Труды Всемирного конгресса Международного общества солнечной энергии

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Proceedings of ISES Solar World Congress 2007: Solar Energy and Human Settlement

852

5. CONCLUSIONS

The comparison of the

chartf −− φ method with hourly

simulation of solar assisted ejector cooling cycle has been

carried out, for a particular vapor generator temperature of

80°C.

The numerical results show that the

chartf −− φ

prediction for the annual solar fraction is in agreement with

the simulation results, for a minimum equivalent

utilizability temperature of 77°C. The present results are far

from being conclusive. The present analysis should be

made for other values of the vapor generator temperature. It

should also to be extended to other refrigerant working

fluids, in order to find a correlation between vapor

generation temperature and the respective equivalent

minimum temperatures for the

chartf −− φ correlation.

It should be pointed out here that the present results are

valid for other values of

COP , since the specific load

ejg

/Q ω depends only on the vapor generator

temperature

T .

6. ACKNOWLEGMENT

The authors are indebted to CNPq – National Research

Council - Brazil for the support to attend ISES 2007

meeting and also to PETROBRAS, for the support to the

present work, under contract CT-Petro / FINEP No.

21.01.0387.00 .

7. REFERENCES

(1) E. B. Pereira, et al., “SWERA Country Report – Brazil”,

São José dos Campos, CPTEC/INPE, 2007 (in press).

(2) F. R. Martins, E. B. Pereira, S. L. Abreu, and S. Colle,

“Validation of DNI estimates using Brazil-SR model”,

Proceedings of the ISES 2005 Solar World Congress,

Orlando, Fa., USA, 2005.

(3) S. A. Klein, and W. A. Beckman, “A general design

method for closed-loop solar energy systems”, Solar

Energy, Vol. 22, pp. 269-282, 1979.

(4) H. R. V. Gutiérrez, “Hourly simulation and economical

optimization of an ejector cooling cycle assisted by

solar energy” (in portuguese), Doctor of Science Thesis,

Department of Mechanical Engineering, UFSC,

Florianopolis, Brazil, 2005.

(5) S. L. Abreu, S. Colle, A. Almeida, and S. Mantelli,

“Quality control of solar radiation data collected at

BSRN – Baseline Surface Radiation Network of

Florianopolis” (in Portuguese), ENCIT 2000 - 8th

Brasilian Congress of Thermal Engineering and

Sciences, Porto Alegre, October, 2000.

(6) B. J. Huang, J. M. Chang, V. A. Petrenko, and K. B.

Zhuk, “Solar ejector cooling system using refrigerant

R141b”, Solar Energy. Vol. 64, Nos. 4-6, 223-226,

1998.

(7) B. J. Huang, J. M. Chang, and V. A. Petrenko, “A 1-D

Analysis of Ejector Performance”, International

Journal of Refrigeration, Vol. 22, 354-364, 1999.

(8) S. Colle, “Report of Project SIRESOL”, Contract

CT-Petro / FINEP No. 21.01.0387.00, November 2004,

pp. 14-86.

PERFORMANCE AND TEST OF A SOLAR AIR-CONDITIONING SYSTEM

Zhu Dunzhi, Feng Lei, Xie Guangming, Lu Chao

Beijing Solar Energy Research Institute Co., Ltd.

10 Dayangfang, Beiyuan Road, Chaoyang District, Beijing 100012, China

zhudunzhi@sina.com

ABSTRACT

In order to get the experience in design, control and

operation of solar cooling, Beiyuan demonstration project

for solar energy application was implemented in Beijing

four years ago. The basic features and system control

philosophy were presented in the paper. A performance test

was made by NCSA in September 2005. An experimental

study was undertaken to evaluate the system performance,

the operating status was recorded all the year round, and

the performance test results were summarized, too.

1. INTRODUCTION

Air-conditioning is the dominating energy consuming

service in the building in many countries. Conventional

cooling technologies exhibit several disadvantages clearly:

(1) Creating higher energy consumption; (2) Causing

higher electricity peak load; (3) Employing refrigerants

which influence on environment badly (Hans-Martin

Henning, 2004). Solar-assisted air conditioning offers

opportunities to meet the increasing cooling demand in

buildings in an energy-efficient way.

A solar absorption air-conditioning system, with 360 kW,

was successfully designed and constructed in 2004. The

solar cooling system was installed in the SUNPU solar

building of Beijing Solar Energy Research Institute Co.,

Ltd. (BSERI) in Beiyuan, Beijing. The system is the largest

solar cooling plant in China, and the second plant designed

and constructed by BSERI.

There are multiple functions for the system, space cooling

in summer, space heating in winter and providing hot water

in other seasons, with cooling and heating capacity 360kW

for 3000m

area, and 50m

hot water per day. The solar

cooling system was put in action in July 2004, and has been

operated successfully by now.

To promote solar cooling application, an experimental

study was carried out all the year round by BSERI. Some

experimental results of this system were presented in the

paper, including solar collector efficiency, COP of the

chiller, solar fraction of the space cooling or heating.

2. SYSTEM LAYOUT

Beiyuan solar air-conditioning system consists of heat-pipe

ETC solar collector array, absorption chiller, cooling tower,

hot water storage tank, chilled water storage tank,

circulating pumps, fan-coil units, auxiliary electric boiler

and control system. A layout of the plant is shown in Fig. 1,

the schematic design of the system is shown in Fig. 2.

2.1 Solar Collector Array

The solar collector array used 3600 heat-pipe evacuated

tubes with outer diameter of 100mm, 2000mm length and

0.018m

absorber area. The ETC modules are SUNDA

Seidoĉ (He Zinian, 1997, 2003), which were made by

Beijing SUNDA Solar Energy Technology Co., Ltd. The

solar collector array has a total collector aperture area

850m

and a total absorber area of 655 m

, which were

Proceedings of ISES Solar World Congress 2007: Solar Energy and Human Settlement

854

installed on a flat roof with a tilt angle 50ć.

Fig. 1: Layout of Beiyuan solar air-conditioning system.

2.2 Absorption Chiller

The lithium-bromide single-effect absorption chiller with

387 kW cooling capacity was used in the cooling system

with the operating temperature of approximately 88ć, and

the chilled water temperature of about 8ć.

2.3 Storage Tank

There are 2 storage tanks in the system. One is 40m

hot

water storage tank, which is used to store the hot water

produced by solar collectors; the other is 30m

chilled-water storage tank, which is used to store the chilled

water. The thermal insulation of tanks is polyurethane foam

with thickness of 100 mm.

2.4 Auxiliary Boiler

There is not other auxiliary energy in the location of this

system except electricity; hence a 100kW electric boiler

was installed to ensure all-weather operation.

2.5 System Control Philosophy

2.5.1 Solar Collector Loop Control

The pump of the collector loop is under the control of a

differential controller. If the outlet temperature of the

collector T1 is too low, hot water in the hot water tank is

pumped to solar collector array for freezing protection.

2.5.2 Air-Conditioning System Control

The chiller is controlled by two sensors: the temperature T3

of chilled water tank indicates whether there is a cooling

demand, and the temperature T2 of hot water tank indicates

whether there is a heat-derived cooling capacity. Cooling

tower provides overheating protection. The backup energy

Fig. 2: Schematic design of the system.

3 SOLAR COLLECTOR TECHNOLOGIES AND SYSTEMS

855

of the system is from the electric boiler. Fan-coil loop is

controlled by the room temperature.

3. SOLAR COOLING TEST BY NCSA

In order to determine performances of the plant, a

performance test was made by National Center of Quality

Supervision and Inspection and Testing for Air

Conditioning Equipment (NCSA) in September 2005. Test

data are shown in Fig. 3. The test results show that the

average thermal efficiency of collector array is 42%, COP

of the chiller is 0.75 and average indoors temperature is

23.8ć, while the average ambient temperature is 30.3ć

during the period of the test.

Fig. 3: Space cooling performance.

4. SYSTEM TEST OF UNDP/GEF PROJECT

In support of UNDP/GEF Project (CPR/G97/G31), an

experimental study was undertaken to evaluate the

performance of Beiyuan solar air-conditioning system all

the year round, schematically shown in Fig.2. The obtained

results were over the period from Dec. 2005 to Nov. 2006.

Following data were recorded: a) Tank temperature; b)

Inlet/outlet solar collector temperature; c) Supply/return

temperature of fan coil; d) Outdoor/indoor temperature; e)

Solar irradiation; f) Heat gain; g) Heating /cooling load; h)

Back-up heat input. The test sequences were performed

automatically; and integraph meters recorded the data. The

data logger interval was 1 hour for solar irradiance and 2

hours for the temperatures or flowmeters.

4.1 Space Cooling Performance

The test records implied that the solar collector loop began

to operate after 8 o'clock and stop before 16 o'clock. In

most cases, when solar irradiance was greater than 250

W/m

, solar loop began to be in operation; when solar

irradiance was down to about 100 W/m

, solar loop stop to

operate. On a sunny day, the outlet temperature easily met

with working temperature of the chiller (about 88ć) by

heat-pipe ETC solar collectors.

The monthly average values for solar energy gain, heat for

the chiller, and solar fraction are shown in Fig. 4.

Fig. 4: Space cooling performance.

4.2 Space heating Performance

The test records show that the solar collector loop began to

operate after 10 o'clock and stopped before 16 o'clock. In

most cases, when solar irradiance was less than 250 W/m

all day long, solar loop was not in operation. Since

heat-pipe ETC possessed low heat lose coefficient, solar

collector array worked with higher efficiency on higher

working temperature (more than 60 ć) for fan-coil units.

The monthly average values of solar energy gain, space

heating load and solar fraction are shows in Fig. 5.

Proceedings of ISES Solar World Congress 2007: Solar Energy and Human Settlement

856

Fig. 5: Space Heating Performance.

5. CONCLUSIONS

The solar absorption air–conditioning plant using heat-pipe

evacuated tubular collectors was constructed in Beijing in

2004. The system has been in operation for 3 years with

multi-purpose utilization for space cooling, space heating

and domestic water heating.

According to the test by NCSA, the COP of the chiller is

0.75; the average collector array thermal efficiency is 42%.

In 2006, the monthly average thermal efficiencies of the

solar collector array ranged from 40% to 55% for space

cooling, from 36% to 52% for space heating; solar fraction

was from 62% to 100% for space cooling, from 43% to

100% for space heating.

The operation results show that heat-pipe evacuated tubular

collectors can meet easily with the working temperature

condition of a lithium-bromide single-effect absorption

chiller. The heat-pipe ETC can work with higher efficiency

on higher working temperature, and has great potential in

solar cooling utilization.

6. ACKNOWLEDGMENTS

We gratefully acknowledge financial supports for Beiyuan solar

air-conditioning plant from Beijing Municipal Commission of

Development and Reform and for this experimental research

from UNDP /GEF Project (CPR/G97/G31).

The results presented in this paper were achieved in

cooperation with our colleagues Li Zhongming and LIU

Guojun. The authors gratefully acknowledge this.

7. REFERENCES

(1) Hans-Martin Henning, Jan Albers, “Decision Scheme

for the Selection of the Appropriate Technology Using

Solar Thermal Air-conditioning”, IEA Solar Heating

and Cooling, Task 25 Guideline Document, 2004

(2) He Zinian, “Development and Application of Heat Pipe

Evacuated Tubular Solar Collectors in China”, ISES

1997 Solar World Congress, Korea, 1997

(3) He Zinian, “A Solar Absorption Air-conditioning Plant

Using Heat-Pipe Evacuated Tubular Collectors”, ISES

1999 Solar World Congress, Korea, 1997

(4) He Zinian, “Advance evacuated tube solar collectors”,

Asia Pacific Tech Monitor, Nov.-Dec., 1997

(5) UNDP/GEF Project CPR/97/G31, Capacity Building

for the Rapid Commercialisation of Renewable Energy

in China

EXPERIMENTAL STUDY ON A NEW INTERNALLY COOLED

DEHUMIDIFIER USING LiCl-H

Yonggao Yin, Xiaosong Zhang

School of Energy and Environment, Southeast University

Sipailou Road 2#, Nanjing 210096, China

minigao_79@hotmail.com

ABSTRACT

Internally cooled dehumidifier is a new type of equipment

applied to liquid desiccant systems involving heat and mass

transfer. The experimental setup is built for testing the

performance of the internally cooled dehumidifier. All

experiments were conducted in the environmental chamber

for providing the air with different temperature and

humidity ratio. Effects of inlet parameters such as the flow

rate of the air, temperature of the coolant and the solution

on the outlet parameters were discussed. Some

experimental results were shown and compared with the

adiabatic dehumidifier, and the data showed that the

internally cooled dehumidifier could offer better

dehumidifying performance than the adiabatic

dehumidifier.

1. INTRODUCTION

Liquid desiccant systems show great energy-saving

potential so that much research on them has been

conducted recently (Factor and Grossman 1980). Liquid

desiccant systems can be driven by low-grade heat (about

70-80ć), such as solar energy, industrial waste heat etc.,

and have no pollution to the environment. In the earlier

experimental studies on liquid desiccant systems, most of

them (Fumo and Goswami 2002; Gandhidsan 2005; Liu etc.

2006; Yin etc. 2007) focused on packed bed dehumidifiers

and regenerators which could provide much contacting area

for air and liquid desiccant, but the heat and mass transfer

processes happening in them were adiabatic and with the

dehumidification process progress the heat and mass

transfer gradients would decease greatly. Internally cooled

dehumidifiers could provide more heat and mass transfer

gradient and have the possibility to make dehumidifiers

miniaturization. Jain etc. (2000) investigated a liquid

desiccant system which was made up of a packed bed

regenerator and an internally cooled dehumidifier and

suggested that the improper wetness had important effect

on the performance of dehumidifier and gave the wetness

factor. Saman and Alizadeh (2002) presented the

experimental results using cross-flow type plate heat

exchanger (PHE) as a dehumidifier/cooler. Many flow

passages were separated by thin plastic plates, and one side

of each thin plastic plate was for the desiccant solution/air

passage; the other side is for water/air passage. So the

indirect evaporation process in the water/air passage

provided cooling to the dehumidification process. The

experimental results indicated the effects of inlet

parameters of air and solution on the PHE effectiveness.

Yin etc. (2006) presented a modeling of internally cooled

and adiabatic dehumidifier and carried out the comparative

parameters study on the two types of dehumidification

processes.

This study presented an experimental apparatus which

could be used as an internally cooled dehumidifier and also

as an internally heated regenerator depending on the

operation conditions, and parameters investigation on the

internally cooled dehumidifier processes was carried out.

Proceedings of ISES Solar World Congress 2007: Solar Energy and Human Settlement

858

2. EXPERIMENTAL APPARATUS

A plate-fin heat exchanger (PFHE) made of stainless steel

is proposed to use for internally cooled/heated element of

the dehumidifier. The schematic diagram of the PFHE is

shown in Fig.1. There are seven water passages and six

desiccant solution/air passages in every PFHE, shown in

Fig. 1(b). Each solution passage is 298 mm in length and

12 mm in width. The cooling water can enter into and leave

the PFHE at the same side of the PFHE. Between two

neighboring plates, there are three layers of fin side by side

intercrossing, which can provide more contacting area for

desiccant solution and air. The distance between fins is 4

mm. The dimensions of the PFHE are shown in Fig. 1(a)

and (b). The height of the PFHE is 100 mm. The desiccant

solution is sprayed to the fins between the plates from the

upside and flows down by the gravity, at the same time the

air is blown from the underside counter-flowing with the

desiccant solution.

The internally cooled dehumidifier is made up of six

PFHEs stacking up along the vertical direction, shown in

Fig. 1(c). For the convenient of installing these PFHEs the

direction of water inlet changes every one PFHE, and

therefore three of them have their water inlet/outlet on one

side and remnant three PFHEs have their water inlet/outlet

on the other side. The desiccant solution enters into the

internally cooled/heated dehumidifier from the top and

contacts with the countercurrent air blown from the bottom.

The solution would be dispersed to the fins by a

distributing unit between the plates due to the gravity. The

cooling water in the water passages flows horizontally and

carries out heat transfer with the crossed air/solution. Fig. 2

showed the schematic diagram of the experimental setup

for testing the internally cooled dehumidifier.

1 2

Dehumidif ier/R egenerator

P 1

Valve

Drainage

567

He ater Exhaust airCooler

Air

Chilling

heating

Flowmeter

Pump

Valve

Fig. 2: Schematic Diagram of the Experimental Setup.

298

Water

out

Solution and

air channel

Solution

Air

Water

Out

100

Solution In

Air In

Air Out

Solutio n Out

Water In

Water Out

(a) Top view of the plate-fin heat exchanger

(b) Schematic diagram of the plate-fin heat exchanger

(c)

Fig. 1: A New Type of Internally Cooled/Heated Dehumidifier/Regenerator.

3 SOLAR COLLECTOR TECHNOLOGIES AND SYSTEMS

859

3. EXPERIMENTAL RESULTS AND DISCUSSIONS

For the internally cooled desiccant solution dehumi-

dification processes, the flow rate of the air and the

temperature of the cooling water have great effect on the

processes. So following experiments were intended to find

out effects of these parameters on the dehumidification and

regeneration processes.

3.1 Dehumidification With Different Cooling Temperature

Under the operation conditions shown in Table 1, the

dehumidification experiments were conducted with

different temperatures of the cooling water from 19 to ć

25 . Everyć experiment would last 8 minutes after reaching

the steady state.

TABLE 1: EXPERIMENT CONDITIONS WITH DIFF-

ERENT TEMPERATURES OF WATER

()ć

(g/kg)

/s)

(kg/s)

()ć

(%)

(kg/s)

30.3 12.6 0.072 0.1036 27.0 38.65 0.151

Fig. 3 demonstrated the effects of the cooling water

temperature T

on the outlet temperatures of desiccant

solution and air and the cooling efficiency. The figure

showed that the outlet temperature of the desiccant solution

increased with the increase of the temperature of cooling

water, and the outlet temperature of the solution was very

close to the outlet temperature of the cooling water. It was

easily concluded that the outlet temperature difference

between the solution and air was less than 1 , which ć

indicated that the PFHE had good performance in cooling

the solution. But the cooling efficiency went down with the

increase of the cooling water temperature, which was very

different from the only heat transfer process in the PFHE.

Fig. 4 also indicated that the removed vapor from the air

decreased with the increase of the cooling water

temperature, which was resulted from two main reasons:

one was that the desiccant solution with low temperature

had low surface vapor partial pressure and provided

stronger mass transfer force gradient; the other was that

there was more mass transfer coefficients between the air

and solution with lower temperature. The air absolute

humidity difference (Δω) between the inlet and outlet was

about 2.8 g/kg under the cooling water temperature of

19.4 and about 2.5 g/kg under the cooling water ć

temperature of 24.5 , which meant that the outlet absolute ć

humidity of the air was about 10 g/kg and was remarkably

higher than the saturation air absolute humidity at

equilibrium with the desiccant solution about 4 g/kg.

19 20 21 21 22 22 23 23 24

0.2

0.3

0.4

0.5

0.6

0.7

0.8

T T

T /ć

Cooling efficiency

T /ć

Fig. 3: Effects of T

on the cooling efficiency, outlet

temperature of solution and cooling water.

Fig. 4: Effects of T

on the absolute humidity change (Δω)

of the processed air.

3.2 Dehumidification with Different Flow Rate of Air

In this set of experiment the flow rate of the processed air

was at the lowest rate of 0.042 m

/s and up to the maximum

of 0.075 m

/s, and the experiment conditions were set at

Table 2. Two dehumidification models were investigated:

one was that the cooling water was activated, which was

internally cooled dehumidification; the other was that the

cooling water was not activated, which was adiabatic one.

TABLE 2: EXPERIMENT CONDITIONS WITH DIFF-

ERENT FLOW RATE OF AIR

(ć)

(g/kg)

(kg/s)

(ć)

(kg/s)

(ć)

(%)

30.9 10.6 0.151 24 0.1036 25.3 38.4

Proceedings of ISES Solar World Congress 2007: Solar Energy and Human Settlement

860

Fig. 5 displayed contrastively the effects of the processed

air flow rate (G

) on the absolute humidity change (Δω)

under the internally cooled and adiabatic dehumidification

processes. The figure showed that the absolute humidity

difference (Δω) between the inlet and outlet air increased

with the increase of flow rate of the processed air in both

internally cooled dehumidification and adiabatic

dehumidification, the reason for which was that the mass

transfer coefficients increased greatly by increasing the

processed air flow rate. At low air flow rate, the Δω

increased rapidly and at high flow rate the Δω nearly kept

constant, which was explained that at low flow rate of the

air the rate of increase of the mass transfer coefficient was

more than the rate of increase of the air flow rate, but at

high flow rate of the air both rates of increase of them were

balanceable. As described in literature (Saman and

Alizadeh, 2002), if the air flow rate continued to increase to

exceed the increase rate of the mass transfer coefficient, the

value Δω of would be decrease. So the PFHE dehumidifier

could export the best dehumidification performance at the

air flow rate about 0.07m

/s under the experimental

conditions. But higher rate of moisture removal was

achieved in the internally cooled dehumidification, and the

Δω of which was 0.5 g/kg more than that of the adiabatic

dehumidification.

1.5

2.5

0.04 0.05 0.06 0.07 0.08

/m /s

Internally cooled Adiabatic

¹ / g/kg

Fig. 5: Effect of the processed air flow rate on the absolute

humidity change.

3.3 Dehumidification With Different Desiccant Temperature

In this set of experiment, the internally cooled and adiabatic

dehumidifier made of the PFHE was respectively tested

under two groups of experimental conditions shown in

Table 3. The experimental results displayed in Fig. 6. From

the figure, it was concluded that the absolute humidity

difference (Δω) of the processed air decreased with the

increase of the desiccant temperature. The reason for this

behavior is explained that desiccant with lower temperature

can bring more mass transfer coefficient and lower vapor

partial pressure, which would result in more moisture

removal. In addition, under the same experimental

conditions the internally cooled dehumidification process

produced lower absolute humidity of the processed outlet

air, and from Fig. 6 it was observed that with the increase

of inlet desiccant temperature, the rate of decrease of Δω in

the adiabatic dehumidification was more than that in the

internally cooled dehumidification. So both low inlet

desiccant temperature and simultaneous cooling during the

dehumidification can provide better dehumidification

performance.

TABLE 3: EXPERIMENT CONDITIONS WITH DIFF-

ERENT DESICCANT TEMPERATURE

Case

()ć

(g/kg)

/s)

(kg/s)

(%)

(kg/s)

()ć

1 30.5 13.4 0.061 0.1036 37.7 0.151 22

2 30.9 12.6 0.061 0.1036 38.8 0.151 22

1.5

2.5

3.5

20 22 24 26 28 30 32

/ć

¹ / g/kg

Adiabatic-1

Internally c oole d-1

Adiabatic-2

Internally c oole d-2

Fig. 6: Effect of desiccant temperature on the air absolute

humidity change.

4. CONCLUSIONS

A new type of internally cooled dehumidifier based on the

PFHE unit was constructed and experimental study on its

operation behavior under different conditions was carried

3 SOLAR COLLECTOR TECHNOLOGIES AND SYSTEMS

861

out. The dehumidification performance could be promoted

by increasing the air flow rate or decreasing the cooling

water temperature. The outlet temperature of the desiccant

solution increased with the increase of the temperature of

cooling water, and the outlet temperature of the solution

was very close to the outlet temperature of the cooling

water, which indicated that the PFHE had good cooling

performance for the desiccant. During the internally cooled

dehumidification process, the cooling efficiency of

desiccant deceased with the increase of the cooling water

temperature, which was very different from the only heat

transfer process in the PFHE. There is an optimal air flow

rate to achieve the maximum absolute humidity change of

the air. Here the optimal value of the air is about 0.07m

/s.

Contrastively studying the internally cooled and adiabatic

dehumidification processes, it is suggested that in order to

obtain good dehumidification performance, two very

important factors have to be taken into account: one is to

providing more contacted area between solution and air as

possible, and the other is to keep low temperature of the

solution and air. As a whole, both desiccant with low inlet

temperature and simultaneous cooling during the

dehumidification can provide better dehumidification

performance.

5. ACKNOWLEDGMENTS

This research was supported by the grants from the fund of

National Natural Science Foundation of China under the

contracts No.50676018, the key grant project of Chinese

Ministry of Education (307013) and the Foundation for

Excellent Doctoral Dissertation of Southeast University.

These supports are gratefully acknowledged.

6. REFERENCES

(1) H.M. Factor, G. Grossman, “A packed bed

dehumidifier/regenerator for solar air conditioning with

liquid desiccant”, Solar Energy 1980, 24, 541-550.

(2) N. Fumo, D.Y. Goswami, “Study of an aqueous lithium

chloride desiccant system: air dehumidification and

desiccant regeneration”, Solar energy 2002, 72(4),

351-361

(3) P. Gandhidsan, “Quick performance predictions of

liquid desiccant regeneration in a packed bed”, Solar

Energy 2005, 79 (1), 47-55

(4) S. Jain, P.L., Dhar, S.C. Kaushik, “Experimental study

on the dehumidifier and regenerator of a liquid

desiccant cooling system”, Applied Thermal

Engineering 2000, 20, 253-267

(5) W.Y. Saman, S. Alizadeh, “An experimental study on a

cross-flow type plate heat exchanger for

dehumidification/cooling”, Solar Energy 2002, 73(1),

59-71

(6) X.H. Liu, Y. Zhang, K.Y. Qu etc, “Experimental study

on mass transfer performances of cross flow

dehumidifier using liquid desiccant”, Energy Convers.

Mgmt 2006, 47, 2682-2692

(7) Yonggao Yin, Xiaosong Zhang, Rongbing Lai,

“Modeling and comparative study on two types of

dehumidifiers with liquid desiccant”, Journal of

Chemical Industry and Engineering 2006, 57(12),

2828-2833

(8) Y.G. Yin, X.S. Zhang, Z.Q. Chen, “Experimental study

on dehumidifier and regenerator of liquid desiccant

cooling air conditioning system”, Building and

Environment 2007, 42(7), 2505-2511

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