Project Title Evaluation of the use of Solar Flat Plate

Collectors for Solar Thermal Refrigeration

Student Name-Dinesh Khanna

Reg. No.-4NM15MES03

M.Tech in Energy Systems Engineering. NMAMIT, Nitte.

Project guide: Mr. AneeshJose(Asst. Professor) NMAMIT, Nitte.

Contents• INTRODUCTION• PROJECT OBJECTIVE• LITERATURE SURVEY• COP CALCULATIONS FOR THE STVARS• DESIGN OF STVARS• FABRICATION OF STVARS• OPTIMIZATION OF DESIGN• RESULT AND DISCUSSION• CONCLUSIONS• REFERENCES

1.Introduction1.1 Refrigeration

• Refrigeration is the thermodynamic process toproduce cooling effect below the atmospherictemperature.

• Refrigeration may be defined as the process ofachieving and maintaining a temperaturebelow that of the surroundings, the aim beingto cool some product or space to the requiredtemperature.

• Refrigeration has many applications, includinghousehold refrigerators, industrial freezersand air conditioning .

• The performance of refrigeration system isevaluated in terms in Coefficient ofPerformance (COP) .

1.2 Types of Vapour Refrigeration Cycle

1. Compression Refrigeration Cycle.

• The most popular and widely used system inrefrigeration and air conditioning both forindustrial and domestic applications.

Fig.1 VCR

1.3 Problems with VCRS• The major share of electricity that is being

supplied with a refrigerator is consumed by thecompressor.

• Since a refrigerator is operated 24 hours a day,there is considerable energy consumption.

• The refrigerants used in these refrigerators areenvironmentally hazardous.

• The Freon gases that are popularly used incompression refrigerators are ozone depletingand add on to global warming.

• The performance of vapour compressing systemis very poor at partial load.

2. Absorption Refrigeration Cycle.

• The vapour absorption system replaces thecompressor with a generator absorber set.

• The first NH3-H2O absorption refrigerationsystem was developed by Ferdinand Carre in1860.

• Combination of refrigerant and absorbent.

• Most widely use NH3-H2O & LiBr-H2O.

• In addition, the VARS use natural substanceswhich do not cause ozone depletion asworking fluids

Fig.2 VARS

1.4 Solar Energy for Cooling• Solar energy is the most readily available source

among renewable energy sources.

• With the use of solar energy, usage ofconventional energy sources and its peakdemand will be reduced.

• Utilization of solar energy for cooling was anattractive one, as the demand for cooling is somewhat in tune with the availability of heat.

• The VARS being a heat operated system, isespecially suited for refrigeration using solarenergy.

1.4.1 PV Operated Refrigeration Cycle

• PV involve the direct conversion of solarradiation to direct current (DC) electricityusing semiconducting materials.

• DC electrical power that can be either used tooperate a dc motor, which is coupled to thecompressor

• Inverter can be used to convert this DCcurrent to AC current for running thecompressor of a vapour compressionrefrigeration system.

Fig.3 PV operated Refrigeration

1.4.2 Solar Thermal Refrigeration• Solar thermal systems use solar heat rather than

solar electricity to produce refrigeration effect.• The thermal component of solar energy is taken

up the working fluids in solar collector.• The heat energy will be supplied to generator

unit that has a strong solution of refrigerant-absorbent mixture, wherein the concentration ofrefrigerant is high.

• This heat energy heats up the mixture and themixture should be chosen in such that, therefrigerant has a lower boiling point than theabsorbent, so the refrigerant boils and getsconverted to vapour phase.

Fig.4 Solar thermal NH3-H2O VARS

2.Project Objective• The main objective of this project work is to

design and fabricate a solar thermal vapourabsorption system using ammonia as refrigerantand water as absorbent.

• A solar flat plate collector will be used, that iscapable of providing the thermal energy requiredto operate vapour absorption refrigeration unit.

• A detailed analysis on solar radiation, collectorarea has to be done. After which the vapourabsorption system is to be designed andfabricated.

• This new solar thermal refrigeration systemshould prove better than PV refrigeration system.

3.Literature Survey3.1 VCRSl.No Author Title Year

1 Eng. Naser R. M. AL-Ajmi

Coefficient of Performance Enhancement of Refrigeration Cycles

2015

2 M. Krishna Prasanna& P. S. Kishore

Enhancement of COP in Vapour Compression Refrigeration System

2014

3 Shoyab hussan Improve the cop of Vapour compression cycle with change in Evaporator and

Condenser pressure

2015

4 F. Memet A Performance Analysis on a Vapour Compression Refrigeration System Generated

by the Replacement of R134a

2014

5 Dr. A.C. Tiwari and Shyam kumar

Barode

Performance Analysis of Vapour Compression Refrigeration Systems Using

Hydrofluorocarbon Refrigerants

2012

3.2 PV operated refrigerationSl.No Author Title Year

1 Navneet Kumar Sharma, Hari Singh

,Madan Kumar Sharma and B. L.

Gupta

Performance Analysis of Vapour Compression and

Vapour Absorption Refrigeration Units Working on

Photovoltaic Power Supply

2016

2 S. R. Kalbande and Sneha Deshmukh

Photovoltaic Based Vapour Compression Refrigeration System for Vaccine Preservation

2015

3 Armand Noël Ngueche Chedop,

Noël Djongyang and Zaatri Abdelouahab

Modelling of the Performance of a Solar Electric-Vapour Compression Refrigeration

System in Dry Tropical Regions

2012

4 Kapil K. Samar, S. Kothari and S. Jindal

Thermodynamic and economic analysis of solar photovoltaic

operated vapour compressor refrigeration system

2014

5 Mehmet AzmiAktacir

Experimental study of a multi-purpose PV-refrigerator

system

2011

3.3 Solar Thermal VARSSl.No. Author Title Year

1 D.S. Kima and C.A. Infante Ferreirab

Solar refrigeration options – a state-of-the-art review

2008

2 Preethu Johnson and K. B. Javare Gowda

Fabrication of Solar of Thermal Vapour Asorption Refrigeration

System

2015

3 Subi Salim and Rajesh V Thermodynamic Analysis of Aqua-Ammonia Based Miniaturized Vapor

Asorption Refrigeration System Utilizing Solar Thermal Energy

2016

4 Narale Pravin et al. Vapour Absorption Refrigeration System by using Solar Energy

2016

5 Anadi Mondal et al. Design & Construction of a Solar Driven Ammonia Absorption

Refrigeration System

2015

Sl.No Author Title Year

6 Dr. Adel et al. The use of Direct Solar Energy in Absorption Refrigeration Employing NH3-

H2O System

2010

7 Jasim Abdulateef et al.

Experimental Investigation on Solar Absorption Refrigeration System

in Malaysia

2009

8 Rahul Yadav and Mohini Sharma

Analytical Study of Ammonia –Water (NH3-H2O) Vapor Absorption

Refrigeration System Based On Solar Energy

2016

9 K.V.N. Srinivasa Rao Low Cost Solar Cooling System 2013

10 Moreno-Quintanaret al.

Development of a solar intermittent refrigeration system for ice production

2011

11 Abhishek Sinha and S.R Karale

A review on Solar Powered Refrigeration and the Various Cooling Thermal Energy

Storage (CTES) Systems

2013

Literature surveySl.No Author Title Year

12 V.K.Bajpai Design of Solar Powered Vapour Absorption System

2012

13 Sameh Alsaqoor& S. AlQdah

Performance of a Refrigeration AbsorptionCycle Driven by Different Power Sources

2014

14 O. Babayigit et al.

Investigation of Absorption Cooling Application Powered by Solar Energy in the South Coast

Region of Turkey

2013

15 Dillip Kumar and Abhijit Padhiary

Thermodynamic Performance Analysis of a Solar Vapour Absorption Refrigeration System

2015

16 K Karthik Design, Fabrication and Analysis of Solar Vapour Absorption Refrigeration System

2014

17 N.D. Hingaweand R.M.

Warkhedkar

Design and Analysis of Solar Electrolux Vapour Absorption Refrigeration System

2015

18 K.R. Ullah et al. A review of solar thermal refrigeration and cooling methods

2013

Observation from Literature Review• Replacing the electrical energy with solar

energy will reduce the consumption of highgrade electrical energy.

• Also the replacement of compression systemwith absorption system eliminates the energyconsumption by compressors.

• The overall system energy efficiency of PVoperated refrigerator was found low becauseof energy conversion efficiency and exergyefficiency of the photovoltaic system was low.

• Thermal cooling technology is preferred to PV-based cooling systems because it can utilizemore incident sunlight than a PV system.

• Evacuated collectors have less heat loss andperform better at high temperatures.

• Solar thermal Vapour absorption refrigerationtechnology has great potential to offereconomical and innovative solutions tovarious refrigeration requirements.

• Using ammonia as refrigerant in VARS hasmany advantages.

• Aqua-ammonia VAR system integrated with solarcollector that can be used small and large scalecooling applications.

• The COP depends primarily on the temperaturesof the evaporator and the condenser. Alsodepends on Refrigerant and the model ofgenerator used in VARS.

• The detailed study of these papers gave a goodidea about solar thermal vapour absorptionsystem.

• It was observed that the accumulation ofammonia, solar collector efficiency, clearness ofsky played great factor for overall efficiency.

4. COP Calculations for the STVARS• The Coefficient of performance (COP) of the

system as theoretically known is given by• COP= Heat Absorbed in the Evaporator / (Work

done by pump +Heat Supplied in the evacuatedtube )or COP =Qe/(Qg+Wp).

• Negelecting pump work,Theoretical COP = Qe/Qg

• Assumed values as follows.High pressure = 7 barGenerator temperature (max) = 110°CEvaporator temperature (max) = -5°CQe= 1TR = 3.516 KW (Theoretical valve)

• Let m = mass flow rate of refrigerant, kg/s

• Q=Heat

• Heat absorbed at generator Qg= m (h3-h2)

• COP=3.516/m (h3-h2)

• Mass Concentrations: X1 = X2 = 0.55

X3=X5= X6 = X7= X8 = 1

X4 = 0.42

Figure 5 Circuit of STVARS

• At Pump (Aqua ammonia liquid state), Pressure = 7 bar, X2= 0.55Temperature = 40°C, h2= 130 kj/kg

• At Evacuated tube (Ammonia vapour state), X3=1 and temperature=110°CPressure =7 bar, h3= 1716.4 kj/kg

• At Evaporator, taking concentration X7=1 and temperature = -5°C,Pressure =3 bar

Applying the Energy balance• Qe = Refrigerating effect =3.516kW = m (h8 – h7)• = m× (1461.56-176.9)• m=3.788/ (1461.56-176.9) = 2.94×10^-3 kg/s• m =2.94×10^-3 kg/s = mass flow rate of refrigerant.• Now circulation ratio, λ= X4/(X1-X4) = 3.23• Strong solution, m1=m2= λ× m= 9.49×10^-3 kg/s• Weak solution, m4=(1+ λ)m= 12.43×10^-3 kg/s• So, Qg= m(h3-h2)= 2.94×10^-3 (1716.4-130) =4.66 kj/sec = 4.66 KW• Theoretical COP=3.516/4.66 = 0.75

Statement: For such a design circuit the refrigeration system produce acooling capacity of COP 0.75 which a good value for applications such asair conditioning where the temperature is not much of concern.

5. Design of STVARS The design of solar thermal refrigeration designed consideringvarious criteria and assumptions. The design is done to get therefrigeration capacity of 1 ton with required COP. The calculatedCOP of the system is 0.75.Design depends on the individualcomponents used in the system. Following are the individualcomponents used in STVARS are as follows.• Absorber tank• Pump• PV panel• Generator tank• Evacuated Tubes• Rectifier tank• Condenser• Capillary tube• Evaporator tank

Fig.6 STVARS 3D model

5.1 Absorber Tank• Absorber tank is designed according the volume of

evacuated tube collectors (6ltrs) and specification of the pump (5ltrs/min).

Specifications:• Type: cylindrical tank • Material used: Mild Steel• Refrigerant= R717 (Ammonia)• Absorber = Water• Inner diameter of the tank = 260mm• Outer diameter of the tank = 263mm• Length of the tank = 370mm• Total volume of the tank = V = π r^2 h=

π×(0.153m)^2×0.4m= 0.02m^3= 20.10 litres• Volume of ammonia water solution used= V = π r^2 h =

π×(0.13m)^2×0.3m= 16 litres

Fig.7 Designed Absorber tank

WEAK SOLUTION IN

VAPOUR IN

TO PUMP

5.2 Pump

• Pump is used to pump the ammonia hydroxide from the absorber to the generator tank attached to the evacuated tube. It is used according to the maximum pressure rate required and also maintain adequate discharge flow rate at the refrigerant.

• Specifications:

• Type: Auto Diaphragm DC pump

• 0.08 Hp = 60 W

• Pump flow rate = 5 ltrs/min

• Rated pressure = max 8bar

• Dimensions: 165×95×60mm

5.3 Generator Tank

Generator tank is designed to maintain steady

state level for continuous discharge and act as

accumulator above the evacuated tube. Figure 8

shows design of a generator tank .

• Specifications:

• Type: Cylindrical tank

• Inner Diameter= 100mm

• Thickness = 2mm

• Length = 300mm

• Volume=πr^2h=π×(50)^2×300= 2.3litres

• All dimensions in cm

Fig.8 Generator tank

OUTLET

INLET

5.4 Evacuated Tubes

• To get higher temperature to vaporize ammoniarefrigerant, Evacuated tube collectors are usedinstead of solar flat collectors. Figure 9 shows thedesign of evacuated tube collectors.

Specifications:

• No. of Tubes = 2

• Length of the Tube = 1500mm

• Outer diameter of the tube = 58mm

• Inner diameter of the Tube = 48mm

• Volume of one tube = V = π r^2 h=π×(23.5)^2×1500= 2.6 litres

All dimensions in cm

Fig.9 Design of Evacuated tube collectors

5.5 Rectifier Tank• Rectifier tank is designed according to the volume of

absorber, evacuated tube collectors and coolingrequired converting water vapour to liquid state. Figure10 shows a design of rectifier tank.

Specifications:• Type: Water cooled tank• Material used = Mild steel• Inner diameter of tank one = 200mm• Outer diameter of the tank= 203mm• Length of the tank = 200mm• Thickness of inner tank = 3mm• Capacity of the tank = V = π r^2 h = π

×(0.115m)^2×0.3m= 6.28 litres• Copper coil length= 3m• Copper tube diameter= 9mm

Fig.10 Design of Rectifier tankWEAK SOLUTION OUT

VAPOUR OUT

5.6 Condenser• Condenser is selected to withstand the

temperature and pressure and that amount ofheat to be removed from ammonia vapour andconvert it into liquid state.

Specification:• Type: Wire and tube coil• Material: Mild steel• No. of turns = 26• Outer diameter of condenser pipe= 6mm• Thickness = 1mm• Area of the condenser = 0.95m × 0.4 m = 0.38

m^2

5.7 Capillary tube• Capillary tube has very small internal diameter

and it is of very long in length. It is coiled toseveral turns, so that it would occupy less space.This device connects between condenser andevaporator to reduce the pressure. Therefrigerant comes out of capillary tube toevaporator this change in diameter drops therefrigerant pressure there by reducing itstemperature.

Specifications• Material: Copper• Inner diameter = 0.3mm• Thickness = 0.1mm• Capillary tube length = 3m

5.8 Evaporator• In evaporator low temperature, low pressure

refrigerant extract the heat from the cabin or systemwhich we have to cool. Evaporator should be designedto get capacity of 1 ton as the heat input is of 4.65 KW(from COP calculations).

• Specifications:• Material : Mild steel• Cylinder inner diameter = 200mm• Cylinder length = 300mm• Cylinder thickness= 3mm• Volume of the thank V = π r^2 h = π×(100)^2×2= 9.42

litres• Coil material= Copper• Coil length = 3m• Coil outer diameter = 6mm

6. Fabrication of STVARS The solar vapour absorption refrigeration system isfabricated with reference to the designed detailsusing available parts and materials in market, whichis cost effective. The following are steps involved inFabrication.• 1. Selecting the type of materials and parts to be

used.• 2. Fabricating the cylinders and modifying the

parts.• 3. Assembling the system as per design and

installing the instruments.• 4. Sealing done at required spots in the system.• 5. Testing and modifying the assembly.

• The fabrication process is done in Gajananamachine works, Bunder Mangaluru

Fig.11 Fabricated STVARS

6.1 Fabricated Absorber Tank

• Absorber tank is fabricated with reference tothe designed details of capacity 20 litres. Thematerial used to fabricate is galvanized mildsteel and the thickness is 3mm.

Operations performed:

• Arc Welding

• Drilling

• Brazing

• Sealing

Fig.12 Absorber tank

6.2 Diaphragm Pump

• Pump is fixed between absorber tank andgenerator tank using union coupling parts of ¾inch stainless steel, both in inlet and outlet ofpump.

• 60W DC pump

Operation performed:

• Threading on

coupling parts

Fig.13 60W pump

6.3 Generator Tank with Evacuated Tubes

• Tank is fabricated with reference to designed modelof generator tank that can attached to evacuatedtubes with the help of bush, so there will be noleakage .

Operation Performed:

• Drilling

• Welding

• Sealing

Fig.14 Generator tank with Evacuated tubes

6.4 Fabricated Rectifier Tank

• Rectifier tank is made up of mild steel of capacity6.28 litres is fabricated according to the designdetails.

Operations performed:

• Welding

• Drilling

• Soldering

• Brazing

• Sealing

Fig.15 Rectifier tank

6.5 Wire and Tube Condenser• The condenser is selected depending upon the area of the

condenser that able to give required condensation to the system.

• A wire and tube type condenser used to household refrigerator ofsystem 1TR is purchased in micro refrigeration bunder,Mangalore.

• Wire and tube condenser

is a type of natural convection

condenser used in small capacity

refrigeration systems.

Fig.16 Wire and tube condenser

6.6 Copper Capillary Tube

• A capillary tube is selected by its length anddiameter for capacity one ton refrigerationand fabricated in Christal refrigeration,Surathkal Mangalore.

Operations performed:

• Brazing

• Soldering

Fig. 17 Capillary tube

6.7 Evaporator tank

• Evaporator tank is fabricated according to thedesign details of capacity 9.42 litres, material usedis mild steel.

• It is insulated by asbestos webbing tape.

• A 6mm diameter of 2m

copper coil is used.

Operation Performed :

• Welding

• Brazing

• Drilling

• Sealing Fig.18 Evaporator tank

6.8 Instrumentations

• Two pressures gauges of 150psi are installed, onepressure gauge is threaded in 20mm diameterstainless steel pipe after the pump and other onebetween evaporator and absorber tank.

• Three digital thermometers

rated from -50°C to +300°C

is installed in the system,

one in absorber tank and

other two in rectifier tank

and evaporator tank .

Fig.19 Pressure gauge

6.9 Modification

• Modification is done after testing of fabricatedsystem.

Fig.20 Modified System

6.10 Ammonium Hydroxide as Working fluid

• Ammonium hydroxide (NH3+H2O) solution (13 litres) isfilled in absorber tank where ammonia is the refrigerantand water acts as absorber.

• Ammonia Solubility in H2O = 47% at 0°C , 31% at 25°Cand 18% at 50 °C

Fig.21 Ammonium hydroxide

7.Optimization of Design• The fabricated system was found to be not

holding the system pressure in evacuated tubecollectors.

The following are the areas where newmodification is put in the place due to the abovereasons.

• Design of solar collector area.

• Connective areas of generator tank.

• Identification of valves

• Proper insulation in the system.

• Better instrumentations in the system.

7.1 Stainless tube Collectors• Maximum temperature of 65 to 70°C can obtain by using

stainless tube collector.• Specification:• Rectangular box dimensions = L×W×H=

347.09mm×291.24mm×150mm• Absorber plate area (copper)= 342mm×286mm = 0.097m^2• Tube material used = Stainless steel• Number of tubes = 2• Length of the tube = 150mm• Outer diameter of the tube= 64mm• Thickness = 2mm• Volume of generator tank = 2.97 litres• Volume of the two tubes = 0.96 litres• Quantity of ammonium hydroxide used in absorber tank = 6

litres

• All dimensions in mm

Fig.22 Designed stainless tube collector

7.2 Insulation

• Insulation is done to rectifier tank and thestainless steel pipe connections to maintain therequired temperature in the system.

• Asbestos tapes can be used for insulation thecomponents.

7.3 Finned tube Condenser• Finned tube condenser is a type of natural convection heat

exchanger (condenser), it is suggested to a solar vapour absorptionrefrigeration system.

• Calculations:

• The optimum heat and mass transfer area can be calculated using A= Q/(F×h×ΔT)

• t1= 70°C, t2= 45°C, T1= 30°C and T2 = 35°C

• P = 0.62 and R= 0.2, from graph F= 0.97

Fig.23 Correction factor F chart

• Assuming heat transfer co-efficient, h =10W/(m^2×K) • The heat flow rate is the mass flow rate times the latent heat of

condensation of the ammonia = Q = m×Δh• Mass flow rate of refrigerant = 2.94×10^-3 kg/s• If ammonia vapour entering condenser at maximum

temperature of 70°C then• Δh = (1484-545) = 939 kj/kg• The log mean temperature difference ΔT = (Tc-Tai)×(Tc-Tao) /

log((Tc-Tai)/(Tc-Tao))• Tc is Condenser temperature = 45°C = 318 K• Tai is air inlet temperature = 30°C = 303 K• Tao is air outlet temperature = 35°C = 308 K• ΔT = (318-303)× (318-308)/log((318-303)/(315-308) = 851.83 K • A = (2.94×10^-3 × 939)/ (0.97×10×851.83) = 330.93

(kj/sec×m^2/w)= 0.34 m^2

7.4 Optimized Instrumentations

• For calculating COP of the system, temperature andpressure of refrigerant flow is required to be noted ateach point.

• High pressure P1=P2=P3=P5

• Low pressure= P6=P7

• T1=Absorber temperature

• T2=Generator temperature

• T3=Rectifier temperature

• T4=Condenser temperature

• T5= Evaporator temperature

Fig.24 Circuit diagram of STVARS for instrumentations

8.Result and Discussion• Literature review is done on different type refrigeration system mostly based on solar

thermal refrigeration.• Solar thermal refrigeration is designed and fabricated with reference to the COP

calculation.• System fabrication components had drilling, welding, brazing and other operations.• Fabrication model is tested, and find out that there is leakage in pump outlet coupling

part due to pressure as the pump in working condition.• Modification is done by removing pump from the system and changing the position of

absorber and generator setup, also replacing the stainless steel pipes to flexible pipe.• Ammonia solution is filled successfully as per the procedure of handling ammonium

hydroxide.• As the absorber tank valve is opened the solution entering evacuated tubes by

generator is failed to hold up the pressure developed by ammonia vapour and therewas gas leakage in bush to that connects generator tank and evacuated tubes.

• Design has optimized on the system by replacing evacuated tube collector by stainlesssteel flat plate collectors and some minor modifications in piping and insulations.

• Optimized design is better to the system’s new design which can deal with pressureand leakage problems and quantity of ammonia ammonium hydroxide is used is 6litres.

• Instrumentations like new pressure gauges and ball valve has been introduced to beused in the system as per the requirements.

9. Conclusion• The new solar thermal refrigeration has been introduced with

ammonia as working fluid Evacuated tubes mainly to replace thehigh grade electricity.

• Reviews of different area of solar thermal refrigeration system havebeen carried out, designed components used in solar thermalrefrigeration system are shown in detailed with its pictures.

• To find the performance parameter of refrigeration systeminstrumentation studies has been carried out and different types ofgauges and exact locations have been represented.

• The designed refrigeration system is fabricated, tested and modifiedas per the requirement.

• The fabricated system when tested it was found incapable ofholding the system pressure and the evacuated tubes could notkeep itself in place. The evacuated tubes lost its vacuum pressurenot suitable for ammonia solution for present design.

• Considering the factor a new design has been introduced afteroptimization which takes care of problems encountered in theearlier design.

10.References• [01] Prof. Dr. Adel A. Al-Hemiri and Ahmed Deaa Nasiaf, ‘‘The use of direct Solar energy

in Absorption Refrigeration employing NH3 – H2O system’’, Iraqi Journal of Chemical and Petroleum Engineering, Vol.11 No.4 (December 2010) 13-21.

• [02] Preethu Johnson and K. B. Javare Gowda, ‘‘Fabrication of Solar Thermal Vapour Absorption Refrigeration System’’, International Research Journal of Engineering and Technology, Volume: 02 Issue: 05 | Aug-2015.

• [03] Shireesha Mary Ch, Nandini Ch, Divya Samala, Siva Kumar B and ParthasarathyGarre, ‘‘A Review: Increase in Performance of Vapour Compression Refrigeration System Using Fan’’, International Journal of Engineering and Applied Sciences (IJEAS) ISSN: 2394-3661, Volume-2, Issue-4, April 2015.

• [04] F. Memet, ‘‘A Performance Analysis on a Vapour Compression Refrigeration System Generated by the Replacement of R134a’’, Journal of maritime research, Vol XI. No. III (2014) pp 83–87.

• [05] Shubham Srivastava, Ravi Kumar Sen, Arpit Thakur and Manish Kumar Tated, ‘‘Review paper on analysis of Vapour Absorption Refrigeration System’’, International Journal of Research in Engineering and Technology, Volume: 04 Issue: 06 June 2015.

• [06] Sachin Kaushik and Dr. S. Singh, ‘‘Thermodynamic Analysis of Vapour Absorption Refrigeration System and Calculation of COP’’, International journal for research in applied science and engineering technology’’, Vol. 2 Issue II, February 2014.

• [07] Jose  FernaÂndez-Seara and Manuel VaÂzquez, ‘‘Study and control of the optimal generation temperature in NH3-H2O absorption refrigeration systems’’, Applied Thermal Engineering 21 343±357 @ Elsevier Science Ltd., March 2000.

References• [8] Subi Salim and Rajesh V. R., ‘‘Thermodynamic analysis of Aqua-Ammonia based miniaturized vapour

Absorption Refrigeration system utilizing solar thermal energy’’, ARPN Journal of Engineering and Applied Sciences, VOL. 11, NO. 9, MAY 2016.

• [09] K.V.N. Srinivasa Rao, ‘‘Low Cost Solar Cooling System’’, International Journal of Engineering and Innovative Technology (IJEIT) Volume 3, Issue 4, October 2013.

• [10] N.D. Hingawe and R.M. Warkhedkar, ‘‘Design and Analysis of Solar Electrolux Vapour Absorption Refrigeration System, International Journal of Advance Research in Science and Engineering’’, IJARSE, Vol. No.4, Issue 04, April 2015.

• [11] O. Babayigit,a, M. H. Aksoy, M. Ozgoren and O. Solmaz, ‘‘Investigation of Absorption Cooling Application Powered by Solar Energy in the South Coast Region of Turkey’’, EPJ Web of Conferences DOI: 10.1051/ C _ Owned by the authors, published by EDP Sciences,2013.

• [12] Satish Raghuvanshi and Govind Maheshwari, ‘‘Analysis of Ammonia –Water (NH3-H2O) Vapour Absorption Refrigeration System based on First Law of Thermodynamics’’, International Journal of Scientific & Engineering Research Volume 2, Issue 8, August-2011.

• [13] Sanford A. Klein, Ph.D., Fellow ASHRAE, and Douglas T. Reindl, Ph.D., ‘‘ Solar Refrigeration’’, © 2005, American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc. ASHRAE Journal, (Vol. 47, No. 9, September 2005).

• [14] K.R. Ullah , R.Saidur , H.W.Ping , R.K.Akikur and N.H.Shuvo, ‘‘A review of solar thermal refrigeration and cooling methods’’, Renewable and Sustainable Energy Reviews 24 (2013) 499–513 @ Elsevier journals, March 2013.

• [15] Amar Rouag, Adel Benchabane and Adnane Labed “Thermal design of air cooled condenser of a solar adsorption refrigerator” Laboratoire de Génie Energétique et Matériaux (LGEM), Université de Biskra, B.P. 145 R.P. 07000, Biskra, Algeria

THANK YOU