Laboratory Evaluation of the

Steady-State and Part Load

Performance of Absorption Type

Heating and Cooling Equipment

U S. DEPARTMENT OF COMMERCE

National Bureau of Standards

National Engineering Laboratory

Center for Building Technology

Building Equipment Division

Washington, DC 20234

March 1984

-QC

. 100

• U56

84-2016

1934

Sponsored by:

U.S. Department of Energy

(via Oak Ridge National Laboratory)

Washington, DC 20585

v

NBSIR 84-2816

LABORATORY EVALUATION OF THE

STEADY-STATE AND PART LOAD

PERFORMANCE OF ABSORPTION TYPE

HEATING AND COOLING EQUIPMENT

tiATlOh'AT, B u?.Z O? STAND.ajlL;:- LIBlir-PY QC

1 00

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S4 '2 £ Ik

m4

Reinhard Radermacher

Mark McLinden

Sanford Klein

David Didion

U S. DEPARTMENT OF COMMERCE

National Bureau of Standards

National Engineering Laboratory

Center for Building Technology

Building Equipment Division

Washington, DC 20234

March 1984

Sponsored by:

U.S. Department of Energy

(via Oak Ridge National Laboratory)

Washington, DC 20585

U.S. DEPARTMENT OF COMMERCE, Malcolm Baldrige, Secretary

NATIONAL BUREAU OF STANDARDS, Ernest Ambler, Director
> .

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ABSTRACT

An absorption water chiller and an absorption heat pump were extensively

tested under steady-state and cyclic operating conditions. The tests were

performed on two different units, one for a cooling only and one for a heating only application, and the results are reported in two separate parts.

In addition to the "black box tests" of the units, the causes for the

degradation during part load operation were investigated in more detail using

the absorption chiller. Migration of the fluids during the off periods were

found to be a major contribution to the degradation.

Furthermore, the influence of various heating water temperatures and flow

rates and the sensitivity of the charge on steady-state performance was more

closely investigated employing the absorption heat pump.

Key Words: Absorption heat pump; absorption water chiller; causes of

degradation; part load performance; steady-state performance

iii
ACKNOWLEDGEMENTS

This study was sponsored by the U.S. Department of Energy, Office of Building

Energy Research and Development through the program management service of

Mr. Robert DeVault of the Energy Division of Oak Ridge National Laboratory.

The support of R. Radermacher during this investigation by a scholarship from

the NATO Science Committee by the German Academic Exchange Service is gratefully

acknowledged

.

iv
TABLE OF CONTENTS

Page

Abstract iii

Acknowledgements iv

List of Figures (Parts I and II) vi

List of Tables (Parts I and II) vii

PART I - TESTING OF THE ABSORPTION WATER CHILLER

Introduction ..... , 1

Experimental Set-Up . 1

Testing Procedure and Evaluation 3

Results and Discussion 5

Steady-State Performance 5

Part Load Performance in the Original Operating Mode 5

Part Load Performance with the Valves in Operation

and Without Insulation Applied . ..... 7 Part Load Performance with Insulation and the Valves in Operation . . 9

Part Load Performance at High Cycle Rates 11

Seasonal Performance 11

Conclusions 12

References 12

Appendix 15

PART II - TESTING OF THE ABSORPTION HEAT PUMP

Introduction 33

Experimental Set-Up 33

Heat Pump Description 33

Test Facility 35

Instrumentation 35

Steady-State Test Procedure 36

Cyclic Tests ........ 36

Results and Discussions 37

Steady-State Test Results 37

Cyclic Test Results 40

Charge Sensitivity 40

Further Tests 44

Conclusions 44

References 45

Appendix 47

v
LIST OF FIGURES

Part I

Figure 1. Scheme of the absorption water chiller under investigation ... 2

Figure 2. Steady-State capacity of the absorption water chiller

versus outdoor air temperature 6

Figure 3. Part load factor versus cooling load factor for different

cycle rates and operating modes of the absorption chiller ... 8

Figure 4. Comparison of typical behavior of high- and low-side

pressures during a cycle with and without valves in

operation; spindown was enabled in the latter case 10

Part II

Figure 1. Schematic of the absorption heat pump 34

Figure 2. Coefficient of performance and heating capacity for the

absorption heat pump as a function of ambient temperatures ... 38

Figure 3. Effect of varying inlet load water temperatures on COP

for three ambient temperatures 39

Figure 4. Cyclic performance of the heat pump 41

Figure 5. Capacity and evaporator inlet and outlet temperatures as

a function of time for a typical cyclic test 42

Figure 6. COP as a function of ambient temperature and refrigerant

charge 43

vi
LIST OF TABLES

V

Part I

Table 1. Cyclic Test Results 14

Table 2. Calculated Seasonal Performance Results 14

Table 3. Thermocouple Locations, Absorption Chiller 16

Part II

Table 1. System Pressures and Concentrations and Evaporator

Conditions as a Function of Refrigerant Charge and

Ambient Temperature 46

Table 2. Channel Numbers and Thermocouple Locations 48

vii

PART I

TESTING OF THE ABSORPTION WATER CHILLER

INTRODUCTION

An experimental investigation designed to determine the part-load performance

of an ammonia-water absorption water chiller is described. The steady-state

and cyclic performance of the chiller were measured under controlled conditions

in an environmental chamber. Two valves were installed in the chiller to

separate high- and low-pressure regions during off times, and insulation was applied to the chiller components. By these measures, losses due to cyclic

operation were reduced by over 50%, resulting in a 6% to 7% increase in the

calculated seasonal performance factor for typical northern and southern

climates in the United States. The use of the valves eliminated the need of

the "spindown" period, thereby reducing the consumption of parasitic electrical

energy.

EXPERIMENTAL SETUP

An air-cooled ammonia-water absorption chiller was used in the experimental

investigation. The chiller was rated by the manufacturer as capable of cooling

0.45 1/s (7.2 gpm) of water from 12.8°C (55°F) to 7.2°C (45°F) at 35°C (95°F)

outdoor dry-bulb temperature; this corresponds to a nominal capacity of 10,550 W

(36,000 Btu/hr). The unit is fired by natural gas and requires an energy

input of 23,150 W (79,000 Btu/hr) to the combustor. It was designed for residential service, with all of the absorption system components included in one modular package. Also included is a pump for circulating chilled water through

the evaporator. The electrical energy required to run the blower and the

chilled water and solution pumps is 1050 W.

The chiller was installed in an environmental chamber at the National Bureau

of Standards in which the operating conditions (i.e., the air and inlet water

temperatures) could be controlled. Air was circulated within the chamber to ensure a uniform air temperature. During cyclic tests, the air temperature

was maintained within +1°C (+ 1.8°F) of the set point, while fluctuations

during steady-state tests were less than 0.3°C (0.5°F). The test facility was designed to allow a once-through passage of chilled water through the evaporator

at a constant inlet temperature of 12.8°C (55°F).

A schematic diagram showing the major components of the absorption chiller

appears in Fig. 1. Thermocouples were installed at the inlet and outlet of

every component, which provided meaningful temperature measurements at these

locations when the solution pump was in operation. The thermocouples were

connected to a data acquisition system, which recorded the temperatures at

these locations at one-minute intervals.

The capacity of the chiller was obtained by measuring the flow rate and

temperature change of the water flowing through the evaporator. A turbine

meter was installed in the inlet stream and calibrated in situ at the design
1 CONDENSER

2 REFRIGERANT HEAT EXCHANGER

3 EVAPORATOR

4 SOLUTION COOLED ABSORBER

5 STRONG SOLUTION

w WEAK SOLUTION

a AMMONIA VAPOR

W CHILLED WATER

5 RECTIFIER

6 GENERATOR

7 SOLUTION PUMP

8 AIR COOLED ABSORBER

V VALVES BUILT IN TO SEPARATE

HIGH AND LOW PRESSURE REGIONS

T RESTRICTORS

Figure 1. Scheme of the absorption water chiller under investigation.

2
flow rate. An electronic counter was connected to the turbine meter to allow

recording of the instantaneous and average flow during a test. The chilled

water flow rate and inlet temperature were maintained constant at 0.45 1/s and

12.8°C (55°F) in all tests. Thermocouples were installed in the chilled water

inlet and outlet streams close to the unit and were connected to the data

acquisition system. In addition, two thermopiles were installed between the

two streams and connected to a strip-chart recorder to provide a continuous

record of the temperature difference. The estimated precision of the capacity

measurement is within 1%.

The volumetric flow rate, temperature, and pressure of the natural gas were

measured in each test. The higher heating value of the natural gas was determined in a calorimeter in operation at the National Bureau of Standards. The

energy consumption of the combustor heating the generator was determined with

an estimated precision of 2%.

Pressure gauges were mounted on the generator and absorber of the unit to

measure the high- and low-side pressures. These pressures were recorded at

the beginning and end of the burner on-time and spindown periods. In addition,

for some cyclic tests, the pressures were recorded at short time intervals

during the entire cycle. Both pressure gauges were calibrated on a deadweight

gauge-tester prior to the tests.

Before most of the tests were conducted, two remote-activated ball valves were

installed. Their positions within the unit are indicated in Fig. 1. In order

to install the valves, it was necessary to remove ammonia and to replace it

again after the work was completed. The ammonia charge was adjusted to maximize the steady-state capacity at the standard rating point (35° C [95°F] outdoor

air temperature, 12. 7° C [55°F] chilled water return temperature). This capacity

was within 1% of that obtained before the valves were installed.

After testing the influence of the valves, the following parts of the absorption

chiller were insulated with glass wool: the solution-cooled absorber, the

receiver located before the solution pump, and the rectifier and that part of

the generator that is not in direct contact with the burner. In addition, the

panel between the components listed above and the condensing unit was insulated.

To prevent further heat losses from the generator by convection, the exhaust

for the flue gases was closed during off-times. The effect of the insulation

on the steady-state performance was checked, and no change in the capacity was detectable.

TESTING PROCEDURE AND EVALUATION

All tests were conducted with a chilled water flow rate of 0.45 1/s (7.2 gpm)

and a chilled water inlet temperature of 12.8°C (55°F). Prior to each steadystate test, steady conditions were first established in the environmental

chamber and then data were taken and averaged over a 30-minute period. The

steady-state capacity, Q ss , was determined by the relationship

Qss mCpATgg ( 1 )

3
where in is the mass flow rate of chilled water, Cp is the specific heat of

water, and ATSS is the steady-state temperature difference between

the inlet and outlet chilled water streams. Q ss is the instantaneous

capacity which is equal to the average capacity in steady-state

operation

The steady-state coefficient of performance (COP ss ) is defined here as the ratio

of the capacity to the sum of the rate of gas energy input to the combustors

and the steady-state electrical power input to the blower and pumps.

Qss

COPss = “ (2)

Ess

This definition of COP weights the rate of gas energy input and power

consumption equally. Since other equally appropriate definitions of COP exist,

the experimental results in Tab. 1 contain the ratio of the electrical power

to the rate of gas energy inputs.

For the cyclic tests, steady conditions were first established in the

environmental chamber. After a warm-up period, the unit was cycled on and off

for the amount of time appropriate for each test for three cycles. The averaged

data from the last two cycles were used in the following calculation.

The total cooling during a cycle, QCyC , was determined by

Q_„_ = mC f

Z x AT dt

cyc p

J t (3)

where AT is the instantaneous temperature difference between the inlet and

outlet chilled water streams and t^ and t 2 are the times that the

chilled water pump was turned on and off, respectively.

The pump operating time coincided with the burner on-time when the spindown

period was disabled. Otherwise, the pump operating time was about 4.5 minutes

longer than the burner on-time. (In the following discussion, the term "ontime" always means burner on-time, although the capacity was evaluated for the

entire period in which the chilled water circulation pump was in operation.)

The total gas and electrical energy input to the unit over the interval t^ to

t 2» E Cy C , was measured and used to calculate the coefficient of performance

for cyclic operation.

COP

eye

Qcyc

E

cyc

(4)

4
The cyclic test data are presented in Tab. 1 in terms of a cooling-load factor

and a part-load factor, similar to the factors used to describe the cyclic

performance of vapor compression machines. ^ The cooling load factor, CLF, is

defined

Qcyc

CLF = . (5)

Qss "^cyc

• where QCy C is the integral cyclic capacity over one cycle, Qss is the

steady-state capacity rate at the same air temperature as for the

cyclic test, and T Cy C is the cycle period which is the sum of the

burner on- and off-times.

Defined in another (equivalent) way, CLF is the ratio of the cooling that is

supplied at a particular outdoor air temperature to the steady-state capacity

of the machine at that temperature. It is a dimensionless measure of the

degree of part-load operation. Values near unity indicate that the machine

must operate nearly continuously to meet the load; values near zero occur when

the machine is off for most of the time.

The part-load factor, PLF, is defined

COP

PLF = cy° (6)

CO^ss

The part-load factor is less than or equal to unity; it is a dimensionless

measure of the performance penalty for cyclic operation.

RESULTS AND DISCUSSION

STEADY-STATE PERFORMANCE

Steady-state tests were conducted at air temperatures of 21.7°C (71°F), 26.7°C

(80°F), 35.0°C (95°F), and 38.0°C (100. 4°F). The test results appear in lines

1, 2, 3, and 4 of Tab. 1. A plot of the measured capacity versus air temperature is shown in Fig. 2. The capacity is strongly dependent on the air temperature, especially for temperatures higher than about 30°C (86°F). Increasing

temperatures decreased the capacity significantly.

PART-LOAD PERFORMANCE IN THE ORIGINAL OPERATING MODE — - T — - — 1 — — • < Cycle rates were chosen for most of the tests according to the thermostat

characteristics supplied by the manufacturer. (Thermostat cycle rates are not

constant but rather a parabolic function of burner on-time. ^ The maximum

recommended cycle rate for this absorption chiller is about 1.5 cycles per

hour (CPH) , which occurs at 50% on-time. At 20% and 80% on-time, the cycle

rate with the recommended thermostat is 1.0 CPH.)

5
TEMPERATURE,

MX

UH/nig ‘AlIQVdVQ

6

Figure

2.

Steady-state

capacity

of

the

absorption

water

chiller

vs.

outdoor

air

temperature
The tests listed in lines 5, 6, 7, 8, and 14 of Tab. 1 were conducted to

measure the part-load performance of the absorption chiller in its original

operating mode (i.e., without additional insulation, without the valves in

operation, and with the spindown period enabled). The tests shown in lines 5 and 8 were conducted under the same conditions but at the beginning and in

between the other tests, respectively, to check the reproducibility of the

experimental data, which was found to be satisfactory. During a cooling

season, an absorption chiller is operated at a variety of cycle rates and

outdoor air temperatures. Tests were conducted to determine how changes in

the outdoor temperature affect the part-load factor (PLF) at a given cycle

rate. The results in lines 5, 6, and 7 of Tab. 1 show that both the part-load

factor and the cooling load factor (CLF) decrease with increasing outdoor air

temperature. The deviation in PLF between 21.6°C (71°F) and 35°C (95°F) is

about 7%, while the change in CLF is about 9% In an installation in which the

chiller is appropriately sized, part-load operation is more likely to occur at

temperatures below the design condition. Therefore, all of the remaining

cyclic tests were conducted at 26.6°C (80°F) as a representative condition.

The circles in Fig. 3 show the experimental values of PLF plotted versus CLF

for the absorption chiller in its original operating mode over a range of

part-load operating conditions. The size of the symbols in Fig. 3 is indicative of the uncertainty in the measured values. For comparison, the part-load

performance of vapor compression systems (at a maximum cycle rate of 3 CPH)

,

as assumed in Ref 4, is indicated by line a in Fig. 3. The performance of the

absorption system is not considerably lower than that of vapor compression

systems when it is operated at the recommended cycle rate, which is about

one-half the cycle rate for vapor compression systems.

PART-LOAD PERFORMANCE WITH THE VALVES IN OPERATION AND WITHOUT INSULATION

APPLIED 7

‘ 1 ' ’

In this section, the part-load performance of the chiller in its original

operating mode (lines 5, 6, 7, 8, and 14 of Tab. 1) is compared with its

performance when the valves are closed during the burner off-time and open

during the burner on-time (lines 10 and 16). The spindown period was disabled

when the valves were operated. Tests were also conducted in which the valves were closed after the spindown period was completed. However, these tests

resulted in slightly lower part-load factors than those with disabled spindown,

and they required significantly more electrical energy. Apparently, the

operation of the valves eliminates the need of the spindown period.

Comparing the temperature changes within the unit during the on-time, it was

obvious that the average temperatures during the cycle are closer to their

steady-state values when the valves are operated than when they are not.

Further, when the valves were operated, there was no time delay for the temperature rise of the fluid leaving the solution-cooled absorber. This time-delay,

which was 1.5 minutes in the original operating mode, indicates that the liquid

absorbent solution traveled during the off-time from the generator to the

solution-cooled absorber and needed to be pumped back to the generator. A

similar time-delay was observed for the capacity in the original operating

mode. Again, it took approximately 1.5 minutes after turning on the unit

7
dOlOVJ OVOI lHVd

8

Figure

3.

Part

load

factor

vs.

cooling-load

factor

for

different

cycle

rates

and

operating

modes

of

the

absorption

chiller.
until it started to cool down the incoming water. This time-delay was not

present when the valves were operated.

The valves also affect the behavior of the pressures as illustrated in Fig. 4.

During the off-time, the high- and low-side pressures converge to the same pressure, and then they both drop at the same rate in the original operating

mode. The low-side pressure remains unchanged during the off-time when the

valves are operated, while the high-side pressure drops significantly in the

beginning of the off-time but then stabilizes at a relatively high value.

During the on-time, the high-side pressure achieves higher values (closer to

the steady-state values) when the valves are operated, while the low-side

pressure remains stable at its steady-state value. The peaks shown by the

high- and low-side pressures after turning off the unit were observed in all

cases in which spindown was disabled including those cases in which the valves were not operated. They are due to time-delays in heat and mass fluxes in

generator and absorber, respectively. During cyclic operation at high outdoor

air temperatures, these peaks could cause the pressure relief valve to open.

The peaks could be significantly reduced by a short spindown period, e.g.,

thirty seconds.

The above described behavior was qualitatively observed for all cycle rates.

It indicates that, during the on-time, these variables return toward their

steady-state values from higher initial values, resulting in an increased COP

and PLF. The increase in performance is significant. For example, at 1.0 CPH

and 20% on-time, the PLF increases by more than 13% (lines 5 and 10 of Tab. 1).

In this case, the valve operation reduces the degradation in performance as a result of cyclic operation to almost half its original value.

Less electrical energy is used when the spindown period is disabled. The

difference in electrical use increases as the on-time decreases. For 1.0 CPH

and 20% on-time, the power consumption is reduced by 30%; this can be evaluated

by comparison of the electricity to gas input ratio in Tab. 1 lines 8 and 10.

PART-LOAD PERFORMANCE WITH INSULATION AND THE VALVES IN OPERATION

The chiller was insulated as described earlier in an effort to further improve

its part-load performance. The insulation produced no detectable change in

the steady-state performance. With the insulation in place, the chiller was operated with the spindown period disabled and the valves in operation

(Tests 11, 13, 17, 18, Tab. 1). The effect of the insulation could be seen

by examining the temperatures at various points within the unit. With the

insulation in place, the temperatures were generally higher when the unit was turned on. For example, the temperature of the weak solution leaving the

generator was 75°C (167°F) at the beginning of the on-time in the case of

the insulated unit and 47°C (117°F) when the unit was not insulated; the valves

were operated in both cases. (For comparison, the steady-state value is 115°C

[239°F]). The behavior of the pressures was, within experimental error, not

affected by the insulation. Qualitatively, these effects were observed for

all cycle rates.

9
CYCLE

Without valves in operation

With valves in operation (no spindown)

H - High side pressure

L - Low side pressure

Figure 4 . Comparison of typical behavior of high- and low-side pressures

during a cycle with and without valves in operation; on the latter

case, spindown was enabled.

10

PRESSURE,

kPa
Insulating the chiller components improved the part-load performance of the

chiller. The triangles in Fig. 3 show values of PLF plotted versus CLF for

the insulated unit with the valves in operation and the spindown period disabled

(Tests 11, 13, Tab. 1). The square symbol in Fig. 3 represents a test that was conducted without insulation (line 16, Tab. 1). However, since the PLF

for this test was 0.994, a further increase in PLF due to insulation is not

expected; the test result indicated by the square in Fig. 3 thus represents

both the uninsulated and insulated results with the valves in operation. The

PLF at 20% on-time and 1.0 CPH is 15% higher than that for the unit in its

original operating mode. The insulation itself achieves an increase in PLF of

3% compared to operation of the valves alone, which is a much smaller contribution than that attributed to the operation of the valves alone (Tests 10,

11, Tab. 1).

PART-LOAD PERFORMANCE AT HIGH CYCLE RATES

The maximum cycle rate recommended for the absorption chiller (1.5 CPH at 50%

on-time) is about half of that commonly employed for vapor compression systems.

Lower cycle rates result in larger temperature fluctuations in the airconditioned space and, presumably, lower occupant comfort. To see if this

disadvantage of the absorption chiller could be relaxed, the unit was tested

with the insulation in place and with the valves in operation at 2.0 CPH, 20%

on-time and 3.0 CPH, 50% on-time. The results are shown in lines 17 and 18 of

Tab. 1. The performance is almost as good as for the lower cycle rates, which

are displayed in lines 11 and 16. The maximum deviation in PLF is 2%. These

results demonstrate that, with the insulation and valves, the absorption unit

may be operated at cycle rates typical for vapor compression systems while

still showing a considerably higher performance than vapor compression systems,

as indicated by line a in Fig. 3.

In order to show the influence the cycle rate on the absorption chiller

performance in its original operating mode, the chiller was tested at 3.0 CPH,

50% on-time. The test results appear in line 19 of Tab. 1. The PLF is 7%

lower at the higher cycle rate than at the recommended cycle rate (line 14).

Higher cycle rates with spindown enabled result in a larger percentage of

electrical energy input. A 37% reduction in electrical energy consumption is

achieved at 3.0 CPH, 50% on-time, by eliminating the spindown period (Tab. 1 lines 18 and 19).

SEASONAL PERFORMANCE

The performance data obtained in this investigation were used to calculate the

seasonal performance factor, SPF, of the absorption chiller. The seasonal

performance factor is defined as the ratio of the total cooling load supplied

to the total fuel and electrical energy consumed by the chiller during the

cooling season. In the results given below, the fuel and electrical energy

were equally weighted. To fairly compare absorption chillers with vapor

compression machines, however, the electrical energy consumption should be

divided by the efficiency of its generation for both systems.

11
The calculations were made fo> residential applications according to the

modified bin-temperature method given in Ref 5. The modified bin-temperature

calculation procedure uses the information in Fig. 3 to estimate the part-load

performance of the chiller in each temperature bin and thereby provides an estimate of the seasonal performance including the effects of cyclic operation.

The calculations were done for a generalized northern and southern climate;

the results are shown in Tab. 2.

Column 1 in Tab. 2 shows the values of SPF that would be achieved if the unit were to operate under all circumstances with the steady-state COP for any

given air temperature. This is an upper limit for the SPF. Column 2 in Tab. 2 displays the SPF obtained by the unit in its original operating mode, while

column 3 shows the SPF achieved by the unit with insulation in place, the

valves in operation, and the spindown period disabled. Compared with the

original operating mode, the insulation and valves increase the SPF by 7.0% in

the southern climate and by 6.4% in the northern climate. Expressed in another

way, these figures indicate that the losses due to part-load operation can be

reduced by approximately 50% by the insulation and valves.

CONCLUSIONS

The results show that migration of the working fluids during the off-time is a major factor contributing to the degradation of the absorption chiller performance during cyclic operation. This migration can be reduced by the installation of automatic valves that separate the low- and high-pressure regions during

the off-periods. The use of the valves eliminates the need for the spindown

period and results in a significant reduction of electrical energy consumption

during cyclic operation. Insulating the chiller components in this way also

increased the part load performance but not to the same extent as the valves.

A 6% to 7% increase in the calculated seasonal performance factor results from

the use of the valves and insulation.

REFERENCES

1. J. M. Froemming, B. D. Wood, and J. M. Guertin, "Dynamic Test Results of an Absorption Chiller for Residential Solar Application," ASHRAE Transactions,

85:11 (1979), pp 777-786.

2. W. H. Parken, P. E. Beausoliel, and G. E. Kelly, "Factors Affecting the

Performance of a Residential Air-to-Air Heat Pump," ASHRAE Transactions,

83:1 (1977).

3. Low Voltage Room Thermostat , NEMA Standards Publication No. DC 3-1978,

New York: National Electrical Manufacturers Association (1972).

4. G. E. Kelly and W. H. Parken, "Method of Testing, Rating, and Estimating

the Seasonal Performance of Central Air-Conditioners and Heat Pumps

Operating in the Cooling Mode,” National Bureau of Standards, NBSIR 77-1271.

5. Proposed ASHRAE Standard 116, Methods of Testing for Seasonal Efficiency of

Unitary Air Conditioners and Heat Pumps,” (currently in public review).

12
6

.

James M. Guertin, "Residential Solar Absorption Chiller Thermodynamics,"

thesis, Mechanical Engineering Department Arizona State University, 1981.

13
TABLE 1 Cyclic Test Results

No. Air

Temp.

°C(°F)

Cycle

Rate

CPH

Burner

On/off

Time

[min]

Burner

On

Time

percent

Electric to

Gas Input

Ratio

102

Valves

Applied

Insulation

Applied

1

Sp indown

Enabled

PLF CLF

1 21.7 (71) Steady State Test 4.69 N.A. no N.A. 1.0 1.0

2 26.7 (80)

** M 4.64 N.A. no N.A. 1.0 1.0

3 35.0 (95)

M " •• 4.73 N.A. no N.A. 1.0 1.0

- 4 37.8 (100) " " M 4.80 N.A. no N.A. 1.0 1.0

5 26.7 (80) 1 12/48 20 6.27 no no yes 0.771 0.153

6 21.7 (71) 1 12/48 20 6.10 no no yes 0.788 0.164

7 35.0 (95) 1 12/48 20 6.56 no no yes 0.735 0.149

8 26.7 (80) 1 12/48 20 6.26 no no yes 0.769 0.152

9 26.7 (80) 1 12/48 20 6.21 yes no yes 0.870 0.171

10 26.7 (80) 1 12/48 20 4.78 yes no no 0.882 0.172

11 26.7 (80) 1 12/48 20 4.86 yes yes no 0.918 0.180

12 26.7 (80) 0.6 10/90 10 6.52 no yes yes 0.679 0.068

13 26.7 (80) 0.6 10/90 10 4.75 yes yes no 0.783 0.076

14 26.7 (80) 1.5 20/20 50 5.68 no no yes 0.912 0.451

15 26.7 (80) 1.5 20/20 50 5.67 yes no yes 0.979 0.489

16 26.7 (80) 1.5 20/20 50 4.72 yes no no 0.994 0.491

17 26.7 (80) 2 6/24 20 4.87 yes yes no 0.898 0.175

18 26.7 (80) 3 10/10 50 4.86 yes yes no 0.996 0.483

19 26.7 (80) 3 10/10 50 6.65

------ - 1

no no yes 0.849 0.429

TABLE 2

Calculated Seasonal Performance Results

Maximum

Achievable

SPF

Absorption Chiller in

Original Operation

Mode

Modified

Absorption

Chiller

Southern Climate 0.434 0.387 0.413

Northern Climate 0.436 0.386 0.405

14
APPENDIX

Experimental Data in Detail

In the following, the original experimental data will be presented for all

the tests performed. Table 3 gives all thermocouple locations. In Table 4,

all steady-state test data are presented. The cyclic test data follow.

15
Table 3. Thermocouple Locations, Absorption Chiller

Channel No. Location

0

1

2

3

4

5

6

78

9

10

11

12

13

14

15

16

17

18

19

20

21

22

23

24

25

26

27

28

29

30

31

32

33

34

35

36

37

38

39

40

41

42

43

44

45

46

47

Icebath

Pump in

Pump Ou t Solution into Generator

Solution out of Generator

Solution into Absorber Heat Exchanger

Unit Plenum Air DB

Ammonia into Condenser

Ammonia out of Condenser

Ammonia into Evaporator

Ammonia out of Evaporator

Ammonia into Absorber

Liquid Ammonia into Refr. Heat Ex.

Liquid Ammonia out of Refri Heat Ex.

Generator Top

Middle

Bottom

Solution cooled Absorber Top

Bottom

Air cooled Absorber Bottom

Middle

Top

Condenser Top

Middle

Bottom

Evaporator Top

Middle

Bottom

Air Inlet

Air off Condenser Coils

Stack Gases

Water Inlet

Water Outlet

Water Bypass

Ambient Air DB

Ambient Air WB

Temperature Difference Water Inlet/Outlet (16 Junction

Thermopile, Reading in mV)

Evaporator Water Discharge Line

Evaporator Water Bottom

Middle

Top

Evaporator Water Inlet Line

Solution out of Absorber

Solution out of Absorber Coils

Absorbent into Absorber

Refrigerant into Refr. Heat Ex.

Gas Supply Temperature

Icebath

16
NUMBER

OF

TEST

d0) u0) d &

"H

CD cd wo oo

CTj i—

d i d U I s -H o sr H CM QJ

4-4 • 4-> CM Cd

aj

X ^

wj o

Cd

N

H & OS 4-1

m

Kf

CO

CM

OCOO

COoCO

vO

CM NO

NO

CMco St ON • ON CM ON CO co

co

m CM CO

m

m CM

vO• CM• r-• in o

tH

CO 00 CO

m ON CM I--' CM CO

co CM co

m

m CM

m

CM

CM NO• NO o

NO

CM NO CM

00 ON CM CM CM CM co in CM CO St m CM

On00m

00

O'!

ONo

inom

on

onoo

ON

ON

CMst

in• o

sr

m

ooo

r-" ooo

como oom

ONo

00 o00 m

St

CM

CM

m• St

CM St ON

00 • ON CM NO CM iH

CO

m CM CO CO in CM

CO

in

co

co o

CM X+

00 r! 'w' CO

•H T*

CO s X s pH

/—N

X '•w' 0 o 00 /-N CM X N /*s fo -O CD X X X r! rH d c 00 s d d d •H •H X o 4J •H a) Pd v^ cd > v-/ 4-1 CO BM 4m d

4-1 aj cd 3 4-1 a.

O

d CD

4-1 CD

d

X o •H

b CD 6M BM o X V-X d 0 X d 0 rH d •H B 0 CO 5 X a. X d O o 4-1 (D d CO CO o CO cd d •H d H

<D co a) T—

CD o o S'? CO C4 cd 4-1 rH

4-1 CD

d pHu 4-1 4-J CO CO CM •H o d

d Pm 0 d CO co

O s Pm d CO d d CD O O • 0) CO CD ai oo X -X T3

co CO

d 4J CD 5 5 CM

B cd 4-1 CO cd cd d o o X O o CD d

O

O PQ

X Pm Pm 6 c_> o o

17

STEADY-STATE

TEST

DATA
Cyclic Test

12/48

min

on/off

time

80°F

outdoor

No

. 5

ABC

20%

on

time

temperature

vO

eg eg H cn noin

eg

CSI m • ON eg ih rH O »—

1

rH m eg cn eg ih m

m

o m

no sr

eg rH ON

00cn

rH m eg eg co Is* in cn <r in co

sr cn m rH ON • •

m

o

cn

CM

rH cn r^ m no o

m m H eg H eg

00 o

•ocn m

IHcn

rH

•

CM m • ON eg rH r» in cn St m <• cn

rH i-H in eg cn CM rH no cn m rH ON • •

m

.35 eg rH

CO m CM

in ONm

eg

cn

in

rH egm

cn rH CO

rH

•

r^* ON

cn o

om

m • ON CM m rH rH m NO <r »n MT CO -a- m rH m eg CO eg rH St cn m rH • • • cn

00 •H ••

CO a) a £

•• N—

T

iH a) 4J £

0) •H -a 3 4-1 •H O •• /—

V

CO c c >N

/~

\

o Pi o 3 4-1 c eg eg 43 0) O Pi “rl •H 33 * 00 p Pi TJ rH 43 a

£ '—

43 •H c <U /n Pi 3

N_/ 3 oo S 43 3 p 3 Pi 43 3 CP a

•H 43 0) X> ft •rl 43 4-1 o 3

(U CO 4-1 s 3 CP 3 CQ u CJ £ 4J 3 cd /s o 14-1 -O CO 3 4J iH 4H a) •H Pi 0) rJ o 4-1 CQ 3

4-1 M N-/ rH <4H <4-4 CQ N-/ Cn 4-1 3 > o 4-> o O N^ 4-1 3

3 u w Pi O Cn •• Pi 4-1 •H 4-1 o a> CO <U rH o 0) cd XJ X) Cn 3 O CO

a> 4-1 «4H N-/ Pi H 3 3 4-1 CP •rl pg u <D Pi (U 3 CO 3 a) •H 3 Pi O rJ Ps

0) e CP E Pi Pi CO O •rl 4-1 Cn O XI p O 01 a) CO 4J 4-1 4-1 cd a U \ 3

C CO CO Pi 4-1 IS <D cd cd <d a. a a> CP Ph a) 3

<3

cd cd cd O Pi c3

cd rH o id 4-1 CQ o CQ 3 CP CP o Cd o CP CO

18

CYCLIC

TEST

DATA
Cyclic Test

12/48

min

on/off

time

70°F

Outdoor

No.

6

A

B

. C

20%

on

time

temperature

*3- CN

I—1• CO rH

O'

v£> m i m

1 o

COO'

CO vOm

I9T

*/98

CN in • CM O' HON'^ 00 m CN CO

rH rH m CN CO CN rH \D 1 i m rH CO • •

• CN rH

• CO NO

CN m -<r

l£> CN fO ^ 1 m

Nt

00mCO rH

O'm

92/.

162

CN m • ON CN O' H 00 IN-N 00 in CO

T—

1

rH m CN CO CN rH m CO 1 m rH O' • •

o• CN

rH

• o m

m o

O' CO CO 'T CN rH 00

rH

O'm

O' CN vOm

85/.

167

CN CO CN in i—

i

CN vO On CN 00 rH CN NO CO O m O' CO NO

rH rH m CN CO CN rH NT CO CN NO rH O' • • . CO

60

•H • • ft

CO aj PC

cu B • • 'w' •rl 3 3

4-4 B 4-4 <u •H PC 33 3 4-1 v-/ •H O ..

/—

s

CO 3 cj Po —

o ft O 3 4-1 3 CN N PC CU O iH

•H PC PC 60 3 ft 30 PC O

s (H •rl ft 3 ft 3

'—

'

(C 60 2 PC 3 3 3 ft PC 3 P+ CU

•H PC 3 ,3 •

PC ft •rH PC '

4-4 o 3

3 CO '—

/

4-1 3 3. \ 3 PC o CJ E 4-1 3 cO o 1+4 pc CO 3 4-4 v—

•H IH 3 •H 3 cu rJ o U PC 3

4-1 '— ft V ? rH ift ift PC V—' 4-4 3 > U 4-1 o O v«/ 4-1 3

3 ft CO o • • ft 4-1 •rl 4-4 O 3 CO <u rH a <U 3 TO 33 3 o C/0

4-1 3 4-> <4-1 '— 3 4J 3 3 4-4 cu •H fH

ft 3 1h 3 3 CO 3 3 •H 3 ft a HI

a) 6 a. B ft ft CO o •H 4-1 pn o 33 3 o 3 a) CO 4J 4-1 4-4 3 u o 3

ft co CO ft 4J > <u 3 3 3 Cu co 3 pL4 JH 3

3 3 ccj CO CO o ft 3 3 rH o 4-4 PC o o PC Ph Pu O o H o P-i C/C

19

CYCLIC

TEST

DATA
12/48

min

on/off

time

ncOT

,

..j

onCT/

.

.

95F

Outdoor

20%

on

time

temperature

mj- sr in

<r CM O ON ON o VO ON CO rH o in iH a • CM • <r r-' v£) **«. ^

— CO o ON ON CM

CM m • CTl CM 00 rH m 00 o n- m r-~- CM rrH rH m CM CO CM rH 00 m MT sf rH ON • •

r-s <r

rH o r-'. O • O' rH o ON ON "—

.

ON vO rH CO rH CO O ON CM

• CM • CO CM 00 "—

_

\ ON O VO ON CO

CM '3- • ON CM ON rH 00 00 ON n- m ON CM rH rH m CM CO CM rH vO m CO Mf rH ON •

iHm

rH

in ON • rH O o n- ON *"*

o

O NO ON CO rH rH O 00 cn ON o

<1 CM • m ON 00 \ CM O VO o m o iO

CM m • ON CM 00 rH 00 m ON in 00 CO CM

rH rH m CM CO CM iH 00 m <r MT rH ON • CO

IH 3 44 >N

/*\ o rs X o O 44 4J c CM N 44 •H

•H X X 3 5h >4 O X o

B n CU CU "

cd w 3 00 2 5*. c 3 -U 54 X 3 Ph CL •H XI q> X rH >4 54 •H X 4J o cd

a) V 4J 3 P P 3 3 co CJ u

6 CO c cd rs o X X p P 4J *—

/

4J CU •H M <U 4-1 PQ cu u 44 54 rH CO PQ vy >N 4J w 3 & O Cl • • v-> 4J cd 3 CO >4 O >N 6 CO X •H 4J O a) CO a) rH a 3 (U £“> 3 O CO

*J a) ±j IH 'w' d, 5h 44 CL •tH Pl M cd M 0) P H 3 H o X >N

a) M CU e M 5h 54 CO O •rH 4J C_> X

a o a) CU CU CO cd O o '

cd

• u co CO *4 4J s s (U a CO a) Ph (JL a) o p cd cd cd o o >4 cd cd rH O X 4J

CQ o o OQ pH Ph Ph o a w O X CO

20

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80°F

Outdoor

No.

8

A

B

C

20%

on

time

temperature

<-

CM m m co> v£> o

m O'

00 CM o

m

rH <T> O

O'o00 M084/.

158

CN m • CM CM 00 r—

1

r-~ m vO m 00 CO

rH i—

i

m co CO CM rH O' CO U0 : rH ON • •

O'

CM MO

Mf CM m

o

vO

CM

vo

CM o

m

rH O'o

m

m

vO CM CO

68/.

158

CN m . CTV CN 00 rH CO vO CM vO m MO CO

rH i—i m CM CO CM rH m •<r co m T 1 C0> • •

00

rH o Mn • in CM MO in CTV "—

„

O

o vO i

l CM i—

1

VO m rH ^r CTv o . CM • m CM O ’—' M '—

.

vO ov 00 CO in CO m

CM m . OV CM O' rH vO O' CM CM MT CM CO in

iH rH m CM co CM rH CO -3- MO m tH co • • • CO

<4-1

on of f /r-s <4-4 /“S JO 3 3 O Pn o r' 5 a) 3 3

a CM N 3 (C 4-1 •H

•H PC PC V4 C ^ H MC o

s /—> 3 3 3 /*>

\

3

v^ c 00 x—

s

Jo JO jo 3 3 rC 3 Pm Cl

/"N •H PC 3 r3 rH X 4J O 3

3 CO s-/ 4-1 & 3 3 PC O U

e 3 e cU O -H 3 4J v—

•H <3 3' •rl 3 '

s CO 4-1 PC 3 3 u v-' CO CL PC v—

Po 3

3 3 4-1 CL w 4J 3

cs 3 CO 3 o •H £ 4-1 •H 3

o 3 CO a) I—

1

(C 3 O Po 3 O CO

4-1 0) 4-1 *4-1 3 Ou 3 4-1 a •H U-i 3 3 3 (1> 3 •H 3 3 o HI Po

<v £ a £ 3 3 3 CO O •H 3 Po CJ TJ a o a) 3 3 CO 3 O o 3

5 CO eg 3 3 & £ 3 a 3 3 Pm (H 3

3 co 3 3 3 o O 3 3 3 rH O HI 3

PC O o PC £ Pm Pm d u O w o PH CO

21

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80°F

Outdoor

C

20%

on

time

temperature

i

CM

00

CSJ rHoo CN

co

rH

vDCN o

UO

1—

1

e'-

er*

onCO

-d’ in

<r

00

CO

CN • on CM T—

H

00 CM CM m •d- co 00

rH rH LT) CM CO CN rH rH CO 10 rH ON • •

in CM

rH CO rH

m o oo <r vo <r

rH CM rH On

CM

CT> COm On 00

7/.

380

CN m • ON CM 00 rH in m co CO m m CO 00

iH i—

i

m CM CO CM rH CM -J- CO MO rH ON • •

<roo

io

CM

rH

CO i0

rH<r

tH

ONm

CM m

mrH o

r--

ON

00m m

CO o

oin

CN m • ON CM 00 rH 00 m CM CM m O' co 00 m

rH rH in CM co CM iH rH <r CO vO rH ON • • CO

3 HH O O >4h

>4-1 r—

s

X u tH O >n O /*S IS 3 3 4-1 o CM N A! 3 3 4J •H

•H 32 32 w }j E -H 32 o

B 3 3 3 rs 3 a 00 tn-0 -O 3 3 X 3 ph a •H X a> r* rH J3 —

4-1 O 3

0) CO v-/ 4-1 g 3 3 CQ a <j B u c 3 O -H 3 4-1 '—

•H M-l 0) tH V4 CO 4-1 CP 3

4J v-/ l-l M/ CO O. P3 >_/ >N 4-1 3 3 4-* PI*'--' v_r 4-1 3

c M 00 M o •rH g 4-1 iH 4-1 o 0) CO 3 rH 3 3 3 >N 3 O CO

4J 3 *J 14-1 3 3- 3 4-1 a •H pH

l-l 0) M 3 3 •H 3 tH CJ rJ to ON 0) 6 a B U M 3 CO o iH 4-1 tH O 33 F o aj 0) 3 CO 3 o O

1—

3 • H co

59 h 4-1 3 3 3 a CO 3 Ph Ph 3

o 3 03 3 (0 CT3 o O tH 3 3 rH O rJ 4-1 z 03 O u « 3 PH CH PH CJ O P4 C_> Ph C0

22

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80°F

Outdoor

No.

10

A

B

C

20%

on

time

temperature

CN

CN

r-~ o CN

O CN

NO vO

rH CN

1 o

m

rHCO

CN cn m00

rH

tH

CN m • on CN rH oo oo m v. rH m CN cn rH

i—

rH in CN cn CN oo cn <r i rH r-- • •

CN

CN

r-' CN cn

n* cn m

rH CN \ ^ 1

r-~ 00

00cn

CN f"- rH

00

rH

00

CN m • r CN rH on cn '

O m CN CO 00

rH rH m CN cn CN oo cn i vO t—

r-. • •

00 o i—

nO 00 • o

CN rH CN O cn rH -ON o • CN • O iH — "

1 'J CN o ON 00 cn m

CN m • ON CN rH m m CN in CN cn 00 Nf m

rH *—m CN cn CN oo cn Nt 1 i£> i—

I-" • • • cn

3

O

/-N rs 3 Pn

/"V O 3 3

s CN N 3 tH

•H tc SC

N—

3 42 a

s /"> /—

3 /> —\ 3

>-> a 00 £

Pn 42 3 42 3 Ph PH n •rl SC 3 rH 42 3 o 3

3 cn 3 4>S 3 3 PQ CJ CJ 6 3 3 3 n—

O *H 3 3 v-< •H 4H a) H 3 CO 13 3 pa 3 3 3 V-/ 4J co Cu H-l PQ 'w' Pn 3

3 U •rl ex ^ O <3 v_

3 3

3 3 CO 3 o 3 e 13 3 •H 3

o <U CO 0) 1—

3 3 3 3 o Pn 3 3 cn 3 a) u M-l PH 3 3 3 ex •H pH 3 a) u 0) 3 3 3 "H 3 3 O rJ Pn 3 6 a. 6 3 3 3 co 3 •rl o •H 3 Pn O 'O

(2 o 3 3 3 CO 3 3 3 o O 3

5 CO 3 4-1 | s 3 40 3 PH 3 3 P-i Ph 3

3 id 3 3 3 O o 3 3 3 rH O rJ 3

PQ O o PQ 5 PH Ph PH CJ O W CJ Ph cn

23

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80°F

Outdoor

No.

11

A

B

C

20%

on

time

temperature

00

CM

CN CM 00

O CO

rH CM

( iHCO

O'

i

n

i—l o

m

o

CMCM m • O' CM 1—

1

CM 00 vO X Mt m •sT O'

rH m CM CO CM O' co ^ l lO i—i • •

00

r-~ o m • 'O vO O'

rH r^ .H CM 00 m rH CO

• CM • <fr V. *'

, | CM o o o rH

CN m • CN rH on m ^ CO m CO Mf a> rH rH m CN CO CN 00 CO <3- 1 lO »H • •

o00

CM

CM CM CO

cm m

M3 \D

iH CM COo

CO

ON

rH COo

00

rH o

o co m

m • O' CM rH O 00 (O V <r in CM Mf ON <r m

i—i m CM CO CN O' co -<r I v£5 rH O' • • • co

C CM N X G

•H X X ^ H

S V 3 r~N \ w G oo Ph X u X 3 X

•H X CD X rH X HI O

a) co V—/ H> 3 r-s 3 PQ CJ B HI G cd O -H 3 HI •H <HI a) •H CO IH HI PQ a) HI H CO Cu IH CQ v-/ PH HI 3 S HI ' O IH N_T HI cd C u CO H o •H B IH HI •H HI o a) CO <U rH C 3 qj H o rH 3 O

ft. 00

HI <u HI IH 3 pl, h ai HI a iH

a) u 0) 3 C HI •H G H o rJ PH

<u 6 a B u U H CO H •H CJ •H HI Ph O ’O p o 0) <0 0) CO 3 C cd CJ cj cd

ft co CQ u HI i S <U 3 3 Cu CO 0) X Ch CU 3 3 cd cd id o O H cd 3 rH o rJ HI PQ CJ o CQ Bt X PH CJ O w CJ X CQ

o

cda

Cd

24

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80

°F

Outdoor

No.

12 ABC

20%

on

time

temperature

00NOo o m • LO m m 00 o CM i-H On 00 ON

CM • NO CM rH nO nO ON C' o • ON CM <r NO NO CO O CM CM CM no

rHm CM CO CM On vD CO iH 00 • •

.76 CM o m ON

m

C"

CMm

CM

CO

U0

rH

PCB

pci O3 o CM • ON CM <r 00 r-- St CM O

rH rH

m CM co CM ON NO si- CO

H

3>O£1H—

PC«

00 o m in m m

H

O

NO CM i—

PC ON o . CM NO < —

*S, <3 CO

m o CM • ON CM -3- 00 00 m in PC sr m I—1 i—

m CM CO CM ON sr co u • CO 3o

“N

-p 5-i Po o On 5 CU 3 s CM N JC 3 /-N •H •H PC PC w ^ -3 O s On '— 3 /~N 3 a 00 /*—N Po X> 3 X! 3 3 3

/—

•H PC a) Cp rH Xi 4-1

O 3

<u CO 4-1 3 3 PQ

a

O i 4-1 e cU O -H 3 4-1 Ni/ •H >4-4 0) •H 3 N-/ CO 14-1 4-1 PC (U

4-1

u CO Ou NM PQ -— to 4-1 3 5 4-1 3- s-/ O 14-1 N

' 4-1 3 3 3 CO u o -rH e <4-1 4-1 •H 4-1 o a) CO <U i—

3 3 CU 3 O Po 3 O CO

4-1 CU 4-1 *4-1 3 P-i 3 CU 4-1

a •H 3 1-4 a) u a) 3 3 4-1 •H 3 3 o 31 to

a) 6 o. 6 J-t 3 3 CO 3 •H CJ •H 4-1 Po CJ *3 p o 0) 3 <U CO 3 3 cd CJ CJ — 5 CO eg u 4-1 3 3 cu -O 3 3. CO (U 3. 3 <U 3 co 3 3 3 o O 3 cd cd i—

O 31 4-1 PQ O o PC 3 3 3 3 CJ e> W u 3 CO

25

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80°F

Outdoor

No.

13

A

B

C

20%

on

time

temperature

m

CM r^ o

-d* iH

CM

Ml

i—1 o

rH

r-- COm mi co

Ml

82/.

076

o CM • O' CN nt in vO \ m CM o co r^

1—

1

H m CN CO rH co CO 1 >d- rH vO • •

CN o m NT • Ml vO O 00 '"•M. vO rH CM CO o co CO rH

• CM • rH in \ "— 'd- VO "d- CO o CN • O' CN r- CM VO m iH m CM on co

r—

1

rH m CN CO iH 1"- CO -d- Nf Ml- rH m • •

00

c-O

00 rH • 00 co m o r' — o

m fM. rH CM CO vO rH ON m ON o

CM . -O’ r- — \ -

rH vO -d- Ml 'd- co m

o CM • ON CM mi vo Ml rH vO CM O CO Ml m

rH rH m CM CO rH r- co Ml *d- •d- rH NO * * # co

3

o x >-i Pn /M O /M 3 CD 4-1 s CM N M 3 /M •rl •H PC PC M-' t-l ,3 O

6 /M M/ 3 /M 3

Va/ a 00 /-\ Po Xi t-l ,3 3 PL, a

/—

\

•H PC CD _c rH X 4-4 o 3

<D CO 4-4 3 r, 3 PQ a CJ E 4J s cO O -rl 3 4-1 v-/ •H UH a) H tH v-/ CO 14-4 4J PQ <v 4J S-X t-i CO CL 14-4 PQ -W' to 4-1 3 5 U 3- N-x o 14H M/ 4-1 3

3 t-l CO tH o •H E >4H 4-4 •H 4-1 o a) CO <D r-H C 3 OJ t-l o P>> 3 a W

u <U 4J 4H 3 C- Li (D 4H CL •H IH u a> M a) 3 3 4-1 •H 3 tH o rJ

<u E CL, 6 t-l u t-l co tH -rH a iH 4-1 >N O -T3 c o <D 0) <D CO 3 c co o o 3

y co eg u 4-1 2 5 CD Xi 3 CL CO CD Ph 3

3 co 3 CO CO o O t-l cO co rH O 4-4 « o O PQ S Ph CL, o O W CJ P-l C/1

CYCLIC

TEST

DATA
Cyclic Test

12/48

on/off

time

80

°F

Outdoor

C

20%

on

time

temperature

vO

r-~ 35 o

o

rH o n r-' in

CN rH

in

in

CNO OV CO 00

• CN m cn \\ 00 in cn o rH o m • Ov CN o <r o in <r <r OS

CN CN in CN cn OSCN

CNNT

-3- cn cn

r-' rH

rH CN rH

<r

in o • in r-. m CN 1—

NT cn OV CN rH O o cn T—

i

in

• CN • in \ \ \ r-'. CN in o rH o in • OS CN vo oo in o in '3' OS

CN CN in CN cn oc_*a-_co rH CN i—

i

• •

vo

cn

<3- rH

in • in in r-~ vo cn CN <S

**«s* O

lO cn rH CN r-' in CN <3- OS o • CN • cn N N H vO CN O' O cn in n • OV CN r- in —

.

o n <r cn OS -3- in

CN in CN cn rH l 1—1 CN rH • • cn

27
Cyclic Test

12/48

on/off

time

80°F

Outdoor

No.

A

B

C

20%

on

time

temperature

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31

CYCLIC

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DATA
Cyclic Test

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80°F

Outdoor

No.

19

A

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20%

on

time

temperature

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32

CYCLIC

TEST

DATA
PART II

TESTING OF THE ABSORPTION HEAT PUMP

INTRODUCTION

A gas-fired air-to-water heating only absorption heat pump using ammonia and

water as the working fluid has been investigated. This machine is a prototype

unit developed by an American investigator under Government sponsorship and

was tested in an environmental chamber. The steady state COP (based on total

energy input) and capacity ranged from 0.81 and 14 3 kW at an ambient temperature of -21°C to 1.14 and 15.9 kW at 16 °C with an inlet water temperature of

41°C. The sensitivity of the steady-state performance to inlet water temperature was also investigated. The performance was significantly decreased by

cycling; for example, at a cycling rate of two cycles per hour and 20 percent

burner on time the COP was 0.53 of the steady-state value.

In the second set of steady-state tests samples of the strong and weak absorbent were taken, heat flows across the components of the absorption cycle were

measured and the sensitivity to varying refrierant charges was investigated.

The performance of the heat pump was found to be sensitive to the charge of

ammonia with the optimum charge a function of ambient temperature.

EXPERIMENTAL SET UP

HEAT PUMP DESCRIPTION

The unit tested in this study was an air-to-water absorption heat pump using

ammonia and water as refrigerant and absorbent. It is fired by natural gas

and is designed for heating-only operation in a residential application. The

complete absorption cycle, burner, controls, etc. are contained in a single

package which will be located outdoors; only the heating coil and load water

circulating pump would be located inside.

The heat pump utilizes an ammonia-water absorption cycle with the addition of

flue gas heat exchanger as shown in Fig. 1. In the generator, direct firing

by natural gas supplies the heat necessary to boil refrigerant vapor out of

the weak absorbent returning from the absorber. Cooling water flows in

parallel to the absorber and condenser. The rectifier employs a "triple heat

exchanger" which preheats the weak absorbent flowing into the generator by

both cooling the exiting strong absorbent and partially condensing the exiting

vapor, thus purifying the refrigerant vapor.

In the falling-film type absorber, solution absorbs refrigerant vapor as it

drips over tubes while load water inside the tubes removes the heat of

absorption.

The evaporator is a finned coil which extracts heat from ambient air,

vaporizing liquid refrigerant supplied by the condenser.

Defrosting of the evaporator coil is accomplished by routing refrigerant vapor

from the rectifier through the solenoid-operated defrost valve directly to the

evaporator. A defrost is initiated when the difference between the ambient

and evaporator outlet temperatures exceeds a given value which depends on ambient temperature. For the purposes of these tests the temperatures were

monitored and the defrost cycle was initiated manually.

33
RESTRICTOR

CO

EHO

I I I I I I I M I )

1 1 1 1 1 1 1

1

1 1

1

CD

CO

5 ti

CO

i -s

CO

£ «

.E _ _ _ »» « B g MSeIs" 2 S S o ft 2 t: £ £ Q. U_ CO CO •£

D “0

34

Figure

1.

Scheme

of

the

absorption

heat
TEST FACILITY

The heat pump was tested in an environmental chamber with controlled dew point

and dry bulb temperatures. The chamber had sufficient volume such that air

was internally circulated to insure a uniform temperature distribution.

Ambient air temperature was maintained within +03°C during steady state tests

and jJ.°C during cyclic tests.

Load water circulates in a closed loop between the heat pump and indoor

heating coil which would normally be located in a supply air duct. In the

test facility, this was modified to a once-through flow arrangement with a constant (+0.2°C) water temperature supplied to the unit. This arrangement

eliminated any transient effects of an indoor coil during cyclic operation and

provided better control of the water temperature.

INSTRUMENTATION

The mass flow rate of the load water, M^ oa(j, was measured with a turbine flow

meter. The temperature rise of the water was measured with a 16 junction

copper-constantan thermopile installed in thermowells. Literature values were

used for the specific heat capacity, Cp of water.

The gas input to the heat pump was measured with a dry volume flow test meter.

The volume of gas used by the machine over a given time was corrected to

standard conditions and multiplied by the higher heating value of the gas,

which was determined on the NBS site daily, to obtain the energy supplied.

The electrical energy needed to power the solution pump, fan and controls was

measured with a watt-hour meter.

A turbine flowmeter and thermopile were installed in the condenser water loop

so that the heats of condensation and absorption could be separated. A thermopile was installed across the air side of the evaporator to measure the

temperature change of the air. This AT was multiplied by a measured correction factor to account for the temperature distribution over the evaporator

coil. The volume rate of the air flow was determined by traversing a vane

anemometer across the face of the evaporator coil were used to calculate the

heat supplied to the evaporator. Finally, samples of the strong and weak

absorbent were taken for determining the mixture composition.

In addition to these data, the temperatures at various points in the cycle (as

indicated in Fig. 1) were measured with thermocouples attached to the outside

of the tubes. The pressure in the generator and absorber were recorded. The

heat input to generator and the gas heat exchanger was determined by an analysis of the combustion products in the exhaust. The heat lost through the

exhaust stack was calculated from the temperature of the flue gas (measured by

a six junction averaging thermocouple) and its CC>2 content determined by an infrared analyzer.

The output of the thermocouples, thermopiles and pressure transducers were

scanned by a datalogger and stored by a microcomputer. The gas and electric

consumption and turbine flowmeter readings were recorded manually.

35
STEADY-STATE TEST PROCEDURE

The steady-state tests followed the procedures outlined in (1) where applicable. The entire test set up was operated until steady conditions were

obtained. A test lasting for 30 minutes was then started. The datalogger

recorded data every two minutes; the gas, electric and flow meters were

recorded at the beginning and end of the test, and samples of the weak and

strong absorbent were taken and analyzed. Average values for all measurements

were then used for analysis.

The primary indices used for the performance of a heat pump were COP and

capacity. The heating capacity of the unit was determined by:

Qload

= ^load C

p

AT (1)

The coefficient of performance was defined as:

COP =

^ load (2)

• +

• Qgas Eelec

CYCLIC TESTS

In the cyclic tests, which also followed the procedures of (1), part load

operation was simulated by manually cycling the unit on and off. The chamber

and water supply were allowed to reach the desired conditions and then the

heat pump was turned on and allowed to reach steady-state. The unit was then

turned off for the predetermined time and cycled on and off for two or three

complete cycles until reproducable behaviors were observed. The next cycle

was then used for the determination of cyclic performance. During the "off"

portion of the cycle the load water system continued to operate, but the water

was diverted past the heat pump.

Cycling rates of 1.5 and 3 cycles per hour at 50% burner on time were tested.

At 20% on time, the rates were decreased to 1 and 2 CPH following the characteristic parabolic thermostat behavior as discussed in (2). The on time

refers to that fraction of a complete cycle where the burner is operating.

The machine continued to operate for a 3.5-4 minute "spindown" period after

the burner shut off to recover residual heating capacity in the unit.

The total heat provided by the heat pump during a cycle was given by:

Qload, eye

= Mioad

C

p f

AT dt

J t o where the temperature difference of the water entering and exiting the unit,

AT, was integrated between t Q

, the time at which the unit was turned on and

the time the machine was shut off (i.e., after "spindown"). This was determined by integrating the output of the load water thermopile recorded on a strip chart recorder with a planimeter. The energy input to the machine

during a cycle is the total gas input from t Q to t^ , the time that the burner

was operating and the electrical input measured for the entire cycle length T. The cyclic coefficient of performance was then calculated by:

36
(4) COP eye

load , eye

I

e J'

Qgas dt + J'

^elec dt

The cyclic performance can also be expressed as a fraction of the steady-state

performance. The heating load factor, represents the fractional capacity

in cyclic operation:

Q (T)

p* - load .eye

Qload , ss^^ * T

(5)

where Q^oa(j ss is the steady-state capacity and T is the time for a complete

cycle. The 5 COP penalty in cyclic operation is given by the part load factor:

PLF

COP

C yc

(T)

COP ss

(T)

( 6 )

where COP

gs

is the steady-state coefficient of performance, determined for the same ambient temperature as COP rwr .

RESULTS AND DISCUSSIONS

STEADY- STATE TEST RESULTS

The steady-state performance of the heat pump was tested over a range of

ambient and inlet load water temperatures. The coefficient of performance and

the capacity variations with ambient temperature are shown in Fig. 2 for a load water temperature of 41°C and flow rate of 0.38 Jl/sec (which are the

manufacturer's design conditions). The COP and capacity curves have similar

shapes because the energy inputs were almost independent of the ambient

temperature. The gas input varied from 13.4 to 14.3 kW and the electric input

from 0.55 to 0.6 5 kW as the ambient temperature decreased.

The performance levels off at both high and low ambient temperatures. Below

about 0°C, a two-phase mixture of liquid and vapor refrigerant exits the

evaporator (as indicated by a constant temperature profile throughout the

evaporator). At the extreme case of -21 °C, the COP is slightly lower than the

combustion efficiency of 0.84, any heat extracted from ambient is thus offset

by heat losses from the unit. Above about 5°C, the performance is relatively

insensitive to ambient temperature.

The effect of varying inlet load water temperature on COP is shown in Fig. 3.

At an ambient temperatures of -21 and -9°C, the COP decreases as inlet water

temperature increases. At an ambient temperature of 9°C, performance does not

depend on water temperature over the range investigated. This and the fact

that the performance levels off at high ambient temperatures indicates that

the generator is the component limiting the performance at high ambient

temperatures

37
dOO

[m] Aiiovdvo

38

Figure

2.

Coefficient

of

performance

and

heating

capacity

for

the

absorption

heat

pump

as

a

function

of

ambient

temperature.
d03

a)

a)

S-i x:

4-1

a

§

4J

4-> C

o a;

>4-1 X*

>4-i e w cO

CO

a>u

3

bO

•H

39

INLET

WATER

TEMPERATURE

(

0

0
In another series of tests, the load water flow rate was varied 6 percent

above and 16 percent belov: 'he nominal value of 0.38 &/sec at 8 and -8°C

ambients with no significant effect on COP or capacity.

CYCLIC TEST RESULTS

Since in normal operation, a heat pump will cycle on and off to meet varying

loads, the cylic performance is of particular interest. Tests were

performed at an 8°C ambient and the design load water conditions. Two cycling

rates were investigated: the typical vapor compression heat pump cycle rate

of 3 cycles per hour at 50 percent on time (3) and half this rate (1 1/2 cph),

which is commonly used for absorption chillers (4). The results expressed in

terms of the part load and heating load factors are shown in Fig. 4. With

decreasing heating load factor the part load factor decreases very rapidly,

especially for short on times; indicating that a substantial performance

penalty is associated with the cyclic operation. As can be seen from the

symbols in Fig. 4, the performance penalty is less severe for a lower cycle

rate ("•" in Fig. 4) than for the higher rate ("0" in Fig. 4). Although the

lower cycle rate yields better performance it is not clear whether it is

practical because longer off-periods may result in less comfort control in a heating application. The cyclic performance of the heat pump is dependent not

only on the cycle rates but also on the ambient temperature. All cyclic tests

were conducted at 8°C except one at 20% on time, 1 cycle per 3 hours, which

was also conducted at -8°C ("<>" in Fig. 4). As can be seen in Fig. 4 by

comparison of the symbols, • , O, at 20% on time that a decrease in ambient

temperature reduces the cyclic performance.

The capacity versus time behavior for a cyclic test with 10 minutes on, 10

minutes off is shown in Fig. 5. This response is typical. The capacity

appears to rise very quickly when the machine turns on; however, this is when

the warm load water which was sitting in the unit flows out across the exit

thermopile. The refrigerant side capacity soon dominated causing a drop in

water side capacity which starts to rise after about 3 minutes. (The cause of

the small "bump" in the curve at 4 minutes was not determined but is very

reproducible and appears in varying degrees in all the tests.) The unit had

not yet reached steady-state when the burner shut off. During the "spin-down"

period the capacity continued to rise briefly and then fell off sharply.

While the machine was off, the difference in the high and low side pressures

caused hot solution to migrate from the generator to the absorber and from

there into the evaporator. The refrigerant from the condenser also migrates

into the evaporator. These migrations resulted in a significant heat loss to

ambient air. Also, since the absorber is filled with solution, a reduced area

for heat and mass transfer is available when the unit cycled back on; consequentially, absorption starts gradually while the solution pump pumps the

solution out of the absorber back into the generator. During this period the

capacity is severely limited.

CHARGE SENSITIVITY

The heat pump was tested with varying charges of ammonia. The optimum charge

was found to be a function of ambient temperature (Fig. 6). The overall

effect of reduced charge is to give a more constant COP over the range of

ambient temperatures investigated. The original charge was adjusted for

40
I

41

Figure

4.

Cyclic

performance

of

the

heat

pump.
60

40

20

0

-20

Figure 5. Capacity and evaporator inlet and outlet temperatures as a function

of time for a typical cyclic test.

42

EVAPORATOR

TEMPERATURE

(°C|
43

Figure

6.

COP

as

a

function

of

ambient

temperature

and

refrigerant

charge.
optimum performance of 2°C. The highest and lowest charges investigated were

adjusted for optimum performance of about 9°C and -9°C, respectively.

The refrigerant charge has a significant effect on the evaporator pressure and

temperature, thus controlling heat transfer from ambient due to the amount of

refrigerant present in the evaporator. Table 1 shows values for pressure,

temperature and compositions of the solution and their dependence of ambient

temperature and charge.

FURTHER TESTS

a) The effects of frost accumulation on the evaporator coil were investigated

according to the procedures outlined in (1). The unit was brought to steadystate operation at a 1.5°C ambient temperature with -1°C dewpoint temperature.

A defrost cycle was initiated and upon its completion the frost accumulation

test was begun. The evaporator accumulated frost very slowly and operated for

8.4 hours before requiring defrosting. The average COP and capacity over the

test were 0.96 of steady state dry coil values at the same ambient temperature.

b) The split of load water between the condenser and absorber was investigated at -8 and 8°C ambient with the condenser flowrate being varied from 33%

to 67% of the total flowrate. Over the entire range of conditions the change

in COP was no more than 2%.

c) A turbine flowmeter was installed in the cycle to measure the flow rate of

the strong absorbent (absorber inlet) line. The measured flow rate was compared against the value which can be obtained by calculation using the heat of

condensation and the compositions of the weak and strong solution assuming

that saturated refrigerant vapor is leaving the rectifier. The values agree

within 4%.

In order to check the consistency of the measurements an energy balance was

calculated for each steady-state test. The heat delivered by the heat pump

was typically 8% smaller than the amount of energy supplied. The error in the

overall energy balance is due to neglecting heat losses to the ambient.

CONCLUSIONS

The prototype absorption heat pump tested shows a significant performance

degradation in cyclic operation; this would suggest modifications to the

absorption cycle to improve cyclic performance or possibly some type of heat

storage system to reduce the need for cycling. Except at very low ambient

temperatures the steady-state performance of the heat pump would be superior

to that of a natural gas furnace, however any meaningful comparison must be

based on a seasonal efficiency which takes cycling into account. Finally, the

performance is sensitive to the refrigerant charge. Unlike a vapor compression heat pump, however, there is no single optimum charge for this absorption

machine; rather, the optimum charge varies with temperature.

44
REFERENCES

1. W. H. Parken, et al., "Method of Testing, Rating and Estimating the

Heating Seasonal Performance of Heat Pumps," National Bureau of Standards,

Washington, D.C., NBSIR 80-2002, April 1980.

2. "Low-Voltage Room Thermostats," NEMA Standards Publication no. DC3-1978,

National Electrical Manufacturers Association, New York, 1972.

3. Lome Nelson, Honeywell, Inc., Minneapolis, MN, private communication.

4. Richard Merrick, Arkla Industries, Inc., Evansville, IN, private

communication.

45
Table

Relative

NHo charge*

(kg)

1. System

as a Fu

Ambient

Temp.

(°C)

Pressures and Concentrations and

nction of Refrigerant Charge and

Pressure NH^

(MP a ) cone.

a

Evaporator Condition

Ambient Temperature

Evap

.

Temp. (°C) •^evap

gen abs strong weak inlet outlet (kW)

+ 1.0 -9.1 2.15 0.27 0.169 .363 -10.8 -10.9 .93

+0.6 -8.4 2.14 0.26 0.149 .342 -11.2 -11.3 2.17

0 -8.7 2.10 0.25 0.134 .3 20 -12.1 -12.1 2.83

-0.5 -8.9 2.10 0.21 0.096 .280 -13.7 -12.5 5.48

+ 1.0 8.8 2.22 0.44 0.200 .393 2.4 3.4 6.49

+0.6 8.0 2.22 0.41 0.186 .381 0.8 8.0 7 .00

0 8.6 2.20 0.38 0.173 .369 - 0.4 8.8 6.63

-0.5 7 .5 2.15 0.27 0.129 .316 - 7.5 6 .8 7.11

*Ammonia charge of heat pump relative to original charge! of unit

46
APPENDIX

In Table 2 a listing of channel numbers and thermocouple locations

All other test data refer to these channel numbers.

Following Table 2 all test data are presented, first those for the

state tests and second, those of the cyclic tests.

is given.

steady47
Table 2. Channel Numbers and Thermocouple Locations

Channel No.

Original

Units Location

0 °F Icebath

1 °F Solution Pump Outlet, Weak Absorbent

2 °F Flue Gas HX, Outlet, Strong Absorbent

3 °F Condenser Inlet, Ref. Vapor

4 °F Refrigerant Heat Exchanger Inlet (Condenser

Side)

5 °F Refrigerant Heat Exchanger Outlet (Condenser

Side)

6 °F Evaporator Outlet, Refrigerant HX Inlet

7 °F Refrigerant Heat Exchanger Outlet (Evaporator

Side)

8 °F Triple Heat Exchanger Inlet , Weak Absorbent

9 °F Absorber Inlet, Strong Absorbent

10 °F Load Water Outlet

11 °F Load Water Out of Absorber

12 °F Rectifier Shell

13 °F 3% of way through Evaporator

14 °F Generator Outlet/Triple HX Inlet (Strong

Absorber)

15 °F 82% of Way through Condenser

16 °F 62% of Way through Condenser

17 °F 41% of Way through Condenser

18 °F 20% of way through Condenser

19 °F Condenser Outlet

20 °F Load Water into Mixing Barrel

25 °F Load Water out of Condenser (in thermocouplewell)

26 °F Load Water Inlet (in thermowell)

27 mV Condenser Lodd Water Thermopile (10 June Cu-Co)

28 °F Air Into Evaporator (averaging T.C.)

29 mV Evaporator Air Thermopile (4 June Cu-Co)

30 °F Stack Gas Exhaust (Chromel-Alumel T.C.)

31 °F Load Water Inlet (in thermocouplewell)

32 °F Load Water Outlet (in thermocouplewell)

33 °F Bypass Water (not used when unit is operating)

34 °F Dry Bulb Near Evaporator Inlet

35 °F Wet Bulb Near Evaporator Inlet

36 mV Load Water Thermopile (16 junc. Cu-Co)

37 °F Rectifier Outlet, Refrigerant Vapor

38 °F 33% of Way Through Evaporator

39 °F 67% of Way Through Evaporator

40 °F 19% of Way Through Evaporator

41 °F 48% of Way through Evaporator

42 °F 85% of Way Through Evaporator

48
46

47

48

49

°F Natural Gas Supply at Meter

V Pressure Transducer Supply Voltage

mV Absorber Pressure

mV Generator Pressure

NOTES: In data sheets that follow, temperatures have been converted

to °C, thermopile readings to temperature difference in °C,

and pressures to MPa.

Unless noted, all thermocouples are copper-cons tantan and installed on outside of pipe.

49
STEADY STATE TEST NO

DATE

AB1701

11/ 3/82

TEST conditions:

AMBIENT- -DRY BULB * -0.6 C DEW PTJ -17.0 C COOLING WATER -•temp: 40.5 C TOT flow: 366 L/SEC

COND flow: 139 L/SEC

AMMONIA icharge: .0 KG

ENERGY INPUTS*.

GAS! 13.71 kw ELECTRIC —total: .579 KW

fan: .214 KW

QGEN: 11.56 KW COMB eff: .043

QEVAP: 3.27 KW

ENERGY OUTPUTS: ' gload: 14.10 KW

QCOND: 5.64 KW qabs; 0.54 KW

ENERGY BALANCE:

QGEN QEVAP ? QLOAD L . 0 . C .* » .65 KW =•- 4.6 X COP: .993 cop- gas

:

1.035

SAMPLE concentrations:

STRONG ADS! .135 WEAK ABS1 .320

.137 .313

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG S TD DEV CH AVG STD DEV

0 .2 C .03 26 40.2 C: .00

1 42.4 c .13 27 9.92 CD .03

2 58.9 c .16 28 -8.6 C .10

3 75.4 r. .12 29 -2.11 CD .04

4 15.1 c .23 30 69.1 C .24

5 -12.2 c .08 31 40.5 C .08

6 -12.3 c .07 32 49.9 c .08

7 -11.7 c .43 33 38.6 c .07

0 41.0 c .16 34 -9.0 c .14

9 74.0 c .08 35 - 0.6 c .11

10 49.4 c .07 36 9.40 CD .04

11 49.6 c .08 37 75.7 C .16

12 115.3 c .20 30 -12.1 C .09

13 • 12.3 c .08 39 - 12.2 C .07

14 127.1 c .10 40 -12.1 C .08

15 52.0 c .06 41 - 12.1 c .07

16 52.0 c .06 42 -12.1 c .06

17 54,4 c .07 46 22.0 c .03

18 50.1 c .10 47 10.126 V .000

19 40.5 c .12 48 .243 MPA .002

20 40.1 c .16 49 2.137 MPA .003

25 49.0 c .08

*Lack of closure

50
STEADY STATE TEST NO? ADI 702

date: 11/ 3/02

test conditions:

AMBIENT—DRY BULIO -9.2 C DEW Pi: -17.0 C COOLING WATER -temp: 35.5 C TOT flow: .366 L/5

COND flow: .139 L/5

AMMONIA lcharge: .0 KG

ENERGY INPUTS 4. gas: 13.00 KW ELECTRIC —total: .561 KW

fan: .214 KW

QGEN: 11.64 KW comb eff: .043

qevap: 4.00 KW

ENERGY OUTPUTS:

QLOAD: 14.70 KW

QCOND: 5.76 KW qads : 8.94 KW

ENERGY BALANCE:

QGEN i QEVAP ? QLOAD L.O.C. - .94 KW c

It

COP: 1.023 cop-gas: 1.065

SAMPLE concentrations:

STRONG ADS: .133 WEAK ADS: .320

.133 .339

AVERAGE AND STANDARD DEVIATION 01" RECORDED CHANNELS

CH AVG S TD DEV CH AVG STD DEV

0 .2 C .03 26 35.1 C .06

1 30.2 C .10 27 10.24 CD .02

2 53.0 C .06 20 -9.2 C .09

3 69.0 C .03 29 - 2.57 CO .06

4 15.2 C .16 30 66.9 C .09

5 13.4 C .06 31 35.5 C .05

6 -13.5 C .00 32 45.2 C .05

7 •13.2 C . 36 33 33.5 C ,05

8 37.6 C .08 34 -9.2 C .11

9 70.4 C .05 35 - 0.0 C .11

10 44.7 C .05 36 9.93 CD .03

11 44.9 C .05 37 69.2 C .07

12 107.0 C .09 30 -13.3 C .00

13 -13.5 C .06 39 -13.3 C .07

14 119.3 C .10 40 -13.2 C .06

15 47.6 C .03 41 -13.3 C .07

16 48.3 C .03 42 -13.3 <; .06

17 49.5 c .05 46 22.1 c .03

18 52.6 c .06 47 10.126 V .000

19 42.1 c .07 48 .228 MPA .001

20 34.9 c .10 49 1.911 MPA .001

25 45.1 c .06

51

<a

is
STEADY STATE TEST NO? AD 1 703

DATE: 11/16/82

TEST conditions:

AMBIENT--DRY BULIC -0.7 C DEW Pi: -16.1 C COOLING WATER --TEMP : 40.7 C TOT FLOW: .337 L/

COND FLOW: .167 L/

AMMONIA CHARGE: .0 KG

ENERGY INPUTS*.

GAS: 14.02 KW ELECTRIC - -total: .577 KW

fan: .220 KW

qgen: ti . go KW comd eff: .842

QEVAP: 2.03 KW

energy outputs:

qload: 14 . is KW

QCOND: 5.77 KW qabs: 0.37 KW

ENERGY BALANCE:

QGEN + QEVAP ? QLOAD L.O.C. - .49 KW =- 3. s :

COP: .969 cop-oas: 1.009

SAMPLE concentrations:

STRONG ADS? .135 WEAK AB SJ .323

.132 .316

AVERAGE AND STANDARD DEVIATION OT RECORDED CHANNELS

CH AVG S TO dev CH AVG STD DEV

0 .2 C .02 26 40.4 C .12

1 42.1 C .11 27 0.47 CD .02

n 58.6 C .15 20 - 8.7 C .09

3 75.7 C .14 29 - 1.79 CD .03

4 17.2 C .10 30 73.6 C .27

5

- 12.0 C .03 31 40.7 C .12

6

- 12.1 C .05 32 50.9 C .11

7

- 11.9 C .14 33 26.4 c .05

8 41.1 c .13 34 - 8.9 c .14

9 7 4.7 c .09 35 - 0.7 c .09

10 50.4 c .13 36 10.25 CD .02

11 51 .5 c .13 37 74.3 C .16

12 116.4 c .21 30 - 11.9 c .07

13 12.1 c .04 39 - 12.0 c .06

14 127.9 c .10 40 - 11.0 c .07

15 51.3 c .13 41 - 11.9 c .06

16 52.1 c .12 42 - 11.9 c .07

17 S3.

6

c .13 46 20.8 c .06

18 57.1 c .15 47 10.125 V . 000

19 47.5 c .14 48 .246 MPA .011

20 39.7 c .14 49 2.101 MPA .006

25 40.7 c .11

52

o

i.1
STEADY STATE TEST NO

DATE

ADI 704

11/16/32

TEST conditions:

AMBIENT—DRY BULUJ -8.9 C DEW PT l -16.1 C COOLING WATER- -TEMPI 40.0 C TOT FLOW * .339 L/

COND FLOW: .113 L/

AMMONIA CHARGE: .0 KG

ENERGY INPUTS 4. gas: 14.01 KW ELECTRIC

-total: .579 KW

fan: .220 KW

qgem: 11.77 KW comb eff: .840

QEVAP: 2.98 KW

ENERGY OUTPUTS:

QLOAD: 14.17 KW

QCOND*. 5.43 KW qabs: 8.74 KW

ENERGY BALANCE*.

QGEN i QEVAP ? QLOAD _i a a * u .57 KW = 4 .1

COP: .971 cop-oas: 1 .011

sample concentrations:

STRONG ABS: .137 WEAK ABs: .325

.137 .318

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AVG STD DEV

0 .3 C .03 26 40.5 C .06

1 4 2.1 C .09 27 11.76 CD .03

2 60.4 C .12 28 -0.9 C .10

3 77.9 C .13 29 -1.00 CD .05

4 16.2 C .16 30 74.4 C .07

5 -12.3 C .06 31 40.0 c .07

6 -12.4 C .08 32 51.0 c .08

7 -12.0 C .18 33 26.3 c .09

8 41.2 C .08 34 -9.0 c .14

9 75.9 C .10 35 -0.9 c .07

10 50.6 C .08 36 10.21 CD .02

11 50.5 C .07 37 76.5 C .09

12 119.5 C .10 38 -12.2 C .08

13 - 12.4 C .07 39 -12.2 C .09

14 131.8 C .09 40 -12.2 C .09

15 54.0 C .06 41 - 12.2 c .08

16 54.9 C .07 42 -12.2 c .09

17 56.5 C .09 46 20.6 c .03

18 60.6 C .07 47 10.125 V .000

19 51 .4 C .06 48 .242 MPA .001

20 40.0 C .07 49 2.245 MPA .004

25 52.1 C .03

53

w

V)
STEADY STATE TEST no: ADI 70S

DATE? 11/10/82

TEST conditions:

AMBIENT —DRY BULB:

COOLING WATER- -TEMP:

AMMONIA CHARGE:

-0.4 C DEW PT: -16.1 C 40.6 C TOT FLOW*. .324 L/SEC

COND FLOW. .159 L/SEC

.6 KG

ENERGY INPUTS:

GAS*. 13.97 KW ELECTRIC—TOTAL*. .503 KW

fan: .210 KW

ogen: n.oi KW comb eff: .045

QEVAP: 2.17 KW

encrgy outputs:

qload: 13.01 KW

QCOND: 5.05 KW QABS: 7.96 KW

ENERGY BALANCE*.

QGEN + QEVAP ? QLOAD L.O.C. - .17 KW - 1.3

COP: .948 COP-GAS: .908

SAMPLE concentrations:

STRONG ABS: .149 WEAK ABS*. .345

.149 .329

X

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG S TO DEV CH AVG STD DEV

0 .2 c .03 26 40.3 C .05

1 41.3 c .06 27 9.03 CD .02

2 57.6 c .07 20 -0.4 C .07

3 73.5 c .09 29 -1.30 CD .05

4 18.6 c .16 30 73.4 c. .10

5 -11.2 c .04 31 40.6 C .04

6 -11.3 c .05 32 51 .0 c .05

7 •11.3 c .08 33 39.1 c .04

8 40.3 c .05 34 -8.0 c .10

9 73.5 c .06 35 - 0.6 c .09

10 50.5 c .05 36 10.42 CD .03

11 51.3 c .06 37 71.5 C .06

12 110.5 c .13 30 -11.1 c .03

13 -11.2 c .03 39 -11.1 c .01

14 122.2 c .11 40 -11.0 c .05

15 52.1 c .06 41 -11.1 c .06

16 52.9 c .07 42 -11.1 C: .03

17 54.1 c .06 46 21.3 C .02

18 57.2 c .07 47 10.125 V .000

19 47.0 c .08 48 .257 MPA .001

20 39.9 c .06 49 2.143 MPA .003

25 49.1 c .06

i

54
STEADY STATE TEST NO: AB1706

DATE: 1 1/24/32

-9.1 C DEW PT : -17.0 C 10.7 C TOT FLOW. .336 L/

COND FLOW: .171 L/

1.0 KG

TEST conditions:

AMBIENT -DRY BULB:

cooling water -temp:

AMMONIA CHARGE:

ENERGY INPUTS*.

gas : 13.93 KW

qgen: 11.74 KW

oevap: .93 KW

ENERGY OUTPUTS:

qload: 12.99 KW

qcond: 5.97 KW

energy balance:

QGEN i QEVAP ? QLOAD

cop: .095

SAHPLE concentrations:

STRONG ADS: .169

.169

ELECTRIC— TOTAL 4

. .501 KW

FAN*. .216 KW

COMB EFF: .043

QABS: 7.02 KW

L.O.C. =f -.31 KW -2.4 X

COP- CAS { .932

WEAK ABS: .365

.360

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AVG STD DEV

0 .1 C .00 26 40.4 C .06

1 39.3 C .12 27 8.56 CD .03

2 55.9 c .09 20 -9.1 C .09

3 69.4 c .06 29 -•.60 CD .04

4 19.7 c .16 30 70.7 C .08

5 -10.0 c .08 31 40.7 C .05

6 -10.9 c .11 32 50.1 C .06

7 -11.0 c .18 33 30.3 C .04

8 38.4 c .11 34 -9.1 C .17

9 71 .3 c .06 35 -9.0 C .09

10 49.6 c .07 36 9.45 CD .03

11 50.3 c .07 37 67.7 C .07

12 105.3 c .09 30 -10.7 C .07

13 - 10.0 c .07 39 - 10.7 C .0?

14 117.5 c .10 40 -10.6 C .11

15 52.1 c .06 41 -10.6 C .09

16 52.0 c .07 42 -10.6 C .09

17 53.0 c .06 46 20.7 C .04

18 56.3 c .06 47 10.125 V .001

19 47.0 c .06 48 .266 MPA .003

20 39.9 c .07 49 2.140 MPA .005

25 40.7 c .06

55

V>O
STEADY STATE TEST NO

DATE

A B 1 7 0 7 11/30/82

TEST conditions:

AMBIENT—DRY BULBS

COOLING WATER TEMPS

AMMONIA CHARGES

-0.9 C DEW PI S -17.0 C 41.0 C TOT PLOWS .320 L/SEC

COND PLOWS .164 L/SEC

-.4 KG

ENEROY INPUTS:

GASS 13.95 KW ELECTRIC —TOTALS .567 KW

FANS .216 KW

QCENS 11.60 KW COMB EFFS .837

QEVAT S 5.04 KW

ENEROY OUTPUTS:

QLOADS 15.25 KW

QCONDS 5.66 KW GAPS? 9.59 KU

ENEROY DALANCCS

QGEN F OEVAP T Ql.OAD L.O.C. « 1.46 KW = 9.6 : COPS 1.050 COP- GASS 1.093

SAMPLE concentrations:

STRONG ADSS .096 WEAK ABSS .203

.096 .277

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG S TD DEV CH AVG STD DEV

0 .2 C .03 26 40.9 C .03

1 40.3 C .06 27 0.44 CD .01

2 65.6 C .04 20 -0.9 C .07

3 00.3 C .05 29 -2.98 CD .08

4 15.7 C .41 30 70.2 C .05

5 •12.1 C . 15 31 41.0 C .03

6 -12.5 C .17 32 52.3 C .04

7 15.1 C .41 33 30.7 c .03

8 47.6 c .06 34 -9.1 c .14

9 01.9 c .03 35 -9.2 c .21

10 51.6 c .04 36 11.34 CD .02

11 53.0 c .04 37 06.5 C .05

12 129.9 c .07 30 -13.7 C .09

13 13.7 c .07 39 -13.6 C .14

14 140.0 c .09 40 -13.7 C .10

15 51.6 c .03 41 -13.7 c .06

16 52.4 c .03 42 -13.2 c .12

17 54.9 c .02 46 21.9 c .03

1C 61.0 c .09 47 10.125 V .000

19 49.3 c .03 48 .210 MPA .002

20 40.1 c .04 49 2.097 MPA .002

25 49.2 c .03

56
STEADY STATE TEST NO! AB4701

DATE: 10/20/32

TEST conditions:

AMBIENT --DRY BULB: 0.3 C DEW PI 1 COOLING WATER -TEMP! 40.5 C TOT FLOW 4. COND flow:

AMMONIA CHARGE: .0 KG

5.1 C .352 L/SEC

.124 L/SEC

ENERGY INPUTS:

gas: 13.45 KW ELECTRIC—TOTAL: .569 KW

fan: .200 KW

qgen: 11.46 KW cond eff: .052

gevap: 6.56 KW

energy outputs:

qload: 16.57 KW

qcond: 5.94 KW QADS : 10.63 KW

energy dalance:

qgen i QEVAP ? QLOAD L.O.C. •" 1.45 KW = 0. o : cor: 1.102 COP- GAS 4

. 1.232

SAMFLE CONCENTRATIONS 4. STRONG ABS: .181 WEAK ABO : .366

,177 .368

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AVG STD DEV

0 .2 C .02 26 40.3 C .09

1 46.0 C .10 27 11.70 CD .03

2 60.0 C .11 20 0.3 C .28

3 73.1 C .11 29 -4.16 CD .08

4 33.1 C .00 30 60.7 C .22

5 21 .0 C .24 31 40.5 C .10

6 6.7 C .06 32 51.9 C .07

7 34.3 C .04 33 39.7 C .09

8 45.3 C .09 34 0.3 C .30

9 75.3 C .09 35 5.1 C .09

10 51.5 C .08 36 11.50 CD .04

11 51.7 C .07 37 73.3 C .11

12 107.9 C .14 30 -2.1 C .05

13 -2.3 c .06 39 7.4 C .08

14 119.1 c .12 41 -1,7 C .11

15 54.0 c .08 42 7.7 C .06

16 54,7 c .09 46 21 .4 C .06

17 55.8 c .09 47 10.125 V .000

16 58.0 c .10 40 .354 MPA .001

19 47.0 c .17 49 2.253 MPA ,004

25 51.0 c .07

57
STEADY STATE TEST NO: AK4702

DATES 11/ 1/82

TEST conditions:

AMBIENT - -DRY BULB:

COOl. I NO WATER —TEMP:

AMMONIA CHARGE:

0.4 c dew r

• r : 34.9 C TOT PLOW:

cond flow:

.0 KG

4.4 C .375 L/GEC

,140 L/SEC

ENER0Y INPUTS?

gas: 13.48 KU ELECTRIC— TOTAL : .'.545 fan: .190

QGEN S 11.43 KW comb eff: .048

qevap: 6.74 KU

ENERGY OUTPUTS*.

qload: 16.42 KU

qcond: 5.98 KU QABS! 10.43 KU

ENERGY BALANCE:

OGEN + QEVAP ? GLOAD L.O.C. « 1.75 KU r. io

cop: i.i7i C0P-0AS: 1.218

SAMPLE concentrations:

STRONG ABS: .170

.172

WEAK ABS S .373

369

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STO DE

0 .2 C .00

1 40.7 C .04

nd. 54.2 c .03

3 66.7 c .03

4 30.4 c .05

5 16.0 c .07

6 6.0 c .05

7 31 .4 c .04

8 40.2 c .03

9 70.4 c .04

10 45.2 c .05

11 45.5 c .05

12 100.5 c .07

13 - 4.9 c ,06

14 111.7 c .07

15 40.6 c .04

16 49.2 c .03

17 50.0 c .05

18 52.5 c .05

19 39.4 c .07

25 45.2 c .04

CH AVG STD DEV

26 34.8 C .05

27 10.60 CD .01

20 0.4 C .20

29 -4,30 CD .06

30 77.7 C .11

31 34.9 C ,05

32 45.6 c .04

33 33.2 c .04

34 0.4 c .23

35 4.4 c .07

36 10.00 CD .01

37 66.7 C ,04

30 -4.5 C .09

39 0.3 c .04

41 5.2 c .11

42 7.9 c .05

46 22.2 c .03

47 10.125 V .000

40 .309 MPA .001

49 1.970 MPA .003

58
STEADY STATE TEST NO! AB4703

DATE? 11/15/82

TEST conditions:

AMBIENT - -DRY BULB: 0.6 C DEW PTJ 5.4 C COOLING WATER- -TEMP: 40.0 C TOT FLOW: .334 L/SEC

COND FLOW: .167 L/SEC

AMMONIA CHAROE: .0 KG

WEAK. A&SOU15-rr Plouj: 0. 0101 -fi/sec. ENERGY INPUTS:

gas: 13.54 KW ELECTRIC —TOTAL: . 549 KW

FAN : . 200 KW

qgen: 1 1 » 47 KW COMB eff: . 047

QEVAP: 6.63 KW

ENEROY OUTPUTS:

QLOAD: 16.40 KW

qcond: 6.ii KW QABS: 10.20 KW

ENERGY BALANCE:

QGEN + QEVAP T QLOAD L.O.C. - 1.70 KW = 10.4 : COP: 1.164 COP-OAS: 1.211

SAMPLE concentrations:

STRONG ABS: .173 WEAK ABS! *369

.173 .368

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AVG STD DEV

0 .2 C .00 26 40.6 C .05

1 47.6 C .06 27 0.05 CD ,02

2 60.2 C .06 20 8.6 C .08

3 73.0 C .07 29 - 4,20 CD .07

4 35.3 C .07 30 00.7 C .06

5 20.7 C .19 31 40.0 C .06

6 8.0 C .07 32 52.7 C .06

7 34.5 C .07 33 31.0 C .04

8 46.0 C .05 34 9.1 C .20

9 75.9 C .05 35 5.4 C .06

10 52.3 C .07 36 11.96 CD . 02

11 53.9 C .04 37 72.2 C .10

12 107.5 C .10 30 -.3 C .06

13 -.4 C .06 39 0.6 C .09

14 117.9 C .08 40 -.4 C .07

15 53.0 c .07 41 .0 C .10

16 53.7 c .06 42 9.6 r. .04

17 54.0 c .07 46 21.0 c .05

18 57.7 c .10 47 10.110 V .001

19 45.7 c .04 48 .301 MPA .001

20 39.7 c .06 49 2.197 MPA .003

25 49.4 c .06

59
STEADY STATE TEST NO: AD4704

DATE: 11/17/82

test conditions:

AMBIENT —DRY BULB:

COOLING WATER -••TEMP: AMMON I A CHAROC:

8.3 C DEW PT: 3.8 C 40.6 C TOT FLOW: .282 L/SEC

CONP FLOW: .108 L/SEC

.0 KG

ENERGY INPUTS*.

GAS*. 13.60 KW ELECTRIC --TOTAL: .547 KW

, fan: .199 KW

ODEN: 11.49 KW comb eff: .043

QEVAP: 6.69 KW

ENERGY OUTPUTS:

QLOAD: 16.37 KW

QCOND: 6.27 KW QABS: 10.10 KW

ENERGY BALANCE: i OGEN + QE VAP T QLOAD L.O.C. r 1.82 KW = 11 .1 X

COP: 1.157 . COP- gas: 1.203 • *

SAMPLE concentrations:

strong ads: .162 WEAK ADS: < 359

.161 .362

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AUG S TD DEV CH AVG STD DEV

0 .2 C .03 26 40.5 C .04

1 51 .6 C .09 27 8.18 CD .02

2 62.7 C .07 28 C.3 C .07

3 77.7 C .03 29 -4.23 CD .08

4 32.6 C .15 30 82.2 C .05

5 13.3 C 1.05 31 40.6 C .04

6 6.5 C .39 32 54.7 C .03

7 32.0 C .13 33 31.9 C .03

8 50.6 C .08 34 8.8 c .12

9 70.0 c .05 35 3.8 c .03

10 54.0 c .07 36 14.12 CD .02

11 50.9 c .05 37 75.7 C .04

12 110.0 c .06 30 1.0 C .06

13 1.7 c .07 39 1 .8 C .07

14 120.1 c .06 40 >1.7 C .09

15 52.4 c .04 41 1.7 c .08

16 53.2 c .03 42 2.8 c .20

17 54.4 c .05 46 20.8 c .05

18 57.7 c .06 47 10.112 V .004

19 45.4 c .07 48 .422 MPA .001

20 39.7 c .11 49 2.169 MPA .002

25 48.5 c .05

60
STEADY STATE TEST NOS AB4705

DATES 1 1/17/82

TEST conditions:

AMBIENT—DRY BULB! 0.1 C dew pt: 3.7 C COOLING HATER—TEMPI

AMMONIA CHAROE:

35.4 C TOT FLOW.

cond flow:

.0 KG

.340 L/SEC

.16? L/SEC

ENERGY INPUTS*.

gas: 12.62 KH ELECTRIC —TOTAL:

fan:

.532 KW

.200 KW

QOEN*. 11.55 KW

OEVAP: 6.04 KU

comb eff: .048

ENEROY OUTPUTS:

QLOAD: 16.52 KW

QCOND: 6.16 KU QABS: 10.37 KW

ENERGY BALANCE:

OGEN + OEVAP T QLOAD L.O.C. « 1.06 KW » 11.2 X

cop: 1.168 COP-OAS: 1.214

SAMPLE concentrations:

STRONG ADS*. .172

.172

WEAK ABS1 .278

.274

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG S TD DEV CH AVO 3TD DEV

0 .2 C .03 26 35.2 C .06

1 42.7 C .05 27 9.00 CD .02

2 55.1 C .04 20 8.1 C .11

3 60.7 C .03 29 - 4.32 CD .09

4 32.0 C .03 30 79.2 r. .10

5 16.0 C .10 31 35.4 c .04

6 8.4 C .06 32 47.2 C .03

7 31 .9 C .03 33 27.4 C .08

8 41 .9 C .05 34 0.0 C .15

9 71.7 C .04 35 3.7 C .06

10 47.0 C .06 36 11.90 CD .02

11 40.3 C .06 37 66.5 C .03

12 99.9 C .06 30 -2.4 C .03

13 -2.3 C .06 39 9.3 C .06

14 111.2 C .06 40 -2.5 C .06

15 40.6 C .03 41 1.2 C .36

16 49.3 C .05 42 9.1 C .07

17 50.1 C .04 46 20.0 C .05

18 52.7 C .05 47 10.124 V .000

19 30.7 C .07 48 .346 MPA .001

20 34.5 C .0? 49 1 .977 MPA .001

25 44.1 C .04

61
STEADY STATE TEST NO: AB4706

DATE: 1 1/18/32

test conditions:

AMBIENT—DRY BULB: 8.0 C DEW PTJ 5.0 C

COOI.INO WATER -TEMP’. 40.7 C TOT FLOW: .341 L/3EC

COND FLOW: .172 L/SEC

AMMONIA CHARGE: .6 KO

ENERGY INPUTS*.

gas: 13.62 KW ELECTRIC —TOTAL! .551 KW

fan: .190 KW

qcen: 11.54 KW comb eff: .047

qevapj 7.00 KW

eneroy outputs:

qload: 16.54 KW

qcond: 6.23 KW QADS : 10.31 KW

ENERGY BALANCE:.

GGEN -» QEVAP ? QLOAD L.O.C. * 1.9? KW - 12. o : COP: 1.167 COP-CAS: 1.214

SAMPLE concentrations:

STRONG ABC : .184 WEAK ABS: .301

.187 .300

, 1 ,

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STO DEV CH AVG STD DEV

0 .2 C .03 26 40.6 C .08

1 47.7 0 .09 27 0.07 CD .02

2 60.0 C .10 20 0.0 C .08

3 73.5 C .06 29 -4.41 CD .08

4 35.1 C .11 30 80.6 C .06

5 19.5 C .67 31 40.7 C .08

6 8.0 C .10 32 52.5 C .07

7 34.4 C .10 33 35.3 C .06

8 46.8 C .09 34 8.6 C .22

9 75.6 C .06 35 5.0 C .06

10 52.3 C .09 36 11.85 CD .03

11 53.7 C .06 37 71.5 C .08

12 105.1 C .11 30 .9 C .08

13 .8 C .09 39 1.0 C .13

14 115.6 C .09 40 .9 C .08

15 53.3 C .07 41 .8 C .08

16 54.0 C .06 42 5.2 C 1 .00

17 55.0 c .07 46 21.1 C .04

18 57.7 c .07 47 10.124 V .000

19 45.6 c .13 48 .406 MPA .002

20 39.0 c .15 49 2.220 MPA .003

25 49.3 c .07

62
STEADY STATE TEST NO: AB4707

DATE: 11/23/82

TEST conditions:

AMBIENT—DRY BULB*. 8.8 C DEU PT • 4.1 C COOLING WATER- -temp: 40.6 C TOT FLOW •

• 341 L cond flow: 169 L AMMONIA CHARGE: 1.0 KG

ENERGY INPUTS:

gas: 13.51 KU ELECTRIC- TOTAL: .549 1 fan: .194 1 qcen: 11 .44 KU comb eff: .847

qevap: 6.49 KU

ENERGY OUTPUTS*.

gload: 16. 9G KU

qcond: 6.23 KU QABS: 10.75 KU

ENERGY DALANCf*

GGEN + QEVAP ? QLOAD L.O. C. => .95 KU *= 5.i

COP : 1.208 COP-OAS: 1.257

sample concentrations:

STRONG iabs: .200 UEAK ABS: .388

.174 .398

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AV6 STD DEV

0 .2 C .02 26 40.5 C .07

1 47.7 C .07 27 9.06 CD .02

2 59.5 C .07 28 8.8 C .08

3 72.0 C .06 29 -4.12 CD .06

4 29.4 C .31 30 79.9 C .07

5 3.6 C .14 31 40.6 C ,05

6 3.4 C .23 32 52.7 C .05

7 20.6 C .29 33 39.2 C .06

8 46.9 C .05 34 8.8 C .20

9 75.0 C .04 35 4.0 C .04

10 52.4 C .05 36 12.17 CD .02

11 53.0 C .05 37 70.3 C .03

12 102.3 c .11 38 2.5 C .06

13 2.4 c .07 39 2.4 C .08

14 112.7 c .11 40 2.5 C .04

15 53.4 c .04 41 2.5 C .05

16 54.0 c .04 42 2.8 C .06

17 54.9 c .06 46 21.3 C .06

18 57.5 c .05 47 10.124 V .000

19 46.3 c .10 48 .441 MPA .001

20 40.9 c .12 49 2.222 MPA .002

25 49.3 c .07

63
STEADY STATE TEST NO: AK4700

DATEJ 1 1/30/32

TEST conditions:

AMBIENT-DRY bulb: 7.4 C DEW PTI 3.8 C

COOL. I NO WATER- -temp: 40.7 C TOT flow: .330 L/SEC

COND flow: .166 L/SEC

AMMONIA CHAROE: -.4 KG

ENERGY INPUTS:

gas: 13.58 ku ELECTRIC — TOTAL : .532 KU

fan: .196 KW

COEN: 11.46 KW COMB EPFl .844

QEVAP1 7.07 KU

ENERGY OUTPUTS*.

QLOAD: 15.86 KW

OCOND: 5.87 KW qabs: 9.99 KW

ENERGY BALANCE:

QGEN + QEVAP 7 QLOAD L 0 • C r* 2.67 KW *• 16.8 X COP: 1.124 cop- oas: 1.168

sample concentrations:

STRONG ADS: .129

.128

WEAK ADS: • 321

.312

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG STD DEV CH AVG sro DEV

0 .1 C .03 26 40.7 C .19

1 49.7 C .16 27 8.67 CD .03

2 63.8 C .17 28 7.4 C .28

3 HI .9 C .18 29 -4.43 CD 07

4 33.1 C .09 30 83.2 t: .10

5 21.3 C .22 31 40.7 C .19

6 6.8 C .09 32 52.4 C: .17

7 32.4 C .09 33 39.1 c .17

8 48.9 C .15 34 7.5 c .17

9 79.0 C .15 35 3 . U c .08

10 51.9 C .17 36 11.73 CD .04

11 53.3 C .16 37 79.9 C .19

12 119.7 C .23 38 2.4 C .18

13 - 7.5 C .08 39 8.0 C .08

14 129.9 C .24 40 - 7.1 C .00

15 52.2 C .16 41 6.8 c .08

16 52.9 C .16 42 7.7 c .08

17 54.7 C .16 46 21.1 c .08

18 58.9 C .21 47 10.123 V .000

19 47.9 C .23 48 .270 MPA .001

20 39.9 c .35 49 2.146 MPA .008

25 49.2 c .17

64
STEADY STATE TEST NO: AD4709

DATE: 1/ 4/83

TEST conditions:

AMBIENT --DRY BULB: 0.7 C BEU PT1

COOLING WATER --TEMP: 40.4 C TOT FLOW:

CONB flow:

AMMONIA CHARGE: -.2 KG

-1.1 C

.333 l./SEC

.164 L/SEC

ENERGY INPUTS’.

gas: 13.81 KW ELECTRIC- -TOTAL: .540 KU

fan: .200 KW

QGLN: 11.68 KU comb eff: .846

QEVAP: 6.69 KW

ENERGY OUTPUTS*.

QLOAD: 16.77 KU

OCOND: 5.85 KW QABS: 10.92 KW

ENERGY BALANCE:

QGEN + QEVAP 7 QLOAD L.O.C. •’ 1.60 KW « 9.6 :

COPJ 1,169 COP-OAS: 1.214

sample concentrations:

STRONG ABS: .154 WEAK ADS: .361

.152 .358

AVERAGE AND STANDARD DEVIATION OF RECORDED CHANNELS

CH AVG S TD DEV CH AVG STD DEV

0 21.4 C .03 26 40.4 c. .16

1 40,9 C .14 27 0.76 CD .04

2 62.7 C .18 20 0.7 C .72

3 79.2 C .18 29 - 4.30 CD .37

4 34.4 C .19 30 04.0 C .15

5 21.9 C .31 31 40.4 C .15

6 9.1 C .60 32 52.7 C: .17

7 33.7 0 .17 33 27.9 C .03

8 49.1 c .15 34 0.7 C .74

9 70.4 c .13 35 9.1 C .64

10 52.1 c .15 36 12.27 CD .05

11 53.7 c .15 37 00.1 C .19

12 117.0 c .21 38 .8 C 1 .53

13 -4.4 c .21 39 10.0 C .56

14 127.0 c .24 40 -4.1 C .21

15 52.4 c .12 41 0.6 C .75

16 53.2 c .12 42 9.0 C .60

17 54.9 c .13 46 21.1 c .04

18 58.5 c .19 47 10.111 V .001

19 47.2 c .23 48 .314 MPA .003

20 39.1 c .24 49 2.166 MPA .007

25 49.0 c .14

65
CYCLIC TEST

NO.: C17-1

DATE: 8-18-82

CYCLE TIMES: 12 / 48 ON/OFF

AMBIENT DRY BULB : -8.5 c

16.7 a F

WET BULB: -11.7 C -orDEW POINT: 11.0 °F

INTEGRATED CAPACITY 6 . Ill MJ

5792 B TU

GAS INPUT: 10- 30MJ

9759 BTU

COP: 0-561

PLF = 0.582

WATER TEMP: 40.8 c

105. 5°f

WATER FLOW ; 0. 377 kg/sec

6.03 g al/mln

ELECTRIC INPUT: 0-587 MJ

557 B TU

HLF - 0.123

(Date are average of last 2 cycles)

66
Test

No.

Cl

7-1

67

ture

Rise

of

Water

Flowing

Through

Unit

AsA

Function

of

Time

For

the

Last

Cycle
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FOR

LAST

CYCLE

-

Test

No.

Cl7

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63

Unit

On:

13:

29:59

Burner

Off:

13:

41:59

Unit

Off:

13:

45:43
CYCLIC TEST

NO.: c47 1

DATE:

8-5-82

CYCLE TIMES: 8

/ 24 ON/OFF

AMBIENT DRY BULB

:

7 - 9 C WATER TEMP: 46,6 C

46 . 2 *p 105.1 •f

WET BULB: 6.3 Q WATER FLOW : 0,367 kg/sec

-orDEW POINT: 43.3 * F

5.88 jgal/min

INTEGRATED CAPACITY 3 - 178 MJ

3012 BTU

GAS INPUT : 4 ' 972 MJ ELECTRIC INPUT : 0 * 316 MJ

4712 BTU 300 BTU

COP: 0.601

PLF -0.529 HLF -0.104

(Data are average of last two cycles)

69
Test

No.

C47-

(Outlet -

Inlet

Water

Temp.

Thermopile)
DATA

FOR

LAST

CYCLE

-

Test

No.

C47-

D O

- ^DO DO DO

( n i p rsj i % + o

OO DO DO DO D DO DO D

D O

VJ O

D K

SO oo

D O

#

DODO m 5 k.

DO DO DO

o o

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D O

r*D

lA O k/0 "\ O D O D

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O n

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71

Unit

Off:

11:49:15
CYCLIC TEST

NO. : c47 ~ 2

DATE: 8 ~ 5 ~82

CYCLE TIMES: 12 / 48 ON/OFF

AMBIENT DRY BULB: 7.6 c WATER TEMP: 40 • 8 C

45.6 105.4 o F

WET BULB: 6.0 c WATER FLOW: °- 369 kg/sec

-orDEW POINT: 42 - 8 °F

INTEGRATED CAPACITY 7 ‘ 342 MJ

6959 BTU

5 ‘ 90 gal/min

GAS INPUT: 10 * 02 MJ ELECTRIC INPUT: 0.535MJ

9495 BTU 507 BTU

COP: 0.696

PLF « 0.619 HLF ». 0.122

(Data are average of last two cycles)

72
Test

No.

C47-

CM

>

B

vO

CO

JG

73

(Outlet

-

Inlet

Water

Temp.

Thermopile)
DATA

FOR

LAST

CYCLE

-

Test

No.

C47-

a o

0 o

a +

r «a

1

i3

«,

L“

:x

3 O

> *a

3 O

tc ©

> N.

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74

Unit

On:

15:05:57

Burner

Off:

15:17:57

Unit

Off:

15:21:37
CYCLIC TEST

NO. : C47-3

DATE

8-6-82

CYCLE TIKES: 2 0 /

2 0 ON/OFF

AMBIENT DRY BULB: 7 - 7 C

45.9 » F

WET BULB: 6 - 4 C

-orDEW POINT: 43 - 5 °F

INTEGRATED CAPACITY 16 - 64 MJ

15739 BTU

WATER TEMP: 40 - 7 C

105.3

WATER FLOW: °- 367 kg/sec

5,88

gal /min

GAS INPUT: 16 - 52 MJ ELECTRIC INPUT: 0,798 MJ

15653 b tu 756 B TU

COP: °- 961

PLF* 0,854 HLF - 0.413

(Data are average of last two cycles)

75
Test

No.

C47-

76

ture

Rise

of

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Through

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as

a

Function

of

Time

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the

Last

Cycle
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77

Unit

On:

11:29:56

Burner

Off:

ll:4y:56

Unit

Off:

11:53:49
CYCLIC TEST

NO.: C47-4

DATE: 8-6-82

CYCLE TIMES: 10 / 10 ON/OFF

AMBIENT DRY BULB: 7.9 C

46.2 * F

WET BULB : 6.6 C

-orDEW POINT: A3.

8

»f

INTEGRATED CAPACITY 8 - 2 94iJ

7858 btu

GAS INPUT: 8 - 28QMJ

7848 btu

WATER TEMP: 40.4 c

104 . 8*p

WATER FLOW: 0.366fcg / 8ec

5.85

g al/mln

ELECTRIC INPUT:0 - 445 MJ

422 BTU

COP: 0-950

PLF -0.845 HLF - 0.412

(Data are average of last two cycles)
Test

No.

C47-4

oo

79

Temperature

Rise

of

Water

Flowing

Through

Unit

as

a

Function

of

Time

For

the

Last

Cycle
DATA

FOR

LAST

CYCLE -

Test

No.

C47-4

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80

Unit

On:

13:14:51

Burner

Off:

13:14:51

Unit

Off:

13:18:19
CYCLIC TEST

NO. : c47 ~ 5

DATE: 8-16-82

WATER TEMP: 40 • 2 C

104.4 o F

WATER FLOW: 0,362 kg/sec

3,20

gal /min

ELECTRIC INPUT: 0,466 MJ

442 BTU

0.050

(Data are average of last two cycles)

I

I

I

I

CYCLE TIMES: 10 / 90 ON/ OFF

AMBIENT DRY BULB : 8 - 3 C

jj 46.9 q f

WET BULB

6 - 6 C

-orDEW POINT: 43 - 9 ° F

11

il INTEGRATED CAPACITY 5,043 MJ

4780 BTU

GAS INPUT: 8 - 5Q6 MJ

8062 BTU

COP: 0- 562

PLF - 0.500 HLF «

81
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83

Unit

On:

14:25:00

Burner

Off:

14:35:00

Unit

Off:

14:38:32
FROST ACCUMULATION TEST

DATE ; 8-30-82

AMBIENT: DRY BULB: 1.7 C

35.1 °F

WET BULB: 0.4 C

32.8 °F

ELAPSED TIME: 8.429 HRS.

(END OF DEFROST TO END OF

ENERGY TO LOAD: 472.8 MJ

448.1 MBTU

GAS INPUT: 411.2 MJ

389.8 MBTU

WATER TEMP . : 40.6 C

105.0 °F

WATER FLOW: 0.365 kg /sec

5.84 gal /min

DEFROST)*

AVERAGE CAPACITY: 15569 W

53157 BTU/HR

ELECTRIC INPUT: 16.98 MJ

16.09 MBTU

COP: —1.104 (AVG. OVER 8.43 HOURS) COP : 1.150

gas

AVERAGE COP AND CAPACITY ARE APPROXIMATELY 96.1% OF STEADY-STATE WITH DRY COIL

(AS DETERMINED DURING FIRST PORTION OF TEST WHEN COIL WAS ONLY SLIGHTLY FROSTED)

.

*Defrost was initiated when (ambient - evaporator outlet) temperature exceeded

25. 5°F.

84
NBS-1 14A (rev. 2*ec

U.S. DEPT. OF COMM.

BIBLIOGRAPHIC DATA

1. PUBLICATION OR

REPORT NO.

2. Performing Organ. Report No. 3. Publication Date

SHEET (See instructions) NBSIR 84-2816 March 1984

4. TITLE AND SUBTITLE

LABORATORY EVALUATION OF THE STEADY- STATE AND PART LOAD

PERFORMANCE OF ABSORPTION TYPE HEATING AND COOLING EQUIPMENT

5. AUTHOR(S)

Reinhard Radermacher, Mark McLinden, Sanford Klein, David Didion

6. PERFORMING ORGANIZATION (If joint or other than NBS, see instructions) 7. Contract/Grant No. national bureau of standards

DEPARTMENT OF COMMERCE S. Type of Report & Period Covered

WASHINGTON, D.C. 20234

9. SPONSORING ORGANIZATION NAME AND COMPLETE ADDRESS (Street. City. State. ZIP)

Oak Ridge National Laboratory

U.S. Department of Energy

Washington, D.C. 20585

10. SUPPLEMENTARY NOTES

Document describes a computer program; SF-185, FIPS Software Summary, is attached.

11. ABSTRACT (A 200-word or less factual summary of most significant information. If document includes a significant

bibliography or literature survey, mention it here)

In this investigation, an absorption water chiller and an absorption heat pump

were extensively tested under steady-state and cyclic operating conditions. Since

the tests were performed on two different units, one for a cooling only and one

for a heating only application, the report is set up in two parts discussing the

results of the testing of each unit separately.

In addition to the "black box tests" of the units, the causes for the degradation

during part load operation were investigated in more detail using the absorption

chiller and determining that migration of the fluids during the off periods are a major contribution to the degradation.

Furthermore, the influence of various heating water temperatures and flow rates

and the sensitivity to the charge was more closely investigated employing the

absorption heat pump.

12. KEY WORDS (Six to twelve entries; alphabetical order; capitalize only proper names; and separate key words by semicolon s) Charge sensitivity; investigation of part load degradation; laboratory test of

absorption heat pump; laboratory test of absorption water chiller; part load

performance; seasonal performance; steady-state performance.

13. AVAILABILITY

QF] Unlimited

| | For Official Distribution. Do Not Release to NTIS

[~j Order From Superintendent of Documents, U.S. Government Printing Office, Washington, D.C.

20402.

[x] Order From National Technical Information Service (NTIS), Springfield, VA. 22161

14. NO. OF

PRINTED PAGES

92

15. Price

$11.50

USCOMM-DC 6O43-P80
.