EP1860390A2 - Dampf-Kompressionskältezyklus - Google Patents

Dampf-Kompressionskältezyklus Download PDF

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Publication number
EP1860390A2
EP1860390A2 EP07108417A EP07108417A EP1860390A2 EP 1860390 A2 EP1860390 A2 EP 1860390A2 EP 07108417 A EP07108417 A EP 07108417A EP 07108417 A EP07108417 A EP 07108417A EP 1860390 A2 EP1860390 A2 EP 1860390A2
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EP
European Patent Office
Prior art keywords
gas
refrigerant
pressure
liquid separating
separating means
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07108417A
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English (en)
French (fr)
Other versions
EP1860390A3 (de
Inventor
Kenichi Suzuki
Masato Tsuboi
Yuuichi Matsumoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP1860390A2 publication Critical patent/EP1860390A2/de
Publication of EP1860390A3 publication Critical patent/EP1860390A3/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the present invention relates to a vapor compression refrigerating cycle, and specifically, to a vapor compression refrigerating cycle using carbon dioxide, which is a natural-system refrigerant, suitable particularly as a refrigerating cycle used in an air conditioning system for vehicles.
  • an electric expansion means and the like is thus controlled by referring to the refrigerant temperature of the high-pressure side so that the pressure of the high-pressure side becomes an optimum pressure, in order to adjust an air temperature at an exit of an evaporator, a displacement of an external signal control type variable displacement compressor is controlled, and the signal for controlling the displacement of the compressor is calculated generally from the information of thermal load, etc.
  • a gas injection cycle (a cycle for introducing gas-phase refrigerant, separated by a gas/liquid separator, into a midway of a compression step of a compressor) is disclosed in JP-A-11-63694 and JP-A-10-288411 .
  • the refrigerating cycle of such a gas injection cycle is structured as a system provided with a gas/liquid separator between two expansion means. Further, in a refrigerating cycle using carbon dioxide, it is difficult to control a degree of superheating of refrigerant at an exit of an evaporator, and further, it is necessary to separate the refrigerant at the exit of the evaporator into gas/liquid phases by a gas/liquid separator and flow out only the gas-phase refrigerant to a suction side of a compressor in order to deal with a variation of a load to the system.
  • a vapor compression refrigerating cycle with a structure of gas injection cycle, in particular, a vapor compression refrigerating cycle using carbon dioxide refrigerant which is a natural-system refrigerant, in which, by forming a structure of gas injection cycle while maintaining a good refrigeration ability, an efficiency of a compressor is improved and a consumption power required for the compressor is decreased, and while the efficiency as the whole of the refrigeration cycle is improved, the number of junction parts is decreased particularly by integrating a gas/liquid separator and expansion means, thereby simplifying the entire structure of the refrigerating cycle, reducing the cost thereof, and removing the fear of refrigerant leakage and the like.
  • a vapor compression refrigerating cycle which can cool the refrigerant to be injected and achieve a further high efficiency by employing a new structure for exchanging heat between the refrigerant injected into a compressor and the refrigerant sucked into the compressor.
  • a vapor compression refrigerating cycle can operate in a supercritical region of refrigerant, the refrigerating cycle has a compressor for compressing refrigerant and discharging compressed refrigerant, a radiator for cooling high-temperature and high-pressure refrigerant compressed by the compressor, a first pressure-reducing means for reducing the pressure of refrigerant cooled by the radiator, a first gas/liquid separating means for separating refrigerant reduced in pressure by the first pressure-reducing means into gas-phase refrigerant and liquid-phase refrigerant, a second pressure-reducing means for reducing the pressure of liquid-phase refrigerant separated by the first gas/liquid separating means, an evaporator for evaporating refrigerant reduced in pressure by the second pressure-reducing means, and a second gas/liquid separating means for separating refrigerant evaporated by the evaporator into gas-phase refrigerant and liquid-phase refrigerant, wherein the gas-phase refrigerant separated by the second
  • the pressure-reducing means and the gas/liquid separating means are integrated with each other, the number of junction parts is decreased, the entire structure of the refrigerating cycle is simplified and reduced in cost, and the fear of refrigerant leakage and the like is removed. Further, basically by forming the refrigerating cycle as a gas injection cycle, the efficiency of the compressor is improved and the consumption power required for the compression is decreased, and therefore, the efficiency as the whole of the refrigerating cycle is improved.
  • a vapor compression refrigerating cycle can operate in a supercritical region of refrigerant, the refrigerating cycle has a compressor for compressing refrigerant and discharging compressed refrigerant, a radiator for cooling high-temperature and high-pressure refrigerant compressed by the compressor, a first pressure-reducing means for reducing the pressure of refrigerant cooled by the radiator, a first gas/liquid separating means for separating refrigerant reduced in pressure by the first pressure-reducing means into gas-phase refrigerant and liquid-phase refrigerant, a second pressure-reducing means for reducing the pressure of liquid-phase refrigerant separated by the first gas/liquid separating means, an evaporator for evaporating refrigerant reduced in pressure by the second pressure-reducing means, and a second gas/liquid separating means for separating refrigerant evaporated by the evaporator into gas-phase refrigerant and liquid-phase refrigerant, wherein the gas-phase refrigerant separated
  • a vapor compression refrigerating cycle can operate in a supercritical region of refrigerant, the refrigerating cycle has a compressor for compressing refrigerant and discharging compressed refrigerant, a radiator for cooling high-temperature and high-pressure refrigerant compressed by the compressor, a first pressure-reducing means for reducing the pressure of refrigerant cooled by the radiator, a first gas/liquid separating means for separating refrigerant reduced in pressure by the first pressure-reducing means into gas-phase refrigerant and liquid-phase refrigerant, a second pressure-reducing means for reducing the pressure of liquid-phase refrigerant separated by the first gas/liquid separating means, an evaporator for evaporating refrigerant reduced in pressure by the second pressure-reducing means, and a second gas/liquid separating means for separating refrigerant evaporated by the evaporator into
  • a structure may be employed wherein the first gas/liquid separating means and the second gas/liquid separating means are integrated with each other.
  • the number of junction parts can be decreased, the entire structure of the refrigerating cycle can be simplified and reduced in cost, and the fear of refrigerant leakage and the like can be removed.
  • a structure may be employed wherein the first gas/liquid separating means, the second gas/liquid separating means, the first pressure-reducing means and the second pressure-reducing means are all integrated with each other.
  • the number of junction parts can be further decreased, the entire structure of the refrigerating cycle can be further simplified and further reduced in cost, and the fear of refrigerant leakage and the like can be removed more surely.
  • a structure may be employed wherein the first gas/liquid separating means and the second gas/liquid separating means are formed as an integral vessel, the first pressure-reducing means is incorporated into a refrigerant passageway extending from a first inlet port of the first gas/liquid separating means opening at a side of the radiator to a second inlet port of the first gas/liquid separating means opening toward an interior of the first gas/liquid separating means, and the second pressure-reducing means is provided in a refrigerant passage route extending from an outlet port of the first gas/liquid separating means for discharging liquid-phase refrigerant from the first gas/liquid separating means to a position of the evaporator.
  • the integrated portion can be made compact efficiently.
  • a structure may be employed wherein a refrigerant passageway forming a part of the refrigerant passage route passes through a refrigerant storing space formed in the second gas/liquid separating means.
  • a structure may be employed wherein the refrigerant passageway forming a part of the refrigerant passage route is formed so as to pass through the refrigerant storing space formed in the second gas/liquid separating means and come into contact with liquid-phase refrigerant separated by the second gas/liquid separating means and stored in the refrigerant storing space.
  • a structure may be employed wherein the first gas/liquid separating means and the second gas/liquid separating means are formed as an integral vessel, the first pressure-reducing means is incorporated into a refrigerant passageway extending from a first inlet port of the first gas/liquid separating means opening at a side of the radiator to a second inlet port of the first gas/liquid separating means opening toward an interior of the first gas/liquid separating means, and a refrigerant passage route extending from the first gas/liquid separating means to the second pressure-reducing means passes through a refrigerant storing space formed in the second gas/liquid separating means.
  • this refrigerant passage route extending from the first gas/liquid separating means to the second pressure-reducing means is formed so as to pass through the refrigerant storing space formed in the second gas/liquid separating means and come into contact with liquid-phase refrigerant separated by the second gas/liquid separating means and stored in the refrigerant storing space.
  • Such vapor compression refrigerating cycles according to the present invention are suitable as refrigerating cycles including supercritical region of refrigerant, in particular, for a case where carbon dioxide is used as the refrigerant for the vapor compression refrigerating cycle. Further, the vapor compression refrigerating cycles according to the present invention are suitable as refrigerating cycles used for an air conditioning system for a vehicle.
  • the efficiency of the compressor can be improved and the consumption power required for the compressor can be decreased by employing a structure of a gas injection cycle
  • the number of junction parts can be decreased, the entire structure of the refrigerating cycle can be simplified and reduced in cost, and the fear of refrigerant leakage and the like can be removed.
  • the injected refrigerant can be cooled, the advantage due to the injection can be increased, and the efficiency as the whole of the refrigerating cycle can be improved.
  • Fig. 1 depicts a vapor compression refrigerating cycle according to a first embodiment of the present invention for use in an air conditioning system for a vehicle, using carbon dioxide which is a natural-system refrigerant.
  • Refrigerating cycle 1 is provided relative to an air path 11 provided with a blower 10.
  • Refrigerant compressed by a compressor 2 is introduced into a radiator 3, and at the radiator 3, the refrigerant is exchanged in heat with an outside fluid (for example, air) using a fan for radiator 4 and the like.
  • the refrigerant cooled by and discharged from radiator 3 is reduced in pressure by an orifice provided as a first expansion device 5 forming a first pressure-reducing means.
  • the pressure-reduced refrigerant is separated into gas-phase refrigerant and liquid-phase refrigerant by a first gas/liquid separating chamber (a first gas/liquid separating means) in a gas/liquid separator module 7 formed by integrating a first gas/liquid separating means and a second gas/liquid separating means with each other.
  • the separated liquid-phase refrigerant is reduced in pressure by an orifice provided as a second expansion device 6 forming a second pressure-reducing means, and the pressure-reduced refrigerant is introduced into an evaporator 8 and exchanged in heat with an outside fluid (for example, air in air path 11).
  • the refrigerant flowed out from evaporator 8 is separated into gas-phase refrigerant and liquid-phase refrigerant by a second gas/liquid separating chamber (a second gas/liquid separating means) in gas/liquid separator module 7.
  • the separated liquid-phase refrigerant is stored in gas/liquid separator module 7, and the gas-phase refrigerant is discharged from gas/liquid separator module 7, and flowed into compressor 8 and compressed by the compressor 8.
  • the gas-phase refrigerant flowed out from the first gas/liquid separating chamber provided in gas/liquid separator module 7 is cooled at heat exchanger 9 by the gas-phase refrigerant flowed out from the second gas/liquid separating chamber provided in gas/liquid separator module 7, and injected into compressor 2 (into a midway of the compression step of compressor 2).
  • This compressor 2 of this refrigerating cycle 1 is a fixed displacement compressor or a variable displacement compressor, and its drive source may be either an engine of a vehicle or a drive source except an engine.
  • Fig. 2 depicts a detailed structure of gas/liquid separator module 7 according to the first embodiment.
  • Refrigerant storing vessel 100 provided as gas/liquid separator module 7 is separated therein into a first gas/liquid separating chamber 101 formed as a first gas/liquid separating means and a second gas/liquid separating chamber 105 formed as a second gas/liquid separating means.
  • Both gas/liquid separating chambers have a function for separation into gas and liquid phases.
  • the refrigerant from radiator 3 is flowed from a high-pressure refrigerant inlet port 112, reduced in pressure by a first expansion device 102, flowed into first gas/liquid separating chamber 101 from a middle-pressure refrigerant inlet port 103, and separated into middle-pressure gas-phase and liquid-phase refrigerants.
  • the middle-pressure gas-phase refrigerant separated by first gas/liquid separating chamber 101 passes through a middle-pressure refrigerant passageway 104 and flows out from a middle-pressure refrigerant outlet port 114.
  • the middle-pressure liquid-phase refrigerant separated by first gas/liquid separating chamber 101 is reduced in pressure by a second expansion device 106, passes through a refrigerant storing space in second gas/liquid separating chamber 105 and passes through a refrigerant tube 107 provided so as to come into contact with stored liquid-phase refrigerant 118, and thereafter, flows out from a low-pressure refrigerant outlet port 116 toward evaporator 8.
  • second expansion device 106 provided as a second pressure-reducing means may be provided in a refrigerant passage route extending from a position of refrigerant outlet port 120 from first gas/liquid separating chamber 101 to a position of evaporator 8, in this embodiment it is provided immediately after the refrigerant outlet port 120.
  • the gas and liquid two-phase refrigerant flowed out from evaporator 8 passes through a refrigerant tube 108 extending from a low-pressure refrigerant inlet port 113 through first gas/liquid separating chamber 101, flows into second gas/liquid separating chamber 105, and therein, is separated into low-pressure gas-phase and liquid-phase refrigerants.
  • the separated low-pressure liquid-phase refrigerant 118 is stored at a lower part in second gas/liquid separating chamber 105, oil 119 for being contained in the refrigerant flowed in for lubricating the refrigerating cycle is stored in the bottom part in second gas/liquid separating chamber 105, and the separated low-pressure gas-phase refrigerant is discharged through a refrigerant tube 109 toward the suction side of compressor 2.
  • Oil 119 stored in the bottom part in second gas/liquid separating chamber 105 is sucked from an oil returning hole 111 disposed at a lower part of a refrigerant discharge tube 109, and the sucked oil is sent to compressor 2 through the refrigerant discharge tube 109 and a low-pressure refrigerant outlet port 115 together with low-pressure gas-phase refrigerant.
  • a diffuser 110 prevents the gas and liquid two-phase refrigerant, passing through low-pressure refrigerant inlet port 113 and being flowed in from refrigerant tube 108, from being flowed directly into refrigerant discharge tube 109. Where, it is considered that the oil and the liquid-phase refrigerant are not completely separated from each other as shown in the figure, and in practice, the liquid-phase refrigerant is contained in the oil more or less.
  • Fig. 3 depicts an example of a heat exchanger having a double-pipe structure, capable of being applied to heat exchanger 9 in the first embodiment.
  • the double-pipe structure 200 utilized as heat exchanger 9 is formed so that the gas-phase refrigerant separated by first gas/liquid separating chamber 101 passes through an inner passageway 201 and the gas-phase refrigerant flowed out from second gas/liquid separating chamber 105 passes through an outer passageway 202, and the gas-phase refrigerant, separated by first gas/liquid separating chamber 101 and being injected into compressor 2, is cooled by heat exchange between both gas-phase refrigerants.
  • Fig. 4 depicts a Mollier chart, showing the operation of the refrigerating cycle in the first embodiment.
  • the axis of the abscissa represents the enthalpy, and the axis of the ordinate represents the pressure.
  • the number of junction parts can be decreased, the entire structure of the refrigerating cycle can be simplified and reduced in cost, and the fear of refrigerant leakage and the like can be removed.
  • the gas-phase refrigerant injected into compressor 2 can be cooled by heat exchange between the refrigerant being injected into the compressor 2 and the refrigerant being sucked into the compressor 2, the advantage due to the injection can be increased, and the efficiency as the whole of the refrigerating cycle can be improved.
  • Fig. 5 depicts a vapor compression refrigerating cycle using carbon dioxide, according to a second embodiment of the present invention.
  • the basic structure of this refrigerating cycle according to the second embodiment is same as that of the refrigerating cycle according to the first embodiment.
  • the position for incorporating second expansion device 6 in the gas/liquid separator is different from that in the first embodiment. The operation of the second embodiment will be explained referring to Fig. 6.
  • Fig. 6 depicts a detailed structure of gas/liquid separator module 7 according to the second embodiment.
  • Refrigerant storing vessel 100 provided as gas/liquid separator module 7 is separated therein into a first gas/liquid separating chamber 101 formed as a first gas/liquid separating means and a second gas/liquid separating chamber 105 formed as a second gas/liquid separating means, similarly to in the first embodiment.
  • Both gas/liquid separating chambers have a function for separation into gas and liquid phases.
  • the refrigerant from radiator 3 is flowed from a high-pressure refrigerant inlet port 112, reduced in pressure by a first expansion device 102, flowed into first gas/liquid separating chamber 101 from a middle-pressure refrigerant inlet port 103, and separated into middle-pressure gas-phase and liquid-phase refrigerants.
  • the middle-pressure gas-phase refrigerant separated by first gas/liquid separating chamber 101 passes through middle-pressure refrigerant passageway 104 and flows out from middle-pressure refrigerant outlet port 114.
  • first gas/liquid separating chamber 101 passes through refrigerant tube 107, and it is reduced in pressure by second expansion device 106, and flows out from low-pressure refrigerant outlet port 116 toward evaporator 8. At that time, a part of refrigerant tube 107 comes into contact with low-pressure liquid-phase refrigerant 118 as shown in the figure, and it is possible to cool the refrigerant flowing in the refrigerant tube 107.
  • the refrigerant flowing in the refrigerant tube 107 can be cooled by the gas-phase refrigerant and the liquid-phase refrigerant in the second gas/liquid separating chamber 105, and the refrigeration ability can be increased.
  • the gas and liquid two-phase refrigerant flowed out from evaporator 8 passes through refrigerant tube 108 from refrigerant inlet port 113, flows into second gas/liquid separating chamber 105, and therein, is separated into low-pressure gas-phase and liquid-phase refrigerants.
  • the separated low-pressure liquid-phase refrigerant 118 is stored at a lower part in second gas/liquid separating chamber 105, oil 119 for being contained in the refrigerant flowed in for lubricating the refrigerating cycle is stored in the bottom part in second gas/liquid separating chamber 105, and the separated gas-phase refrigerant is discharged through refrigerant tube 109 toward the suction side of compressor 2. Oil 119 stored in the bottom part in second gas/liquid separating chamber 105 is sucked from oil returning hole 111 disposed at a lower part of refrigerant discharge tube 109, and the sucked oil is sent to compressor 2 through the refrigerant discharge tube 109 together with the low-pressure gas-phase refrigerant.
  • diffuser 110 prevents the gas and liquid two-phase refrigerant, passing through low-pressure refrigerant inlet port 113 and being flowed in from refrigerant tube 108, from being flowed directly into refrigerant discharge tube 109.
  • the oil and the liquid-phase refrigerant are not completely separated from each other as shown in the figure, and in practice, the liquid-phase refrigerant is contained in the oil more or less.
  • means for accelerating the heat exchange such as fins may be provided to refrigerant tube 107.
  • Fig. 7 depicts a Mollier chart, showing the operation of the refrigerating cycle in the second embodiment. As shown in Fig. 7, a supercooling region appears partially, as compared with the Mollier chart in the first embodiment depicted in Fig. 4.
  • the efficiency of compressor 2 can be improved and the consumption power required for the compression can be decreased.
  • the gas/liquid separator and the pressure-reducing mechanism with each other (forming the integrated gas/liquid separator module 7), it becomes possible to decrease the number of junction parts, simplify the structure, reduce in cost, and remove the fear of refrigerant leakage.
  • the injected refrigerant can be cooled, and the advantage due to the injection can be increased.
  • the vapor compression refrigerating cycle according to the present invention can be applied to any vapor compression refrigerating cycle capable of operating in a supercritical region of refrigerant, and in particular, it is suitable for a refrigerating cycle using carbon dioxide which is a natural-system refrigerant, and especially, suitable as a refrigerating cycle used for an air conditioning system for vehicles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP07108417A 2006-05-26 2007-05-17 Dampf-Kompressionskältezyklus Withdrawn EP1860390A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006146324A JP4776438B2 (ja) 2006-05-26 2006-05-26 冷凍サイクル

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EP1860390A2 true EP1860390A2 (de) 2007-11-28
EP1860390A3 EP1860390A3 (de) 2008-07-23

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US8327651B2 (en) 2009-07-07 2012-12-11 Hamilton Sundstrand Corporation Transcritical fluid cooling for aerospace applications
WO2015184933A1 (zh) * 2014-06-05 2015-12-10 珠海格力电器股份有限公司 闪蒸器及具有该闪蒸器的空调系统
WO2016026253A1 (zh) * 2014-08-22 2016-02-25 珠海格力电器股份有限公司 闪发器和具有该闪发器的空调
CN109073298A (zh) * 2016-12-27 2018-12-21 株式会社不二工机 制冷剂容器
US10234181B2 (en) 2013-11-18 2019-03-19 Carrier Corporation Flash gas bypass evaporator
CN117553364A (zh) * 2024-01-09 2024-02-13 深圳中集天达吉荣航空制冷有限公司 基于相变蓄冷的飞机地面空调系统及控制方法

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JP2012093051A (ja) * 2010-10-28 2012-05-17 Fuji Koki Corp ヒートポンプ用気液分離器及びインジェクション式ヒートポンプシステム
JP5911728B2 (ja) * 2012-01-17 2016-04-27 カルソニックカンセイ株式会社 気液分離器及び車両用空気調和装置
JP5920272B2 (ja) * 2013-03-29 2016-05-18 株式会社デンソー 統合弁
EP3775716A1 (de) * 2018-03-27 2021-02-17 BITZER Kühlmaschinenbau GmbH Kälteanlage
WO2020208736A1 (ja) * 2019-04-10 2020-10-15 三菱電機株式会社 冷凍サイクル装置
JP7439658B2 (ja) 2020-06-30 2024-02-28 株式会社デンソー 冷凍サイクル装置

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CN109073298B (zh) * 2016-12-27 2021-06-22 株式会社不二工机 制冷剂容器
CN117553364A (zh) * 2024-01-09 2024-02-13 深圳中集天达吉荣航空制冷有限公司 基于相变蓄冷的飞机地面空调系统及控制方法
CN117553364B (zh) * 2024-01-09 2024-04-02 深圳中集天达吉荣航空制冷有限公司 基于相变蓄冷的飞机地面空调系统及控制方法

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