Performance analysis of a new combined absorption-adsorption refrigeration system to improve energy

Abstract

Keywords: Absorption; Adsorption; Cascaded System; Low Grade Heat Source; Refrigeration

Introduction

One of the most essential topics of research in energy-related applications is how to improve energy efficiency while simultaneously mitigating the impact of associated environmental issues. The amount of energy that is used all over

the globe is steadily growing and is anticipated to increase by 28% from 2015 to 2040 [1-2]. Due to the long and hot summer months in the gulf countries, one of the key contributors to the region’s ever-increasing energy consumption is the ever-increasing burden placed on refrigeration

*Corresponding author. *E-mail address: aminmt@rcjy.edu.sa This paper was recommended for publication in revised form by Editor-in-Chief Ahmet Selim Dalkılıç Published by Yıldız Technical University Press, İstanbul, Turkey Copyright 2021, Yıldız Technical University. This is an open access article under the CC BY-NC license (http://creativecommons.org/licenses/by-nc/4.0/).

and air-conditioning systems. The overall trend in cooling applications is rising, which may be attributed to the rising rates of energy consumption, population growth, and economic activity. Traditional vapor compression refrigeration cycles (VCRC) are the basis for the most popular types of cooling cycles and the commonly utilized today due to the great performance they provide. Harby and Fahad [3] concluded that traditional VCRC have a high rate of electrical energy consumption, which is generated by fossil fuels, and they use refrigerants that are harmful to the environment. Therefore, alternative cooling solutions need to be introduced to strike a balance between the development of new technologies, the consumption of energy, and the conservation of the environment. In today’s world, thermally driven sorption technology (absorption/adsorption) has become of great importance nowadays compared with traditional systems (VCRC). Recently, there is a lot of interest in thermally driven sorption systems because of the benefits they provide. This technology can be run on clean and sustainable energy, it is inexpensive, it does not have any moving parts, and it uses working fluids that are beneficial to the environment [4-5]. Ali et al. [6] declared that absorption systems (ABS) are widely used compared with ADS for large cooling capacity and high COP. Harby et al. [7] concluded that ADS can work effectively at low heat-source temperatures compared to ABS. Stephan [8] showed that the COP of LiBr/H2O ABS varied from 0.6 to 0.8 when tested with heat sources between 80 and 100°C and cooling water at 20oC. Adsorption systems can be operated at lower heat source temperatures. Because it can withstand temperatures in this range, sorption cycles are an excellent choice for lowgrade heat source temperatures. However, because of their low COP and large sizes, sorption cycles (ABS and ADS) have limitations in the more widespread implementation and commercialization that have been carried out worldwide [9-11]. Various research projects on the assessment of ABS’s performance have been carried out recently. Sun et al. [12] provide a comprehensive overview of the working fluids that are utilized for ABS. Different studies have focused on improving the heat and mass transfer coefficients of the heat exchanger elements [13-14]. Sun et al. [15] suggested new working fluids. Ibarra-Bahena and Wang [1617] proposed new designs and configurations of the cycle components. Other studies utilized a variety of low-grade heat sources [18-21]. Seyfouri et al. and Bruno et al. [22-23] utilized a combined with cogeneration power plants. Many other studies focused on the investigation of increase the rate of heat transfer rate [24-26]. In addition, investigations on multi-effect ABS are being examined [27-30]. Cascade absorption systems are also investigated with the goal of improving energy usage [31]. Integration of the single effect ABS with other cooling technologies, such as VCRs, has also been researched [32-36] with the goal of increasing the system’s coefficient of performance (COP).

In addition, a great deal of work is put in to improving the performance of ADS, which includes the creation of more advanced strategies [37-39]. There have been several research also that have concentrated on enhancing the heat and mass transfer coefficients of the adsorbent beds [40-41]. Additional adsorbent pairs were also investigated by several research [42-44]. Alam et al. [45] provided a new design and construction of adsorbent bed heat exchangers to achieve greater heat transmission. Tamainot et al. [46] provided several investigations on the relationship between energy efficiency and the use of a variety of heat sources. A great number of additional research recommends the use of multi-stage and multi-bed multi-stage ADS to improve overall efficiency [47-50]. Additional studies are being done to investigate the possibility of integrating the ADS with several alternative cooling methods [51-55]. It has been observed in the past. Meunier and Akahira et al. [5657] concluded that, combined cascade of two-bed two-stage ADS may increase the total system COP by up to 50-60% as reported. As was just said, the cooling cycles cause consumers to utilize higher-grade energy, which in turn increases the consumption of fossil fuels and the amount of CO2 emissions. A considerable number of studies have been performed on sorption cooling systems that are either single or combined or integrated with other cooling technologies such as VCRC. Deshdeep et al. and Touaibi et al. [58-59] showed that the COP of the integrated systems which may include a cascade cycle can be improved leading to greater energy efficiency. As a result of the low COP, there are still obstacles in the way of the broad deployment and commercialization of sorption cooling systems around the globe. A decrease in the use of primary energy as well as a reduction in CO2 and other emissions may result from improved energy efficiency. Additional research is still required to improve the technologies’ coefficients of performance (COP) and energy consumption efficiency. The purpose of this work was to explore the performance of combined absorption-adsorption cascade refrigeration systems (ABS-ADS) to increase energy efficiency and provide low-temperature cooling. In this work, the upper cycle makes use of the single-stage ADS, while the bottom cycle operates with the single-effect ABS. A shell and tube heat exchanger connects the evaporator of the ADS to the condenser of the ABS. Additionally, in a series arrangement, the hot water that is discharged from the generator of the ABS chiller is used to power the desorber of the ADS chiller. This configuration has the potential to enhance energy usage, raise the total COP, save the environment, and create chilled water at low temperatures using sources of heat with low temperatures. In addition, combining the two methods may provide the benefits that each cycle offers while simultaneously minimizing the drawbacks. The outcomes of the suggested combined ABS-ADS chiller are evaluated and compared with the findings of previous research using standalone ABS, ADS, and other

methodologies. The impact that the various operating circumstances have on the output of the proposed system is another aspect that is being investigated.

Description And Working Principle Of The Proposed Cascade Abs-Ads

The suggested combined cascading absorption-adsorption refrigeration systems (ABS-ADS) that are driven by low-grade heat sources are shown in Figure 1 with a conceptual structure of the system. In the bottom cycle of this system is an ABS chiller with a single effect, and in the top cycle is ADS chiller with a single stage. The evaporator of the ADS and the condenser of the ABS are included in the same shell and tube heat exchanger, which couples the two components together. In a series configuration, the hot water that is discharged from the generator of the ABS chiller is routed to the desorber of the ADS chiller, where it is utilized to drive the system at the same mass flow rate. Figure 2 is a schematic representation of the different components of the ABS-ADS system. The single-effect

LiBr-H2O ABS contains an evaporator element, a condenser element, a generator element, an absorber element, a throttling valve, a pump, and a heat exchanger. The single-stage Silica-gel-water ADS contains two adsorbent beds (A and B), a condenser, an expansion valve, and an evaporator element. The evaporator of the ADS is thermally coupled with the condenser of the ABS in the same shell . and tube heat exchanger. The system cooling capacity Q evap is obtained from the evaporator of the ABS. The hot water from the heat source is firstly used to drive the generator of ABS and is then used to generate the desorber of the ADS. At the . beginning of operation, hot water from heat source (Qgen) is flows to power the generator of ABS causing water evaporates from LiBr/H2O solution. The water evaporates quickly and flows to the shell side of integrated condenser-evaporator heat exchanger. The water vapor . condensed at high pressure (Qcond), and the strong solution returns to the absorber through the internal heat exchanger. The condensation water vapor is throttled through the throttling valve and flows to evaporator of ABS providing . the overall cooling capacity (Q evap) of the cascade cycle.

Figure 1. General layout of the cascade combined ABS and ADS.

The water vapor leaving the evaporator is then absorbed by the strong LiBr solution in the absorber. The weak solution LiBr/H2O from the absorber element is then pumped again to generator through the solution heat exchanger and the cycle repeated. A detailed operating work of ABS can be found in the literature [17]. The outlet hot water from the ABS chiller flows to drive the desorber bed (A) of. ADS to heat the Silica-gel. At the same time, cold water (Qads) from the cooling tower is flows to cool the second adsorber bed (B). During these processes (pre-cooling/pre-heating), all valves (V1, V2, V3, V4)

are closed and no adsorption/desorption process occurs. After this short intermediate period, valves V3 and V2 are opened to allow refrigerant (water vapor) to flow from the bed (A) to condenser and refrigerant transfer from integrated condenser-evaporator heat exchanger to bed (B). The vapor is condensed as it travels through the condenser element to the throttling mechanism, which then allows it to go to the evaporator. Because of the condensation load that ABS places on the integrated condenser-evaporator heat exchanger, water is turned into vapor there. When the concentration of the working fluid reaches the level

Figure 2. Schematic of the proposed combined cascade ABS-ADS in series arrangement with the heat source.

of equilibrium, the flows of heated and cooling fluid are diverted by switching the three-way valves. This allows for the concentration of the working fluid to remain constant. Several research have already described how the ADS operates according to its fundamental concept [60-61]. Simulation Modeling of the Cascade ABS-ADS Cycle

The outlet temperature from the condenser of ADS: (8) Energy balance of evaporator for of ADS:

Adsorption isotherm and kinetics The equilibrium of the RD silica gel/water pair calculated by Ahmed et al. [43]: (1) The rate of adsorption and desorption the RD silica gel/ water pair calculated by:

(9) The outlet temperature of evaporator for of ADS: (10) Energy balance absorber for the ABS:

(4) The parameters used in the previous equations are given by [43]. Energy equilibrium The energy balance equation for the two-bed adsorption cooling system was given previously by Khairul et. al [49] and El-Sharkawy et. al [50]. The same model is used here for RD silica gel/water pair while considering the proposed cascading part of the ABC section. The correlation of energy balance in the adsorber/ desorber beds of ADS given by:

(13) The outlet temperature of generator for ABS: (14) Energy balance of condenser for ABS:

(5) The outlet temperature of adsorber/desorber beds of ADS given by:

of model inputs, and choose the appropriate property correlations.

The outlet chilled temperature evaporator of ABS: (18) Performance indicators The system performance includes cooling capacity (Cap) and COP is typically given by: (19)

(20) The above developed model is implemented and solved simultaneously by MATLAB code that was just generated. The design conditions that were intended to be used for the ABS-ADS system are shown in Table 1 [62]. During the computation, a period of 0.01 seconds was used. When the absolute difference between subsequent cycles becomes less than 10-4. the iteration has reached its conclusion. As soon as we have the collection of equations, the next step is to think about the relevant assumptions, define the collection

Model Validations The mathematical model that was built for ABS-ADS chiller is validated by comparing the findings obtained results with the results obtained from the standalone ABS chiller model, ADS chiller model, and with experimental data that can be found in the literature. Table 2 shows the comparison of the findings of current model and experimental data from Balghouthi et al. [63] at the same design and operating characteristics. The findings from the current model and the experimental data [63] were found to be in excellent agreement with each other, with the greatest error being less than ±2%. Figure 3 depicts the comparison between the temperature profiles of the adsorber (Tads) and desorber (Tdes) heat exchangers results from the present simulation model and the those from the experimental data collected by Almohammadi and Harby [64] under the same design and operating circumstances. The heat source temperature was 85oC. As indicated, the inaccuracy is not more than ± 4% of the experimental data. Hence, it demonstrates that the present model can predict experimental data well.

Table 1. Design conditions for the ABS-ADS cycle [62] Parameters

Overall heat transfer coefficient of the utilized evaporator

Overall heat transfer coefficient of the utilized evaporator

Table 2. Simulation model validation with experimental data . Qabs [kW] . Qcond [kW] . Qgen [kW] . Qevap [kW] COP [-]

Figure 3. Validation of the simulated model of adsorption chiller with experimental data.

Results And Discussion

The purpose of this study is to evaluate the performance of a cascade ABS-ADS under a variety of various operating situations, with the goal of using low-grade heat source temperatures between 65-90oC and making effective use of the heat source. The findings of the ABS-ADS are analyzed and compared to those obtained from the single-effect ABS, the two-bed ADS, and other research of a similar kind. Figure 4 examines the temperature profiles of several components of the ABS-ADS chiller along the half cycle period. These temperatures include those of the adsorbent beds, the condenser, the evaporator, the generator, the absorber, and the hot and cold water. The hot water temperature for desorber and absorber beds is 85oC, while the cooling water temperature is 25oC. At the operating parameters detailed in Table 1, the adsorption/desorption cycle lasts for a duration of 400 seconds, whereas the switching time lasts for 25 seconds. As shown, during two-half cycles, the cycle transitions from a fluctuating condition to an almost steady state condition. After circumstances have reached steady state, the temperature of the desorber bed is about 2.7oC lower than the temperature of the hot water input, and the temperature of the adsorber bed is approximately 3oC higher than the temperature of the cooling water exit. The refrigeration capacity is 25.4 kW, and the average temperature of the cooled water is 12oC.

Figure 5 shows a comparison between cooling capacity of cascade ABS-ADS, single-effect ABS, and single-stage ADS versus regeneration temperature. Increasing regeneration temperature increases linearly the cooling capacity for all cycles. Increasing regeneration temperature from 65 to 90oC increases the cooling capacity from 3.5-16.8 and 10-36 and 13.2-40.8 for single stage two beds ADS, single effect ABS, and cascade ABS-ADS systems respectively. The cooling capacity by ABS-ADS is higher than that of ABS and ADS. The high temperatures of the heat source cause a partial desorption with a larger cycle time which increases the cooling effect. Figure 6 shows a comparison between cooling capacity of cascade ABS-ADS, ABS, and ADS versus regeneration temperature. It is also shown that in all systems, the COP first increases with the temperature of the heat source up to 75°C and then begins to decline as the temperature continues to rise. This might be because heat is insufficient for complete desorption process at temperatures lower than 75°C. Subsequently, the working fluid that has not been undesorbed has an impact on the subsequent adsorption process, which in turn reverses the cooling effect. The system needed more time and an additional water cycle in order to achieve the same level of cooling which resulted in a low COP. Because of the high temperatures of the regeneration process, more input energy is required for the operation, which results in larger losses from the system.

Figure 4. Temperature profiles of components for the cascade ABS-ADS cycle.

Figure 5. Comparison of cooling capacity for single-effect ABS, single-stage ADS, and cascade ABS-ADS vs temperatures of heat source. The greatest system COPs that were achieved were at a temperature of 75°C, and they were 0.36 for single-stage two-beds ADS, 0.59 for single-effect ABS, and 0.644 for cascade ABS-ADS systems. The COP of the proposed cascade ABS-ADS cycle is superior to that of the ABS cycle by 8.39% and the ADS cycle by 44%. In addition to the COP,

cooling capacity is also an important indicator that should be used to determine the performance of heat driven cooling systems. Figure 7 presents the variation of hot water flow rate . (m hw) on both cooling effect and system COP of the cascade ABS-ADS cycle. As shown, the cooling capacity and

Figure 6. Comparison of COP for ABS, ADS, and cascade ABS-ADS vs temperatures of heat source.

Figure 7. Effect of hot water flow rate of cascade ABS-ADS on cooling capacity and COP. COP raise with increasing hot water flow rates. However, the effect of hot water flow rate is high in lower than 1.0 kg/s, over that the raise in cooling effect and system COP is only minor. Figure 8 shows the variation of solution pump mass flow rate on cooling effect and system COP of cascade ABS-ADS. As observed, increasing solution pump flow rate from 0.06-0.16 kg/s increases cooling capacity linearly from 16-44 kW and COP from 0.61-0.63. The maximum value

of achieved COP is 0.63 obtained at 0.12 kg/s. The COP remains constant after 0.12 kg/s solution flow rate. A higher solution flow rate required more pumping work, which reduces COP by additional energy input to the system. Figure 9 presents the variation of chilled water inlet temperature with capacity and COP of the cascade ABSADS system. Increasing chilled water inlet temperature of ABS system from 8-16oC increases cooling capacity linearly from 20.6-36 kW and COP from 0.58-0.622. It is observed

Figure 8. Effect of solution pump flow rate of cascade ABS-ADS on cooling capacity and COP.

Figure 9. Chilled water inlet temperature variation vs cooling capacity and COP of cascade ABS-ADS. that a rise of 6oC in the chilled water temperature can cause around 7.2% enhancement of COP and around 71% that of cooling capacity at the same operating conditions. Rising chilled water temperatures have only small effects on the system COP. Comparison with Other Related Studies As mentioned earlier, the primary purpose of this work is to enhance the energy utilization and total COP of sorption systems at low grade heat source temperatures. The performance of the combined cascade absorption-adsorption

cooling systems is investigated under different temperature heat sources between 65 and 90 oC. Figure 10 shows a performance comparison between the present cascade ABSADS cycle and different standalone absorption systems and combined cascade absorption/absorption systems [72] found in the literature. The performance of the present cascade ABS-ADS cycle is driven by a low temperature heat source at 65 oC compared with other studies. The standalone conventional ABS cycles cannot operate effectively below 70 °C [71]. As can be seen, the performance of the

Figure 10. Comparison between present cascade ABS-ADS cycle and other previous single effect ABS cycle. proposed cascade ABS-ADS cycle works at low heat source temperatures (65oC) and produces around 13 kW cooling capacity with 0.56 COP. The proposed cascade ABS-ADS cycle provides a good value of COP and cooling capacity. In addition, at 60°C heat source temperature, the proposed cascade ABS-ADS cycle provides higher performance than other cycles working at higher heat source temperatures including the combined cascade absorption/absorption systems [72].

Conclusion

The current study investigates the performance assessment of a proposed combined cascade absorption-adsorption refrigeration system (ABS-ADS). The primary purpose is to increase energy efficiency and provide low-temperature cooling. The system under consideration is propelled by the low-grade heat source at low temperatures. The results from the ABS-ADS study are compared to those from the solo ABS and ADS investigations, as well as other research in the literature that is relevant to this topic. The following observations may be made as a result:

1. The cooling capacity of the ABS-ADS is 25.5 kW more

than the single-stage ABS and ADS, which is a difference of 16.8% and 177% at hot water outlet temperatures of 75oC generated from a low-grade heat source.

2. The temperature at which the COP is at its highest for

all systems is 75oC; beyond that, it begins to fall as the temperature of the heat source increases.

3. The COP of the proposed cascade ABS-ADS system is

superior to that of the ABS and ADS by 8.39% and 44%, respectively.

4. The effect of hot water flow rate is significantly lower

than 1.0 kg/s, after that the rise in cooling effect and system COP is only marginally significant. 5. The cooling capacity of the ABS-ADS system grows linearly from 16 to 44 kW when the solution pump flow rate is increased from 0.06-0.16 kg/s. The coefficient of performance also increases from 0.61-0.63.

6. The highest value of COP that may be attained is 0.63,

which can be acquired by operating the ABS-ADS system at 0.12 kg/s.

7. Raising the temperature of the chilled water from

8-16oC raises the cooling capacity of the ABS-ADS system linearly from 20.6-36 kW and raises the COP from

9. The performance of the suggested ABS-ADS system can

function at a temperature of 75oC and generate a high cooling effect in comparison to the other published research from the literature on various system designs and sizes.

Nomenclature

area, m2 specific heat capacity, Jkg-1k activation energy of surface diffusion, jmol-1 constant enthalpy jkg-1 mass flow rate, kgs-1

mass, kg pressure, Pa saturated pressure, Pa heat transfer, kW universal gas constant, jmol-1K-1 radius of the adsorbent particle, m temperature, oC overall heat transfer coefficient, Wm-1K isosteric heat of adsorption, Jkg-1 uptake, kgkg-1 concentration, % density, kgm-3

Subscripts Al aluminum abs absorption ads adsorption des desorber ads adsorbent bed sorption bed h Enthalpy, kJkg-1 hw hot water Cu copper heat transfer tube chw chilled water cond condenser cwa cooling water in adsorber/desorber cwc cooling water in condenser des desorption gen generator hex heat exchanger sg Silica gel sol solution ss strong solution ws weak solution eva evaporator in inlet out outlet ref refrigerant w water

Conflict Of Interest

The author declared no potential conflicts of interest with respect to the research, authorship, and/or publication of this article.

Ethics

There are no ethical issues with the publication of this manuscript.

References

1. Sumathy K, Yeung KH, Yong L. Technology devel- ACKNOWLEDGMENTS opment in the solar adsorption refrigeration sys- I author would like to thank Yanbu Industrial College tems. Prog Energy Combust Sci 2003;29:301-327. staff for providing me with good technical assistance while [CrossRef] conducting this research. [10] Wang R, Wang L. Adsorption refrigeration-green cooling driven by low grade thermal energy. Chin Sci Bull 1993;50:204. [CrossRef] AUTHORSHIP CONTRIBUTIONS
2. Ziegler F. State of the art in sorption heat pump- Authors equally contributed to this work. ing and cooling technologies. Int J Refrigeration 2002;25:450-459. [CrossRef]
3. Sun J, Fu L, Zhang S. A review of working fluids DATA AVAILABILITY STATEMENT of absorption cycles. Renew Sustain Energy Rev The authors confirm that the data that supports the 2012;16:1899-1906. [CrossRef] findings of this study are available within the article. Raw [13] Jawahar C, Saravanan R. Generator absorber heat data that support the finding of this study are available from exchange-based absorption cycle-a review. Renew the corresponding author, upon reasonable request. Sustain Energy Rev 2010;14:2372-2382. [CrossRef] 734 J Ther Eng, Vol. 10, No. 3, pp. 722−736, May, 2024
4. Alka S, Yash P. Evaluation and optimization of sin- gle-effect vapour absorption system for the dairy sor-assisted triple-effect H2O/LiBr absorption cool- industry using design of experiment approach. J ing cycles. Appl Therm Engineer 2002;22:295-308. Therm Engineer 2022;8:619-631. [CrossRef] [CrossRef]
5. Kamel A, Khalil KMS, Askalany A, Ali ES, Harby K, Ghazy M. Improving adsorption materials proper- absorption refrigeration cycles driven by low-tem- ties for renewable energy-driven cooling systems, perature heat sources using organic fluid mixtures as Therm Sci Engineer Prog 2024;50:102551. [CrossRef] working pairs. Appl Energy 2001;68:173-185. [CrossRef]
6. Ibarra-Bahena J, Romero RJ. Performance of dif- ferent experimental absorber designs in absorption Exergetic analysis of a double stage LiBr-H2O heat pump cycle technologies: A review. Energies thermal compressor cooled by air/water and 2014;7:751-766. [CrossRef] driven by low grade heat. Energy Conver Manage
7. Wang X, Chua HT. Absorption cooling: a review of 2005;46:1029-1042. [CrossRef] lithium bromide-water chiller technologies. Recent [31] Ahmet SD. Parametric study of energy, exergy, and Pat Mech Engineer 2009;2:193-213. [CrossRef] thermoeconomic analyses on vapor compression
8. Zhai X, Qu M, Li Y, Wang R. A review for research system cascaded with LiBr/Water and NH3/Water and new design options of solar absorption cooling absorption cascade refrigeration cycle. Anadolu systems. Renew Sustain Energy Rev 2011;15:4416- Univ J Sci Technol A - Appl Sci Engineer 2017;18:78- 4423. [CrossRef] 96. [CrossRef]
9. Siddiqui M, Said S. A review of solar powered absorption systems. Renew Sustain Energy Rev energy saving of a compression-absorption refrig- 2015;42:93-115. [CrossRef] eration system assisted by geothermal energy. Appl
10. Wang X, Bierwirth A, Christ A, Whittaker P, Therm Engineer 2006;26:288-294. [CrossRef] Regenauer-Lieb K, Chua HT. Application of geo- [33] Seyfouri Z, Ameri M. Analysis of integrated com- thermal absorption air-conditioning system: A case pression-absorption refrigeration systems powered study. Appl Therm Engineer 2013;50:71-80. [CrossRef] by a microturbine. Int J Refrig 2012;35:1639-1646.
11. Tugcu A, Arslan O. Optimization of geother- [CrossRef] mal energy aided absorption refrigeration sys- [34] Fernández-Seara J, Sieres J, Vázquez M. Compression- tem-GAARS: A novel ANN-based approach. absorption cascade refrigeration system. Appl Therm Geothermics 2017;65:210-221. [CrossRef] Engineer 2005;26:502-512. [CrossRef]
12. Seyfouri Z, Ameri M. Analysis of integrated com- pression-absorption refrigeration systems powered Thermo-economic and environmental analyses by a microturbine. Int J Refrig 2012;35:1639-1646. based multi-objective optimization of vapor com- [CrossRef] pression-absorption cascaded refrigeration system
13. Bruno JC, Ortega-López V, Coronas A. Integration using NSGA-II technique. Energy Conver Manage of absorption cooling systems into micro gas turbine 2016;113:230-242. [CrossRef] trigeneration systems using biogas: case study of a [36] Cimsit C, Ozturk IT, Kincay O. Thermoeconomic sewage treatment plant. Appl Energy 2009;86:837- optimization of LiBr/H2O-R134a compression-ab-
14. Sira S, Somchai W. A critical review of recent Engineer 2015;76:105-115. [CrossRef] investigations on two-phase pressure drop in flow [37] Ehab SA, Ahmed AA, Harby K, Mohamed RD, boiling micro-channels. Front Heat Mass Transf Bahgat RM, Ahmed A. Experimental adsorption 2012;3:013007. [CrossRef] water desalination system utilizing activated clay for
15. Awad M, Dalkılıç AS, Wongwises S. A critical review low grade heat source applications. J Energy Storage on condensation heat transfer in microchannels 2021;43:103219. [CrossRef] and minichannels. J Nanotechnol Engineer Med [38] Verde M, Harby K, Robert B, Corberán JM. 2014;5:010801-1. [CrossRef] Performance evaluation of a waste-heat driven
16. Alican Ç, Ali C, Aydın H, Yakup K, Pınar C, Mehmet adsorption system for automotive air-condition- SC, et al. A review of flow boiling in mini and micro- ing: Part I- Modeling and experimental validation. channel for enhanced geometries. J Therm Engineer Energy 2016;116:526-538. [CrossRef] 2018;4:2037-2074. [CrossRef] [39] Verde M, Harby K, Robert B, Corberán JM.
17. Boer D, Valles M, Coronas A. Performance of Performance evaluation of a waste-heat driven double effect absorption compression cycles for adsorption system for automotive air-conditioning: air-conditioning using methanol-TEGDME and Part II- performance optimization under different TFE-TEGDME systems as working pairs. Int J real driving conditions. Energy 2016;115:996-1009. Refrig 1998;21:542-555. [CrossRef] [CrossRef] J Ther Eng, Vol. 10, No. 3, pp. 722−736, May, 2024 735
18. Maggio G, Freni A, Restuccia G. A dynamic model of heat and mass transfer in a double-bed adsorp- formance of a compression-driven adsorption tion machine with internal heat recovery. Int J Refrig cooling cycle. Appl Therm Engineer 1999;19:1-0. 2006;29:589-600. [CrossRef] [CrossRef]
19. Restuccia G, Freni A, Maggio G. A zeolite-coated bed for air conditioning adsorption systems: para- pression-adsorption combined for cooling and metric study of heat and mass transfer by dynamic desalination. Energy Conver Manage 2017;143:538- simulation. Appl Therm Engineer 2002;22:619-630. 552. [CrossRef] [CrossRef] [56] Meunier F. Second law analysis of a solid adsorption
20. Mohamed G, Askalany A, Harby K, Ahmed MS. heat pump operating on reversible cascade cycles: Adsorption isotherms and kinetics of HFC-404A Application to the zeolite-water pair. Heat Recov Sys onto bituminous based granular activated carbon 1985;5:133-141. [CrossRef] for storage and cooling applications. Appl Therm [57] Akahira A, Alam KCA, Hamamoto Y, Akisawa A, Engineer 2016;105:639-645. [CrossRef] Kashiwagi T. Mass recovery four-bed adsorption
21. Ahmed S, Ahmed A, Harby K, Mahmoud S. refrigeration cycle with energy cascading. Appl Performance evaluation of a solar driven adsorption Therm Engineer 2005;25:1764-1768. [CrossRef] desalination cooling system. Energy 2017;128:196- [58] Deshdeep G, Ahmad FS, Akhilesh A, Ashwni.
22. Zhang LZ, Wang L. Performance estimation of an double-effect vapour absorption refrigeration sys- adsorption cooling system for automobile waste tem. J Therm Engineer 2022;8:78-89. [CrossRef] heat recovery. Appl Therm Engineer 1997;17:1127- [59] Touaibi R, Hasan K, Boudjema F, Selmane S, Hemis 1139. [CrossRef] M. Energy and exergy analysis of a combined sys-
23. Alam K, Saha B, Kang Y, Akisawa A, Kashiwagi T. tem: Cascade organic Rankine cycle and cascade Heat design effect on the performance of silica gel refrigeration cycle. J Therm Engineer 2021;7:1139- adsorption refrigeration systems. Int J Heat Mass 1149. [CrossRef] Transf 2000;43:4419-4431. [CrossRef] [60] Saha BB, El-Sharkawy II, Chakraborty A, Koyama S.
24. Tamainot-Telto Z, Metcalf SJ, Critoph RE. Novel Study on an activated carbon fiber-ethanol adsorp- compact sorption generators for car air condition- tion chiller: Part I - system description and model- ing. Int J Refrig 2009;32:727-733. [CrossRef] ling. Int J Refrigeration 2007;30:86-95. [CrossRef]
25. Liu Y, Leong KC. Numerical study of a novel cascad- ing adsorption cycle. Int J Refrig 2006;29:250-259. Study on an activated carbon fiber-ethanol adsorp- [CrossRef] tion chiller: Part II - performance evaluation. Int J
26. Meunier F. Theoretical performances of solid adsor- Refrigeration 2007;30:96-102. [CrossRef] bent cascading cycles using the zeolite-water and [62] Chua HT, Ng KC, Malek A, Kashiwagi T, Akisawa active carbon-methanol pairs: four case studies. BB, Saha. Modeling the performance of two-bed, sil- Heat Recov Sys 1986;6:491-498. [CrossRef] ica gel-water adsorption chillers. Int J Refrigeration
27. Khairul H, Bidyut BS, Anutosh C, Shigeru K, 1999;22:194-204. [CrossRef] Kandadai S. Performance evaluation of combined [63] Balghouthi M, Chahbani MH, Guizani A. Feasibility adsorption refrigeration cycles. Int J Refrigeration of solar absorption air conditioning in Tunisia. Build 2011;34:129-137. [CrossRef] Environ 2008;43:1459-1470. [CrossRef]
28. Saha BB, El-Sharkawy II, Chakraborty A, Koyama S. Study on an activated carbon fiber-ethanol adsorp- ditions optimization of a proposed solar-powered tion chiller: Part I - system description and model- adsorption cooling system: Experimental, model- ling. Int J Refrigeration 2007;30:86-95. [CrossRef] ing, and optimization algorithm techniques. Energy
29. Banker ND, Dutta P, Prasad M, Srinivasan K. 2020;206:118007. [CrossRef] Performance studies on mechanical-adsorption com- [65] Herold KE, Radermacher R, Klein SA. Absorption bined compression refrigeration cycles with HFC Chillers and Heat Pumps. Florida: CRC Press; 2016. 134a. Int J Refrigeration 2008;31:1398-1406. [CrossRef] [CrossRef]
30. Skander J, Shigeru K, Bidyut BS. Performance Investigation of a novel CO2 compression-adsorp- of operating conditions on performance of absorp- tion based combined cooling cycle. Eng Sci Rep tion refrigeration system. Energy Conver Manage Kyushu Univ 2010;32:12-18. 2007;48:599-607. [CrossRef]
31. Salvatore V, Valeria P, Davide LR, Walter M. Adsorption-compression cascade cycles: An experi- procedure and performance evaluation for a water- mental study. Energy Conver Manage 2018;156:365- LiBr absorption refrigeration machine. Energy
32. [CrossRef] 2014;65:272-284. [CrossRef] 736 J Ther Eng, Vol. 10, No. 3, pp. 722−736, May, 2024
33. Gonzales-Gil A, Izquierdo M, Marcos JD, Palacios absorption chiller for low-grade driving heat. Int E. Experimental evaluation of a direct air-cooled Sorption Heat Pump Conf., Denver, USA; 2005. lithium bromide-water absorption prototype [71] Rasoul Nikbakhti, Xiaolin Wang, Andrew Chan. for solar air conditioning. Appl Therm Engineer Performance analysis of an integrated adsorp- 2011;31:3358-3368. [CrossRef] tion and absorption refrigeration system. Int J
34. Chen JF, Dai YJ, Wang RZ. Experimental and ana- Refrigeration 2020;117:269-283. [CrossRef] lytical study on an air-cooled single effect LiBr-H2O absorption chiller driven by evacuated glass tube [72] Dakkama HJ, Elsayed A, AL-Dadah RK, Mahmoud solar collector for cooling application in residential SM, Youssef P. Integrated evaporator-condenser buildings. Sol Energy 2017;151:110-118. [CrossRef] cascaded adsorption system for low temperature
35. Kuhn A, Petersen S, Ziegler F, Kohlenbach P, Harm cooling using different working pairs. Appl Energy M, Schweigler C. Operational results of a 10 kW 2017;185:2117-2126. [CrossRef]

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