Al-Khwarizmi 

Engineering   

Journal 
Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 77 (2014) 

 

 

Experimental Performance of a Finned-tube Silica Gel Adsorption  

Chiller for Air-Conditioning Application 
 

Mohammed A. Atiya*     Farkad A. Lattieff**
 
     Adil A. Al-Hemiri***

 
 

*Dean of Alkhwarizmi College of Engineering / University of Baghdad  

**Research & Development Department / Ministry of Higher Education 

***Department of Environment / Collage of Engineering / University of Baghdad 

*Email: mohatiya1965@gmail.com 

 **Email: farkad400@yahoo.com 

***Email: hemiri2004@gmail.com 

 
(Received 21 may 2014; accepted  12 October 2014) 

 
 

Abstract 

 
    This work presents the construction of a test apparatus for air-conditioning application that is flexible in changing a 
scaled down adsorbent bed modules. To improve the heat and mass transfer performance of the adsorbent bed, a 

finned-tube of the adsorbent bed heat exchanger was used. The results show that the specific cooling power (SCP) and 

the coefficient of performance (COP) are 163 W/kg and 0.16, respectively, when the cycle time is 40 min, the hot 

water temperature is 90
o
C, the cooling water temperature is 30

o
C and the evaporative water temperature is 11.4

o
C. 

 

Keywords: Adsorption, refrigeration, cooling power, COP, silica gel-water. 

 
 

1. Introduction  
 

Energy is the main driver for the well being, 

development and quality of life for people. 

Nowadays, the strength of countries depends on 

the extent of diversification of energy that they 

get it. It is no longer limited to oil as principal 

source of energy but diversified to include many 

sources of energy, called Renewable Energy 

[1].Electricity consumption on air-conditioning 

results in a shortage of the rush of electricity in 

summer [2]. In addition, the usage of CFCs and 

HCFCs in traditional air-conditioning systems 

causes the ozone depletion and green house 

effects [2]. Due to the large consumption for air-

conditioning systems in building, solar cooling 

systems have attracted great attention nowadays 

[2]. There are many researches about adsorption 

air-conditioning. For example, in order to 

improve COP, C.J. Chen and his co-workers have 

adopted a heat and mass recovery by installing 

vacuum valves between the adsorption and 
desorption chambers of the adsorption chiller [3]. 

However, silica gel-water adsorption chillers are 

welcomed for the solar air-conditioning systems 

and widely studied [4]. Kahan et al. studied the 

influence of the overall thermal conductance of 

the sorption elements and evaporator as well as 

the adsorbent mass on the chiller performance 

and indicated that the cycle performance strongly 

influenced by the overall thermal conductance of 

the sorption elements [5]. Generally, a heat 

source with 70-80
o
C is economical for silica gel-

water adsorption chiller and easily obtained from 

solar energy or waste heat [6]. Demir et al. 

handled the mechanism of heat and mass transfer 

in annulus adsorbent with which shows that the 

adsorption period increases with increase the 

porosity value [7]. Al Sapienza et al. investigated 

a new composite adsorbent and tested it by a lab-

scale adsorption chiller. They observed that the 

optimal cycle time performance was strongly 

depended on cycle time and relative duration of 

the isobaric desorption and adsorption steps [8].  

Aristov et al. investigated, using an intermittent 

cycle, the effect of the relative duration isobaric 

mailto:mohatiya1965@gmail.com
mailto:farkad400@yahoo.com
mailto:hemiri2004@gmail.com


Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

69 
 

adsorption/desorption stages to maximize the 

coefficient of performance and the specific 

cooling power of the cycle. They found that the 

desorption phase is faster than the adsorption one 

and this should considered as a routine case for 

adsorption refrigeration cycle, probably, because 

adsorption occurs at higher temperature and 

pressure and hence, they suggested practical 

recommendation to rationally reallocate the 

duration of  adsorption and  desorption  phases 

[9]. A newly developed adsorption chiller was 

described and tested by Liu et al. In this 

adsorption cycle system, there is no refrigerant 

valve. Thus, the problem of mass transfer 

resistance was eliminated. The experimental 

results proved that it is able to produce a cooling 

capacity of 6.5 kW with COP of about 0.4[10]. 

To demonstrate the effect of mass and heat 

transfer on the SCP and COP, a laboratory 

prototype of adsorption cooling machine has been 

designed by Wang and his team. Experiments 

showed that the COP was between 0.2-0.4 for 

refrigeration temperature of -10 to -15
o
C 

depending on the cooling water temperature. The 

SCP ranges from 300-500 W/kg adsorbent [11]. 

In order to improve the reliability of silica gel-

water adsorption chiller, chillers combined by 

two bed cooling systems were modified. The 

recent results [12] were that the cooling capacity 

and COP of such chiller were 3.6 kW and 0.32, 

respectively, at the hot water inlet temperature of 

57
o
C, cooling water temperature of 27

o
C,and 

chilled water temperature of 15
o
C; those were up 

to 5.7 kW and COP of 0.41, respectively, when 

the hot water inlet temperature, cooling water 

temperature, were changed to 80
o
C and 29

o
C, 

respectively. Those  investigation had resulted in 

closer steps to commercial prototypes thought so 

far those prototypes were not really commercial 

once due to its high cost [13]. A novel composite 

dsorbent “Silica gel modified by Calcium nitrate” 

(SWS-L8) for utilization in adsorption chillers 

driven by low temperature heat has tested by 

Freni et al. SWS-8L grains were embedded inside 

aluminium heat exchanger with high thermal 

efficiency. Experimental cooling COP, specific 

cooling power SCP and volumetric specific 

cooling power VSCP obtained were 0.18-0.31 

(cycle time 10 min), 190-383 w/kg dry sorbent 

and 104-212 w/dm
3
, respectively [14]. Miyazaki 

et al. investigated the influenced of heat 

exchanger parameters, such as heat capacity and 

NTU, on the optimum performance of a single-

stage adsorption chiller using silica gel as a 

working pair. He concluded that the smaller heat 

capacity improved both the SCP and COP. While 

the large NTU of the adsorbent bed resulted in the 

decrease of COP due to the short cycle time 

although the maximum SCP was enhanced [15]. 

Niazamand and Dabadeh analyzed the effect of 

the bed configuration, such as fins spacing, bed 

high, and particle size high on the performance of 

the system. They showed that fins in general 

reduced the COP of the system; however, for a 

given cooling capacity CP, the bed size can be 

reduced dramatically, when fins were employed 

at the cost of slightly lower COP. Also, It is 

shown that there is an optimal particle diameter 

associated with each bed configuration that 

maximizes the COP and SCP [16]. 

In this work, a fine-tube silica gel-adsorption 

chiller for air-conditioning application built in 

order to generate cooling energy and evaluate the 

cooling output performance. The experimental 

data evaluated in terms of cooling output (or 

specific cooling power SCP) and coefficient of 

performance COP. This study will benefit the 

further application and development of the solar 

adsorption air-conditioning system.  

 

 

2. Description of the Prototype  
 

    The optimization of the refrigeration adsorption 

cycle conducted at the Solar Energy Laboratory / 

Federal University of Paraiba by the use of a lab-

scale facility realized to the support the 

development of the solar adsorption chiller.  

Fig. 1 (A) shows the schematic diagram of the 

experimental adsorption chiller prototype. The 

adsorption chiller has a single bed, a condenser, 

an evaporator and heating/cooling water system. 

The evaporator lies at the bottom of the chiller, 

and the condenser is located at the top of the 

conditions and operating adsorption cycles. The 

whole prototype connected to a water heating 

system, for refrigeration, tape water for cooling, 

and a vacuum pump system. The heating system 

is next to the adsorber. All the valves controlled 

manually. The prototype designed to test various 

operations. Two main parameters measured 

during the experiment: temperature and pressure. 

All sensors connected to a data logger and 

recorded every 8.5 seconds. The data 

measurements taken after the cycle steady has 

been reached. A computer used to collect and 

process the data measurement acquired by the 

data logger. The flow rate of the hot water and 

cooling water are constant at 0.4 kg/s. The 

adsorber is of a shell-and-tube configuration, 

which readily manufactured, and it withstand high 

operating pressure and incur low energy mass. 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

70 
 

Using fins and tubes design, (Fig. 1 (B)), made 

the surface area to volume relatively low. The fins 

on the adjacent tube overlap slightly in order to 

reach all the portions of the shell voids. They 

allowed tubes to be more widely spaced to 

accommodate greater proportion of adsorbent. 

Furthermore, the fins have several times a wider 

surface area than the bare tube, which counter the 

low conductance through the contact between the 

metal and the adsorbent. This design has 905 m
2
 

surface area / m
3
 volume. The main properties are 

resumed in Table. 1. 

 

 

3. Measurements 
 

The experimental conditions are stated in 

Table. 2. The temperature are measured at the 

inlet and outlet of the heat exchanger of the 

adsorber during cooling and heating periods. The 

pressures are measured at the adsorber. The 

amount of the desorbed water,   , are measured 
by the level graduated  cylinder. 

     The performance evaluation of the adsorption 

chiller is calculated from the terms of cooling 

power    [w], specific cooling power SCP 
[w/kg] , and coefficient of performance COP, 

which are calculated as follows: 

     
            

  
                                       …(1) 

                                                        …(2)  

    
    

    
                                                    …(3) 

 

    
    

                    
                         …(4) 

 

 

 

 

 

 

 

 

 

 

 
Table 1, 
Main properties of the adsorber bed.  

 
 

Table 2, 

Prototype experimental conditions. 

   

 

 

 

 

 

 

 

 

 

 

 

 

                                                   

 

 

 

Property Value Unit 

Total mass of 

adsorbent 

Grain size  

4 

7 

Kg 

mm 

Tube length 0.5  m 

Number of tube 4  

Inside tube diameter 0.017 m 

Outside tube diameter 

Fin diameter 

Fin space 

0.19  
0.05  

0.008 

m 

m 

m 

Parameter Value Unit 

   

   

   

   

  

  

        

        

            

   

                     

       

     

    

   

    

    

    



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

71 
 

 

 

 

 

 

                                 

 

 

 

 

 

 

 

 

 

 
                                                                  C  

                     
          

(A) (B) 
 

Fig. 1. Schematic of experimental adsorption chiller (A),  adsorber (B)

 

4. Results and Discussion  

 

4.1. Temperature Profile of System 
 

As the driving forces, the hot water inlet 

temperature is very important to the adsorption 

refrigeration system. A high water temperature 

causes a large temperature lifts for the system at 

the same cooling temperature. Then, the larger 

temperature lifts results in a high refrigeration 

capacity. Fig. 2 illustrates the cycle variation of 

the adsorbent temperature with inlet hot water 

temperature of 90
o
C (with constant cooling water 

of 30
o
C) in the adsorber heat exchanger packed 

with silica gel grains. Fig. 2 also shows that, the 

temperature effectiveness of the adsorbent 

element’s capability to exchange sensible heat is 

based on the actual and maximum temperature 

difference. This difference decreases with time. 

According to this figure, the bed temperature rises 

sharply before the 10 mins, but after 20 mins this 

temperature difference becomes small. The reason 

of this small difference is the water vapour 

releases from the silica gel grains. After 60 mins, 

this difference reduced to a very small value. Fig. 
3 shows the temporal evolution of the isosteric 

cooling, isosteric heating, desorption and 

adsorption phases at a steady state for the 

following operating conditions concluded from the 

experiment test (Table 2). It is observed that 

during the isostering cooling, the temperature of 

the bed will decrease from 90
o
C to 62

o
C (blue 

linear line) at after this moment the valve between 

the adsorber and the evaporator will open until the 

temperature of the adsorbent bed becomes 35
o
C 

(blue curve line). After elapsed of 20 mins, the 

isostearing heating will start and the temperature 

of the adsorbent bed increases from 35
o
C to 62

o
C 

(red linear line), then the valve between the 

condenser and the adsorber will open for 

desorption process until the temperature becomes 

90
o
C again (red curve line).  

 

 

 
Silica gel 

Metal screen 

Cooling 
water  

Data logger 

Cylinder 

Condense
r 

Vapor 

Hot water out 

Pressure transducer 

Hot water in 

 Heating 
   Water device 

device 

 

Pressure transducer 

transducer 

Evaporator 

Condenser 

r 

Shell 

l 

Adsorber 

wir 

 
Silica gel 

computer 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

72 
 

  
 

Fig. 2. Isosteric heating/cooling cycles. 

 

 
 

Fig. 3. Cycle time of the system. 

 

 

4.2. Refrigerant Exchange Amount (  ) 
 

Desorptoin process is very close in 

concentration change to adsoption process at the 

same temperature, and many researches assume 

both are the same in adsorption refrigeration 

process [17] . Working on the temperature of 90
o
C 

tends to decrease the water content to the 

minimum and, consequently, it results in 

increasing the water adsorbed during the 

adsorption process and that increases the cooling 

capacity. Fig. 4 aims to determine the desorbed 

water, which represents the amount of water 

involved in one adsorption-desorption cycle. The 

experiment has consisted of loading adsorbent 

with water under a temperature desorbed at the 

temperature of 90
o
C in the same of 35

o
C, then the 

adsorbent were, afterwards, duration as the 

adsorption time. The difference between adsorbent 

loading at the end of the adsorption, and its 

loading at the end of desorption constitutes the 

water exchanged amount (  ). Therefore, during 
the desorption phase, the refrigerant vapor was 

allowed to be collected via the flask by opening 

valve 6 (Fig. 1). The measurment of the adsorpion 

capacity of this type of silica-gel showed that it is 

able to exchange a large amount of water of 0.08 

kg/kg under operating conditions so it is typical 

for air conditioning applictions as well as to be 

driven by hot water temperaure of 90
o
C. 

 

 

 

                

 

Fig. 4. Mass and concentration of water desorbed variation with time. 

0 

0.05 

0.1 

0.15 

0.2 

0.25 

0.3 

0.35 

0.4 

0 10 20 30 40 

M
a

ss
 o

f 
w

a
te

r 
a

d
so

rb
e

d
 (

K
g

) 

Time [min] 

0 

0.01 

0.02 

0.03 

0.04 

0.05 

0.06 

0.07 

0.08 

0.09 

0 10 20 30 40 

∆
X

 (
k

g
/k

g
) 

Time [min] 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

73 
 

4.3.  Cooling power, SCP, and COP 
 

      Generally, cooling capacity, CP (or specific 

cooling capacity, SCP) and COP are two 

parameters to determine the performance of the 

refrigeration cycle. The cycle time will be the best 

when the CP and COP reach their maximum values 

at the same time, but in real system, they are not 

[18]. The results for cooling capacity, COP, and 

SCP values are shown in Fig. 5. The COP has an 

optimum value of about 0.16 at the proposed first 

half cycle of 20 mins. Indeed, the COP is affected 

by the dynamic limitations of the adsorbent bed, 

parasitic losses and inert mass of the heat 

exchangers. The SCP reaches the peak value of 

198.2 W/kg of dry adsorbent when the cycle time is 

9.1 mins and decreases for a higher cycle time with 

minimum value of 163 W/kg at a time of 20 mins. 

Cycle time at 9.1 mins or shorter resulted in lower 

performance of heat transferred/extracted to/from 

the adsorbent bed. Moreover, in our case, the cycle 

time at 9.1 mins was not sufficient to complete the 

hydration of silica gel during adsorption phase. The 

obtained results indicate that the cycle time of 20 

mins gives a reasonable compromise between the 

SCP and COP. 

The cycle time of 9.1 mins allows maximizing 

the SCP, while the maximum COP is obtained 

when the cycle time is 31 mins. This information is 

of  a  high  practical  significance  when  optimized   

for high COP and SCP. In general, there designing 

an adsorption chiller that must be is a maximum of 

the cooling power (Qe) at a specific cycle time. 

Larger cycle time leads to higher coefficient of 

performance COP, but less cooling power. The 

relation is shown in Fig. 5, it can be noted that by 

increasing the cooling time, the cooling power (Qe) 

value increases and there is a maximum Qe value 

(793 W) when the cooling time is 9.1 mins, after 

that the Qe decreases as the cooling time increases. 

This time of  9.1 mins, is enough just to cool the 

adsorbent up to 42.5
o
C, not to 35

o
C, and the 

adsorbers are insufficiently cooled or heated during 

the adsorption and desorption processes 

respectively. However, the value of Qe at 20 mins 

is 664 W, which is less than the maximum value by 

149 W. But, it is still an acceptable value to work 

on. Consequently, a strategy was adopted to assess 

the adsorption time of 20 mins. The same results 

are obtained for the COP and SCP: increasing the 

temperature of the bed leads to increase the cooling 

power.

               

 

Fig. 5. Experimental results of COP, SCP, and cooling capacity as a function of the time. 

 

 

4.4. Effect of Operating Conditions on the  
System    Performance 

  
The tests for measuring the performance of the 

adsorber were continued by carrying out a large 

number of experiments under various operating 

temperatures. Fig. 6 shows the COP and SCP as a 

function of the bed temperature for the time of 20 

mins. As expected, the variation of the bed 

temperature had strong effect on the performance. 

It can be observed that the performance increases 

when the bed temperature increases. However, 

adequate performance can be achieved even for a 

lower bed temperature. In particular, the COP of 

0.072 and SCP of 71 W/kg were measured for a 

bed temperature of 70
o
C, demonstrating that this 

adsorbent can be driven by a low-temperature heat 

source. In general, there is a maximum of the 

cooling power (Qe) at a specific cycle time. Larger 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

74 
 

cycle time leads to higher coefficient of 

performance COP, but less cooling power. The 

relation is shown in Fig. 7, it can be noted that by 

increasing the cooling time, the cooling power 

(Qe) value increases and there is a maximum Qe 

value (793 W) when the cooling time is 9.1 mins, 

after that the Qe decreases as the cooling time 

increases. This time of  9.1 mins, is enough just to 

cool the adsorbent up to 42.5
o
C, not to 35

o
C, and 

the adsorbers are insufficiently cooled or heated 

during the adsorption and desorption processes 

respectively. However, the value of Qe at 20 mins 

is 664 W, which is less than the maximum value 

by 149 W. But, it is still an acceptable value to 

work on. Consequently, a strategy was adopted to 

assess the adsorption time of 20 mins. The same 

results are obtained for the COP and SCP: 

increasing the temperature of the bed leads to 

increase the cooling power. 

 

              
 

Fig. 6. Experimental results of COP and SCP as a function of the bed temperature. 

 

 

 
 

Fig. 7. Cooling capacity variations with bed temperature.   

 

4.5. Comparison with Other Adsorption 
Chillers  

 

As discussed from the results, the chiller 

performance is quite similar to that on the former 

adsorption chiller [19-21]. Compared with adsorber 

presented by Chang et al. [19], this adsorber shows 

a lower refrigerant exchange amount (        
kg H2O / kg adsorbent). According to Chang et al., 

       kg H2O / kg adsorbent, that the 
rectangular fins were used to extend the mass 

transfer area, while in this study, circular fin tubes 

were adopted in the adsorber. Geyer and Paar [20] 

built up a laboratory unit (approx. 1000 w cooling 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

75 
 

capacity) using a flat fin- tube heat exchanger. 

The maximum values of the cooling capacity and 

COP under operating conditions of hot water (= 

80
o
C), cooling water (= 27

o
C), and entire cyle time 

(= 45 mins), were 700 w and 0.3, respectively [20]. 

It was close to the operating conditions of our 

results, but the difference is with the value of COP, 

which is higher in Geyer and Paar silica gel used in 

the experiment. Another work. May be the reason is 

due to the properties of considered comparison is 

with the work of Kubota et al. [21], who used 5.8 

kg of dry silica gel in a circular finned-tube heat 

exchanger. However, his results showed that water 

exchange amount,          kg H2O / kg 
adsorbent, for 6 min, hot water of 80

o
C, and 

cooling water of 30
o
C. While the cooling capacity 

and COP are 1200 W and 0.25, respectively.  

 

 

4. Conclusions  
 

In this paper, a new design of a fin-tube heat 

exchanger was presented and tested in adsorption 

chiller prototype.  

The measurement of the equilibrium properties 

showed that the silica gel adsorbent is able to 

exchange amount of 0.08 kg H2O/kg silica gel 

under the operating conditions of air-conditioning 

applications.  

Considering, the results of this work for 20 

mins adsorption time demonstrated that the values 

of cooling power, SCP, and COP are 664 w,      

163 w/kg adsorbent, and 0.16, respectively [21]. 
 

 

Acknowledgment  

 

The authors would like to greatly acknowledge 

the R & D Dep. (Research & Development 

Department/ Iraqi Ministry of Higher education 

and Scientific Research) for supporting this 

research through a Program Research Missions. 

As well as extend our sincere thanks to LSE 

(Laboratory of solar energy) at Fedral University 

of Paraiba/Brazil, where the prototype and 

experiments were carried out.  

 

Nomenclature 
 

   Specific Surface area, [m
2
/g] 

    Coefficient of performance 

     Specific heat of hot water, [kJ/kg.
o
C] 

   Average particle diameter, [mm] 

      latent heat of evaporation, [kJ/kg] 

k Thermal conductivity, [W/m.
 o
C] 

     Mass of adsorbent, [kg] 

    Mass flow rate of hot water, [kg/s] 

     Cooling power, [W] 

    Specific cooling power, [W/kg] 

   Adsorption time, [min] 

   Desorption time, [min] 

     Isostering time, [min] 

       Cycle time, [min] 

   Cooling water temperature, [
o
C] 

     Hot water in, [
o
C] 

     Hot water out, [
o
C] 

   Adsorption temperature, [
o
C] 

   Desorption temperature, [
o
C] 

   Concentration at specific time,[kg/kg] 

   Concentration at specific time,[kg/kg] 

ρ Apparent density, [kg/m
3
] 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 



Mohammed A. Atiya                       Al-Khwarizmi Engineering Journal, Vol. 10, No. 3, P.P. 68- 78 (2014) 
 

76 
 

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Adsorption Air-Conditioning System” 

Ph.D. Thesis, Baghdad University. 



 (2014) 68- 78، صفحة 3، العدد10دجلة الخوارزمي الهندسية المجلالسراج                                                      ممحمد عبد عطية 
 

77 
 

 

 

الغراض تبريد الهواءلمبرد امتزازي ذو انبوب زعنفي للسيلكا جل  التجريبي األداء  
 

*محمد عبد عطية السراج
 

 ***عادل احمد عوض      * *فرقد علي لطيف       
 جامعة بغداد/ عميد كلية الهندسة الخوارزمي*

 وزارة التعليم العالي والبحث العلمي/ دائرة البحث والتطوير**                  
 بغدادجامعة / كلية الهندسة / قسم هندسة البيئة ****

mohatiya1965@gmail.com : االلكتروني البريد*         
 farkad400@yahoo.com **االلكتروني البريد :     

 hemiri2004@gmail.com: االلكتروني البريد***

 

 
 

 الخالصة 

 
 ،ين كفاءة انتقال الحرارة والمادةفمن اجل تحس. ة االمتزازوحد موديل تغيير في بالمرونة يتسم لمنظومة تبريد الهواء اختبار جهاز بناء البحث هذا يعرض

 ،6136 و كجم/  واط 361 هي (COP) األداء ومعامل (SCP) التبريد سعة أن النتائج أظهرت. مزود بزعانف لوحدة االمتزاز  حراري مبادل استخدام تم

 ودرجةمئوية  درجة 16 التبريد مياه ودرجة حرارةمئوية، درجة 06 الساخن الماء حرارة ودرجة دقيقة، 06 هو دورةال وقت يكون عندما التوالي، على

  .درجة مئوية 3310 المبرد الماء حرارة

 

 

 

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