WO2017170139A1 - Heat exchange device, refrigeration system, and heat exchange method - Google Patents

Heat exchange device, refrigeration system, and heat exchange method Download PDF

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Publication number
WO2017170139A1
WO2017170139A1 PCT/JP2017/011771 JP2017011771W WO2017170139A1 WO 2017170139 A1 WO2017170139 A1 WO 2017170139A1 JP 2017011771 W JP2017011771 W JP 2017011771W WO 2017170139 A1 WO2017170139 A1 WO 2017170139A1
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WIPO (PCT)
Prior art keywords
heat exchange
gas
phase refrigerant
refrigerant
liquid
Prior art date
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PCT/JP2017/011771
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French (fr)
Japanese (ja)
Inventor
有仁 松永
吉川　実
寿人 佐久間
雅人 矢野
明日華 松葉
貴文 棗田
Original Assignee
日本電気株式会社
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Application filed by 日本電気株式会社 filed Critical 日本電気株式会社
Priority to US16/089,994 priority Critical patent/US20190145667A1/en
Priority to JP2018509186A priority patent/JP6888616B2/en
Publication of WO2017170139A1 publication Critical patent/WO2017170139A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F28D1/0233—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 air flow channels
    • F28D1/024—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 air flow channels with an air driving element
    • 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
    • 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
    • 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
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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

Definitions

  • the present invention relates to a heat exchange device and a heat exchange method, and more particularly to a heat exchange device and a heat exchange method used in a refrigeration system.
  • Refrigeration systems that transport heat by changing the state of refrigerant are widely used in air conditioning equipment and the like.
  • An example of such a refrigeration system is described in Patent Document 1.
  • the related refrigeration system described in Patent Document 1 is an application of a refrigeration cycle to an automotive air conditioner.
  • the associated refrigeration system has a compressor, a condenser, a receiver, an internal heat exchanger, an expansion valve, an evaporator, and a control valve.
  • the compressor compresses the refrigerant.
  • the condenser condenses the compressed refrigerant by heat exchange with the outside air.
  • the receiver separates the condensed refrigerant into gas and liquid and stores excess refrigerant in the refrigeration cycle.
  • the expansion valve is a temperature type expansion valve, and expands and expands the liquid refrigerant separated into gas and liquid.
  • an evaporator evaporates the expanded refrigerant
  • the internal heat exchanger has a high-pressure passage through which high-temperature and high-pressure refrigerant flows to the expansion valve and a low-pressure passage through which low-pressure refrigerant flows to the compressor, and a high-temperature refrigerant flowing through the high-pressure passage and a low-temperature refrigerant flowing through the low-pressure passage. Heat exchange between them.
  • the control valve adjusts the degree of superheat of the low-pressure refrigerant sent from the internal heat exchanger to the compressor.
  • the double pipe connected between the expansion valve and the control valve functions as an internal heat exchanger.
  • the outer pipe is concentrically arranged so as to surround the inner pipe.
  • the control valve adjusts to reduce the degree of superheat of the low-pressure refrigerant sent from the internal heat exchanger to the compressor, so that the refrigerant compressed by the compressor can be reduced.
  • the abnormal temperature rise can be suppressed.
  • heat exchange is performed between a low-pressure, low-temperature gas-phase refrigerant and a high-pressure, high-temperature liquid-phase refrigerant.
  • the enthalpy of the gas phase refrigerant can be increased.
  • the efficiency of the compressor can be increased.
  • the heat transfer coefficient between the liquid phase refrigerant and the wall surface becomes small.
  • the length of the double pipe provided in the related refrigeration system is lengthened or bent, It is necessary to have a complicated structure that generates a flow.
  • the wall surface in contact with the liquid phase refrigerant needs to have a complicated structure in which turbulent flow is generated even with a liquid phase refrigerant having a small flow rate.
  • An object of the present invention is a heat exchange apparatus that solves the problem that the efficiency of the entire refrigeration system is lowered when the heat exchange performance of the gas-phase refrigerant and the liquid-phase refrigerant is improved in the refrigeration system, which is the above-described problem. And providing a heat exchange method.
  • the heat exchange device of the present invention includes a refrigerant supply means for supplying a liquid refrigerant at a first temperature and a gas-phase refrigerant at a second temperature in one circulation system, and a liquid-phase refrigerant and a gas-phase refrigerant.
  • a plurality of heat exchange means each configured to perform heat exchange, a gas phase refrigerant is circulated so that the gas phase refrigerant flows in parallel through the plurality of heat exchange means, and the liquid phase refrigerant has a plurality of heat exchange means.
  • a refrigerant circulation means for circulating the liquid-phase refrigerant so as to flow in series.
  • a liquid phase refrigerant having a first temperature and a gas phase refrigerant having a second temperature are supplied in one circulation system, the gas phase refrigerants are paralleled and circulated, and the liquid phase refrigerants are serially connected.
  • the heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant, which are circulated in a state and paralleled.
  • the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved.
  • FIG. 1 is a schematic diagram showing a configuration of a heat exchange device 100 according to the first embodiment of the present invention.
  • the heat exchange device 100 according to the present embodiment includes a refrigerant supply unit (refrigerant supply unit) 110, a plurality of heat exchangers (heat exchange unit) 120, and a refrigerant circulation unit (refrigerant circulation unit) 130.
  • refrigerant supply unit refrigerant supply unit
  • heat exchange unit heat exchangers
  • refrigerant circulation unit refrigerant circulation unit 130.
  • the refrigerant supply unit 110 supplies the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system.
  • the heat exchanger 120 is configured to perform heat exchange between the liquid phase refrigerant and the gas phase refrigerant.
  • the refrigerant circulation unit 130 circulates the gas-phase refrigerant so that the gas-phase refrigerant flows in the plurality of heat exchangers 120 in parallel, and the liquid-phase refrigerant flows in the plurality of heat exchangers 120 in series. Circulate phase refrigerant.
  • the liquid-phase refrigerant and the gas-phase refrigerant are supplied in one circulation system. Since the refrigerant flows in a circulating manner, the same mass flow rate flows between the liquid-phase refrigerant and the gas-phase refrigerant from the law of conservation of mass. However, since the density of the gas-phase refrigerant is several hundredths of the density of the liquid-phase refrigerant, the volume flow rate of the gas-phase refrigerant is several hundred times larger than that of the liquid-phase refrigerant. Therefore, the flow rate of the gas-phase refrigerant is larger than that of the liquid-phase refrigerant, causing a large pressure loss in the gas-phase refrigerant. On the other hand, a liquid phase refrigerant has a lower volume flow rate than a gas phase refrigerant, and therefore has a low flow rate, and therefore has a low heat transfer coefficient.
  • the refrigerant circulation section 130 causes the gas-phase refrigerant to branch and flow through the plurality of heat exchangers 120 in parallel.
  • the gas phase refrigerants branched in parallel have a small flow rate per one heat exchanger 120, so the flow velocity in the heat exchanger 120 is small and the pressure loss is reduced.
  • coolant becomes small, since a contact area increases by passing through the several heat exchanger 120, the reduction
  • the liquid-phase refrigerant flows through the plurality of heat exchangers 120 in series, the liquid-phase refrigerant having the same flow rate flows through each heat exchanger 120. Therefore, even if it is a case where it is a structure provided with the several heat exchanger 120, since the fall of a flow rate does not arise, the heat transfer rate of a liquid phase refrigerant
  • coolant does not fall.
  • the flow velocity of a liquid phase refrigerant is about several hundredths of the flow velocity of a gaseous phase refrigerant.
  • the heat exchange apparatus 100 includes a plurality of heat exchangers 120, and the gas-phase refrigerant circulates in parallel and the liquid-phase refrigerant circulates in series.
  • the heat exchange device 100 of the present embodiment the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved.
  • the heat exchanger 120 a fin-and-tube heat exchanger can be typically used.
  • An example of the configuration of such a heat exchanger 120 is shown in FIGS. 2A and 2B.
  • 2A is a front view
  • FIG. 2B is a side view.
  • the heat exchanger 120 includes a tube (heat transfer tube) 121 through which the liquid refrigerant R11 flows, a fin (heat transfer plate) 122 connected to the outer periphery of the tube 121, and in contact with the gas phase refrigerant R21. It can be set as the structure provided with.
  • a gas phase refrigerant has a smaller heat transfer coefficient than a liquid phase refrigerant when the flow rates are equal.
  • the contact area of the gas-phase refrigerant can be increased, so that the heat exchange performance can be improved.
  • the louver on the fin 122 the flow of the gas-phase refrigerant can be disturbed to generate a turbulent flow. Thereby, even if the length of the gas phase flow path is short and the flow velocity is small, the heat transfer rate can be improved.
  • the flow rate of the liquid phase refrigerant increases by passing through the small-diameter channels connected in series, thereby improving the heat transfer rate. Therefore, the heat exchange performance of the heat exchanger 120 can also be improved by this.
  • the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system.
  • the gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is circulated in series.
  • heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are arranged in parallel.
  • the gas-phase refrigerant is circulated in parallel and the liquid-phase refrigerant is circulated in series.
  • the heat exchange method of the present embodiment it is possible to improve the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant and improve the efficiency of the entire refrigeration system.
  • FIG. 3A and 3B show the configuration of the heat exchange device 200 according to the second embodiment of the present invention.
  • FIG. 3B is a partial view of the heat exchange device 200 as seen from the direction of arrow A in FIG. 3A.
  • the heat exchange apparatus 200 includes a refrigerant supply unit (refrigerant supply unit) 210, a plurality of heat exchangers (heat exchange unit) 220, a first gas phase pipe 231, a second gas phase pipe 232, a liquid phase. It has a pipe 241 and a liquid phase connecting pipe 242.
  • the first gas phase pipe 231, the second gas phase pipe 232, and the liquid phase connection pipe 242 are connected to the refrigerant supply unit 210, and the gas phase refrigerant R 21 is connected to the first gas phase pipe 231 and the liquid phase connection pipe.
  • the liquid phase refrigerant R11 is supplied from the refrigerant supply unit 210 to 242.
  • the first gas phase pipe 231, the second gas phase pipe 232, the liquid phase pipe 241, and the liquid phase connection pipe 242 constitute a refrigerant circulation means.
  • the heat exchanger 220 includes a gas-phase refrigerant inflow portion 221 into which the gas-phase refrigerant flows, a gas-phase refrigerant outflow portion 222 from which the gas-phase refrigerant flows out, a liquid-phase refrigerant inflow portion 223 into which the liquid-phase refrigerant flows, and a liquid-phase refrigerant A liquid-phase refrigerant outflow portion 224 that flows out is provided.
  • the first gas phase pipe 231 connects the plurality of gas phase refrigerant inflow portions 221 and the refrigerant supply unit 210 respectively provided in the plurality of heat exchangers 220.
  • the second gas phase pipe 232 connects the plurality of gas phase refrigerant outflow portions 222 and the refrigerant supply unit 210 respectively provided in the plurality of heat exchangers 220.
  • the liquid phase pipe 241 includes a liquid phase refrigerant inflow portion 223 provided in one heat exchanger of the plurality of heat exchangers 220 and a liquid phase refrigerant outflow portion provided in another heat exchanger adjacent to the one heat exchanger. 224 is connected.
  • the liquid phase connection pipe 242 connects the liquid phase refrigerant inflow portion 223 and the refrigerant supply portion 210 provided in the heat exchanger at one end of the plurality of heat exchangers 220. Further, the liquid phase connection pipe 242 connects the liquid phase refrigerant outflow part 224 and the refrigerant supply part 210 provided in the heat exchanger at the other end of the plurality of heat exchangers 220.
  • the heat exchange device 200 includes a plurality of heat exchangers 220, and is configured to exchange heat between the gas-phase refrigerant and the liquid-phase refrigerant supplied from the refrigerant supply unit 210.
  • a low-temperature (second temperature) and low-pressure gas-phase refrigerant before entering the compressor of the refrigeration system is used as the gas-phase refrigerant
  • a high-temperature (first first) before entering the expansion valve is used as the liquid-phase refrigerant.
  • Temperature) and a high-pressure liquid phase refrigerant can be used.
  • the heat exchange device 200 can be used in a refrigeration system that uses a gas phase refrigerant and a liquid phase refrigerant in one circulation system.
  • the heat exchanger 220 two kinds of refrigerant fluids in different states respectively pass through the spaces, and heat is transferred from the high-pressure and high-temperature liquid phase refrigerant to the low-pressure and low-temperature gas-phase refrigerant.
  • the first gas-phase pipe 231 and the second gas-phase pipe 232 in which the gas-phase refrigerant flows are branched into a plurality and connected in parallel with the plurality of heat exchangers 220. Thereby, the branched gaseous-phase refrigerant
  • coolant passes each heat exchanger 220, respectively.
  • the liquid-phase refrigerant passes through each heat exchanger through a liquid-phase tube 241 connecting a plurality of heat exchangers 220 in series.
  • the heat exchange apparatus 200 may be configured such that a plurality of heat exchangers 220, a first gas phase pipe 231 and a second gas phase pipe 232 are connected as shown in FIG. 3A. it can. That is, the order in which the plurality of heat exchangers 220 are connected to the first gas phase pipe 231 and the order in which the plurality of heat exchangers 220 are connected to the second gas phase pipe 232 are connected to the refrigerant supply unit 210. It can be set as the structure connected so that it might become the same order seeing from the side to be performed.
  • the present invention is not limited thereto, and a plurality of heat exchangers 220, a first gas phase pipe 231 and a second gas phase pipe 232 may be connected as shown in FIG. That is, in the heat exchange device 201, the order in which the plurality of heat exchangers 220 are connected to the first gas phase pipe 231 and the order in which the plurality of heat exchangers 220 are connected to the second gas phase pipe 232 are: It can be set as the structure connected so that it might become reverse order seeing from the side connected with the refrigerant
  • the heat exchanger 220 ⁇ / b> A disposed on the side close to the outflow side of the refrigerant supply unit 210 of the first gas phase tube 231 is connected to the second gas phase tube 232.
  • the refrigerant supply unit 210 is disposed on the far side from the inflow side.
  • a plurality of heat exchangers 220 can be sequentially arranged.
  • the pressure of the fluid is generally higher on the upstream (upstream) side, so the fluid tends to flow on the upstream side.
  • the fluid flowing in the pipe is generally easier to flow on the downstream (downstream) side near the outflow port because it is easier to discharge.
  • the heat exchanger 220 ⁇ / b> A connected to the upstream (upstream) side of the first gas phase pipe 231 is on the side far from the outlet of the second gas phase pipe 232. Connected to (Kawakami). Therefore, in the heat exchanger 220A, the gas-phase refrigerant R21 tends to flow into the heat exchanger 220A, but is difficult to flow out.
  • the heat exchanger 220 ⁇ / b> B connected to the downstream (downstream) side of the first gas phase pipe 231 is connected to the side (downstream) near the outflow port of the second gas phase pipe 232. Therefore, in the heat exchanger 220B, the gas-phase refrigerant R21 does not easily flow into the heat exchanger 220B, but easily flows out.
  • the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system.
  • the gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is circulated in series.
  • heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are arranged in parallel.
  • the order of the parallel gas phase refrigerants when performing heat exchange with the liquid phase refrigerant and the order of the parallel gas phase refrigerants when circulating after performing the heat exchange are the same order. There can be a certain configuration. In addition, the order of the parallel gas phase refrigerants when performing heat exchange with the liquid phase refrigerant and the order of the parallel gas phase refrigerants when circulating after performing the heat exchange are reversed. It is good.
  • the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved. it can.
  • the heat exchange device includes a refrigerant supply unit (refrigerant supply unit), a plurality of heat exchangers (heat exchange unit), and a refrigerant circulation unit (refrigerant circulation unit).
  • the heat exchange device according to the present embodiment differs from the heat exchange device 100 according to the first embodiment in the configuration of the heat exchanger and the refrigerant circulation unit.
  • FIG. 5A and 5B show a configuration of the heat exchange device 300 according to the present embodiment.
  • 5A is a side sectional view and
  • FIG. 5B is a top view.
  • Each heat exchanger 320 included in the heat exchange device 300 includes a gas phase refrigerant passage surface 321 through which the gas phase refrigerant R21 passes, a liquid phase refrigerant inflow portion 322 into which the liquid phase refrigerant flows in, and a liquid phase refrigerant through which the liquid phase refrigerant flows out.
  • An outflow portion 323 is provided.
  • the refrigerant circulation unit includes a gas phase tube 330, a plurality of partition plates 350, a liquid phase tube 341, and a liquid phase connection tube 342.
  • the vapor phase tube 330 includes a plurality of heat exchangers 320, and the vapor phase refrigerant R21 flows through the inside of the vapor phase tube 330.
  • the plurality of partition plates 350 are respectively located on the side where the gas-phase refrigerant R21 flows in the gas-phase refrigerant passage surfaces 321 provided in the plurality of heat exchangers 320, respectively.
  • the liquid phase pipe 341 includes a liquid phase refrigerant inflow portion 322 included in one heat exchanger of the plurality of heat exchangers 320, and a liquid phase refrigerant outflow included in another heat exchanger adjacent to the one heat exchanger.
  • the part 323 is connected.
  • the liquid phase connection pipe 342 connects the liquid phase refrigerant inflow portion 322 and the refrigerant supply portion 310 provided in the heat exchanger 320A at one end of the plurality of heat exchangers 320, and the other end of the plurality of heat exchangers 320.
  • the liquid-phase refrigerant outflow part 323 and the refrigerant supply part 310 included in the heat exchanger 320B are connected.
  • the heat exchange apparatus 300 includes a plurality of heat exchangers 320 in a gas phase pipe 330 that is a pipe having an inner diameter capable of disposing a heat exchanger therein. Is arranged.
  • the gas phase refrigerant R21 flows in parallel into the heat exchangers 320 by the plurality of partition plates 350, and the liquid phase refrigerant is configured to flow in the plurality of heat exchangers 320 in series by the liquid phase pipe 341. It is.
  • the heat exchanger 320 a fin-and-tube heat exchanger can be typically used. Further, the cross-sectional shape of the gas phase tube 330 may be circular or polygonal.
  • the partition plate 350 provided between the heat exchangers 320 can separate the gas phase refrigerant region before passing through the heat exchanger 320 and the gas phase refrigerant region after passing through the heat exchanger 320.
  • the partition plate 350 is arranged to be inclined with respect to the flow direction of the gas-phase refrigerant R21, so that the gas-phase refrigerant R21 can pass through each heat exchanger 320. It is.
  • the heat exchange device 300 of the present embodiment it is possible to improve the heat exchange performance of the gas-phase refrigerant and the liquid-phase refrigerant and improve the efficiency of the entire refrigeration system. Furthermore, since it is possible to reduce the number of pipes for circulating the gas-phase refrigerant through the plurality of heat exchangers 320, the heat exchange device 300 can be reduced in size.
  • the heat exchanger 320 may be arranged such that the normal line of the gas-phase refrigerant passage surface 321 is substantially parallel to the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330. it can. Not only this but the angle which the normal line of the gaseous-phase refrigerant
  • this angle was made into the angle which the normal line which goes to the side into which the gaseous-phase refrigerant
  • the angle formed by the normal line of the gas-phase refrigerant passage surface 321 and the normal line of the partition plate 350 may be a substantially right angle.
  • the normal line of the partition plate 350C among the plurality of partition plates 350 may be substantially parallel to the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330.
  • the partition plate 350C is located on the side where the gas phase refrigerant R21 flows in the heat exchanger 320C located at the end on the side where the gas phase refrigerant R21 flows.
  • the gas-phase refrigerant first flows into the heat exchanger 320C located on the most upstream side (upstream) in the flow direction of the gas-phase refrigerant R21, a large amount of gas-phase refrigerant is likely to flow in.
  • the heat to be heat exchange is biased and the heat exchange performance is lowered.
  • the partition plate 350C is provided in front of the most upstream heat exchanger 320C, it is possible to prevent the gas-phase refrigerant from concentrating and flowing into the heat exchanger 320C. Therefore, it is possible to prevent the unevenness of heat in the plurality of heat exchangers 320 and improve the cooling performance.
  • the angle formed by the normal line of the gas-phase refrigerant passage surface 321 and the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330 is substantially perpendicular. can do.
  • the angle formed by the normal line of the partition plate 350 and the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330 may be substantially perpendicular. With such a configuration, it is possible to further reduce the cross-sectional area of the gas phase tube 330 that accommodates the plurality of heat exchangers 320.
  • FIG. 9 is a schematic diagram showing the configuration of the refrigeration system 1000 according to the present embodiment.
  • the refrigeration system 1000 includes a heat exchange device 1100, a heat receiving unit (heat receiving unit) 1200, a compressor (compression unit) 1300, a heat radiating unit (heat radiating unit) 1400, and an expansion valve (expansion unit) 1500.
  • any of the heat exchanging devices 100, 200, 201, 300, 301, 302 described in the first to third embodiments can be used. And it is set as the structure which the refrigerant
  • the heat receiving unit 1200 vaporizes the refrigerant liquid by receiving heat to generate a gas phase refrigerant.
  • the compressor 1300 compresses the gas-phase refrigerant to generate a high-pressure gas-phase refrigerant.
  • the heat radiating unit 1400 condenses the high-pressure gas-phase refrigerant by heat radiation to generate a liquid-phase refrigerant.
  • the expansion valve 1500 expands the liquid phase refrigerant to generate a low-pressure refrigerant liquid, and recirculates the refrigerant liquid to the heat receiving unit 1200.
  • a refrigerant circulation system is configured.
  • the gas-phase refrigerant supplied to the heat exchange device 1100 is a low-temperature (second temperature) and low-pressure gas-phase refrigerant before entering the compressor 1300.
  • the liquid phase refrigerant supplied to the heat exchange device 1100 is a high-temperature (first temperature) and high-pressure liquid-phase refrigerant before entering the expansion valve 1500.
  • the heat exchange device 1100 includes a plurality of heat exchangers, and the gas-phase refrigerant circulates in parallel and the liquid-phase refrigerant circulates in series.
  • the heat exchange device 1100 the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved without increasing the pressure loss of the gas-phase refrigerant. Therefore, even when the heat exchange performance is improved, it is not necessary to increase the work amount of the compressor 1300.
  • the efficiency of the entire refrigeration system can be improved.
  • Refrigerant supply means for supplying the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system, and heat exchange between the liquid-phase refrigerant and the gas-phase refrigerant
  • a plurality of heat exchanging means each configured to perform the operation, circulating the gas phase refrigerant so that the gas phase refrigerant flows in parallel through the plurality of heat exchanging means, and the liquid phase refrigerant
  • a refrigerant circulation means for circulating the liquid-phase refrigerant so that the exchange means flows in series.
  • the heat exchange means is connected to a heat transfer tube in which the liquid-phase refrigerant flows, and an outer periphery of the heat transfer tube, and is in contact with the gas-phase refrigerant. , And a heat exchange device.
  • the heat exchange means includes a gas phase refrigerant inflow portion into which the gas phase refrigerant flows in, a gas phase refrigerant outflow portion from which the gas phase refrigerant flows out, A liquid-phase refrigerant inflow section through which the liquid-phase refrigerant flows in, and a liquid-phase refrigerant outflow section through which the liquid-phase refrigerant flows out, and the refrigerant circulation means includes a plurality of the gas exchange units respectively included in the plurality of heat exchange means.
  • a first gas phase pipe connecting the phase refrigerant inflow portion and the refrigerant supply means, and a plurality of gas phase refrigerant outflow portions and a second gas phase connecting the refrigerant supply means respectively provided in the plurality of heat exchange means A liquid phase refrigerant inflow portion provided in one heat exchange means of the pipe, the heat exchange means, and the liquid phase refrigerant outflow portion provided in another heat exchange means adjacent to the one heat exchange means.
  • a heat exchange apparatus comprising: a liquid phase connection pipe.
  • the plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are the plurality of heat exchange means,
  • the order in which the plurality of heat exchange means are connected to the second gas phase pipe and the order in which the plurality of heat exchanging means are connected to the second gas phase pipe are in the same order as viewed from the side connected to the refrigerant supply means. Connected heat exchange device.
  • the plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are the plurality of heat exchange means, The order in which the plurality of heat exchanging means are connected to the second gas phase pipe and the order in which the plurality of heat exchanging means are connected to the second gas phase pipe are reversed from the side connected to the refrigerant supply means. Connected heat exchange device.
  • the heat exchange means includes a gas phase refrigerant passage surface through which the gas phase refrigerant passes, a liquid phase refrigerant inflow portion into which the liquid phase refrigerant flows in, A liquid-phase refrigerant outflow portion through which the liquid-phase refrigerant flows out, wherein the refrigerant circulation means includes the plurality of heat exchange means, and the gas-phase tubes in which the gas-phase refrigerant flows and the plurality of heat exchanges A plurality of partition plates located on the gas-phase refrigerant inflow side of each of the gas-phase refrigerant passage surfaces provided in the means, and the liquid-phase refrigerant inflow provided in one heat exchange means among the plurality of heat exchange means A liquid-phase pipe connecting the liquid-phase refrigerant outflow part provided in another heat exchange means adjacent to the first heat exchange means, and the heat exchange means at one end of the plurality of heat exchange means A liquid phase refrigerant inflow section and
  • an angle formed by a normal line of the gas-phase refrigerant passage surface and a flow direction of the gas-phase refrigerant in the gas-phase pipe is greater than 90 degrees and less than 180 degrees
  • the angle formed by the normal line of the gas-phase refrigerant passage surface and the normal line of the partition plate is a substantially right angle.
  • the heat exchange apparatus as described in any one of additional remark 1 to 10, the heat receiving means which vaporizes a refrigerant
  • the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system, the gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is connected in series.
  • a heat exchange method in which heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are circulated and arranged in parallel.
  • Heat exchange device 110 100, 200, 201, 300, 301, 302, 1100 Heat exchange device 110, 210, 310 Refrigerant supply part 120, 220, 320 Heat exchanger 121 Tube 122 Fin 130 Refrigerant circulation part 221 Gas phase refrigerant inflow part 222 Gas phase refrigerant Outflow portion 223, 322 Liquid phase refrigerant inflow portion 224, 323 Liquid phase refrigerant outflow portion 231 First gas phase tube 232 Second gas phase tube 241, 341 Liquid phase tube 242, 342 Liquid phase connection tube 321 Gas phase refrigerant passage Surface 330 Gas-phase pipe 350 Partition plate 1000 Refrigeration system 1200 Heat receiving part 1300 Compressor 1400 Heat radiation part 1500 Expansion valve

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Since improving heat exchange between a gas-phase refrigerant and a liquid-phase refrigerant in a refrigeration system could instead result in a reduction in the efficiency of the refrigeration system as a whole, the present invention provides a heat exchange device (201) comprising: a refrigerant supply means (210) for supplying a first-temperature liquid-phase refrigerant (R11) and a second-temperature gas-phase refrigerant (R12) in one circulation system; a plurality of heat exchange means (220A, 220B) which are each configured so as to perform heat exchange between the liquid-phase refrigerant (R11) and the gas-phase refrigerant (R12); and a refrigerant circulation means (231, 232, 242) for circulating the gas-phase refrigerant (R12) in such a manner that the gas-phase refrigerant (R12) flows in parallel in the plurality of heat exchange means, and circulating the liquid-phase refrigerant (R11) in such a manner that the liquid-phase refrigerant (R11) flows in series in the plurality of heat exchange means.

Description

[規則37.2に基づきISAが決定した発明の名称]　熱交換装置、冷凍システム及び熱交換方法[Title of Invention Determined by ISA Based on Rule 37.2] Heat Exchanger, Refrigeration System, and Heat Exchange Method
　本発明は、熱交換装置および熱交換方法に関し、特に、冷凍システムに用いられる熱交換装置および熱交換方法に関する。 The present invention relates to a heat exchange device and a heat exchange method, and more particularly to a heat exchange device and a heat exchange method used in a refrigeration system.
　冷媒の状態変化によって熱を輸送する冷凍システムが、空調設備等に広く用いられている。このような冷凍システムの一例が特許文献１に記載されている。 Refrigeration systems that transport heat by changing the state of refrigerant are widely used in air conditioning equipment and the like. An example of such a refrigeration system is described in Patent Document 1.
　特許文献１に記載された関連する冷凍システムは、冷凍サイクルを自動車用空調装置に適用したものである。関連する冷凍システムは、圧縮機、凝縮器、レシーバ、内部熱交換器、膨張弁、蒸発器、および制御弁を有する。 The related refrigeration system described in Patent Document 1 is an application of a refrigeration cycle to an automotive air conditioner. The associated refrigeration system has a compressor, a condenser, a receiver, an internal heat exchanger, an expansion valve, an evaporator, and a control valve.
　ここで、圧縮機は冷媒を圧縮する。凝縮器は、圧縮された冷媒を外気との熱交換により凝縮させる。レシーバは、凝縮された冷媒を気液に分離するとともに冷凍サイクル内の余剰冷媒を蓄えておく。膨張弁は温度式の膨張弁であり、気液分離された液冷媒を絞り膨張させる。そして、蒸発器は、膨張された冷媒を車室内の空気との熱交換により蒸発させる。 Here, the compressor compresses the refrigerant. The condenser condenses the compressed refrigerant by heat exchange with the outside air. The receiver separates the condensed refrigerant into gas and liquid and stores excess refrigerant in the refrigeration cycle. The expansion valve is a temperature type expansion valve, and expands and expands the liquid refrigerant separated into gas and liquid. And an evaporator evaporates the expanded refrigerant | coolant by heat exchange with the air of a vehicle interior.
　内部熱交換器は、膨張弁へ高温・高圧の冷媒を流す高圧通路と圧縮機へ低圧冷媒を流す低圧通路とを有し、高圧通路を流れる高温の冷媒と低圧通路を流れる低温の冷媒との間で熱交換を行う。これにより、高圧通路を流れる冷媒は、低圧通路の冷媒によって過冷却され、低圧通路を流れる冷媒は、高圧通路の冷媒によって過熱されることになるため、冷凍サイクルの効率を向上させることができる。そして制御弁は、内部熱交換器から圧縮機に送られる低圧冷媒の過熱度を調整する。 The internal heat exchanger has a high-pressure passage through which high-temperature and high-pressure refrigerant flows to the expansion valve and a low-pressure passage through which low-pressure refrigerant flows to the compressor, and a high-temperature refrigerant flowing through the high-pressure passage and a low-temperature refrigerant flowing through the low-pressure passage. Heat exchange between them. Thereby, the refrigerant flowing through the high-pressure passage is supercooled by the refrigerant in the low-pressure passage, and the refrigerant flowing through the low-pressure passage is overheated by the refrigerant in the high-pressure passage, so that the efficiency of the refrigeration cycle can be improved. The control valve adjusts the degree of superheat of the low-pressure refrigerant sent from the internal heat exchanger to the compressor.
　ここで、膨張弁と制御弁との間に接続される二重管が内部熱交換器として機能する。二重管は、内管を囲うように外管が同心状に配置されたものである。内管に高圧冷媒を流し、外管と内管との間に低圧冷媒を流すことにより、内管を介して高圧冷媒と低圧冷媒との間で熱交換が行われる。 Here, the double pipe connected between the expansion valve and the control valve functions as an internal heat exchanger. In the double pipe, the outer pipe is concentrically arranged so as to surround the inner pipe. By flowing a high-pressure refrigerant through the inner pipe and a low-pressure refrigerant between the outer pipe and the inner pipe, heat exchange is performed between the high-pressure refrigerant and the low-pressure refrigerant through the inner pipe.
　関連する冷凍システムによれば、冷凍負荷が高いときに、制御弁が内部熱交換器から圧縮機に送られる低圧冷媒の過熱度を低減するよう調整することで、圧縮機によって圧縮された冷媒の異常昇温を抑制することができる、としている。 According to the related refrigeration system, when the refrigeration load is high, the control valve adjusts to reduce the degree of superheat of the low-pressure refrigerant sent from the internal heat exchanger to the compressor, so that the refrigerant compressed by the compressor can be reduced. The abnormal temperature rise can be suppressed.
特開２００９－００８３６９号公報JP 2009-008369 A
　上述した関連する冷凍システムのように、蒸発器、凝縮器、圧縮機、膨張弁によって構成される冷凍システムにおいては、低圧で低温の気相冷媒と高圧で高温の液相冷媒を熱交換することによって、気相冷媒のエンタルピーを増大させることができる。これにより、圧縮機の効率を上昇させることが可能である。 In a refrigeration system composed of an evaporator, a condenser, a compressor, and an expansion valve, as in the related refrigeration system described above, heat exchange is performed between a low-pressure, low-temperature gas-phase refrigerant and a high-pressure, high-temperature liquid-phase refrigerant. By this, the enthalpy of the gas phase refrigerant can be increased. Thereby, the efficiency of the compressor can be increased.
　このとき、気相冷媒と液相冷媒が壁面を介して熱交換する熱交換器により、液相冷媒から気相冷媒に熱が伝えられる。ここで、気相冷媒は液相冷媒と比べて密度が小さいので、気相冷媒と液相冷媒の流速が等しい場合、気相冷媒と壁面との間の熱伝達率は小さくなる。一方、液相冷媒は気相冷媒よりも密度が大きいので、気相冷媒と液相冷媒の質量流量が等しい場合、流速は小さくなる。そのため、液相冷媒と壁面との間の熱伝達率は小さくなる。それぞれの熱伝達率を増大させるためには、気相冷媒と壁面との接触面積を拡大するため、例えば関連する冷凍システムが備える二重管の長さを長くしたり屈曲させたり、また、乱流が発生するような複雑な構造とする必要がある。また、液相冷媒と接する壁面も、流量が小さい液相冷媒でも乱流が発生する複雑な構造にする必要がある。 At this time, heat is transferred from the liquid-phase refrigerant to the gas-phase refrigerant by a heat exchanger in which the gas-phase refrigerant and the liquid-phase refrigerant exchange heat through the wall surface. Here, since the density of the gas-phase refrigerant is smaller than that of the liquid-phase refrigerant, the heat transfer coefficient between the gas-phase refrigerant and the wall surface is small when the flow rates of the gas-phase refrigerant and the liquid-phase refrigerant are equal. On the other hand, since the liquid-phase refrigerant has a higher density than the gas-phase refrigerant, the flow velocity is small when the mass flow rates of the gas-phase refrigerant and the liquid-phase refrigerant are equal. Therefore, the heat transfer coefficient between the liquid phase refrigerant and the wall surface becomes small. In order to increase each heat transfer coefficient, in order to increase the contact area between the gas-phase refrigerant and the wall surface, for example, the length of the double pipe provided in the related refrigeration system is lengthened or bent, It is necessary to have a complicated structure that generates a flow. Also, the wall surface in contact with the liquid phase refrigerant needs to have a complicated structure in which turbulent flow is generated even with a liquid phase refrigerant having a small flow rate.
　しかし、冷凍システムにおいては、気相冷媒の圧力損失が大きくなると、圧縮機によって圧力降下分の圧力をさらに付加する必要が生じる。すなわち、熱交換性能を向上させるために熱交換器の構造を複雑にすると、乱流などの発生により大きな圧力損失が生じ、かえって冷凍システムの効率を低下させることになる。 However, in the refrigeration system, when the pressure loss of the gas-phase refrigerant increases, it is necessary to further add a pressure drop by the compressor. That is, when the structure of the heat exchanger is made complicated in order to improve the heat exchange performance, a large pressure loss occurs due to the occurrence of turbulence and the like, and the efficiency of the refrigeration system is reduced.
　このように、冷凍システムにおいて、気相冷媒と液相冷媒の熱交換性能を向上させると、かえって冷凍システム全体の効率が低下する、という問題があった。 Thus, in the refrigeration system, if the heat exchange performance of the gas-phase refrigerant and the liquid-phase refrigerant is improved, there is a problem that the efficiency of the entire refrigeration system is lowered.
　本発明の目的は、上述した課題である、冷凍システムにおいて、気相冷媒と液相冷媒の熱交換性能を向上させると、かえって冷凍システム全体の効率が低下する、という課題を解決する熱交換装置および熱交換方法を提供することにある。 An object of the present invention is a heat exchange apparatus that solves the problem that the efficiency of the entire refrigeration system is lowered when the heat exchange performance of the gas-phase refrigerant and the liquid-phase refrigerant is improved in the refrigeration system, which is the above-described problem. And providing a heat exchange method.
　本発明の熱交換装置は、第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する冷媒供給手段と、液相冷媒と気相冷媒との間で熱交換を行うようにそれぞれ構成された複数の熱交換手段と、気相冷媒が複数の熱交換手段を並列に流動するように気相冷媒を循環させ、液相冷媒が複数の熱交換手段を直列に流動するように液相冷媒を循環させる冷媒循環手段、とを有する。 The heat exchange device of the present invention includes a refrigerant supply means for supplying a liquid refrigerant at a first temperature and a gas-phase refrigerant at a second temperature in one circulation system, and a liquid-phase refrigerant and a gas-phase refrigerant. A plurality of heat exchange means each configured to perform heat exchange, a gas phase refrigerant is circulated so that the gas phase refrigerant flows in parallel through the plurality of heat exchange means, and the liquid phase refrigerant has a plurality of heat exchange means. And a refrigerant circulation means for circulating the liquid-phase refrigerant so as to flow in series.
　本発明の熱交換方法は、第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給し、気相冷媒を並列化して循環させ、液相冷媒を直列状で循環させ、並列化した気相冷媒と液相冷媒との間で熱交換を行わせる。 In the heat exchange method of the present invention, a liquid phase refrigerant having a first temperature and a gas phase refrigerant having a second temperature are supplied in one circulation system, the gas phase refrigerants are paralleled and circulated, and the liquid phase refrigerants are serially connected. The heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant, which are circulated in a state and paralleled.
　本発明の熱交換装置および熱交換方法によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。 According to the heat exchange device and the heat exchange method of the present invention, the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved.
本発明の第１の実施形態に係る熱交換装置の構成を示す概略図である。It is the schematic which shows the structure of the heat exchange apparatus which concerns on the 1st Embodiment of this invention. 本発明の第１の実施形態に係る熱交換装置が備える熱交換器の構成の一例を示す正面図である。It is a front view which shows an example of a structure of the heat exchanger with which the heat exchange apparatus which concerns on the 1st Embodiment of this invention is provided. 本発明の第１の実施形態に係る熱交換装置が備える熱交換器の構成の一例を示す側面図である。It is a side view showing an example of the composition of the heat exchanger with which the heat exchanging device concerning a 1st embodiment of the present invention is provided. 本発明の第２の実施形態に係る熱交換装置の構成を示す概略図である。It is the schematic which shows the structure of the heat exchange apparatus which concerns on the 2nd Embodiment of this invention. 本発明の第２の実施形態に係る熱交換装置の構成を示す部分概略図である。It is a partial schematic diagram which shows the structure of the heat exchange apparatus which concerns on the 2nd Embodiment of this invention. 本発明の第２の実施形態に係る熱交換装置の別の構成を示す概略図である。It is the schematic which shows another structure of the heat exchange apparatus which concerns on the 2nd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置の構成を示す側面断面図である。It is side surface sectional drawing which shows the structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置の構成を示す上面図である。It is a top view which shows the structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置の別の構成を示す側面断面図である。It is side surface sectional drawing which shows another structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置の別の構成を示す上面図である。It is a top view which shows another structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置の別の構成を示す側面断面図である。It is side surface sectional drawing which shows another structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置のさらに別の構成を示す側面断面図である。It is side surface sectional drawing which shows another structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施形態に係る熱交換装置のさらに別の構成を示す上面図である。It is a top view which shows another structure of the heat exchange apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第４の実施形態に係る冷凍システムの構成を示す概略図である。It is the schematic which shows the structure of the refrigerating system which concerns on the 4th Embodiment of this invention.
　以下に、図面を参照しながら、本発明の実施形態について説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
　〔第１の実施形態〕
　図１は、本発明の第１の実施形態に係る熱交換装置１００の構成を示す概略図である。本実施形態による熱交換装置１００は、冷媒供給部（冷媒供給手段）１１０、複数の熱交換器（熱交換手段）１２０、および冷媒循環部（冷媒循環手段）１３０を有する。 [First Embodiment]
FIG. 1 is a schematic diagram showing a configuration of a heat exchange device 100 according to the first embodiment of the present invention. The heat exchange device 100 according to the present embodiment includes a refrigerant supply unit (refrigerant supply unit) 110, a plurality of heat exchangers (heat exchange unit) 120, and a refrigerant circulation unit (refrigerant circulation unit) 130.
　冷媒供給部１１０は、第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する。熱交換器１２０は、液相冷媒と気相冷媒との間で熱交換を行うようにそれぞれ構成されている。そして、冷媒循環部１３０は、気相冷媒が複数の熱交換器１２０を並列に流動するように気相冷媒を循環させ、液相冷媒が複数の熱交換器１２０を直列に流動するように液相冷媒を循環させる。 The refrigerant supply unit 110 supplies the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system. The heat exchanger 120 is configured to perform heat exchange between the liquid phase refrigerant and the gas phase refrigerant. The refrigerant circulation unit 130 circulates the gas-phase refrigerant so that the gas-phase refrigerant flows in the plurality of heat exchangers 120 in parallel, and the liquid-phase refrigerant flows in the plurality of heat exchangers 120 in series. Circulate phase refrigerant.
　本実施形態による熱交換装置１００においては、液相冷媒と気相冷媒が一の循環系で供給される。冷媒は循環して流れるため、質量保存則から液相冷媒と気相冷媒は同じ質量流量が流れる。しかし、気相冷媒の密度は液相冷媒の密度の数１００分の１であるため、体積流量は気相冷媒の方が液相冷媒よりも数１００倍大きい。そのため、気相冷媒の流速は液相冷媒の流速よりも大きく、気相冷媒に大きな圧力損失を生じさせる。一方、液相冷媒は、気相冷媒よりも体積流量が小さいので流速が遅く、そのため熱伝達率が小さい。 In the heat exchange device 100 according to the present embodiment, the liquid-phase refrigerant and the gas-phase refrigerant are supplied in one circulation system. Since the refrigerant flows in a circulating manner, the same mass flow rate flows between the liquid-phase refrigerant and the gas-phase refrigerant from the law of conservation of mass. However, since the density of the gas-phase refrigerant is several hundredths of the density of the liquid-phase refrigerant, the volume flow rate of the gas-phase refrigerant is several hundred times larger than that of the liquid-phase refrigerant. Therefore, the flow rate of the gas-phase refrigerant is larger than that of the liquid-phase refrigerant, causing a large pressure loss in the gas-phase refrigerant. On the other hand, a liquid phase refrigerant has a lower volume flow rate than a gas phase refrigerant, and therefore has a low flow rate, and therefore has a low heat transfer coefficient.
　本実施形態による熱交換装置１００では冷媒循環部１３０によって、気相冷媒は分岐して複数の熱交換器１２０を並列に流動する。並列に分岐された気相冷媒は、一個の熱交換器１２０あたりの流量が小さくなるため熱交換器１２０内の流速が小さくなり、圧力損失が低減される。なお、気相冷媒の流速は小さくなるが、複数の熱交換器１２０を通過することにより接触面積は増大するので、気相冷媒の熱伝達率の低減を回避することができる。 In the heat exchange apparatus 100 according to the present embodiment, the refrigerant circulation section 130 causes the gas-phase refrigerant to branch and flow through the plurality of heat exchangers 120 in parallel. The gas phase refrigerants branched in parallel have a small flow rate per one heat exchanger 120, so the flow velocity in the heat exchanger 120 is small and the pressure loss is reduced. In addition, although the flow velocity of a gaseous-phase refrigerant | coolant becomes small, since a contact area increases by passing through the several heat exchanger 120, the reduction | decrease in the heat transfer rate of a gaseous-phase refrigerant | coolant can be avoided.
　一方、液相冷媒は複数の熱交換器１２０を直列に流動するため、各熱交換器１２０には同じ流速の液相冷媒が流れる。そのため、複数の熱交換器１２０を備えた構成とした場合であっても流速の低下は生じないので、液相冷媒の熱伝達率が低下することはない。なお、熱交換器を直列に接続すると圧力損失が増大することが想定されるが、液相冷媒の流速は気相冷媒の流速の数１００分の１程度である。そのため、熱交換装置１００が用いられる冷凍システム全体の圧力損失に比べて十分小さいので、無視することができる。また、液相冷媒は熱容量が気相冷媒より十分大きいため、複数の熱交換器１２０のうち液相冷媒の流れの下流に位置する熱交換器においても、気相冷媒と十分な温度差を有することが可能である。 On the other hand, since the liquid-phase refrigerant flows through the plurality of heat exchangers 120 in series, the liquid-phase refrigerant having the same flow rate flows through each heat exchanger 120. Therefore, even if it is a case where it is a structure provided with the several heat exchanger 120, since the fall of a flow rate does not arise, the heat transfer rate of a liquid phase refrigerant | coolant does not fall. In addition, although it is assumed that a pressure loss will increase if a heat exchanger is connected in series, the flow velocity of a liquid phase refrigerant is about several hundredths of the flow velocity of a gaseous phase refrigerant. Therefore, since it is sufficiently small compared with the pressure loss of the whole refrigeration system in which the heat exchange device 100 is used, it can be ignored. Moreover, since the heat capacity of the liquid phase refrigerant is sufficiently larger than that of the gas phase refrigerant, a heat exchanger located downstream of the flow of the liquid phase refrigerant among the plurality of heat exchangers 120 has a sufficient temperature difference from the gas phase refrigerant. It is possible.
　上述したように、本実施形態による熱交換装置１００は複数の熱交換器１２０を備え、気相冷媒は並列に循環し、液相冷媒は直列に循環する構成としている。このような構成としたことにより、気相冷媒の熱交換器１２０における圧力損失を低下させ、しかも液相冷媒の熱交換能力を減少させることなく両者の熱交換を行うことが可能になる。すなわち、本実施形態の熱交換装置１００によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。 As described above, the heat exchange apparatus 100 according to the present embodiment includes a plurality of heat exchangers 120, and the gas-phase refrigerant circulates in parallel and the liquid-phase refrigerant circulates in series. By adopting such a configuration, it is possible to reduce the pressure loss in the heat exchanger 120 for the gas-phase refrigerant and to perform heat exchange between the two without reducing the heat exchange capability of the liquid-phase refrigerant. That is, according to the heat exchange device 100 of the present embodiment, the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved.
　熱交換器１２０として、典型的にはフィンアンドチューブ型熱交換器を用いることができる。図２Ａおよび２Ｂに、このような熱交換器１２０の構成の一例を示す。図２Ａは正面図であり、図２Ｂは側面図である。熱交換器１２０は同図に示すように、液相冷媒Ｒ１１が流動するチューブ（伝熱管）１２１と、チューブ１２１の外周に接続し、気相冷媒Ｒ２１と接触するフィン（伝熱板）１２２とを備えた構成とすることができる。 As the heat exchanger 120, a fin-and-tube heat exchanger can be typically used. An example of the configuration of such a heat exchanger 120 is shown in FIGS. 2A and 2B. 2A is a front view and FIG. 2B is a side view. As shown in the figure, the heat exchanger 120 includes a tube (heat transfer tube) 121 through which the liquid refrigerant R11 flows, a fin (heat transfer plate) 122 connected to the outer periphery of the tube 121, and in contact with the gas phase refrigerant R21. It can be set as the structure provided with.
　一般に、気相冷媒は流速が等しい場合、液相冷媒よりも熱伝達率が小さい。しかし、フィン１２２を気相冷媒Ｒ２１と接触するように設けることによって気相冷媒の接触面積を増大させることができるので、熱交換性能を向上させることが可能である。さらに、フィン１２２にルーバを設けることによって、気相冷媒の流れをかき乱して乱流を発生させることができる。これにより、気相流路の長さが短く、流速が小さい場合であっても、熱伝達率を向上させることが可能になる。 Generally, a gas phase refrigerant has a smaller heat transfer coefficient than a liquid phase refrigerant when the flow rates are equal. However, by providing the fins 122 in contact with the gas-phase refrigerant R21, the contact area of the gas-phase refrigerant can be increased, so that the heat exchange performance can be improved. Further, by providing a louver on the fin 122, the flow of the gas-phase refrigerant can be disturbed to generate a turbulent flow. Thereby, even if the length of the gas phase flow path is short and the flow velocity is small, the heat transfer rate can be improved.
　一方、液相冷媒は、直列に接続された小口径の流路を通ることで流速が増大し、これにより熱伝達率が向上する。したがって、これによっても熱交換器１２０の熱交換性能を向上させることができる。 On the other hand, the flow rate of the liquid phase refrigerant increases by passing through the small-diameter channels connected in series, thereby improving the heat transfer rate. Therefore, the heat exchange performance of the heat exchanger 120 can also be improved by this.
　次に、本実施形態による熱交換方法について説明する。 Next, the heat exchange method according to this embodiment will be described.
　本実施形態の熱交換方法においては、まず、第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する。この気相冷媒を並列化して循環させ、液相冷媒を直列状で循環させる。そして、並列化した気相冷媒と液相冷媒との間で熱交換を行わせる。 In the heat exchange method of the present embodiment, first, the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system. The gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is circulated in series. Then, heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are arranged in parallel.
　このように、本実施形態の熱交換方法においては、気相冷媒を並列化して循環させ、液相冷媒を直列状で循環させる構成としている。このような構成としたことにより、気相冷媒の圧力損失を低下させ、しかも液相冷媒の熱交換能力を減少させることなく両者の熱交換を行うことが可能になる。 Thus, in the heat exchange method of the present embodiment, the gas-phase refrigerant is circulated in parallel and the liquid-phase refrigerant is circulated in series. By adopting such a configuration, it becomes possible to perform heat exchange between the two without reducing the pressure loss of the gas-phase refrigerant and reducing the heat exchange capability of the liquid-phase refrigerant.
　上述したように、本実施形態の熱交換方法によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。 As described above, according to the heat exchange method of the present embodiment, it is possible to improve the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant and improve the efficiency of the entire refrigeration system.
　〔第２の実施形態〕
　次に、本発明の第２の実施形態について説明する。図３Ａおよび図３Ｂに、本発明の第２の実施形態に係る熱交換装置２００の構成を示す。図３Ｂは、図３Ａ中の矢印Ａの方向から見た熱交換装置２００の部分図である。 [Second Embodiment]
Next, a second embodiment of the present invention will be described. 3A and 3B show the configuration of the heat exchange device 200 according to the second embodiment of the present invention. FIG. 3B is a partial view of the heat exchange device 200 as seen from the direction of arrow A in FIG. 3A.
　本実施形態による熱交換装置２００は、冷媒供給部（冷媒供給手段）２１０、複数の熱交換器（熱交換手段）２２０、第１の気相管２３１、第２の気相管２３２、液相管２４１、および液相接続管２４２を有する。第１の気相管２３１、第２の気相管２３２、および液相接続管２４２は冷媒供給部２１０に接続され、第１の気相管２３１には気相冷媒Ｒ２１が、液相接続管２４２には液相冷媒Ｒ１１がそれぞれ冷媒供給部２１０から供給される。なお、第１の気相管２３１、第２の気相管２３２、液相管２４１、および液相接続管２４２が冷媒循環手段を構成する。 The heat exchange apparatus 200 according to this embodiment includes a refrigerant supply unit (refrigerant supply unit) 210, a plurality of heat exchangers (heat exchange unit) 220, a first gas phase pipe 231, a second gas phase pipe 232, a liquid phase. It has a pipe 241 and a liquid phase connecting pipe 242. The first gas phase pipe 231, the second gas phase pipe 232, and the liquid phase connection pipe 242 are connected to the refrigerant supply unit 210, and the gas phase refrigerant R 21 is connected to the first gas phase pipe 231 and the liquid phase connection pipe. The liquid phase refrigerant R11 is supplied from the refrigerant supply unit 210 to 242. The first gas phase pipe 231, the second gas phase pipe 232, the liquid phase pipe 241, and the liquid phase connection pipe 242 constitute a refrigerant circulation means.
　熱交換器２２０は、気相冷媒が流入する気相冷媒流入部２２１、気相冷媒が流出する気相冷媒流出部２２２、液相冷媒が流入する液相冷媒流入部２２３、および液相冷媒が流出する液相冷媒流出部２２４を備える。 The heat exchanger 220 includes a gas-phase refrigerant inflow portion 221 into which the gas-phase refrigerant flows, a gas-phase refrigerant outflow portion 222 from which the gas-phase refrigerant flows out, a liquid-phase refrigerant inflow portion 223 into which the liquid-phase refrigerant flows, and a liquid-phase refrigerant A liquid-phase refrigerant outflow portion 224 that flows out is provided.
　第１の気相管２３１は、複数の熱交換器２２０がそれぞれ備える複数の気相冷媒流入部２２１と冷媒供給部２１０を接続する。第２の気相管２３２は、複数の熱交換器２２０がそれぞれ備える複数の気相冷媒流出部２２２と冷媒供給部２１０を接続する。 The first gas phase pipe 231 connects the plurality of gas phase refrigerant inflow portions 221 and the refrigerant supply unit 210 respectively provided in the plurality of heat exchangers 220. The second gas phase pipe 232 connects the plurality of gas phase refrigerant outflow portions 222 and the refrigerant supply unit 210 respectively provided in the plurality of heat exchangers 220.
　液相管２４１は、複数の熱交換器２２０のうちの一の熱交換器が備える液相冷媒流入部２２３と、一の熱交換器と隣接する他の熱交換器が備える液相冷媒流出部２２４を接続する。液相接続管２４２は、複数の熱交換器２２０のうちの一端の熱交換器が備える液相冷媒流入部２２３と冷媒供給部２１０を接続する。また、液相接続管２４２は、複数の熱交換器２２０のうちの他端の熱交換器が備える液相冷媒流出部２２４と冷媒供給部２１０を接続する。 The liquid phase pipe 241 includes a liquid phase refrigerant inflow portion 223 provided in one heat exchanger of the plurality of heat exchangers 220 and a liquid phase refrigerant outflow portion provided in another heat exchanger adjacent to the one heat exchanger. 224 is connected. The liquid phase connection pipe 242 connects the liquid phase refrigerant inflow portion 223 and the refrigerant supply portion 210 provided in the heat exchanger at one end of the plurality of heat exchangers 220. Further, the liquid phase connection pipe 242 connects the liquid phase refrigerant outflow part 224 and the refrigerant supply part 210 provided in the heat exchanger at the other end of the plurality of heat exchangers 220.
　上述したように、本実施形態による熱交換装置２００は複数の熱交換器２２０を備え、冷媒供給部２１０から供給される気相冷媒と液相冷媒が熱交換するように構成されている。ここで、気相冷媒には例えば、冷凍システムの圧縮機に入る前の低温（第２の温度）かつ低圧の気相冷媒を、液相冷媒には膨張弁に入る前の高温（第１の温度）かつ高圧の液相冷媒を用いることができる。すなわち、本実施形態による熱交換装置２００は、気相冷媒と液相冷媒を一の循環系で使用する冷凍システムに用いることができる。この場合、熱交換器２２０においては、２種の異なる状態の冷媒流体が隔離された空間をそれぞれ通過し、高圧かつ高温の液相冷媒から低圧かつ低温の気相冷媒に熱が移動する。 As described above, the heat exchange device 200 according to the present embodiment includes a plurality of heat exchangers 220, and is configured to exchange heat between the gas-phase refrigerant and the liquid-phase refrigerant supplied from the refrigerant supply unit 210. Here, for example, a low-temperature (second temperature) and low-pressure gas-phase refrigerant before entering the compressor of the refrigeration system is used as the gas-phase refrigerant, and a high-temperature (first first) before entering the expansion valve is used as the liquid-phase refrigerant. Temperature) and a high-pressure liquid phase refrigerant can be used. That is, the heat exchange device 200 according to the present embodiment can be used in a refrigeration system that uses a gas phase refrigerant and a liquid phase refrigerant in one circulation system. In this case, in the heat exchanger 220, two kinds of refrigerant fluids in different states respectively pass through the spaces, and heat is transferred from the high-pressure and high-temperature liquid phase refrigerant to the low-pressure and low-temperature gas-phase refrigerant.
　気相冷媒が流動する第１の気相管２３１および第２の気相管２３２は複数に分岐し、複数の熱交換器２２０と並列に接続される。これにより、分岐した気相冷媒が各熱交換器２２０をそれぞれ通過する。一方、液相冷媒は、複数の熱交換器２２０を直列に接続する液相管２４１を通って各熱交換器を通過する。 The first gas-phase pipe 231 and the second gas-phase pipe 232 in which the gas-phase refrigerant flows are branched into a plurality and connected in parallel with the plurality of heat exchangers 220. Thereby, the branched gaseous-phase refrigerant | coolant passes each heat exchanger 220, respectively. On the other hand, the liquid-phase refrigerant passes through each heat exchanger through a liquid-phase tube 241 connecting a plurality of heat exchangers 220 in series.
　このような構成としたことにより、気相冷媒の熱交換器２２０における圧力損失を低下させ、しかも液相冷媒の熱交換能力を減少させることなく両者の熱交換を行うことが可能になる。すなわち、本実施形態の熱交換装置２００によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。 By adopting such a configuration, it is possible to reduce the pressure loss in the heat exchanger 220 of the gas-phase refrigerant and to perform heat exchange between the two without reducing the heat exchange capacity of the liquid-phase refrigerant. That is, according to the heat exchange device 200 of the present embodiment, the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved.
　本実施形態による熱交換装置２００は、複数の熱交換器２２０、第１の気相管２３１、および第２の気相管２３２が、図３Ａに示したように接続された構成とすることができる。すなわち、複数の熱交換器２２０が第１の気相管２３１に接続される順番と、複数の熱交換器２２０が第２の気相管２３２に接続される順番が、冷媒供給部２１０と接続される側から見て同順になるように接続された構成とすることができる。 The heat exchange apparatus 200 according to the present embodiment may be configured such that a plurality of heat exchangers 220, a first gas phase pipe 231 and a second gas phase pipe 232 are connected as shown in FIG. 3A. it can. That is, the order in which the plurality of heat exchangers 220 are connected to the first gas phase pipe 231 and the order in which the plurality of heat exchangers 220 are connected to the second gas phase pipe 232 are connected to the refrigerant supply unit 210. It can be set as the structure connected so that it might become the same order seeing from the side to be performed.
　これに限らず、複数の熱交換器２２０と、第１の気相管２３１と、第２の気相管２３２とが、図４に示したように接続された構成としてもよい。すなわち、熱交換装置２０１において、複数の熱交換器２２０が第１の気相管２３１に接続される順番と、複数の熱交換器２２０が第２の気相管２３２に接続される順番が、冷媒供給部２１０と接続される側から見て逆順になるように接続された構成とすることができる。具体的には、複数の熱交換器２２０のうち、第１の気相管２３１の冷媒供給部２１０の流出側に近い側に配置された熱交換器２２０Ａが、第２の気相管２３２の冷媒供給部２１０の流入側から遠い側に配置される。同様に、複数の熱交換器２２０を順次、配置した構成とすることができる。 However, the present invention is not limited thereto, and a plurality of heat exchangers 220, a first gas phase pipe 231 and a second gas phase pipe 232 may be connected as shown in FIG. That is, in the heat exchange device 201, the order in which the plurality of heat exchangers 220 are connected to the first gas phase pipe 231 and the order in which the plurality of heat exchangers 220 are connected to the second gas phase pipe 232 are: It can be set as the structure connected so that it might become reverse order seeing from the side connected with the refrigerant | coolant supply part 210. FIG. Specifically, among the plurality of heat exchangers 220, the heat exchanger 220 </ b> A disposed on the side close to the outflow side of the refrigerant supply unit 210 of the first gas phase tube 231 is connected to the second gas phase tube 232. The refrigerant supply unit 210 is disposed on the far side from the inflow side. Similarly, a plurality of heat exchangers 220 can be sequentially arranged.
　ポンプ等によって流体を強制的に流動させる循環系においては、流体の圧力は一般に上流（川上）側の方が大きいので、流体は上流側の方が流れやすい。一方、配管内を流動する流体は一般に、流出口に近い下流（川下）側の方が、排出が容易なので流れやすい。 In a circulation system in which a fluid is forced to flow by a pump or the like, the pressure of the fluid is generally higher on the upstream (upstream) side, so the fluid tends to flow on the upstream side. On the other hand, the fluid flowing in the pipe is generally easier to flow on the downstream (downstream) side near the outflow port because it is easier to discharge.
　図４に示した熱交換装置２０１の構成にすると、第１の気相管２３１の上流（川上）側に接続された熱交換器２２０Ａは、第２の気相管２３２の流出口から遠い側（川上）に接続される。そのため、熱交換器２２０Ａでは、気相冷媒Ｒ２１は熱交換器２２０Ａに流入しやすいが、流出はしにくくなる。 With the configuration of the heat exchange device 201 shown in FIG. 4, the heat exchanger 220 </ b> A connected to the upstream (upstream) side of the first gas phase pipe 231 is on the side far from the outlet of the second gas phase pipe 232. Connected to (Kawakami). Therefore, in the heat exchanger 220A, the gas-phase refrigerant R21 tends to flow into the heat exchanger 220A, but is difficult to flow out.
　反対に、第１の気相管２３１の下流（川下）側に接続された熱交換器２２０Ｂは、第２の気相管２３２の流出口に近い側（川下）に接続される。そのため、熱交換器２２０Ｂでは、気相冷媒Ｒ２１は熱交換器２２０Ｂに流入しにくいが、流出はしやすくなる。 On the contrary, the heat exchanger 220 </ b> B connected to the downstream (downstream) side of the first gas phase pipe 231 is connected to the side (downstream) near the outflow port of the second gas phase pipe 232. Therefore, in the heat exchanger 220B, the gas-phase refrigerant R21 does not easily flow into the heat exchanger 220B, but easily flows out.
　このように、図４に示した熱交換装置２０１の構成にすると、気相冷媒Ｒ２１が各熱交換器２２０を流動する際の流れやすさを、均等にすることが可能になる。その結果、各熱交換器２２０に気相冷媒がより均等に流れるようになるため、熱の偏りが減少し熱交換性能を高めることができる。 As described above, with the configuration of the heat exchange device 201 shown in FIG. 4, it is possible to make the easiness of flow when the gas-phase refrigerant R21 flows through each heat exchanger 220 uniform. As a result, since the gas-phase refrigerant flows through each heat exchanger 220 more evenly, the heat bias can be reduced and the heat exchange performance can be improved.
　次に、本実施形態による熱交換方法について説明する。 Next, the heat exchange method according to this embodiment will be described.
　本実施形態の熱交換方法においては、まず、第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する。この気相冷媒を並列化して循環させ、液相冷媒を直列状で循環させる。そして、並列化した気相冷媒と液相冷媒との間で熱交換を行わせる。 In the heat exchange method of the present embodiment, first, the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system. The gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is circulated in series. Then, heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are arranged in parallel.
　このとき、液相冷媒との間で熱交換を行わせる際の並列化した気相冷媒の順番と、熱交換を行った後に循環させる際の並列化した気相冷媒の順番が、同順である構成とすることができる。また、液相冷媒との間で熱交換を行わせる際の並列化した気相冷媒の順番と、　熱交換を行った後に循環させる際の並列化した気相冷媒の順番が、逆順である構成としてもよい。 At this time, the order of the parallel gas phase refrigerants when performing heat exchange with the liquid phase refrigerant and the order of the parallel gas phase refrigerants when circulating after performing the heat exchange are the same order. There can be a certain configuration. In addition, the order of the parallel gas phase refrigerants when performing heat exchange with the liquid phase refrigerant and the order of the parallel gas phase refrigerants when circulating after performing the heat exchange are reversed. It is good.
　以上説明したように、本実施形態の熱交換装置２００、２０１および熱交換方法によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。 As described above, according to the heat exchange devices 200 and 201 and the heat exchange method of the present embodiment, the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved, and the efficiency of the entire refrigeration system can be improved. it can.
　〔第３の実施形態〕
　次に、本発明の第３の実施形態について説明する。本実施形態に係る熱交換装置は、冷媒供給部（冷媒供給手段）、複数の熱交換器（熱交換手段）、および冷媒循環部（冷媒循環手段）を有する。本実施形態による熱交換装置は、熱交換器および冷媒循環部の構成が第１の実施形態に係る熱交換装置１００の構成と異なる。 [Third Embodiment]
Next, a third embodiment of the present invention will be described. The heat exchange device according to the present embodiment includes a refrigerant supply unit (refrigerant supply unit), a plurality of heat exchangers (heat exchange unit), and a refrigerant circulation unit (refrigerant circulation unit). The heat exchange device according to the present embodiment differs from the heat exchange device 100 according to the first embodiment in the configuration of the heat exchanger and the refrigerant circulation unit.
　図５Ａ、５Ｂに、本実施形態による熱交換装置３００の構成を示す。図５Ａは側面断面図であり、図５Ｂは上面図である。 5A and 5B show a configuration of the heat exchange device 300 according to the present embodiment. 5A is a side sectional view and FIG. 5B is a top view.
　熱交換装置３００が備える各熱交換器３２０は、気相冷媒Ｒ２１が通過する気相冷媒通過面３２１、液相冷媒が流入する液相冷媒流入部３２２、および液相冷媒が流出する液相冷媒流出部３２３を有する。 Each heat exchanger 320 included in the heat exchange device 300 includes a gas phase refrigerant passage surface 321 through which the gas phase refrigerant R21 passes, a liquid phase refrigerant inflow portion 322 into which the liquid phase refrigerant flows in, and a liquid phase refrigerant through which the liquid phase refrigerant flows out. An outflow portion 323 is provided.
　冷媒循環部は、気相管３３０、複数の仕切板３５０、液相管３４１、および液相接続管３４２を備える。 The refrigerant circulation unit includes a gas phase tube 330, a plurality of partition plates 350, a liquid phase tube 341, and a liquid phase connection tube 342.
　気相管３３０は複数の熱交換器３２０を内包し、気相管３３０の内部を気相冷媒Ｒ２１が流動する。複数の仕切板３５０は、複数の熱交換器３２０がそれぞれ備える気相冷媒通過面３２１の気相冷媒Ｒ２１が流入する側にそれぞれ位置している。 The vapor phase tube 330 includes a plurality of heat exchangers 320, and the vapor phase refrigerant R21 flows through the inside of the vapor phase tube 330. The plurality of partition plates 350 are respectively located on the side where the gas-phase refrigerant R21 flows in the gas-phase refrigerant passage surfaces 321 provided in the plurality of heat exchangers 320, respectively.
　液相管３４１は、複数の熱交換器３２０のうちの一の熱交換器が備える液相冷媒流入部３２２と、この一の熱交換器と隣接する他の熱交換器が備える液相冷媒流出部３２３を接続する。液相接続管３４２は、複数の熱交換器３２０のうちの一端の熱交換器３２０Ａが備える液相冷媒流入部３２２と冷媒供給部３１０を接続し、複数の熱交換器３２０のうちの他端の熱交換器３２０Ｂが備える液相冷媒流出部３２３と冷媒供給部３１０を接続する。 The liquid phase pipe 341 includes a liquid phase refrigerant inflow portion 322 included in one heat exchanger of the plurality of heat exchangers 320, and a liquid phase refrigerant outflow included in another heat exchanger adjacent to the one heat exchanger. The part 323 is connected. The liquid phase connection pipe 342 connects the liquid phase refrigerant inflow portion 322 and the refrigerant supply portion 310 provided in the heat exchanger 320A at one end of the plurality of heat exchangers 320, and the other end of the plurality of heat exchangers 320. The liquid-phase refrigerant outflow part 323 and the refrigerant supply part 310 included in the heat exchanger 320B are connected.
　図５Ａ、５Ｂに示したように、本実施形態による熱交換装置３００は、内部に熱交換器を配置することが可能な内径を有する配管である気相管３３０に、複数の熱交換器３２０を配置している。そして、複数の仕切板３５０によって各熱交換器３２０に気相冷媒Ｒ２１が並列に流入し、液相冷媒は液相管３４１によって複数の熱交換器３２０を直列に流動するように構成としたものである。 As shown in FIGS. 5A and 5B, the heat exchange apparatus 300 according to the present embodiment includes a plurality of heat exchangers 320 in a gas phase pipe 330 that is a pipe having an inner diameter capable of disposing a heat exchanger therein. Is arranged. The gas phase refrigerant R21 flows in parallel into the heat exchangers 320 by the plurality of partition plates 350, and the liquid phase refrigerant is configured to flow in the plurality of heat exchangers 320 in series by the liquid phase pipe 341. It is.
　熱交換器３２０として、典型的にはフィンアンドチューブ型熱交換器を用いることができる。また、気相管３３０の断面形状は、円形であっても多角形であってもよい。 As the heat exchanger 320, a fin-and-tube heat exchanger can be typically used. Further, the cross-sectional shape of the gas phase tube 330 may be circular or polygonal.
　各熱交換器３２０の間に設けた仕切板３５０によって、熱交換器３２０を通過する前の気相冷媒領域と、熱交換器３２０を通過した後の気相冷媒領域とを分離することができる。図５Ａに示したように、仕切板３５０を、気相冷媒Ｒ２１の流動方向に対して傾斜して配置した構成とすることにより、気相冷媒Ｒ２１が各熱交換器３２０を通過することが可能である。 The partition plate 350 provided between the heat exchangers 320 can separate the gas phase refrigerant region before passing through the heat exchanger 320 and the gas phase refrigerant region after passing through the heat exchanger 320. . As shown in FIG. 5A, the partition plate 350 is arranged to be inclined with respect to the flow direction of the gas-phase refrigerant R21, so that the gas-phase refrigerant R21 can pass through each heat exchanger 320. It is.
　このような構成とすることによって、本実施形態の熱交換装置３００によれば、気相冷媒と液相冷媒の熱交換性能を向上させ、冷凍システム全体の効率の改善を図ることができる。さらに、複数の熱交換器３２０を通って気相冷媒を循環させるための配管を少なくすることが可能になるので、熱交換装置３００を小型化することができる。 With such a configuration, according to the heat exchange device 300 of the present embodiment, it is possible to improve the heat exchange performance of the gas-phase refrigerant and the liquid-phase refrigerant and improve the efficiency of the entire refrigeration system. Furthermore, since it is possible to reduce the number of pipes for circulating the gas-phase refrigerant through the plurality of heat exchangers 320, the heat exchange device 300 can be reduced in size.
　熱交換器３２０の配置は、図５Ａに示したように、気相冷媒通過面３２１の法線が、気相管３３０内の気相冷媒Ｒ２１の流動方向と略平行である構成とすることができる。これに限らず、図６Ａおよび６Ｂに示す熱交換装置３０１のように、気相冷媒通過面３２１の法線と気相管３３０内の気相冷媒Ｒ２１の流動方向とがなす角度が、９０度よりも大きく１８０度未満である構成としてもよい。なお、この角度は、気相冷媒通過面３２１の法線のうち気相冷媒Ｒ２１が流入する側に向かう法線と、気相冷媒Ｒ２１の流動方向とがなす角度とした。すなわち、気相管３３０内の気相冷媒Ｒ２１の流動方向に対して、熱交換器３２０を傾斜させて配置した構成とすることができる。このような構成とすることにより、気相管３３０の内径方向における熱交換器の設置スペースを縮小することが可能になるので、熱交換器を収容する気相管３３０の断面積を低減することができる。 As shown in FIG. 5A, the heat exchanger 320 may be arranged such that the normal line of the gas-phase refrigerant passage surface 321 is substantially parallel to the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330. it can. Not only this but the angle which the normal line of the gaseous-phase refrigerant | coolant passage surface 321 and the flow direction of gaseous-phase refrigerant | coolant R21 in the gaseous-phase pipe | tube 330 make is 90 degree | times like the heat exchange apparatus 301 shown to FIG. 6A and 6B. It is good also as a structure which is larger than 180 degree | times. In addition, this angle was made into the angle which the normal line which goes to the side into which the gaseous-phase refrigerant | coolant R21 flows among the normal lines of the gaseous-phase refrigerant | coolant passage surface 321, and the flow direction of gaseous-phase refrigerant | coolant R21 make. That is, the heat exchanger 320 can be inclined and arranged with respect to the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330. By adopting such a configuration, it becomes possible to reduce the installation space of the heat exchanger in the inner diameter direction of the gas phase tube 330, so that the cross-sectional area of the gas phase tube 330 containing the heat exchanger can be reduced. Can do.
　この場合、気相冷媒通過面３２１の法線と仕切板３５０の法線とがなす角が略直角である構成としてもよい。これにより、流動する気相冷媒の損失が減少し、気相冷媒の圧力損失を低減することができる。 In this case, the angle formed by the normal line of the gas-phase refrigerant passage surface 321 and the normal line of the partition plate 350 may be a substantially right angle. Thereby, the loss of the flowing gas-phase refrigerant is reduced, and the pressure loss of the gas-phase refrigerant can be reduced.
　また、図７に示すように、複数の仕切板３５０のうち仕切板３５０Ｃの法線が、気相管３３０内の気相冷媒Ｒ２１の流動方向と略平行である構成としてもよい。ここで、仕切板３５０Ｃは、気相冷媒Ｒ２１が流入する側の端部に位置する熱交換器３２０Ｃの気相冷媒Ｒ２１が流入する側に位置している。 7, the normal line of the partition plate 350C among the plurality of partition plates 350 may be substantially parallel to the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330. Here, the partition plate 350C is located on the side where the gas phase refrigerant R21 flows in the heat exchanger 320C located at the end on the side where the gas phase refrigerant R21 flows.
　気相冷媒Ｒ２１の流動方向の最も上流（川上）側に位置している熱交換器３２０Ｃには、気相冷媒が最初に流入するため、多量の気相冷媒が流入しやすい。気相冷媒が一の熱交換器に集中して流入すると、熱交換する対象となる熱に偏りが生じ、熱交換性能が低下する。これに対して、図７に示すように、仕切板３５０Ｃを最上流の熱交換器３２０Ｃの前に設けると、気相冷媒がこの熱交換器３２０Ｃに集中して流入することを防止できる。そのため、複数の熱交換器３２０における熱の偏りを防止し冷却性能を高めることができる。 Since the gas-phase refrigerant first flows into the heat exchanger 320C located on the most upstream side (upstream) in the flow direction of the gas-phase refrigerant R21, a large amount of gas-phase refrigerant is likely to flow in. When the gas-phase refrigerant is concentrated and flows into one heat exchanger, the heat to be heat exchange is biased and the heat exchange performance is lowered. On the other hand, as shown in FIG. 7, if the partition plate 350C is provided in front of the most upstream heat exchanger 320C, it is possible to prevent the gas-phase refrigerant from concentrating and flowing into the heat exchanger 320C. Therefore, it is possible to prevent the unevenness of heat in the plurality of heat exchangers 320 and improve the cooling performance.
　さらに、図８Ａおよび８Ｂに示す熱交換装置３０２のように、気相冷媒通過面３２１の法線と気相管３３０内の気相冷媒Ｒ２１の流動方向とがなす角が略直角である構成とすることができる。この場合、仕切板３５０の法線と気相管３３０内の気相冷媒Ｒ２１の流動方向とがなす角が略直角である構成としてもよい。このような構成とすることにより、複数の熱交換器３２０を収容する気相管３３０の断面積をさらに縮小することが可能になる。 Furthermore, as in the heat exchange device 302 shown in FIGS. 8A and 8B, the angle formed by the normal line of the gas-phase refrigerant passage surface 321 and the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330 is substantially perpendicular. can do. In this case, the angle formed by the normal line of the partition plate 350 and the flow direction of the gas-phase refrigerant R21 in the gas-phase pipe 330 may be substantially perpendicular. With such a configuration, it is possible to further reduce the cross-sectional area of the gas phase tube 330 that accommodates the plurality of heat exchangers 320.
　〔第４の実施形態〕
　次に、本発明の第４の実施形態について説明する。図９は、本実施形態による冷凍システム１０００の構成を示す概略図である。 [Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described. FIG. 9 is a schematic diagram showing the configuration of the refrigeration system 1000 according to the present embodiment.
　冷凍システム１０００は、熱交換装置１１００、受熱部（受熱手段）１２００、圧縮機（圧縮手段）１３００、放熱部（放熱手段）１４００、および膨張弁（膨張手段）１５００を有する。 The refrigeration system 1000 includes a heat exchange device 1100, a heat receiving unit (heat receiving unit) 1200, a compressor (compression unit) 1300, a heat radiating unit (heat radiating unit) 1400, and an expansion valve (expansion unit) 1500.
　熱交換装置１１００には、上述した第１の実施形態から第３の実施形態で説明した熱交換装置１００、２００、２０１、３００、３０１、３０２のいずれかを用いることができる。そして、熱交換装置１１００が備える冷媒供給部と、上述した受熱部１２００、圧縮機１３００、放熱部１４００、および膨張弁１５００が接続した構成としている。これにより、本実施形態の冷凍システム１０００においては、冷媒供給部を介して熱交換装置１１００に液相冷媒と気相冷媒が一の循環系で供給される。 As the heat exchanging device 1100, any of the heat exchanging devices 100, 200, 201, 300, 301, 302 described in the first to third embodiments can be used. And it is set as the structure which the refrigerant | coolant supply part with which the heat exchange apparatus 1100 is equipped, the heat receiving part 1200 mentioned above, the compressor 1300, the thermal radiation part 1400, and the expansion valve 1500 was connected. Thereby, in the refrigeration system 1000 of the present embodiment, the liquid-phase refrigerant and the gas-phase refrigerant are supplied to the heat exchange device 1100 through the refrigerant supply unit in one circulation system.
　受熱部１２００は、冷媒液を受熱により気化させて気相冷媒を生成する。圧縮機１３００は、この気相冷媒を圧縮して高圧気相冷媒を生成する。放熱部１４００は、放熱により高圧気相冷媒を凝縮させ液相冷媒を生成する。そして、膨張弁１５００は、液相冷媒を膨張させて低圧にした冷媒液を生成し、この冷媒液を受熱部１２００に還流させる。これにより、冷媒の循環系が構成される。 The heat receiving unit 1200 vaporizes the refrigerant liquid by receiving heat to generate a gas phase refrigerant. The compressor 1300 compresses the gas-phase refrigerant to generate a high-pressure gas-phase refrigerant. The heat radiating unit 1400 condenses the high-pressure gas-phase refrigerant by heat radiation to generate a liquid-phase refrigerant. The expansion valve 1500 expands the liquid phase refrigerant to generate a low-pressure refrigerant liquid, and recirculates the refrigerant liquid to the heat receiving unit 1200. Thus, a refrigerant circulation system is configured.
　ここで、熱交換装置１１００に供給される気相冷媒は、圧縮機１３００に入る前の低温（第２の温度）かつ低圧の気相冷媒である。また、熱交換装置１１００に供給される液相冷媒は、膨張弁１５００に入る前の高温（第１の温度）かつ高圧の液相冷媒である。 Here, the gas-phase refrigerant supplied to the heat exchange device 1100 is a low-temperature (second temperature) and low-pressure gas-phase refrigerant before entering the compressor 1300. In addition, the liquid phase refrigerant supplied to the heat exchange device 1100 is a high-temperature (first temperature) and high-pressure liquid-phase refrigerant before entering the expansion valve 1500.
　上述した各実施形態で説明したように、熱交換装置１１００は複数の熱交換器を備え、気相冷媒は並列に循環し、液相冷媒は直列に循環する構成としている。このような構成としたことにより、気相冷媒の熱交換器における圧力損失を低下させ、しかも液相冷媒の熱交換能力を減少させることなく両者の熱交換を行うことが可能になる。すなわち、熱交換装置１１００によれば、気相冷媒の圧力損失の増大を招くことなく、気相冷媒と液相冷媒の熱交換性能を向上させることができる。したがって、熱交換性能を向上させた構成とした場合であっても、圧縮機１３００の仕事量を増大させる必要がない。 As described in the above-described embodiments, the heat exchange device 1100 includes a plurality of heat exchangers, and the gas-phase refrigerant circulates in parallel and the liquid-phase refrigerant circulates in series. By adopting such a configuration, it becomes possible to perform heat exchange between the two without reducing the pressure loss in the heat exchanger of the gas-phase refrigerant and reducing the heat exchange capability of the liquid-phase refrigerant. That is, according to the heat exchange device 1100, the heat exchange performance between the gas-phase refrigerant and the liquid-phase refrigerant can be improved without increasing the pressure loss of the gas-phase refrigerant. Therefore, even when the heat exchange performance is improved, it is not necessary to increase the work amount of the compressor 1300.
　以上より、本実施形態の冷凍システム１０００によれば、冷凍システム全体の効率の改善を図ることができる。 As described above, according to the refrigeration system 1000 of the present embodiment, the efficiency of the entire refrigeration system can be improved.
　上記の実施形態の一部又は全部は、以下の付記のようにも記載されうるが、以下には限られない。 Some or all of the above embodiments can be described as in the following supplementary notes, but are not limited thereto.
　（付記１）第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する冷媒供給手段と、前記液相冷媒と前記気相冷媒との間で熱交換を行うようにそれぞれ構成された複数の熱交換手段と、前記気相冷媒が前記複数の熱交換手段を並列に流動するように前記気相冷媒を循環させ、前記液相冷媒が前記複数の熱交換手段を直列に流動するように前記液相冷媒を循環させる冷媒循環手段、とを有する熱交換装置。 (Supplementary Note 1) Refrigerant supply means for supplying the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system, and heat exchange between the liquid-phase refrigerant and the gas-phase refrigerant A plurality of heat exchanging means each configured to perform the operation, circulating the gas phase refrigerant so that the gas phase refrigerant flows in parallel through the plurality of heat exchanging means, and the liquid phase refrigerant And a refrigerant circulation means for circulating the liquid-phase refrigerant so that the exchange means flows in series.
　（付記２）付記１に記載した熱交換装置において、前記熱交換手段は、前記液相冷媒が流動する伝熱管と、前記伝熱管の外周に接続し、前記気相冷媒と接触する伝熱板、とを備える熱交換装置。 (Supplementary note 2) In the heat exchange apparatus according to supplementary note 1, the heat exchange means is connected to a heat transfer tube in which the liquid-phase refrigerant flows, and an outer periphery of the heat transfer tube, and is in contact with the gas-phase refrigerant. , And a heat exchange device.
　（付記３）付記１または２に記載した熱交換装置において、前記熱交換手段は、前記気相冷媒が流入する気相冷媒流入部と、前記気相冷媒が流出する気相冷媒流出部と、前記液相冷媒が流入する液相冷媒流入部と、前記液相冷媒が流出する液相冷媒流出部、とを備え、前記冷媒循環手段は、前記複数の熱交換手段がそれぞれ備える複数の前記気相冷媒流入部と前記冷媒供給手段を接続する第１の気相管と、前記複数の熱交換手段がそれぞれ備える複数の前記気相冷媒流出部と前記冷媒供給手段を接続する第２の気相管と、前記複数の熱交換手段のうちの一の熱交換手段が備える前記液相冷媒流入部と、前記一の熱交換手段と隣接する他の熱交換手段が備える前記液相冷媒流出部を接続する液相管と、前記複数の熱交換手段のうちの一端の熱交換手段が備える前記液相冷媒流入部と前記冷媒供給手段を接続し、前記複数の熱交換手段のうちの他端の熱交換手段が備える前記液相冷媒流出部と前記冷媒供給手段を接続する液相接続管、とを備える熱交換装置。 (Appendix 3) In the heat exchange device according to appendix 1 or 2, the heat exchange means includes a gas phase refrigerant inflow portion into which the gas phase refrigerant flows in, a gas phase refrigerant outflow portion from which the gas phase refrigerant flows out, A liquid-phase refrigerant inflow section through which the liquid-phase refrigerant flows in, and a liquid-phase refrigerant outflow section through which the liquid-phase refrigerant flows out, and the refrigerant circulation means includes a plurality of the gas exchange units respectively included in the plurality of heat exchange means. A first gas phase pipe connecting the phase refrigerant inflow portion and the refrigerant supply means, and a plurality of gas phase refrigerant outflow portions and a second gas phase connecting the refrigerant supply means respectively provided in the plurality of heat exchange means A liquid phase refrigerant inflow portion provided in one heat exchange means of the pipe, the heat exchange means, and the liquid phase refrigerant outflow portion provided in another heat exchange means adjacent to the one heat exchange means. The liquid phase tube to be connected and the heat of one end of the plurality of heat exchange means The liquid phase refrigerant inflow portion provided in the conversion means is connected to the refrigerant supply means, and the liquid phase refrigerant outflow portion provided in the heat exchange means at the other end of the plurality of heat exchange means is connected to the refrigerant supply means. A heat exchange apparatus comprising: a liquid phase connection pipe.
　（付記４）付記３に記載した熱交換装置において、前記複数の熱交換手段と、前記第１の気相管と、前記第２の気相管とが、前記複数の熱交換手段が前記第１の気相管に接続される順番と、前記複数の熱交換手段が前記第２の気相管に接続される順番が、前記冷媒供給手段と接続される側から見て同順になるように接続されている熱交換装置。 (Supplementary note 4) In the heat exchange device according to supplementary note 3, the plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are the plurality of heat exchange means, The order in which the plurality of heat exchange means are connected to the second gas phase pipe and the order in which the plurality of heat exchanging means are connected to the second gas phase pipe are in the same order as viewed from the side connected to the refrigerant supply means. Connected heat exchange device.
　（付記５）付記３に記載した熱交換装置において、前記複数の熱交換手段と、前記第１の気相管と、前記第２の気相管とが、前記複数の熱交換手段が前記第１の気相管に接続される順番と、前記複数の熱交換手段が前記第２の気相管に接続される順番が、前記冷媒供給手段と接続される側から見て逆順になるように接続されている熱交換装置。 (Supplementary note 5) In the heat exchange device according to supplementary note 3, the plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are the plurality of heat exchange means, The order in which the plurality of heat exchanging means are connected to the second gas phase pipe and the order in which the plurality of heat exchanging means are connected to the second gas phase pipe are reversed from the side connected to the refrigerant supply means. Connected heat exchange device.
　（付記６）付記１または２に記載した熱交換装置において、前記熱交換手段は、前記気相冷媒が通過する気相冷媒通過面と、前記液相冷媒が流入する液相冷媒流入部と、前記液相冷媒が流出する液相冷媒流出部、とを備え、前記冷媒循環手段は、前記複数の熱交換手段を内包し、前記気相冷媒が流動する気相管と、前記複数の熱交換手段がそれぞれ備える前記気相冷媒通過面の前記気相冷媒が流入する側にそれぞれ位置する複数の仕切板と、前記複数の熱交換手段のうちの一の熱交換手段が備える前記液相冷媒流入部と、前記一の熱交換手段と隣接する他の熱交換手段が備える前記液相冷媒流出部を接続する液相管と、前記複数の熱交換手段のうちの一端の熱交換手段が備える前記液相冷媒流入部と前記冷媒供給手段を接続し、前記複数の熱交換手段のうちの他端の熱交換手段が備える前記液相冷媒流出部と前記冷媒供給手段を接続する液相接続管、とを備える熱交換装置。 (Appendix 6) In the heat exchange apparatus according to appendix 1 or 2, the heat exchange means includes a gas phase refrigerant passage surface through which the gas phase refrigerant passes, a liquid phase refrigerant inflow portion into which the liquid phase refrigerant flows in, A liquid-phase refrigerant outflow portion through which the liquid-phase refrigerant flows out, wherein the refrigerant circulation means includes the plurality of heat exchange means, and the gas-phase tubes in which the gas-phase refrigerant flows and the plurality of heat exchanges A plurality of partition plates located on the gas-phase refrigerant inflow side of each of the gas-phase refrigerant passage surfaces provided in the means, and the liquid-phase refrigerant inflow provided in one heat exchange means among the plurality of heat exchange means A liquid-phase pipe connecting the liquid-phase refrigerant outflow part provided in another heat exchange means adjacent to the first heat exchange means, and the heat exchange means at one end of the plurality of heat exchange means A liquid phase refrigerant inflow section and the refrigerant supply means, Liquid connection pipe for connecting the coolant supply means and the liquid-phase refrigerant outlet portion of the heat exchange means comprises the other end of the exchange means, heat exchange device comprising a city.
　（付記７）付記６に記載した熱交換装置において、前記気相冷媒通過面の法線が、前記気相管内の前記気相冷媒の流動方向と略平行である熱交換装置。 (Supplementary note 7) The heat exchange device according to supplementary note 6, wherein a normal line of the gas-phase refrigerant passage surface is substantially parallel to a flow direction of the gas-phase refrigerant in the gas-phase pipe.
　（付記８）付記６に記載した熱交換装置において、前記気相冷媒通過面の法線と前記気相管内の前記気相冷媒の流動方向とがなす角度が、９０度よりも大きく１８０度未満であり、前記気相冷媒通過面の法線と前記仕切板の法線とがなす角が略直角である熱交換装置。 (Supplementary note 8) In the heat exchange apparatus according to supplementary note 6, an angle formed by a normal line of the gas-phase refrigerant passage surface and a flow direction of the gas-phase refrigerant in the gas-phase pipe is greater than 90 degrees and less than 180 degrees And the angle formed by the normal line of the gas-phase refrigerant passage surface and the normal line of the partition plate is a substantially right angle.
　（付記９）付記８に記載した熱交換装置において、前記複数の仕切板のうち、前記気相冷媒が流入する側の端部に位置する前記熱交換手段の前記気相冷媒が流入する側に位置する仕切板の法線が、前記気相管内の前記気相冷媒の流動方向と略平行である熱交換装置。 (Supplementary note 9) In the heat exchange device according to supplementary note 8, among the plurality of partition plates, the heat exchange means located at an end portion on the side where the gas-phase refrigerant flows in, on the side where the gas-phase refrigerant flows in The heat exchange apparatus in which the normal line of the partition plate located is substantially parallel to the flow direction of the gas-phase refrigerant in the gas-phase pipe.
　（付記１０）付記６に記載した熱交換装置において、前記気相冷媒通過面の法線と前記気相管内の前記気相冷媒の流動方向とがなす角が略直角であり、前記仕切板の法線と前記気相管内の前記気相冷媒の流動方向とがなす角が略直角である熱交換装置。 (Supplementary note 10) In the heat exchange device according to supplementary note 6, an angle formed by a normal line of the gas-phase refrigerant passage surface and a flow direction of the gas-phase refrigerant in the gas-phase pipe is substantially perpendicular, A heat exchange device in which an angle formed by a normal line and a flow direction of the gas-phase refrigerant in the gas-phase pipe is substantially a right angle.
　（付記１１）付記１から１０のいずれか一項に記載した熱交換装置と、冷媒液を受熱により気化させて前記気相冷媒を生成する受熱手段と、前記気相冷媒を圧縮して高圧気相冷媒を生成する圧縮手段と、放熱により前記高圧気相冷媒を凝縮させ前記液相冷媒を生成する放熱手段と、前記液相冷媒を膨張させて低圧にした前記冷媒液を生成する膨張手段、とを備えた冷凍システム。 (Additional remark 11) The heat exchange apparatus as described in any one of additional remark 1 to 10, the heat receiving means which vaporizes a refrigerant | coolant liquid by receiving heat, and produces | generates the said gaseous-phase refrigerant | coolant, and compresses the said gaseous-phase refrigerant | coolant and is high pressure Compression means for generating a phase refrigerant, heat dissipation means for condensing the high-pressure gas-phase refrigerant by heat dissipation to generate the liquid-phase refrigerant, and expansion means for generating the refrigerant liquid having a low pressure by expanding the liquid-phase refrigerant, And a refrigeration system.
　（付記１２）第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給し、前記気相冷媒を並列化して循環させ、前記液相冷媒を直列状で循環させ、前記並列化した前記気相冷媒と前記液相冷媒との間で熱交換を行わせる熱交換方法。 (Supplementary Note 12) The liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature are supplied in one circulation system, the gas-phase refrigerant is circulated in parallel, and the liquid-phase refrigerant is connected in series. A heat exchange method in which heat exchange is performed between the gas-phase refrigerant and the liquid-phase refrigerant that are circulated and arranged in parallel.
　（付記１３）付記１２に記載した熱交換方法において、前記液相冷媒との間で前記熱交換を行わせる際の前記並列化した前記気相冷媒の順番と、前記熱交換を行った後に循環させる際の前記並列化した前記気相冷媒の順番が、同順である熱交換方法。 (Supplementary note 13) In the heat exchange method according to supplementary note 12, the order of the parallel gas phase refrigerants when the heat exchange is performed with the liquid phase refrigerant, and the circulation after the heat exchange is performed. The heat exchange method in which the order of the paralleled gas-phase refrigerants in the process is the same.
　（付記１４）付記１２に記載した熱交換方法において、前記液相冷媒との間で前記熱交換を行わせる際の前記並列化した前記気相冷媒の順番と、前記熱交換を行った後に循環させる際の前記並列化した前記気相冷媒の順番が、逆順である付記１２に記載した熱交換方法。 (Supplementary note 14) In the heat exchange method according to supplementary note 12, the order of the parallel gas phase refrigerants when the heat exchange is performed with the liquid phase refrigerant, and circulation after the heat exchange is performed. The heat exchange method according to appendix 12, wherein the order of the gas-phase refrigerants arranged in parallel is reversed.
　以上、実施形態を参照して本願発明を説明したが、本願発明は上記実施形態に限定されるものではない。本願発明の構成や詳細には、本願発明のスコープ内で当業者が理解し得る様々な変更をすることができる。 The present invention has been described above with reference to the embodiments, but the present invention is not limited to the above embodiments. Various changes that can be understood by those skilled in the art can be made to the configuration and details of the present invention within the scope of the present invention.
　この出願は、２０１６年３月３１日に出願された日本出願特願２０１６－０７０２１８を基礎とする優先権を主張し、その開示の全てをここに取り込む。 This application claims priority based on Japanese Patent Application No. 2016-070218 filed on Mar. 31, 2016, the entire disclosure of which is incorporated herein.
　１００、２００、２０１、３００、３０１、３０２、１１００　　熱交換装置
　１１０、２１０、３１０　　冷媒供給部
　１２０、２２０、３２０　　熱交換器
　１２１　　チューブ
　１２２　　フィン
　１３０　　冷媒循環部
　２２１　　気相冷媒流入部
　２２２　　気相冷媒流出部
　２２３、３２２　　液相冷媒流入部
　２２４、３２３　　液相冷媒流出部
　２３１　　第１の気相管
　２３２　　第２の気相管
　２４１、３４１　　液相管
　２４２、３４２　　液相接続管
　３２１　　気相冷媒通過面
　３３０　　気相管
　３５０　　仕切板
　１０００　　冷凍システム
　１２００　　受熱部
　１３００　　圧縮機
　１４００　　放熱部
　１５００　　膨張弁 100, 200, 201, 300, 301, 302, 1100 Heat exchange device 110, 210, 310 Refrigerant supply part 120, 220, 320 Heat exchanger 121 Tube 122 Fin 130 Refrigerant circulation part 221 Gas phase refrigerant inflow part 222 Gas phase refrigerant Outflow portion 223, 322 Liquid phase refrigerant inflow portion 224, 323 Liquid phase refrigerant outflow portion 231 First gas phase tube 232 Second gas phase tube 241, 341 Liquid phase tube 242, 342 Liquid phase connection tube 321 Gas phase refrigerant passage Surface 330 Gas-phase pipe 350 Partition plate 1000 Refrigeration system 1200 Heat receiving part 1300 Compressor 1400 Heat radiation part 1500 Expansion valve

Claims (14)

  1. 　第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給する冷媒供給手段と、
    　前記液相冷媒と前記気相冷媒との間で熱交換を行うようにそれぞれ構成された複数の熱交換手段と、
    　前記気相冷媒が前記複数の熱交換手段を並列に流動するように前記気相冷媒を循環させ、前記液相冷媒が前記複数の熱交換手段を直列に流動するように前記液相冷媒を循環させる冷媒循環手段、とを有する
    　熱交換装置。     A refrigerant supply means for supplying the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system;
    A plurality of heat exchanging means each configured to exchange heat between the liquid phase refrigerant and the gas phase refrigerant;
    The gas-phase refrigerant is circulated so that the gas-phase refrigerant flows through the plurality of heat exchange means in parallel, and the liquid-phase refrigerant is circulated so that the liquid-phase refrigerant flows through the plurality of heat exchange means in series. A heat exchanger having a refrigerant circulating means.
  2. 　請求項１に記載した熱交換装置において、
    　前記熱交換手段は、
    　　前記液相冷媒が流動する伝熱管と、
    　　前記伝熱管の外周に接続し、前記気相冷媒と接触する伝熱板、とを備える
    　熱交換装置。     In the heat exchange device according to claim 1,
    The heat exchange means includes
    A heat transfer tube through which the liquid-phase refrigerant flows;
    A heat exchange device comprising: a heat transfer plate connected to an outer periphery of the heat transfer tube and in contact with the gas phase refrigerant.
  3. 　請求項１または２に記載した熱交換装置において、
    　前記熱交換手段は、前記気相冷媒が流入する気相冷媒流入部と、前記気相冷媒が流出する気相冷媒流出部と、前記液相冷媒が流入する液相冷媒流入部と、前記液相冷媒が流出する液相冷媒流出部、とを備え、
    　前記冷媒循環手段は、
    　　前記複数の熱交換手段がそれぞれ備える複数の前記気相冷媒流入部と前記冷媒供給手段を接続する第１の気相管と、
    　　前記複数の熱交換手段がそれぞれ備える複数の前記気相冷媒流出部と前記冷媒供給手段を接続する第２の気相管と、
    　　前記複数の熱交換手段のうちの一の熱交換手段が備える前記液相冷媒流入部と、前記一の熱交換手段と隣接する他の熱交換手段が備える前記液相冷媒流出部を接続する液相管と、
    　　前記複数の熱交換手段のうちの一端の熱交換手段が備える前記液相冷媒流入部と前記冷媒供給手段を接続し、前記複数の熱交換手段のうちの他端の熱交換手段が備える前記液相冷媒流出部と前記冷媒供給手段を接続する液相接続管、とを備える
    　熱交換装置。     In the heat exchange device according to claim 1 or 2,
    The heat exchange means includes a gas phase refrigerant inflow portion into which the gas phase refrigerant flows in, a gas phase refrigerant outflow portion from which the gas phase refrigerant flows out, a liquid phase refrigerant inflow portion into which the liquid phase refrigerant flows, and the liquid A liquid phase refrigerant outflow portion from which the phase refrigerant flows out,
    The refrigerant circulating means is
    A plurality of the gas-phase refrigerant inflow portions respectively provided in the plurality of heat exchange means and a first gas-phase pipe connecting the refrigerant supply means;
    A plurality of gas phase refrigerant outflow portions respectively provided in the plurality of heat exchange means and a second gas phase pipe connecting the refrigerant supply means;
    A liquid that connects the liquid-phase refrigerant inflow portion provided in one heat exchange means of the plurality of heat exchange means and the liquid-phase refrigerant outflow portion provided in another heat exchange means adjacent to the one heat exchange means. Phase tube,
    The liquid provided in the heat exchange means at the other end of the plurality of heat exchange means by connecting the liquid phase refrigerant inflow portion provided in the heat exchange means at one end of the plurality of heat exchange means and the refrigerant supply means. A heat exchange apparatus comprising: a phase refrigerant outflow portion and a liquid phase connection pipe connecting the refrigerant supply means.
  4. 　請求項３に記載した熱交換装置において、
    　前記複数の熱交換手段と、前記第１の気相管と、前記第２の気相管とが、
    　前記複数の熱交換手段が前記第１の気相管に接続される順番と、前記複数の熱交換手段が前記第２の気相管に接続される順番が、前記冷媒供給手段と接続される側から見て同順になるように接続されている
    　熱交換装置。     In the heat exchange device according to claim 3,
    The plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are:
    The order in which the plurality of heat exchange means are connected to the first gas phase pipe and the order in which the plurality of heat exchange means are connected to the second gas phase pipe are connected to the refrigerant supply means. Heat exchange device connected in the same order as seen from the side.
  5. 　請求項３に記載した熱交換装置において、
    　前記複数の熱交換手段と、前記第１の気相管と、前記第２の気相管とが、
    　前記複数の熱交換手段が前記第１の気相管に接続される順番と、前記複数の熱交換手段が前記第２の気相管に接続される順番が、前記冷媒供給手段と接続される側から見て逆順になるように接続されている
    　熱交換装置。     In the heat exchange device according to claim 3,
    The plurality of heat exchange means, the first gas phase pipe, and the second gas phase pipe are:
    The order in which the plurality of heat exchange means are connected to the first gas phase pipe and the order in which the plurality of heat exchange means are connected to the second gas phase pipe are connected to the refrigerant supply means. A heat exchange device connected in reverse order when viewed from the side.
  6. 　請求項１または２に記載した熱交換装置において、
    　前記熱交換手段は、前記気相冷媒が通過する気相冷媒通過面と、前記液相冷媒が流入する液相冷媒流入部と、前記液相冷媒が流出する液相冷媒流出部、とを備え、
    　前記冷媒循環手段は、
    　　前記複数の熱交換手段を内包し、前記気相冷媒が流動する気相管と、
    　　前記複数の熱交換手段がそれぞれ備える前記気相冷媒通過面の前記気相冷媒が流入する側にそれぞれ位置する複数の仕切板と、
    　　前記複数の熱交換手段のうちの一の熱交換手段が備える前記液相冷媒流入部と、前記一の熱交換手段と隣接する他の熱交換手段が備える前記液相冷媒流出部を接続する液相管と、
    　前記複数の熱交換手段のうちの一端の熱交換手段が備える前記液相冷媒流入部と前記冷媒供給手段を接続し、前記複数の熱交換手段のうちの他端の熱交換手段が備える前記液相冷媒流出部と前記冷媒供給手段を接続する液相接続管、とを備える
    　熱交換装置。     In the heat exchange device according to claim 1 or 2,
    The heat exchange means includes a gas phase refrigerant passage surface through which the gas phase refrigerant passes, a liquid phase refrigerant inflow portion into which the liquid phase refrigerant flows in, and a liquid phase refrigerant outflow portion through which the liquid phase refrigerant flows out. ,
    The refrigerant circulating means is
    A gas phase tube containing the plurality of heat exchange means and in which the gas phase refrigerant flows;
    A plurality of partition plates respectively positioned on the gas-phase refrigerant inflow side of the gas-phase refrigerant passage surface provided in each of the plurality of heat exchange means;
    A liquid that connects the liquid-phase refrigerant inflow portion provided in one heat exchange means of the plurality of heat exchange means and the liquid-phase refrigerant outflow portion provided in another heat exchange means adjacent to the one heat exchange means. Phase tube,
    The liquid provided in the heat exchange means at the other end of the plurality of heat exchange means by connecting the liquid phase refrigerant inflow portion provided in the heat exchange means at one end of the plurality of heat exchange means and the refrigerant supply means. A heat exchange apparatus comprising: a phase refrigerant outflow portion and a liquid phase connection pipe connecting the refrigerant supply means.
  7. 　請求項６に記載した熱交換装置において、
    　前記気相冷媒通過面の法線が、前記気相管内の前記気相冷媒の流動方向と略平行である
    　熱交換装置。     The heat exchange device according to claim 6,
    The heat exchange device, wherein a normal line of the gas-phase refrigerant passage surface is substantially parallel to a flow direction of the gas-phase refrigerant in the gas-phase pipe.
  8. 　請求項６に記載した熱交換装置において、
    　前記気相冷媒通過面の法線と前記気相管内の前記気相冷媒の流動方向とがなす角度が、９０度よりも大きく１８０度未満であり、
    　前記気相冷媒通過面の法線と前記仕切板の法線とがなす角が略直角である
    　熱交換装置。     The heat exchange device according to claim 6,
    The angle formed by the normal line of the gas phase refrigerant passage surface and the flow direction of the gas phase refrigerant in the gas phase pipe is greater than 90 degrees and less than 180 degrees,
    The heat exchange device, wherein an angle formed by a normal line of the gas-phase refrigerant passage surface and a normal line of the partition plate is substantially a right angle.
  9. 　請求項８に記載した熱交換装置において、
    　前記複数の仕切板のうち、前記気相冷媒が流入する側の端部に位置する前記熱交換手段の前記気相冷媒が流入する側に位置する仕切板の法線が、前記気相管内の前記気相冷媒の流動方向と略平行である
    　熱交換装置。     The heat exchange device according to claim 8,
    Among the plurality of partition plates, the normal line of the partition plate located on the side where the gas-phase refrigerant flows in the heat exchange means located at the end portion on the side where the gas-phase refrigerant flows in, A heat exchange device that is substantially parallel to a flow direction of the gas-phase refrigerant.
  10. 　請求項６に記載した熱交換装置において、
    　前記気相冷媒通過面の法線と前記気相管内の前記気相冷媒の流動方向とがなす角が略直角であり、
    　前記仕切板の法線と前記気相管内の前記気相冷媒の流動方向とがなす角が略直角である
    　熱交換装置。     The heat exchange device according to claim 6,
    The angle formed by the normal line of the gas-phase refrigerant passage surface and the flow direction of the gas-phase refrigerant in the gas-phase pipe is substantially perpendicular.
    The heat exchange device, wherein an angle formed by a normal line of the partition plate and a flow direction of the gas-phase refrigerant in the gas-phase pipe is substantially a right angle.
  11. 　請求項１から１０のいずれか一項に記載した熱交換装置と、
    　冷媒液を受熱により気化させて前記気相冷媒を生成する受熱手段と、
    　前記気相冷媒を圧縮して高圧気相冷媒を生成する圧縮手段と、
    　放熱により前記高圧気相冷媒を凝縮させ前記液相冷媒を生成する放熱手段と、
    　前記液相冷媒を膨張させて低圧にした前記冷媒液を生成する膨張手段、とを備えた
    　冷凍システム。     The heat exchange device according to any one of claims 1 to 10,
    Heat receiving means for evaporating the refrigerant liquid by receiving heat to generate the gas-phase refrigerant;
    Compression means for compressing the gas-phase refrigerant to produce a high-pressure gas-phase refrigerant;
    Heat dissipation means for condensing the high-pressure gas-phase refrigerant by heat dissipation to generate the liquid-phase refrigerant;
    A refrigerating system comprising: expansion means for expanding the liquid-phase refrigerant to generate the refrigerant liquid having a low pressure.
  12. 　第１の温度の液相冷媒と第２の温度の気相冷媒を、一の循環系で供給し、
    　前記気相冷媒を並列化して循環させ、
    　前記液相冷媒を直列状で循環させ、
    　前記並列化した前記気相冷媒と前記液相冷媒との間で熱交換を行わせる
    　熱交換方法。     Supplying the liquid refrigerant at the first temperature and the gas-phase refrigerant at the second temperature in one circulation system;
    Circulating the gas-phase refrigerant in parallel;
    Circulating the liquid phase refrigerant in series,
    A heat exchange method in which heat exchange is performed between the parallel gas phase refrigerant and the liquid refrigerant.
  13. 　請求項１２に記載した熱交換方法において、
    　前記液相冷媒との間で前記熱交換を行わせる際の前記並列化した前記気相冷媒の順番と、
    　前記熱交換を行った後に循環させる際の前記並列化した前記気相冷媒の順番が、同順である
    　熱交換方法。     The heat exchange method according to claim 12,
    The order of the parallel gas phase refrigerants when the heat exchange with the liquid refrigerant is performed,
    The heat exchange method, wherein the order of the parallel gas phase refrigerants when circulating after the heat exchange is the same order.
  14. 　請求項１２に記載した熱交換方法において、
    　前記液相冷媒との間で前記熱交換を行わせる際の前記並列化した前記気相冷媒の順番と、
    　前記熱交換を行った後に循環させる際の前記並列化した前記気相冷媒の順番が、逆順である
    　請求項１２に記載した熱交換方法。     The heat exchange method according to claim 12,
    The order of the parallel gas phase refrigerants when the heat exchange with the liquid refrigerant is performed,
    The heat exchange method according to claim 12, wherein an order of the parallel gas phase refrigerants when circulating after the heat exchange is reversed.
PCT/JP2017/011771 2016-03-31 2017-03-23 Heat exchange device, refrigeration system, and heat exchange method WO2017170139A1 (en)

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