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Vapour Compression Cycle
CONDENSER
EVAPORATOR
COMPRESSOREXPANSION VALVE
2
1
3
4
Basic Components of the vapour compression refrigeration system
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Vapour Compression CyclePRESSUR
E
COMPRESSION
CONDENSATION
EVAPORATION
THROTTLING
REFRIGERATION EFFECT WORK DONE
CONDENSER HEAT REJECTION
ENTHALPY
KN/m2
KJ/Kg
Pd
Pe 1
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4
CONDENSER
EVAPORATOR
COMPRESSOREXPANSION VALVE
2
1
3
4
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Ideal Vapour Compression Cycle
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Ideal Vapour Compression Cycle
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Actual Vapour Compression Cycle
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VAPOUR COMPRESSION CYCLECOMPONENTS
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REFRIGERANTSCHLOROFLUOROCARBONS (CFC)
• R-11• R-12
HYDROCHLOROFLUOROCARBONS (HCFC)R- 22R-123
HYDROFLUOROCARBONS (HFC)R-32R-125R-134aR-143a
INORGANIC COMPOUNDSR- 717R- 718R- 729
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Unit of Refrigeration
The unit of refrigeration is TON OF REFRIGERATION ( TR )1 TR = 12’000 Btu/hr BRITISH UNITS
1 TR = 3.517 KW SI UNITS
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Refrigeration Cycle Efficiency
The refrigeration cycle efficiency is known asCOEFFICIENT OF PERFORMANCE (COPREF) (COPREF) = Refrigeration Effect KJ/Kg
Work Done KJ/Kg
(COPHP) = Condenser Heat Rejection KJ/Kg
Work Done KJ/Kg
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Refrigeration Equipment Efficiency
The equipment efficiency is given as EER or kW/TRENERGY EFFICIENCY RATIO (EER) Use for smaller capacity equipment such as Window type & Split type
equipment(EER) = Capacity Btu/hr
Power Input Watts
kW/TR Use for large capacity equipment such as Chillers
(kW/TR) = Power Input kW
Capacity TR
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P-h DIAGRAM FOR REFRIGERANT 134a
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1. Face-out of CFC in year 20052. Introduction of Quota for HCFC in
year 20153. Face-out of HCFC in year 2040
MONTRÉAL PROTOCOL OBLIGATIONS
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ASHRAE Standard 34-1992 Refrigerant Safety Classifications
Group A3 Group B3
Group A2 Group B2
Group A1 Group B1
INC
RE
AS
ING
FLA
MM
AB
ILIT
Y
INCREASING TOXICITY
HigherFlammability
LowerFlammability
No FlamePropagation
LowerToxicity
HigherToxicity
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• In-expensive Refrigerant best suited for industrial use
• Specific volume of suction gas is high 8 ft3/lb compare to 1.2 ft3/lb of R-22, needs larger pipes, compressors
• Higher delivery temperatures 210 ºF, needs water cooled heads for compressor
AMMONIA (NH3) R-717
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COOLING TOWER (CT)INDUCED DRAUGHT
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COOLING TOWER (CT)CROSS FLOW
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COOLING TOWER (CT)FORCED DRAUGHT
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WATER PUMPSVERTICAL IN-LINE
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COMPRESSED AIR SYSTEMS
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Provides air under compression to pneumatic drives
Use reciprocating or screw compressors with storage receiver
Use pressure regulators at the air user point to reduce the air pressure
Use water separators to prevent water vapour entering the air user equipment
Compressed air system provides……..
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ROTARY SCREW COMPRESSORS
Pulsation free air 100% continuous duty Quiet operation Energy efficient at full load Extended service intervals Reliable long life Improved air quality
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The temperature limits of an ammonia refrigerating system are 25° C and - 10° C. If the gas is dry at the end of compression, calculate the coefficient of performance of the cycle assuming no undercooling of the liquid ammonia. Use the following table for properties of ammonia :
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Since the entropy at point 1 is equal to entropy at point 2, therefore equating equations (i) and (ii),0.5443 + 4.934 Z1 = 5.04
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A water cooltr using R-12 works on the condensing and evaporatingtemperatures of 26° C and 2° C respectively. The vapour leaves theevaporator saturated and dry. The average output of cold water is 100kgjhr cooled from 26° C to 6°C. Allowing 20% of useful heat into watercooler and the volumetric efficiency of the compressor as 80% andmechanical efficiency of the compressor and the electric motor as 85%and 95% respectively, find (a) volumetric displacement of the compressor,and (b) power of the motor. Data for R-12 is given below
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T-s and p-H diagrams are shown in Fig. 4-12 (a) and (b)respectively. Since 20% of the usefJ heat is lost into watercooler therefore, actual heat extracted from the water cooler
We know that heat extracted or the net refrigerating effectper kg of the refrigerant
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(b) Power of the motorFirst of all, let us 8nd the temperature at point 2 (T2). We know thatentropy at point 2,
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A vapour compression refrigeration plant works between pressurelimits of 5-3 bar and 2'1 bar. The, vapour is superheated at the endof compression, its temperature being 37° C. The vapour issuperheated by 5° C before entering the compressor. If the specificheat of superheated vapour is 0,63 kJjkg.K, find the coefficient ofperformance of the plant. Use the data given below :
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The T-s and p-H diagrams are shown in Fig. 4-14 (a) and (b) respectively
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A food storage lorkcr requires a refrigeration capacity of 12 TR andworks between the evaporating temperature of —8°C andcondensing temperature of 30° C, The refrigerant R-12 is subcooledby 5° C before entry to expansion valve and the vapour issuperheated to—2° C before leaving the evaporator coils. Assuminga two cylinder single acting compressor operating at WOO r p.m.with stroke equal to 1-5 times the bore, determine (a) coefficient ofperformance, (b) theoretical power per ton of refrigeration, and (c)bore and stroke of compressor when (i) there is no clearance, and-(ii) there is a clearance of 2%.Use the following data for R-12
The specific heat of liquid R-12 is 1-235 kJ/kg °K, and ofvapour R-12 is 0'733 kJ/kg °K
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The T-s and p-H diagrams are shown in Fig. 4.26 (a) and (b)respectively,(a) Coefficient of performance
First of all, let us find the temperature of superheated vapour atpoint 2 (T2).
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We know that entropy at point 1
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Since the entropy at point 1 is equal to entropy at point 2,therefore equating equations (i) and (ii),
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(b) Theoretical power per ton of refrigerationWe know that the heat extracted or refrigerating effect per kg of therefrigerant,
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First of all, let us find the specific volume at suction to thecompressor, i.e. at point 1. Applying Charles1 law
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(i) When there is no clearanceWe know that theoretical suction volume or piston displacement per minute
= 0.0245 m3/kg
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We know that volumetric efficiency of the compressor,
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THANK YOU
Prof. Ir. Amiral Aziz, MS.c. APU
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