EP3141857A1 - Radiateur et cycle frigorifique à pression supercritique l'utilisant - Google Patents

Radiateur et cycle frigorifique à pression supercritique l'utilisant Download PDF

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Publication number
EP3141857A1
EP3141857A1 EP16183460.1A EP16183460A EP3141857A1 EP 3141857 A1 EP3141857 A1 EP 3141857A1 EP 16183460 A EP16183460 A EP 16183460A EP 3141857 A1 EP3141857 A1 EP 3141857A1
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EP
European Patent Office
Prior art keywords
heat transfer
refrigerant
transfer pipe
refrigerant flow
transfer pipes
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.)
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Application number
EP16183460.1A
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German (de)
English (en)
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EP3141857B1 (fr
Inventor
Takeshi Takeda
Kenichi Murakami
Minemasa Omura
Hitonobu SATO
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP3141857A1 publication Critical patent/EP3141857A1/fr
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    • 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
    • F28D1/047—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 the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • 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
    • F28D1/053—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 the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • 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
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements

Definitions

  • the present invention relates to a radiator for radiating heat of a refrigerant that is pressurized to supercritical pressure and for cooling the refrigerant, and a supercritical pressure refrigeration cycle using the radiator.
  • a supercritical pressure refrigeration cycle using CO 2 (carbon dioxide) as a refrigerant includes a compressor that pressurizes the CO 2 refrigerant to supercritical pressure, and a radiator (gas cooler) that radiates heat of the CO 2 refrigerant discharged from the compressor, and cools the CO 2 refrigerant (refer to Japanese Unexamined Patent Application, Publication No. 2007-232365 , for example).
  • a radiator applied to this type of supercritical pressure refrigeration cycle a fin and tube type heat exchanger including a large number of plate fins disposed at predetermined intervals, and a plurality of heat transfer pipes that are inserted into the plate fins, and allow a refrigerant to flow therein is generally used, and high efficiency of heat exchange with outside air is attained.
  • a heat exchanger that includes a plurality of refrigerant flow passages formed in parallel, and that attains improvement of cooling or heating capacity is known (refer to Japanese Unexamined Patent Application, Publication Nos. Hei07-208822 and Hei08-121915 , for example).
  • the refrigerant is not condensed, and circulates in the radiator as a gas refrigerant in the supercritical pressure state with sensible heat change.
  • COP coefficient of performance
  • an outlet heat transfer pipe of one of refrigerant flow passages, and an inlet heat transfer pipes of the one of the refrigerant flow passages and other refrigerant flow passages are disposed adjacent to each other, and therefore there is a fear that the outlet temperature of the refrigerant is increased by the high-temperature refrigerants flowing through the inlet heat transfer pipes.
  • the present invention has been made in view of the above circumstances, and an object of the invention is to provide a radiator capable of enhancing heat exchanging performance, and further reducing the refrigerant temperature at a refrigerant flow passage outlet, and a supercritical pressure refrigeration cycle using the same.
  • the radiator, and the supercritical pressure refrigeration cycle using the same of the present invention employ the following solutions.
  • a radiator according to the present invention is a radiator for radiating heat of a refrigerant that is pressurized to supercritical pressure, the radiator including: multiple plate fins extending in a vertical direction and disposed at a predetermined pitch; and a plurality of refrigerant flow passages formed in parallel by multiple heat transfer pipe group inserted into the plate fins in multiple stages, wherein the plurality of refrigerant flow passages each include an inlet heat transfer pipe provided in upper parts of the plate fins, an outlet heat transfer pipe provided in lower parts of the plate fins, and an intermediate heat transfer pipe provided between the inlet heat transfer pipe and the outlet heat transfer pipe, and a flow passage cross sectional area of the refrigerant flow passages is gradually reduced from the inlet heat transfer pipes to the outlet heat transfer pipes.
  • the inlet heat transfer pipes are provided in the upper parts of the plate fins, and the outlet heat transfer pipes are provided in the lower parts of the plate fins, and therefore the outlet heat transfer pipe of one of the refrigerant flow passages can be disposed to separate from the inlet heat transfer pipes of the one of the refrigerant flow passages and other refrigerant flow passages.
  • the intermediate heat transfer pipes are provided between the inlet heat transfer pipes and the outlet heat transfer pipes, and therefore the inlet heat transfer pipes and the outlet heat transfer pipes are not adjacent to each other.
  • the flow passage cross sectional area of the refrigerant flow passages is gradually reduced from the inlet heat transfer pipes to the outlet heat transfer pipes, and therefore even when the cooling proceeds, and the gas density (specific gravity) of the refrigerants is increased, reduction in the flow velocity of the refrigerants is prevented, and heat exchange efficiency can be maintained. Accordingly, the refrigerant outlet temperatures are never increased by the high temperature refrigerants that flow through the inlet heat transfer pipes, and the refrigerant temperature at a radiator outlet can be further reduced by performance improvement of the radiator, and it is possible to improve the coefficient of performance (COP) of the refrigeration cycle.
  • COP coefficient of performance
  • the flow passage cross sectional area of the refrigerant flow passages is reduced by gradual reduction in the number of circuits of the inlet heat transfer pipes, the intermediate heat transfer pipes and the outlet heat transfer pipes.
  • the flow passage cross sectional area of the refrigerant flow passages is reduced by the gradual reduction in the number of circuits of the inlet heat transfer pipes, the intermediate heat transfer pipes, and the outlet heat transfer pipes, and therefore even when the cooling proceeds while the refrigerants entering from the inlet heat transfer pipes circulate in the intermediate heat transfer pipes and the outlet heat transfer pipes, and the gas density (specific gravity) of the refrigerants is increased, the flow passage cross sectional area of the refrigerant flow passages is gradually reduced in the refrigerant flow direction, so that reduction in the flow velocity of the refrigerants is prevented, and heat exchange efficiency can be maintained. Accordingly, high heat exchanging performance of the radiator is enhanced, and the refrigerant outlet temperature is further lowered, so that it is possible to improve the coefficient of performance of the refrigeration cycle.
  • the flow passage cross sectional area of the refrigerant flow passages is reduced by gradual reduction in flow passage diameters of the inlet heat transfer pipes, the intermediate heat transfer pipes, and the outlet heat transfer pipes.
  • the flow passage cross sectional area of the refrigerant flow passages is reduced by the gradual reduction in the flow passage diameters of the inlet heat transfer pipes, the intermediate heat transfer pipes, and the outlet heat transfer pipes, and therefore even when the cooling proceeds while the refrigerants entering from the inlet heat transfer pipes circulate in the intermediate heat transfer pipes and the outlet heat transfer pipes sequentially, and the gas density (specific gravity) of the refrigerants is increased, the flow passage cross sectional area of the refrigerant flow passages is gradually reduced in the refrigerant flow direction, so that reduction in the flow velocity of the refrigerants is prevented, and heat exchange efficiency can be maintained. Accordingly, high heat exchanging performance of the radiator is enhanced, and the refrigerant outlet temperature is further reduced, so that it is possible to improve the coefficient of performance of the refrigeration cycle.
  • each of the refrigerant flow passages is formed such that the refrigerant circulates from the inlet heat transfer pipe of an upper stage to the outlet heat transfer pipe of a lower stage.
  • each refrigerant flow passages is formed such that the refrigerant circulates from the inlet heat transfer pipe of the upper stage to the outlet heat transfer pipe of the lower stage. Accordingly, the refrigerant that is pressurized to the supercritical pressure is cooled but is not condensed in the radiator, and the gas density (specific gravity) is increased, but each refrigerant flow passages is formed so as to allow the refrigerant to flow from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage, so that it is possible to facilitate the circulation of the refrigerants in the radiator by gravity. Consequently, it is possible to improve heat exchange efficiency of the radiator, and further lower the refrigerant outlet temperature.
  • the radiator of the present invention further includes a plurality of heat exchange parts divided up and down, wherein each of the refrigerant flow passages is formed such that the refrigerant flows from the upper heat exchange part to the lower heat exchange part.
  • the radiator includes the plurality of heat exchange parts divided up and down, the refrigerant flow passages are each formed such that the refrigerant flows from the upper heat exchange part toward the lower heat exchange part, and therefore it is possible to form the temperature gradient of gradually lowering from the upper heat exchange part toward the lower heat exchange part. Consequently, it is possible to suppress temperature irregularity in the radiator to improve heat exchange efficiency, and further lower the refrigerant outlet temperature.
  • each of the refrigerant flow passages includes a first intermediate heat transfer pipe continued to the inlet heat transfer pipe, and a second intermediate heat transfer pipe or a third intermediate heat transfer pipe continued to the outlet heat transfer pipe, and includes an intermediate header connected to all the first intermediate heat transfer pipes, the second intermediate heat transfer pipes or the third intermediate heat transfer pipes of the refrigerant flow passages.
  • each of the refrigerant flow passages includes the first intermediate heat transfer pipe continued to the inlet heat transfer pipe, and the second intermediate heat transfer pipe or the third intermediate heat transfer pipe continued to the outlet heat transfer pipe, and includes the intermediate header connected to all the first intermediate heat transfer pipes, the second intermediate heat transfer pipes or the third intermediate heat transfer pipes of the refrigerant flow passages, and therefore even in a case where distribution of the refrigerants in the inlet heat transfer pipes of the refrigerant flow passages is inappropriate, the refrigerants are collected in the intermediate header once, and thereafter distributed in the refrigerant flow passages again, and therefore the distribution can be made appropriate. Consequently, the distribution of the refrigerants into the respective refrigerant flow passages is made appropriate, and heat exchanging performance of the radiator is improved, and it is possible to further lower the refrigerant outlet temperature.
  • the heat transfer pipe group is inserted into the plate fins in multiple rows and stages, and the inlet heat transfer pipes are disposed in a row on a leeward side with respect to the outlet heat transfer pipes.
  • the heat transfer pipe group is inserted into the plate fins in the multiple rows and stages, and the inlet heat transfer pipes are disposed in the row on the leeward side with respect to the outlet heat transfer pipes, and therefore the refrigerants flowing through the outlet heat transfer pipes can be prevented from being heated by air whose temperature is increased due to heat exchange with the high temperature refrigerants flowing through the inlet heat transfer pipes, and increase in the refrigerant outlet temperature can be suppressed. Accordingly, it is possible to further lower the refrigerant outlet temperature of the radiator, and improve the coefficient of performance of the refrigeration cycle.
  • a supercritical pressure refrigeration cycle includes: any of the above radiators; and a closed-cycle refrigerant circuit connecting a compressor for pressurizing a refrigerant to supercritical pressure, a decompression device, and a load side heat exchanger by piping.
  • the supercritical pressure refrigeration cycle includes: any of the above radiators; and the closed-cycle refrigerant circuit connecting the compressor for pressurizing the refrigerant to supercritical pressure, the decompression device, and the load side heat exchanger by piping, and therefore the high-performance radiator having improved heat exchange efficiency and heat exchanging performance is incorporated, so that it is possible to enhance the cooling effect of the refrigerant, and further lower the refrigerant temperature at a radiator outlet. Accordingly, it is possible to provide the supercritical pressure refrigeration cycle having a further enhanced coefficient of performance (COP).
  • COP coefficient of performance
  • the outlet heat transfer pipe of one of the refrigerant flow passages can be disposed to separate from the inlet heat transfer pipes of the one of the refrigerant flow passages and other refrigerant flow passages. Additionally, the inlet heat transfer pipes are not adjacent to the outlet heat transfer pipes, and even when the cooling proceeds, and the gas density (specific gravity) of the refrigerants is increased, reduction in the flow velocity of the refrigerants is prevented, and heat exchange efficiency can be maintained.
  • the refrigerant outlet temperature is never increased by the high temperature refrigerants that flow through the inlet heat transfer pipes, and can further reduce the refrigerant temperature at a radiator outlet by performance improvement of the radiator, and it is possible to improve the coefficient of performance (COP) of the refrigeration cycle.
  • COP coefficient of performance
  • the high-performance radiator having improved heat exchange efficiency and heat exchanging performance is incorporated, so that it is possible to enhance the cooling effect of the refrigerant, and further lower the refrigerant temperature at the radiator outlet. Accordingly, it is possible to provide the supercritical pressure refrigeration cycle having further enhanced coefficient of performance (COP).
  • COP coefficient of performance
  • FIG. 1 is a configuration diagram of a supercritical pressure refrigeration cycle according to the first embodiment of the present invention
  • FIG. 2 is a Mollier diagram of the supercritical pressure refrigeration cycle
  • FIG. 3 is a schematic diagram of a radiator applied to the cycle.
  • the present invention is not limited to the following embodiments, and it goes without saying that components in the following embodiments include components that are replaceable and easy to replace by a person skilled in the art, or substantially the same components.
  • a supercritical pressure refrigeration cycle 10 includes a heat source unit 11 and a load unit 12.
  • a liquid refrigerant pipe 13 and a gas refrigerant pipe 14 connect the heat source unit 11 and the load unit 12, so that a closed-cycle refrigerant circuit 15 is formed.
  • This closed-cycle refrigerant circuit 15 is filled with a carbon dioxide refrigerant (hereinafter referred to as a CO 2 refrigerant) whose high pressure side becomes supercritical pressure.
  • the CO 2 refrigerant is a refrigerant having an advantage of having a small load to environment, has no toxicity, has no combustibility, and is safe and cheap.
  • refrigerant as long as the high pressure side becomes supercritical pressure, of course, other refrigerant may be used.
  • the heat source unit 11 includes a compressor 16 that compresses a refrigerant, and an oil separator 18, a radiator (gas cooler) 19, and an expansion valve (decompression device) 20 are sequentially connected on the discharge side of the compressor 16 through a refrigerant discharge pipe 17.
  • a heat source unit side liquid refrigerant pipe 30 for allowing a liquefied refrigerant to circulate is connected on the outlet side of the expansion valve 20, and is connected to the liquid refrigerant pipe 13.
  • a heat source unit side refrigerant suction pipe 21 is connected on the suction side of the compressor 16, and is connected to the gas refrigerant pipe 14 through an accumulator (not illustrated) and the like.
  • the compressor 16 includes an electric motor and a compression element 23 in a sealed housing 22,
  • the compression element 23 herein is a two-stage compressible compressor including a low stage compression element and a high stage compression element, and compresses low pressure refrigerant gas sucked through the refrigerant suction pipe 21 to discharge, to the refrigerant discharge pipe 17, high temperature and high pressure refrigerant gas that is pressurized to supercritical pressure.
  • the compression element 23 is driven by the electric motor (not illustrated), and the rotational frequency of the compression element 23 is adjustable by change in the operation frequency of the electric motor.
  • oil for lubricating respective parts (a bearing and a sliding part) of the compression element 23 is housed, and a sensor 29 that detects oil quantity in the sealed housing 22 is provided.
  • the oil separator 18 separates oil contained in the high pressure refrigerant gas (supercritical pressure) discharged from the compressor 16, from a refrigerant.
  • This oil separator 18 includes an oil return pipe 24 that returns the separated oil to the sealed housing 22 of the compressor 16, and the oil return pipe 24 is connected to the refrigerant suction pipe 21 through a solenoid valve 25, and a capillary tube (throttle) 26.
  • the solenoid valve 25 opens/closes on the basis of a signal of the sensor 29 that detects oil quantity.
  • the gas cooler 19 heat-exchanges the high temperature and high pressure (supercritical pressure) refrigerant gas discharged from the compressor 16 with outside air, and radiates heat to cool the high temperature and high pressure (supercritical pressure) refrigerant gas.
  • the gas cooler 19 is composed of a fin and tube type heat exchanger, and is disposed so as to face a blower fan (not illustrated) that blows outside air to the heat exchanger.
  • the expansion valve 20 decompresses (expands) and liquefies the gas refrigerant cooled by the gas cooler 19.
  • the load unit 12 includes a load unit side pipe 27 connected to the liquid refrigerant pipe 13 and the gas refrigerant pipe 14, and a vaporizer (load side heat exchanger) 28 provided in this load unit side pipe 27, vaporizes a liquid refrigerant supplied through the liquid refrigerant pipe 13 by use of the vaporizer 28, and is used as an indoor unit for cooling that cools an object to be cooled such as air, or various cooling apparatuses for freezing/refrigerating.
  • the vaporizer 28 is composed of a fin and tube type heat exchanger similarly to the gas cooler 19, and is provided with a blower fan (not illustrated) that blows air to be cooled to the heat exchanger.
  • the vaporizer 28 is used for cooling or freezing and refrigerating by absorbing heat from the air to be cooled, vaporizing the liquid refrigerant, and cooling the air.
  • the low temperature and low pressure refrigerant gas vaporized by the vaporizer 28 passes through the gas refrigerant pipe 14, the accumulator, and the refrigerant suction pipe 21 to be sucked in the compressor 16, and is compressed again.
  • the single load unit 12 is connected in this embodiment, a plurality of the load units 12 having the vaporizers 28 may be connected in parallel.
  • each of the expansion valves 20 is desirably provided in the inlet side (liquid refrigerant pipe 13 side) of the vaporizer 28 in each load unit side pipe 27.
  • FIG. 2 is a Mollier diagram of the supercritical pressure refrigeration cycle 10 of the refrigerant that is pressurized to the supercritical pressure.
  • a point A shows the pressure and the enthalpy of the refrigerant on the suction side of the compressor 16.
  • a point B shows the pressure and the enthalpy of the refrigerant on the inlet side of the gas cooler 19
  • a point C shows the pressure and the enthalpy of the refrigerant on the outlet side of the gas cooler 19
  • a point D shows the pressure and the enthalpy of the refrigerant on the inlet side of the vaporizer 28.
  • the broken lines in FIG. 2 illustrate respective isotherms.
  • the sensible heat change by cooling is performed.
  • enthalpy quantity of 120°C to 100°C, enthalpy quantity of 100°C to 80°C, enthalpy quantity of 80°C to 60°C, and enthalpy quantity of 60°C to about 35°C are denoted by a, b, c, and d, respectively
  • the enthalpy quantities satisfy a ⁇ b ⁇ c ⁇ d
  • the enthalpy quantity d of 60°C to about 35°C is particularly larger than the enthalpy quantities in other temperature ranges.
  • the refrigerant outlet temperature in the gas cooler 19 is further reduced, so that a cooling effect can be increased by the lowered amount, and it is possible to improve a coefficient of performance (COP).
  • COP coefficient of performance
  • FIG. 3 is a schematic diagram of the gas cooler 19 according to this embodiment.
  • the gas cooler 19 includes a large number of strip-like plate fins 31 vertically extending and disposed in parallel to each other at predetermined intervals (pitches), and a heat transfer pipe group 33 composed of a plurality of heat transfer pipes penetrating a large number of these plate fins 31, and allows air to flow in the direction orthogonal to a paper surface.
  • the heat transfer pipe group 33 is disposed in one row multiple stages (12 stages in this embodiment) in the vertical direction of the plate fins 31.
  • An in-radiator refrigerant flow passage is formed by the heat transfer pipe group 33 such that a plurality of branched refrigerant flow passages 34A, 34B, 34C (three in this embodiment) are formed in parallel on the inlet side, and the number of refrigerant flow passages (the number of circuits) is reduced to two refrigerant flow passages 34D, 34E from the above branched refrigerant flow passages 34A, 34B, 34C toward the outlet side, and a single refrigerant flow passage 34F is further formed on the outlet side.
  • the in-radiator refrigerant flow passage is formed so as to branch the refrigerant flow passage into the plurality of refrigerant flow passages 34A, 34B, 34C on the inlet side, and gradually reduce the number of the refrigerant flow passages from the inlet to the outlet, so that the refrigerant is distributed to flow through the respective refrigerant flow passages 34A, 34B, 34C, and therefore it is possible to reduce the flow rate of the refrigerant flowing through each of the refrigerant flow passages 34A, 34B, 34C, and it is possible to shorten a refrigerant flow passage length from the refrigerant flow passages 34A, 34B, 34C to the single refrigerant flow passage 34F on the outlet side. Consequently, it is possible to reduce the pressure loss of the refrigerants in the gas cooler 19 to improve the coefficient of performance.
  • the number of the refrigerant flow passages (the number of circuits) in the gas cooler 19 is gradually reduced from the inlet side to the outlet side, and the flow passage cross sectional area of the refrigerant flow passages is gradually reduced with the reduction in the number of the refrigerant flow passages, so that even when the cooling of the refrigerants in the gas cooler 19 proceeds, and the gas density (specific gravity) of the refrigerants is gradually increased with this cooling, reduction in the flow velocity of the refrigerants is prevented, and heat exchange efficiency is maintained, so that it is possible to obtain high heat exchanging performance.
  • the gas cooler 19 includes an inlet header 36 connected to an inlet pipe 35 (refrigerant discharge pipe 17) through the oil separator 18, and an outlet side header 38, and forms the in-radiator refrigerant flow passage such that the three refrigerant flow passages 34A, 34B, 34C on the inlet side are first reduced to the two refrigerant flow passages 34D, 34E, and further reduced to the single refrigerant flow passage 34F on the outlet side between this inlet header 36 and the outlet side header 38, the number of the refrigerant flow passages (the number of circuits) is reduced in the pattern of 3 ⁇ 2 ⁇ 1.
  • This in-radiator refrigerant flow passage is formed by connecting four heat transfer pipes, has a configuration in which a refrigerant flows from the upper side to the lower side in the height direction (vertical direction) of the gas cooler 19, and has a configuration in which an outlet heat transfer pipe 42C of a lowermost stage is connected to an outlet pipe 37 (refrigerant discharge pipe 17) which leads to the expansion valve 20.
  • the refrigerant flow passages 34A, 34B, 34C on the inlet side include inlet heat transfer pipes 40A, 40B, 40C connected to the inlet header 36, respectively, and these inlet heat transfer pipes 40A, 40B, 40C are disposed in upper parts (the first stage, the third stage, the fifth stage) of the plate fins 31.
  • Third intermediate heat transfer pipes 41A3, 41B3 are disposed on the outlet side, and connected to the outlet side header 38 that allows the plurality of refrigerant flow passages 34D, 34E to merge into the single refrigerant flow passage 34F, and outlet heat transfer pipes 42A1, 42A2 continued to the outlet pipe 37 (refrigerant discharge pipe 17) are disposed below the third intermediate heat transfer pipes 41A3, 41B3.
  • These third intermediate heat transfer pipes 41A3, 41B3 and the outlet heat transfer pipes 42A1, 42A2 are disposed on lower parts of the plate fins 31 (the eighth stage, the tenth stage, the eleventh stage, and the twelfth stage).
  • the refrigerant flow passage 34A includes a first intermediate heat transfer pipe 41A1 connected to the inlet heat transfer pipe 40A through a U-shaped pipe 43.
  • This refrigerant flow passage 34A is communicated with both the refrigerant flow passages 34D, 34E including second intermediate heat transfer pipes 41A2, 41B2 connected to the third intermediate heat transfer pipes 41A3, 41B3 respectively through U-shaped pipes 43, through an intermediate header 44.
  • the first intermediate heat transfer pipe 41A1 is disposed below the inlet heat transfer pipe 40A by one stage, and the second intermediate heat transfer pipe 41A2 is disposed above the third intermediate heat transfer pipe 41A3 by one stage.
  • the first intermediate heat transfer pipe 41A1 and the second intermediate heat transfer pipes 41A2 and 41B2 are communicated with each other through the intermediate header 44. Accordingly, the refrigerant flowing in the refrigerant flow passage 34A passes through the inlet heat transfer pipe 40A, and the first intermediate heat transfer pipe 41A1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34B includes a first intermediate heat transfer pipe 41B1 connected to the inlet heat transfer pipe 40B through a U-shaped pipe 43.
  • the refrigerant flow passage 34B is communicated with both the refrigerant flow passages 34D, 34E including the second intermediate heat transfer pipes 41A2, 41B2 connected to the third intermediate heat transfer pipes 41A3, 41B3 respectively through U-shaped pipes 43, through the intermediate header 44.
  • the first intermediate heat transfer pipe 41B1 is disposed below the inlet heat transfer pipe 40B by one stage, and the second intermediate heat transfer pipe 41B2 is disposed above the third intermediate heat transfer pipe 41B3 by one stage.
  • the first intermediate heat transfer pipe 41B1, and the second intermediate heat transfer pipes 41A2 and 41B2 are communicated with each other through the intermediate header 44. Accordingly, the refrigerant flowing in the refrigerant flow passage 34B passes through the inlet heat transfer pipe 40B, and the first intermediate heat transfer pipe 41B1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34C includes a first intermediate heat transfer pipe 41C1 connected to the inlet heat transfer pipe 40C through a U-shaped pipe 43.
  • This refrigerant flow passage 34C is communicated with both the refrigerant flow passages 34D, 34E including the second intermediate heat transfer pipes 41A2, 41B2 connected to the third intermediate heat transfer pipes 41A3, 41B3 respectively through U-shaped pipes 43, through the intermediate header 44.
  • the first intermediate heat transfer pipe 41C1 is disposed below the inlet heat transfer pipe 40C by one stage. Additionally, the first intermediate heat transfer pipe 41C1, and the second intermediate heat transfer pipes 41A2 and 41B2 are communicated with each other through the intermediate header 44.
  • the refrigerant flowing in the refrigerant flow passage 34C passes through the inlet heat transfer pipe 40C, and the first intermediate heat transfer pipe 41C1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerants distributed into the three refrigerant flow passages 34A, 34B, 34C to flow in the gas cooler 19 flow in the two refrigerant flow passages 34D, 34E formed by the second intermediate heat transfer pipes 41A2, 41B2 and the third intermediate heat transfer pipes 41A3, 41B3, through the first intermediate heat transfer pipes 41A1, 41B1, 41C1 and the intermediate header 44.
  • the number of the refrigerant flow passages is reduced from 3 to 2
  • the flow passage cross sectional area is reduced to two-thirds.
  • the outlet heat transfer pipe 42A1 is disposed below the third intermediate heat transfer pipe 41B3 by one stage, and is connected to the outlet side header 38, and the outlet heat transfer pipe 42A2 connected to the outlet pipe 37 (refrigerant discharge pipe 17) is disposed below this outlet heat transfer pipe 42A1 by one stage, and is connected to the outlet heat transfer pipe 42A1 through the U-shaped pipe 43.
  • This outlet side header 38 allows the refrigerants that circulate in the two refrigerant flow passages 34D, 34E formed by the second intermediate heat transfer pipes 41A2, 41B2 and the third intermediate heat transfer pipes 41A3, 41B3 into merge and flow to the single refrigerant flow passage 34F formed by the outlet heat transfer pipes 42A1, 42A2.
  • the number of the refrigerant flow passages (the number of circuits) is reduced from 2 to 1, and the flow passage cross sectional area is further reduced to one-half.
  • the gas cooler 19 includes an upper heat exchange part 45 and a lower heat exchange part 46 formed by division into a plurality of parts (two in this embodiment) in the height direction (vertical direction).
  • the refrigerant flow passages 34A, 34B, 34C on the inlet side are formed on the upper heat exchange part 45 side.
  • the inlet heat transfer pipes 40A, 40B, 40C and the first intermediate heat transfer pipes 41A1, 41B1, 41C1 that form the refrigerant flow passages 34A, 34B, 34C, respectively are provided in the upper heat exchange part 45
  • the second intermediate heat transfer pipes 41A2, 41B2, the third intermediate heat transfer pipes 41A3, 41B3, and the outlet heat transfer pipes 42A1, 42A2 that form the refrigerant flow passages 34D, 34E and 34F on the downstream side respectively are connected to the inlet heat transfer pipes 40A, 40B, 40C and the first intermediate heat transfer pipes 41A1, 41B1, 41C1 through the intermediate header 44, respectively, and the lower heat exchange part 46 is provided.
  • the inlet heat transfer pipes 40A, 40B, 40C and the first intermediate heat transfer pipes 41A1, 41B1, 41C1 are disposed in the respective upper parts of the plate fins 31, and the outlet heat transfer pipes 42A1, 42A2 that form the single refrigerant flow passage 34F on the downstream side are disposed in the respective lower parts of the plate fins 31, and therefore the outlet heat transfer pipes 42A1, 42A2 that form the refrigerant flow passage 34F can be disposed to separate from the inlet heat transfer pipes 40A, 40B, 40C forming its own and other refrigerant flow passages.
  • the first intermediate heat transfer pipes (intermediate heat transfer pipes) 41A1, 41B1, 41C1, the second intermediate heat transfer pipes (intermediate heat transfer pipes) 41A2, 41B2, and the third intermediate heat transfer pipes (intermediate heat transfer pipes) 41A3, 41B3 are disposed between the inlet heat transfer pipes 40A, 40B, 40C, and the outlet heat transfer pipes 42A1, 42A2, respectively, and therefore the inlet heat transfer pipes 40A, 40B, 40C, and the outlet heat transfer pipes 42A1, 42A2 are not adjacent to each other.
  • the refrigerants circulate in the inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, the third intermediate heat transfer pipes 41A3, 41B3, and the outlet heat transfer pipes 42A1, 42A2 in order from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage.
  • the refrigerant that is pressurized to the supercritical pressure is not condensed in the gas cooler 19, but the density (specific gravity) of refrigerant gas is increased with the cooling.
  • the in-radiator refrigerant flow passage is formed such that the refrigerants flow from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage, so that it is possible to facilitate the circulation of the refrigerants by gravity to improve heat exchange efficiency.
  • the refrigerants are gradually cooled from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage, and therefore a temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be made below a predetermined temperature, and heat transfer between the adjacent heat transfer pipes can be suppressed.
  • the outlet-inlet temperature difference of the gas cooler 19 is 85°C in this embodiment, and therefore the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 20°C to 25°C.
  • the outlet-inlet temperature difference of the gas cooler 19 is generally about 60°C, and therefore, in this case, the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 15°C.
  • the gas cooler 19 includes the upper heat exchange part 45 and the lower heat exchange part 46 divided up and down, and the refrigerant flow passages 34A, 34B, 34C, 34D, 34E, 34F forming the in-radiator refrigerant flow passage each has a configuration in which the refrigerant sequentially flows from the upper heat exchange part 45 toward the lower heat exchange part 46, and therefore a temperature gradient of lowering a temperature from the upper heat exchange part 45 toward the lower heat exchange part 46 is formed. Therefore, it is possible to suppress temperature irregularity of the gas cooler 19.
  • the refrigerant flow passages 34A, 34B, 34C, 34D, 34E, 34F include the first intermediate heat transfer pipes 41A1, 41B1, 41C1 continued to the inlet heat transfer pipes 40A, 40B, 40C, and the second intermediate heat transfer pipes 41A2, 41B2 and the third intermediate heat transfer pipes 41A3, 41B3 continued to outlet heat transfer pipes 42A1, 42A2, and include the intermediate header 44 connected to all the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, and the third intermediate heat transfer pipes 41A3, 41B3, and therefore even when distribution of the refrigerants in the inlet heat transfer pipes 40A, 40B, 40C of the refrigerant flow passages 34A, 34B, 34C on the inlet side is inappropriate, the refrigerants are collected in the intermediate header 44 once, and thereafter distributed again when flowing through the refrigerant flow passages 34D, 34E, and therefore the distribution can be made appropriate. Consequently, it is possible to uniformize refrigerant distribution
  • the flow passage cross sectional area of the refrigerant flow passages in the gas cooler 19 is gradually reduced from the inlet side to the outlet side. That is, the number of the refrigerant flow passages of the refrigerant flow passages 34A, 34B, 34C on the inlet side, and the number of refrigerant flow passages (the number of circuits) of the refrigerant flow passages 34D, 34E and the refrigerant flow passage 34F continued to the downstream side of the refrigerant flow passages 34A, 34B, 34C is gradually reduced in a manner of 3 ⁇ 2 ⁇ 1, and the flow passage cross sectional area of the in-radiator refrigerant flow passage is gradually reduced from the inlet side to the outlet side.
  • FIG. 4 is a schematic diagram of a gas cooler according to another embodiment (1).
  • the flow passage cross sectional area of refrigerant flow passages in a gas cooler 50 is not gradually reduced from the inlet side to the outlet side by gradual reduction in the number of the refrigerant flow passages (the number of circuits), and the flow passage cross sectional area of an in-radiator refrigerant flow passage is gradually reduced from the inlet side to the outlet side by change in flow passage diameters of heat transfer pipes of the refrigerant flow passages.
  • a heat transfer pipe group 33 is disposed in one row multiple stages (12 stages in this embodiment) in the vertical direction of plate fins 31, and a plurality of refrigerant flow passages 34A, 34B, 34C (three in this embodiment) are formed in parallel by the heat transfer pipe group 33.
  • a plurality of the refrigerant flow passages 34A, 34B, 34C (the number of circuits: 3) are formed, so that the refrigerant is distributed into the refrigerant flow passages 34A, 34B, 34C to flow, and therefore it is possible to reduce the flow rate of the refrigerant flowing through each of the refrigerant flow passages 34A, 34B, 34C, and it is possible to shorten the respective refrigerant flow passage lengths of the refrigerant flow passages 34A, 34B, 34C. Consequently, it is possible to reduce the pressure loss of the refrigerants in the gas cooler 50 to improve a coefficient of performance.
  • the gas cooler 50 includes an inlet header 36 connected to an inlet pipe 35 (refrigerant discharge pipe 17) through an oil separator 18, and an outlet side header 38 connected to an outlet pipe 37 (refrigerant discharge pipe 17) which leads to an expansion valve 20, and the three refrigerant flow passages 34A, 34B, 34C are formed from the inlet to the outlet between the inlet header 36 and the outlet side header 38.
  • These refrigerant flow passages 34A, 34B, 34C are each formed by connecting four heat transfer pipes, and allow the refrigerant to flow from the upper side to the lower side in the height direction (vertical direction) of the gas cooler 50.
  • the refrigerant flow passages 34A, 34B, 34C include inlet heat transfer pipes 40A, 40B, 40C connected to the inlet header 36, respectively.
  • the inlet heat transfer pipes 40A, 40B, 40C are disposed in upper parts (the first stage, the third stage, the fifth stage) of the plate fins 31.
  • the refrigerant flow passages 34A, 34B, 34C include outlet heat transfer pipes 42A, 42B, 42C connected to the outlet side header 38, respectively. These outlet heat transfer pipes 42A, 42B, 42C are disposed in lower parts of the plate fins 31 (the eighth stage, the tenth stage, and the twelfth stage).
  • the refrigerant flow passage 34A includes a first intermediate heat transfer pipe 41A1 connected to the inlet heat transfer pipe 40A through a U-shaped pipe 43, and a second intermediate heat transfer pipe 41A2 connected to the outlet heat transfer pipe 42A through a U-shaped pipe 43.
  • the first intermediate heat transfer pipe 41A1 is disposed below the inlet heat transfer pipe 40A by one stage, and the second intermediate heat transfer pipe 41A2 is disposed above the outlet heat transfer pipe 42A by one stage. Additionally, the first intermediate heat transfer pipe 41A1 and the second intermediate heat transfer pipe 41A2 are communicated with each other through an intermediate header 44.
  • the refrigerant flows through the inlet heat transfer pipe 40A, the first intermediate heat transfer pipe 41A1, the second intermediate heat transfer pipe 41A2, and the outlet heat transfer pipe 42A in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34B includes a first intermediate heat transfer pipe 41B1 connected to the inlet heat transfer pipe 40B through a U-shaped pipe 43, and a second intermediate heat transfer pipe 41B2 connected to the outlet heat transfer pipe 42B through a U-shaped pipe 43.
  • the first intermediate heat transfer pipe 41B1 is disposed below the inlet heat transfer pipe 40B by one stage
  • the second intermediate heat transfer pipe 41B2 is disposed above the outlet heat transfer pipe 42B by one stage.
  • the first intermediate heat transfer pipe 41B1 and the second intermediate heat transfer pipe 41B2 are communicated with each other through the intermediate header 44.
  • the refrigerant flows through the inlet heat transfer pipe 40B, the first intermediate heat transfer pipe 41B1, the second intermediate heat transfer pipe 41B2, and the outlet heat transfer pipe 42B in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34C includes a first intermediate heat transfer pipe 41C1 connected to the inlet heat transfer pipe 40C through a U-shaped pipe 43, and a second intermediate heat transfer pipe 41C2 connected to the outlet heat transfer pipe 42C through a U-shaped pipe 43.
  • the first intermediate heat transfer pipe 41C1 is disposed below the inlet heat transfer pipe 40C by one stage
  • the second intermediate heat transfer pipe 41C2 is disposed above the outlet heat transfer pipe 42C by one stage.
  • the first intermediate heat transfer pipe 41C1 and the second intermediate heat transfer pipe 41C2 are communicated with each other through the intermediate header 44.
  • the refrigerant flows through the inlet heat transfer pipe 40C, the first intermediate heat transfer pipe 41C1, the second intermediate heat transfer pipe 41C2, and the outlet heat transfer pipe 42C in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the flow passage diameters of the four heat transfer pipes forming the flow passage of each of the refrigerant flow passages 34A, 34B, 34C namely, the inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, 41C2, and the outlet heat transfer pipes 42A, 42B, 42C are flow passage diameters satisfying the relation of inlet heat transfer pipe > first intermediate heat transfer pipe > second intermediate heat transfer pipe > outlet heat transfer pipe. Consequently, the respective flow passage cross sectional areas of the refrigerant flow passages 34A, 34B, 34C are set so as to be gradually reduced from the inlet side to the outlet side.
  • the flow passage diameter of each pipe expresses the inner diameter of a circular pipe, but means a fluid diameter that is a diameter conversion value of a pipe in a case of a pipe other than the circular pipe.
  • the present invention includes a case where the pipe other than the circular pipe is used.
  • the gas cooler 50 includes an upper heat exchange part 45 and a lower heat exchange part 46 formed by division into a plurality of parts (two in this embodiment) in the height direction (vertical direction).
  • the refrigerant flow passages 34A, 34B, 34C are each formed so as to sequentially circulate in the upper heat exchange part 45 and the lower heat exchange part 46. More specifically, in the refrigerant flow passage 34A, the inlet heat transfer pipe 40A and the first intermediate heat transfer pipe 41A1 are provided in the upper heat exchange part 45, and the second intermediate heat transfer pipe 41A2 and the outlet heat transfer pipe 42A are provided in the lower heat exchange part 46 through the intermediate header 44.
  • the inlet heat transfer pipe 40B and the first intermediate heat transfer pipe 41B1 are provided in the upper heat exchange part 45, and the second intermediate heat transfer pipe 41B2 and the outlet heat transfer pipe 42B are provided in the lower heat exchange part 46.
  • the inlet heat transfer pipe 40C and the first intermediate heat transfer pipe 41C1 are provided in the upper heat exchange part 45, and the second intermediate heat transfer pipe 41C2 and the outlet heat transfer pipe 42C are provided in the lower heat exchange part 46.
  • the inlet heat transfer pipes 40A, 40B, 40C are provided in the respective upper parts of the plate fins 31, and the outlet heat transfer pipes 42A, 42B, 42C are provided in the respective lower parts of the plate fins 31, and therefore the outlet heat transfer pipes 42A, 42B, 42C of the refrigerant flow passages 34A, 34B, 34C can be disposed to separate from the inlet heat transfer pipes 40A, 40B, 40C of its own and other refrigerant flow passages 34A, 34B, 34C.
  • the first intermediate heat transfer pipes (intermediate heat transfer pipes) 41A1, 41B1, 41C1, and the second intermediate heat transfer pipes (intermediate heat transfer pipes) 41A2, 41B2, 41C2 are provided between the inlet heat transfer pipes 40A, 40B, 40C, and the outlet heat transfer pipes 42A, 42B, 42C, respectively, and therefore the inlet heat transfer pipes 40A, 40B, 40C, and the outlet heat transfer pipes 42A, 42B, 42C are not adjacent to each other.
  • the refrigerants flow through the inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, 41C2, the outlet heat transfer pipes 42A, 42B, 42C in order from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage.
  • a refrigerant that is pressurized to supercritical pressure by a compressor 16 is not condensed in the gas cooler 50, but the density (specific gravity) of refrigerant gas is increased with the cooling.
  • the refrigerant flow passages 34A, 34B, 34C are formed such that the refrigerants flow from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage, so that it is possible to facilitate the circulation of the refrigerants by gravity to improve heat exchange efficiency.
  • the refrigerants are gradually cooled from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage, and therefore a temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be made below a predetermined temperature, and heat transfer between the adjacent heat transfer pipes can be suppressed.
  • a temperature difference between refrigerants in the outlet and the inlet of the gas cooler 50 is 85°C in this embodiment, and therefore the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 20°C to 25°C.
  • the outlet-inlet temperature difference of the gas cooler 50 is generally about 60°C, and therefore, in this case, the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 15°C.
  • the gas cooler 50 includes the upper heat exchange part 45 and the lower heat exchange part 46 divided up and down, and the refrigerant flow passages 34A, 34B, 34C each has a configuration in which the refrigerant sequentially flows from the upper heat exchange part 45 toward the lower heat exchange part 46, and therefore a temperature gradient of lowering a temperature from the upper heat exchange part 45 toward the lower heat exchange part 46 is formed, and it is possible to suppress temperature irregularity of the gas cooler 50.
  • the refrigerant flow passages 34A, 34B, 34C include the first intermediate heat transfer pipes 41A1, 41B1, 41C1 continued to the inlet heat transfer pipes 40A, 40B, 40C, the second intermediate heat transfer pipes 41A2, 41B2, 41C2 continued to the outlet heat transfer pipes 42A, 42B, 42C, respectively, and include the intermediate header 44 connected to all the first intermediate heat transfer pipes 41A1, 41B1, 41C1 and the second intermediate heat transfer pipes 41A2, 41B2, 41C2 of the refrigerant flow passages 34A, 34B, 34C, and therefore even when distribution of the refrigerants in the inlet heat transfer pipes 40A, 40B, 40C of the refrigerant flow passages 34A, 34B, 34C is inappropriate, the refrigerants are collected in the intermediate header 44 once, and thereafter distributed again in the refrigerant flow passages 34A, 34B, 34C, and therefore the distribution can be made appropriate. Consequently, it is possible to sufficiently perform heat exchange in the gas cooler 50.
  • the flow passage cross sectional area of the refrigerant flow passages in the gas cooler 50 is gradually reduced from the inlet side to the outlet side. That is, the respective flow passage diameters (inner diameters) of the inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, 41C2, and the outlet heat transfer pipes 42A, 42B, 42C forming the refrigerant flow passages 34A, 34B, 34C are set such that the relation of inlet heat transfer pipe > first intermediate heat transfer pipe > second intermediate heat transfer pipe > outlet heat transfer pipe is satisfied, and the respective flow passage cross sectional areas of the refrigerant flow passages 34A, 34B, 34C are set so as to be gradually reduced from the inlet side to the outlet side.
  • FIG. 5 is a schematic diagram of a gas cooler according to another embodiment (2).
  • first intermediate heat transfer pipes 41A1, 41B1, 41C1 and second intermediate heat transfer pipes 41A2, 41B2, 41C2 are connected to each other through connecting pipes 47A, 47B, 47C, respectively.
  • the intermediate header 44 is unnecessary, and therefore it is possible to realize miniaturization of the gas cooler 50.
  • inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, 42C2, and outlet heat transfer pipes 42A, 42B, 42C forming the refrigerant flow passages 34A, 34B, 34C respectively satisfy the relation of inlet heat transfer pipe > first intermediate heat transfer pipe > second intermediate heat transfer pipe > outlet heat transfer pipe.
  • the refrigerant flow passages 34A, 34B, 34C each include two pipes, namely include the first intermediate heat transfer pipes 41A1, 41B1, 41C1 and the second intermediate heat transfer pipes 41A2, 41B2, 41C2, respectively, as intermediate heat transfer pipes.
  • the number of intermediate heat transfer pipes may be appropriately changed in response to the refrigerant flow rate or the size of plate fins 31.
  • At least one intermediate heat transfer pipe may be provided, and the refrigerant flow passage may have a minimum configuration of a flow of one round trip and a half by three pipes, namely, the inlet heat transfer pipe, the intermediate heat transfer pipe, and the outlet heat transfer pipe. In this configuration, the outlet of the refrigerant is located on an opposite side to the inlet of the refrigerant in the direction in which the heat transfer pipe extends.
  • a refrigerant temperature difference in the outlet and the inlet of the gas cooler 50 is 85°C (refer to FIG. 2 ), and therefore a temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 25°C to 30°C.
  • the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes is increased, and may become about 30°C.
  • the outlet-inlet temperature difference of the gas cooler 50 is generally about 60°C, and therefore, in this case, the temperature difference between the refrigerants flowing through the adjacent heat transfer pipes can be lowered to about 20°C.
  • the intervals (pitches) of the heat transfer pipes are the same.
  • the interval between the upper heat exchange part 45 and the lower heat exchange part 46, and the interval between the first intermediate heat transfer pipe 41C1 of the refrigerant flow passage 34C, and the second intermediate heat transfer pipe 41A2 of the refrigerant flow passage 34A may be wider by one pipe more. In this configuration, heat transfer between the upper heat exchange part 45 and the lower heat exchange part 46 is suppressed, and therefore it is possible to further suppress increase in the refrigerant outlet temperature.
  • FIG. 6 is a schematic diagram of a gas cooler according to another embodiment (3).
  • gas coolers 19, 50 each include the one row of heat transfer pipe group 33 in the above respective embodiments
  • this embodiment is different from the above embodiments in that a plurality of rows of heat transfer pipe group 33 are provided.
  • Configurations identical with the configurations of the above gas coolers 19, 50 are denoted by the same reference numerals, and description thereof will be omitted.
  • a gas cooler 60 of this embodiment includes the heat transfer pipe group 33 formed by multiple rows and stages (two rows and six stages in this embodiment) heat transfer pipes.
  • the height positions of the heat transfer pipes of each row are different, and heat transfer pipes of a row on a leeward side are disposed slightly above heat transfer pipes of a row on a windward side.
  • the gas cooler 60 includes three refrigerant flow passages 34A, 34B, 34C on an inlet side, formed in parallel by the heat transfer pipe group 33, two refrigerant flow passages 34D, 34E sequentially connected to the refrigerant flow passages 34A, 34B, 34C, and a single refrigerant flow passage 34F.
  • the refrigerant flow passages 34A, 34B, 34C on the inlet side include inlet heat transfer pipes 40A, 40B, 40C connected to an inlet header 36, respectively. These inlet heat transfer pipes 40A, 40B, 40C are disposed in upper parts (the first stage, the second stage, the third stage) of the row on the leeward side of plate fins 31. Additionally, the refrigerant flow passage 34F on outlet side includes outlet heat transfer pipes 42A1, 42A2 connected to an outlet side header 38. These outlet heat transfer pipes 42A1, 42A2 are disposed in respective lowermost parts (the sixth stage) of the rows on the leeward side and the windward side of the plate fins 31.
  • the refrigerant flow passage 34A includes a first intermediate heat transfer pipe 41A1 connected to the inlet heat transfer pipe 40A through a U-shaped pipe (not illustrated). This refrigerant flow passage 34A is communicated with both the refrigerant flow passages 34D, 34E including second intermediate heat transfer pipes 41A2, 41B2 connected to third intermediate heat transfer pipes 41A3, 41B3 respectively through U-shaped pipes (not illustrated), through an intermediate header 44.
  • the first intermediate heat transfer pipe 41A1 is disposed in an uppermost stage of an adjacent row of the inlet heat transfer pipe 40A (row on the windward side), and the second intermediate heat transfer pipe 41A2 is disposed in a lower part (the fourth stage) of an adjacent row of the third intermediate heat transfer pipe 41A3 (row on the leeward side). Additionally, the first intermediate heat transfer pipe 41A1 and the second intermediate heat transfer pipe 41A2 are connected to each other through the intermediate header 44.
  • a refrigerant flowing in the refrigerant flow passage 34A passes through the inlet heat transfer pipe 40A, and the first intermediate heat transfer pipe 41A1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34B includes a first intermediate heat transfer pipe 41B1 connected to the inlet heat transfer pipe 40B through a U-shaped pipe.
  • the refrigerant flow passage 34B is communicated with both the refrigerant flow passages 34D, 34E including the second intermediate heat transfer pipes 41A2, 41B2 connected to the third intermediate heat transfer pipes 41A3, 41B3 through the U-shaped pipes, respectively through the intermediate header 44.
  • the first intermediate heat transfer pipe 41B1 is disposed in an upper part (the second stage) of an adjacent row of the inlet heat transfer pipe 40B (row on the windward side), and the second intermediate heat transfer pipe 41B2 is disposed in a lower part (the fifth stage) of an adjacent row (row on the leeward side) of the third intermediate heat transfer pipe 41B3. Additionally, the first intermediate heat transfer pipe 41B1 and the second intermediate heat transfer pipes 41A2 and 41B2 are communicated with each other through the intermediate header 44.
  • a refrigerant flowing in the refrigerant flow passage 34B passes through the inlet heat transfer pipe 40B, and the first intermediate heat transfer pipe 41B1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerant flow passage 34C includes a first intermediate heat transfer pipe 41C1 connected to the inlet heat transfer pipe 40C through a U-shaped pipe.
  • the refrigerant flow passage 34C is communicated with both the refrigerant flow passages 34D, 34E including the second intermediate heat transfer pipes 41A2, 41B2 connected to the third intermediate heat transfer pipes 41A3, 41B3 respectively through U-shaped pipes, through the intermediate header 44.
  • the first intermediate heat transfer pipe 41C1 is disposed in an upper part (the third stage) of an adjacent row of the inlet heat transfer pipe 40C (row on the windward side).
  • a refrigerant flowing in the refrigerant flow passage 34C passes through the inlet heat transfer pipe 40C, and the first intermediate heat transfer pipe 41C1 to flow through the second intermediate heat transfer pipe 41A2, the third intermediate heat transfer pipe 41A3 or the second intermediate heat transfer pipe 41B2, and the third intermediate heat transfer pipe 41B3 in order from the heat transfer pipe of the upper stage to the heat transfer pipe of the lower stage.
  • the refrigerants distributed into the three refrigerant flow passages 34A, 34B, 34C to flow in the gas cooler 60 flow in the two refrigerant flow passages 34D, 34E formed by the second intermediate heat transfer pipes 41A2, 41B2 and the third intermediate heat transfer pipes 41A3, 41B3, through the first intermediate heat transfer pipes 41A1, 41B1, 41C1 and the intermediate header 44.
  • the number of the refrigerant flow passages (the number of circuits) is reduced from 3 to 2, and the flow passage cross sectional area is reduced to two-thirds.
  • outlet heat transfer pipe 42A1 is disposed in the lowermost part (the sixth stage) of the adjacent rows of the third intermediate heat transfer pipe 41B3 (row on the leeward side), and is connected to the outlet side header 38
  • outlet heat transfer pipe 42A2 connected to the outlet pipe 37 is disposed at the position of the lowermost part (the sixth stage) of the adjacent rows of this outlet heat transfer pipe 42A1 (row on the windward side), and is connected to the outlet side header 38 through the U-shaped pipe 43.
  • This outlet side header 38 allows the refrigerants that circulate in the two refrigerant flow passages 34D, 34E formed by the second intermediate heat transfer pipes 41A2, 41B2 and the third intermediate heat transfer pipes 41A3, 41B3 to merge and flow into the single refrigerant flow passage 34F formed by the outlet heat transfer pipes 42A1, 42A2.
  • the number of the refrigerant flow passages is reduced from 2 to 1, and the flow passage cross sectional area is further reduced to one-half.
  • the gas cooler 60 includes an upper heat exchange part 45 and a lower heat exchange part 46 formed by division into two parts in the height direction (vertical direction).
  • the three refrigerant flow passages 34A, 34B, 34C on the inlet side are provided in the upper heat exchange part 45, and both the two refrigerant flow passages 34D, 34E at intermediate parts, and the single refrigerant flow passage 34F on the outlet side are provided in the lower heat exchange part 46 through the intermediate header 44, so that the refrigerants sequentially circulate from the upper heat exchange part 45 to the lower heat exchange part 46.
  • the heat transfer pipe group 33 is inserted into the plate fins 31 in two rows and six stages, the inlet heat transfer pipes 40A, 40B, 40C of the refrigerant flow passages 34A, 34B, 34C on the inlet side are disposed at separated positions above the third intermediate heat transfer pipes 41A3, 41B3 and the outlet heat transfer pipes 42A1, 42A2 on the refrigerant outlet side, and disposed on the row of the leeward side, and therefore it is possible to suppress the influence of heat of air which heat-exchanges with the high temperature refrigerants flowing through the inlet heat transfer pipes 40A, 40B, 40C, and suppress increase in the outlet temperatures of the refrigerants.
  • the number of the refrigerant flow passages of the refrigerant flow passages 34A, 34B, 34C on the inlet side, and the number of refrigerant flow passages (the number of circuits) of the refrigerant flow passages 34D, 34E and the refrigerant flow passage 34F continued to the downstream side of the refrigerant flow passages 34A, 34B, 34C can be gradually reduced in a manner of 3 ⁇ 2 ⁇ 1, and the flow passage cross sectional area of an in-radiator refrigerant flow passage can be gradually reduced from the inlet side to the outlet side.
  • FIG. 7 and FIG. 8 are schematic diagrams of gas coolers according to other embodiments (4) and (5).
  • the intermediate header 44 is omitted similarly to another embodiment (2) illustrated in FIG. 5 , and a heat transfer pipe group 33 is disposed in multiple rows and stages (two rows and six stages in this embodiment) like another embodiment (3) illustrated in FIG. 6 .
  • gas coolers 65, 70 configurations identical with the configurations of the above gas coolers 19, 60 are denoted by the same reference numerals, and description thereof will be omitted.
  • first intermediate heat transfer pipes 41A1, 41B1, 41C1 and second intermediate heat transfer pipes 41A2, 41B2, 41C2 are connected to each other through connecting pipes 51A, 51B, 51C, respectively, as illustrated in FIG. 7 .
  • the intermediate header 44 is unnecessary, and therefore it is possible to realize miniaturization of the gas cooler 65.
  • the inlet heat transfer pipes 40A, 40B, 40C are not adjacent to the outlet heat transfer pipes 42A, 42B, 42C, and the refrigerant flow passages 34A, 34B, 34C are formed so as to allow respective refrigerants to flow from the heat transfer pipes of the upper stage to the heat transfer pipes of the lower stage, location configuration of the heat transfer pipes can be appropriately changed.
  • the inlet heat transfer pipes 40A, 40B, 40C is not provided in a row on a leeward side, and the inlet heat transfer pipe 40B may be provided in an uppermost stage of a row on a windward side.
  • the outlet heat transfer pipes 42A, 42B, 42C needs to be provided in the row on the windward side, and the outlet heat transfer pipe 42B may be provided in a lowermost stage of the row on the leeward side.
  • first intermediate heat transfer pipes 41A1, 41B1, 41C1 and second intermediate heat transfer pipes 41A2, 41B2, 41C2 are connected to each other through connecting pipes 52A, 52B, 52C, respectively, without providing the intermediate header 44.
  • the intermediate header 44 may be provided in place of the connecting pipes 52A, 52B, 52C.
  • the respective flow passage diameters (inner diameters) of the inlet heat transfer pipes 40A, 40B, 40C, the first intermediate heat transfer pipes 41A1, 41B1, 41C1, the second intermediate heat transfer pipes 41A2, 41B2, 42C2, and the outlet heat transfer pipes 42A, 42B, 42C respectively satisfy the relation of inlet heat transfer pipe > first intermediate heat transfer pipe > second intermediate heat transfer pipe > outlet heat transfer pipe such that the flow passage cross sectional area of the refrigerant flow passages 34A, 34B, 34C is gradually reduced from the refrigerant inlet side to the outlet side.
  • the flow passage cross sectional area of the refrigerant flow passages 34A to 34F is gradually reduced from the inlet side to the outlet side, and therefore a plurality of examples, in which the number of circuits of the refrigerant flow passages is gradually reduced, and a plurality of examples, in which the flow passage diameters (inner diameters) of the heat transfer pipes are gradually reduced, are exemplified.
  • the flow passage diameters (inner diameters) of the heat transfer pipes may be gradually reduced at the same time when the number of circuits is gradually reduced.

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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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP16183460.1A 2015-08-13 2016-08-09 Radiateur et cycle frigorifique à pression supercritique l'utilisant Active EP3141857B1 (fr)

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JP2015159916A JP2017036900A (ja) 2015-08-13 2015-08-13 放熱器およびそれを用いた超臨界圧冷凍サイクル

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Cited By (1)

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US11892178B2 (en) 2016-12-28 2024-02-06 Daikin Industries, Ltd. Heat exchanger unit and air conditioner using the same

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6531063B2 (ja) * 2016-04-26 2019-06-12 日立ジョンソンコントロールズ空調株式会社 熱交換器及び空気調和機
WO2020129180A1 (fr) * 2018-12-19 2020-06-25 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle frigorifique

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JPH08121915A (ja) 1994-10-24 1996-05-17 Mitsubishi Heavy Ind Ltd ヒートポンプ式空気調和機
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JPH07208822A (ja) 1994-01-21 1995-08-11 Mitsubishi Heavy Ind Ltd ヒートポンプ式冷凍サイクル
JPH08121915A (ja) 1994-10-24 1996-05-17 Mitsubishi Heavy Ind Ltd ヒートポンプ式空気調和機
WO2004061147A1 (fr) * 2002-12-27 2004-07-22 Showa Denko K.K. Tuyau d'aluminium et son procede de production
DE10322165A1 (de) * 2003-05-16 2004-12-09 Valeo Klimasysteme Gmbh Kältemittel-Kühlwärmetauscher
JP2005214525A (ja) * 2004-01-30 2005-08-11 Mitsubishi Electric Corp 冷凍機内蔵型ショーケース
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Publication number Priority date Publication date Assignee Title
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