

forth below, effective January 17, 1980. 

Issued in Washington, D.C., December 10. 

1979. 

Maxine Savitz, 

Acting Assistant Secretary, Conservation and 

Solar Energy. 

1. Section 430.2 is amended by 

deleting the present definitions of 

"central air conditioner," "condenserevaporator coil combination," 

"condensing unit" and adding the 

following new defmitions in appropriate 

alphabetical order: 

§ 430.2 Definitions. 

* * * * * 

"Air-source heat pump" means a 

"heatpump" which consists of one or 

more assemblies, which utilizes an 

indoor conditioning coil, compressor(s), 

and refrigerant-to-outdoor-air heat 

exchanger to provide air heating, and 

which may also provide air cooling, 

dehumidifying, Circulating, and air 

cleaning. 

* * * * * 

"Central air conditioner" means a 

consumer product which is powered by 

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, and which is 

either a "heat pump" or a "cooling only 

unit". 

* * * * * 

"Condenser-evaporator coil 

combination" means a condenSing unit 

made by one manufacturer and one of 

several evaporator coils, either 

manufactured by the same manufacturer 

or another manufacturer, intended to be 

combined with that particular 

condensing unit. 

* * * * * 

"Condensing unit" means a 

component of a central air conditioner 

which is designed to remove the heat 

absorbed by the refrigerant and to 
CAS-RM-79-102 COMMENT 02

76706 Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 

transfer it to the outside erivironinent, 

and which consists of an outdoor coil, 

compressor(s). and air moviIlg device. 

* * * * * 

"Cooling only unit" means a "central 

air conditioner" which consists of an air 

cooled condensing unit and an 

evaporator coil. and which is designed 

to provide air cooling. dehumidifying. 

circulating. and air cleaning. 

* * * * * 

"Heat pump" means a "central air 

conditioner" which is either an "airsource heat pump" or a "water-source 

heat pump." 

* * * * * 

"Water-source heat pump" means a 

"heat pump" which consists of one 

assembly which utilizes an indoor 

conditioning coil with air moving 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 amended by 

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 of the following: 

(i) For cooling only units or the cooling 

portion of the estimated annual 

operating cost for air-source heat pumps 

which provide both heating and cooling, 

the product of (A) the quotient of the 

cooling capacity. in Btu's per hour. 

determined from the steady-state wetcoil test (test A) measured at the highest 

compressor speed. as described in 

Section 3.1 of Appendix 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 of 1000 

cooling load hours per year; (C) a 

conversion factor of .001 kilowatts per 

watt; and (D) a representative average 

unit cost of electricity in dollars per 

kilowatt-hour as provided pursuant to 

Section 323(b)(2) of the Act. the resulting 

product then being rounded off to the 

nearest dollar per year; 

(ii) For heat pumps which provide 

only heating or the heating portion of the 

estimated annual operating cost for 

central air conditioners which provide 

both heating and cooling. the product of 

(Al the quotient of the 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 of Appendix M to this subpart, and 

the heating seasonal performance factor. 

in Btu's per watt-hour. calculated for 

heating region IV correspondiIlg to the 

above mentioned standardized design 

heating requirement determined from 

Section 5.2 of Appendix M to this 

subpart; (B) the representative average 

use cycle of 2080 heating load hours per 

year; (C) 0.77. a correction factor 

described in section 5.2 of Appendix M 

to this subpart; (0) a representative 

average unit cost of electricity in: dollars 

per kilowatt-hour as provided pursuant 

to Section 323(b)(2) of the Act; and (E) a 

conversion factor of .001 kilowatts per 

watt; the resulting quotient then being 

rounded off to the nearest dollar per 

year; or 

(iii) For central air conditioners which 

provide both heating and cooling. the 

quantity determined in paragraph 

(m)(l)(i) of this section added to the 

quantity determined in paragraph 

(m)(l)(ii) of this section. 

(2) [Reserved] 

(3) The estimated regional annual 

operating costs for cooling only units 

and air-source heat pumps shall be one 

of the following: 

(i) For cooling only units or the cooling 

portion of the estimated annual 

operating cost for central air 

conditioners which provide both heating 

and cooling, the product of (A) the 

quotient of cooling 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 

in Btu's per watt-hour both determined 

from Section 5.1 of Appendix M to this 

subpart; (B) the estimated number 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 of electricity in dollars per 

kilowatt-hour as prOVided pursuant to 

Section 323(b)(2) of the Act. the resulting 

product then being rounded off to the 

nearest dollar per year. 

(ii) For heat pumps which provide 

only heating or the heating portion of the 

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 of the estimated number of 

local heating load hours per year 

determined from Section 6.2.5 of 

Appendix M to this subpart. and the 

heating seasonal performance factor. in 

Btu's per watt-hour, corresponding to 

the appropriate standardized design 

heating requirement determined from 

Section 5.2 of Appendix M to this 

subpart; (B) 0.77, a correcuon factor 

described in Section 5.2 of Appendix M 

to this subpart; (C) the standardized 

design heating requirement in Btll's per 

hour determined in Sections 5.2 and 6.2.6 

of Appendix M to this subpart; (D) a 

representative average unit cost of 

electricity in dollars per kilowatt-hour 

as provided pursuant to Section 

323(b)(2) of the Act; and (E) a 

conversion factor of .001 kilowatts per 

watt, the resulting quotient then being 

rounded off to the nearest dollar pet' 

year; or 

(iii) For central air conditioners which 

provide both heating and cooling. the 

quantity determined in paragraph 

(m)(3)(i) of this section added to each 

quantity determined in paragraph 

(m)(3)(ii) of this section. 

(4) [Reserved] 

(5) The measure(s) of efficiency for 

cooling only units and air-source heat 

pumps shall be one or more of the 

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. in Btu's per watt-hour, 

determined according to Section 5.1 of 

Appendix M to this Subpart. rounded off 

to the nearest 0.05. 

(ii) The heating seasonal performance 

factors for air-source heat pumps shall 

be the heating seasonal performance 

factors. in Btu's per watt-hour. 

determined according to Section 5.2 of 

Appendix M to this subpart for each 

applicable standardized design heating 

requirement within each climatic region. 

rounded off to the nearest 0.05. 

(iii) The annual performance factors 

for air-source heat pumps which provide 

heating and cooling, shall be the annual 

performance factors, in Btu's per watthour. determined according to Section 

5.3 of Appendix M to this subpart for 

each standardized design heating 

requirement within each climatic region. 

rounded off to the nearest 0.05. 

(6) [Reserved] 

(7) Other useful measures of energy 

consumption for central air conditioners 

shall be 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 of Appendix 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 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations '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 of estimated 

annual operating cost, energy 

consumption or other measure of energy 

consumption of the condenserevaporator coil combination for which consumers would favor lower values 

shall be no less than the higher of (AJ 

the mean of the sample or (B) the upper 

90 percent confidence limit of the true 

mean divided by 1.05, and 

(ii) Any represented value of the 

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 of the sample or (B) the lower 

90 percent confidence limit of the true 

mean divided by 0.95. 

(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 of retail 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 of the 

measures of energy consumption shall 

be determined by the use of computer 

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 of energy 

consumption determined by computer 

simulation or by engineering analysis do 

not agree with measures of energy 

consumption determined by actual 

testing, the values determined by actual 

testing shall be used to comply with 

section 323(cl of the Act, or to comply 

with rules prescribed under section 324 

of the Act. 

(4) The sample selected for testing 

under paragraph (m)(l) of this section 

shall be comprised of units which are 

production units, or representative of 

production units. 

1 Components of similar design may be 

substituted without requiring additional testing if 

the represented measures of energy consumption 

continue to satisfy the applicable sampling 

provision. 

(5) The basis of the computer 

simulation or engineering analysis 

method referred to in paragraph 

(m)(2)(ii) of this section shall be a 

representation of the 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 of graphic or tabular 

performance data. Heat transfer 

characteristics of coils may be modeled 

as a function of face 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 of a new product into the 

market) a manufacturer discovers that 

the condenser-evaporator coil 

combination tested does not have the 

largest volume of retail 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 under paragraphs 

(m)(2)(ii) and (m)(5) of this 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 of basic models 

using the same condensing unit, submit 

to DOE the results from all tests 

required by section 3 of Appendix 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 

of those test results with the values 

predicted when the simulation method 

used to rate other members of the family 

is used to rate such combination. 

(8) Manufacturers who choose to use 

computer simulation or engineering 

analysis for determining measures of 

energy consumption under paragraphs 

(m)(2)(ii) and (m)(5) of this section shall 

permit representatives of the 

Department of Energy to inspect for 

verification purposes the simulation 

method or methods used. This 

inspection may include conducting 

simulations to predict the performance 

of particular condenser-evaporator coil 

combinations specified by DOE. 

analysis of previous simulations 

conducted by a manufacturer, or both. 

§ 430.24 [Revoked] 

4. Section 430.24(m) is revoked. 

5. Appendix M to Subpart B of Part 

430 is amended to read as follows: 

Appendix M to Subpart B-Uniform Test 

Method for Measuring the Energy 

Consumption of Central Air Conditioners 

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 1979 by 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 1976 by the ARJ and 

titled "Standard for Water-Source Heat 

Pumps", 

1.6 "ASHRAE" means the American 

Society of Heating. Refrigeration anli AirConditioning Engineers. Inc. 

1.7 "ASHRAE Standard 37-78" means the 

test standard published by ASHRAE in 1978 

and titled "Methods of Testing for Rating 

Unitary Air-Conditioning and Heat Pump 

Equipment." 

1.8 "Continuously recorded" means a method of recording measurements in 

intervals no greater than 5 seconds. 

1.9 "Cooling load factor (CLF)" means the 

ratio of the total cooling done in a complete 

cycle of a 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 of the efficiency loss due to the 

cycling of the unit. 

1.12 "Demand-defrost control system" 

means a system which is designed to perform 

the defrost function on the outdoor coil of the 

heat pump only when a predetermined 

degradation of performance is measured. 

1.13 "Design heating requirement (DHR)" 

is the amount of heating 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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76708 Federal Register I Vol. 44. No. 249 I Thursday. December 27, 1979 I Rules and Regulations 

1.15 "Heating seasonal performance 

factor (HSPF)" means the total heating output 

of a heat pump during its normal annual 

usage period for heating divided by the total 

electric power input during the same period. 

1.16 "Heating load factor (HLF)" means 

the ratio of the-total heating done in a 

complete cycle of a specified time period. 

consisting of an "on" time "ofr' time. to the 

ste!ldy state heating done over the same 

period at constant ambient conditions. 

1.17 "Latent cooling" means the amount 

of cooling in Btu's necessary to remove water 

vapor from the air passing over the indoor 

coil by condensation during a period of time. 

1.18 "Part-load factor (PLF)" means the 

ratio of the 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 of a central 

air conditioner in Btu's during its normal 

annual usage period for cooling divided by 

the total electric power input in watt-hours 

during the same period. 

1.20 "Sensible cooling" means the amount 

of cooling in Btu's performed by a unit over a 

period of time. 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 

conditioner in which one or more of the 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 in non-changing 

operating mode. 

1.24 "Temperature bin" means a 5° F 

increment over a dry-bulb temperature range 

of 65° 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 whenever the 

outdoor temperature drops below a level 

where frosting will occur. 

1.26 "Test condition tolerance" means the 

maximum permissible variation of the 

average of the test observations from the 

standard or desired test condition as 

provided in 6.1.1. 6.2.1. 6.2.2. and 6.2.3 of this 

Appendix. 

1.27 "Test operating tolerance" means the 

maximum permiSSible difference between the 

maximum and the minimum instrument 

observation during a test as provided in 6.1.1. 

6.2.1. 6.2.2. and 6.2.3 of this 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 evaporator coil. 

Z. Testing Required 

2.1 Testing required for air source cooling 

only units with single speed compressors, 

two-speed compressors, two compressors, or 

cylinder unloading. Two steady state wet coil 

tests required to be performed, test A and 

test B. Test A is to be ~onducted as an 

outdoor dry bulb temperature of 95° F and 

test B at 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 dry bulb 

temperature of 82° F. Test D is a cyclic test 

also conducted at an outdoor dry bulb 

temperature of 82° F; In lieu of conducting 

tests C and D, an assigned value of 0.25 may 

be used for the degradation coefficient, CD. 

2.1.1 Testing required for units with 

single speed compressors and single speed 

condenser fans. Test A and test B shall be 

performed according to the test procedures 

outlined in 4.1 of this Appendix. In addition, 

the cyclic performance shall be evaluated by 

conducting test C and D according to the 

requirements outlined in 4.1 of this Appendix. 

2.1.2 Testing required for units with 

single speed compressors and multiple-speed 

condenser fans. The test requirements for 

multiple-speed condenser fan units shall be 

the same as described in section 2.1.1 for 

single speed condensor fan units. 

2.1.3 Testing required for units with twospeed compressors, 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 of this Appendix 

except that test A and test B shall be 

performed at each compressor speed or at 

each compressor capacity. 

2.1.4 Testing required for units with twospeed compressors, two compressors, or 

cylinder unloading capable of varying the 

sensible to total (SIT) capacity ratio. When a 

unit employing a two-speed compressor, two 

compressors, or cylinder unloading provides 

a method of varying the ratio of the sensible 

cooling capacity to the total cooling capacity. 

(S/T), the test requirements are the same as 

for two-speed compressor units as described 

in 2.1.3 of this Appendix. 

2.2 Testing required for air source. heating 

only units with single speed compressors, 

two-speed compressors, two compressors, or 

cylinder unloading. Four types of tests are 

required to be performed: High Temperature. 

Cyclic. Frost Accumulation. and Low 

Temperature. In lieu of conducting the Cyclic 

Test an assigned value of 0.25 may be used 

for the degradation coefficient, CD. 

2.2.1 Testing required for units with 

single speed compressors. Units with single 

speed compressors shall be subjected 

respectively to the High Temperature Test at 

47° F described in section 3.2.1.1. the Cyclic 

Test as described in section 3.2.1.2, the Frost 

Accumulation Test as described in section 

3.2.1.3. and the Low Temperature Test as 

described in section 3.2.1.4. 

2.2.2 Testing required for units with twospeed compressors, two compressors, or 

cylinder unloading. With the unit operating: 

at high compressors speed (two-speed 

compressor). with both compressors in 

operation (two-compressors). or at the 

maximum capacity (cylinder unloading): the 

following tests are required to be performed 

on all units; the High Temperature Test at 

47° F, the Frost Accumulation Test. and the 

Low Temperature Test. 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 (cylinder unloading); if 

the normal mode of operation requires 

cycling "on" and "ofr' of the compressor(s) at 

high speed or maximum capacity. 

With the unit operating: at the low 

compressor speed (two-speed compressor). 

with the single compressor which normally 

operates at low loads (two compressors). or 

at the low compressor capacity (cylinder 

unloading); the following tests are required to 

be performed on all units: the High 

Temperature Test at 47° F. the High 

Temperature Test at 62° F. and the Cyclic 

Test Additional tests, (Frost Accumulation 

• Test and Low Temperature Test) are 

required, with the unit operating: on low 

compressor speed (two-speed compressor). 

with the single compressor which normally 

operates at low loads (two compressors) or at 

the low compressor capacity (cylinder 

unloading). if the unit's low speed, one 

compressor or low capacity performance at 

and below 40° F is needed to calculate its 

seasonal performance. 

2.3 Testing required for air source units 

which provide both heating and cooling. The 

requirements for units which provide both 

heating and cooling shall be the same as the 

requirements in Section 2.1. and 2.2 of this 

Appendix. 

2.4 Testing required for water source 

units which provide both heating and cooling. 

(Reserved) 

3. Testing conditions 

3.1 Testing conditions for air source cooling only units with single speed 

compressors, two-speed compressors, two 

compressors or cylinder unloading. The test 

room requirement and equipment installation 

procedures are the same as those specified in 

sections 11.1 and 11.2 of ASHRAE Standard 

37-78. Units designed for both horizontal and 

vertical installation shall be tested in the 

orientation in which they are most frequently 

installed. All tests shall be performed at the 

normal residential voltage and frequency for 

which the equipment is designed (either 115 

or 230 volts and 60 hertz). the test installation 

shall be designed such that there will be no 

air flow through the cooling coil due to 

natural or forced convection while the indoor 

fan is "ofr·. This shall be accomplished by 

installing dampers upstream and downstream 

of the test unit to block the off period air 

flow. Values of capacity for rating purposes 

are to be rounded off to the nearest 100 Btu/ 

hour for 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 capacities 

between 36.000 and 64.999 Btu/hour. 

The following conditions listed in AR1 

Standard 210.79 shall apply to all tests 

performed in Section 3.1 of this Appendix: 

5.1.3.4 Cooling Coil Air Quantity. 

5.1.3.6 Requirements for Separated 

Assemblies. 

3.1.1 Testing conditions for units with single 

speed compressors and single speed 

condenser fans. 

3.1.1.1 Steady state wet-coiJ performance 

tests (Test A and Test B). Test A and test B 

shall be performed with the air entering the 

indoor side of the unit having a dry-bulb 

temperature of 80° F and a wet-bulb 

temperature of 87" F. The dry-bulb 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 76709 

temperature of the air entering the outdoor 

side of the unit shall be 95° F in test A and 

82° F in test B. The temperature of the air 

surrounding the outdoor side of the unit in 

each test shall be the same as the outdoor 

entering air temperature except for units or sections thereof intended 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 of the unit, the outdoor wetbulb temperature surrounding the outdoor 

side of the unit shall be 75° F in test A and 

65° F in test B. 

3.1.1.2 Steady state dry coil performance 

test {Test C) and cyclic dry coil performance 

test {Test D}. Test C and test D shall be 

performed with the air entering the indoor 

side of the unit having a dry-bulb 

temperature of 80° F and a wet-bulb 

temperature which does not result in 

formation of condensate on the indoor coil. (It 

is recommended that an indoor wet-bulb 

temperature of 57° F or less be used.) The 

dry-bulb temperature of the air entering the 

outdoor portion of the unit shall be 82° F. The 

outdoor portion of the unit shall be subject to 

the same conditions as the requirements for 

conducting test B as stated previously in 

section 3.1.1.1. Test C shall be conducted with 

the unit operating steadily. Test D shall be 

conducted by cycling the unit "on" and "off" 

by manual or automatic operation of the 

normal control circuit of the unit. The unit 

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 of the indoor fan "on" and "ofr' 

periods being governed by the automatic 

controls which the manufacturer normally 

supplies with the unit. The results of tests C 

and D shall be used to calculate a 

degradation coefficient, CD by the procedures 

outlined in 5.1 of this Appendix. 

3.1.2 Testing conditions for units with 

single speed compressors and multiple-speed 

condenser fans. The condenser fan speed to 

be used in test A shall be that speed which 

normally occurs at an outdoor dry-bulb 

temperature of 95° F. and for test B. the fan 

speed shall be that which normally occurs at 

an outdoor dry-bulb temperature of 82° F. If 

elected to be performed, tests C and D shall 

be conducted at the same condenser fan 

speed as in test B. 

3.1.3 Testing conditions for units with 

two-speed compressors, two compressors, or cylinder unloading. The condenser fan speed 

used in conducting test A at each compressor 

speed shall be that which normally occurs at 

an outdoor dry-bulb temperature of 95° F. For 

test B. the condenser fan speed at each 

compressor speed shall be that which 

normally occurs at an outdoor dry-bulb 

temperature of 82° F. If elected to be 

performed. tests C and D shall be conducted 

at the low compressor speed with the same 

condenser fan speed as used in test B. For 

those two-speed units in which the normal 

mode of operation involves cycling the 

compressor "on" and "off" at high speed, 

tests C and D 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 of two 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 at low speed. only the compressor 

which normally operates at an outdoor drybulb temperature of 82° F shall be operating. 

In lieu of conducting tests C and D. an assigned value of 0.25 may be used for the 

degradation coefficient. CD' at each 

compressor speed. If the assigned 

degradation coefficient is used for one compressor speed it must also be used for the 

other compressor speed. 

In the case of units 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 conditions for units with 

two-speed compressors, two compressors, or cylinder unloading capable of varying the 

sensible to total (SIT) capacity ratio. The 

mode of operation selected for controlling the 

SIT ratio in the performance of test A and 

test B at each compressor speed shall be such 

that it does not result in an operating 

configuration which is not typical of a normal 

residential installation. If elected to be 

performed, tests C and D shall be conducted 

at low compressor speed (single compressor 

operating) with the same 

SIT control mode as used in test B when 

performed at the low compressor speed. 

Likewise, tests C and D shall also be 

conducted at high compressor speed (two 

compressors operating) and with the same S/ 

T control mode as in test A when performed 

at the high compressor speed. 

In the case of units with cylinder 

unloading, the loaded and unloaded 

conditions correspond to high and low 

compressor speed on two-speed units 

respectively. 

3.2 Testing conditions for air source heating only units with single speed 

compressors, two-speed compressors, two 

compressors, or cylinder unloading. The 

equipment under test shall be installed 

according to the requirements of Section 11.2 

of ASHRAE Standard 37-78 and Section 

5.1.4.5 of ARI Standard 240-77. Test chamber 

requirements are the same as given in Section 

11.1 of ASHRAE Standard 37-78. Units 

designed for both horizontal and vertical 

installation shall be tested in the orientation 

in which they are most often installed. All 

tests shall be performed at the normal 

residential voltage and frequency for which 

the equipment is designed (either 115 or 230 

volts and 60 hertz). Values of capacity for 

rating purposes are to be rounded off to the 

nearest 100 Btu/hour for 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 

capacities between 38,000 and 64,999 Btu/ 

hour. 

3.2.1 Testing conditions for units with 

single speed compressors. 

3.2.1.1 High temperature test conditions. 

The High Temperature Test at 47° F shall be 

conducted at an outdoor dry-bulb 

temperature of 47° F and an outdoor wet-bulb 

temperature at 43° F. The High Temperature 

Test at 62° F shall be conducted at an outdoor 

dry-bulb temperature of 82° F and an outdoor 

wet-bulb temperature of 56.5° F. For both 

tests. the dry-bulb air temperature entering 

and surrounding the indoor portion of the unit 

shall be 70° F and a maximum wet-bulb 

temperature of 80° F. The duration of the tests 

shall be for a minimum of Ih hour. 

3.2.1.2 Cycling test conditions. The 

Cycling Test at 47° F shall be 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 

of the test unit to block the off period airflow. 

3.2.1.3 Frost accumulation test conditions. 

The dry-bulb temperature and the resultant 

dew-point temperature of the air entering the 

outdoor portion of the unit shall be 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. 

The Frost Accumulation Test 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 it to change defrost 

operation to normal heating operation. During 

the test. auxiliary resistance heaters shall not 

be employed during either the heating or defrost portion of the test. 

3.2.1.4 Low temperature test conditions. 

The Low Temperature Test shall be 

conducted at a dry-bulb temperature entering 

the outdoor portion of the unit of 17° F and a wet-bulb temperature of 15° F. The air 

entering the indoor portion of the unit shall 

have a dry-bulb temperature of 70° F and a maximum wet-bulb temperature of 60° F. 

3.2.1.5 Additional testing conditions. All 

tests shall be conducted at the indoor-side air 

quantities specified in Sections 4.1.4.3 and 

5.1.4.6 and Table 2 of ARI Standard 240-77. 

The following conditions listed in ARI 

Standard 240-77 shall apply to all tests 

performed in Section 3.2 of this Appendix. 

5.4.4.4 Outdoor-Side Air Quantity; and 

5.1.4.5 Requirements for Separated 

Assemblies. 

In all tests, the specified dry-bulb 

temperature entering the outdoor portion of 

the unit also applies to the air temperature 

surrounding the outdoor portion of the unit. 

Similarly. models where portions are intended to be installed indoors shall have 

the air temperature surrounding that portion 

of the unit the same as the indoor air 

temperature. 

3.2.2 Testing conditions for units with 

two-speed compressors, two compressors or cylinder unloading. The testing conditions for 

two-speed compressors, two compressors, or cylinder unloading shall be the same as those 

for single speed units as described in 3.2.1. 
CAS-RM-79-102 COMMENT 02

76710 Federal Register I Vol. 44. No. 249 I Thursday, December 27, 1979 I Rules and Regulations 

3.3 Testing conditions for air source units 

which provide both heating and cooling. The 

testing conditions for units which provide 

botli heating and cooling shall be the same as 

the requirements in Sections 3.1 and 3.2 of 

this Appendix. 

3.4 Testing conditions for water source units which provide both heating and cooling. 

(Reserved) 

4.0 Testing procedures. Measure all 

electrical inputs as described in the 

procedures below. All electrical 

measurements during all "on" and "off' 

periods shall include auxiliary power or 

energy (controls, transformers, crankcase 

heaters, etc.) delivered to the unit. 

4.1 Testing procedures for air source cooling only units with single speed 

compressors, two-speed compressors, two 

compressors, or cylinder unloading. All 

steady:state wet- and dry-coil performance 

tests on single package units shall 

simultaneously employ the Air-Enthalpy 

Method (Section 3 of ASHRAE Standard 37-

78) on the indoor side and one other method 

consisting of either the Air-Enthalpy Method 

or the Compressor Calibration Method 

(Section 4 of ASHRAE 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 or the 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 shall be installed and 

tested in such a manner that when operated 

under steady-state conditions. the cooling 

coil and condenser coil air flows meet the 

requirements of Sections 5.1.3.4. 5.1.3.5. and 

5.1.3.7 of ARl Standard 210.79. 

4.1.1 Test operoting procedures. 

4.1.1.1 Steady-state wet-coil performance 

tests {Test A and Test B}. 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 of this Appendix and the procedures 

described for cooling tests in Section 11.3 of 

ASHRAE standard 37-78 and evaluated in 

accordance with the cooling-related 

requirements of Section 12 of the ASHRAE 

Standard 37-78. The test room reconditioning 

apparatus and the equipment under test shall 

be operated until equilibrium conditions are 

attained. 

4.1.1.2 Steady-state and cyclic dry-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 of Sections 12.1.5.12.1.6.12.1.7. 

of ASHRAE Standard 37.78. The test room 

reconditioning apparatus and the equipment 

under test shall be operated until equilibrium 

conditions are attained. but not for less than 

one hour before data for test C are recorded. 

For all equipment test methods including the 

Compressor Calibration Method. 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 of ASHRAE 

Standard 37-78. When the Air-Enthalpy 

Method is used on the outdoor side for test C. 

the requirements of this section shall apply tq 

both the preliminary test and the regular 

equipment iest; the requirements of Section 

3.6 of ASHRAE 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. 

but for 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 of this 

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 and Table n of ASHRAE 

Standard 37.78. For the cyclic dry-coil 

performance tests. the dry-bulb temperature 

of the air entering and leaving the cooling 

coil. or the difference between these two drybulb temperatures. shall be continuously 

recorded with instrumentation accurate to 

within ±0.3· F of indicated value and have a 

response time of 2.5 seconds or less. 

Response time in the time required for the 

instrumentation to obtain 63 percent of the 

final steady-state temperature difference 

when subjected to a step change in 

temperature difference of 15· F or more. 

Electrical measurement devices (watt-hour 

meters) used during all tests shall be accurate 

to within ±O.5 percent of indicated value. 

4.1.3 Test tolerances. All steady-state 

wet-and dry-coil performance tests shall be 

performed within the applicable operating 

and test condition tolerances specified in 

Section 11.6 and Table III of ASHRAE 

Standard 37-78. 

4.1.3.1 The indoor and outdoor average 

dry-bulb temperature for the cyclic dry coil 

test D shall both be within 1.0· F of the indoor 

and outdoor average dry bulb temperature for 

the steady-state dry coil test C. respectively. 

4.1.3.2 The test condition and test 

operating tolerances for conducting test Dare 

stated in 6.1.1 of this Appendix. Variation in 

the test conditions greater than the tolerances 

prescribed in 6.1.1 of this Appendix shall 

invalidate the test. It is 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 should be installed in 

the outdoor test room 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 

heater having a heating capacity 

approximately equal to the cooling capacity 

of the unit could be installed in the indoor 

test room. and cycled "on" and "off' as the 

test unit cycles "on" and "off' to improve 

indoor room control. 

4.2 Testing procedures for air source heating only units with single speed 

compressors, two-speed compressors, two 

compressors. or cylinder unloading. 

4.2.1 Test operoting procedures. All High 

Temperature Tests. the Cyclic Test. the Frost 

Accumulation Test. and the low Temperature 

test shall have the performance evaluated by 

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 Test procedure for 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. It is necessary to determine and adjust 

for system resistance when the outdoor air 

measuring apparatus is attached to the 

outdoor portion of the unit. The test room 

apparatus and test units must be operated for 

at least 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 

prior to the start of the test. When the 

outdoor Air-Enthalpy Method is used as a 

second test then a preliminary test must be 

conducted for a minimum of 30 minutes with 

4 or more sets of data 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 test for the outdoor air enthalpy 

method. For some units. at the ambient 

condition of the test. frost may accumulate on 

the outdoor coil. U the supply air temperature 

or the difference between the supply air 

temperature and the indoor air entering 

temperature has decreased by more than 1.50 

F at the end of the test. the unit shall be 

defrosted and the test restarted. Only the 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 76711 

results of this 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 heating mode 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 and room conditions are within 

the test condition tolerances specified in 

Section 6.2.1 of this Appendix. 

4.2.1.2 Test procedures for 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 2 complete 

"off"/"on" cycles. Without a break in 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. of this Appendix. If. prior to the 

High Temperature Test. the unit underwent a 

defrost cycle to rid the outdoor coil of any 

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 and room conditions are within the High Temperature Test 

condition tolerances specified in section 6.2.1 

of this Appendix. Attention should be given 

to prevent defrost after the cycling process 

has begun. 

4.2.1.3 Test procedures for the frost 

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 of this 

Appendix. The test room reconditioning 

equipment and the unit lh,der test shall be 

operated for at least lh hour prior to the start 

of a "preliminary" test period. The 

preliminary test period and the test period 

itself are to be conducted within the test 

tolerances given in section 4.2.3.3 of this 

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 of a defrost cycle 

which automatically occurs and shall end at 

the termination of the 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 of this defrost 

cycle and ends at the termination of the next 

automatically occurring defrost cycle. If the 

unit has not undergone a defrost after 12 

hours, then the tests shall be concluded and 

the results calculated for this 12-hour period. 

For units which turn the indoor fan off during 

defrost the indoor supply duct shall be 

blocked during all defrost cycles to prevent 

natural or forced convection through the 

indoor unit. During defrost. resistance heaters 

normally installed with the unit shall be 

prevented from operating. 

4.2.1.4 Test procedures for the low 

temperature test. Where applicable, the High 

Temperature Test preparation and 

performance requirements shall also be used 

in the Low Temperature Test. The test room reconditioning equipment shall first be 

operated in a steady-state manner for at least 

one-half hour at equilibrium and at the 

specified test conditions. The unit shall then 

undergo a defrost. either automatic or manually induced. It is important that the 

unit terminate the defrost sequence by the 

action of its 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-half hour. For 

all units. defrost should be prevented during 

the one-half hour test period. 

4.2.2 Test instrumentation. 

4.2.2.1 Test instrumentation for the high 

temperature test. The indoor air flow rate 

shall be determined as described in Section 

7.1 through 7.4 of ASHRAE Standard 37-78. 

This requires the construction of an air 

receiving chamber and discharge chamber 

separated by partition in which one or more 

nozzles are located. The receiving chamber is 

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 ±1.0 percent of indicated 

value and having minimum scale divisions 

not exceeding 2,0 percent of the reading. 

Static pressure and temperature 

measurements must be taken at the nozzle 

throat in order to obtain density of the air. 

The areas of the nozzles shall be determined 

by measuring their diameter with an error no 

greater than ±0.2 percent in four places 

approximately 45 degrees apart around the 

nozzle in each of two places through the 

nozzle throat. one at the outlets and the 

others in the straight section near the radius. 

The energy usage of the 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 of the quantity measured. 

Measurements of the air temperature entering 

and leaVing the indoor coil or the difference 

between these two shall be made in 

accordance with the requirements of 

ASHRAE Standard 41 part 1. These 

temperatures shall be continuously recorded 

with instrumentation having a total system 

accuracy within ±0.3° F of indicated value 

and a response time of 2.5 seconds or less. 

Temperature measurements are to be made 

upstream of the static pressure tap on the 

inlet and downstream of the static pressure 

taps on the outlet. The indoor and outdoor 

dry-bulb temperatures shall be continuously 

recorded with instrumentation which will 

result in an error no greater than ±0.3° F of 

indicated value. The outdoor wet-bulb 

temperature shall be continuously recorded. 

Static pressure measurements in the ducts 

and across the unit shall be made in 

accordance with Section 8 of ASHRAE 

Standard 37-78 using equipment which will 

result in an error no greater than ±0.01 inch 

of water. Static pressure measurements shall 

be made and recorded at 5 minute intervals. 

All other data not continuously recorded 

shall be recorded at 10 minute intervals. 

4.2.2.2 Test instrumentation for the 

cycling test. The air flow rate during the onperiod of the Cyclic Test shall be the same 

agreed within ±1. percent as the air flow rate 

measured during the previously conducted 

High Temperature Test. All other 

instrumentation requirements are identical to 

4.2.2.1 of this Appendix. 

4.2.2.3 Test instrumentation for the frost 

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 of indicated value. 

The outdoor dew point temperature shall be 

determined with an error no greater than 

±0.5° F of indicated value using continuously 

recording instrumentation. All other data 

shall be 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) of the 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 be made so that 

instrumentation in capable of recording the 

cooling done during defrost as well as the 

total electrical energy usage during defrost. 

These data and the continuously recorded 

data need be the only data obtained during 

defrost. 

4.2.2.4 Test instrumentation for the low 

temperature test. Instrumentation for the Low 

Temperature Test is identical to that of the 

High Temperature Test described in section 

4.2.2.1 of this Appendix. 

4.2.3 Test tolerances. 

4.2.3.1 Test tolerances for the high 

temperature test. All tests shall be conducted 

within the tolerances specified in Section 

6.2.1. Variation greater than those given shall 
CAS-RM-79-102 COMMENT 02

76712 Federal Register I Vol. 44, No. 249 I Thursday, December 27, 1979 I Rules and Regulations 

invalidate the test. The heating capacity 

results by the indoor Air Enthalpy Method 

shall agree within 6 percent of the value 

determined by any other simultaneously 

conducted capacity test in order for the test 

to be valid. 

4.2.3.2 Test tolerances for the cyclic test. 

The test condition tolerances and test 

operating tolerances for the on-period portion 

of the test cycle are specified in Section 6.2.2. 

Variation exceeding any specified test 

tolerance shall invalidate the test results. 

4.2.3.3 Test tolerances for the frost 

accumulation test. Test condition and test 

operating tolerances for Frost Accumulation 

Tests are specified in Section 6.2.3. Test 

operating tolerances during heating applies 

when the unit is in the heating mode. except 

for the first 5 minutes after the termination of 

a defrost cycle. Test operating tolerance 

during defrost applies during a defrost cycle 

and during the first 5 minutes after defrost 

termination when the unit is operating in the 

heating mode. In determining whether the 

test condition tolerances are met. only the 

heating portion of the test period shall be 

used in calculating the average values. 

Variations exceeding the tolerances 

presented in Section 6.2.3 shall invalidate the 

test. 

4.2.3.4 Test tolerances for the low 

temperature test. During the test period for 

the Low Temperature Test. the operating 

conditions shall be within the tolerances 

specified in Section 6.2.1 of this Appendix. 

4.3 Testing pracedures for air source units which pravide both heating and cooling. 

The testing procedures for units which 

provide both heating and cooling shall be the 

same as those specified in Sections 4.1 and 

4.2 of this Appendix. Also during the offperiod of the dry-coil cooling test (test D). the 

switch-over valve shall remain 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 of the cyclic 

heating test at 47· F. the switch-over valve 

shall remain 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 Testing procedures for water source units which provide both heating and cooling. 

(Reserved) 

5.0 Calculations for performance factors. 

5.1 Calculations of seasonal energy 

efficiency ratios (SEER) in air-source units. 

The testing data and results required to 

calculate the seasonal energy efficiency ratio 

(SEER) in Btu's per watt-hour shall include 

the following: 

(i) Cooling capacities (Btu/hr) from tests A 

and B and. if applicable. the cooling capacity 

(Btu/hr) from test C and the total cooling 

done from test D (Btu·s). 

Q .. k (95F) 

Q .. k (82F) 

Q..,dry 

QeyCO dry . (ii) Electrical power input to all 

components and controls (watts) from tests 

A. B. and if applicable 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 

external resistance to indoor air flow (inches 

of water). 

(iv) Air temperature (" F) 

Outdoor dry bulb 

Outdoor wet bulb 

Indoor dry bulb 

Indoor wet bulb . 

Where the pooling capacities o..k (9qF). 

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

dry. from test C. are calculated using the 

equations specified in section 3.7 of ASHRAE 

Standard 37-78. The total cooling done. QeyCO 

dry from test D. is calculated using equation 

(1) below. 

Units which do not have indoor air 

circulating fans furnished as part of the 

model shall have their measured total cooling 

capacities adjusted by subtracting 1250 Btu/ 

hr per 1.000 CFM of measured indoor air flow 

and adding to the total steady-state electrical 

power input 365 watts per 1.000 CFM of 

measured indoor air flow. 

Energy effiCiency ratios from tests A. B. 

and C. EERA• EERs. EER... dry respectively. are each calculated as the ratio of the total 

cooling capacity in Btu/hr to the total 

electrical power input in watts. 

Units which do not have indoor air 

circulating fans furnished as part of the 

model shall adjust their total cooling done 

and energy used in one complete cycle for the 

effect of circulating indoor air equipment 

power. The value to be used for the 

circulating indoor air equipment power shall 

be 1250 Btu/hr per 1.000 CFM of circulating 

indoor air. The energy usage required in one 

complete cycle required for indoor air 

circulation is the product of the circulating 

indoor air equipment power and the duration 

of time 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 air circulation in one 

complete cycle. The total electrical energy 

usage shall be the sum of the energy usage 

required for indoor air circulation in one 

complete cycle and the energy used by 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 of the total 

cooling done in Btu's to the total electrical 

en.ergy usage in watt-hours. 
CAS-RM-79-102 COMMENT 02

Federal Register I Vol. 44, No. 249 I Thursday, December 27,1979 I Rules and Regulations 76713 

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 of measurement. . 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.=Humidity ratio (Ib/lb). 

and r (hr.-OF), which is described by the 

equation: 

(2) 

r = f(time indoor fan 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-bulb temperature of air leaving the indoor 

coil (,F) at time (t). 

(3) CLF= QcYC.d!:!.. Q •• dryX .. 

where 

CLF=cooling load factor. 

Q .. d,. = Total steady-state cooling capacity from 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. P LF(O.5) = Part-load performance factor when cooling load factor=O.5 as determined from the 

equation: 

PLF( 0.5) = 1-0.5 X CD 

where 

CD=Is the degradation coefficient described in 2.1.1 or as calculated in 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 in 2.8 P LF(O.5) = Part-load performance factor as determined from the equation: 

PLF (0.5) = 1-0.5 X 0 D 

where 

CD=The delll'l!.datlon coefficient described in 2.1.2 or as calculated in equation (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 .. ~( Tj }, and power input, 

E •• k( Tt}, at temperature Tj 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- (5 Xi)] 

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 outlined in 2.1.3. 

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 in 2.1.3. 

E .. ' (82 F) = Electrical power input measured from 

using test A as outlined 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 at low compressor speed (k= 1) for which the steady-state cooling capacity, (f..-l (Tj ), is greater 

than or equal to the building cooling load, 

BL ( Tj ), evaluate the following equations: 

Xk-I BL(T;} 

(f..-l( T i ) (1) 

where 

Xk-,=Loa!l factor. 

B L( Tj) = Bnllding cooling load (Btu/hr) at tempera- 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 

binj to the number of temperature bin hours. 

Ui is the fractional number of hours in temperature N bin j from 6.1.2. 

(3) 

where 

~~ "]i{" = ratiO . of Energy usage (watt-hr.) .. 

m temperature bin j to the number of temperature bin hours. 

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 (Ti )Xj} 

(2) E<J;) =E~;'(T;) xiJ 
CAS-RM-79-102 COMMENT 02

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 

ASH RAE 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) watts per 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 of the 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 

total energy 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 "demand defrost 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 of ASH RAE 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 of air-water mixture at the same dry-bulb temperature, htunidity ratio, and 

pressure nsed in the determination of the indoor 

air flow rate (ft3jl b). 

Wn=Humidity ratio (lbjlb). 

and r (hr-OF), which is described by the 

equation: 

f

(time indoor fan off) r= [Ta2 (t) (time indoor fan 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 of the air flow rate calculated at fOllr 

or more time intervals throughout the heating phase of the test using the equation in section 7.4 

of ASHRAE Standard 3i-78. Cp.=Specific heat at constant pressnre of air-water 

mixtnre per pound of dry air, (Btu/lb-OF). 

Vn 1=Specific voltune of air-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.=Humidity ratio (lb/lb). 

and r (hr.-OF), which is described by the 

equation: 

f

(tlme of next defrost termination) 

r= 

(time of defrost termination 

where 

T.'(t)=Dry·bulb temperature of air entering the indoor coil (OF) at time (t). 

T .'(t) = Dry-bulb temperature of air leaving the indoor 

coil ("F) at time (t). 

The cyclic degradation coefficient shall 

be calculated as follows: 

(3) 

where 

1 COPcyo (47) 

COP,,(47) 

1-HLF 

CD=the cyclic degradation coefficient rounded to the nearest .01 

COPCyc (41) as dermed above 

COP .. (41) as defined above 

H LF is the heating load factor calculated as follows: 

HLP QOyo( 47) 

Q •• (47)XT 
CAS-RM-79-102 COMMENT 02

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 of one. conlpressor "on" time 

and one corn pressor "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(Tj) J 

[ 

n· X( T) . ~N PLF(X) Ii(Tj)E(Tj)(Tj) 

+ 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 

the j'h bin, (OF).. . l:=indicated the quantIty followmg the symbol ; is to be summed over all temperature bins. 

RH(T;) =snpplemenlary resistance heat term at N temperature T; required in those cases where 

the heat pump automatically turns off 

(T;< To") or when it is needed to meet the 

balance of the building heating requirements . 

.':'.!=&";,'r:~;'mber of hours in thej,h temperature N bin divided by N=l:. ni and is referred to as 

the "fractional hours'inj'b temperature bin". 

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)=heat pump part load factor. 

The quantities BLCTj ) , 6(Tj ), X (Tj ) , 

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 

and measured building loads 

(DHR)=the minimum and maximum designhea,ting requirement which the heat pump IS Illtely to encounter when installed in a residence, 

rounded off to the nearest standardized DH R 

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- T OD) • 

_ 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(Ti) <1 

(3.413)(E( Ti » 

and Q(Ti) >1 

(3,413)(E(T;» -

1; Ti>ToN 

and Q(T~) >1 

(3.413)(E(T;» -

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

I

BL( Ti) .. 

1; Q( Tj ) ~BL( T i ) 

PLF(X)=I-CD(l-X( Tj» 

RH(Ti ) 

N 

where 

. n' [BL(T;)-Q(Tj)X(T;)Ii(Ti)] 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(Ti )= 

(Q .. (47)-Q .. (17» 

. X(T;-17) Q ,,( 17)+ -----::c3

""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(Tj) 

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(Ti) is thE' huilding load at temperature Ti , in Btu/hI', calculated by: 

BL(Tj ) =(6~5~ :£~) X (C) X (DHR) 

where 

(C)=0.77 is a correction factor which tends to improve the agreement between calculated 

and measured building 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's per 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 , {2Q

' 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. 
CAS-RM-79-102 COMMENT 02

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 the heat pump electrical energy usage in the 

N ph temperature bin divided by the total 

number of bin hours 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 to the four possible cases of heat pump opera- 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( T j). 

BL( T j ) ~Qk-l( T j ) 

E(Tj)_Ek-I(Tj)Xk=l(Ti)l/(Ti ) !Ii 

-r- PLFk-l N 

RH(Ti) !JJ BL(Tj )[I-8'(Tj)) 

N 3.413 

Xk=l( T j

) !lL( T j ) 

Qk=l(Tj) 

PLFk-l=I_~=l(I-X~=l) 

{

OJ Tj~ TOFF 

8'(Tj)= ~; TOFF<Tj~ TON 

1; T;>ToN 

Case H.-Units alternating between high 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( Tj )< 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(Ti

) }J BL(Ti)[l-o'(Ti }] 

N 3.413 

ijc=Z( Tj } - BL( T j ) Xk=l(Ti } Qk=2( Ti } _(jk=I( T i ) 

Xk=Z(Tj} = I-X k=l( Ti ) 

{

OJ Tj-$. TOFF 

8'(Tj ) ~; TOFF<Tj :::, 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 building heating load at temperature Tj • . 

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. 

.at high compressor speed or with 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 pnmp heating load factor. 

P LF .. heat pnmp part load factor (not required for 

_Hand IV.) 

8"( TI) ~ heat pump low temperatnre Cnt-ollt factor. T." as defined in 5.2.1. 

T .. as defined in 6.2.1. CDii-2=the part load del!redatlon factor described In 

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( .... ' -the part load del!redatlon factor described in . sectIOn 2.2.1 and 5.2 for the nnit cycling at . ~ 

low compressor speed or with the single com· tba& IIOI'JIiaIly operates at low 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 ' 
CAS-RM-79-102 COMMENT 02

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 (APF A) 

for a particlliar location and for 

each standardized design heating 

requirement. 

where 

(CLHAWi •• k (95F) ) 

+ (H LH.1 ) (DH R) (C) 

(CLHA ) (Q.h95F» 

(SEER) 

+(HLHA ) (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 heati ng 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. 

(CLHR) (Q.l(95F» 

+ (HLHR)(DHR) (C) 

(CLHR) (Q.l(95F» 

SEER 

+ (HLHR) (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 determined in 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- quirement within 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 Toleranee vv 

•• 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 
CAS-RM-79-102 COMMENT 02

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