NATIONAL BUREAU OF STANDARDS REPORT

6403

CAPACITY TESTS OF GENERAL ELECTRIC HEAT PUMP

MODEL 21 WT33G1

by

J. C. Davis, W. M. Ellis and P. R. Achenbach

Report to

Housing Construction Division

Directorate of Installations

United States Air Force

Washington, D. C.

U. S. DEPARTMENT OF COMMERCE

NATIONAL BUREAU OF STANDARDS
THE NATIONAL BUREAU OF STANDARDS

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NATIONAL BUREAU OF STANDARDS REPORT

NBS PROJECT

1000-30-4835 May 6, 1959

NBS R^^ORT

CAPACITY TESTS OP GENERAL ELECTRIC HEAT PUMP

MODEL 21 WT33G1

by

J. C. Davis, W. M. Ellis and P. R. Achenbach

Air Conditioning, Heating, and Refrigeration Section

Building Technology Division

to

Housing Construction Division

Directorate of Installations

United States Air Force

Washington, D. C.

IMPORTANT NOTICE

NATIONAL BUREAU 01 intended for use within

to additional evaluation

listing of this Report, ei the Office of the Directo however, by the Governr

to reproduce additional

or progress accounting documents Approved for public release by the formally published it is subjected

^ XT 1 T ^ ^ ting, reproduction, or open-literature

Director of the National Institute of emission is obtained In writing from Standards and Technology (NIST) C. Such permission is not needed, on October 9, 201 5. '"'b '^ency wishes

U. S. DEPARTMENT OF COMMERCE
Li
CAPACITY TESTS OP GENERAL ELECTRIC HEAT PUMP

MODEL 21 WT33GI

by

J. C. Davis^ W. M. Ellis and P. R. Achenbach

ABSTRACT

At the request of the Housing Construction Division, Directorate of Installations, United States Air Force, cooling

and heating capacity tests were made of a General Electric

Company heat pump. Model 21 WT33G1 • The specimen was selected

by Air Force representatives from among those furnished by the

manufacturer for Installation at Homestead Air Force Base,

Florida. The indoor and outdoor conditions under which tests

were to be made were agreed upon In a meeting of representatives of the U. S. Air Force, the General Electric Company,

and the National Bureau of Standards. The tests, except for

minor deviations, were made under the procedures and conditions

specified in the American Society of Refrigerating Engineers

Standard No. 16-56. The cooling capacity of the unit varied

linearly from '^^,h00 Btu/hr to 31:»100 Btu/hr for the range of

outdoor temperature from 85°P to 105°F when the indoor conditions were maintained at 80°F dry bulb temperature and 67°F

wet bulb temperature. Lowering the indoor dry bulb temperature

to 75°P decreased the cooling capacity of the unit 2350 Btu/hr

for the same range of outdoor temperatures. The heating capacity varied linearly from 38,400 Btu/hr to 24,600 Btu/hr for

the range of outdoor temperature from 50°F to 20°F when the

indoor dry bulb temperature was maintained at 70 °F and the outdoor coil was kept free of frost. Under severe frosting conditions at an outdoor temperature of 35 the average hourly

heat output was reduced about 2900 Btu/hr or about 9.0 percent by the insulating effect of the frost on the outdoor coil

and the interruption of heating during the defrosting period.

The defrost cycle lasted from 3 to 4 1/2 minutes and was repeated every 35 40 minutes under the test conditions. The

coefficient of performance varied linearly with outdoor temperature under both heating and cooling conditions. The coefficient

of performance was 2.03 at an outdoor temperature of 35°F under

heating conditions, and 1.75 at an outdoor temperature of 95°F

under cooling conditions.

1 . INTRODUCTION

In accordance with a request by letter of October 13, 195Q,

from Colonel Guy H. Goddard, Chief, Housing Construction Division, Directorate of Installations, Headquarters, United States

Air Force, cooling and heating capacity tests were made of a

General Electric heat pump. Model 21 WT3301 . The specimen

tested was one of two chosen by Air Force representatives from

units furnished for installation at the Homestead Air Force

Base, Florida. Since the testing of this unit was not detailed

in purchase specifications, the testing conditions were agreed

upon in a meeting held on October 8 , 1958 , with the United States

Air Force, the General Electric Company, and the National Bureau

of Standards represented.

The following table summarizes the indoor and outdoor temperature and humidity conditions agreed upon for the tests.

Carrying out the three cooling tests at an indoor temperature

of 75°F was made contingent upon the cumulative cost of the

tests. Actually, only two of these tests, at outdoor dry bulb

temperatures of 1 C5 °F and 85 °F, were performed. Cne heating

test was to be made at an outdoor temperature of 35°^ with some

frost accumulation on the outdoor coil to determine the effect

of the frost on the heating capacity and to permit an automatic

defrosting cycle to occur during which the heating function

would be Interrupted. This test was to continue for at least

3 hours.

CCCLING TESTS

Indoor Conditions Cutdoor Temperature

“DB "UB IT TFT. DB

(»p) (°p) {%) (°p)

8 C 67 - 85

8 C 67 - 95

8 C 67 - 1 C5

78 65 - 91

75 - 50 85

75 - 50 95

75 - 50 1 C5

HEATING TESTS • Indoor Temp, DB Cutdoor Temp, DB Special Conditions

TF) TfI

70 2 C Cutdoor coil, frost-free

70 35 ft ?? ft M 70 50 rt ft ff ft 70 35 Cutdoor coil, frosted

- 2 -

One cooling test at an outdoor DB temperature of 95 snd

indoor conditions of 80 °F DB and 67 °F WB was to be made with

an external static resistance on the Indoor blower of O.3O in.

W.G.; which was an Intermediate value between that used by the

General Electric Co. for teating and that anticipated in the

Air Force houses. This test was then to be repeated with an

external static resistance of O.15 in. W.G. and all other cooling tests and the heating tests were to be made without further

adjustment of the air dampers. The adjustments for static pressure were to be made with the compressor operating and the indoor coll condensing room moisture in the normal way. The heating tests were then to be performed without further adjustment

of the air dampers. The air circulation rate of the Indoor

blower was not specified.

The vapor line and liquid line of the test unit were each

to be approximately 25 ft long^ with ten feet of the total being

exposed to outdoor conditions.

The engineering data submitted to the U. S. Air Force by

the General Electric Co. Indicated that the capacity of the

specimen would be as follows:

Outdoor Temp.(°F) Indoor Temp.(°F) Capacity, (Btu/hr)

Cooling Conditions

DB DB WB ' 95 80 67 33.500

Heating Conditions

DB DB WB

20 70 - 24,500

35 70 - 32,000

50 70 - 37.800
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2. DESCRIPTION OF TEST SPECIMEN

The General Electric 21 WT33C1 heat pump is known as a

"split type" or "remote type" heat pump in which one section

of the apparatus is placed outdoors and the other inside the

home at a suitable place for delivering conditioned air. These

two sections were designated respectively on nameplates as

21 WTA40B11 and 21 WTB32E9^ and will be referred to hereafter

in the report as the outdoor unit and the indoor unit.

During the cooling cycle, the coil of the Indoor unit

served as an evaporator, absorbing heat; and during the heating cycle, as a condenser, rejecting heat. This operational

change was accomplished by means of a change in direction of

circulation of the refrigerant through the system, using

thermostatically-controlled solenoids in a four-way valve.

During the tests the solenoids were controlled by a manuallyoperated switch to preclude automatic shifting from cooling

to heating conditions and vice versa. Thermostatic expansion

valves were used as the liquid refrigerant flow control devices

in both the indoor and outdoor units with check valves to bypass each when not needed. Following the new ASRE refrigerant

designations, the refrigerant used was R-22.

A schematic diagram of the heat pump system and auxiliary

test instrumentation is shown in Figure 1. A list of line

sizes between the indoor and outdoor units is shown below. The

liquid and vapor lines were each about 25 ft in length.

During the tests the vapor line was Insulated with a glass

fiber type material 1 in. thickness, vapor sealed.

1. Liquid line except for flowmeter manifold*, in. 3/8 OD

2. Lines in manifold*, in. 1/2 OD

Vapor line, in. 7/8 OD

* Part of testing apparatus.

3.

J

INDOOR UNIT

The indoor unit consisted essentially of a finned coil,

a blower for circulating conditioned air through the duct system of the house, a motor for powering the blower, an expansion valve, a check valve, and a drain pan for collecting condensate. The indoor unit was designed for installation of resistance heaters to supplement compressor heating during extremes of cold weather. However, because of the mild weather

usually prevailing at the Homestead Air Force Base, these heaters were not provided in these units. Material and dimensional

data on the components of the indoor unit are contained in the

Appendix at the end of the report.

Figure 2 shows the Indoor unit ready for test inside the

laboratory enclosure.

OUTDOOR UNIT

The outdoor unit consisted essentially of a finned coll,

a blower, a hermetically-sealed motor-compressor, an expansion

valve, a check valve, a four-way valve, a condensate drain,

and 24-volt controls for operation and defrost. Material and

dimensional data on the components of the outdoor unit are

contained in the Appendix at the end of the report.

Figure 3 shows the outdoor unit with test equipment. Note

the flve-in-one thermocouple system and the thermostat used

for controlling outdoor conditions during the test.

The heat pump system arrived from the manufacturer with

a complete R-22 charge, contained principally in the outdoor

unit. The amount of charge was selected to be adequate for

installations employing moderate length liquid and vapor lines.

The Indoor unit held R-22 under pressure within its coils and

refrigerant lines. Gas was released from the Indoor unit when

the lines between outdoor and indoor units were connected, thus

Indicating that the indoor lines were probably without leaks.

The controls on the outdoor unit consisted of a defrost

control system employing a pressure-sensing device and a defrost termination switch, and a combination high and low pressure switch.


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OFFICE FILE COPY

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PRINT FROM BUREAU OF STANDARDS

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2?830
-5-

Defrostlng was initiated by a pressure-sensing device

actuating the solenoid of the four-way valve to place the

unit on cooling operation. Under these conditions the outdoor coil became a condenser and the frost was melted by the

heat rejection in the condenser. The outdoor fan was stopped

during the defrosting period. The pressure-sensing device

employed a diaphragm,, which was actuated by a threshhold difference between atmospheric pressure and the pressure at the

inlet to the outdoor fan. This pressure difference gradually increased as frost accumulated on the outdoor coil.

The defrost termination switch ended the defrost period

when a sufficiently high temperature was reached in the outdoor ooil to assure that no frost remained. When this switch

opened,, the four-way valve was switched from cooling to heating operation and the outdoor fan was energized again. Defrosting could not be initiated by the pressure-sensing device unless the defrost termination switch was closed, but

this was its normal position during winter operation. During

spring or summer operation the defrost termination switch was

always open.

During the defrosting period, the suction pressure sometimes fell below the setting of the low-pressure cut-off switch.

Stopping of the compressor was prevented, however, by means of

an electrical shunt around the low-pressure switch that was

closed when the defrost relay operated.

The high pressure switch stopped the unit when the discharge pressure was too high and the low-pressure switch stopped the unit when the suction pressure was too low. The high

pressure switch was of the manual reset type and the low pressure switch of the automatic reset type.

3. METHODS OF TESTING

Except for minor deviations, the heat pump was tested under

the conditions described in ASRE Testing and Rating Standard No.

16 - 56 . Figure 4 shows the enclosure housing the Indoor unit

and the 33-vin. square test duct attached to the outlet side

of the unit. This duct housed the nozzle used for measuring

the air circulation rate and the instruments for measuring
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4

TEST

ENCLOSURE;

DUCT

SYSTEM

AND

MANIFOLD

- 6 -

temperature and humidity of the outlet air. Because the nozzle, mixing baffles, and mixing screen Introduced considerable resistance in the outlet duct, an auxiliary blower powered

by a one HP motor was provided at the downstream end of the

33-ln. duct. Required adjustments of external static resistance on the unit- under test were made by a wooden slide-type

damper at the outlet of the auxiliary blower. The air delivery

rate of the Indoor blower depended only on the adjustment of

this damper, since the pulley on the blower was not adjustable.

The auxiliary blower, return air heaters, and humidifier are

shown in Figure 5.

ASRE Standard 16-56 requires that two independent measuring

methods be used during the test to provide greater reliability

in the results. One method, known as the psychrometric method.

Involved measuring the mass flow of air through the indoor unit

and the change in enthalpy of the air between inlet and outlet

of the unit . The other method, referred to as the flowmeter

method. Involved determination of the rate of flow of refrigerant through the indoor coil and the change in enthalpy of

the refrigerant between inlet and outlet of the indoor coll.

A correction to the total enthalpy change of the refrigerant

was necessary, either by adding or subtracting the heat equivalent of the electrical energy supplied to the indoor blower

motor depending on whether the heating or cooling cycle was in

use, before comparing it with the result of the psychrometric

method. Acceptable precision required that the values obtained

by the two methods should not differ by more than six percent.

Mass flow rate of air in the psychrometric method was determined by measuring humidity and temperature conditions of the

air entering the long-radius nozzle and the static pressure drop

across the nozzle. Enthalpy change of the air was determined by

measuring temperature, humidity, and barometric pressure of the

air entering the Indoor unit, and in the duct immediately after

it left the unit.

Flow rate of refrigerant was measured by means of a flowmeter in the liquid line of the system - a Potter Electronic

type with an impeller which generated an electrical pulse on
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each revolution. A Potter Counter coupled to the flowmeter

served to translate the pulses into a volume flow rate. By

measuring the temperature of the liquid in the llne^ the volume flow rate was converted to mass flow rate. Enthalpy change

was determined by temperature and pressure measurements at the

inlet and outlet of the Indoor coll. For accurate measurement

of capacity by the refrigerant flow method it was necessary

that there be no gas bubbles in the liquid refrigerant as it

passed through the meter, and that the liquid refrigerant all

be evaporated in the coil.

It was possible to maintain "state’’ conditions for both

cooling and heating with the use of a test structure having

two controlled temperatures.

During the tests, the energies consumed by the indoor

blower, outdoor fan and compressor were read from separate

watthour meters. Simultaneous readings were also made of

currents and voltages. The various meters, together with

the other instruments for measuring temperature and humidity, are shown in Figure 6.

The same amount of refrigerant chargq was used for the

cooling tests as for the heating tests. By agreement with

the General Electric Co. representative, a run on the cooling cycle at an outdoor temperature of 95 DB and indoor conditions of 80°F DB and 67 WB was made at the beginning of

the test program with a trial charge. An amotint of refrigerant somewhat greater than the factory charge was necessary

because of the volume of the gage lines and other lines not

found in home installations. After adjusting the charge to

obtain the correct pressures and temperatures, operation was

switched to heating at 20°F outdoor temperature. Since pressures and temperatures appeared normal under these conditions,

the charge was left unchanged for all tests under both heating and cooling conditions. It is of interest to note that

specifications at the General Electric plant call for storage

of about 8 lbs of refrigerant in the outdoor unit; whereas 'on

completion of the tests, measurements showed that the test

charge was very close to 9 lbs. The indications were that no

refrigerant leakage occurred during the tests.

Before each test run, steady-state conditions were held

for a minimum of one hour. During all runs, readings were

taken every ten minutes. In most cases the data for an hour

FIGURE

6

TEST

PANEL
27134 b
-8 -

representlng the steadiest conditions were used for evaluating

performance

.

During the heating test at an outdoor temperature of 20°P^

the pressure drop across the liquid flowmeter was excessive

and the flow rate varied in a cyclic manner. For these reasonS;, the flowmeter data were not used in evaluating this test.

The special test with the coll of the outdoor unit operating under frosting conditions was performed at 35°F with a wind-blown mist directed toward the coil face. Before starting

the test, the controls of the unit were arranged so the heat

pump would defrost automatically in the normal sequence determined by its defrost controls.

During the morning of the test, fine spray was blown

towards the outdoor coll and the rate was adjusted until the

defrost cycle occurred once in about 35 to 40 min. During

the test, readings were made every ten minutes, as was done

for all other tests. When defrost cycles occurred during the

periods between readings, the most pertinent pressures, temperatures, and electrical values were read about 2 1/2 minutes after defrost initiation, and when the gages appeared

to have become steady under cooling cycle operation. Each

defrost cycle lasted from 3 to 4 1/2 minutes. The entire

test lasted for 3 hours and all data were used in the calculations .

As a first step in the calculations, capacity was determined in Btu/hr as if no defrost cycles had occurred. As would

be expected, calculations showed that capacity decreased as

frosting Increased during each period between defrosts. As

a second step, the heating effect that was lost during the

defrosting periods was calculated and subtracted from the values

firsts obtained . Certain approximations were necessary in calculation of this last step because of the difficulty in taking

accurate readings during the periods of rapidly changing conditions . Because of these large and abrupt changes in the refrigerant flow in the system, it was Impossible to use the flowmeter during this test.
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4. TEST RESULTS

A. Table 1 summarizes the results obtained on cooling capacity, heating capacity, and coefficient of performance for

the various test conditions agreed upon. These data are plotted separately for the cooling tests and heating tests in

Fig. 7 and 8 , respectively. These figures show that both

the coefficient of performance and the capacity of the heat

pump was very nearly linear with respect to outdoor temperature when the indoor conditions were held constant.

Fig. 7 shows that the cooling capacity of the test specimen was reduced an average of 2350 Btu/hr by lowering the indoor dry bulb temperature from 80°F to 75 a-nd keeping the

relative humidity constant. This difference was constant for

the range of outdoor temperature from 85 °F to 105°F. The change

in indoor dry bulb temperature also changed the coefficient of

performance by a constant amount throughout this same range of

outdoor temperature.

The data in Table 1 show that the static pressure difference between the outlet of the indoor unit and the unit inlet

averaged about O.I8 in. W.G. during the heating tests, which

were performed first. This was the static pressure created in

the system during the heating tests without readjustment of

dampers, after initially adjusting the static pressure to O.I 5

in. W.G. during cooling conditions.

It was noted as the cooling tests progressed that the static pressure at the unit outlet gradually decreased to values

as low as O.O5 and 0.06 in. W.G. This effect was caused by

dust deposits on the air filter located in the unit inlet.

Changing the filter restored the outlet static pressure to

0.15 in. W.G. A comparison of the three cooling tests in Table 1

at an-putdoor temperature of 95 indicates that static pressure variations in the range from 0 . 05 to O. 3 O in. W.G. caused

less than 2 percent change in cooling capacity which is probably less than the precision of this type of test. Air flow

rate, however, was reduced by nearly 10^ as static pressure

changed from O.I 5 in. W.G. to O. 3 O in. W.G. The air filter

was clean for both of these tests.

The variations in static pressure at the unit outlet cannot be correlated satisfactorily with the variations in air

delivery because two blowers were connected in series in the

test apparatus for these tests.
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B. Cooling Test Under Standard ASRE Conditions

Details of a typical cooling test with the outdoor temperature at the Indoor temperature at 80°P DB, and with 67 °F

WB are given below. Static resistance at the outlet of the Indoor blower was O.I 5 in. W.G. for this test.

Summary of Cooling Capacity Values (Btu/hr)

Test

Value

By psychrometrlc method

By flowmeter method

33.520

32,970

Average 33.245

Allowance for deviation of

barometric pressure from

normal 0

Rounded

Value

Total 33.245 33.200

Psychrometrlc Method

Air Temperatures ( °F ) At inlet to enclosure around indoor unit 79-9

At outlet of indoor unit in duct 60 .

5

Temperature difference across indoor coil 19.4

At inlet to outdoor unit 95.0

Wet Bulb Depressions

At inlet to enclosure around indoor unit 13-0

At outlet of indoor unit in duct 2.5

Static pressure across nozzle (in. W.G.) 1.35
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Volume air flow at nozzle (cfm) 1215

Mass air flow at nozzle (lb dry alr/hr) 5^80

Barometric pressure (in. Hg) 29.94

Area of nozzle (sq ft) 0.268

Nozzle coefficient 0

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Static resistance external to unit (in. W.G.) O.I 5

Flowmeter Method

Refrigerant Temperatures ( °F)

In vapor line leaving coil of Indoor unit 49.7

In liquid line entering coll of indoor unit 111.4

Superheat at indoor coll outlet 5.0

Subcooling at indoor coil inlet* 9-2

In discharge line of compressor 233-0

In suction line of compressor 63-4

* Subcooling determined using pressure at

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Refrigerant Pressures (pslg)**

Compressor discharge 290

In liquid line preceding flowmeter 278.5

In liquid line entering coll of indoor unit 271

Pressure drop across flowmeter 7.5

In vapor line leaving coil of indoor unit 76

In suction line of compressor 70.5

** Pressure referenced to compressor level

Potter meter count for 1 minute 32.7***

Motor power consumption (Watts)

Indoor blower 460

Outdoor fan 540

Compressor 4620

Total 5620

Refrigerant flow^ gal. /min *** count for one minute x 100

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Coefficient of performance 1.73

Motor voltages (Volts)

Indoor blower 115.5

Outdoor fan 230.0

Compressor 230.0

Motor current (Amperes)

Indoor blower 4.9

Outdoor fan 2.6

Compressor 20.5

C . Heating Test at 20°F Outdoor Temperature

Details of the heating test with the outdoor temperature

at 20°F and the Indoor temperature at JO°F are given below:

Summary of Heating Capacity Values (Btu/hr)

Test

Value

By psychrometrlc method 24,440

Allowance for deviation of barometric

pressure from normal 110

Total 24,550

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Value

24,600

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Air Temperatures ( °F

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At Inlet to Indoor unit 70-0

At outlet of Indoor unit In duct 89.8

Temperature difference across Indoor coll I 9.8

At Inlet to outdoor coll 20.6
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Relative humidity of Indoor air In duct (^) 12.7

Static pressure across nozzle (in. W.G.) 1.23

Volume air flow at nozzle (cfm) 1195

Mass air flow at nozzle (lb dry alr/hr) 5095

Barometric pressure (in. Hg) 29-69

Area of nozzle (sq ft) .268

Nozzle coefficient . 981

Static pressure at Indoor blower outlet (in. W.G.) .19

Refrigerant Pressures (pslg)*

Compressor discharge 229-5

In vapor line entering coll of Indoor unit 227-0

In liquid line leaving coll of Indoor unit 225-5

In liquid line after flowmeter 217.0

Pressure drop across flowmeter 8.5

Suction pressure at compressor 27.0

* Referenced to compressor level

Other Temperatures

Compressor discharge 217-8

Near 4-way valve between valve and Indoor unit 195-3

At Inlet to coll of Indoor unit 191 - At outlet to coll of Indoor unit 76-5

Suction line at compressor I 8.9

Superheating at compressor IO7 .O**

Superheating at Inlet to coll of Indoor unit 82 . 6 ** Subcooling at outlet to Indoor unit 32 . 0** Superheating at suction line of compressor 15 - 5 **

** Subcooling or superheating determined using pressure

at point of measurement

Motor power consumption (Watts)

Indoor blower 411.5

Outdoor fan 65 O .5

Compressor 3072 .

5

Total 4134.5
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Coefficient of performance 1.74

Motor voltages

Indoor blower 115.0

Outdoor fan 230.0

Compressor 230.0

Motor current (Amperes)

Indoor blower 4.5

Outdoor fan 3.1

Compressor 14.3

D. Heating Test with Frosted Coll

A summary of the capacity values for the heating test with

frosted outdoor coll Is shown below. The outdoor temperature

was 35 °FHeating Capacity Values (Btu/hr)

Test Rounded

Value Value

By psychrometrlc method 31,960

By flowmeter method (estimated*) 29,820

Average of two methods 30,890

Loss In capacity during defrost cycles 2,310

Net value 28,580

Allowance for deviation of barometric

pressure from normal 400

28, 980 29,000

* Estimate based on ratio or psychrometrlc value of

flowmeter values for heating test at 35 outdoors

without frost.
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-15-

E. Motor Currents vs. Nominal Ratings

The current used during the tests by the motors on the indoor blower and outdoor fan was within that allowed by the

National Electric Manufacturers Association Standards, or 1.35

service factor times the nominal rating. Nominal ratings,

allowable maximum current, and the maximum readings observed

during the tests are summarized below:

Nominal Ratings

( amperes

)

Indoor blower 4.30

Outdoor fan 2.35

Allowable

Maximum

Current

( amperes

)

5.80

3.17

Maximum

Current

Reading

( amperes

)

4.95

3.00

Values as low as 2.50 amperes were obtained for the outdoor fan on the cooling tests and 4.43 amperes for the indoor

blower on the heating tests.

Information on the nominal current rating of the compressor motor was not readily available.

F . Temperature drop across 4-way valve, heating test

During heating tests on other heat pumps at 20°F outdoor

temperature, the temperature drop between the compressor and

inlet to the indoor coll was greater than 30°F. In all cases

the vapor line was well insulated where it was surrounded by

the cold outdoor temperature. This decrease in temperature

seemed rather large but there was insufficient instrumentation

used during testing to make a complete analysis of the causes.

During the test on the Model 21 WT33G1 General Electric

Company heat pump extra thermocouples were placed in the outdoor unit, one of which was positioned on the vapor line between the 4-way valve and the Indoor unit. In this way it

was possible to isolate data for the temperature drop due to

heat exchange in the 4-way valve.
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- 16 -

Inspection of the listing of refrigerant temperatures for

the 20°F heating test^ Part C of the Test Results,, will show

that the temperature decreased from the compressor discharge

to the inlet of the coll in the Indoor unit about 26 °F, and

that 22°F of this decrease occurred across the 4-way valve.

A rather high value like this would be expected considering

the large difference in temperature of 199 °F between the discharge gas and the suction gas entering the 4-way valve. Temperatures measured during the 35 ^-nd 50 °F heating tests showed

temperature drops in each case of about 20°F between compressor

discharge and indoor unit,, with about 10°F drop across the 4-

way valve.

G . Calculation of oil in content in refrigerant

To determine the amount of oil flowing through the lines

with the refrigerant and the effect of this oil on the flowmeter registration, the refrigerant was sampled under both

cooling and heating conditions. The refrigerant, taken from

the line while the heat pump was operating, was discharged into

special flasks precooled by dry ice, and then allowed to evaporate slowly as the ice melted, leaving a residue of oil. The

ratio of oil to refrigerant was measured volumetrlcally . This

method was checked by a gravimetric method in which the refrigerant was withdrawn from the heat pump liquid line into

an evacuated copper vessel at room temperature, and the residue of oil weighed after the refrigerant had slowly evaporated

for comparison with the weight of refrigerant and oil. The

ratio of oil to refrigerant was about 0.01 by weight for both

cooling and heating conditions, and agreed reasonably well with

the volumetric determinations.
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-17-

APPENDIX

A . Material and Dimensional Data on Components of Indoor Unit

Coll

Three rows of 3/8 In. OD copper tubing,, 20 tubes each row

1 In. apart, center to center. l4 aluminum fins per Inch

of tube length. Dimension of coil assembly: 20 In. high,

25 in. wide, 4 1/2 in. deep.

Blower

Centrifugal; direct driven; wheel, 9 1/2 In. wide, 10 in.

diameter; scroll, 12 in. wide, l4 1/2 in. diameter.

Blower Motor

General Electric AC 1/6 HP, 1075 rpm. Model 5KCP3966609T.

Thermal protection. GE J3308, 50°C rise. cont. air over

motor. Ser. VRD-2, 4.3 amps. II 5 volts, 60 cycles. Requires oiling.

Expansion Valve

Alco, non-adjustable, thermostatic type, 3/8 In. OD sweat,

237 HG. Charged thermal bulb. External equalizer, 1/4 in.

OD line.

Check Valve

One-half In. sweat, pressure-activated.

Air Filter

One glass fiber filter, throw-away type, 20 in. wide,

20 in. high, 1 in. thick.

Insulation of Cabinet

One in. of glass fiber covered with moisture-resistant

paper.

- 18 -

Descrlptlon of Lines Inside Indoor Unit

Liquid line 3/8 in. OD. Vapor line 5/8 in. OD and 7/8 in.

OD. Header line 5/8 in. OD. Four 1/4 in. distributor

lines to coll. All lines brazed with "Sil-Fos”-type solder.

Housing Dimension, Indoor Unit

21 in. high^ 22 1/2 in. wlde^ 22 1/2 in. deep. Duct opening, 10 1/2 in. by 11 1/h in. Wall thickness .048 in.

Nameplate, Indoor Unit

Model 21 WTB32E9. Motor 1/6 HP, 3-6 F.L. amps, 1 phase,

60 cycles, 115 volts. Test pressure 420 psl, Refrigerant22, Ser. No. 2002900.

B. Material and Dimensional Data on Components of Outdoor Unit

Coll

Three rows of 1/2 in. OD copper tubing, 20 tubes each row,

1 1/4 in. apart, center to center. Twelve aluminum fins

per in. of tube length. Dimension of coll assembly:

25 in. high, 28 1/2 in, wide, 3 1/^4 in. deep.

Fan

Propeller ’’pull through” type, direct driven, 20 in. diameter, for 1/2 in. shaft. 5 blades, metal, approximately

40° pitch.

Fan Motor

» r. General Electric 1/3 HP, 1075 npm. Model 5KCP37MG1351,

230 volts, 2.35 amps, 60 cycles, 1 phase, thermal protection, 50 °C rise, cont. air over motor, 1/2 in. shaft,

Ser. No. WRD-2. Requires oiling, capacitor start.
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Motor-Compressor Unit

General Electric^ Refrlgerant-22^ Model 21CT 4HH41, 230

voltSj 1 phase, 60 cycles. Serial No. 1328738-40, F.L,

amps. 21.5, L.R, amps. 98 , test pressure 350 psi. Rubber

mounted. Hermetic sealed. Includes thermal overload and

external locked rotor protector, both automatically reset

Expansion Valve

Alco, non-adjustable, thermostatic type, 5/8 In. OD sweat

external equalizer, 1/4 In. line, charged thermal bulb.

Check Valve

Pressure-activated, 1/2 in. OD sweat.

Four-Way Valve

Alco, Solenoid-operated on low voltage 24 volts.

Other Components

Drier in liquid line 1/2 in. OD sweat, sight glass, 1/2

in. OD sweat.

Insulation in Housing

One Inch of glass fiber, 9 in. by 3 I 1/2 in. under top

cover to cover coll assembly only. No foil.

Description of Lines of Outdoor Unit

Discharge line from compressor to 4-way valve 1/2 in. OD.

Suction line from compressor to 4-way valve, 7/8 in. OD.

Line from 4-way valve to coil 7/8 in. OD. Vapor line inside of unit 7/8 in. OD. Liquid line inside of unit 1/2

in. OD. Three distributor lines from expansion valve to

coll 1/4 in. OD. Header line 7/8 in. OD. All lines

brazed with ”Sil-Fos"-type of solder.

Housing, Outdoor Unit

25 1/2 In. high, 31 1/2 In. wide, 28 In. deep. Thickness,

.048 In.

Nameplate Covering Outdoor Unit

General Electric Weathertron Model 21 WTA40B11, Ser. No.

253321S40, Fan motor 1/3 HP, 2.35 amps, 230 volts, 1 phase

60 cycles, compressor motor amps. 20.0, 230 volts, 1 phase

60 cycles, L.R, amps. 96 Ref. -22, 8 lbs, high side test

420 psl, low side test I 50 psl. Cat. No. 2 IDIOII 387 , Ser. No. 353321840.

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A. V, AftUlt, hlrrctor TItK NATIOIVAI. lUJnKAII or STAm^Aims

Tlic scope ot nctlvitlcs of the Nntiotinl Bumiu of Slntiflnrcls nl its hcjiH<(ii!irlcrs in Wii.shinf(l()n,

f). C., rind Its oinjor Inhorotorlns in Honidor. Colo., is stif'Rc'slod in Mie f<»llf)\vitif' lislinp; c»f ilm

divisions nnd sections engoged In Icchnirnl work. In grnernl, enrh sedion rorrics oof spet inli/cd research, development, and engineering in (he field indif!nt<*d hy Its title. A brief ‘deseription of

the mtivltles, and of (he resultant ptihlications. appears on the inside front i;over. WASIIINOTOIV, BP. €.

Klnctl*lclty nn€!HlftCtroiil<?S). Kesisinnre and Reactance. Electron Devices. Electrical In- strutnentSi Magnetic Measurements. Dielectrics.. Engineering Electronics. Electronic Instru- mentation. Electrochemistry.

Optics and Metrology. Photometry and Colorimetry. Optical Instruments. Photographic

Technology. Length. Engineering Metrology.

Hont. Temperature Physics. Thermodynamics. Cryogenic Physics. Rheology. Engine Fuels. Free Radicals Research.

Atomic and IlndSntlon l^'liyfllcs. Spectroscopy. Radiometry. Mass Spectrometry, Solid

State Physics. Electron Physics. Atomic Physics. Neutron Physics. Radiation Theory.

Radioactivity, X-rays. High Energy Radiation. Nucleonic Instrumentation. Radiological

Equipment. ' Cltcxnlstry. Organic Coatings. Surface Chemistry. Organic Chemistry. Analytical Chemistry.

Inorganic Chemistry. Electrodeposilion. Molecular Structure and Properties of Gases. Phy.sical

Chemistry. Thermochemistry. Spectrochemistry. Pure Substances.

Moclinnlcs* Sound. Mechanical Instruments. Fluid Mechanics. Engineering Mechanics. Mass

and Scale. Capacity, Density, and Fluid Meters. Combustion Controls. Organic and FiliroilN Rubber. Textiles. Paper. Leather. 'festing aiul Specifications. Polymer Structure. Plastics. Dental Research,

Mclalllirgy* Thermal Metallurgy. Chemical Metallurgy. Mechanical Metallurgy, Corrosion.

Metal Physics.

Mineral l*roductSo Engineering Ceramics. Glass. Refractories, Enameled Metal-s. Concreting

Materials, Constitution and Microstructure.

Illlilxilug Tecllliology. Structural Engineering. Fire Protection. Air Conditioning, Heating,

and Refrigeration. Floor, Roof, nnd Wall Coverings. Codes and Safety Standards. Heal Transfer.

A|»plied MallieiaaticN. Numerical Analysis, Compulation. Statistical Engineering, Mall>e- matical Physics.

llaia l*roeesslag Sys<cilfis>j. SEAC Engineering Group. Components and 'I'cchniques. Digital

Circuitry. Digital Systems, Anolog .Systems. Application Engineering.

• Office of Basic Instrumentation. * Oifice of Weights and Measures. COLOIBAIIIO

<*B*yogO«llo Bi)ngin<N'^l*ing. Cryogenie E(|iiipm(!iU. Cryogenie Procoss(;s. P.operlies of Materials. Gas Lfijuefactiori.

lSa<ll<l fi*r4»|»agali<ia Upper Alinosphere R(\seareh. lomtspheri j Researeh. Regular Prtjpagation Servi('.(!s. Sui\-Earlli Relationships. VHI'' Resc'areh. Ionospheric Communiealion

.Systems.

BlaUio BVo|iaga«ii«»ii BCagSiH^orSag. Dula Re.liielion lostnimenlalion, Mo.lulalion Systems.

Navigation SysUntis. Radio Nois(!. Tidposplierie M<iasnreioeiils. 'I'roposplu'iie Analysis. Radio

Systems Appliewtion Engim^ering. RiidiccMc^leorology.

Htudia .SiaiuBaas-dN. High Eretpieocy l;l(M:trie^d Siandards. Radio Rroadcast S<-rviee. High

I'i’(a|ueney linpedagie.’.: .Standards, I'.leetidnie. (.idiliralioii (ieiiler. Miei'ovvavi' Pliysies. Miernwiive

Circuit .Sliuidardb.