NATIONAL BUREAU OF STANDARDS REPORT

6699

CAPACITY TESTS OF TWO PEERLESS HEAT PUMPS,

MODELS CPA584-1A/54CPH-A AND CPA384-1A/34CPH-A

Manufactured "by

Peerless Corporation

Indianapolis, Indiana

by

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

Report to

McCoy Air Force Base

Orlando, Florida

U. S. DEPARTMENT OF COMMERCE

NATIONAL BUREAU OF STANDARDS
THE NATIONAL BUREAU OF STANDARDS

Functions and Activities

The functions of the National Bureau of Standards are set forth in the Act of Congress, March

3, 1901, as amended by Congress in Public Law 619, 1950. These include the development and

maintenance of the national standards of measurement and the provision of means and methods for making measurements consistent with these standards: the determination of physical constapls and

properties of materials; the development of methods and instruments for testing materials, 'devices,

and structures; advisory services to government agencies on scientific and technical problems; in- vention and development of devices to serve special needs of the Government; and the development

of standard practices, codes, and specifications. The work includes basic and applied researcli,

development, engineering, instrumentation, testing, evaluation, calibration services, and various

consultation and information services. Research projects are also performejd, for other government

agencies when the work relates to and supplements the basic program of the Bureau or when the Bureau’s unique competence is required. The scope of activities is suggested by the fisting of

divisions and sections on the inside of the back cover.

Publications

The results of the Bureau’s work take the form of either actual equipment and devices or published papers. These papers appear either in the Bureau’s own series of publications or in the journals

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of Documents, Government Printing Office, Washington 25, D.C.
NATIONAL BUREAU OF STANDARDS REPORT

NBS PROJECT NBS REPORT

1003-30-10531 March 28, I96O 6699

CAPACITY TESTS OF TWO PEERLESS HEAT PUMPS,

MODELS CPA584 - 1 A/54CPH-A AND CPA384- 1 A/34 CPH-A

Manufactured by

Peerless Corporation

Indianapolis, Indiana

by

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

Air Conditioning, Heating, and Refrigeration Section

Building Technology Division

to

McCoy Air Force Base

Orlando, Florida

NATIONAL BUREAU OF ST

intended for use within the

to additional evaluation and r listing of this Report, either the Office of the Director, Na

however, by the Government

to reproduce additional copie

IMPORTANT NOTICE

Approved for public release by the

Director of the National Institute of

Standards and Technology (NIST)

on October 9, 2015.

irogress accounting documents

mally published it is subjected

reproduction, or open-literature

;ion is obtained in writing from Such permission is not needed,

prepared if that agency wishes

<NBS>

U. S. DEPARTMENT OF COMMERCE

NATIONAL BUREAU OF STANDARDS

Capacity Tests of Two Peerless Heat Pumps^

Models CPA584-1A/54CPH-A and CPA384-1A/34CPH-A

by

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

ABSTRACT

Tests were performed to determine the heating and cooling

capacity of a 5-ton and a 3-ton Peerless heat pump intended for

use in the housing development at McCoy Air Force Base, Orlando,

Florida. The original letter, outlining specifications and test

conditions, was amended after discussions with the Contracting

Officer and corroborated by letters dated October 21, 1959j) and

December 8 , 1959- The tests were performed using a psychrometric

calorimeter, as described in ASRE Standard 16-56, Standard Methods

for Testing and Rating Air Conditioners. All cooling tests were

performed at 95 °^ outdoors and 80°F DB, 67 WB, indoors. All

heating tests were performed at 30°F outdoors and 70°F indoors.

For the 5-ton heat pump, the cooling capacity was 53^800 Btu/hr

as compared to 53,000 Btu/hr required by specifications. The

heating capacity, including the capacity of the supplementary resistance heater, was 60,700 Btu/hr as compared to a requirement of

62,000 Btu/hr. When another supplementary resistance heater of

the same physical dimensions and same manufacturer, submitted at

a later date, was used, the total heating capacity was 61,900 Btu/hr.

For the 3-ton heat pump, the cooling capacity was 32,600 Btu/hr as

compared to 30,000 Btu/hr required by specifications. The heating capacity, including the capacity of the supplementary resistance heater, was 43^100 Btu/hr as compared to a requirement of 46,000

Btu/hr. The heating capacity, using the same alternate supplementary heater mentioned above, was 44,300 Btu/hr. When the 5-ton

heat pump was tested, the air flow rate across the indoor coil was

close to that specified for heating, or I85 O cfm; but the air flow

rate for cooling was about 95 cfm lower. Later determinations indicated that the cooling capacity for this system would probably

have been I 5 OO Btu greater if the air flow rate had been I85 O cfm.

During the tests on the3-ton heat pump, the air flow rate was about

80 cfm greater than the 1100 cfm specified for the test. Later determinations Indicated that the capacity for this system would probably have been 250 Btu/hr less if the air flow rate had been 1100

cfm.
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1 . INTRODUCTION

In accordance with a request from Captain Paul R. Miller,

Contracting Officer, McCoy Air Force Base, Orlando, Florida, by

letter dated October 19 , 1959^ tests were made to determine the

heating and cooling capacity of two Peerless heat pumps. One, a nominal 5-ton system, was designated as CPA584-IA/54CPH-A; and

the other, a nominal 3-ton system, as CPA384-IA/3'4CPH-A.

Contract specification requirements and test conditions were

outlined in written material and drawings supplied with the letter

of October 19^ 1959- Following the receipt of this letter, discussions were held by telephone with Captain Miller and several

amendments were made in the test conditions. These amendments

were authorized by letters dated October 21, 195^ and December 8,

1959.

The specification requirements and the test conditions which

applied after amendment are shown below:

SPECIFICATION CAPACITY VALUES

FOR 5 -TON HEAT PUMP

Minimum Minimum Minimum

Total Total Heating

Building Cooling Heating Supplied

Type Requirement Requirement by Compres

(Btu/hr

j

(Btu/hr) (Btu/hr)

Minim.um

Heating

Supplied

by

Supplementary

Strip Heater

(Btu/hr)

0-G 46,500 53,000

0-H 46,000 58,000

0-J 53,000 62,000

31.800

34.800

37,200

Difference between

total heat required and amount

obtained by compressor in laboratory tests.

TEST CONDITIONS FOR 5-TON HEAT PUMP

Design Test Conditions

Cooling Heating

T'Tl “ (“PJ

Indoors 80 DB, 67 WB 70 OB

Outdoors 95 DB, 78 WB* 30 DB

External Static

Pressure on

Indoor Unit

(In. W. G.

)

0.4

Rate of Air Flow

Across Indoor Coil

1850

* In the NBS facility, it would have been difficult to control

humidity in the air section simulating the outdoor air. Because
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of this and since humidity of the air entering the outdoor coil

during the cooling cycle has a negligible effect on capacity for

a dry coil_, no effort was made to control this atmospheric condi'

tion

.

SPECIFICATION CAPACITY VALUES

FOR 3 -TON HEAT PUMP

Building

Type

Minimum

Total

Cooling

Requirement

Minimum

Total

Heating

Requirement

Minimum

Heating

Supplied

by Compressor

Minimum

Heating

Supplied

by

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Strip Heater

(Btu/hr

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(Btu/hr) (Btu/hr ) (Btu/hr

j

A-A 20,500 32,000 19,200 Difference

A-B 24,500 36,000 21,600 between total

A-C 25,500 41,000 24,600 h'eat required

0 -A 26,000 40,000 24,000 and

0-B 25,500 41,000 24,600 amount

0-C 26,000 43,000 25,800 obtained by

0-D 27, 000 43,000 25,800 compressor

0-E 29,500 46,000 27,600 in laboratory

0-F 30,000 45,000 27, 000 tests

.

TEST CONDITIONS FOR

Design Test Conditions

Cooling Heating

3 -TON HEAT PUMP

External Static

Pressure on

Indoor Unit

Rate of Air Flow

Across Indoor Coil

(-Fj (In. W. G.

)

(CFW}

Indoors 80 DB, 67 WB 70 DB 0.3 1100

Outdoors 95 DB, 78 WB* 30 DB

* In the NBS test facility, it would have been difficult to control

humidity in the air section simulating the outdoor air. Because

of this and since humidity of the air entering the outdoor coil

during the cooling cycle has a negligible effect on capacity for

a dry coll, no effort was made to control this atmospheric condition .
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Inspection of drawings supplied by McCoy Air Force Base showed

that the lengths of the liquid and vapor lines were specified at

values ranging from about 12 ft to about 32 ft. Based on this

specification, the length of each line In the test Installation

was 25 ft.

2. DESCRIPTION OP TEST SPECIMENS

The two heat pumps are known as "split type" or "remote type"

heat pumps In which one section of the apparatus Is placed outdoors

and the other Inside the home at a suitable place for delivering

conditioned air. The 5-ton heat pump tested consisted of a Model

No, CPA584-1A outdoor unit with a 54CPH-A Indoor unit; and the

3-ton heat pump of a CPA384-1A outdoor unit with a 34CPH-A Indoor

unit. The operational features for both heat pumps were very nearly

the same. These are described as follows;

During the cooling cycle, the coll 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 a thermostatically-controlled solenoid In

a four-way valve. During the tests, the solenoid was controlled by

a manually-operated switch to preclude automatic shifting from cooling to heating conditions and vice versa. Capillary tubes were used

as a liquid refrigerant flow control device In both the Indoor and

outdoor units with a check valve In the by-pass line around the capillary tubes of the outdoor unit. No check valve was provided In the

Indoor unit. On the heating cycle, therefore, the refrigerant flowed

through the capillary tubes In the reverse direction, since no alternate refrigerant flow path was provided. Following the new ASRE

refrigerant designations, the refrigerant used was R-22.

A schematic diagram of the 5-ton heat pump system and auxiliary test Instrumentation Is shown In Figure 1, and of the 3-ton

system In Figure 2. A list of line sizes between the Indoor and

outdoor units for the two heat pumps Is shown below. The liquid

and vapor lines were each about 25 ft long.
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5-Ton 3-Ton

1. Liquid line except flowmeter manifold, in. 1/2 OD 3/8 OD

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

3. Vapor line, in, 3/-4 OD** 3/^4 OD

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** Two lines, 5-ton unit. Two 3/4- in. OD lines were used to provide an acceptable gas velocity in the vapor line, and to limit

the number of sizes that needed to be stocked by the manufacturer

2.1 Indoor Units

The indoor units of both heat pumps consisted of 2 finned coils

a blower for circulating conditioned air through the duct system of

the house, a motor for powering the blower, capillary tubes, and a drain pan for collecting condensate. These units also Included resistance heaters to supplement compressor heating during extremes of

cold weather. The supplementary strip heaters in the two heat pumps

were physically interchangeable.

Figure 3 shows the indoor unit of the 5-ton heat pump and

Figure 4- shows that of the 3-ton heat pump.

2.2 Outdoor Units

The outdoor unit of the 5-ton heat pump consisted of 3 finned

colls, a hermetically-sealed motor-compressor, a set of capillary

tubes, a check valve, a four-way valve and controls for operation

and defrost. The 3-ton heat pump consisted of essentially the

same components as the 5-ton heat pump except there were two coils

Instead of three.

The outdoor unit Installed in a home also includes a defrost

control system employing a temperature differential device, an outdoor thermostat, high- and low-pressure switches, and a compressor

crankcase heater. All of these devices, except the high-pressure

switch, were left out of the system during the tests.
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Figupe 5 shows the outdoor unit of the 5-ton heat pump with

test equipment and Figure 6 shows the outdoor unit of the 3-ton

model. Only one coil appears In Figure 5j h^t the unit actually

has two other colls each Identical to the one showing. Likewise^

only one coll appears in Figure 6, but the unit has another coil

identical and 90 degrees displaced from that showing. Note on

both figures the five-ln-one thermocouple system and the thermostat used for controlling outdoor conditions during the test.

2 . 3 Controls

Defrost Control (Ranco D-50) Although no defrosting controls were

used during the tests^ defrosting was initiated during heating operation on an Increase over a set differential between

the outdoor ambient temperature and the refrigerant temperature of the outdoor coil, which opened a defrost switch. Opening of the defrost switch contacts de-energized the four-way

valve solenoid and also shut off the outdoor fan. The system

thus was placed on the cooling cycle. Under these conditions,

the outdoor coil became a condenser and the frost was melted

by heat rejection.

The defrost switch consisted of a temperature sensing

bulb, which sensed the refrigerant temperature of the outdoor

coil; and a gas-filled ambient sensing capillary tube. The

bulb and gas-filled capillary were connected to separate bellows. Both bellows acted upon a common lever connected to

the switch contacts. When the coll frosted or iced up, the

refrigerant temperature was reduced so that the pressure of

the refrigerant sensing bulb was less than that of the capillary. This caused the switch to open, a relay de-energized

the reversing valve, which caused the unit to go on the cooling cycle, also cutting off the outdoor fan. The system remained on the cooling cycle until the pressure of the refrigerant sensing bulb was great enough to overcome the pressure of the ambient sensing capillary, and the temperature

differential was no greater than the set value.

During the defrost period, the suction pressure sometimes, in home operation, goes below the setting of the lowpressure cut-off switch. Stopping of the compressor during

this operation was prevented, however, by means of an electrical shunt around the low-pressure switch during the defrost cycle.
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Hlgh- and Low-Pressure Switches The high-pressure switch stopped

the unit when the discharge pressure was too high^ and the

low-pressure switch stopped the unit when the pressure was

too low. A table showing high- and low-pressure switch performance for the two heat pumps is given below.

3 -TON HEAT PUMP

Low-Pressure Switch pslg.* 1. Setting adjustable from 10-30 *

2. By-passed after initiation of defrost to prevent

shut-off during surges of low suction pressure.

By-pass not removed from circuit until 3 minutes

have elapsed after termination of defrost.

3. By-passed throughout the heating cycle to allow

for low suction pressures which occur when the

outdoor temperature is near 0°F.

4. Manually reset at Indoor thermostat.

High-Pressure Switch

1. Factory-set at about 405 psig.

2. Manually reset at Indoor thermostat.

3 -TON HEAT PUMP

Low-Pressure Switch

1. Setting adjustable from 10-30 psig.*

2. By-passed after initiation of defrost to prevent

shut-off during surges of low suction pressure.

No time delay in removal of by-pass after termination of defrost, as was included in 5-ton unit.

3. By-passed during heating cycle to allow for low

suction pressures which occur when the outdoor

temperature is near 0°F.

4. Automatic reset in outdoor unit.

* Special wrench required. The Peerless Corporation representative

requested that the company be consulted before adjustment is made

of this control in the field.
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Hlgh-Pressure Switch

1. Factopy-set at about 405 pslg.

2. Manually reset In outdoor unit.

Indoor thermostat (Mlnneapolls-Honeywell Model T 870_, two stage)

The first stage starts the heat pump for either heating or

cooling^ the solenoid in the four-way valve being energized

on heating. The second stage (heating only) turns on the

supplementary strip heat if the temperature drops more than

one and three-fourths degrees below the setting of the thermostat. The indoor fan can be controlled manually at this

thermostat even though the compressor is inoperative. In

the case of the 5-ton unit^ the high- and low-pressure

switches can be reset at the Indoor thermostat if either

one stops the compressor.

Outdoor thermostat (Ranco Corp. No. A-ll) This thermostat was in

series with the second stage of the Indoor thermostat to prevent the operation of supplementary heaters unless the outside temperature falls below a predetermined setting. The

thermostat worked on about a 7-degree differential^ closing

at about 40°F and opening at about 47 °F.

Crankcase Heater Both the 5-ton and 3-ton units were equipped with

an 80-watt heater (industrial Equipment and Engineering Co.^

St. Louis, Mo.), attached to the crankcase of the compressor

to reduce absorption of refrigerant in the oil and to prevent excessive foaming and ebullition of the oil when starting the compressor. The heater is always in operation, but

is needed only after the heat pump has been shut down either

in cold weather, in a warm season when the outdoor temperature is colder than the Indoor temperature, or when the system is greatly overcharged.

Material and dimensional data on the components of the Indoor

and outdoor units are contained in the Appendix at the end of the

report

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3. METHODS OF TESTING

Except for minor deviations, the heat pumps tested under

the conditions described in ASRE Testing and Rating Standard No,

16-56. Figure 7 shows the enclosure housing the Indoor unit and

the 33“in. square 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 temperature and humidity of

the outlet air. Because the 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-in. duct. Required adjustments of external static

resistance on the units under test were made by a wooden slidetype damper at the outlet of the auxiliary blower. The air delivery rate of the indoor blower depended on the adjustment of this

damper in conjunction with the adjustable pulley on the fan motor.

The auxiliary blower, return air heaters, and humidifier are shown

in Figure 8.

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 coll and the change in enthalpy of the refrigerant between

inlet and outlet of the Indoor coil. 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. 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 determ.lned by measuring humidity and temperature conditions of the air

entering the long-radius nozzle and the static pressure difference

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. The flowmeter was a Potter

electronic type with an impeller, which generated an electrical
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pulse on each revolution. A Potter Counter coupled to the flowmeter served to translate the pulses into a volume flow rate.

The temperature of the liquid in the line was measured so the

volume flow rate could be converted to mass flow rate. Enthalpy

change of the refrigerant was determined from the temperature and

pressure measurements at the inlet and outlet of the Indoor coil

and the refrigerant tables. 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

flowmeter and the point of measurement of temperature for enthalpy

determilnatlon, and that all of the liquid refrigerant be evaporated in the coil.

It was possible to maintain "state” conditions for both the

indoor and outdoor units during cooling and heating operation with

the use of a test structure having two controlled-temperature

spaces

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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 watthour meters, together with the other instruments for

m.easuring pressure, pressure difference, temperature and humidity,

are shown in Figure 9 -

A refrigerant charge of approximately l4 lbs, measjced after

all corrections were made for gages and lines, was used for the

5“ton unit. Ten pounds of refrigerant were used for the 3-ton

unit. During the tests of both heat pumps, charging was done on

the cooling cycle, after which the system was exposed to heating

conditions and sufficiency of charge determined. No change of

charge was made thereafter for the cooling tests.

Specifications required that the tests be performed using an

air delivery rate over the indoor coll of 185 O cfm for the 5-ton

heat pump, and 1100 cfm for the 3-ton heat pump. In either case,

since the density of the air crossing the coil was different for

the cooling test and the heating test, it was Impossible, unless

pulley adjustments were made, to perform the tests at the specified rate for both cooling and heating. It was considered advisable to perform the tests without change in the pulley adjustment between heating and cooling or vice versa, since the pulley

adjustment remains the same when the heat pump is in the home.
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The cooling test for the 5-ton unit was performed at the

standard conditions of 95°F outdoor temperature,, 80°F DB and

67°F WB inside. At these conditions, it was not possible to

obtain subcooling in the liquid line entering the indoor unit.

Consequently, the flowmeter method could not be used for this

test. Another test was performed with the outside temperature

at 91 °F and with the inside conditions the same as the original

test, but with artificial subcooling in the liquid line between

the outdoor and indoor units. From this test, it was possible

to obtain a comparison between the psychrometrlc and flowmeter

results. This comparison resulted in a ratio of 100/97*3 fon

the ratio of the psychrometrlc value/flowmeter value, which in

turn was subsequently used to determine a flowmeter value for

the cooling test at the standard test conditions. This difficulty was not encountered during any other cooling or heating

test for either type of heat pump. The ratio of the psychrometrlc value to the flowmeter value for these other tests agreed closely with 100/97 . 3 . Both the 5-ton and 3-ton outdoor units had vertical discharge

of air from the fan as shown in Figures 5 snd 6 . The temperature

of the air entering the outdoor colls was checked several times

during the tests to be certain that there was no short-circuiting

of discharge air back into the colls caused by the characteristics

of the test facilities, and to give assurance that the air temperature entering each coil was the same.

Following the tests for cooling and heating capacity of the

2 heat pumps, the power consumption of the supplementary strip

heater for each heat pump was measured. For this determination,

230 volts were applied to the strip heater for a period of one

hour while the energy consumption was measured with a calibrated

watthour meter and checked with voltage and current readings which

were made every 15 minutes. The results of the 2 tests showed a lower electrical energy consumption than required by specifications. As a result, and in conformance with an authorizing letter

of December 29^ 1959 from Captain Miller, another strip heater was

tested at the same voltage. The energy consumption, as shown

under Test Results was greater.

The energy consumption of the crankcase heater for both the

5 “ton and 3 -ton heat pumps was measured using 230 volts and the

same method of measurement as for the strip heaters. These heaters

were disconnected during the tests on the heat pumps.
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4 . TEST RESULTS

4. 1 5-ton Unit

A. Cooling Test under Standard ASRE Conditions

Details of the cooling test on the 5-ton heat pump with outdoor temperature at 95°F, and Indoor conditions at 80°P DB, and

67°P WB^ are given below.

Summary of Cooling Capacity Values (Btu/hr)

5-Ton

Test

Value

Unit

Rounded

Value

By psychrometrlc method

By flowmeter method*

54,510

53,030

Average 53.770

Correction for deviation

pressure from normal

of barometric

0.0

Total 53.770 53,800

* Due to Inability to obtain both subcooling and superheating during

the test at Standard ASRE conditions^ both conditions being necessary for use of the flowmeter method, this value was calculated

using the ratio of the psychrometrlc value/flowmeter value determined during another test In which conditions were such that both

subcooling and superheating existed (See Methods of Testing ).

Psychrometrlc Method

Air Temperatures ( °F

)

At Inlet to enclosure around Indoor unit 79-8

At outlet of Indoor unit In duct 60.7

Temperature difference across Indoor coll 19»1

At Inlet to outdoor unit 95-0

Wet Bulb Depressions ( °F

)

At Inlet to enclosure around Indoor unit 12.9

At outlet of Indoor unit In duct 3-7
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Relatlve HiAmldltles {%)

At Inlet to enclosure around indoor unit 50.7

At outlet of indoor unit in duct 79-7

Static pressure across nozzle (in. W.G.) 0.67

Volume air flow at nozzle (cfm) 1755

Mass air flow at nozzle (lb dry air/hr) 7900

Barometric pressure (in. Hg) 29.87

Area of nozzle (sq ft) 0.5^44

Nozzle coefficient 0 . 99

Static resistance external to unit (in. W.G.) 0.39

Refrigerant Temperatures ( °F

)

In vapor line leaving coil of Indoor unit 46.5

In' liquid line entering coil of Indoor unit 118.4

In discharge line of compressor 227-5

In suction line of compressor 61.7

Superheat at Indoor coll outlet 3.2 (pslg)* Refrigerant Pressures *

Com_pressor discharge 273.0

In liquid line preceding flowmeter 264,0

In liquid line entering coll of Indoor unit 260.5

Pressure drop across flowmeter 3.5

In vapor line leaving coil of Indoor unit 74.0

In suction line of compressor 70.0

* Pressure referenced to compressor level

Motor Power Consumption (watts)

Indoor blower 730

Outdoor fan 630

Compressor 6930

Total 8290
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Coefficient of performance 1.90

Motor Voltages (volts)

Indoor blower 113.0

Outdoor fan 230.0

Compressor 230.0

Motor Current (amperes)

Indoor blower 8.5

Outdoor fan 3.4

Compressor 30.3

B . Heating Test at 3 Q°F Outdoor Temperature, ^-^on Unit

Details of the heating test with the outdoor temperature at

3

'0 °F and the Indoor temperature at 70 °^ given below.

Summary of Heating Capacity Values (Btu/hr)

5 -Ton

Test

Value

Unit

Rounded

Value

By psychrometrlc method

By flowmeter method

45,790

43,980

Average 44,885

Correction for deviation

pressure from standard

pressure

of barometric

barometric

150

Total 45,035 45,000
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Psychromet rlc Method

Air Temperatures ( °F ) At Inlet to indoor unit 70-1

At outlet of indoor unit in duct 93-8

Temperature difference across indoor coil 23*7

At inlet to outdoor coil 30-0

Wet Bulb Depression ( °F)

At outlet of indoor unit in duct 34.4

Relative Humidity (^)

At outlet of Indoor unit in duct 8.7

Static pressure across nozzle (in. W.G.) 0.72

Volume air flow at nozzle (cfm) l880

Mass air flow at nozzle (lb dry alr/hr) 7990

Barometric pressure (in. Hg) 29-76

Area of nozzle (sq ft) 0.544

Nozzle coefficient 0 . 99

Static pressure at Indoor blower outlet (in. W.G.)0.38

Flowmeter Method

Refrigerant Temperatures ( °F)

Compressor discharge 215 •

5

Compressor discharge after 4-way valve 175.0

At inlet to coll of Indoor unit 17'^.

5

At outlet of coil of Indoor unit 91-5

Suction line at compressor l8.5

Superheating at compressor discharge 104.3*

Superheating at inlet to coil of Indoor unit 64,9*

Subcooling at outlet of Indoor unit 12.5*

Superheating at suction line of compressor 5.5*

* Subcooling and superheating determined using pressure at point

of measurement.
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Refrlgerant Pressures (pslg)**

Compressor discharge 232.5

In vapor line entering coil of indoor unit 230.5

In liquid line leaving coil of Indoor unit 213.0

In liquid line after flowmeter 213.0

Pressure drop across flowmeter Negligible

Suction pressure at compressor 36.0

** Referenced to compressor level.

Potter meter count for 1 minute 28.17***

*** Refrigerant flow, gal. /min =

co’ant for one minute x 100

3404

Motor Power Consumption (watts)

Indoor blower 720

Outdoor fan 750

Compressor 5020

Total 6490

Coefficient of performance 2 . 03

Motor Voltages (volts)

Indoor blower II 5 .O

Outdoor fan 230.0

Compressor 230,0

Motor Current (amperes)

Indoor blower 8.3

Outdoor fan 4.0

Compressor 22.1
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- 16 -

C . Power Consumption of Strip Heater

Readings of the energy dissipated by the strip heater which

came with the 5-ton indoor unit were made every fifteen minutes

for a period of one hour with the following results:

Watthour meter value (watts) 4590

Average terminal voltage (volts) 230

Average current (amperes) 20,0

Voltage times current (watts) 4600

Heat energy (Btu/hr) 15,700

D. Power Consumption of Crankcase Heater (watts) 80

4 . 2 3~ton Unit

A . Cooling Test under Standard ASRE Conditions

Details of the cooling test with the outdoor temperature at

95 and the indoor conditions at 80°F DB and 6j°F WB, are given

below.

Summary of Cooling Capacity Values (Btu/hr)

3-Ton

Test

Value

Unit

Rounded

Value

By psychrometrlc method

By flowmeter method

33,030

32,100

Average 32,565

Correction for deviation

pressure from normal

of barometric

80

Total 32,645 32,600
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Psychrometrlc Method

Alp Temperatures ( °P)

At inlet to enclosure around Indoor unit 80.0

At outlet of indoor unit in duct 60.5

Temperature difference across coil 19.5

At inlet to outdoor unit 9'^.

7

Wet Bulb Depressions ( °P)

At inlet to enclosure around indoor unit 13.1

At outlet of Indoor unit in duct 3-1

Relative Humidities {%)

At inlet to enclosure around Indoor unit . 50.3

At outlet of Indoor unit in duct 83.3

Static pressure across nozzle (in. W.G.) 1.13

Volume air flow at nozzle (cfm) 1115

Mass air flow at nozzle (lb dry air/hr) -4976

Barometric pressure (in. Hg) 29.60

Area of nozzle (sq ft) 0.268

Nozzle coefficient O. 98 I

Static resistance external to unit (in, W.G.) O. 3 I

Flowmeter Method

Refrigerant Temperatures ( °F)

In vapor line leaving coll of Indoor unit 4-9.0

In liquid line entering coil of Indoor unit 110.2

In discharge line of compressor 213.5

In suction line of compressor 75.3

Superheating at Indoor coil outlet 5.0 inlet* Subcooling at Indoor coll * 9.5

* Subcooling determined using pressure at point of measurement as

determined by correction for liquid pressure drop in gage line.

No correction necessary for superheating Involving gage with

vapor in line.
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Refrigerant Pressures (pslg)**

Compressor discharge 276.5

In liquid line preceding flowmeter 266.0

In liquid line entering coll of Indoor unit 264.5

Pressure drop across flowmeter 2.5

In vapor line leaving coll of Indoor unit 75-0

In suction line of compressor 72.0

** Pressure referenced to compressor level

Potter meter count for 1 minute 31.05***

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

3400

Motor Power Consumption (watts)

Indoor blower 430

Outdoor fan 350

Compressor 3850

Total 4630

Coefficient of performance 2 . 06

Motor Voltages (volts)

Indoor blower 115

Outdoor fan 230

Compressor 230

Motor Current ( ampere s

)

Indoor blower 5.1

Outdoor fan 1.9

Compressor l8 .

4

B. Heating Test at 30°F Outdoor Temperature, 3-Ton Unit

Details of the heating test with the outdoor temperature at

30°F and the Indoor temperature at 70°F are given below.
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-19-

Summary of Heating Capacity Values (Btu/hr)

3-Ton Unit

Test Rounded

Value Value

By psychrometrlc method 27,^10

By flowmeter method 27,320

Average 2T,365

Correction for deviation of barometric

pressure from normal None

Total 27.365 27,400

Psychrometrlc Method

Air Temperatures (°F)

At Inlet to Indoor unit 70.2

At outlet of Indoor unit In duct 92.5

Temperature difference across Indoor coll 22.3

At Inlet to outdoor coll 30.2

Wet Bulb Depression (°F)

At outlet of Indoor unit In duct 33.8

Relative Himnldlty

At outlet of Indoor unit In duct 8.27

Static pressure across nozzle (in. W.G.) 1.21

Volume air flow at nozzle (cfm) ll80

Mass air flow at nozzle (lb dry alr/hr) 5085

Barometric pressure (in. Hg) 29.97

Area of nozzle (sq ft) .268

Nozzle coefficient .981

Static pressure at Indoor blower outlet (in. W. G. )0.29
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- 20 -

Flowmeter Method

Refrigerant Temperatures ( °P)

Compressor discharge 198.O

Compressor discharge after 4-way valve 169.0

At Inlet to coll of Indoor unit 168.3

At outlet of coll of Indoor unit 89.8

Suction line at compressor I5.O

Superheating at compressor discharge 79.0*

Superheating at Inlet to coll of Indoor unit 49.8*

Subcooling at outlet of Indoor unit 21.5*

Superheating at suction line of compressor 0.0*

* Subcooling or superheating determined using pressure at point

of measurement

Refrigerant Pressures (pslg)**

Compressor discharge 263.0

In vapor line entering coll of Indoor unit 260.0

In liquid line leaving coll of Indoor unit 236.0

In liquid line after flowmeter 236.0

Pressure drop across flowmeter Negligible

Suction pressure at compressor 38.0

** Referenced to compressor level

Potter meter count for 1 minute 17-22***

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

3339

Motor Power Consumption (watts)

Indoor blower 440

Outdoor fan 390

Compressor 303O

Total 3860

Coefficient of performance 2 . 08
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Motor Voltages (volts)

Indoor blower 115

Outdoor fan 230

Compressor 230

Motor Current (amperes)

Indoor blower 5.0

Outdoor fan 2.1

Compressor 14.7

C . Power Consumption of Strip Heater

Readings of the energy dissipated hy the strip heater which

came with the 3-ton indoor unit were made every fifteen minutes

for a period of one hour with the following results:

Watthour meter value (watts) 4540

Average terminal voltage (volts) 230

Average current (amperes) 19.75

Voltage times current (watts) 4545

Heat energy (Btu/hr) 15^500

This same test was performed on another strip heater of the same

size and manufacture supplied by the Peerless Company_, at the request of Captain Miller^ McCoy Air Force Base. The results are

the following:

Watthour meter value (watts) 4950

Average terminal voltage (volts) 230

Average current (amperes) 21.51

Voltage times current (watts) 4950

Heat energy (Btu/hr) 16^,900

D. Power Consumption of Crankcase Heater (watts) 80

5. RELATED RESULTS AND DISCUSSION

5 . 1 Motor Currents vs. Normal Ratings

The current used by the motors on the indoor blowers during

the tests was within that allowed by the nameplate service factor;

the current used by the outdoor fans was within that allowed by
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the National Electric Manufacturers Standards^ or 1.35 service

factor times the nominal rating, even though no service factors

were shown on the nameplates. The current used by the compressor

motors was less than the nominal rating on the motor nameplates.

Nominal ratings, allowable maximum current and the maximum readings observed during the tests are summarized below:

Nameplate Allowable Maximum

Nominal Service Maximum Current

Ratings, Factor Current, Readings,

amperes amperes amperes

5-Ton Unit

Outdoor blower 8.0 1.25 10.0 8.5

Outdoor fan 3.5 None — 4.0

Compressor 31.,5 None — 30.3

3-Ton Unit

Outdoor blower 4.5 1.35 6 . o8 5.1

Outdoor fan 2.0 None — 2.1

Compressor 21.0 None — 18.4

5.2 Temperature Drop Across 4-way Valve, Heating Tests

The listing of refrigerant temperatures for the 30°F heating

test of the 5-ton, unit, under Test Results , shows that the tempen

ture decreased from the compressor discharge to the Inlet of the

coll of the Indoor unit about 4l°F. Of this total, the decrease

In temperature across the four-way valve was 40 degrees. A significant decrease In temperature like this would be expected considering that the difference In temperature between the discharge

gas and the suction gas entering the four-way valve was 197 degrees

for this test.

The 30°F heating test for the 3~ton unit showed a temperature

decrease of about 30 °F from the discharge of the compressor to the

Inlet of the coll of the Indoor unit. Twenty-nine degrees of this

decrease occurred In the four-way valve.

5 . 3 Outdoor Thermostat

Section 20.2.8 of the Specifications for the All Electric Heat

Pump System, supplied to the National Bureau of Standards by

Captain Miller, required outdoor thermostats for both heat pumps.
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Thls thermostat prevents energizing the supplementary resistance

heaters unless the outdoor temperature falls below a predetermined

setting. The heat pumps tested did not contain this device, but

representatives of the Peerless Company advised that all 3-ton

and 5-ton units would be supplied to the McCoy Air Force Base with

an outdoor thermostat.

5 . 4 Mild-Weather Switch

The specifications do not require a mild-weather switch. This

device. Included in many residential air-to-air heat pump systems

today, is Intended to preclude compressor shut-off on high head

pressure during heating operation when the outdoor weather is mild.

This is accomplished by cycling the operation of the outdoor fan

to reduce the amount of heat absorbed by the outdoor coll from the

air. The possible need for the mild-weather switch was called to

the attention of the Peerless Company representative, but he advised that the design of both the 3-ton and 5-ton units made its

use unnecessary.

5 . 5 Effect of Deviation of Air Flow Rate over Indoor Coll from

Specified Rate

5-ton Heat Pump Tests performed on the 5-ton heat pump under

the National Bureau of Standards program after completing the specification tests for the United States Air Force, showed that there

was a decrease in cooling capacity when the air flow rate over the

indoor coll was decreased. This is clearly Indicated in the following table:

Air Flow Rate

( cfm)

Cooling Capacity

(Psychrometrlc Method Only)

(Btu/hr)

1630

1660

1755

1840

53.500

53,400

54.500

56,900

The specification cooling test, reported in Section 4, was performed

at an air flow rate of 1755 cfm, because the air flow rate was originally adjusted for the heating test and no change in pulley adj'ustment was made for the cooling test

.

The data in this table
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indlcate a decrease in capacity of about I5OO Btu/hr for a 95 cfm

reduction in air flow rate from I85O cfm. It is probable^, therefore^ that the 5-ton heat pump would have shown a capacity about

1500 Btu/hr greater for an air flow rate of I85O cfm than the value

reported.

Deviation of the air flow rate from I85O cfm was small during

the heating test so no similar determination of capacity change

with air flow rate was made for the heating condition.

3 -ton Heat Pump Tests performed on the 3 -ton heat pump under

the NBS program also showed a direct linear change of cooling capacity with air flow rate. However^ the cooling test^ in this case^

was performed at an air flow rate very close to the 1100 cfm

specified.

Since no change in pulley adjustment was made after the cooling test was completed^ the specification test for heating was performed at 1180 cfm. Heating tests performed on this unit for a range of air flow rates showed_, as indicated by the table belowj, an

increase in capacity of about 250 Btu/hr for an increase of 80 cfm

from 1100 cfm. Therefore, the 3 -ton heat pump would probably have

shown a capacity decrease of about 250 Btu/hr when operating at

1100 cfm, as compared to the reported value in Section 4 of this

report

.

Average with

Correction for

Deviation in

Barometric

Air Flow Rate

( c fm

)

Heating Capacity

Psychrometrlc Flowmeter

Pressure

from Normal

(Btu/hr) (Btu/hr) (Btu/hr)

860

930

1075

1305

26,305

26,555

26,980

27.825

26,445

26,660

26,995

27.705

26,500

26,800

27. 200

27.900
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6 . APPENDIX

6 . 1 Material and Dimensional Data on Components of Indoor Unit

(5-Ton Unit)

The following material and dimensional data were obtained

from the manufacturer’s representative, from nameplates, or from

Inspection or measurement of the heat pump components In the laboratory.

2 Colls , Three rows, 1/2 In. o.d. copper tubing, 11 tubes each row,

1 1/4 In. spacing center to center, 12 aluminum fins per Inch

of tube length. Two colls assembled In the shape of an Inverted V. Overall dimensions of each coll: 15 In. high,

24 In. wide, 3 1/4 In. deep. Coll Model 54-UAF, Serial No.

014124.

Blower , (Lau Mfg. Co.), Centrifugal, 7 In. pulley, 12 In. wide,

12 In. diameter.

Blower Motor, (Marathon Electric Co., Model WFQ 124a64w), Type SCS,

Frame 56-4, 1/2 HP, 1725 rpm, 1 phase, 60 cycle, 115/230 volts,

F.L. amp. 8. 0/4.0, cont. duty, 40°C rise, S.F. 1.25^ 4 1/2 In.

adjustable pulley, thermal protection, MEJ30AX Code C, requires

oiling

.

Capillary Tubes , Four capillary tubes, two for each coll,

0.080 t’ooi in- 36 Inches long, and strainer.

Air Filter, Three glass fiber filters, throw-away type, 25 In. wide,

10 In. high, 1 In. thick.

Insulation of Cabinet , One-Inch glass fiber covered with moistureresistant cloth.

Description of Lines Inside Indoor Unlt_, 1/2 In. o.d. liquid line,

3/4 In. o.d. vapor line, 3/4 In. condensate drain. All lines

brazed with "Sll-Fos” type of solder.

Supplementary Strip Heater , (H. W. Tuttle Co., Tecumseh, Mich.),

One 5000 watt, 240 volt heater with Kllxon limit switch, opens

at 200°F. A second supplementary heater, furnished by the

Peerless Co., was rated at 5000 watts, 230 volts. See Methods

of Testing In this report.
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Accumulator-Driep, (Kenmore Machine Products),, 8 In. long^ 2 in.

diameter^ with silica gel and strainer.

Housing Dimensions , 25 in. wide,, 62 in. high, 30 in. deep, 0.032 in.

wall thickness.

6 . 2 Material and Dimensional Data on Components of Outdoor Unit

(5-Ton Unit

)

3 Colls , Three rows, 1/2 in. o.d. copper tubing, 16 tubes each row,

1 1/4 in. spacing center to center, 8 1/2 aluminum fins per

inch of tube length, average. Overall dimensions of each coll:

21 in. high, 27 in. wide, 3 1/4 in. deep. Coils are vertically

placed

.

Fan, (Elec. Motor &Spec.), Propeller "pull-through" type, direct

driven, 6 blades, 30 in. diameter, requires oiling.

Fan Motor , (Electric Motor and Specialties, Inc., Model S-16-HGl),

Type S, 1/2 HP, 630 rpm, 60 cycle, 230 volts, 3.5 amp., cont.

duty, requires oiling.

Motor Compressor Unit , (Tecumseh PFB500), Hermetically sealed,

1 phase, 60 cycle, 230 volts, F.L. amp. 31-5

thermal overload.

Capillary Tubes , Three capillary tubes, one for each coll,

0.070 +.000 in. l.d., 60 inches long, and strainer.

-.001

Check Valve , ( "Magna-Chek" Watsco Co.), 1/2 in. o.d. sweat, pressure

activated. This valve returns to closed position by magnetic

action and is not spring-loaded.

Four-Way Valve , (Ranco V25 500 SRll), 230 volts. Solenoid energizes

on heating.

Description of Lines of Outdoor Unit , Discharge line from comipressor

to 4-way valve, 1/2 in. o.d'. Sanction line from compressor to

4-way valve, 7/8 in. o.d. Vapor line. Inside of unit, j/8 in.

o.d. Line from 4-way valve to outdoor coll, 3/4 in. o.d.

Liquid line Inside of unit, 1/2 in. o.d. All lines brazed with

"Sil-Fos" type of solder.

Housing Dimensions , 37 in. square, 31 in. high, O.O808 in. base

plate thickness, O.O32 in. cabinet thickness.
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6 . 3 Material and Dimensional Data on Components of Indoor Unit

(3-Ton Unit)

2 Colls , Three rows, 1/2 in. o.d. copper tubing, 10 tubes each row,

1 1/4 in. spacing center to center, 12 aluminum fins per inch

of tube length. Two coils mounted in V shape. Overall dimenslons of each coll: 13 in. high, 19 in. long, 3 l/‘4 in. deep.

Blower, (Lau Mfg. Co.), Centrifugal, 5 in. pulley, 10 in. wide, 12 in

diameter.

Blower Motor, (Marathon Electric Co., Model WOF 48S17D 35FE)^ Type SS

Frame 48-5^ 1/3 HP, 1725 npm, b phase, 60 cycle, 115 volts,

F.L. amp. 4.5j cont. duty, 40°C rise, S.F. 1.35^ 3 1/4 in.

adjustable pulley, thermal protection, MEH22JX, requires oiling.

C ap i 1 1 ary Tubes, Two capillary tubes, one for each coll,

O.OoO +.000 in. i.d., 36 Inches long, and strainer.

-.001

Air Filter, One glass fiber filer, throw-away type, 25 in. wide,

20 in. high, 1 in. thick.

Insulation of Cabinet , One-inch glass fiber covered with moistureresistant cloth.

Description of Lines Inside Indoor Unit , 1/2 in. liquid line, 3/4 in.

vapor line, 3/4 in. condensate drain

.

Supplementary Strip Heater, (H. W. Tuttle Co., Tecumseh, Mich.),

One 5000 watt, 230 volt heater with Klixon limit switch, opens

at 200°F.

6 . 4 Material and Dimensional Data on Components of Outdoor Unit

(3-Ton Unit)

2 Coils , Three rows, 1/2 in. o.d. copper tubing, 17 tubes each row,

1 1/4 in. spacing center to center, 8 1/2 aluminum fins per

inch of tube length, average. Overall dimensions of each coil:

21 in. high, 27 in. wide, 3 1/4 in. deep. Coils are vertically

placed

.

Fan , (Elec. Motor & Spec.), Propeller ’’pull-through” type, direct

driven, 4 blades, 24 in. diameter, requires oiling.
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Fan Motor, (Electric Motor and Specialties^ Inc.^ Model S-13-HB4)^

Type Sj 1/3 HP, 750 rpm, 230 volts, 2 amp., 60 cycle, cont.

duty, 1 phase.

Motor Compressor Unit , (Tecumseh Jo. 316-123^ 01458 380079^ PJE 300),

Hermetically sealed, 1 phase, 50/60 cycle, 230 volts, F.L,

amp. 21.0, thermal protection.

Capillary Tubes , Two capillary tubes, one for each coll,

0.064 +.000 in. l.d., 60 Inches long, and strainer.

-.001

Check Valve ,

( ”Magna-Chek” Watsco Co.), 1/2 in. o.d. sweat connections,

pressure activated. This valve returns to closed position by

magnetic action and is not spring-loaded.

Four-Way Valve , (Ranco V30 lOl), 230 volts. Solenoid energizes on

heating.

Description of Lines of Outdoor Unit , Discharge line from compressor

to 4-way valve, 3/8 in. o.d. Suction line from compressor to

4-way valve, 3/4 in. o.d. Vapor line Inside of unit, 3/4 in.

o.d. Line from 4-way valve to outdoor coil, 3/4 in. o.d.

Liquid line inside of unit, 1/2 in. o.d. All lines brazed

with ”Sll-Fos" type of solder.

Housing Dimensions , 37 in. square, 31 in. high, base plate thickness

0.0808 in., cabinet 0.032 in.

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PANEL
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U;S. DEPARTMENT OF COMMERCE

Frederick H. Mueller, Secretary NATIONAL BUREAU OF STANDARDS

A. V. Asiih, Director THE NATIONAL BUREAU OF STANDARDS

Tlie scope of activities of the National Rureau of Standards at its major laboratories in Washington, D.C., and

Roulder, Colorado, is suggested in the following listing of the divisions and sections engaged in technical work.

In general, each section carries out specialized research, development, and engineering in the field indicated hy

its title. A brief description of the activities, and of the resultant publications, appears on the inside of the front cover. WASHINGTON, D.C.

Electricity and Electronics. Resistance and Reactance. Electron Devices. Electrical Instruments. Magnetic Measurements. Dielectrics. Engineering Electronics. Electronic Instrumentation. Electrochemistry.

Optics and Metrology. Photometry and Colorimetry. Photographic Technology. Length. Engineering

Metrology.

Heat. Temperature Physics. Thermodynamics. Cryogenic Physics. Rheology. Molecular Kinetics. Free

Radicals Research. Atomic and Radiation Physics. Spectroscopy. Radiometry. Mass Spectrometry. Solid Stale Physics. Electron Physics. Atomic Physics. Neutron Physics. Radiation Theory. Radioactiyity-. X-rays. High

Energy Radiation. Nucleonic Instrumentation. Radiological Equipment.

Chemistry. Organic Coatings. Surface Chemistry. Organic Chemistry. Analytical Chemistry. Inorganic

Chemistry. Electrodeposition. Molecular Structure and Properties of Gases. Phy sical Chemistry. Thermochemistry. Spectrochemistry. Pure Substances.

Mechanics, Sound. Mechanical Instruments. Fluid Mechanics, i'ingineering Mechanics. Mass and Scale. Capacity, Density, and Fluid Meters. Combustion Controls.

Organic and Fibrous Materials. Rubber. Textiles. Paper. Leather. I'esting and Specifications. Poly- mer Structure. Plastics. Dental Research.

Metallurgy. Thermal Metallurgy. Chemical Metallurgy. Mechanical Metallurgy. Corrosion. Metal

Physics.

Mineral Products. Engineering Ceramics. Glass. Refractories. Enameled Metals. (Jonstilnlion and Microstructure.

Building Technology. Structural Engineering. Fire Protection. Air Conditioning, Heating, and Refrigeration. Floor, Roof, and Wall Coverings. Codes and Safely Standards. Heat Transfer. Concreting Materials.

Applied Mathematics. Numerical Analysis. Computation. Statistical Engineering. Mathematical Physics.

Data Processing Systems. SEAC Engineering Group. Components and Techniques. Digital Circuitry.

Digital Systems. Analog Systems. Application Engineering.

• Office of Basic Instrumentation. ® Office of Weights and Measures. BOULDER, COLORADO

Cryogenic Engineering. Cryogenic Equipment. Cryogenic Processes. Properties of Materials. Gas Liquefaction. Radio Propagation Physics. Upper Atmosphere Research. Ionospheric Research. Regular Pro|)agation

Services. Sun-Earth Relationships. VHF Research. Radio Warning Services. Airglow and .Aurora. Radio

Astronomy and Arctic Propagation.

Radio Propagation Engineering. Data Reduction Instrumentation. Modulation Research. Radio Noise. Tropospheric Measurements. Tropospheric Analysis. Propagation Obstacles Engineering. Radio-Mctcorology. Lower Atmosphere Physh’S.

Radio Standards. High Frequency Electrical Standards. Radio Broadcast Service. High Frc(jucncv Impedance .Stanilards. I'dccironic; Calibration Center. Microwave Physics. AIierowav(> Circuit Standards.

Radio Commnaiicatson and Systems. Low Frequency and Very Low Frecpieney Research. High Fre- quency' and Very H igh Freqiamey Research. Ultra High Freapieney arid Super I ligh Frecpienev Resi-areh. Modidation Research. Antenna Beseareh. Navigation Systems. Systems Analysis. Field ( fperations.
NBS