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SOLAR ENERGY

PHOTOVOLTAIC ORGANIC RANKINE SOLAR THERMAL

CYCLE

VAPOUR COMPRESSION

REFRIGERATION

VAPOUR ABSORPTION VAPOUR JET

REFRIGERATION REFRIGERATION

VAPOUR COMPRESSION THERMOELECTRIC

REFRIGERATION REFRIGERATION

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SOLAR VAPOUR COMPRESSIONREFRIGERATION SYSTEM


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SOLAR VAPOUR COMPRESSION REFRIGERATION SYSTEM12/27/2013 Solar Refrigeration : Current Statusand Future Trends

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12/27/2013

Fig. 3 Comparison of mass flow rate for R12 and R134a

Solar Refrigeration : Current Statusand Future Trends

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12/27/2013

Fig. 4 Comparison of compressor capacity for R12 and R134a


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12/27/2013

Fig. 5 Comparison of power requirement for R12 and R134a


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12/27/2013

Fig. 6 Comparison of COP for R12 and R134a


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Intermittent solar Refrigeration System


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12/27/2013

Fig. 7 Basic Intermittent Absorption Refrigeration System


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A solar refrigerator capable producing of 250kg of ice

per day reported by Kirpichev and Baum (1954) which isoperated by a vapour compression principle. Steam is

used as working fluid which produced by a cylindrical

parabolic concentrators.

A intermittent solar refrigerator of production capacity 6

kg per ice per day built by Trombe and Foex (1957),

working on vapour absorption principle and ammonia-

water combination used as working fluid. Willam et al (1957) tried different refrigerant-absorbent

combination like methonol-silicagel, accetone-silicagel,

ammonia-water etc, for a small food cooler working on

intermittent cycle.12/27/2013 Solar Refrigeration : Current Statusand Future Trends 12


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Muradov and Shadie (1971)investigated an intermittent

absorption solar refrigerator with ammonia-calciumchloride. A sub-zero evaporator temperature reported

which obtained within 1-2 hours from starting of

refrigeration process.

A solar refrigerator of 5 ton capacity working on

absorption principle with NH3-H2O working fluid

reported, Farber (1973).

Swartman et al (1973) have reported experimental resultson an intermittent solar refrigerator which built based on

two vessel system, one for generator cum absorber and

other condenser and evaporator. NH3-H2O and NH3-

NaSCN solution used as working fluid.12/27/2013 Solar Refrigeration : Current Statusand Future Trends 14


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A LiBr-H2O intermittent absorbent refrigeration

system theoretical studied and its performancepredicted as a function of initial and finaltemperature of generator and condenser by Perry(1975).

A theoretical and experimental study on NH3-H2Osolar refrigerator carried out by Venkatesh et al(1978) and its performance predicted as a function ofgenerator temperature, condenser temperature andinitial solution con concentrations.

Ali Mansoori and Vinod Patel(1979) studiedtheoretically and computed the performance of vapour absorption cycle as a function of generator,atmospheric and evaporator temperatures.


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EXPERIMENTAL SET-UP


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Fig. EXPERIMENTAL STUDIES ON TWO VESSEL12/27/2013 Solar Refrigeration : Current Statusand Future Trends 22


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12/27/2013

Table 1. Experimental

performance of twovessel intermittent

system


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COLLECTOR WITH MIRROR BOOSTERS12/27/2013 Solar Refrigeration : Current Statusand Future Trends 24


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25


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12/27/2013

Fig.15 Thermodynamic cycle for single stage intermittent solar

refrigerator


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12/27/2013

Fig. 19 Effect of tc and tg on COP of single stage system


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SOLAR REFRIGERATOR12/27/2013 Solar Refrigeration : Current Statusand Future Trends 29


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SOLAR REFRIGERATOR WITH INSULATION12/27/2013 Solar Refrigeration : Current Statusand Future Trends 30


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Fig. EXPERIMENTAL STUDIES ON SINGLE STAGE

INTERMITTENT SOLAR REFRIGERATOR12/27/2013 Solar Refrigeration : Current Statusand Future Trends 31


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Fig. EXPERIMENTAL STUDIES ON SINGLE STAGE

INTERMITTENT SOLAR REFRIGERATOR12/27/2013 Solar Refrigeration : Current Statusand Future Trends 32


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12/27/2013

Fig. 25 Effect of increase in condenser temperature on single stage

intermittent solar refrigerator

Solar Refrigeration : Current Statusand Future Trends 34


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12/27/2013

Fig. 30 Effect of tgh and volume ratio on COP of two stage system



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12/27/2013

Fig. 31 Effect of tgh and x1 on COP of two stage system



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TWO-STAGE INTERMITTENT SOLAR

REFRIGERATOR (FRONT VIEW)12/27/2013 Solar Refrigeration : Current Statusand Future Trends 39


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TWO-STAGE INTERMITTENT SOLAR

REFRIGERATOR (REAR VIEW)



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TWO STAGE INTERMITTENT SOLAR REFRIGERATOR

GENERATION PROCESS12/27/2013 Solar Refrigeration : Current Statusand Future Trends 41



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REFRIGERATION PROCESS



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12/27/2013

Fig. 35 Comparison of predicted and experimental performance

characteristics of two stage solar refrigerator



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Triple Fluid Vapour AbsorptionRefrigerator

12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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PLATEN-MUNTERS ABSORPTION SYSTEM


and Future Trends

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Platen and Munters[1926] modified the existingrefrigerators that utilized solely the heat in

practice. Electrolux Inc. took up the responsibility

of commercial production of it. Later on, further

modifications were being added and refrigerators

were then assigned with different names,Triple

Fluid Vapour Absorption Refrigerator,

Absorption-Diffusion Refrigerator,Pumpless Continuous Action Absorption

Refrigerator, etc.


and Future Trends

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Nesselmann[1933] conducted theoretical

investigations on the gas circuit ofTFVAR

with an ideal operating conditions. Heignored the propulsion force required for the

circulation of the gas mixture and diffusion

effects in evaporator and absorber, butclarified the influence of the circulation rate

of the gas mixture and Gas Heat Exchanger

(GHE) efficiency.12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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Miller et al[1946], Nesselmann[1933]andBackstorm[1956] proposed Helium as analternative for Hydrogen because of its lowerspecific heat and hence height differencebetween evaporator and condenser requiredwill be more.

Young and Makiya[1983] illustrated thatCOPs are higher at higher evaporator loads .Helium yield lower COP at lower loads.


and Future Trends

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Watts and Gulland[1958] experiments

proposed a noticeable increase in

refrigerating effect when TFVAR wasoperated at low unit pressure and higher

evaporator temperature. It involved force,

natural and restricted gas flows through thecircuit at pressures: 11.4 and 16.7 bar and

mean evaporator temperature 00C,-100C and

-200C.12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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Martynovsky et al[1973] suggested anincrease in the COP of TFVAR by cooling theweak gas mixture from absorber temperatureto the ambient temperature prior to its gas heatexchanger entry.

Shpilevoy[1982] and Almen[1983] have

reported the usage of the special tubes withinternal capillary incision for evaporator toincrease the mass transfer area.


and Future Trends

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Narayanhedkar and Maiya[1985] worked

for the increase in optimum power input to

the TFVAR and also refrigerating effectwith the inert gas charge pressure which

validates the results of Watts and

Gulland[1957] and Prasad[1986].


and Future Trends

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Maiya[1988] carried out theoretical andexperimental investigations of Triple Fluid

Vapour Absorption Refrigerator which

concluded following results:

Helium as a better substitute to hydrogen as

inert gas with corresponding increase in the

height difference in evaporator and condenser.

However, hydrogen does marginally better for

the same height difference.


and Future Trends

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Major Components of Triple Fluid Vapour Absorption

Refrigerator


and Future Trends

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Evaporator of Triple Fluid Vapour Absorption

Refrigerator


and Future Trends

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Transfer Tank operated VapourAbsorption Refrigeration System


and Future Trends

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and Future Trends

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and Future Trends

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and Future Trends

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and Future Trends

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and Future Trends

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TRANSFER TANK OPERATED VARS

(FRONT VIEW)


and Future Trends

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TRANSFER TANK OPERATED VARS

(REAR VIEW)12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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EFFECT OF GENERATOR TEMPERATURE ON TRANSFER

TANK VAPOUR FLOW12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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EFFECT OF GENERATOR TEMPERATURE ON

CIRCULATION RATIO12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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EFFECT OF GENERATOR TEMPERATURE ON COP12/27/2013 Solar Refrigeration : Current Statusand Future Trends

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SOLAR VAPOUR ABSORPTION

REFRIGERATION SYSTEMS


and Future Trends

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A water cooling VAR system used R22-DMF as

working fluid built by Agarwal and Sabti (1982),capacity of 60 kg of water per day from 30C to 15C.

A theoretical study of NH3-H2O two stage absorption

system with high generator temperature range 100C to

170C by Jhonston(1980). He suggested that the

performance of the system improve than a steady state

system by using evacuated tubular collectors.

Keizer (1982) reported a theoretical and experimentalanalysis of single and two stage ammonia-water

absorption system. He also made a detailed study about

film and vertical tubular bubble absorber and compared

the obtained result12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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T20


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Condenser

R134a liquid

receiver

Hot water

thermostat

Cooling water

thermostat

Cooling load

simulator(Chilled water)

Water

pump

Water

pump

Water

pump

Generator

Solution

heat exchanger

Absorber

Evaporator

R134a refrigerant line

R134a-DMF Solution line

Water line

Absorber

storage

tank Solution

pump

Generator

storage

tank

F

T4

P4

P1

T1

P2

T2

T3P3

P5T5

T8 P8

T9

P9

T7 P7

P6 T6

Hand shut-off valve

Capillary tube

Gate valve

Ball valve

Needle valve

S

F

L

P

T

Pressure gauge

Temperature gauge

Level gauge

Filter/Drier

Flow meter

Online density

meter

S1

S2

S3

S4

S5

S6

T1 0 P1 0

T11 P11

P12T12

P13

T13

T14 P14

T15 T16

T17

T18

T19

T21

T22

HSV1HSV2

HSV3HSV4

NV1

NV2

NV3

HSV5

HSV6HSV7

HSV8

Throttle valve

L3

L2

L1

GV1

GV2

GV3

GV4

GV5

GV6

GV7

GV8

GV9

GV10

GV11

GV12

GV13

GV14

BV1

BV2

BV3

BV4

BV5

BV6

BV7

BV8

BV9

BV10

BV11

Fig. 41 Schematic diagram of R134a-DMF based vapour absorption

refrigeration system12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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Generator

Condenser

Solution

heat

exchanger

Hot water

flow meter

Hot water tank

Generator

receiver

Data acquisition

system

MCB switch

board

Chilled water

flow meter

Liquid refrigerant

receiver

Fig.42 Experimental setup

R134a-DMF vapour absorption refrigeration system

Expansion

device

Liquid

refrigerant

flow meter

Evaporator


and Future Trends

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Liquid


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Fig.43. Experimental setup VARS with plate heat

exchangers

Liquid

Refrigerant

Flow meter

Evaporator

Cooling water tank

with cooling coils

Liquid

refrigerant

receiver

Absorber

Expansion

devices

Condensing unit

for cooling watersystem

Absorber

receiver

Chilled water

tank


and Future Trends

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Solution

pump

Chilled

waterpump

Cooling

water

pumpHot water

pump

Online

density

meter

Fig.44 Solution pump, water pumps and online density meter12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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Compressors

Condenser fans

Condensers

Fig.45 Condensing unit for cooling water system12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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R134a

gas

cylinder

Mass

flowcontroller

Mass

flow

indicator

0 - 5 V DC

power

supplyData

Acquisition

System

24 V DC

power

supply

Glass

absorber

Expt. set-up

equiped with DAS


and Future Trends

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Fig.59 Effect of generator temperature on strong and weak solution

concentration difference at different evaporator temperatures

0

0.05

0.1

0.15

0.2

0.25

0.3

50 55 60 65 70 75 80 85 90 95

Generator temperature,oC

Differenceinstrongandweaksoln.concentratio

ns,kgkg-1

Evaporator temp. = -1.7 C

Evaporator temp. = 4.2 C


Cooling capacity = 3.4 kW

Condenser temperature = 21 C

Absorber temperature = 19.7 C

Experimental

- - - - - Simulation

o

o

o


and Future Trends

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Fig. 60 Effect of generator temperature on circulation ratio at different

evaporator temperatures

0

2

4

6

8

10

12

14

16

18

50 55 60 65 70 75 80 85 90 95


Circulationratio







Experimental


o

o

o


and Future Trends

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Fig. 61 Effect of generator temperature on coefficient of performance at

different evaporator temperatures

0.1

0.2

0.3

0.4

0.5

0.6

0.7

50 55 60 65 70 75 80 85 90 95


CoefficientofPerformance,COP







Experimental


o

o

o


and Future Trends

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SOLAR VAPOUR JET

REFRIGERATION SYSTEM


and Future Trends

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Working Fluids


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Working fluids generally used in Jet refrigeration system areR11, R12, R-113, R-123, R-141b, R134a, R718b, and R717.

Working fluids could be classified as wet and dry vapor byChang et al. [22]. Wet vapour experiences small droplets at theexit of the primary nozzle, and it undergoes two phasecondition. The small droplets block the hypothetical throat area

and hits on the ejector walls, causing damage. It can be avoidedby slightly superheating the primary stream working fluid .

Dry vapour is preferable compared to wet vapour. Comparativestudies on the performance of ejector refrigeration cycle with

eleven refrigerants including water, halocarbon compounds(CFCs, HCFCs, and HFCs), a cyclic organic compound and anazeotrope were carried out by Da- Wen Sun [23]. Therefrigerants were used for achieving better performance of thesystem.12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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One dimensional analysis contd.,


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Ozzane and Aidoun [6] carried out one dimensional analysis ofcompressible refrigerant flow of ejector based on forward

marching technique for the solution of conservation equationsthrough computer simulation for R141b. Mixing chamberlength had a great impact over the performance by controllingthe shock wave occurrence and intensity, its length wasadjusted to bring supersonic mixed flow to near sonic

conditions for maximum exit pressure.

The performance of the ejector under critical operating modewas studied by Selvaraju and Mani [7] and also they comparedthe performance of the ejector with different environmental

friendly refrigerants like R134a, R152a, R290, R600a andR717.. Among the refrigerants selected for analysis, R134agives a better performance and higher critical entrainment ratio.They observed that critical entrainment ratio increases withincrease in driving pressure ratio and decrease with increase in

compression ratio. [8]12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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Simulation of one dimensional analysis based on mass,

momentum and energy balances was carried out Cizungu et al.[36] and validated the same with experimental results from

literature. . Also they compared the system performance using

the environmentally friendly working fluids like R123, R134a,

R 152a and R717. The author suggests that the entrainment ratioand COP of the system depends on ejector geometry and

compression ratio.



and Future Trends

85

Numerical CFD analysis


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Numerical CFD analysis

Bartosiewicz et al. [14] carried out performance analysis of

supersonic ejector using CFD analysis and experimental underdifferent modes, ranging from on-design to off-design

condition. Six turbulence models namely, k-, RNG-k-, RSM

and two k- were tested and compared with measurements

from literature.

The effect of suction tube which entrains secondary flow on

entraining performance was studied by comparing the

axisymmetric and 3- dimensional analysis by Pianthong et al.

[21]. They concluded that the suction tube does not affect the

overall performance of the system, because the flow velocity

at the suction is very low.


and Future Trends

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Numerical CFD analysis contd.,


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y ,

Numerical analyses were performed with 3D axisymmetric

geometry, with realizable k- model as a turbulence model[15].He studied the performance of the ejector with differentcombinations of primary nozzles throat diameter and exitdiameter, mixing chamber diameter, length of constant areamixing tube under varied operating conditions. The author [16]continued the work to explore the flow phenomena inside

ejector.

The influence of geometrical factors of steam ejector on theperformance was studied using CFD by Szabolcs et al. [17,18].The optimal area ratio fo the corresponding operating

conditions could be achieved by adjusting the area ratio, by anadjustable spindle arrangement in the conventional ejectorsystem.


and Future Trends

87

Numerical CFD analysis contd.,


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Selvaraju and Mani [37] carried out performance analysiswith R134a using 3-Dimensional CFD analysis. Governingequations for mass, momentum, energy and turbulence modelswere solved using CFD technique.

Riffat and Omer [12] have studied ejector refrigeration system

using methanol as a working fluid, numerically using CFD andexperimentally. The results of the CFD analysis focused ondetermining the optimum ejector geometry for the givenoperating conditions. Rusly et al. [13] have studied the flow

behavior of the ejector with 2D -CFD analysis.

Scott [11] carried out CFD analysis of an ejector working withR245fa for cooling / refrigeration applications.

y ,


and Future Trends

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Two phase ejector contd.,


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Stefan Elbel [35] studied two-phase ejector used as an

expansion device to reduce throttling losses The author listed

the types of ejector based on the thermodynamic state of theworking fluid as shown in Table.


and Future Trends

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P


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Fig. 2 Thermodynamic diagram of vapour jet refrigeration system

4

P

1

3

ca b

h

2

65


and Future Trends

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Assembled view of the ejector components


and Future Trends

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EJECTOR COMPONENTS OF VJRS12/27/2013 Solar Refrigeration : Current Status

and Future Trends

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12/27/2013

Fig. 105 Meshed view of the ejector

Solar Refrigeration : Current Status

and Future Trends

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12/27/2013

Fig. 106 Shaded view of the ejector


and Future Trends

99

Region of shock waves


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12/27/2013

Fig. 109 Static pressure contour

Pe = 4.15 e+05

PaPc = 7.05 e

+05 Pa

Pg = 26.25 e+05 Pa

Pe = 4.15 e+05

PaPc = 7.05 e+05 Pa

Pg = 30.00 e+05 Pa

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 32.35 e+05 Pa


and Future Trends

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12/27/2013

Fig.110 Velocity vector

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 26.25 e+05 Pa

ms-1

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 30.00 e+05 Pa

Pe = 4.15 e+05 Pa

Pc

= 7.05 e+05 Pa

Pg = 32.35 e+05 Pa

ms-1

ms-1


and Future Trends

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12/27/2013

Fig. 111 Mach number

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 26.25 e+05 Pa

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 30.00 e+05 Pa

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05

PaPg = 32.35 e

+05 Pa


and Future Trends

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12/27/2013

Fig. 112 Distribution of static temperature

Pe = 4.15 e+05

PaPc = 7.05 e

+05 Pa

Pg = 30.35 e+05 Pa

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 32.35 e+05 Pa

Pe = 4.15 e+05 Pa

Pc

= 7.05 e+05 Pa

Pg = 35.81 e+05 Pa


and Future Trends

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12/27/2013

Fig. 113 Variation of enthalpy

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 PaPg = 30.00 e

+05 PaPe = 4.15 e+05 PaPc = 7.05 e

+05 Pa

Pg = 32.35 e+05 Pa

Pe = 4.15 e+05 Pa

Pc = 7.05 e+05 Pa

Pg = 35.81 e+05 Pa


and Future Trends

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0.5T 278 0 K

T


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12/27/2013

Fig. 121 Effect of generator temperature on COP

0

0.1

0.2

0.3

0.4

335 340 345 350 355 360 365

Generator temperature, K

COP

Te = 278.0 K

= 280.5 K

= 283.0 K

= 285.5 K

NA -MATc= 300 K

Te


and Future Trends

106

0.5


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12/27/2013

Fig. 125 Effect of condenser temperature on entrainment ratio

0

0.1

0.2

0.3

0.4

300 302 304 306 308 310

Condenser temperature, K

Entrainmentratio

g = 358 K

= 361K

Te= 283 K

NA - MA

Tg


and Future Trends

107

0.3


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12/27/2013

Fig. 127 Effect of condenser temperature on COP

0

0.1

0.2

300 302 304 306

Condenser temperature, K

COP

= 358 K

= 361 K

Te= 280.5 K

NA - MA

Tg


and Future Trends

108

0.6+10%


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12/27/2013

Fig.128 Comparison of predicted and actual critical entrainment ratio

Correlation for

Critical entrainmentratio

0

0.2

0.4

0 0.2 0.4 0.6

Predicted critical entrainment ratio

A

ctualcriticalentrainm

entrati -10%

968945.0202621.037332.027238.0 cdcritical

RR


and Future Trends

109

0.6


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12/27/2013

Fig.129 Comparison of predicted and actual critical COP

Correlation for

Critical COP

933787.0242682.0284386.0375976.0 cdcritical

RRCOP

0

0.1

0.2

0.3

0.4

0.5

0 0.1 0.2 0.3 0.4 0.5 0.6

Predicted critical COP

ActualcriticalCO

P

-10%

+10%


and Future Trends

110

Payback Analysis


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112/126

Solar and electrical energy costs intersect at 6th year of operation which is

the payback period.

Cost comparison of solar and electrical


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refrigerator The total cost of a selected refrigerator for 10 years is

= Rs.8390 + Rs. 62,052

= Rs.70,442 /-

For solar based refrigeration system the total initial

cost is = Rs 39,340 The saving of cost in 10 years is with a difference of

= 70,442 39,340

= Rs. 31,102.

saving per year is = Rs 31102.00

Courtesy; Ravi Shankar Raman et al / VSRD I nternational Journal of M echanical,

Auto. & Prod. Engg. Vol. 2 (1), 2012

Performance and costs of various solarrefrigeration systems


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Main options of various solar refrigeration


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systems and their ranks

The main options and the options are ranked according totheir reported performance and the required investmentsper kW cooling.

Solar thermal with single-ef fect absorption systemappears to be the best option closely followed by the solarthermal with single-effect adsorption system and by thesolar thermal with double-effect absorption system optionsat the same price level.

Solar thermo-mechanical orsolar photovoltaic options aresignificantly more expensive.



116/126


systems and their ranks , contd..

The vapour compression system and magnetic systems are

the most attractive options followed by the thermo-

acoustic andStirling systems .

Desiccant systems and ejector systems will bemore

expensive than the first three systems but since these

systems require specific equipment their exact position is

difficult to identify.

Courtesy:D.S. Kima, C.A. Infante Ferreirab, Solar refrigeration options a

state-of-the-art review,, I n t e r n a t i o n a l Journal o f R e f r i g e r a t i

on, Vol 3, pp.1 31 5, ( 2 0 0 8 )


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Conclusions


and Future Trends

117

References


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[1] Huang, B.J., J.M. Chang, C.P. Wang and V.A. Petrenko,1999, A 1-D analysis ofejector performance, Int. J. Refrigeration, 22, 354364.

[2] Huang,B.J., Chang.J .M, 1999, Empirical correlation of ejector design, Int. J.Refrigeration , 22, 379388.

[3] Nakagawa. M , Marasigan. A.R, Matsukawa.T and Kurashina. A, 2011,Experimental investigation on the effect of mixing length on the performance of

two-phase ejector for CO2 refrigeration cycle with and without heat exchanger, Int.Journal of Refrigeration , 34,1604-1613.

[5] Seouk Park, I.L, 2009, Enhancement of entraining performance on thermal vaporcompressor for multi-effect desalination plants by swirl effects of motive steam,Numerical Heat Transfer, Part A , 56 : 406-421.

[6] Ouzzane, M. and Z. Aidoun, 2003, Model development and numerical procedurefor detailed ejector analysis and design, App. Thermal Engineering, 23, 2337-2351


and Future Trends

118

References contd.,


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