A capillary tube is widely used as throttling device in small sized refrigeration and air - conditioning applications having capacity less than 3 TR. This research paper provides a set of capillary tube performance data in a vapor compression refrigeration system using R - 134a as working fluid. Several capillary tubes with different length and inner diameter were selected as test sections. Mass flow rate and Pressure drop through capillary tube was measured for several inlet temperatures of each capillary tube. The sub cooling and superheating temperatures are maintained constant throughout the experimentation. Experimental condit ions for the condensing temperatures were selected from 38 to 54� C in the interval of 2� C. The effect of above given parameters on the Pressure difference,Power input,Evaporating capacity and Coefficient of performance for R - 134a through the helically coiled capillary tube has been analyzed.
The COP of the refrigeration increasing the performance and to get high efficiency of the refrigeration system. By using nano coating over the evaporator of the refrigeration component the objective can be achieved. The improper heat dissipation occurred in the heat exchanger components causes effect in performance. The vapour compression refrigeration system consuming the high power. Though the energy taken for the refrigeration process has increased and leads to more power consumption. In order to increase the performance, Nano coating Copper Oxide has been applied over the evaporator. By applying the Nano coating Copper Oxide over the evaporator the COP increased. In result the energy required for the refrigeration process and global warming problems has been reduced. By addition of nanoparticles to the refrigeration results in improvements in the COP of the refrigeration, thereby improving the performance of the refrigeration system. In this experiment the effect of using CuO-R134a in the vapour compression system expected COP will be increased by 5% with nano coating.
There are many applications where
refrigeration plant is required to meet the various refrigerating
loads at different temperatures. For example, systems for hotels,
large restaurant, institutions and food preservation industries. In
these cases, it is necessary that each location is cooled by separate
evaporators to maintain the particular temperature and produce
the required refrigeration load. Hence it requires different
refrigerating units with single evaporator for each location.
Instead it will be beneficial to use a refrigerating unit with
multiple evaporators working at different temperatures.
Therefore, it is the purpose of this paper to introduce vapor
compression system which uses a single compressor and
individual expansion devices to provide the concurrent testing.
Also we have to analyse the performance of the refrigeration
system when different refrigerants are used in the same system
with changing suction and discharge pressure. The performance
parameters will be COP & the refrigerating effect obtained at
evaporator.
Project report on vcr system with liquid suction heat exchangerSant Lal Patel
vapour compression refrigeration system with liquid suction heat exchanger is benificial for engineering students .it is a final year project of mechanical engineering.
Presentation of Refrigeration SimulationShafiul Munir
This presentation is the aftermath of a laboratory experiment to understand the refrigeration cycles and functions in detail. It also shows the various uses and modifications refrigeration system accounts to.
The COP of the refrigeration increasing the performance and to get high efficiency of the refrigeration system. By using nano coating over the evaporator of the refrigeration component the objective can be achieved. The improper heat dissipation occurred in the heat exchanger components causes effect in performance. The vapour compression refrigeration system consuming the high power. Though the energy taken for the refrigeration process has increased and leads to more power consumption. In order to increase the performance, Nano coating Copper Oxide has been applied over the evaporator. By applying the Nano coating Copper Oxide over the evaporator the COP increased. In result the energy required for the refrigeration process and global warming problems has been reduced. By addition of nanoparticles to the refrigeration results in improvements in the COP of the refrigeration, thereby improving the performance of the refrigeration system. In this experiment the effect of using CuO-R134a in the vapour compression system expected COP will be increased by 5% with nano coating.
There are many applications where
refrigeration plant is required to meet the various refrigerating
loads at different temperatures. For example, systems for hotels,
large restaurant, institutions and food preservation industries. In
these cases, it is necessary that each location is cooled by separate
evaporators to maintain the particular temperature and produce
the required refrigeration load. Hence it requires different
refrigerating units with single evaporator for each location.
Instead it will be beneficial to use a refrigerating unit with
multiple evaporators working at different temperatures.
Therefore, it is the purpose of this paper to introduce vapor
compression system which uses a single compressor and
individual expansion devices to provide the concurrent testing.
Also we have to analyse the performance of the refrigeration
system when different refrigerants are used in the same system
with changing suction and discharge pressure. The performance
parameters will be COP & the refrigerating effect obtained at
evaporator.
Project report on vcr system with liquid suction heat exchangerSant Lal Patel
vapour compression refrigeration system with liquid suction heat exchanger is benificial for engineering students .it is a final year project of mechanical engineering.
Presentation of Refrigeration SimulationShafiul Munir
This presentation is the aftermath of a laboratory experiment to understand the refrigeration cycles and functions in detail. It also shows the various uses and modifications refrigeration system accounts to.
Basics of refrigeration engineering section bAkshit Kohli
i hope, it will helpful to the students and peoples in the search of topics mentioned
it is informative to study to even get passing marks or for revision
Ijri te-03-011 performance testing of vortex tubes with variable parametersIjripublishers Ijri
Conventional refrigeration system is a type of refrigeration systems which are costly; noisy, harmful gases released from a machine based on application of this type of system and it is required more maintenance. So, we need to go for unconventional refrigeration systems like vortex tube refrigeration system, which produce less vibrations and which require less maintenance and which are noiseless. It is required for our mechanical engineers to look for enhancing the performance of such vortex tubes. So as a part of my project work, I have chosen various sizes of vortex tubes and test their performances for finding out optimum performance. We will be testing the performance of vortex tubes with different ‘l/d’ ratios and different cold fractions, with different pressures and different nozzle sizes.
Basics of refrigeration engineering section bAkshit Kohli
i hope, it will helpful to the students and peoples in the search of topics mentioned
it is informative to study to even get passing marks or for revision
Ijri te-03-011 performance testing of vortex tubes with variable parametersIjripublishers Ijri
Conventional refrigeration system is a type of refrigeration systems which are costly; noisy, harmful gases released from a machine based on application of this type of system and it is required more maintenance. So, we need to go for unconventional refrigeration systems like vortex tube refrigeration system, which produce less vibrations and which require less maintenance and which are noiseless. It is required for our mechanical engineers to look for enhancing the performance of such vortex tubes. So as a part of my project work, I have chosen various sizes of vortex tubes and test their performances for finding out optimum performance. We will be testing the performance of vortex tubes with different ‘l/d’ ratios and different cold fractions, with different pressures and different nozzle sizes.
Experimental Analysis of Refrigeration system using Microchannel condenser & ...AM Publications
Micro channel condenser now days can be effectively used due to its compact size in automobile sector. For
its performance, refrigeration set up designed to detect experimental performance of microchannel condenser. In this
paper performance analysis of microchannel condenser compared with round tube and coil tube. In analysis of
microchannel condensers it can be found more effective at various loads and operating conditions. For review same size of
microchannel and round tube condenser are considered. From the previous experiments the micro-channel condenser was
made to have nearly an identical face area, depth and fin density as the round-tube condenser which was the baseline. Also
varying the refrigerants, C.O.P & Efficiency of micro channel the various reviews of reviewer micro channel condenser
can be efficient and also refrigerator system requires less power.
Experimental investigate to obtain the effectiveness of regenerator using Air.IJESFT
The regenerator is a kind of heat exchanger that provides a way to get the gas to the low temperature with as much potential work (cooling power) as possible without carrying a lot of heat with it. It doesn’t put heat in or out of the system but it absorbs heat from the gas on one part of the pressure cycle and returns heat to the gas on the other part.
More recent applications of regenerators in cryogenic systems can be found in small cryogenic refrigerators (cryocoolers). Systems such as the Stirling Gifford-McMahon, pulse tube, Solvay, Vuilleumier and magnetic cycle refrigerators all use either a static or rotary regenerator. In fact, the success these coolers have achieved is directly related to the characteristics of compact size and efficiency of the regenerator.
Regenerator effectiveness of 99% results in 21% loss of refrigeration effect, similarly regenerator effectiveness of 98% results in 42% loss of refrigeration effect, with refrigeration effectiveness of 95.238% the loss of refrigeration is 100%. i.e. no net cooling is produced.
In cryogenic applications the regenerator is typically made up of 100 to 500 meshes SS 304, Phosphorous bronze screens or small lead spheres (150 to 300 micro meters) are used, that are tightly packed together and held in place on either end in the same manner.
To develop experimental setup at our laboratory level by using air as working fluid and find out the effectiveness of various regenerative materials is basic goal of this work.
Experimental Optimization of Capillary Tube in Domestic Refrigeratorpaperpublications3
Abstract: This paper describes the experimental optimization of capillary tube for choosing best suitable capillary in domestic refrigerator and comparison in performance of two different refrigerants (R134a and R600a). This experiment deals with optimization performance testing for a domestic refrigerator using experimental method.
Experimental Investigation of Water Cooler Test Rig Using R-22 as RefrigerantIJMERJOURNAL
ABSTRACT: This paper describes Water Cooler; a tool that aggregates shared internal social media and cross-references it with an organization’s directory. We deployed Water Cooler in a large global enterprise and present the results of a preliminary user study. Despite the lack of complete social networking affordances, we find that Water-Cooler changed users’ perceptions of their workplace, made them feel more connected to each other and the company, and redistributed. Water coolers work on vapour compression refrigeration cycle. The behavior of performance parameters of a simple vapour compression refrigeration system were studied while it’s working under transient conditions occurred during cooling of a fixed mass of brine from initial room temperature to sub-zero refrigeration temperature. The effects of different lengths of capillary tube over these characteristics have also been investigated. The main advantage of our project is to cool the water with help of test rig.
an experiment on a co2 air conditioning system with copper heat exchangersINFOGAIN PUBLICATION
This paper presented an experiment on a CO2 air conditioning system with copper heat exchangers. In this study, the compressor and cooler were tested with hydraulic method to determine the deformed and torn temperatures. The results show that conventional compressor is not suitable for using high pressure, due to the COP of cycle is very low (0.5 only). With CO2 compressor, the cycle can be achieved COP of 3.07 at the evaporative temperature of 10C. This value equals with COP of commercial air conditioning system presently.
NUMERICAL ANALYSIS OF DOUBLE INLET PULSE TUBE REFRIGERATORNetha Jashuva
Pulse Tube cryocooler or Pulse Tube Refrigerator (PTR) is a compact refrigerator which is capable of attaining a cryogenic temperature below 123 K (-150 K). As there are no moving components at low temperature side of PTR, it attracts the attention of various researchers. The advantages are mainly its simplicity, low vibration at cold end side, low cost, long life span and ease of manufacturing. With the tremendous development in the performance of PTR and due to its compactness, PTR has a wide range of applications like infrared sensors, aerospace, night vision equipments, communication, micro-biological sciences, superconductivity, in medical science and SQUID. In this present work, modeling and numerical simulation is carried out for Double Inlet Pulse Tube Refrigerator (DIPTR). There are various types of PTRs on the basis of way of their development stages. DIPTR is the modification of Orifice Pulse Tube Refrigerator (OPTR), by simply adding one more valve in between the hot end side of pulse tube and inlet to the regenerator. This arrangement is very much useful to prevent the flow of large amount of gas into pulse tube through the regenerator as in case of OPTR. Here, a two dimensional (2D) model of DIPTR is created using ANSYS Design Modeler and Computational Fluid Dynamics (CFD) solution approach is chosen for numerical simulation purpose. The detailed study on cool down behavior at cold end of DIPTR, pressure variation at inlet and also heat transfer has been performed using CFD package FLUENT software (ANSYS FLUENT 15.0.0). Four numbers of cases have been chosen in which the pressure User Defined Functions (UDFs) are different and all other parameters remain unchanged. Pressure UDFs are applied at inlet as a boundary condition to define the oscillating motion of piston inside the piston-cylinder arrangement. The four pressure UDFs are of different wave forms such as Sinusoidal, Rectangular, Triangular and Trapezoidal. Pulse tube dimension is taken as 15 mm diameter and 250 mm length. The regenerator and other heat exchangers are specified as porous zones with a porosity of 0.6. The operating frequency for all cases is 2 Hz. After simulation using four pressure UDFs, it has been found that pressure UDF generating triangular pressure wave is more efficient than other pressure UDFs and a temperature of 111 K is obtained using triangular wave form of pressure.
This paper describes an experimental study of using the waste heat from a Panasonic Under-
Ceiling split room air - conditioner had a rated capacity of 3.51 kW (12,000 Btu/h). An under – ceiling
split type air conditioning for heating domestic water in private homes. Energy recovery improved the
performance, and the recovered energy could replace electricity completely for heating domestic water
use. An extra charge of refrigerant in the air-conditioner could prevent its compressor from over heating
during energy recovery. The experimental conducted on varies capacity of the range from 22.5 litres to
120 litres storage tank. Results show the water temperature increased lies in the range of 50 OC to 65
OC. It was found that, when the initial water temperature in the 22.5 litres storage tank 27 OC, the water
temperature reached 65 OC in 105 minutes. For 120 litres water, temperature increased from 27 OC to 62
OC,5 in 240 minutes.
Comparative Analysis of Forced Draft Cooling Tower Using Two Design Methods A...YogeshIJTSRD
Cooling towers make use of evaporation whereby some of the water is evaporated into a moving air stream and subsequently discharged into the atmosphere which results in cooling of the remainder water. The current research reviews various studies conducted on cooling tower using experimental and numerical techniques. Different design configuration and operating conditions on cooling towers are evaluated by various researchers. Significant findings from researches have shown new and improved design of cooling tower with much better performance as compared to conventional design. Neetish Kumar Sao | Dr. Surendra K. Dwivedi "Comparative Analysis of Forced Draft Cooling Tower Using Two Design Methods: A Review" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-5 | Issue-5 , August 2021, URL: https://www.ijtsrd.com/papers/ijtsrd45100.pdf Paper URL: https://www.ijtsrd.com/engineering/mechanical-engineering/45100/comparative-analysis-of-forced-draft-cooling-tower-using-two-design-methods-a-review/neetish-kumar-sao
Similar to ANALYSIS OF VAPOR COMPRESSION REFRIGERATION SYSTEM WITH DIFFERENT CONFIGURATIONS OF CAPILLARY TUBES USING R134A AS REFRIGERANT (20)
Since so many years a problem occurs in KSB Pump Va mbori for casting process i.e. cracks occurs in the castings & it is repeated one. Therefore the compan y has given opportunity to me to solve this problem . In case of steel casting there are mainly cracks & also blo w holes induced due to the casting procedure. There are many factors for the casting defects .The factor is unev en material feeding in casting & also due to the mo uld material & also the core material. These cracks finally brea k directly the component of the casting i.e. in cas e of pump the casting component is like Impeller,Volute casing & casing cover. At the time of feeding of steel material in to the casting the material is in liquid us form i.e. it i s hot material & this material is feeding into casting at the time o f feeding it develop different region of heat. At o ne side the temp is high &at other side the temp is low this also pr oduce cracks. To simulate that casting we use the M AGMA SOFTWARE for simulation & validate it using NDT.
A COMPARATIVE STUDY OF DESIGN OF SIMPLE SPUR GEAR TRAIN AND HELICAL GEAR TRAI...ijiert bestjournal
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A leaf spring is a simple form of spring,commonly used for the suspension in wheeled vehicles. It is also one of the oldest forms of spring. Sometimes referred to as a semielliptical l eaf spring (SELS) it takes the form of a slender ar c-shaped length of spring steel of rectangular cross section. The centre of the arc p rovides location for the axle,while tie holes are provided at either end for attaching to the vehicle body. In the present work,a seven-leaf steel spring use d in passenger cars is replaced with a composite mu lti leaf spring made of glass/epoxy composites. The dimensions sand the num ber of leaves for both steel leaf spring and compos ite leaf springs are considered to be the same. The primary objective is to compare their load carrying capacity,stiffness and weight savings of composite leaf spring. Finally,fatigue life of steel and com posite leaf spring is also predicted using life dat a
Brimmed diffuser is collection�acceleration device which shrouds a wind turbine.For a given turbine di ameter,the power augmentation can be achieved by brimmed diffuser,p opularly known as wind lens. The present numerical investigation deals with the effect of low pressure region created by wind l ens and hence to analyze the strong vortices formed by a brim attached to the shroud diffuser at exit. Also in this analysis,a c omparative numerical prediction of mass flow rates through the wind turbine has been carried out with various types of wind lens wh ich in turn helps to optimize the torque augmentati on. It has been numerically proved that there is significant increase in the wa ke formation & vortex strength when brimming effect is added to a diffuser
FINITE ELEMENT ANALYSIS OF CONNECTING ROD OF MG-ALLOY ijiert bestjournal
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This paper consist of working of reciprocating pump which is driven by a compound pendulum. It provide s the energy required to lift the water from a tank placed approximately several meter below the ground level. Basic application of the mechanism will be for watering the garden which will be operated by means of operation opening and closing of entrance gate. Paper consists of basic concept,design of pump and compound pendulum mecha nism and fabricationed model. The concept can also be implemented in the rural areas,having the problem of electric supply. We aim at making a prototype for providing some me an for pumping of water by the pump which requires less human efforts,conside ring cost effectiveness,easy to operate and portab le mechanism.
The IC engine has seen numerous revolutionary and e volutionary modifications in technology and design over the past few decades. The sole motto behind the modifications wa s to increase the overall efficiency of the IC Engi ne including volumetric and thermal efficiency. Recently few benchmarking techn ologies like the CRDI,MPFI,HCCI,etc. in the Otto cycle and Diesel cycle engines have created an enormous revolution in the automobile industry. In spite of these technologica l and design advances,the efficiencies are not being more than a particular l imit. However,the concept of split cycle engines has dra stically increased the overall performance in all respect. The split cycle concept basically separates the fou r strokes of the conventional cycle. The Scuderi engine one of the best-in-class engine desi gns based on the split cycle concept. The Scuderi engine works on the split cycle and gives higher efficiency than the previous split cycle engines resulting overall high perform ance. It also eliminates the problems faced by previous engines based on the spl it cycle in terms of breathing (volumetric efficien cy) and thermal efficiency. This paper throws light on the greater volumetric,thermal and overall efficiency key points related t o the Scuderi Engines.
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The excessive rise of temperature in the journal be aring operating at boundary/mixed lubrication regim es. Journal bearing test set- up is used to measure the temperature along the cir cumference of the bearing specimen for different lo ading conditions. Here in this journal bearing of l/d ratio 1,diameter of jo urnal is 60mm and the bearing length is 60mm,clear ance is .06mm has been designed and tested to access the temperature rise of the bearing. The result shows that as the load o n the bearing is increasing temperature also increasing. Temperature analysis o f journal bearing is also done by the Ansys workben ch software
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Energy is one of the building blocks of the country . The growth of the country has been fueled by chea p,abundant energy resources. Solar energy is a form of renewable ener gy which is available abundantly and collected unre servedly. The parabolic concentrator reflects the direct incident solar rad iation onto a receiver mounted above the dish at it s focal point. The conversion of concentrated solar radiation to heat takes place in receiver. The heat transfer characteristics of the receiver changes during the rotation of the receiver which affects thermal performance. The working temperature may also influence the ther mal performance and overall efficiency of the system. Thermal as well as optica l losses affect the performance of a solar paraboli c dish-cavity receiver system. The thermal losses of a solar cavity receiver include c onvective and radiative losses to the air in the ca vity and conductive heat loss through the insulation used behind the helical tube surface. Convective and radiative heat losses form the major constituents of the thermal losses. The convection heat loss from cavit y receiver in parabolic dish solar thermal power sy stem can significantly reduce the efficiency and consequently the cost effectiveness of the system. It is important to assess this heat loss and subsequently improve the thermal performance of the receiver.
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The demand for bigger,faster and lighter moving ve hicles,such as ships,trains,trucks and buses has increased the importance of efficient str uctural arrangements. In principle two approaches exist to develop efficient structures:e ither application of new materials or the use of new structural design. A proven and well-establi shed solution is the use of composite materials and sandwich structures. In this way high strength to weight ratio and minimum weight can be obtained. The sandwich structures have potential to offer a w ide range of attractive design solutions. In addition to the obtained weight reduction,these so lutions can often bring space savings,fire resistance,noise control and improved heating and cooling performance. Laser-welded metallic sandwich panels offer a number of outstand ing properties allowing the designer to develop light and efficient structural configuratio ns for a large variety of applications. These panels have been under active investigations during the last 15 years in the world.
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Bumper is a energy absorbing protective element whi ch absorb the energy in front collision and protect valuable parts like radiator etc. Bumper is act like protect ive shield generally made of steel material. As eco nomic point of view and to reduce consumption of fuel manufacturin g of light weight vehicle is requirement of current situation. Application of composite material in automobile sec tor is now day common thing. Aluminum honeycomb san dwich panel is basically material from aerospace industri es and known for its high strength to weight ratio. Sandwich structure basically having its properties due to ge ometry. To determine various properties of sandwich structure conducting experiments is expensive,so generally F EA is used .However complex geometry is hurdle so t here are various theories are available for simplification o f model. These theories convert 3D model in to homo genous model .As far as concerning India manufacturing rate of s andwich structure is very less,so generally cost i s more. Greatest giant manufacturer is china we can observe their bu llet train and metro transport facility constructio n. Recently in march 2014 largest selling Indian cars are failed in NCap test in 100% frontal crash test. So requirement of more energy absorbing material with economy cons ideration is important.
Robotic welding requires specialized fixtures to ac curately hold the work piece during the welding operation. Despite the large variety of welding fix tures available today the focus has shifted in maki ng the welding arms more versatile,not the fixture. T he new fixture design reduces cycle time and operat or labor while increasing functionality;and allows co mplex welding operations to be completed on simple two axis welding arms
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In these paper structural fields of the solid disc brake during short and emergency braking with four different materials is studied. The distribution of the tempe rature depends on the various factors such as frict ion,surface roughness and speed. The effect of the angular velo city and the contact pressure induces the temperatu re rise of disc brake. The finite element simulation for three -dimensional model was preferred due to the heat fl ux ratio constantly distributed in circumferential direction . Here value of temperature,friction contact power,nodal displacement and deformation for different pressure condition using analysis software with four materi als namely cast iron,cast steel,aluminium and carbon fibre reinforced plastic are taken. Presently the D isc brakes are made up of cast iron and cast steel. With the v alue of simulation result best suitable material fo r the brake drum with higher life span is determined.
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Metallic matrix composites are combinations of two or more different metals inter metallic compounds or second phases in which dispersed phases are embe dded within the metallic matrix. They are produced by controlling the morphologies of the constituents to achieve optimum combination of properties. Properties of the composites depend on the properti es of the constituent phases,their relative amount,and dispersed phase geometry including particle siz e,shape and orientation in the matrix. In this pap er,The mechanical properties,behaviour and micro stru ctural evolution of aluminium metal matrix metallic composites fabricated under various process conditi ons were investigated to understand their process- structure�property relations by optimization proces s. Addition of silicon carbide to aluminum has show n an increase in its mechanical properties.
PERFORMANCE EVALUATION OF TRIBOLOGICAL PROPERTIES OF COTTON SEED OIL FOR MULT...ijiert bestjournal
A lubricant is a substance that reduces friction an d wear by providing a protective film between two moving surfaces. Good lubricants possess the proper ties such as low toxicity,high viscosity index,hi gh load carrying capacity,excellent coefficient of fr iction,good anti-wear capability,low emission int o the environment,high ignition temperature. So tribolog y related problems can be minimized by proper selection of lubricant from wear consideration. Tod ay,the depletion of reserves of crude oil,the gro wing prices of crude oil and concern about protecting th e environment against pollution have developed the interest towards environment-friendly lubricants. B ecause of these the purpose of this work is to eval uate the anti-wear characteristics of cottonseed oil and to check the suitability of cottonseed oil as a lu bricant for multi-cylinder engine. Four ball testing machin e is used for anti-wear testing as per ASTM D 4172. The wear preventive characteristic of cottonseed oi l is obtained by measuring wear scar diameter. The present study shows the potential of cotton seed oi l as an alternating lubricant.
Magnetic abrasive finishing is a machining process where the tooling allowance is remove by media wi th both magnetic and abrasive properties,with a magnetic f ield acting as a binder of a grain. Such machining falls into the category of erosion by abrasive suspension and lend itself to the finishing of any type of surface . The possibility of finishing complex surfaces is a spec ial benefit of this machining. Magnetic abrasive fi nishing process is most suitable for obtaining quality fini sh on metallic and non-metallic surfaces. Magnetic abrasive finishing used for complicated product finishing & Roughness and tolerance band achieved that is diffi cult using conventional machine process. The product dimension al requirement easily possible with taking trial wi th MAF parameters.
Immunizing Image Classifiers Against Localized Adversary Attacksgerogepatton
This paper addresses the vulnerability of deep learning models, particularly convolutional neural networks
(CNN)s, to adversarial attacks and presents a proactive training technique designed to counter them. We
introduce a novel volumization algorithm, which transforms 2D images into 3D volumetric representations.
When combined with 3D convolution and deep curriculum learning optimization (CLO), itsignificantly improves
the immunity of models against localized universal attacks by up to 40%. We evaluate our proposed approach
using contemporary CNN architectures and the modified Canadian Institute for Advanced Research (CIFAR-10
and CIFAR-100) and ImageNet Large Scale Visual Recognition Challenge (ILSVRC12) datasets, showcasing
accuracy improvements over previous techniques. The results indicate that the combination of the volumetric
input and curriculum learning holds significant promise for mitigating adversarial attacks without necessitating
adversary training.
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Advancements in technology unveil a myriad of electrical and electronic breakthroughs geared towards efficiently harnessing limited resources to meet human energy demands. The optimization of hybrid solar PV panels and pumped hydro energy supply systems plays a pivotal role in utilizing natural resources effectively. This initiative not only benefits humanity but also fosters environmental sustainability. The study investigated the design optimization of these hybrid systems, focusing on understanding solar radiation patterns, identifying geographical influences on solar radiation, formulating a mathematical model for system optimization, and determining the optimal configuration of PV panels and pumped hydro storage. Through a comparative analysis approach and eight weeks of data collection, the study addressed key research questions related to solar radiation patterns and optimal system design. The findings highlighted regions with heightened solar radiation levels, showcasing substantial potential for power generation and emphasizing the system's efficiency. Optimizing system design significantly boosted power generation, promoted renewable energy utilization, and enhanced energy storage capacity. The study underscored the benefits of optimizing hybrid solar PV panels and pumped hydro energy supply systems for sustainable energy usage. Optimizing the design of solar PV panels and pumped hydro energy supply systems as examined across diverse climatic conditions in a developing country, not only enhances power generation but also improves the integration of renewable energy sources and boosts energy storage capacities, particularly beneficial for less economically prosperous regions. Additionally, the study provides valuable insights for advancing energy research in economically viable areas. Recommendations included conducting site-specific assessments, utilizing advanced modeling tools, implementing regular maintenance protocols, and enhancing communication among system components.
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ANALYSIS OF VAPOR COMPRESSION REFRIGERATION SYSTEM WITH DIFFERENT CONFIGURATIONS OF CAPILLARY TUBES USING R134A AS REFRIGERANT
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ANALYSIS OF VAPOR COMPRESSION REFRIGERATION
SYSTEM WITH DIFFERENT CONFIGURATIONS OF
CAPILLARY TUBES USING R134A AS REFRIGERANT
Vivek Ingawale
Department of Mechanical Engineering Fabtech College of Engineering and Research,
Sangola, INDIA
Swapnil Gaikwad
Department of Mechanical Engineering Fabtech College of Engineering and Research,
Sangola, INDIA
Audumbar Ingawale
Department of Mechanical Engineering Fabtech College of Engineering and Research,
Sangola, INDIA
Prof. Mangesh Mane
Department of Mechanical Engineering Fabtech College of Engineering and Research,
Sangola, INDIA
ABSTRACT
A capillary tube is widely used as throttling device in small sized refrigeration and air-
conditioning applications having capacity less than 3 TR. This research paper provides a set
of capillary tube performance data in a vapor compression refrigeration system using R-134a
as working fluid. Several capillary tubes with different length and inner diameter were
selected as test sections. Mass flow rate and Pressure drop through capillary tube was
measured for several inlet temperatures of each capillary tube. The sub cooling and
superheating temperatures are maintained constant throughout the experimentation.
Experimental conditions for the condensing temperatures were selected from 38 to 54º C in
the interval of 2º C. The effect of above given parameters on the Pressure difference, Power
input, Evaporating capacity and Coefficient of performance for R-134a through the helically
coiled capillary tube has been analyzed.
KEYWORDS: Expansion device, Capillary tube, Refrigerant pressure drop, R-134a,
Compressor calorimeter test rig.
INTRODUCTION
Due to environmental problems like depletion of the ozone layer and global warming, CFC
(chlorofluorocarbon) have been banned in developed countries since 1996 & from January 1st
2010 production and use of CFC’s is prohibited completely all over the worlds. HCFC (hydro
chlorofluorocarbon) refrigerants will also be phased out by 2020 & 2030 in developed and
developing countries, respectively. As a result, Eco-friendly HFC (hydro fluorocarbon), like
R-134a has emerged as alternative of R-12. Because of that in this experimental study, R-
134a is used as working fluids.
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The capillary tube as a throttling device is simple, reliable, and inexpensive. It is widely
used in the small-size vapor compression refrigeration appliances such as window air
conditioning and household refrigerators. It works as an automatic flow rate regulator of the
refrigerant through refrigeration system, when varying load conditions and varying
condensing and evaporating temperatures are to be encountered. The capillary tube is used
where the cooling load is almost constant and the cooling capacity is less than 3 TR.
Capillary tube is a long narrow hollow copper tube with an internal diameter ranging from
0.5 to 2.0 mm. The refrigeration systems work on vapor compression cycle comprising of
evaporator, compressor, condenser, and expansion device. A capillary tube as an expansion
device allows hermetically sealed compressor to start in an unloaded condition by allowing
the pressures between the condenser and evaporator to equalize during the off cycle, thus,
reduces the required starting torque of the compressor. Hence, a low starting torque motor
can be used to run the compressor with the vapor compression systems. Also, the small and
critical refrigerant charge required by the refrigeration system using capillary tube results in
cost reduction of the refrigerant as well as no need for a receiver tank in the system. Thus, all
the facts contribute towards substantial savings in the built–up cost of the refrigeration
system.
In the past, capillary tube performance using R-12 and R-22 were extensively studied by
many researchers; Bostland and Jordan [2], Cooper et al.[3], Koizumi and Yokoyama [4],
Chen et al. [5], Li et al. [6].Recently, a capillary tube performance for R-134a has been
studied by many researchers including Chun-Lu Zhang [7], Kim et al.[8], Khan et al. [9] and
Motta et.al.[10] .Also, The experimental studies on straight coiled capillary tubes are mostly
available in open literatures but helically coiled capillary with all practical operating
conditions are not sufficiently covered. Therefore, to strengthen the earlier study, the
experimental investigation has been undertaken to study the flow of R-134a through helically
coiled capillary tube
The main objective of this study is to provide a set of capillary tube performance data in
a vapor compression refrigeration system using R-134a as working refrigerant. While
achieving this objective, the experimental apparatus using capillary tubes is devised. Several
capillary tubes with different length and inner diameter were selected as test sections. Mass
flow rate and Pressure drop through capillary tube was measured for several inlet
temperatures of each capillary tube. The variation of inner diameter, tube length and
operating conditions of inlet pressure/temperature are the main parameters of this study.
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Fig. 1 Schematic diagram of Experimental setup
EXPERIMENTS
EXPERIMENTAL SET-UP AND PROCEDURE
The schematic diagram of experimental set-up is shown in Fig. 1. The test-
section was a copper capillary tube, in which the refrigerant expands from high pressure
side to low pressure side. The helically coiled tube test-section in the experimental set-
up was put in horizontal position. Suitable isolation valves are installed for easy
replacement of test pieces. The low pressure refrigerant coming out from capillary tube
entered the evaporator consisting of a copper coil submerged in a glycol tank. An
electric heater was fitted in the evaporator tank to provide a heat load to the evaporator.
The heating load was varied through a Solid state rely and PID controller. An agitator
was also fitted in the tank to maintain the uniform bulk temperature of glycol. The
refrigerant vapors emerging from the evaporator were sent to suction port of compressor
after assurance of achieving desired suction superheat of refrigerant. The hermetically
sealed compressor was run by means of single phase electrical supply. The high
pressure superheated vapors emerging from the compressor entered the oil separator.
The oil free vapors from separator were condensed in the water cooled condenser. The
desired condensing pressure/temperature was achieved by varying mass flow rate
through condenser by using three way proportionate control valve and PID controller.
The cooling tower was used to reject heat in to the atmospheric. The provision of on-off
of cooling tower fan was made to control the cooling tower water temperature. To vary
the degree of sub-cooling, a pre-heater followed the sub-cooler was installed. In the pre-
heater, liquid refrigerant heating was done by electrical heater and controlled by Solid
state relay and PID controller. The high pressure saturated liquid from the pre-heater
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was made to flow through sub-cooler to control the degree of sub-cool. The same
arrangement like condenser cooling water circuit was made to achieve desired sub-
cooling. However the cooling water first flow through sub-cooler and then flow through
condenser. The sub-cooled liquid refrigerant collected in a receiver to ensure a
continuous supply of refrigerant to the capillary tube.
Table.1. Properties chart for the refrigerants under study
Refrigerants
R-134a
Environmental Classification HFC
Chemical Formula
CH2FCF3
Molecular Weight
102.03
Boiling Point At 1 Atm.(0
C) -26.06
Critical Temperature (0
C) 101.08
Critical Density
(kg/m3
)
515.3
Liquid Density
(kg/m3
)
1220.60
Vapor Density
(kg/m3
)
5.25
Heat of Vaporization 217.01
Specific Heat of Liquid (J/kg-0
C) 1505.99
Specific Heat Vapor (J/kg-0
C) 831.91
Global Warming Potential (CO2 = 1.0) 1674
Lubricant oil used Polyol Ester (POE)
The unwanted solid particles and moisture in refrigerant were removed
through a filter-drier. A hand operated expansion valve was also provided in parallel to
the capillary tube. A centrifugal pump was used to circulate cooling water through the
sub-cooler and condenser. The mass flow rate of high pressure liquid refrigerant was
measured by magnetic mass flow meter having an accuracy of ±0.25% of indicated
value. A sight glass was also provided to visualize the state of refrigerant entering into
the capillary tube. A number of hand shutoff valves were provided in between the major
components of the experimental set-up. Therefore, in case of leakage or any repair, the
damaged component was retrieved with ease. The temperature at different locations of
the set-up and the test section was measured by means of T-type thermocouples with an
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accuracy of ±0.2. The pressure of the refrigerant was measured by pressure transducers
having an accuracy of ±0.25% FS (2000 kPa).
Capillary tubes with three inner diameters, 1.52 mm, 1.63 mm and 1.78 mm, were
selected for this study. The capillary tube diameters were measured with the help of tool
maker’s microscope having an accuracy of 0.01 mm The pressure at capillary tube inlet
was adjusted from 963 kPa to 1492 kPa. The degree of sub-cooling and degree of
superheating was maintained constant throughout the experimentation to 3ºC and 5ºC
respectively. All the test data were collected under steady state conditions. At the start
up, the system typically takes about 1 h to reach the steady state and thereafter, it takes
only 15 min for any subsequent setting.
EXPERIMENTAL CONDITIONS
The refrigerants used in this study were R-134a. Table.1. shows the properties of
R134a.Several capillary tubes with different length and inner diameter were selected as
test sections. Various test sections are named as C1, C2, C3, C4, C5. In this study, the
condensing pressure i.e. pressure at the capillary tube inlet was adjusted to the
saturation pressure corresponding to the condensing temperatures from 38 to 54º C in
the interval of 2º C.
Table 2: Shows The Specification Of Capillary Tubes.
Capillary Sample Configuration (Diameter * Length)
C1 1.625*1599 mm
C2 1,52*1499 mm
C3 1.78*1499 mm
C4 1.625*1499 mm
C5 1.625*1399 mm
The sub cooling and superheating temperatures are maintained constant
throughout the experimentation. In this study, tests were carried out for the capillary
tubes that were coiled with constant coiled diameter every time. Table.2. shows the
specification of capillary tubes.
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EXPERIMENTAL RESULTS AND DISCUSSIONS
Figure 2: Variation of Pressure difference Vs condensing temperature for capillary tube
samples of constant diameter 1.625 mm but of different lengths L1=1.39 m, L2=1.49m,
L3=1.59m.
From figure 2 it is clear that pressure difference increases as the condensing temperature
increases. Also, for a given condensing temperature pressure difference increases as the
length of capillary tube increases.
Figure 3: Variation of Power input Vs condensing temperature for capillary tube
samples of constant diameter 1.625 mm but of different lengths L1=1.39 m, L2=1.49m,
L3=1.59m.
From figure 3 it is clear that power input increases as the condensing temperature
increases. Also for a given condensing temperature power input decreases as the length
of capillary tube increases.
5
6
7
8
9
10
11
42 44 46 48 50 52 54
PressureDifference(bar)
Condensing Temperature (⁰C)
L3=1.59 m
L2=1.49 m
L1=1.39
0.7
0.75
0.8
0.85
0.9
0.95
1
1.82 7.35 0.81 1.32 1.63 7.96 0.88 1.25
Powerinput(kW)
Condensing Temperature (⁰C)
L3=1.59
L2=1.49
L1=1.39
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Figure 4: Variation of Evaporating capacity Vs condensing temperature for capillary
tube samples of constant diameter 1.625 mm but of different lengths L1=1.39 m,
L2=1.49m, L3=1.59m.
From figure 4 it is clear that Evaporating capacity decreases as the condensing
temperature increases. Also, for a given condensing temperature evaporating capacity
decreases as the length of capillary tube increases.
Figure 5: Variation of COP Vs condensing temperature for capillary tube samples of
constant diameter 1.625 mm but of different lengths L1=1.39 m, L2=1.49m, L3=1.59m.
From figure 5 it is clear that COP decreases as the condensing temperature
increases. Also, for a given condensing temperature power COP decreases as the length
of capillary tube increases.
0.9
1.1
1.3
1.5
1.7
1.9
40 42 44 46 48 50 52 54
Evaporatorcapacity(kW)
Condensing Temperature (⁰C)
L3=1.59
L2=1.49
L1=1.39
0.50
0.70
0.90
1.10
1.30
1.50
1.70
1.90
2.10
2.30
40 42 44 46 48 50 52 54
COP
Condensing Temperature (⁰C)
L3=1.59
L2=1.49
L1=1.39
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Figure 6: Variation of Pressure difference Vs condensing temperature for capillary tube
samples of constant length 1.49 m but of different lengths D1=1.52 mm, D2=1.625 mm,
D3=1.78 mm.
From figure 6 it is clear that pressure difference increases as the condensing
temperature increases. Also, for a given condensing temperature pressure difference
decreases as the diameter of capillary tube decreases.
Figure 7: Variation of Power input Vs condensing temperature for capillary tube
samples of constant length 1.49 m but of different lengths D1=1.52 mm, D2=1.625 mm,
D3=1.78 m
From figure 7 it is clear that power input increases as the condensing
temperature increases. Also, for a given condensing temperature power input decreases
as the length of capillary tube decreases.
5
6
7
8
9
10
11
42 46 52
PressureDifference(bar)
Condensing Temperature (⁰C)
D1=1.52 mm
D2=1.625 mm
D3=1.78 mm
0.6
0.65
0.7
0.75
0.8
0.85
0.9
0.95
1
42 46 52
Powerinput(kW)
Condensing Temperature (⁰C)
D1=1.52 mm
D2=1.625 mm
D3=1.78 mm
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Figure 8: Variation of Evaporating capacity Vs condensing temperature for capillary
tube samples of constant length 1.49 m but of different lengths D1=1.52 mm, D2=1.625
mm, D3=1.78 mm.
From figure 8 it is clear that Evaporating capacity decreases as the condensing
temperature increases. Also, for a given condensing temperature Evaporating capacity
decreases as the length of capillary tube decreases.
Figure 9: Variation of COP Vs condensing temperature for capillary tube samples of
constant length 1.49 m but of different lengths D1=1.52 mm, D2=1.625 mm, D3=1.78
mm.
From figure 9 it is clear that COP decreases as the condensing temperature
increases. Also, for a given condensing temperature COP decreases as the length of
capillary tube decreases.
0.6
0.8
1
1.2
1.4
1.6
1.8
2
2.2
42 46 52
EvaporatorCapacity(kW)
Condensing Temperature (⁰C)
D1=1.52 mm
D2=1.625 mm
D3=1.78 mm
0.60
0.80
1.00
1.20
1.40
1.60
1.80
2.00
2.20
2.40
2.60
42 46 52
COP
Condensing Temperature (⁰C)
D1=1.52 mm
D2=1.625 mm
D3=1.78 mm
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Figure 10: Variation of % change in length Vs % change in Power input, Evaporating
capacity, COP and Pressure difference at constant Condensing temperature 42°C for
three different configurations viz. C5, C4 and C1 i.e. of different lengths 1.39, 1.49 and
1.59 m respectively.
From figure it is clear that for length change from 1.39 to 1.49m i.e. for 7.2%
variation in length, variation in Power input, Evaporator capacity and COP is -3.7%, -
11.7% and -8.3% respectively while percentage change in pressure difference is
7.15%.Negative sign indicates with increase in length there is decrease in pressure drop.
Again for length change from 1.49 to 1.59m i.e. for 14.2% variation in length, variation
in Power input, Evaporator capacity and COP is -7.4%, -17.5% and -10.9% respectively
while percentage change in pressure difference is 9.7%.
Figure 11: Variation of % change in Diameter Vs % change in Power input,
Evaporating capacity, COP and Pressure difference at constant condensing temperature
of 42°C for three different configurations viz. C2, C4 and C3 i.e. of different diameters
1.52, 1.625 and 1.78 mm respectively.
From figure it is clear that for diameter change from 1.52 to 1.625 mm i.e. for 6.9 %
variation in diameter, variation in Power input, Evaporator capacity and COP is 1.3%,
-20
-15
-10
-5
0
5
10
15
7.2 14.4
Percentagechange(%)
CHANGE IN LENGTH (40)
work input
Evaporator capacity
COP
Pressure difference
-40
-20
0
20
40
60
80
100
120
6.9 17.1
PERCENTAGECHANGE(%)
CHANGE IN DIAMETER (42)
WORK INPUT
EVAPORATOR CAPACITY
COP
PRESSURE DIFFERENCE
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31.4% and 29% respectively while percentage change in pressure difference is -
2.1%.Negative sign indicates with increase in diameter there is decrease in pressure
drop
Again for length change from 1.49 to 1.59m i.e. for 14.2% variation in length,
variation in Power input, Evaporator capacity and COP is 14.7%, 95.2% and 70.3%
respectively while percentage change in pressure difference is -19.6%.
CONCLUSION
Pressure difference is directly proportional to capillary length while, inversely
proportional to inner diameter of capillary tube.
With change in length of capillary tube, Power input, Evaporating capacity and
COP decreases while Pressure difference increases.
With change in diameter of capillary tube, Power input, Evaporating capacity
and COP increases while Pressure difference decreases
REFERENCES
[1] S. G. Kim, M. S. Kim, S. T. Ro, “Experimental investigation of the performance
of R22, R407c and R410A in several capillary tubes for air-conditioners”. Int J
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[2] Mohd. Kaleem Khan, Ravi Kumar, Pradeep Sahoo, “An experimental study of
the flow of R134a inside an adiabatic spirally coiled capillary tube”.
[3] R.Cabello,J.Navarro-Esbr, “Department of Applied Thermodynamics, Camino
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[4] Chang Nyeun Kim & Young Moo Park,”Investigation on the selection of
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[5] M.A. Akintunde, “The Effects of Friction Factors on Capillary Tube Length”
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[6] C. Aprea,A. Greco,Dipartimento di IngegneriaMeccanica, Universit_a di
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