AProject ReportonTHERMODYNAMIC ANALYSIS OF VAPOUR CASCADE
REFRIGARATION SYSTEM USING R-12 & R-404A (ALTERNATIVE
REFRIGARENT)
Submitted by: Srikanta Biswas, Roll No-11800712053 Biplab Khan,
Roll No-11800713067 Somnath Dey, Roll No-11800712051 Sayan
Sarbajna, Roll No-11800712049 Shovan Ghosh, Roll
No-11800712050Surovita Santra, Roll No 11800713077 Guided by:
Santanu Banerjee(Associate Professor)Department of Mechanical
EngineeringBirbhum Institute of Engineering & Technology,
SURI
CERTIFICATE OF APPROVAL
This is to certify that the project report entitled
THERMODYNAMIC ANALYSIS OF VAPOUR CASCADE REFRIGARATION SYSTEM USING
R-12 & R-404A (ALTERNATIVE REFRIGARENT), being submitted by
Srikanta Biswas (11800712053), Biplab Khan (11800713067), Sayan
Sarbajna (11800712049), Shovan Ghosh (11800712050) , Surovita
Santra (11800713077) , Somnath Dey (11800712051) in the partial
fulfilment of the requirement for the award of the degree of B.
Tech in Mechanical Engineering, is a record of bonafide research
carried out by them at the Department of Mechanical Engineering,
Birbhum Institute of Engineering and Technology, Suri under our
guidance and supervision.
-------------------------------------------
--------------------------------------Santanu Banerjee Prof. TITOV
BANERJEE(Associate Professor) (Head of The Mechanical Department of
Mechanical Engineering Engineering Department)
-------------------------------------------Dr. SUBHASISH
BISWAS(Director) Birbhum Institute of Engineering and Technology,
Suri
2
ACKNOWLEDGEMENT
We would like to express our sincere gratitude to our guide
Santanu Banerjee for their invaluable guidance and steadfast
support during the course of this project work. Fruitful and
rewarding discussions with him on numerous occasions have made this
work possible. It has been a great pleasure for me to work under
his guidance.We would like to express our sincere thanks to all the
faculty members of Mechanical Engineering Department for their kind
co-operation.We would like to acknowledge the assistance of all my
friends in the process of completing this work.Finally, we
acknowledge our sincere gratitude to our family members for their
constant encouragement and support.
______________________(SRIKANTA BISWAS)ROLL NO. 11800712053
________________________(SOMNATH DEY)ROLL NO. 11800712051
_________________________(BIPLAB KHAN)ROLL NO. 11800713067
_________________________(SUROVITA SANTRA)ROLL NO.
11800713077
______________________(SHOVAN GHOSH)ROLL NO. 11800712050
________________________(SAYAN SARBAJNA)ROLL NO. 11800712049
3
CONTENT
TOPICPAGE NO
List of Tables and List of FiguresNomenclature56
CHAPTER 1: INTRODUCTION Refrigeration Refrigerant Classification
of Refrigerant Properties of Ideal Refrigerants Designation Few
Refrigerants and Their Use Effect of Refrigerant Need of
Alternative Refrigerant Alternative Refrigerant COP And TR7-14
CHAPTER 2: VAPOUR CASCADE REFRIGERANT SYSTEM15
CHAPTER 3: LITERATURE REVIEW16-25
CHAPTER 4: MATHEMATICAL FORMULATION Description of proposed
model Thermodynamics of the system26-27
CHAPTER 5: RESULTS AND DISCUSSION Values of different parameters
Effect of evaporator temperature on COP Effect of evaporator
temperature on compressor work Effect of evaporator temperature on
refrigerating effect Effect of evaporator temperature on exegetic
efficiency.28-29
CHAPTER 6: CONCLUSION AND SCOPE OF FUTURE WORK Conclusion Scope
Of Future Work30
CHAPTER 7: REFERENCES31-33
4
List of figure
Figure noDescriptionPage no.
1.1T-S Diagram Of Cascade Refrigeration2
1.2P-H Diagram Of Cascade Refrigeration3
1.3Production Of Halogenated Refrigerant8
1.4Ozone Depletion Potential Of Pure CFC And HCFC
Refrigeration9
1.5Global Warming Of Pure Cfc And HCFC9
1.6Global Warming Of Pure HCFC Refrigerants9
1.7Global Warming Of HFC Mixtures9
1.8Schematic Diagram Of A Two Stage Cascade Refrigeration
System11
5NomenclatureR 12/CFC 12Dichlorodifluoromethane (Freon
12)R22Chlorodifluromethane
R134a1,1,1,2-TetrafluoroethaneR717Ammonia
R143a1,1,1-TrifluoroethaneR1232,2-Dichloro-1,1,1-trifluoroethane
R152a1,1-DifluoroethaneR407CBlend of R32, R125 and R134a
R404ABlend of R125, R143a and R134aR410ABlend of R32 and
R125
R417ABlend of R125, R134a and R600R744Carbon Di-Oxide
R161FluorethaneR507Blend of R125 and R143a
R125PentafluoroethaneR718Water
R600ButaneR502Blend of R22 and R115
R290PropaneR11Trichlorofluoromethane
R600aIsobutaneHCFCHydrochlorofluorocarbon
R422BBlend of R125, R134a and R600aHFCHydrofluorocarbons
GWPGlobal warming potentialCFCChlorofluorocarbon
GHGGreenhouse gasUVUltra violet
TRTon of refrigerationODPOzone depletion potential
COPCoefficient of performanceQ1Heat absorbed
Q2Heat rejectedWCCompressor work
P1Condenser pressureP2Evaporator pressure
hEnthalpy in kJ/kgSEntropy in kJ/kg-k
CConstantTTemperature
vSpecific volume in m3/kgXDryness fraction
1Evaporator outlet2Compressor outlet
3Condenser outlet4Expansion valve outlet
0SurroundingsKTemperature in Kelvin
HCHydro carbonsBPRButane-Propane-R134a
m.Mass flow rateeExergy loss
wCompressorVValve
cCondenserEEvaporator
IIExergetic efficiencySCompressor isentropic efficiency
VVolumetric efficiency VCCVCCVolumetric cooling capacity
rReference stateETotal heat loss
6Chapter -1INTRODUCTIONRefrigeration is a process of moving heat
from lower temperature to higher temperature in controlled
conditions. Refrigeration also can be defined as a process of
achieving & maintaining a temperature below that of
surroundings. Refrigeration has many applications including them
the most important is to preserve foods in a low temperature. It
also used in industrial, agriculture and many other
purposes.Refrigeration system is based on Clausius statement of the
2nd law of thermodynamics. Clausius statement states that: It is
impossible to construct a device that operating a cycle, has no
effect other than the transfer of heat from a cooler to a hotter
body. The devices that provide this help are called refrigeration
units & heat pumps. Refrigerator & Heat pump:The operating
system of refrigerator and heat pump are reversed. In refrigerator
heat transfer from low temperature region to high temperature
region. But in heat pump heat transfer from a low temperature
medium to high temperature medium.The objective of a refrigerator
to remove heat (QL) from the cold medium and the objective of a
heat pump is to supply heat (QH) to a warm medium.The performance
of a refrigerator and heat pump is expressed as co-efficient of
refrigerant (COP) defined asCOPR=cooling effect/work input= QL/W
net inCOPHP= Heating effect / Work input= QH/W net inBoth COPR and
COPHP can be larger than 1. Component of a Vapour Compression
Refrigeration System:There are four essential part of a
refrigeration system i.e., compressor, condenser, expansion valve,
evaporator.Compressor: the low pressure and temperature vapour
refrigerant from evaporator is drawn into the compressor. In
compressor it is compressed to a high pressure and temperature
vapour. The high pressure and temperature vapour is discharged in
the condenser.Condenser: In condenser high pressure and temperature
vapour refrigerant condensed and cooled.Expansion Valve: In
expansion valve the high pressure and temperature liquid
refrigerant is passed to a controlled rate after reducing its
pressure and temperature and makes a liquid vapour
refrigerant.7Evaporator: It consists of coils of pipes in where
liquid vapour refrigerant is evaporates and converted in low
pressure and temperature vapour refrigerant. In evaporating the
liquid vapour refrigerant absorbs latent heat of vaporization
(water, air or brine) which is to be cooled.T-S Diagram of an Ideal
Refrigeration Cycle:Process 1-2 Isentropic compression in low
temperature Compressor. Process 2-3 P: Constant pressure Heat
Rejection in low temperature circuit Process 3-4: Expansion Under
Throttling Process, Isenthalpic Process Process 4-1 P: Constant
Heat Addition Process Process 1-2: Isentropic compression in high
temperature compressor Process 2-3P: Constant pressure Heat
Rejection in high temperature circuit Process 3-4: Expansion Under
Throttling Process, Isenthalpic Process Process 4-1P: Constant
pressure Heat Addition Process P-h Diagram of Ideal Refrigeration
Cycle:Process 1-2 Isentropic compression in low temperature
Compressor. Process 2-3 P: Constant pressure Heat Rejection in low
temperature circuit Process 3-4: Expansion Under Throttling
Process, Isenthalpic Process Process 4-1 P: Constant Heat Addition
Process Process 1-2: Isentropic compression in high temperature
compressor Process 2-3P: Constant pressure Heat Rejection in high
temperature circuit Process 3-4: Expansion Under Throttling
Process, Isenthalpic ProcessProcess 4-1P: Constant pressure Heat
Addition Process8RefrigerantsA refrigerant is defined as any
substance that absorbs heat through expansion or vaporization and
losses it through condensation in a refrigeration system. The ideal
refrigerant would have favourable thermodynamicproperties,
benon-corrosiveto mechanical components, and be safe, including
free fromtoxicityand flammability. It would not cause ozone
depletionor climate change. Since different fluids have the desired
traits in different degree, choice is a matter oftrade off.
Classification of refrigerantsRefrigerants are classified as
follows: Primary refrigerants are those working mediums or heat
carries which directly take part in refrigeration system and cool
the substance by the absorption of latent heat e.g., Ammonia,
Carbon dioxide, Methyl chloride etc. Secondary refrigerants are
those circulating substances which are first cooled with the help
of the primary refrigerants and are then employed for cooling
purposes, e.g., ice, Carbon dioxide etc. These refrigerant cool
substances by absorption of their sensible heat. Properties of
Ideal RefrigerantsA refrigerant is said to be ideal if it has all
of the following properties: -1. Low boiling point and High
critical temperature.2. High latent heat of vaporization and Low
specific heat of liquid.3. Low specific heat of liquid and Low
specific volume of vapour.4. Low specific volume of vapour.5.
Non-corrosive to metal.7. Non-flammable and non-explosive,
non-toxic.9. Low cost.10. Easy to liquidate moderate pressure and
temperature.I l. Easy of locating leaks by suitable indicator,
and12. Mixes well with oil. Designation of Refrigerants: -The
international designation committee of refrigerants uses
Refrigerant or R as the designation followed by certain numbers
(e.g., R-21, R-40, R-30, R-744 etc.)A refrigerant followed by a
two-digit number indicates that the refrigerant is derived methane
base while a three-digit number represents ethane base. 9The
general chemical formula for a compound derived from a saturated
hydrocarbon is given by as: CaHbFcCldWhere, b + c + d=2a+2,and, a=
Number of carbon atoms,b= Number of hydrogen atoms,c= Number of
fluorine atoms,d= Number of chlorine atoms,The complete designation
of the refrigerant is given by:R (a-1) (b+1) (c)Example: In case of
Dichlorodifluoromethane (CCl2F2):a=1, b=0, c=2, d=2So, the
designation is: R (1-1) (0+1) (2) i.e., R-12. Few refrigerants and
their useA refrigerant is a substance used for refrigeration. The
best refrigerant has good thermodynamic properties, is chemically
non-reactive, and is safe. Because some refrigerants can cause
severe damage to the ozone layer, it was decided in 1992 to make it
illegal to release refrigerants into the atmosphere. Refrigerants
used in refrigeration systems are as follows:Refrigerant R11R11 is
a CFC refrigerant, which means it is made of chlorine, fluorine,
and carbon. R11 is typically used in the refrigerators found in
office building and hotel air conditioning systems because it
allows large refrigerators to cool large amounts of water at low
costs. In the past, when air would leak into R11 systems, that air
had to be purged, and usually some of the refrigerant would be
lost. Through newer technological advances and better maintenance,
less R11 has been lost in these large refrigerators. In view of the
global environmental problem resulting from global warming,
depletion of the ozone layer, this CFC refrigerant is currently
being pursued internationally.Refrigerant R22R22 belongs to the
HCFC group of refrigerants, which means it's made of hydrogen,
chlorine, fluorine, and carbon. R22 is the most common refrigerant
on the market as it is used in most residential and commercial air
conditioning systems and even in some large centrifugal
refrigerators. R22 is also pursued internationally for its GWP
(Global warming potential) and ODP (Ozone depletion potential).
Although it is a popular refrigerant, it will be phased out in new
refrigeration equipment that is made in 2010, and it will stop
being produced in 2020. 10Refrigerant R422BR422B is a refrigerant
made by ICOR to be similar to the R22 refrigerant. Like the R22 it
is made for residential and commercial air conditioners. R422B is
an HFC refrigerant, which means that it is made of hydrogen,
fluorine, and carbon. This hydrogen and carbon in refrigerant helps
oil return in those refrigeration systems that have mineral oil or
alkyl benzene in them. R422B won't mix with these oils, but the
hydrogen and carbon allows the oil to thin out and keep moving in
these systems.Refrigerant R717R717 is the refrigerant free from any
halogen atoms. It is named as ammonia. The ammoniawater absorption
refrigerator has been used widely in refrigeration and
air-conditioning applications. R717 has a wide range of
applications. It is particularly suited to working in the range
approximately 0C to -30C and hence is widely used for food
preservation. This includes the chilling of liquids such as milk,
beer and soft drinks, enlarge cold storage facilities, meat
processing and packing plants, large ice-making plants and
commercial refrigeration. Other common applications include large
air conditioning systems (refrigerators), industrial heat
extraction and ice rinks. An advantage of using R717 is its zero
ozone depletion potential and zero global warming
potential.Refrigerant R718R718 is nothing but water. Water can be
used as a refrigerant in refrigerators without any safety
measurement which is cheap, environmentally neutral. Its
maintenance cost is very low since leakages can be accommodated
from the system. There are no extra demands for safety measures or
for skilful operators and no special requirements concerning the
installations components. But the only disadvantage is higher
investment cost (about 200% of a conventional water refrigerator)
and bigger overall dimension.
Environmental Effect of RefrigerantsThe halogenated refrigerants
are a family of chemical compounds derived from the hydrocarbons
(methane and ethane) by substitution of chlorine and fluorine atoms
for hydrogen. The emission of this type of halogen atoms (F, Cl
etc.) are responsible for huge environment impact. Molina and
Rowland [2] first discovered the ozone depleting properties of CFC
and HCFC and by their global warming potential led to the Montreal
Protocol (1987) and the London and Copenhagen amendments (1990,
1992) [3], which is responsible for the end of production of CFCs
by the end of 1995 and of HCFCs by 2030. As figure 1.3 shows, the
production of CFCs and HCFCs has fallen dramatically in the last
few years.
11Ozone layer depletionODP due to artificial chemicals into the
atmosphere was the first major environment impact that was the
after effects refrigeration process. The stability of chlorine
based refrigerants is enough to reach the stratosphere, where the
atoms of chlorine act as a catalyst and destroy the stratospheric
ozone layer (which protects the earth surface from direct UV rays).
About 90% of the ozone exists in the stratosphere layer of earth
surface. The first phase out schedule for the harmful refrigerants
formulated by the Montreal protocol (1987) and was made stringent
during the follow-up international meetings. The ODP values of pure
CFC and HCFC refrigerants are shown pictorially in the figure
[1.3]
Global warming potentialGWP is the second major environment
impact. It is due to the absorption of infrared emissions from the
earth, causing an increase in global earth surface temperature.
While solar radiation at 5800 K and 1360 W/m2 arrives the earth,
more than30% is reflected back into space and most of the remaining
radiation passes through the atmosphere and reaches the ground.
This solar radiation heats up the earth, which approximately as a
black body, radiate energy with a spectral peak in the infrared
wavelength range. This infrared radiation cannot pass through the
atmosphere because of absorption by GHG including the halogenated
refrigerants. As a result, the temperature of atmosphere increases,
which is called as the global warming. During the formulation of
Kyoto protocol, countries around the world have voluntarily
committed to reduce the GHG emissions. HFC refrigerants have
relatively large values of atmospheric lifetime and GWP compared to
chlorine based refrigerants. The GWP values of pure and mixed
refrigerants are illustrated in figure. [3] 12 The Need of
Alternative RefrigerantA refrigerant is a substance used in a heat
cycle usually for enhancing efficiency, by a reversible phase
transition from a liquid to a gas. Traditionally, fluorocarbons,
especially chlorofluorocarbons, were used as refrigerants, but they
are being phased out because of their ozone depletion effects.
Other common refrigerants used in various applications are ammonia,
sulphur dioxide, and non-halogenated hydrocarbons such as propane.
R134a is an inert gas used primarily as a high-temperature
refrigerant for domestic refrigeration and automobile air
conditioners. Contact of R134a with flames or hot surfaces have
toxic and hazardous effect on the humans and environment. So in
this paper, a review of available alternative refrigerants and
their physical and chemical properties have been done. Selection of
efficient, eco-friendly and safe refrigerant for future has been
attempted in this paper through discussions.It is evident that
societies around the globe are demonstrating growing interest and
concern for the environment. In the area of automotive
air-conditioning systems, the technology has evolved to a reliance
on HFC-134a as a stable non-corrosive, non-toxic refrigerant that
avoids adverse impact on the ozone layer. More recently, the
industry has been involved in assessment of refrigerants other than
HFC-134a, motivated primarily by efforts to minimize greenhouse gas
emissions. Typical candidates include carbon-dioxide as well as
members of the hydrocarbon group (usually, propane and
isobutane).The present study was undertaken to assess the relative
advantages of these alternative refrigerants, with specific
emphasis on carbon-dioxide systems. To do so, the study employs the
Total Environmental Warming Impact (TEWI) index as a holistic
measure of the system. The analysis was undertaken with carefully
defined conditions involving two standard production vehicles
representing small and mid-size cars. The simulations were run to
represent vehicle and air-conditioning use in six cities around the
globe using standard vehicle operation cycles. Key assumptions such
as refrigerant emission were made using a range of values cited in
references. In the case of CO2 systems, given lack of adequate
on-road measurements, the effect of approach temperature was also
evaluated with a range of values.Due to several environmental
issues such as ozone layer depletion and global warming and their
relation to the various refrigerants used, the selection of
suitable refrigerant has become one of the most important issues in
recent times. Replacement of an existing refrigerant by a
completely new refrigerant, for whatever reason, is an expensive
proposition as it may call for several changes in the design and
manufacturing of refrigeration systems. Hence it is very important
to understand the issues related to the selection and use of
refrigerants. In principle, any fluid can be used as a refrigerant.
Air used in an air cycle refrigeration system can also be
considered as a refrigerant. However, in this lecture the attention
is mainly focused on those fluids that can be used as refrigerants
in vapour compression refrigeration systems only. 13
Coefficient of Performance (COP)The performance of a
refrigeration system is expressed as Co-efficient of Performance
(COP). It is defined as the ratio of heat absorbed by the
refrigerant while passing through the evaporator to the work input
required to compress the refrigerant in the compressor; i.e. it is
the ratio between heat extracted and work done (in heat units). COP
is highly dependent on operating conditions, especially absolute
temperature and relative temperature between sink and system, and
is often graphed or averaged against expected conditions. The COP
may exceed 1, because, instead of just converting electricity to
heat (which, if 100% efficient, would be a COP of 1), it pumps
additional heat from a heat source to where the heat is
required.C.O.P. = Rn/WWhere, Rn= net refrigerating effect, and W=
work expended in the machine during the same interval of time to
time.Ton of Refrigeration (TR)A ton of refrigeration or TR is a
unit of power used in some countries (especially in North America)
to describe the heat-extraction capacity of refrigeration and
air-conditioning equipment. It is originated from the rate at which
heat is required to be removed to freeze one ton of water and at
zero degree centigrade in 24 hours. 1 TR is equivalent to removal
of 200 BTU of heat per minute and in S.I. units it is rounded off
to 3.5 kJ/s (kW) or 210 KJ/min. Many manufacturers also specify
capacity in BTU/hr especially when specifying the performance of
smaller equipment.
14 Chapter 2Vapour Cascade Refrigeration SystemCascade system
was first used in 1877 by Pick let. Cascade system is just similar
to the binary-vapour cycle used for the power plants. In a binary
vapour cycle, a condenser for mercury works as a boiler for water
as a boiler for water. Similarly, in the cascade system the
condenser for low temperature cycle works as an evaporator for the
high temperature cycle. In cascade system, a series of refrigerants
with progressively lower freezing points is used in a series of a
single stage units. A two stage cascade system using two
refrigerants is shown in figure and its corresponding p-h and T-s
diagram are shown in fig respectively
In this system a cascade condenser serves as an evaporator for
high temperature cascade condenser system and a condenser for the
low temperature cascade system the only useful refrigerating effect
is produced in the evaporator of the low temperature cascade
system. Thus it permits the use of two different refrigerants, with
thermodynamic properties favourable for the two temperature ranges.
Further, the lubricating oil from one compressor cannot be carried
away to another compressor. The temperature difference in low
temperature cascade condenser and high temperature cascade
evaporator is known as temperature overlap.The low temperature
cascade system uses a refrigerant with low boiling temperature
(such asR-13 or R-13BI).There are few advantages of cascade
refrigeration system. The followings are the advantages of cascade
refrigeration systemAdvantages of cascade refrigeration system1. It
also reduces the lubricating problems since the lubricant
associated with each refrigerant has to withstand a temperature
range not more than 60oC, whereas in multistage system, the
lubricant can have to be working over temperature range of order of
105oC.2. Performance of cascade system can be improved through
reducing temperature difference for heat transfer in the
evaporator, condenser and cascade condenser, compare to larger
compressors.3. The performance of cascade system can be enhanced by
reducing the temperature difference for heat transfer in
evaporator, condenser and cascade condenser, and compare to larger
compressors.4. It avoids the problem of sub-atomic pressure which
will octet in the evaporation if a single fluid is used in both the
stages.5. Using a cascade system power consumption can be reduced
through about 9.5%. 15 Chapter 3LITERATURE REVIEW[1] Different
researchers have been carried out them researches on vapour
compression refrigeration system, cascade refrigeration system and
used different refrigerants for the performance analysis of the
system and the refrigerants. Molina et al clarified stratospheric
sink for Chlorofluoromethanes chlorine atom-catalysed destruction
of ozone was that the Chlorofluoromethanes were added to the
atmosphere in steadily increasing amounts. Those components are
chemically inert band may remain in the atmosphere for many years.
Two Chlorofluoromethanes CF2Cl2 and CFCl3, have been detected. Both
CFCl3 and CF2Cl2 absorbed the radiation of ultraviolet. As a
result, they have calculated based on reactions in the gas phase,
this research had been supported by the US Atomic Energy
Commission.[2] Environmental impacts of Halogenated Refrigerants
had been clarified by Sudipta Paul, Achinta Sarkar, and Bijan Kumar
Mandal. A certain percentage of the vapour compression based
refrigeration, air conditioning and heat pump systems continue to
run on halogenated refrigerants due to its excellent thermodynamic
and thermo-physical properties along with the low cost.On the other
hand, the halogenated refrigerants have adverse environmental
impacts such as ozone layer depletion potential and global warming.
This paper reviews the various experimental and theoretical studies
carried out around the globe with environment friendly alternatives
such as hydrocarbons (HC), hydrofluorocarbons (HFC) and their
mixtures, which are going to be the promising long-term
alternatives.CFCS and HCFCS are used as alternative refrigerant.
Natural refrigerant is mainly used. Natural refrigerants are being
used for a long time. HC mixtures and R152a are found to be better
substitutes for R12 and R134a in domestic refrigeration sector.
R290, R1270, R290/R152a, R744 and HC/HFC mixtures are found to be
the best long-term alternatives for R22 in air conditioning and
heat pump applications.[3] The data summary of the Refrigerant was
explained by JAMES M.CALM and GLENN C.HOURAHAN, There were many
refrigerants but R-12 was the most useful refrigerant. The chemical
formula indicates the molecular makeup of the single compound
refrigerants. There were LFT is the lowest concentration which the
refrigerant burns in air. The heat of combustion is an indicator of
how much energy the refrigerant released at the time of burning.
After making the data summary they had decided to change when newer
measurement was made for both specific and different chemical.[4]
Experimental study of new refrigerant mixtures to replace R12 in
domestic refrigerators was clarified by B. Tashtoush, M. Tahat,
M.A. Shudeifat. After the experiment they had decided to change the
R-12 with the hydrocarbon /hydrofluorocarbon refrigerant mixtures.
The results show that butane /propane /R134a mixtures provide
excellent performance parameters, such as coefficient of
performance of refrigerator compression power, volumetric
efficiency, condenser duty, compressor discharge pressure and
temperature, relative to a 210 g charge of R12. In addition, the
results support the possibility of using butane /propane /R134a
mixtures as an alternative to R12 in domestic refrigerators,
without the necessity of changing the compressor lubricating oil
used with R12. On the experimental study, R12 and BPR(M) mixtures
were tested under the same operating conditions using a domestic
refrigerator, designed originally to work with R12.As a result it
was found that domestic refrigerator originally designed to work
with R12, this refrigerant can be replaced successfully by the
BPR(80) mixture without changing the lubricating oil or replacing
the condenser. 16 [5] Performance of mixture refrigerant
R152a/R125/R32 in domestic air-conditioner had been explained by
Jiangtao Wu, Yingjie Chu, Jing Hu, Zhigang Liu. The new mixture
could be regard end as a most likely drop-in substitute for R22 in
many applications. The flammability of this ternary blend was also
studied with an explosion apparatus to prove that it could be used
safely. For the thermodynamically analysis they determined the
optimal mass ratio, the thermodynamic properties and refrigeration
performance of the new mixture with different mass ratios range
from 1% to 98% of each component on a step of 1% were calculated.
According to the measurement procedure described above, the
refrigerant performance of R22, R407C and ternary blend
R152a/R125/R32 with eight different mass ratios were tested. The
intermediate temperature of evaporator, inlet and outlet
temperature of compressor, condenser and evaporator were also
measured. As a result, we can say that new mixture refrigerant,
R152a/R125/R32 with a mass ratio of 48/18/34, was provided in this
work as an alternative to R22, which was widely used in domestic
air-conditioner nowadays and will be restricted to use in the
future.[6] For the The performance of propane/isobutane mixtures in
a vapour-compression refrigeration system Mr. R.N.Richardson and
Mr. J.S.Butterworth had announced that the Hydrocarbons such as
propane (R290, C3Hs) and butane (R600, C4Hao) were used as
refrigerants before the advent of CFCs, although in the open
systems.If the system is designed such that the saturation pressure
is always greater than atmospheric, the danger of a potentially
flammable mixture forming within the circuit should not arise.
There remains, of course, the possibility of leakage, but a
significant loss would be required to produce a flammable
concentration in the immediate vicinity of the leak.A fully
instrumented experimental apparatus was designed to simulate the
operation of a domestic vapour compression system while maintaining
controlled evaporation and condensation conditions. For the
experiment using of R12, propane and a range of propane/isobutane
mixtures with proportions around 50%. The system was purged with
dry nitrogen gas and then send it to purging, evacuating.Evacuating
the hydrocarbons poses no danger provided a 'dry' diaphragm-type
pump is used and the exhaust is vented to atmosphere.[7] On the
basis of Simulation of vapour compression Refrigeration cycle using
HFAC134 and CFC12 was presented by QIYU CHEN and R.C.Prasad. After
analysing the total fact by computer simulation depends upon the
fluid property and Thermo-hydraulic property HFC134 and CFC12 ware
developed. Result indicated that the COP for HFAC134 is slightly
lower than CFC12 system and the power required for a HFAC134.From
the simulation of vapour compression Refrigeration cycle we got
various thermodynamics properties, thermos physical properties,
pressure loss in the evaporator, the condenser and exergy loss for
HFAC134 and CFC12 system.The COP of vapour compression
Refrigeration cycle is an important system. It expressed by COP=Q/W
[Q is the refrigeration effect]. For constant cooling load the cop
is inversely proportional to the compressor work W.W=m (h2-h1).
[Here (h2-h1) is the enthalpy difference from the actual cycle]
mass flow rate (m) is the refrigerant for a given refrigeration
effect is obtained from m=Q/ (h2-h1). The exergy loss evaluated the
thermodynamics performance of a system. The exergy loss analysis is
based on e= (h-h0)-T0(s-s0)Depends upon the COP the power required
and exergy loss the system with HFC134a shows slight detrition in
comparison to CFC12 system. For the same cooling rate, the 3 % of
increasing is effectible. If the cooling rate kept constant. And
increased compressor work result in a reduce COP of the using
HFC134a. 17[8]. Kim and Kim investigated the performance of an auto
cascade refrigeration system using zeotropic refrigerant mixtures
of R744/R134a and R744/R290. The performance was evaluated by both
experiments and computer simulations for various mass fractions of
R744 and several operating conditions. The performance test and
simulation showed that the compressor power increased when inlet
temperature of the secondary heat transfer fluid to condenser was
increased, whereas, the refrigeration capacity and COP decreased
and as the mass fraction of R744 was increased, cooling capacity
and compressor power increased with the decrease in COP. In their
study, they also found that the auto cascade refrigeration cycle
has a merit of low operating pressure as low as that in a
conventional vapour compression refrigeration cycle. They concluded
that natural refrigerants or HFC refrigerants with relatively small
amount of charge could be used as a refrigerant in the auto cascade
refrigeration system. They also mentioned that lower COP of auto
cascade refrigeration cycle was a disadvantage, and the way to
improve it should be sought in the future.[9] Kilicarslan et al.
presented an experimental investigation and theoretical study of a
different type of two-stage vapour compression cascade
refrigeration system using R134 as the refrigerant. When the
calculated refrigeration mass flow rate of single stage systems RU2
was compared with the experimental result, it was observed that the
predictions of theory and experiment results were in close
agreement. It was also observed that the coefficient of performance
in the cascade system was higher than in the single stage system.
There was no benefit from using the cascade system if the economy
was taken into consideration, because the different refrigeration
systems had to be operated simultaneously and the power to drive
both compressors was high.[10] Xuan and Chen experimentally tested
HFC161 mixture (HFC161, HFC125 and HFC143a (10/45/ 45 wt. %)) as an
alternative refrigerant to R502. Their results revealed that the
new refrigerant could achieve a high level of COP than R404A and
R507 and could be considered as a promising retrofit refrigerant to
R502.[11] Wongwises and Chimres presented an experimental study on
the application of hydrocarbon mixtures to replace HFC134a in a
domestic refrigerator. The author used a refrigerator designed to
work with HFC134a in the experiment. The investigated hydrocarbons
used in the work were propane (R290), butane (R600) and isobutane
(R600a). The experiments were conducted with the refrigerants under
the same no load condition at a surrounding temperature of 25C to
record consumed energy, compressor power and refrigerant
temperature and pressure at the inlet and outlet of the compressor.
The same experimental data as well as the distributions of
temperature at various positions in the refrigerator were analysed.
The experiment was carried out by dividing the refrigerant mixtures
into three groups of the mixture of three hydrocarbons, the mixture
of two hydrocarbons and the mixture of two hydrocarbons and
HFC134a. It was concluded from the result that the mixture of
propane and butane of 60% and 40% was the most appropriate
alternative refrigerant to HFC134a.[12] Wongwises et al
experimentally investigated the application of various hydrocarbon
mixtures such as propane (R290), butane (R600), and isobutane
(R600a) to replace HFC134a in automotive air conditioners. From the
experimental results they concluded that the investigated mixture
could successfully replace HFC134a in automotive
air-conditioner.[13] Arora and Kaushik made an energy and exergy
analysis of R502, R404A and R507A in an actual vapour compression
cycle. They observed that the COP and the exergetic efficiency for
R507A were better than that for R404A at condenser temperatures
between 40C and 55C. Both the refrigerants showed 4-17% lower
values of COP and exergetic efficiency than R502 for the same
condensing temperature. It was also noted that the increase in dead
state temperature had a positive effect on exergetic efficiency.
COP and exergetic efficiency of both R404A and R507A improved by
sub cooling of condensed liquid refrigerant and the reversed
happened when effectiveness of liquid vapour heat exchanger was
increased from 0 to 0.1.In that case R507A had better performance
compared to R404A.[14] Mohanraj et al developed a computer program
in which evaporator temperature, condensing temperature, compressor
specifications and properties of various refrigerants were
considered for investigation as an input data. They found that
except for flammability, R152a, R600 and R600 with negligible GWP
compared to R134a were best alternative option. They also stated
that R290 and R1270 could not be used as alternatives due to their
high operating pressures compared to R134a. R152a will reduce the
indirect global warming due to its higher energy efficiency. R152a
offer many desirable characteristics such as low operating
pressure, mass flow rate, and higher COP by about 9%, 40% and 79%
respectively. R152a had approximately the same volumetric cooling
capacity (VCC) with respect to R134a.[15] Dalkilic et al
theoretically studied a traditional vapour-compression
refrigeration system using different refrigerant mixtures (HFC134a,
HFC152a, HFC32, HC290, HC1270, HC600, and HC600a) for various
ratios and their results were compared with possible alternatives
(CFC12, CFC22, and HFC134a). Based on various evaporating
temperatures, the effects of refrigerant type, degree of sub
cooling, and superheating on the refrigerating effect, coefficient
of performance and volumetric refrigeration capacities were also
investigated. Theoretical results showed that the alternative
refrigerants have a slightly lower performance coefficient (COP)
than CFC12, CFC22, and HFC134a for the condensation temperature of
50 C and evaporating temperatures ranging between 30 C and 10 C,
while the refrigerant blends of HC290/HC600a (40/60 by wt. %) &
HC290/HC1270 (20/80 by wt. %) were found to be the most suitable
alternatives tested for R12 and R22 respectively. For a constant
condensing temperature in this analysis it was found that with
increasing in evaporating temperature the COP of the system
increases.[16] Reddy et al performed exergetic analysis of a vapour
compression refrigeration system. The effect of condenser
temperature, evaporator temperature, vapour liquid heat exchanger
effectiveness, sub cooling and superheating on several refrigerants
were determined taking COP and exergetic efficiency of the system
as parameters. During the analysis, it was found that the condenser
and evaporator temperatures have considerable effects on COP and
exergetic efficiency of the system. It was also found that R407C
refrigerant has poor performance, whereas R-134a has the highest
performance in all respect. The results have similarities with
reports presented by Mohan raj et al. (2008) & Sen can et al
(2006).[17] Bolaji et al compared the exergetic performance of a
domestic refrigerator using two eco- friendly refrigerants (R134a
and R152a) with the harmful refrigerant R12. The effects of
evaporator temperature on the coefficient of performance (COP),
exergy flow destruction, exergetic efficiency and efficiency defect
were experimentally investigated. The COP obtained using R152a was
very close to that of R12 with only 1.4% reduction, while that of
R134a was significantly low with 18.2% reduction. Higher exergetic
efficiency and consistently better (lower) overall efficiency
defect were obtained in the case of R152a in the system. The
highest efficiency defects were obtained using R134a as
refrigerant. The experiment showed it is better using R152a than
using R12 and R134a as working fluids.[18] Bolaji et al worked on
the performances of a vapour compression refrigeration system using
three ozone-friendly refrigerants (R32, R152a and R134a). It was
found that R152a has zero Ozone Depletion Potential (ODP) and very
low Global Warming Potential (GWP) & could be used as a
replacement for R134a. The average COP of R152a is higher than
those of R134a and R32 by 2.6 and 17.6%, respectively. The vapour
pressure of R134a was nearly the same with R152a but lower than
that of R32 by 37.2%. 19Heavy compressor is required for using R32
as the mean pressure ratio of R32 was found 25.8% higher than that
of R134a, while R152a had 2.6% lower than that of R134a. It was
also found that the condenser heat load of R152a is close to that
of R134a and the VCC of R32 is lower than that of R134a by
25.2%.[19] K Mani et al improved a vapour compression refrigeration
system by using a new refrigerant mixture (R290/R600a) as drop-in
replacement of CFC12 and HFC134a. It was found that R290/R600a
(68/32 by wt %) mixture was higher in refrigerating capacity than
R12 in the range of 19.950.1% in the lower evaporating temperatures
and 21.228.5% in the higher evaporating temperatures and it was
also higher in the range 28.687.2% in the lower evaporating
temperatures and 30.741.3% in the higher evaporating temperatures
than R134a. Energy consumption of R290/R600a (68/32 by wt %)
mixture was higher in the range 6.817.4% than R12 and 8.9 20% than
R134a. He also showed that the discharge temperature and discharge
pressure of R290/ R600a (68/32 by wt %) mixture was nearly equal to
those of R12 and R134a.[20] Hammad et al studied the performance
parameters of a domestic refrigerator using four ratios of propane,
butane and isobutane (100% propane; 75% propane, 19.1% butane, 5.9%
isobutane; 50% propane, 38.3% butane, 11.7% isobutane and 25%
propane, 57.5% butane, 17.5% isobutane.) As possible alternatives
to the R-12 refrigerant. The parameters investigated are the
evaporator capacity, the compressor power, the coefficient of
performance (COP) and the cooling rate characteristics. It was
found that the 50% propane mixture is most suitable alternative to
R-12 based on both COP and saturated curve match characteristics.
No changes were needed and no defects are detected to the
refrigerators designed for R-12.[21] Jerald et al used five
different configuration of capillaries of diameters 0.033, 0.036,
0.044, 0.050 and 0.30 on a vapour compression refrigeration system
retrofitted with zeotropic blend of refrigerant R404a (alternative
refrigerant) to identify the optimum diameter of capillary which
could be used in the system to give the best performance. The
involved parameters were the Evaporator load (Qe), Coefficient of
Performance (COP), Work done by the compressor (Wc) and
Refrigeration Effect (RE). The results revealed that using the
zeotropic blend R404a provided better cooling capacity, faster pull
down time and better miscibility of oil than R134a which resulted
in the better efficiency in the system. For zeotropic blends the
amount of refrigerant charged was just 600 Gms. When compared to
1kg of R134a to attain the same cooling capacity of the system and
the energy consumed was also 20% less than that of R12 and R134a.
Out of the five capillaries employed in the system, the cooling was
comparatively quick with the capillary having the diameter 0.030
(double) than others. The same experimental set up of vapour
compression system could be operated with hydrocarbons like propane
in future to get better results.[22] This paper firstly presents
the ternary near-azeotropic mixture of HFC-161 as an alternative
refrigerant to R502. The physical characteristics of this
refrigerant is similar to R502. It is eco-friendly. Its ODP is zero
& GWP is smaller than those R502, R404A, and R507. In this case
a reciprocating compressor is used to perform a vapour compression
refrigeration. That reciprocating compressor is used for R404A and
it plays a major role in R502. No extra modification is made in the
system. By two different working method the experimental result
shows that the pressure ratio is nearly equal to the R404A. Under
lower evaporative temperature, its COP is almost equal to that of
R404A and its discharge temperature is slightly higher than that of
R404A, while under higher evaporative temperature, its COP is
greater than that of R404A and its discharge temperature is lower
than that of the latter. This new refrigerant can achieve a high
level of COP and can be considered as a promising retrofit
refrigerant to R502.The physical properties of this new mixture
such as boiling point, critical temperature, critical pressure and
saturation vapour pressure are similar to those of R502. So it can
be used as a retrofit refrigerant.
20[23] Exergy analysis was applied to investigate the
performance of a domestic refrigerator. Originally manufactured to
use 145 g of R134a. The highest exergy destruction occurred in the
compressor followed by the condenser, capillary tube, evaporator,
and superheating coil. There is a method called Taguchi method,
which was applied to design experiments to minimize exergy
destruction while using R600a. Taguchi parameters were selected by
the obtained results from R134a and an experiment using 60 g of
R600a, which indicated similar results as R134a. For the design,
based on the outcomes R600a charge amount, condenser fan rotational
velocity and compressor coefficient of performance were selected.
At the optimum condition, the amount of charge required for R600a
was 50 g, 66% lower than R134a, but that not brings economic
advantages. Compressor modification is strongly recommended to
enhance the system. Furthermore, the amount of total exergy
destruction in optimum condition (0.025 kW) is 45.05% of the base
refrigerator one (0.05549 kW) which confirms the enhancement of the
cycle for 54.95%.By using Taguchi design, the optimum condition was
found to be R600a charge amount of 50 g, compressor coefficient of
performance of 1.82 and condenser fan rotational velocity of 1800.
The amount of total exergy destruction in optimum condition is
45.05% of the base refrigerator one.
[24] R134a is the most widely used refrigerant in domestic
refrigerators. In India, about 80% of the domestic refrigerators
use R134a as refrigerant due to its excellent thermodynamic and
thermos physical propertiesR134a has high GWP of 1300. The higher
GWP due to R134a emissions from domestic refrigerators leads to
identifying a long term alternative to meet the requirements of
system performance. In the present work, an experimental
investigation has been made with hydrocarbon refrigerant mixture
(composed of R290 and R600a in the ratio of 45.2:54.8 by weight) as
an alternative to R134a in a 200 l single evaporator domestic
refrigerator. The tests were continuously performed under different
ambient temperatures (24, 28, 32, 38 and 43 C), while cycling
running (ON/OFF) tests were carried out only at 32 C ambient
temperature. The results showed that the hydrocarbon mixture has
lower values of energy consumption; pull down time and ON time
ratio by about 11.1%, 11.6% and 13.2%, respectively, with 3.253.6%
higher coefficient of performance (COP).Temperature variation in
the evaporator is found to be within 3 K. The miscibility of HCM
with POE was found to be good. HCM also reduce the indirect global
warming due to its higher energy efficiency. Thus, the reported
results prove that the above HCM can be used as an alternative to
phase out R134a in domestic refrigerators.
[25] Refrigeration plays a very important role in industrial,
domestic, and commercial sectors for cooling, heating, and food
preserving applications. This article presents a detailed
experimental analysis of 2TR (ton of refrigeration) vapour
compression refrigeration cycle for different percentage of
refrigerant charge using exergy analysis. Here R22 is used as a
working fluid for different operating condition. The calculations
are made for COP, exergy destruction, and exergetic efficiency for
variable quantity of refrigerant. The present investigation has
been done by using 2TR window air conditioner. The losses in the
compressor are more pronounced, while the losses in the condenser
are less pronounced as compared to other components. The total
exergy destruction is highest when the system is 100% charged &
it becomes least when it is 25% charged. The average COP is highest
when the system is 50% charged and this is because of higher
refrigerating effect and reduced compressor work.This is an
important tool in explaining the various energy flows in a process
and in the final run helps to reduce losses occurring in the
system. The system comprises of four components, i.e., compressor,
a capillary tube (expansion device), a condenser, and an evaporator
and is having a cooling capacity of 24K BTU. The exergy efficiency
of the system varies from 3.5 to 45.9% which is mainly due to the
variation of evaporator temperature. When the actual requirements
are less, the system should be operated with variable refrigerant
flow so as to achieve optimum balance between the exergy efficiency
and energy saving.
[26] In this study, exergy analyses of vapour compression
refrigeration cycle with two-stage and intercooler using
refrigerants R507, R407c. Here R404A is carried out. The
coefficient of performance, exergetic efficiency and total
irreversibility rate of the system in the different operating
conditions for these refrigerants were investigated. All these are
calculated by Solkane program. Its observed that COP increases when
evaporator temperature increases for all refrigerants and COP
decreases when the condenser temperature increases.
21Irreversibility values attained due to variation of evaporator
temperature have reached the highest values in the evaporator when
condenser temperature has been kept constant at 35 C in the system
which uses each three alternative refrigerants. However, when
evaporator temperature has been kept constant at -10 C,
irreversibility values calculated due to variation of condenser
temperature have reached the highest values in evaporator in each
system using R507, R407c and R404a alternative refrigerants. It is
observed that total irreversibility rate depends on evaporator
temperature change. The procedure applied in this study can be
carried out for a number of other refrigerants and actual cycles.
So, its concluded that the best way to improve irreversibility can
be achieved with determination of optimum operation conditions.
[27] In this paper, the influence of the main operating
variables on the energetic characteristics of a vapour compression
plant, based on experimental results, is addressed. The
experimental tests are performed on a single-stage vapour
compression plant using three different working fluids, R134a,
R407C and R22. Main experimental results obtained by the
performance characteristics followed to analyse the energetic
performance are the refrigerating capacity and the power
requirements of the reciprocating compressor, presenting and
discussing in this work. The evaporating pressure, condensing
pressure and superheating degree of the vapour on the energetic
performance of an experimental refrigeration plant using three
different working fluids has been studied. It follows that the mass
flow rate evolution is mainly governed by the compression ratio,
and especially by the evaporating pressure.Analysing the
refrigerating capacity, and considering the negligible
modifications of the specific refrigerating effect, it reaches the
conclusion that the mass flow rate evolution becomes the most
important influence on the refrigerating capacity behaviour. The
refrigeration plant consumption working with R22 tends to decrease
more slowly with increasing compression ratios than using the other
working fluids. This fact is transferred to the COP, obtaining a
smaller value of the COP using R22 than using R407C for high
compression ratios.
[28] This paper provides a comparison of the operating
performance of three alternative refrigerants for use in a vapour
compression refrigeration cycle. The refrigeration capacity and COP
of R401A, R290 and R134A were compared with those of R12 when used
in a propriety vapour compression refrigeration unit initially
designed to operate with R12. The performance of R134a is very
similar to that of R12 justifying the claim that it is a drop in
replacement for R12 but of the refrigerants tested it gave the
poorest performance. When viewed in terms of greenhouse impact
however R290 showed the best performance. The cooling capacity of
R290 (propane) was the largest of the refrigerants tested, and
higher than the original refrigerant R12.R290 represents an
attractive alternative to existing CFCs in small domestic
refrigerators, subject to correct technical application of
operational and safety factors. The refrigerant R401a displayed a
level of performance for both capacity and COP. The substitution of
this refrigerant would allow the original R12 to be disposed of in
an environmentally sensitive way but an economic analysis of a
retrofit must compare the projected lifetime service and
maintenance costs for the system with the original R12 and R401.
R134a is considered to be the preferred HFC replacement for R12.
The lubrication requirements make the substitution of this
refrigerant less straightforward than the case with R290 and R401a
so it would not be the preferred choice unless other circumstances
prevented the use of the other refrigerants.
[29] Xu and Clodic conducted an exergy analysis on a vapour
compression refrigeration system using R12, R134a and R290 as
refrigerants. This experiment was done developing a mathematical
model for carrying out exergy analysis. This exergy analysis had
been done by the refrigerants or freezers i.e. R12, R134a, and R290
to illustrate various exergy losses in various components and for
potential improvements. By this analysis method they had been
localized the exergy losses in refrigeration system and reduced
them. The exergy losses were mainly occurred in compressor and
evaporator in this system. Finally, they got the results that R134a
refrigerator is almost efficient than R12 but for freezers R134a
and R290 is less efficient than R12. These two refrigerants had
some problem i.e. they could not achieve same performance like R12.
22[30] Padmanabhan and Palanisamy conducted an experiment in vapour
compression refrigeration system of an air conditioner to replace
the refrigerant R22 with few environment friendly refrigerants
R134a, R290 & R407c. It is observed that R290 is best
refrigerant among the others but it highly flammable. So R407c
could be used to replace R22. They also observed that the COP of
the system when refrigerant R290 is used was higher than that of
other refrigerants and the total irreversibility of the system is
higher when R134a is used as main working fluid in the system. They
also found that the EE of system is maximum when R290 is used. It
had been also observed that those refrigerants are cheaper with
zero ODP & moderate GWP compared to R22. But R290 had a better
potential. For being highly flammable, R290 cannot be used in a
safe manner in refrigeration system & air conditioning purpose
and for this R 407c could be used.[31] Lee and SU had been done an
experiment on domestic refrigeration system by used isobutane
(R600) as a refrigerant. This experiment was done by an
experimental set up of vapour compression refrigeration system. The
expansion & heat transfer components of the system were
capillary tubes & plate heat exchangers respectively and the
refrigeration temperature was set about 4C to 10C to simulate the
situations of the two applications; one is cold storage and another
is freezing.In cold storage application used two capillary tubes in
parallel that gave better performances than single tube. So COP is
higher in cold storage than freezer application. In normal
condition Refrigeration capacity (QRC) increases with inlet
temperature of brine (TBi) but the volumetric rate flow of the
brine (VB) is decreases but in extreme condition variations are
slight. Naturally it found that in freezing application QRC
decreases with increasing inlet temperature of cooling water (TC).
But in cold storage with single tube the effect was reversed but if
two tubes were used the effect was as same as freezing application.
In cold storage application QRC also decreases with length of
capillary tubes (L) while single tube used but when two tube used
the effect would be reversed and similar effect showed on freezing
application. Ultimately they found that cold storage application
performed better than freezing when two tubes was used.[32]
Baskaran and Koshy experimentally analysed the performance of
vapour compression refrigeration system by using eco-friendly
refrigerants and compared with the performance of the system when
R134a used. This experiment was done developing a simulation model
in software CYCLE_D4.0. The alternative refrigerants used in this
analysis were HFC152a, HFC32, HC290, HC1270, HC600a and RE170.
Among those refrigerants RE170, R152a and R600a gave a higher
performance coefficient than R134a in a specific temperature of
condenser and evaporator. They concluded that RE170 was the
alternative refrigerant of R134a. They found that refrigerant type,
degree of sub cooling degree of superheating has some effect on
refrigerating effect, COP and volumetric refrigeration capacity for
various evaporating temperatures. So ultimately they concluded that
RE170 was most suitable refrigerant comparison to R134a for better
COP, pressure ratio and also evaporating impacts of ozone layer
depletion and global warming.[33] Soni and Gupta numerically
simulated theoretical vapour compression refrigeration cycle using
R404A, R407C and R410A as refrigerants.
23They developed a computational model based on exergy analysis.
They concluded that the COP and exegetic efficiency of R407C were
better than that of R404A and R410A. It was found that COP and
exergy efficiency improved when sub cooling of high pressure
condensed liquid refrigerant was done. They also concluded that if
dead state temperature increased exegetic efficiency will increase
and exergy destruction ratio will reduce while coefficient of
performance will remain constant. With the increase in
effectiveness of liquid vapour heat exchanger, COP and exegetic
efficiency decreased though exergy destruction ratio increased as
reported by the authors.[34] Parekh and Tailor conducted a
thermodynamic analysis on cascade refrigeration system using
R12-R13, R290-R23, R 404-R23 refrigerant pairs. This analysis is
performed by two-stage cascade refrigeration system with some
thermodynamic assumptions. The operating parameters varied in that
analysis are evaporator temp, condenser temperature, temperature
difference in cascade condenser and low temperature condenser which
had an effect on performance parameters such as COP, exegetic
efficiency and refrigerant mass flow rate. They observed that COP
of system when R290-R23 refrigerant pair was used is maximum when
evaporating temperature varied from -80C to -60C. They found that
COP decreases when condenser temperature varied from 25C to 45C.
Similar trend is found when temperature difference in cascade
condenser varied from 2C to 6C. They also mentioned that COP of the
system increases when condenser temperature varied from -5C to -35C
in lower temperature cycle.[35] Fiori and Linba presented a paper
on a thermodynamic analysis of a cascade refrigeration system using
the refrigerant pair R22-R404a where R22 worked as working fluid in
high temperature circuit and R404a in low temperature circuit. This
analysis obtained an optimal value for COP of the cycle considered
the temperature of LT. The operating parameters was evaporation
temperature, condensing temperature and difference between
condensing temperature of LT & evaporating temperature of HT.
It had been obtained that the COP had a maximum value at the
intersection of COP curves of each circuit. But it was not possible
to get maximum COP because the intermediate temperature was very
low.[36] Alhamid et al. conducted an Energy and Exergy analysis on
cascade Refrigeration system using carbon dioxide and
ethane-propane as refrigerant (R-744 + R170-R290). They assumed
that compression process was non isentropic, isenthalpic expansion
and negligible changes in kinetic and potential energy. They also
took the dead state temperature at 25C and 101.3 kPa, mechanical
efficiency of each compressor is 0.95 and difference between
refrigerated space temperature and evaporating temperature is 5C.
They found that an optimal temperature of cascade condenser can
obtained for a specific system and in operating conditions in
energy exergy optimization methods. They also evaluated COPmax and
mass flow ratios using multi linear regression method.[37] Tripathy
et al. conducted a numerical simulation on a cascade refrigeration
system using refrigerants as carbon dioxide and Ammonia (R744,
R717) as the main working fluid in the system. They assumed that
condenser and cascade condenser at subcooled state and that of
evaporator at superheated state. 24In this work they found two
co-relations of optimum condensing temperature and COPmax with
condensing temperature, evaporating temperature and temperature
difference between cascade condensers by these two relations they
determined the optimum condensing temperature and copmax .[38]
Sachdeva et al. investigated for the best substitute of R-12 on
vapour compression cascade refrigeration system. Refrigerants runs
in high temperature circuit are Ammonia (R717), Propane (R290),
Propylene (R1270) R404A and Dichlorodifluoromethane (R12) and in
low temperature circuit Carbon dioxide (R744) is used as working
fluid. They assumed that the compressors isentropic efficiency will
be given for both high and low temperature compressors. They
neglected the pressure loss in pipe networks and changes in kinetic
and potential energy. After the end of their investigation they
found Ammonia is the best alternative of Carbon dioxide.[39] Xu et
al. presented a project on novel low absorption compression
refrigeration system using mixture of refrigerants. In this
experiment they assumed that suction temperature, condensing
temperature and temperature of top and bottom outlets of
rectification column were specified. They neglected the pressure
losses and the heat losses. They also specified volumetric
efficiency and isentropic efficiency off the compressor. They
obtained the cooling range between - 60 C to -140C.[40] Yamaguchi
et al. investigated the dry ice blockage in an ultra-low
temperature of cascade refrigeration with working with carbon
dioxide (R744). They found in this visual experiment that dry ice
sedimentation occurs in low flow velocity and dry ice is
responsible for complicated behaviour of CO2.[41] Yan et al.
conducted a research on performance of an internal auto cascade
refrigeration system (IARC) using R290/R600 or R290/R600a as
refrigerants. They assumed the isentropic efficiency of the
compressor is related to its pressure ratio. They also neglected
the pressure drop and heat losses. They also assumed isenthalpic
throttling in capillary tubes and irreversible compression in the
compressor. They concluded that there is a 7.8 to 13.3% increase in
efficiency for IARC then conventional refrigeration system when
R290/R600a is used.
Objective:The aim of this study is to investigate first law and
second law analysis of mechanical vapour compression refrigeration
system using various refrigerants based on energy and exergy
concept. Various parameters, like COP, required compressor power,
total exergy loss, mass flow rate and exergy efficiency are
computed in this work. Values of some parameters have been assigned
from the literature. The final aim is to choose one or more
alternative refrigerants which can replace CFC12 without
sacrificing much loss in the performance of the refrigeration
system.
25 Chapter 4MATHEMATICAL FORMULATION:1. Description of the
proposed model:A vapour cascade refrigeration system is basically
consist of a one evaporator, two compressors, one condenser, one
cascade condenser and two expansion valve as shown in fig. 1. The
quantity of heat, Q1 taken at low pressure, P3 in the evaporator to
evaporate the liquid refrigerant by taking heat from surrounding.
Then it passed through a compressor of isentropic efficiency, s,
where it is compressed by means of mechanical work, Wc1 on the
system for increasing the pressure of the vaporized refrigerant
from P3 to P4 (condenser pressure). Then, this vaporized high
pressure refrigerant goes to cascade condenser and reject heat to
the low temperature circuit. From this low temperature refrigerant
evaporated and went to the 2nd compressor at pressure P7. Then at
compressor by means of mechanical work Wc2 on the system for
increasing the pressure P7 to P8 (condenser pressure). Then the
refrigerant from compressor to condenser, where it is condensed.
Then condensed refrigerant from cascade condenser enters into the
expansion valves, where the pressure decreases without any loss in
enthalpy. Then the high temperature circuit liquid refrigerant
enters again into the evaporator for running the cycle again.
Fig: 1 Schematic diagram of the vapour-cascade refrigeration
system2. Thermodynamics of the system:Energy and exergy analysis
need some mathematical formulations for the vapour-cascade
refrigeration system. In the vapour-cascade refrigeration system,
there are five major components namely, evaporator, compressor,
cascade-condenser, condenser and expansion valve. Various
calculations are done based on this system using alternative
refrigerants. Coefficient of Performance (COP) of vapour-cascade
refrigeration system is a very important creation for performance
indicator. 26It expresses as-COP= Refrigeration effect / Compressor
work = Q / WWhere Q is the refrigeration effect and W is the
compressor work. This above said two parameters can be calculated
asTCC=cascade-condenser temperature,TC= condenser temperature,TE=
evaporator temperature From T1 we find that, h1, Sg1Sg1=Sg2+Cpln
(T2 / Tc+273)From here we find T2,h2s = hg at Tcc+ Cp (T2-Tc.c), h2
= h1 + (h2s h1) / compressorQ1= (h1-h4),Q2= (h2-hf3),Q2= (h2-hf3)
Where = effectiveness, Taking hf3=h4As it is a cascade-condenser
then,(h2- hf3) = h5-h8From cascade-condenser temperature (TCC),We
get h5, Sg5Sg5=Sg at Tcc+ Cp ln (T6 / Tc+273), H6= hg at Tc+Cpg
(T6-Tc)From condenserQ2= h5-h8 and taking h8= hf7, COP= (mhQ1+mlQ2)
/ (W h+ Wl)Where, Wh= Compressor work done of High Temperature
circuit.Wl= Compressor work done of Low Temperature circuit.And
taking, mh= ml = m = 1kgRefrigeration Effect (R.E) = mh(h1-h2) + ml
(h5-h8)Total Compressor workWcompressor= W h+ Wl= mh(h2-h1) + ml
(h5-h6)Efficiency of exergetic energy (exergetic) = Wrev/ Wact
Wrev= QE [(TC / TE)-1] 27 Chapter 5Results and discussion:In
this project we calculated the co-efficient of performance,
compressor work, refrigerating effect, efficiency of vapour cascade
refrigeration system (R12 in high temperature circuit and R404A in
low temperature circuit). These results are discussed below. Here
is some assumption about some parameters as per given below-Case
1Tevaporator=400C, T cascade=50CCompressor efficiency=65% (for both
the condenser) Effectiveness of the cascade heat exchanger=75% And
mh=ml=m=1[mh=mass flow rate at high temperature circuit, ml=mass
flow rate at low temperature circuit)Case 2Tevaporator=400C, T
cascade=100CCompressor efficiency=65% (for both the condenser)
Effectiveness of the cascade heat exchanger=75% And
mh=ml=m=1[mh=mass flow rate at high temperature circuit, ml=mass
flow rate at low temperature circuit).Piping losses, loss in the
condenser, cascade heat exchanger neglected in both the
cases.Effect of evaporator temperature on COP: Co-efficient of
performance is a vital parameter in Vapour cascade refrigeration
system. It is expressed the system performance. The variations of
COP of the system using refrigerants R-12 in high temperature
circuit and R-404a in low temperature circuit against evaporator
temperature -10to 00C and the condenser temperature have been shown
in figure. It is seen from figure that, as the evaporator
temperature increases then COP of the system increases for the
investigated refrigerants. If the cascade condenser decreases, then
the COP of the system increasesEffect of evaporator temperature on
compressor work: Compressor is the heart of mechanical vapour
cascade refrigeration system as it circulates the refrigerant the
system like the heart of a human being circulating the blood in the
body. Input in the compressor is provided to increase the pressure
of the refrigerant. As we increase the evaporator temperature from
-10c to 0c then the compressor work decreases. It has a
relationship with cascade heat exchanger temperature also. As the
cascade condenser temperature decreases compressor work increases.
The results are plotted in the graphs below. 28Effect of evaporator
temperature on refrigerating effect:The refrigerating effect is the
main measurement of the total work done by the cascade
refrigerator. The refrigerating effect varies proportionally with
the evaporator temperature. As the evaporator, temperature
increases the refrigerating effect increases. It has an inverse
relationship with the cascade condenser temperature. As the cascade
condenser temperature increases, the value of the refrigerating
effect also increases. The refrigerating effect Vs evaporator
temperature curves are plotted be
Effect of evaporating temperature on exergetic efficiency: The
exergetic efficiency indicates the utilization capacity of the
available energy by the system it permits to identify and calculate
the various exergy losses in different components. The exergetic
efficiency increases with the evaporator temperature. It has an
inverse relationship with cascade condenser temperature. As the
cascade condenser temperature decreases the exergetic efficiency
increases. 29Chapter 6
Conclusion The coefficient of performance of the cascade
refrigeration system (R-12 &R-404a) increases with the decrease
in the cascade condenser temperature. The cop of the system
decreases with the decrease in the evaporator temperature. The
compressor work increases with the decrease in the evaporator
temperature. The compressor work decreases with the decrease in the
cascade condenser temperature. Refrigerating effect of the system
increases with the increase in the evaporator temperature. It also
increases with the decrease in the cascade condenser temperature.
The exergetic efficiency decreases with the decrease in the
evaporator temperature. The exergetic efficiency has an inverse
relationship with the cascade condenser temperature. It increases
when the cascade condenser temperature decreases. For the 5C
decrease in evaporator temperature the COP increases 5.67%. The
compressor work increases 2.22% with the 5C increase evaporator
temperature. If the evaporator temperature is increased by 5C, then
the refrigerant effect will decrease by 1.9%. The exergetic
efficiency decreases 3.6% with 5C increase in evaporator
temperature.SCOPE OF FUTURE WORK: This work can be extended, future
trends and research direction keeping on mind as following acts
mentioned below: -1.Develpoment of computer software code to
determined different types of refrigerant properties.2. Hunt for
the alternative refrigerants without hampering the COP can be added
to this work3. Exergy analysis can be done to each components of
the system.4. More refrigerants and mixture of refrigerants can be
used as the working substance. 5. Actual cycle analysis can be done
considering the volumetric efficiency of the compressor and
pressure loss in the system.
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