seprodthermochapter5refrigeration

7/18/2019 seprodthermochapter5refrigeration

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Introduction to Refrigeration and Air - Conditioning

S. Y. B. Tech. Prod Engg.

Introduction toRefrigeration Air Conditioning

ME0223 SEM-IV Applied Thermodynamics & Heat Engines

Applied Thermodynamics & Heat Engines

S.Y. B. Tech.

ME0223 SEM - IV

Production Engineering


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S. Y. B. Tech. Prod Engg.ME0223 SEM-IV Applied Thermodynamics & Heat Engines

Outline

Applications of Refrigeration.

BellColeman Cycle.

COP and Power Calculations

VapourCompression Refrigeration System.

Presentation on T-S and P-h diagram.

VapourAbsorption System.


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Refrigeration

REFRIGERATION Science of producing and maintaining temperature below that of

sur rounding / atmosphere.

REFRIGERATION Cooling of or removal of heat from a system.

Refrigerating System Equipment employed to maintain the system at a low temperature.

Refrigerated System System which i s kept at lower temperatur e.

Refrigeration 1) By melting of a solid,

2) By subl imation of a solid,

3) By evaporation of a liquid.

Most of the commercial refrigeration production : Evaporation of liquid.

This liquid is known as Refrigerant.


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Refrigeration Circuit

Refrigeration Circuit


Evaporator

Compressor

CondenserExpansion

Valve


5/60



Refrigeration - Elements

Compressor

Condenser

Evaporator

Expansion

Valve

Wnet, in

Surrounding Air

Refrigerated Space

QH

QL

High Temp

Source

Low Temp

Sink

QH

QL

Wnet, in


6/60



Refrigeration - Applications

1. Ice making.

2. Transportation of food itemsabove and below freezing.

2. Industrial AirConditioning.

4. Comfort AirConditioning.

5. Chemical and related industries.

6. Medical and Surgical instruments.7. Processing food products andbeverages.

8. Oil Refining.

9. Synthetic Rubber Manufacturing.

10. Manufacture and treatment of metals.

11.Freezing food products.

12. Manufacturing Solid Carbon Dioxide.

13. Production of extremely low temperatures (Cryogenics)

14. Plumbing.

15. Building Construction.

Applications :


7/60



Refrigeration Systems

1. Ice Refrigeration System.

2. Air Refrigeration System.

2. Vapour Compression Refrigeration System.

4. Vapour Absorption Refrigeration System.

5. Adsorption Refrigeration System.

6. Cascade Refrigeration System.

7. Mixed Refrigeration System.

8. Thermoelectric Refrigeration System.

9. Steam Jet Refrigeration System.

10. Vortex Tube Refrigeration System.

Refrigeration Systems :


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Performance - COP

COP Ratio of H eat absorbed by the Refrigerant while passing through the Evaporator

to the Work I nput requi red to compress the Refr igerant in the Compressor.

Performance of Refrigeration System :- Measured in terms of COP (Coefficient of Performance).

If; Rn= Net Refrigerating Effect. W = Work required by the machine.

Then;W

RCOP n

COPlTheoretica

COPActual

COPlative Re

Actual COP = Ratio of Rnand Wactually measured.

Theoretical COP = Ratio of Theoretical values of Rnand Wobtained by applying

Laws of Thermodynamicsto the Refrigerating Cycle.


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Performance - Rating

Rating of Refrigeration System :- Refrigeration Effect / Amount of Heat extracted from a body in a given time.

Unit :

- Standard commercial Tonne of Refrigeration / TR Capacity

Definition :

- Refrigeration Effect produced by melting 1 tonne of ice from and at 0 C in 24 hours.

Latent Heat of ice = 336 kJ/kg.


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Air Refrigeration System

One of the earliest method.

Obsolete due to low COPandhigh operating cost.

Preferred in Aircraft Refrigeration due to its low weight.

Characteristic :

- Throughout the cycle, Refrigerant remains in gaseousstate.

Air Refrigeration

Closed System Open System

Air refrigerant contained within

piping or components of system.

Pressures above atm. Pr.

Refrigerator space is actual room to be cooled.

Air expansion to atm. Pr. And then

compressed to cooler pressure.

Pressures limited to near atm. Pr. levels..


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Air Refrigeration System

1. Suction to compressor in Closed System may be at high pressures. Hence,

the size of Expander and Compressor can be kept small.

Closed System Vs. Open System :

2. In Open Systems, air picks up the moisturefrom refrigeration chamber. This

moisture freezes and chokes the valves.

3. Expansionin Open System is limited to atm. Pr. Level only. No such restriction

to Closed System.


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Reverse Carnot Cycle

3

2

14

Isotherms

Adiabatic

T2

Expansion

Compression

T1

Pressure

Volume

PV Diagram

3 2

14T1

Expansion Compression

T2

Tempera

tu

re

Entropy

14

TsDiagram


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3 2

14T1


T2

Tempera

tu

re

Entropy

14

Operation :

3 4 : Adiabatic Expansion.

Temp. falls from T2to T1.

Cylinder in contact with Cold Body at T1.

4 1 :Isothermal Expansion.

Heat Extraction from Cold Body.

1 2 : Adiabatic Compression.

Requires external power.

Temp. rises from T1to T2.

Cylinder in contact with Hot Body at T2

2 3 :Isothermal Compression.

Heat Rejection to Hot Body.



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3 2

14T1


T2

Tempera

tur

e

Entropy

14

Heat extracted from cold Body : Area 1-1-4-4

= T1X 1-4

Work done per cycle : Area 1-2-3-4

= (T2T1) X 1-4

12

1

12

1

)41()(

)41(

4321

4'4'11

TT

T

XTT

XT

Area

Area

DoneWork

ExtractedHeatCOP



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Example 1

A Carnot Refrigerator requires 1.3 kW per tonne of refrigeration to maintain a region at

low temperature of -38 C. Determine:i) COP of Carnot Refrigerator.

ii) Higher temperature of the cycle.

iii) Heat delivered and COP, if the same device is used Heat Pump.

99.2

)sec/3600()3.1(

/000,14

3.1

1

hrkW

hrkJ

kW

tonne

doneWork

absorbedHeatCOPrefrig .ANS

KTKT

K

TT

TCOPrefrig 6.313

235

23599.2 1

212

1

.ANS

Heat Delivered as Heat Pump ;

sec/189.53.13600

/000,143.11 kJ

hrkJkWtonne

doneWorkabsorbedHeat

.ANS

99.3

3.1

sec/189.5

kW

kJ

doneWork

deliveredHeatCOPHP .ANS


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Example 2

A refrigerating system works on reverse Carnot cycle. The higher temperature in the

system is 35 C and the lower temperature is -15 C. The capacity is to be 12 tonnes.Determine :

i) COP of Carnot Refrigerator.

ii) Heat rejected from the system per hour.

iii) Power required.

18.5258308

258

12

1 KK

K

TT

TCOPrefrig .ANS

hrkJInputWork

InputWork

hrkJX

InputWork

tonne

InputWork

Ef fectfrigCOPrefrig

/32558

/000,14121216.5

.Re

.ANSkWhrkJhrInputWork

Power 04.9

3600

/32558

3600

/

Heat Rejected / hr = Refrig. Effect / hr + Work Input / hr

= 12 x 14,000 (kJ/hr) + 32,558 (kJ/hr) = 2,00,558 kJ/hr. .ANS


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Example 3

Ice is formed at 0 C from water at 20 C. The temperature of the brine is -8 C. Find out

the kg of ice per kWh. Assume that the system operates on reversed Carnot cycle. Takelatent heat of ice as 335 kJ/kg.

46.9265293

265

12

1

KK

K

TT

TCOPrefrig

Heat to be extracted per kg of water ( to from ice at 0 C)Rn = 1 (kg)x Cpw(kJ/kg.K)x (293273) (K)+ Latent Heat (kJ/kg) of ice

= 1 (kg)x 4.18 (kJ/kg.K)x 20 (K)+ 335 (kJ/kg)

= 418.6 kJ/kg.

Also, 1 kWh = 1 (kJ)x 3600(sec/hr)= 3600 kJ.

kgmkJ

kgkJXkgm

kJdoneWork

kJEf fectfrig

W

RCOP

iceice

nrefrig

35.813600

)/(6.418)(46.9

)(

)(.Re

.ANS


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BellColeman / Reverse Bryaton Cycle

Elements of this system :

1. Compressor.

2. Heat Exchanger.

3. Expander.

4. Refrigerator.

Work gained from Expanderis used

to drive Compressor.

Hence, less external work is required.

Heat ExchangerCooling

Water

Refrigerator

CompressorExpander

Cold Air

Very Cold AirWarm Air

Hot Air


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32

1

4

Isobars

Adiabatic

Expansion

Compression

Pressure

Volume

PV Diagram

3

2

1

4

Expansion

Compression

Tempera

tu

re

Entropy

Isobars

Adiabatic

TsDiagram


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3

2

1

4

Expansion

Compression

Tempera

ture

Entropy

Isobars

Adiabatic

Heat Absorbed in Refrigerator :

)( 41 TTCmQ Padded

Heat Rejected in Heat Exchanger :

)( 32 TTCmQ Prejected

If process changes from Adiabaticto Polytropic;

11221

VPVPn

nQcomp

4433exp1

VPVPn

nQ n

We know,

1PCR


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Net Work Done :

1234

4312

44331122

exp

1

1

1

1

TTTTCmn

n

TTTTRmn

n

VPVPVPVPn

n

WWW

P

ncomp

For Isentropic Process :

1234

exp

TTTTCm

WWW

P

ncomp


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COP :

1234

41

1

1

)(

TTTTCmn

n

TTCm

W

Q

QQ

AddedWorkCOP

P

P

net

added

addedrejected

1234

41

1

1

)(

TTTTn

n

TTCOP


23/60



Air Refrigeration Cycle - Merits / Demerits

Merits :

1. No risk of fire (as in case of NH3); as air is nonflammable.

2. Cheaper (than other systems); as air is easily available.

3. Weight per tonne of refrigeration is quite low (compared to other systems).

Demerits :

1. Low COP (compared with other systems).

2. Weight of air (as Refrigerant) is more (compared to other systems).


24/60



Example 4

A BellColeman refrigerator operates between pressure limits of 1 bar and 8 bar. Air is

drawn from the cold chamber at 9 C, compressed and then cooled to 29 C beforeentering the expansion cylinder. Expansion and compression follow the law PV1.35= Const.

Calculate the theoretical COP.

For air, take = 1.4 and Cp= 1.003 kJ/kg.

Polytropic Compression 1-2 :

Kbar

barK

P

PTT

n

n

2.4821

8)282(

35.1

135.11

1

212

Polytropic Expansion 3-4 :

KT

bar

barTK

P

PTT

n

n

6.176

1

8)302(

4

35.1

135.1

4

1

4

343

3 2

14

PV1.35=C

Pr

essure

Volume

P2= 8 bar

P1= 1 bar

282 K

302 K


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Heat Extracted from Cold Chamber:kgkJKKXkgkJTTCP /7.105)6.176282()/(003.1)( 41

Example 4.contd

Heat Rejected to Heat Exchanger:

kgkJKKXkgkJTTCP /7.180)3022.482()/(003.1)( 32

Net Work Done :

kgkJW

KKKKkgkJW

TTTTCmn

nW

net

net

Pnet

/8.82

2822.4823026.176)/003.1(4.1

14.1

135.1

35.1

1

1 1234

27.1/8.82

/7.105

kgkJ

kgkJ

doneWork

absorbedHeatCOPrefrig .ANS


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Example 5

An air refrigeration open system operating between 1 MPa and 100 kPa is required to

produce a cooling effect of 2000 kJ/min. temperature of the air leaving the cold chamber is-5 C, and at leaving the cooler is 30 C. Neglect losses and clearance in the compressor

and expander. Determine :

i) Mass of air circulated per min. ii) Compressor Work, Expander Work, Cycle Work.

ii) COP and Power in kW required.

3 2

14

PV=C

Pre

ssure

Volume

P2= 1 MPa

P1= 100 kPa

268 K

303 K

Polytropic Expansion 3-4 :

KT

MPa

MPaTK

P

PTT

9.156

1.0

1)302(

4

4.1

14.1

4

1

4

343

Refrig. Effect per kg:

kgkJ

KKXkgkJ

TTCP

/66.111

)9.156268()/(003.1

)( 41


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Example 5.contd

min/91.17/66.111

min/2000

.Re

.Rekg

kgkJ

kJ

kgperEffectfrig

Effectfrig

Mass of air circulated per min :

.ANS

Polytropic Compression 1-2 :KkPa

kPa

KP

P

TT 4.517100

1000

)268(

4.1

14.11

1

2

12

.ANS

Compressor Work :

min/85.4486

2684.517)/287.0(min)/91.17(14.1

4.11

12

kJW

KKkgkJkgW

TTRmW

comp

comp

comp

.ANS


28/60



Expander Work :

min/42.2628

9.156303)/287.0(min)/91.17(14.1

4.1

1 43exp

kJW

KKkgkJkgW

TTRmW

comp

comp

.ANS

Example 5.contd

Cycle Work = Wcycle= WcompWexp

= 4486.85 kJ/min2628.42 kJ/min = 1858.43 kJ/minANS

076.1min/43.1858

min/2000.Re kJkJ

requiredWorkEffectfrigCOPrefrig .ANS

Power required : kWkJ

time

WP

cycle97.30

minsec/60

min/43.1858 .ANS

i f i i Ai C i i i


29/60



Vapour Compression System

Elements of this system :

1. Compressor.

2. Condenser.

3. Expansion Valve.

4. Evaporator.

Vapour @ Pr. and Temp. (State 1)

Isentropic Compression:

Pr. and Temp. (State 2)

Condenser : Pr. Liquid (State 3)

Throttling : Pr. Temp. (State 4)

Evaporator : Heat Extraction from surrounding;

Pr. vapour (State 1).

1

2

3

4

1

23

4

I d i R f i i d Ai C di i i


30/60



Vapour Compression System

Merits :

1. High COP; as very close to Reverse Carnot Cycle.

2. Running Cost is 1/5th of that of Air Refrigeration Cycle.

3. Size of Evaporator is small; for same Refrigeration Effect.

Demerits :

1. Initial cost is high.

2. Inflammability.

4. Evaporator temperature adjustment is simple; by adjusting Throttle Valve.

3. Leakage.

4. Toxicity.

I t d ti t R f i ti d Ai C diti i


31/60



Vapour Compression System : T-sDiagram

Case A. Dry and Saturated Vapour after Compression :

Work done by Compressor

= W = Area 1-2-3-4-1

Heat Absorbed

= W = Area 1-4-g-f-1

Entropy, s

Temperature,

T Condensation

Compression

Evaporation

Expansion

T2

T1

3

4

2

1

Compressor Work,

(W)

Net Refrig. Effect,(Rn)

Sat. Vapour L ine

Sat. Liq. Line

fg

12

41

14321

141

hh

hh

Area

fgArea

DoneWork

AbsorbedHeatCOP



32/60




Case B. Superheated Vapour after Compression :


= W = Area 1-2-2-3-4-1

Heat Absorbed

= W = Area 1-4-g-f-1

12

41

143'221

141

hh

hh

Area

fgArea

DoneWork

AbsorbedHeatCOP

Entropy, s

Temperature,

T Condensation

Compression

Evaporation

Expansion

T2

T1

3

4

2

1

Compressor Work,

(W)


Sat. Vapour L ine

Sat. Liq. Line

fg

2

NOTE : h2= h2 + Cp(TsupTsat)



33/60




Case C. Wet Vapour after Compression :


= W = Area 1-2-3-4-1

Heat Absorbed

= W = Area 1-4-g-f-1

Entropy, s

Temperature,

T Condensation

Compression

Evaporation

Expansion

T2

T1

3

4

2

1

Compressor Work,

(W)


Sat. Vapour L ine

Sat. Liq. Line

fg

12

41

14321

141

hh

hh

Area

fgArea

DoneWork

AbsorbedHeatCOP

NOTE : h2= (hf + x.hfg)2

Introd ction to Refrigeration and Air Conditioning


34/60



Vapour Compression System : P-hDiagram

Enthalpy, h

Pressure,

P

r

Isothermal,

T=Const

Isenthalpic,

h=

Const.

Isobaric,

P = Const

Sub-cooled

L iq. region 2 phase

region

Superheated

region


35/60

Introduction to Refrigeration and Air Conditioning


36/60



Factors Affecting Vapour Compression System

A. Effect of Suction Pressure :

Enthalpy, h

Pressure,

Pr

1

23

4

14

2

P1

P212

41

hh

hh

W

RCOP n

COP of Original Cycle :

COP when Suction Pr. decreased :

2'2'1112

'1141

'1'2

'4'1

hhhhhh

hhhh

hh

hh

W

RCOP n

Thus,

Refrig. Effect Work Input COP



37/60




B. Effect of Delivery Pressure :

12

41

hh

hh

W

RCOP n


COP when Delivery Pr. increased :

2'212

4'441

1'2

'41

hhhh

hhhh

hh

hh

W

RCOP n

Thus,

Refrig. Effect Work Input COP

Enthalpy, h

Pressure,

Pr

1

2

3

4

3

4

2

P1

P2



38/60




C. Effect of Superheating :

12

41

hh

hh

W

RCOP n


Thus,

Refrig. Effect Work Input or COP or

Enthalpy, h

Pressure,

Pr

1

23

4

1

2

P1

P2

1'12'212

1'141

'1'2

4'1

hhhhhh

hhhh

hh

hh

W

RCOP n





39/60




D. Effect of Sub-cooling :

12

41

hh

hh

W

RCOP n


Thus,

Refrig. Effect Work Input : SAME

COP

12

'4441

12

'41

hh

hhhh

hh

hh

W

RCOP n


Enthalpy, h

Pressure,

Pr

1

23

4

1

3

P1

P2

4




40/60




E. Effect of Suction & Condenser Temperatures :


Now, Condenser Temp. Evaporator Temp.

12

41

'1'4'3'2'1

1'44'11

hh

hh

Area

fgArea

DoneWorkAbsorbedHeatCOP

COP of Modified Cycle :


12

41

14321

141

hh

hh

Area

fgArea

DoneWork

AbsorbedHeatCOP

COP Entropy, s

Temperature,

T Condensation

Compression

Evaporation

Expansion

T2

T1

3

4

2

1

fg

1

4

23



41/60



Vapour Compression SystemMathematical Analysis

A. Refrigerating Effect :

)/(41 kgkJHeatdSuperheateHeatLatenthhQevap

= Amount of Heat absorbed in Evaporator.

B. Mass of Refrigerant :

= Amount of Heat absorbed / Refrigerating Effect.

)sec/(

3600

000,14

41

tonnekghh

m

1 TR = 14,000 kJ/hr

C. Theoretical Piston Displacement := Mass of Refrigerant X Sp. Vol. of Refrigerant Gas (vg)1.

)sec/(

3600

000,14.. 3

141

tonnemvhh

DisplPistonTh g



42/60



Vapour Compression SystemMathematical Analysis

)(

)/(

12

12

kWhhmP

kgkJhhW

theor

comp

a) Isentropic Compression :D. Theoretical Power Required :

)(1

)/(1

1122

1122

kWVPVPn

nmP

kgkJVPVPn

nW

theor

comp

a) Polytropic Compression :

E. Heat removed through Condenser :

)/(32 kgkJhhmQcond



43/60



Example 7Example 6A refrigeration machine is required to produce ice at 0 C from water at 20 C. The

machine has a condenser temperature of 298 K while the evaporator temperature is 268K. The relative efficiency of the machine is 50 % and 6 kg of Freon-12 refrigerant is

circulated through the system per minute. The refrigerant enters the compressor with a

dryness fraction of 0.6. Specific heat of water is 4.187 kJ/kg.K and the latent heat of ice is

335 kJ/kg. Calculate the amount of ice produced on 24 hours. The table of properties if

Freon-12 is given below:

Temperature

(K)

Liquid Heat

(kJ/kg)

Latent Heat

(kJ/kg)

Entropy of Liquid

(kJ/kg)

298 59.7 138.0 0.2232

268 31.4 154.0 0.1251

hf1 = 31.4 kJ/kghfg1= 154.0 kJ/kg

hf2 = 59.7 kJ/kg

hfg2= 138.0 kJ/kg

hf3 = h4= 59.7 kJ/kg

m =6 kg/minrel=50 %

x2 = 0.6

Cpw= 4.187 kJ/kg.K

Latent Heat of ice = 335.7 kJ/kgGiven :



44/60



Example 6.contd

Entropy, s

Tem

perature,

T298 K

268 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

kgkJhxhh fgf /8.1230.154)6.0(4.31111

kgkJhxhh fgf /2.1330.138)5325.0(7.5922 22

5325.0

268

0.1546.01251.0

298

0.1382232.0

2

2

1

1

112

2

22

111222

12

x

x

T

h

xsT

h

xs

sxssxs

ss

fg

f

fg

f

fgffgf

Isentropic Compression :1-2

kgkJhh f /7.5934


82.6

/8.1232.133

/7.598.123

12

41

kgkJ

kgkJ

hh

hh

W

RCOP n




45/60

oduc o o e ge o d Co d o g


Example 6.contd

Actual COP = relX COPtheor= 0.5 X 6.82 = 3.41

Heat extracted from 1 kg of water at 20 C to form 1 kg of ice at 0 C :

kgkJ

kgkJ

CXKkgkJXkg

/74.418

)/(335

)()020()./(187.4)(1

Entropy, s

Temperatur

e,

T298 K

268 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

Now;

.ANS

hrsintonneXX

kg

kgkJ

kgkJXkgm

hhm

Xm

W

RCOP

ice

iceactualn

actual

24661.01000

2460459.0

min/459.0

41.3/74.418

)/(8.1232.133)(6

74.41841.3

12

)(




46/60

g g


Example 7

28 tonnes of ice from and at 0 C is produced per day in an ammonia refrigerator. The

temperature range in the compressor is from 25 C to -15oC. The vapour is dry andsaturated at the end of compression and an expansion valve is used. Assuming a

co-efficient of performance of 62% of the theoretical, calculate the power required to

drive the compressor. Take latent heat of ice = 335 kJ/kg.

Temp

(C)

Enthalpy (kJ/kg) Entropy of

Liquid(kJ/kg.K)

Entropy of Vapour

(kJ/kg.K)Liquid Vapour

25 100.04 1319.22 0.3473 4.4852

-15 -54.56 1304.99 -2.1338 5.0585


hf1 = -54.56 kJ/kghg1= 1304.99kJ/kg

hf2 = 100.04 kJ/kg

hg2= 1319.22 kJ/kg

hf3 = h4= 100.04 kJ/kg

Tcond =25 CTevap=-15 C

x2 = 1.dry saturated vapour

COPactual= 0.62 (COPtheor)

Latent Heat of ice = 335.7 kJ/kgGiven :



47/60

g g


91.823.119622.1319

04.10023.1196

12

41

hh

hhCOP ltheoreticaCOP of the Cycle :

Entropy, s

Temperatur

e,

T298 K

258 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

Example 7.contd

processcIsenthalpikgkJhh ...../04.10043

kgkJ

hxhh fgf

/23.1196

)56.54(99.1304)92.0()56.54(

)( 1111

92.0

1338.20585.5)1338.2(4852.4

2

1

1112

12

x

x

sxss

ss

fgfg


kgkJhh g /22.131922



48/60

g g


Example 7.contd


Actual COP = relX COPtheor

= 0.62 X 8.91

= 5.52

Entropy, s

Temperatur

e,

T298 K

258 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

Actual Rn= COPactualX Work done

= 5.52 X (h2h1)

= 5.52 X (1319.221196.23)

= 678.9 kJ/kg

Heat extracted from 28 tonnes of water at 0 C to form ice at 0 C :

)(sec/56.108

)(sec/3600)(24

)/(335)/(1000)(28

kWkJ

hrXhr

kgkJXtonnekgXkg

Mass of refrigerant : kg

kgkJ

kJ1599.0

)/(9.678

sec)/(56.108

Total Work done by Compressor :

)(sec/67.19

/)23.119622.1319()(1599.012

kWkJ

kgkJXkghhXmrefrig

.ANS



49/60

g g


Example 8

In a standard vapour compression refrigeration cycle, operating between an evaporator

temperature of -10 C and a condenser temperature of 40 C, the enthalpy of therefrigerant, Freon-12, at the end of compression is 220 kJ/kg. Show the cycle diagram on

T-s plane. Calculate:

1. The C.O.P. of the cycle.

2. The refrigerating capacity and the compressor power assuming a refrigerant flow

rate of 1 kg/min.

You may use the extract of Freon-12 property table given below:

Temp (C) Pr (MPa) hf(kJ/kg) hg(kJ/kg)

-10 0.2191 26.85 183.1

40 0.9607 74.53 203.1


hf1 = 26.85 kJ/kghg1= h1=183.1 kJ/kg

hf2 = 74.53 kJ/kg

hg2= 203.1 kJ/kg

hf3 = h4= 74.53 kJ/kg

Tcond =40 C

Tevap=-10 C


h2=220 kJ/kgGiven :



50/60


Example 8.contd


94.2/1.1830.220

/53.741.183

12

41

kgkJ

kgkJ

hh

hh

W

R

COP

n

.ANS

Refrigerating Capacity :

min/57.108

/53.741.183)(141

kJ

kgkJXkghhm

.ANS

Compressor Power :

kW

kJ

kgkJXkghhm

615.0

min/9.36

/1.1830.220)(112

.ANS

Entropy, s

Temperatu

re,

T40 C

-10 C

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

2



51/60


Example 9

A Freon-12 refrigerator producing a cooling effect of 20 kJ/sec operates on a simple

cycle with pressure limits of 1.509 bar and 9.607 bar. The vapour leaves the evaporatordry saturated and there is no undercooling. Determine the power required by the

machine. If the compressor operates at 300 rpm and has a clearance volume of 3% of

stroke volume, determine the piston displacement of the compressor. For compressor

assume that the expansion following the law PV1.3= Constant.


Temp

(oC)

Ps(bar)

vg

(m3/kg)

Enthalpy

hf

(kJ/kg)

Enthalpy

hg

(kJ/kg)

Entropy

sf

(kJ/kg)

Entropy

sg

(kJ/kg)

Specific

heat

(kJ/kg.K)

-20 1.509 0.1088 17.8 178.61 0.073 0.7082 ---

40 9.607 --- 74.53 203.05 0.2716 0.682 0.747

hf1 = 17.8 kJ/kghg1= h1=178.61 kJ/kg

hf2 = 74.53 kJ/kg

hg2= 203.05 kJ/kg

hf3 = h4= 74.53 kJ/kg

Tcond =40 C

Tevap=-20 C


h2=220 kJ/kgGiven :



52/60


Example 9.contd

Refrigerating Capacity :

sec/192.0

/53.7461.1782041

kgm

kgkJXmkWhhm

KT

T

TTCss

ss

P

2.324

313ln747.0682.07082.0

ln

2

2

'2

2'21

21


kgkJ

KKkgkJkgkJ

TTChh P

/4.211

0.3132.324./747.0)/(05.203

'22'22


Entropy, s

Tempera

ture,

T313 K

253 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

2



53/60


Example 9

.ANS

Power Required :

kW

kgkJXkghhm

29.6

/61.1784.211sec)/(192.012

Vol. Efficiency :

%6.87

509.1

607.903.003.01

1

13.1/1

/1

bar

bar

P

Pkk

n

S

dvol

Vol of Refrigerant

at Intake :

sec/02089.0)/(1088.0sec)/(192.0

3

3

mkgmXkg

vm g

Piston Displ. Vol. : 3

3

00477.0)(300876.0

min)(sec/60sec)/(02089.0

)(

.m

rpm

m

rpm

VolActual

vol

.ANS


Entropy, s

Temperature,

T313 K

253 K

3

4

2

1

Sat. Vapour L ine

Sat. Liq. Line

fg

2



54/60


Example 10

A food storage locker requires a refrigeration capacity of 50 kW. It works between a

condenser temperature of 35 C and an evaporator temperature of -10 C. The refrigeratoris ammonia. It is sub-cooled by 5 C before entering the expansion valve. By the dry

saturated vapour leaving the evaporator. Assuming a single-cylinder, single-acting

compressor operating at 1000 rpm with stroke equal to 1.2 times the bore, determine :

1. The power required.

2. The cylinder dimensions.

Properties of ammonia are :

Sat.

Temp.

(oC)

Pr.(bar)

Enthalpy

(kJ/kg)

Entropy

(kJ/kg)

Sp. Vol.

(m3/kg)

Sp. Heat

(kJ/kg.K)

Liquid Vapour Liquid Vapour Liquid Vapour Liquid Vapour

-10 2.9157 154.056 1450.22 0.82965 5.7550 --- 0.417477 --- 2.49235 13.522 366.072 1488.57 1.56605 5.2086 1.7023 0.095629 4.556 2.903


h1 = 1450.22 kJ/kg

h2 = 1488.57 kJ/kg

hf3 = 366.072 kJ/kg

Tcond =35 C

Tevap=-10 C


State 3 =Sub-cooled by 5 CGiven :



55/60


Example 10.contd

kgkJ

kgkJkgkJ

TTChhh subcoolsatliqPf

/29.343

)/(30330856.405)/(07.366

34'3

KT

T

T

TCssss P

8.371

308ln903.22086.5755.5

ln

2

2

'2

2'2121


kgkJ

KKkgkJkgkJ

TTChh P

/8.1673

0.3088.371./903.2)/(57.1488

'22'22

Entropy, s

Temper

ature,

T308 K

263 K

3

4

2

1Sat. Vapour L ine

Sat. Liq. Line

fg

2

3

303 K



56/60


Example 10.contd

sec/04517.0

/29.34322.1450

)(50

/

)(50

41

kg

kgkJ

kW

kgkJhh

kWm

Mass of Refrigerant :

Compressor Power :

kW

kgkJXkg

hhm

1.10

/22.14508.1673)(04517.0

12

.ANS

Cylinder Dimensions :

mmL

mD

kgm

rpmDD

v

NLD

kgmg

228.0)19.0(2.1

19.0

/417477.0

60

)(1000)2.1(4604

sec)/(04517.03

22

.ANS

.ANS

Entropy, s

Tempe

rature,

T308 K

263 K

3

4

2

1Sat. Vapour L ine

Sat. Liq. Line

fg

2

3303 K



57/60


Vapour Absorption System

1

2

4

3

Solubility of NH3in water @ Temp and Pr.is MOREthan that @ Temp. and Pr.

NH3vapour from Evaporator(State 1) is readily absorbed in Absorber. Heat Rejection

This solution is then pumped to Temp. and Pr. @Generator.

Reduction in stability of solution Vapour removed from Solution.

Vapour passes to Condenser.

Weak Solution returns to Absorber.



58/60


Vapour Absorption System

Merits :

2. Work done on Compression is LESS.

1. Pumping work is much less than work for Compressing vapour.

Demerits :

2. Low COP.

1. Heat input to the Generator is required.

COP :

PumpLiquidondoneWorkGeneratorinpliedHeat

EvaporatorinextractedHeatCOP

sup



59/60


Vapour Compression Vs. Vapour Absorption

Sr.No.

Particulars Vapour CompressionSystems

Vapour AbsorptionSystems

1. Type of Energy Supplied Mechanical High Grade Heat Low Grade2. Energy Supply Rate Low High3. Wear & Tear More Less4. Performance of Part

Load Poor Not affected at Part Load5. Suitability Used where High Grade Mechanical

Energy is available

Can be used at Remote

Places, as can be used with

simple Kerosene lamp

6. Charging of Refrigerant Simple Difficult7. Leakage More chances No chances, as no Compressor

or Reciprocating Part

8. Damage Liquid traces in Suction Linemay damage Compressor

No danger



60/60

Thank You !

seprodthermochapter5refrigeration

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