EP1862749A2 - Dampf-Kompressionskältezyklus - Google Patents

Dampf-Kompressionskältezyklus Download PDF

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Publication number
EP1862749A2
EP1862749A2 EP07108423A EP07108423A EP1862749A2 EP 1862749 A2 EP1862749 A2 EP 1862749A2 EP 07108423 A EP07108423 A EP 07108423A EP 07108423 A EP07108423 A EP 07108423A EP 1862749 A2 EP1862749 A2 EP 1862749A2
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EP
European Patent Office
Prior art keywords
refrigerant
pressure
heat exchanger
refrigerating cycle
compressor
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Withdrawn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
EP07108423A
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English (en)
French (fr)
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EP1862749A3 (de
Inventor
Yuuichi Matsumoto
Masato Tsuboi
Kenichi Suzuki
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Sanden Corp
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Sanden Corp
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Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP1862749A2 publication Critical patent/EP1862749A2/de
Publication of EP1862749A3 publication Critical patent/EP1862749A3/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media

Definitions

  • the present invention relates to a vapor compression refrigerating cycle, and specifically, to a vapor compression refrigerating cycle suitable for a case using carbon dioxide, which is a natural-system refrigerant, particularly suitable as a refrigerating cycle used in an air conditioning system for vehicles.
  • Carbon dioxide refrigerant is proposed as an alternate refrigerant even in the field of air conditioning systems for vehicles, form the viewpoint of environmental problems. Carbon dioxide refrigerant is poisonless and incombustible, however, the critical temperature is low (about 31°C), and when the pressure of the high-pressure side of the refrigerating cycle becomes a supercritical condition (about 7.4 MPa or more), the cycle becomes a cycle transiting a critical condition (a supercritical refrigerating cycle). Generally, because such a cycle is low in coefficient of performance (COP) for refrigeration as compared with a cycle using Freon group refrigerants, it is required to improve the COP.
  • COP coefficient of performance
  • lubricant oil is soluble in the refrigerant and circulates together with the refrigerant.
  • the heat transfer at the evaporator is damaged by the oil flowed in, and the ability of the evaporator decreases.
  • Fig. 7 depicts a circuit diagram of a conventional refrigerating cycle for an air conditioning system in a case using carbon dioxide as its refrigerant, for example, disclosed in JP-A-11-193967 .
  • Refrigerating cycle 100 has a compressor 102 for compressing refrigerant and a radiator 102 (a gas cooler) for radiating heat of the refrigerant compressed by compressor 101.
  • the high-pressure refrigerant from radiator 102 is reduced in pressure by a first pressure reducer 104, and the refrigerant reduced in pressure is evaporated by an evaporator 105.
  • an accumulator 106 is provided for separating the refrigerant flowed out from evaporator 105 at a state of gas/liquid mixing phases into gas-phase refrigerant and liquid-phase refrigerant and storing the separated liquid refrigerant, and the separated gas-phase refrigerant is sent to a suction side of compressor 101.
  • an inside heat exchanger 103 is provided for exchanging heat between the refrigerant at an exit side of radiator 102 (high-pressure side refrigerant) and the refrigerant at an exit side of accumulator 106 (low-pressure side refrigerant).
  • a structure of so-called gas injection cycle wherein, in order to improve the efficiency of a compressor and decrease the consumption power of the whole of a refrigerating cycle, the refrigerant at an exit side of a radiator is reduced in pressure, the pressure-reduced refrigerant is separated into gas/liquid phases, and the separated gas-phase refrigerant is introduced into a midway of a compression step of the compressor (for example, JP-A-11-63694 ).
  • a vapor compression refrigerating cycle in which a function similar to that in a conventional gas injection cycle can be exhibited by utilizing an oil containing a small amount of refrigerant separated by an oil separator, a temperature of a high-pressure side refrigerant can be appropriately lowered through heat exchange with the oil containing a small amount of refrigerant, thereby preventing a low-pressure side refrigerant from being heated too much at the time of heat exchange between the high-pressure side refrigerant and the low-pressure side refrigerant, and protection of a compressor and improvement of an efficiency can be balanced at an optimum condition.
  • a vapor compression refrigerating cycle in which a radiator, an oil separator, a pressure reducer, an inside heat exchanger, etc. can be structured integrally, and while the refrigeration ability can be increased, problems on space and weight can be solved.
  • a vapor compression refrigerating cycle comprises a compressor for comprising refrigerant, a radiator for radiating heat of the refrigerant compressed by the compressor, an oil separator for separating the refrigerant radiated in heat by the radiator into refrigerant and oil containing a small amount of refrigerant, a first pressure reducer for reducing a pressure of the refrigerant separated by the oil separator, an evaporator for evaporating the refrigerant reduced in pressure by the first pressure reducer, and an accumulator for separating the refrigerant flowed out from the evaporator into gas-phase refrigerant and liquid-phase refrigerant and sending only the gas-phase refrigerant to a suction side of the compressor, and is characterized in that a second pressure reducer for reducing a pressure of the oil containing a small amount of refrigerant separated by the oil separator and at least a first inside heat exchanger for exchanging heat between the refrigerant separated by the oil
  • the oil containing a small amount of refrigerant separated by the oil separator is utilized, after this oil is reduced in pressure by the second pressure reducer, it is exchanged in heat with the refrigerant separated by the oil separator, and thereafter, by injecting it into a midway of a compression step of the compressor, a function similar to that in a conventional gas injection cycle is exhibited, the efficiency of the compressor can be improved, and the consumption power of the cycle can be decreased.
  • the temperature of the high-pressure side refrigerant is appropriately lowered, and when this high-pressure side refrigerant is exchanged in heat with the low-pressure side refrigerant sucked into the compressor, the low-pressure side refrigerant is prevented from being heated too much (from becoming a too high degree of superheating) and from becoming wet, the temperature of the refrigerant to be introduced into the compressor can be controlled at an optimum temperature from the viewpoint of protecting the compressor and improving the efficiency.
  • a structure is preferred wherein a second inside heat exchanger is provided for exchanging heat between the refrigerant separated by the oil separator and the refrigerant sent to the suction side of the compressor.
  • This second inside heat exchanger is one similar to a conventional inside heat exchanger (for example, inside heat exchanger 107 depicted in Fig. 7), and it provides a degree of superheating so that the refrigerant sent to the suction side of the compressor does not become wet.
  • the present invention it is possible to form the first and second inside heat exchangers integrally with each other.
  • the radiator is structured integrally with the oil separator, the second pressure reducer, the first inside heat exchanger and the second inside heat exchanger.
  • substantially the number of equipments can be reduced, the refrigeration ability can be increased, and the problems on space and weight when mounted on a vehicle can be solved.
  • each of the first pressure reducer and the second pressure reducer is structured as a pressure reducer capable of changing its degree of opening in accordance with a pressure or a temperature, or both, of refrigerant in the vapor compression refrigerating cycle.
  • the vapor compression refrigerating cycle according to the present invention is suitable as a vapor compression refrigerating cycle having a supercritical region, in particular, for a cycle using carbon dioxide as its refrigerant. Furthermore, the vapor compression refrigerating cycle according to the present invention is suitable as a refrigerating cycle used for an air conditioning system for a vehicle.
  • the vapor compression refrigerating cycle by effectively utilizing the oil containing a small amount of refrigerant separated by the oil separator, a function similar to that in a conventional gas injection cycle can be exhibited, and protection of the compressor and improvement of the efficiency can be balanced at an optimum condition by appropriately lowering the temperature of the high-pressure side refrigerant (the refrigerant separated by the oil separator) through heat exchange with the oil containing a small amount of refrigerant, and preventing the low-pressure side refrigerant from being heated too much at the time of heat exchange between the high-pressure side refrigerant and the low-pressure side refrigerant. Namely, it becomes possible to control the low-pressure side refrigerant sucked into the compressor at an optimum degree of superheating.
  • first inside heat exchanger and the second inside heat exchanger are integrated with each other, and further, if the radiator is integrated with the oil separator, the second pressure reducer, the first inside heat exchanger and the second inside heat exchanger, while the refrigeration ability can be increased, problems on space and weight can be solved. Moreover, because the number of equipment and the number of junction parts can be decreased, prevention of refrigerant leakage and improvement of property of mounting on a vehicle can be expected.
  • Fig. 1 depicts a circuit diagram of a vapor compression refrigerating cycle according to an 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 10 has a compressor 1 for compressing refrigerant and a radiator 2 (a gas cooler) for radiating heat of the refrigerant compressed by compressor 1.
  • Lubricant oil is soluble in refrigerant at a supercritical condition, and circulates together with the refrigerant. In such a condition, if the oil flows particularly into an evaporator, the heat transfer is damaged by the oil, and the evaporation ability of the evaporator decreases.
  • an oil separator 3 is provided for separating the oil contained in refrigerant from the refrigerant.
  • a second pressure reducer 5 reduces the pressure of the oil which is separated by oil separator 3 and which contains a small amount of refrigerant, and a gas injection cycle is formed by flowing the pressure-reduced oil, containing a small amount of refrigerant, through an inside heat exchanger 4 and introducing it into a midway of a compression step of compressor 1. Because the refrigerant on the way of compression is cooled by the injected oil, the temperature of discharged refrigerant does not elevate so much and the efficiency of compressor 1 does not decrease so much.
  • the refrigerant (high-temperature and high-pressure refrigerant) separated by oil separator 3 passes through inside heat exchanger 4, and is reduced in pressure by a first pressure reducer 6.
  • the refrigerant reduced in pressure by first pressure reducer 6 is evaporated at an evaporator 7 by heat exchange with outside heat exchange medium (for example, air sent in an air path of an air conditioning system).
  • An accumulator 8 is provided at a position downstream of evaporator 7 for separating the refrigerant flowed out from evaporator 7 into gas and liquid phases and storing the separated liquid-phase refrigerant therein.
  • the separated gas-phase refrigerant (low-pressure refrigerant, in practice, it is frequently a mixing-phase refrigerant mixed with a small amount of liquid-phase refrigerant) is flowed out to inside heat exchanger 4, and after an appropriate degree of superheating is given by the heat exchange at inside heat exchanger 4, it is sent to the suction side of compressor 1.
  • the arrows represent flows of refrigerant and oil containing a small amount of refrigerant.
  • the above-described inside heat exchanger 4 is formed as a structure wherein a first inside heat exchanger 41 according to the present invention (a heat exchanger for exchanging heat between the refrigerant separated by oil separator 3 and the oil containing a small amount of refrigerant reduced in pressure by second pressure reducer 5) and a second inside heat exchanger 42 according to the present invention (a heat exchanger for exchanging heat between the refrigerant separated by oil separator 3 and the refrigerant sent to the suction side of compressor 1) are integrated with each other.
  • a first inside heat exchanger 41 according to the present invention a heat exchanger for exchanging heat between the refrigerant separated by oil separator 3 and the oil containing a small amount of refrigerant reduced in pressure by second pressure reducer 5
  • a second inside heat exchanger 42 according to the present invention a heat exchanger for exchanging heat between the refrigerant separated by oil separator 3 and the refrigerant sent to the suction side of compressor
  • refrigerating cycle 10 it is provided as an integrated-type inside heat exchanger 4 for exchanging heat between the refrigerant separated by oil separator 3 and the oil containing a small amount of refrigerant after passing through second pressure reducer 5 and the refrigerant to be sucked into compressor 1.
  • the oil containing a small amount of refrigerant after passing through second pressure reducer 5 is injected into a midway of the compression step of compressor 1 after passing through inside heat exchanger 4.
  • a refrigerant such as water or hydrocarbon, whose high-pressure side pressure becomes its critical pressure or more, may used.
  • refrigerating cycle 10 may be used for application other than an air conditioning system for a vehicle.
  • Fig. 2 exemplifies an operation condition of refrigerating cycle 10 depicted in Fig. 1 by using a Mollier chart.
  • Curved line 21 represents a saturated vapor curved line of carbon dioxide refrigerant.
  • Curved line 22 represents an isothermal line passing through the critical temperature.
  • Curved line 23 represents a constant-pressure line passing through the critical pressure.
  • Fig. 3 depicts a circuit diagram in a case where the respective components in Fig. 1 are integrated with each other.
  • radiator 2 a gas cooler
  • oil separator 3 a gas separator
  • second pressure reducer 5 a structure integrated with first inside heat exchanger 41 and second inside heat exchanger 42
  • a demister 32 a fine net woven with fibrous metal wires is provided in one tank of radiator 2 as a member for forming oil separator 3 to separate oil.
  • the refrigerant passes through radiator 2 at a cross-flow condition, and it is flowed through inside heat exchanger 4 disposed at a lower position of radiator 2.
  • the refrigerant and the oil containing a small amount of refrigerant which is reduced in pressure by second pressure reducer 5 are flowed through the part of first inside heat exchanger 41 of inside heat exchanger 4 at a counter-flow condition.
  • the gas-phase refrigerant flowed out from accumulator 8 is flowed through the part of second inside heat exchanger 42 of inside heat exchanger 4.
  • the gas-phase refrigerant flowed out from accumulator 8 (low-pressure refrigerant) is exchanged in heat with the refrigerant at the exit side of radiator 2 (that is, high-pressure refrigerant after being separated by oil separator 3) in the part of second inside heat exchanger 42 of inside heat exchanger 4 at a counter-flow condition.
  • the oil containing a small amount of refrigerant which is reduced in pressure by second pressure reducer 5, and the refrigerant at the exit side of accumulator 8 are in a parallel-flow condition.
  • the efficiency of the heat exchange can be improved by setting the high-pressure refrigerant and the low-pressure refrigerant at a counter-flow condition.
  • first pressure reducer 6 and second pressure reducer 5 it is preferred to use a pressure-reducing mechanism capable of changing its opening degree in accordance with pressure or temperature or both.
  • radiator 2 a gas cooler
  • oil separator 3 second pressure reducer 5 and inside heat exchanger 4
  • inside heat exchanger 4 heat transfer from the refrigerant at the entrance side of radiator 2 is achieved over the entire of gas cooler module 31, therefrom the heat is transferred to the middle-pressure side and the low-pressure side in inside heat exchanger 4, and the degrees of superheating of the middle-pressure side refrigerant and the low-pressure side refrigerant are increased.
  • Figs. 4A-4D depict the appearance of gas cooler module 31 depicted in Fig. 3 shown by trigonometry.
  • Fig. 4A is its elevational view, and is the same as that depicted in Fig. 3, and Fig. 4B (its plan view), Fig. 4C (its side view) and Fig. 4D (its bottom view) are added.
  • Fig. 4B its plan view
  • Fig. 4C its side view
  • Fig. 4D its bottom view
  • an assembly structure may be employed wherein air sent from a front side of a vehicle does not pass through the part of inside heat exchanger 4 provided at the lower position of gas cooler module 31.
  • a design may be employed wherein, while the area of the part of radiator 2 is set as large as possible, inside heat exchanger 4 is incorporated thereinto.
  • Figs. 5A-5D show cross-sectional views of examples of inside heat exchanger 4 of gas cooler module 31, and Figs. 5E and 5F show a structure of an example of an end portion for inlet and outlet ports thereof.
  • a cross-sectional structure 51 depicted in Fig. 5A an inside heat exchanger having a triple-tube structure is formed.
  • a cross-sectional structure 52 depicted in Fig. 5B the inside of a tube is separated uniformly into three chambers, and each of high-pressure refrigerant, middle-pressure refrigerant and low-pressure refrigerant is flowed through each chamber.
  • Port 55 shows a high-pressure side refrigerant port
  • port 56 shows a low-pressure side refrigerant port
  • port 57 shows a middle-pressure side refrigerant port, respectively.
  • Fig. 6 is a vertical sectional view of the above-described gas cooler module 31, showing the more detailed structure thereof.
  • the refrigerant sent from compressor 1 passes through tubes 61 of the part of radiator 2, and radiated in heat through fins 62.
  • the refrigerant flows into a second tank 64 from a first tank 63 through tubes 6I, the oil contained in the refrigerant is trapped by demister 32 provided in second tank 64, and only the refrigerant flows into first tank 63 again through tubes 61.
  • the refrigerant flowed into first tank 63 flows from the part of radiator 2 to the part of inside heat exchanger 4 through the passageway in first tank 63.
  • the oil trapped by demister 32 provided in second tank 64 is reduced in pressure by second pressure reducer 5, and flows into inside heat exchanger 4 through the passageway in second tank 64.
  • the refrigerant flowed out from accumulator 8 is sent to the suction side of compressor 1 through inside heat exchanger 4.
  • inside heat exchanger 4 for example, flat tube structure
  • the oil containing a small amount of refrigerant after passing through second pressure reducer 5 (middle-pressure side refrigerant) and the low-pressure side refrigerant at the exit side of accumulator 8 are exchanged in heat with each other.
  • the flow of the refrigerant in the radiator may be any of a cross flow and a counter flow.
  • the temperature of the high-pressure side refrigerant is lowered. Further, by flowing the low-pressure side refrigerant through inside heat exchanger 4, the low-pressure side refrigerant is heated, and the refrigerant sucked into compressor 1 is prevented from becoming wet.
  • the high-pressure side refrigerant is used to heat the low-pressure side refrigerant, because heat exchange with the middle-pressure side refrigerant is performed, as compared with a conventional case where heat exchange is performed only between the high-pressure side refrigerant and the low-pressure side refrigerant, increase of the temperature of the low-pressure side refrigerant can be appropriately suppressed, and the low-pressure side refrigerant sucked into compressor 1 can be controlled at an optimum degree of superheating in consideration of the efficiency together with protection of compressor 1.
  • radiator 2 oil separator 3, second pressure reducer 5 and inside heat exchanger 4
  • the refrigeration ability can be increased, the problems on space and weight can be solved, and further, it is possible to decrease the number of equipment and junction parts, and therefore, prevention of refrigerant leakage and improvement of property of mounting on a vehicle can be expected.
  • 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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP07108423A 2006-05-30 2007-05-17 Dampf-Kompressionskältezyklus Withdrawn EP1862749A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006149628A JP4787070B2 (ja) 2006-05-30 2006-05-30 冷凍サイクル

Publications (2)

Publication Number Publication Date
EP1862749A2 true EP1862749A2 (de) 2007-12-05
EP1862749A3 EP1862749A3 (de) 2008-12-24

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009105601A1 (en) * 2008-02-20 2009-08-27 Trane International, Inc. Coaxial economizer assembly and method
US7856834B2 (en) 2008-02-20 2010-12-28 Trane International Inc. Centrifugal compressor assembly and method
EP2309208A1 (de) * 2008-05-20 2011-04-13 Sanden Corporation Kühlkreislauf
EP2314955A1 (de) * 2008-06-27 2011-04-27 Sanden Corporation Kühlkreislauf
US8037713B2 (en) 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
FR2960632A1 (fr) * 2010-05-31 2011-12-02 Valeo Systemes Thermiques Echangeur de chaleur interne comportant trois chemins de circulation de fluide
EP2568247A3 (de) * 2011-09-07 2014-07-16 LG Electronics Klimaanlage
US9353765B2 (en) 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
EP3217115A4 (de) * 2014-11-04 2018-07-18 Mitsubishi Electric Corporation Klimatisierungsvorrichtung
EP3742069A1 (de) * 2019-05-21 2020-11-25 Carrier Corporation Kühlvorrichtung und verwendung davon
EP4242551A4 (de) * 2020-11-04 2023-12-06 Mitsubishi Electric Corporation Kältekreislaufvorrichtung

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008046590A1 (de) * 2008-09-10 2010-03-11 Bayerische Motoren Werke Aktiengesellschaft Fahrzeugklimaanlage
KR102086378B1 (ko) * 2013-03-11 2020-03-10 주식회사 두원공조 차량용 냉방시스템
JP2014185811A (ja) * 2013-03-22 2014-10-02 Fujitsu General Ltd 冷凍サイクル装置
JP6929318B2 (ja) * 2019-03-28 2021-09-01 東プレ株式会社 冷凍装置及び冷凍装置の運転方法
CN111059806B (zh) * 2019-09-16 2022-01-18 江苏奥利维尔环境设备有限公司 一种具有油分离功能的空调主机、空调系统及油分离方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0924478A2 (de) * 1997-12-15 1999-06-23 Carrier Corporation Kälteanlage mit eingegliedertem Wärmetauscher zur Ölkühlung
EP0976991A2 (de) * 1998-07-31 2000-02-02 Zexel Corporation Kältekreislauf
JP2000274890A (ja) * 1999-03-18 2000-10-06 Nippon Soken Inc 超臨界サイクル
JP2001027460A (ja) * 1993-12-28 2001-01-30 Mitsubishi Electric Corp 冷凍サイクル装置
JP2002333221A (ja) * 2001-05-01 2002-11-22 Mitsubishi Heavy Ind Ltd ガスクーラ及び車載用空調装置
EP1394479A2 (de) * 2002-08-30 2004-03-03 Sanyo Electric Co., Ltd. Kältemittelkreislauf und Kompressor
EP1647783A2 (de) * 2004-10-18 2006-04-19 Mitsubishi Denki Kabushiki Kaisha Klima-/Kühlanlage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS602179U (ja) * 1983-06-20 1985-01-09 三洋電機株式会社 熱交換装置
JP2001174102A (ja) * 1999-12-13 2001-06-29 Mitsubishi Heavy Ind Ltd 空調装置
JP2003021409A (ja) * 2001-07-10 2003-01-24 Japan Climate Systems Corp 車両用空調装置
JP2003148814A (ja) * 2001-11-15 2003-05-21 Matsushita Electric Ind Co Ltd 冷凍装置
JP2004092933A (ja) * 2002-08-29 2004-03-25 Zexel Valeo Climate Control Corp 冷凍サイクル
JP4112392B2 (ja) * 2003-02-07 2008-07-02 株式会社日本クライメイトシステムズ 車両用空調装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001027460A (ja) * 1993-12-28 2001-01-30 Mitsubishi Electric Corp 冷凍サイクル装置
EP0924478A2 (de) * 1997-12-15 1999-06-23 Carrier Corporation Kälteanlage mit eingegliedertem Wärmetauscher zur Ölkühlung
EP0976991A2 (de) * 1998-07-31 2000-02-02 Zexel Corporation Kältekreislauf
JP2000274890A (ja) * 1999-03-18 2000-10-06 Nippon Soken Inc 超臨界サイクル
JP2002333221A (ja) * 2001-05-01 2002-11-22 Mitsubishi Heavy Ind Ltd ガスクーラ及び車載用空調装置
EP1394479A2 (de) * 2002-08-30 2004-03-03 Sanyo Electric Co., Ltd. Kältemittelkreislauf und Kompressor
EP1647783A2 (de) * 2004-10-18 2006-04-19 Mitsubishi Denki Kabushiki Kaisha Klima-/Kühlanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"2002 Ashrae Handbook, Refrigeration" 2002, ASHRAE , ATLANTA , XP002503576 * page 2.31, right-hand column * *

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101952671B (zh) * 2008-02-20 2013-04-17 特灵国际有限公司 同轴节能器组件和方法
US7856834B2 (en) 2008-02-20 2010-12-28 Trane International Inc. Centrifugal compressor assembly and method
US9683758B2 (en) 2008-02-20 2017-06-20 Trane International Inc. Coaxial economizer assembly and method
US9556875B2 (en) 2008-02-20 2017-01-31 Trane International Inc. Centrifugal compressor assembly and method
WO2009105601A1 (en) * 2008-02-20 2009-08-27 Trane International, Inc. Coaxial economizer assembly and method
US7975506B2 (en) 2008-02-20 2011-07-12 Trane International, Inc. Coaxial economizer assembly and method
US8037713B2 (en) 2008-02-20 2011-10-18 Trane International, Inc. Centrifugal compressor assembly and method
US9353765B2 (en) 2008-02-20 2016-05-31 Trane International Inc. Centrifugal compressor assembly and method
US8627680B2 (en) 2008-02-20 2014-01-14 Trane International, Inc. Centrifugal compressor assembly and method
EP2309208A4 (de) * 2008-05-20 2011-07-06 Sanden Corp Kühlkreislauf
EP2309208A1 (de) * 2008-05-20 2011-04-13 Sanden Corporation Kühlkreislauf
EP2314955A4 (de) * 2008-06-27 2011-11-02 Sanden Corp Kühlkreislauf
EP2314955A1 (de) * 2008-06-27 2011-04-27 Sanden Corporation Kühlkreislauf
FR2960632A1 (fr) * 2010-05-31 2011-12-02 Valeo Systemes Thermiques Echangeur de chaleur interne comportant trois chemins de circulation de fluide
EP2568247A3 (de) * 2011-09-07 2014-07-16 LG Electronics Klimaanlage
EP3217115A4 (de) * 2014-11-04 2018-07-18 Mitsubishi Electric Corporation Klimatisierungsvorrichtung
EP3742069A1 (de) * 2019-05-21 2020-11-25 Carrier Corporation Kühlvorrichtung und verwendung davon
EP4242551A4 (de) * 2020-11-04 2023-12-06 Mitsubishi Electric Corporation Kältekreislaufvorrichtung

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