US20190128577A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20190128577A1
US20190128577A1 US16/091,138 US201716091138A US2019128577A1 US 20190128577 A1 US20190128577 A1 US 20190128577A1 US 201716091138 A US201716091138 A US 201716091138A US 2019128577 A1 US2019128577 A1 US 2019128577A1
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United States
Prior art keywords
reservoir
liquid
phase refrigerant
heat exchanger
gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US16/091,138
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English (en)
Inventor
Ryohei Sugimura
Masaaki Kawakubo
Daiki Kato
Hiroshi Mieda
Tetsuya Ito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Priority claimed from PCT/JP2017/013975 external-priority patent/WO2017175724A1/ja
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITO, TETSUYA, KATO, DAIKI, KAWAKUBO, MASAAKI, MIEDA, HIROSHI, SUGIMURA, RYOHEI
Publication of US20190128577A1 publication Critical patent/US20190128577A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32281—Cooling devices using compression characterised by refrigerant circuit configurations comprising a single secondary circuit, e.g. at evaporator or condenser side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers

Definitions

  • the present disclosure relates to a heat exchanger.
  • the refrigeration cycle device described in Patent Document 1 includes a gas-liquid separator for separating a refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and a switching means for switching a refrigerant circuit, in which a refrigerant circulates, between a refrigerant circuit of a first mode and a refrigerant circuit of a second mode.
  • the gas-liquid separator separates the refrigerant flowing out of an outside heat exchanger into a gas-phase refrigerant and a liquid-phase refrigerant, discharges the gas-phase refrigerant from a gas-phase refrigerant outlet, and discharges the liquid-phase refrigerant from a liquid-phase refrigerant outlet.
  • the refrigerant circuit of the first mode is a refrigerant circuit that causes the liquid-phase refrigerant to flow out from the liquid-phase refrigerant outlet of the gas-liquid separator and into a second pressure reducing means and an evaporator, and further causes the liquid-phase refrigerant to be sucked into a compressor.
  • the refrigerant circuit of the second mode is a refrigerant circuit that causes the gas-phase refrigerant to flow out from the gas-phase refrigerant outlet of the gas-liquid separator and to be sucked into the compressor.
  • the refrigerant is introduced from below.
  • Patent Literature 1 JP 2014-149123 A
  • a heat exchanger for a refrigeration cycle includes a heat exchanging portion ( 34 ) that exchanges heat between a refrigerant passing through therein and air, a reservoir ( 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G) that performs gas-liquid separation on a gas-liquid two-phase refrigerant that flows out from the heat exchanging portion into a gas-phase refrigerant and a liquid-phase refrigerant, the reservoir storing the liquid-phase refrigerant, an inflow passage ( 12 ) that allows the gas-liquid two-phase refrigerant flowing out from the heat exchanging portion to flow into the reservoir, a gas-phase outflow passage ( 13 ) that allows the gas-phase refrigerant to flow out from the reservoir, and a liquid-phase outflow passage ( 14 ) that allows the liquid-phase refrigerant to flow out from the reservoir.
  • the inflow passage is connected so as to be in communication with an inlet port ( 81 a ) of the reservoir disposed above a liquid surface of the liquid-phase refrigerant stored in the reservoir, the gas-phase outflow passage is connected so as to be in communication with a gas-phase outlet port ( 81 b ) of the reservoir disposed above the liquid surface of the liquid-phase refrigerant stored in the reservoir, and the liquid-phase outflow passage is connected so as to be in communication with a liquid-phase outlet port ( 81 c ) of the reservoir disposed below the liquid surface of the liquid-phase refrigerant stored in the reservoir.
  • gas-phase refrigerant since the refrigerant flows in from above the liquid surface, gas-phase refrigerant does not flow into the liquid-phase refrigerant stored in the reservoir, and it is possible to suppress disturbances in the liquid surface.
  • a gas-phase outflow passage and a liquid-phase outflow passage are provided, and can function as both a receiver and an accumulator.
  • the inflow port is provided in the upper region when functioning as a receiver, the gas-liquid two-phase refrigerant flows from above, and it is necessary to address further problems caused by this.
  • the reservoir preferably includes a partition portion ( 82 , 82 B, 82 C) between the inlet port and the gas-phase outlet port.
  • the refrigerant flowing in from the inlet port hits the partition portion before flowing out from the gas-phase outlet port, and continues downward. Therefore, it is possible to suppress the liquid-phase refrigerant from flowing out of the gas-phase outlet port.
  • a buffer portion ( 83 , 83 B, 83 C) is preferably disposed between the inlet port and the liquid surface of the liquid-phase refrigerant
  • the incoming refrigerant is substantially liquid-phase refrigerant
  • it hits the buffer portion and then continues toward the liquid surface. Therefore, the refrigerant does not directly hit the liquid surface of the liquid-phase refrigerant accumulated inside, and disturbances of the liquid surface can be suppressed.
  • the inflow passage is preferably disposed such that if a center line of the inflow passage is extended, the center line reaches an inner wall surface ( 816 , 812 Gb) of the reservoir ( 36 D, 36 E, 36 F, 36 G) without passing through a center ( 815 , 812 Ga) of the reservoir.
  • the incoming refrigerant is substantially liquid-phase refrigerant
  • it hits the inner wall surface of the reservoir and then continues toward the liquid surface. Therefore, the refrigerant does not directly hit the liquid surface of the liquid-phase refrigerant accumulated inside, and disturbances of the liquid surface can be suppressed.
  • FIG. 1 is a view for explaining an example of a refrigeration cycle to which a heat exchanger according to each embodiment is applied.
  • FIG. 2 is a view for explaining a case where the refrigeration cycle shown in FIG. 1 is operated in a cooling operation.
  • FIG. 3 is a view for explaining a case where the refrigeration cycle shown in FIG. 1 is operated in a heating operation.
  • FIG. 4 is a view for further explaining the heat exchanger shown in FIG. 1 .
  • FIG. 5 is a view schematically showing a heat exchanger according to a first embodiment of the present invention.
  • FIG. 6 is a view for explaining the liquid surface height inside a reservoir.
  • FIG. 7 is a view for explaining the interior of a reservoir.
  • FIG. 8 is a view for explaining the interior of a reservoir.
  • FIG. 9 is a view for explaining a reservoir according to a second embodiment.
  • FIG. 10 is a cross-sectional view taken along line X-X of FIG. 9 .
  • FIG. 11 is a view for explaining a reservoir according to a third embodiment.
  • FIG. 12 is a view for explaining a reservoir according to a third embodiment.
  • FIG. 13 is a view for explaining a reservoir according to a modified example of the third embodiment.
  • FIG. 14 is a view for explaining a reservoir according to a fourth embodiment.
  • FIG. 15 is a view for explaining a reservoir according to a fifth embodiment.
  • FIG. 16 is a view for explaining a reservoir according to a modified example of the fifth embodiment.
  • FIG. 17 is a view for explaining a reservoir according to a modified example of the fifth embodiment.
  • FIG. 18 is a view for explaining a reservoir according to a modified example of the second embodiment.
  • an integrated valve device 6 is used in a vehicle air conditioner 2 which is installed in a vehicle and which performs air conditioning in a passenger compartment.
  • the vehicle air conditioner 2 includes a refrigeration cycle device 3 , a water cycle device 4 , and an air conditioning unit 5 .
  • the air conditioning unit 5 is a unit for blowing warm air or cold air into the passenger compartment.
  • the refrigeration cycle device 3 and the water cycle device 4 are form a heat pump unit which adjusts the temperature of the air blown out from the air conditioning unit 5 .
  • the refrigeration cycle device 3 and the integrated valve device 6 will be described.
  • the refrigeration cycle device 3 includes a refrigerant flow passage 30 , a compressor 31 , a condenser 32 , a first heat exchanger 34 , a second heat exchanger 35 , a reservoir 36 , an expansion valve 37 , an evaporator 38 , and the integrated valve device 6 .
  • the first heat exchanger 34 , the second heat exchanger 35 , and the reservoir 36 correspond to the heat exchanger of the present invention.
  • the integrated valve device 6 includes a fixed throttle 61 , a first valve 62 , a second valve 64 , and a third valve 63 .
  • the water cycle device 4 includes a water flow passage 40 , a water pump 41 , a water-side heat exchanger 42 , and a heater core 43 .
  • the air conditioning unit 5 includes a casing 51 , an air mix door 52 , a blower fan 53 , and an inside/outside air switching door 54 .
  • the refrigerant flow passage 30 is a flow passage in which refrigerant flows, and connects the compressor 31 , the condenser 32 , the first heat exchanger 34 , the second heat exchanger 35 , the reservoir 36 , the expansion valve 37 , and the evaporator 38 .
  • HFC refrigerant or HFO refrigerant for example, may be used as refrigerant. Oil for lubricating the compressor 31 is mixed in the refrigerant.
  • the compressor 31 is an electric compressor and includes an suction port 311 and a discharge port 312 .
  • the compressor 31 sucks refrigerant from the suction port 311 and compresses the refrigerant.
  • the compressor 31 discharges the refrigerant, which is in an overheated state due to being compressed, from the discharge port 312 .
  • the refrigerant discharged from the discharge port 312 flows into the condenser 32 .
  • the condenser 32 is a conventional heat exchanger and includes an inlet port 321 and an outlet port 322 .
  • the condenser 32 is configured to exchange heat with the water-side heat exchanger 42 . Since the condenser 32 and the water-side heat exchanger 42 are configured so as to be capable of exchanging heat with each other, they form a water-refrigerant heat exchanger.
  • the high temperature and high pressure refrigerant discharged from the compressor 31 flows into the condenser 32 from the inlet port 321 .
  • the refrigerant, having flown into the condenser 32 exchanges heat with water flowing through the water-side heat exchanger 42 , and flows out from the outlet port 322 in a lower temperature state.
  • the refrigerant flowing out from the outlet port 322 then flows into the fixed throttle 61 and the first valve 62 which form a part of the integrated valve device 6 .
  • the refrigerant When the first valve 62 is closed, the refrigerant is decompressed through the fixed throttle 61 . As such, the pressure of the refrigerant is reduced, and this low pressure refrigerant flows into the first heat exchanger 34 . Conversely, when the first valve 62 is opened, the refrigerant is not decompressed and flows into the first heat exchanger 34 as a high pressure refrigerant.
  • the first heat exchanger 34 is an outside heat exchanger disposed outside of the passenger compartment, and is configured heat exchange with outside air.
  • the refrigerant that flows into the first heat exchanger 34 exchanges heat with the outside air and then flows into the reservoir 36 .
  • the reservoir 36 separates gas-phase refrigerant from liquid-phase refrigerant, and stores the liquid-phase refrigerant.
  • the separated gas-phase refrigerant then flows into the third valve 63 .
  • the gas-phase refrigerant that flows into the third valve 63 then flows toward the compressor 31 when the third valve 63 is opened.
  • the separated liquid-phase refrigerant is stored in the reservoir 36 and flows out toward the second heat exchanger 35 .
  • the second heat exchanger 35 is an outside heat exchanger disposed outside of the passenger compartment, and is configured heat exchange with outside air.
  • the second heat exchanger 35 further enhances the heat exchange efficiency of the refrigerant by cooperating with the first heat exchanger 34 to exchange heat between the incoming liquid-phase refrigerant and outside air.
  • the refrigerant that flows out from the second heat exchanger 35 then flows into the second valve 64 .
  • the second valve 64 is configured as a three-way valve that selectively allows the incoming refrigerant to flow toward either the compressor 31 or the expansion valve 37 .
  • the expansion valve 37 decompresses the incoming refrigerant and then discharges the refrigerant.
  • the refrigerant discharged from the expansion valve 37 then flows toward the evaporator 38 .
  • the expansion valve 37 is a temperature-sensitive mechanical expansion valve that decompresses and expands the refrigerant flowing into the evaporator 38 such that the degree of superheating of the refrigerant discharged from the evaporator 38 falls within a predetermined range.
  • the evaporator 38 has an inlet port 381 and an outlet port 382 .
  • the refrigerant flowing toward the evaporator 38 flows into the evaporator 38 from the inlet port 381 . Since the evaporator 38 is disposed in the casing 51 , the evaporator 38 exchanges heat with the air flowing in the casing 51 . The refrigerant flowing in the evaporator 38 exchanges heat with the air flowing in the casing 51 and then flows out from the outlet port 382 toward the compressor 31 .
  • the water flow passage 40 is a flow passage in which water flows, and connects the water pump 41 , the water-side heat exchanger 42 , and the heater core 43 .
  • the water pump 41 has an inlet port 411 and a discharge port 412 .
  • the water pump 41 sucks in water from the inlet port 411 and discharges water from the discharge port 412 .
  • By driving the water pump 41 it is possible to form a flow of water in the water flow passage 40 .
  • the water-side heat exchanger 42 and the condenser 32 form a water-refrigerant heat exchanger.
  • the water-side heat exchanger 42 has an inlet port 421 and an outlet port 422 .
  • the water that flows into the water-side heat exchanger 42 from the inlet port 421 is heat exchanged with the refrigerant flowing through the condenser 32 , and then flows out from the outlet port 422 . Since the refrigerant flowing through the condenser 32 is a high temperature and high pressure refrigerant, the water flowing through the water side heat exchanger 42 is heated and then flows toward the heater core 43 .
  • the heater core 43 is disposed in the casing 51 of the air conditioning unit 5 .
  • the heater core 43 is for exchanging heat with the air flowing in the casing 51 .
  • the heater core 43 has an inlet port 431 and an outlet port 432 .
  • Water which is heated by flowing through the water-side heat exchanger 42 flows into the inlet port 431 .
  • the water flowing into the heater core 43 exchanges heat with the air flowing in the casing 51 .
  • the water flowing in the heater core 43 is reduced in temperature and then flows out from the outlet port 432 toward the water pump 41 .
  • the casing 51 forms a flow passage that carries the conditioned air that will flow into the passenger compartment. From an upstream side in the casing 51 , the inside/outside air switching door 54 , the blower fan 53 , the evaporator 38 , the air mix door 52 , and the heater core 43 are arranged.
  • the inside/outside air switching door 54 is a door for switching between intaking the air flowing in the casing 51 from outside the passenger compartment or inside the passenger compartment.
  • the blower fan 53 generates an air flow in the casing 51 and sends the conditioned air into the passenger compartment.
  • the air mix door 52 is a door for switching between whether or not the air flowing in the casing 51 passes through the heater core 43 .
  • the vehicle air conditioner 2 is configured to open and close the respective valves of the integrated valve device 6 to adjust the amount of refrigerant flowing through the refrigeration cycle device 3 , to drive the water pump 41 to adjust the amount of water flowing through the water cycle device 4 , and to drive the blower fan 53 to adjust the amount of air flowing through the air conditioning unit 5 , thereby cooling or heating the passenger compartment.
  • the operation of the vehicle air conditioner 2 performing a cooling operation will be described.
  • the flow of the refrigerant is indicated by FLc.
  • the water pump 41 is not driven, and as such no water flow is generated in the water cycle device 4 . Accordingly, the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 31 flows toward the integrated valve device 6 without undergoing changes.
  • the first valve 62 is in an open state. Accordingly, the refrigerant flowing from the condenser 32 flows toward the first heat exchanger 34 without being pressure reduced.
  • the high-temperature and high-pressure gas-phase refrigerant flowing into the first heat exchanger 34 is heat-exchanged with the outside air. As a result, the temperature of the refrigerant decreases, and the refrigerant is cooled into a gas-liquid two-phase refrigerant and flows out to the reservoir 36 .
  • the reservoir 36 mainly functions as a receiver that allows liquid-phase refrigerant to flow out.
  • the third valve 63 is closed, and thus the liquid-phase refrigerant flows out from the reservoir 36 to the second heat exchanger 35 .
  • the second heat exchanger 35 functions as a subcooler.
  • the refrigerant flowing into the second heat exchanger 35 is further cooled through heat exchange with the outside air.
  • the first heat exchanger 34 and the second heat exchanger 35 function as a condenser of the refrigeration cycle device 3 .
  • the liquid-phase refrigerant that flows out from the second heat exchanger 35 then flows into the second valve 64 .
  • the second valve 64 is switched such that the incoming refrigerant is only allowed to flow toward the expansion valve 37 .
  • the refrigerant decompressed by the expansion valve 37 flows into the evaporator 38 .
  • the blower fan 53 is driven, and the air mix door 52 is positioned so as to close the heater core 43 side. Therefore, the air flowing in the casing 51 is cooled through heat exchange with the low-temperature refrigerant in the evaporator 38 . The cooled air flows in the casing 51 and is supplied into the passenger compartment.
  • the operation of the vehicle air conditioner 2 performing a heating operation will be described.
  • the flow of the refrigerant is indicated by FLh.
  • the water pump 41 is driven, and as such a water flow is generated in the water cycle device 4 . Therefore, the high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 31 flows into in the condenser 32 , at which point the refrigerant exchanges heat with the water flowing in the water-side heat exchanger 42 and is cooled. Then, the refrigerant flows toward the integrated valve device 6 .
  • the first valve 62 is in a closed state. Accordingly, the refrigerant flowing from the condenser 32 is pressure reduced, and then flows toward the first heat exchanger 34 .
  • the low-pressure gas-liquid two-phase refrigerant flowing into the first heat exchanger 34 heat exchanges with the outside air and evaporates, and then flows out to the reservoir 36 .
  • the reservoir 36 mainly functions as an accumulator which allows gas-phase refrigerant to flow out.
  • the third valve 63 is opened, and thus the gas-phase refrigerant flows out toward the compressor 31 .
  • the incoming refrigerant is separated into gas and liquid-phases, and the liquid-phase refrigerant is stored.
  • the liquid-phase refrigerant flows out toward the second heat exchanger 35 .
  • the second valve 64 opens a flow passage toward the suction port 311 , and so liquid-phase refrigerant and oil gradually return to the compressor 31 .
  • the blower fan 53 is driven, and the air mix door 52 is positioned so as to open the heater core 43 side. Therefore, the air flowing in the casing 51 is heated through heat exchange with high temperature water in the heater core 43 . The heated air flows in the casing 51 and is supplied into the passenger compartment.
  • the fixed throttle 61 , the first valve 62 , the second valve 64 , and the third valve 63 are integrally formed, and may be housed inside the reservoir 36 .
  • a fourth outlet port 74 is provided so as to extend downward from the insertion end portion 90 . Since the first heat exchanger 34 and the second heat exchanger 35 are disposed on one side of the integrated valve device 6 , the inlet port and outlet port of the integrated valve device 6 which allow refrigerant to be exchanged with the first heat exchanger 34 and the second heat exchanger 35 are disposed toward the side of the first heat exchanger 34 and the second heat exchanger 35 . From this viewpoint, a first outlet port 76 , through which refrigerant flows out to the first heat exchanger 34 , is arranged above the first heat exchanger 34 side.
  • a second inlet port 75 through which refrigerant flows in from the second heat exchanger 35 , is disposed on the second heat exchanger 35 side and below the first outlet port 76 .
  • a first inlet port 71 , A second outlet port 72 , and A third outlet port 73 are provided an opposite side from the side that faces the first heat exchanger 34 and the second heat exchanger 35 .
  • An inflow passage 12 , a gas-phase outflow passage 13 , and a liquid-phase outflow passage 14 will be described next.
  • a heat exchanger 300 according to a first embodiment of the present invention will be described with reference to FIG. 5 .
  • the heat exchanger 300 described with reference to FIG. 5 is described while simplifying the descriptions of the first heat exchanger 34 , the second heat exchanger 35 , and the reservoir 36 described with reference to FIGS. 1 to 4 above, and for the sake of convenience, explanations thereof are omitted except where necessary.
  • the heat exchanger 300 includes the first heat exchanger 34 that is an upstream heat exchanging portion, the second heat exchanger 35 that is a downstream heat exchanging portion, and the reservoir 36 .
  • the first heat exchanger 34 has an upstream core 342 and header tanks 341 , 343 .
  • the illustrated example is provided with a single upstream core 342 , but two or more cores may be used.
  • the upstream core 342 is a part that exchanges heat between the refrigerant flowing therein and the air flowing outside, and includes tubes through which the refrigerant flows and fins provided between the tubes.
  • the header tank 341 is attached.
  • the header tank 343 is attached.
  • An inflow passage 11 is provided in the header tank 341 .
  • An inflow passage 12 is provided in the header tank 343 .
  • the refrigerant flowing in from the inflow passage 11 flows into the upstream core 342 from the header tank 341 .
  • the refrigerant flowing through the upstream core 342 flows into the header tank 343 .
  • the refrigerant flowing into the header tank 343 flows out to the inflow passage 12 .
  • the inflow passage 12 is connected to the reservoir 36 .
  • the refrigerant flowing out to the inflow passage 12 flows into a main body portion 81 of the reservoir 36 .
  • the reservoir 36 has the main body portion 81 , the inflow passage 12 , the liquid-phase outflow passage 14 , and the gas-phase outflow passage 13 .
  • the main body portion 81 is a portion that separates the gas-liquid two-phase refrigerant flowing in from the inflow passage 12 into a liquid-phase refrigerant and a gas-phase refrigerant, and stores the liquid-phase refrigerant.
  • the inflow passage 12 , the liquid-phase outflow passage 14 , and the gas-phase outflow passage 13 are connected to the main body portion 81 .
  • the inflow passage 12 is a passage that connects the first heat exchanger 34 to the reservoir 36 .
  • the inflow passage 12 is connected to an inlet port 81 a provided in the main body portion 81 .
  • the liquid-phase outflow passage 14 is a flow passage that connects the reservoir 36 to the second heat exchanger 35 .
  • the liquid-phase outflow passage 14 is connected to a liquid-phase outlet port 81 c provided in the main body portion 81 .
  • the liquid-phase refrigerant flowing out from the liquid-phase outflow passage 14 flows into the second heat exchanger 35 .
  • the gas-phase outflow passage 13 is a flow passage that allows gas-phase refrigerant to flow out from the reservoir 36 .
  • the gas-phase outflow passage 13 is connected to a gas-phase outlet port 81 b provided in the main body portion 81
  • the second heat exchanger 35 has a header tank 351 , a downstream core 352 , and a header tank 353 .
  • the liquid-phase outflow passage 14 is connected to the header tank 351 .
  • the header tank 351 is provided at the upstream end of the downstream core 352 .
  • the header tank 353 is provided at the downstream end of the downstream core 352 .
  • An outflow passage 15 is connected to the header tank 353 .
  • Liquid-phase refrigerant flows from the header tank 351 to the downstream core 352 .
  • the downstream core 352 is a part that exchanges heat between the refrigerant flowing therein and the air flowing outside, and includes tubes through which the refrigerant flows and fins provided between the tubes. Accordingly, the liquid-phase refrigerant flowing into the downstream core 352 is directed to the header tank 353 while being subcooled.
  • the liquid-phase refrigerant flowing into the header tank 353 from the downstream core 352 then flows out to the outflow passage 15 .
  • the outflow passage 15 is connected to an expansion valve included in the refrigeration cycle device, and an evaporator is connected before the expansion valve.
  • the header tank 341 and the header tank 353 are formed by partitioning an integrally formed tank with a partitioning portion 356 .
  • the header tank 343 and the header tank 351 are formed by partitioning an integrally formed tank with the partitioning portion 356 .
  • the liquid-phase outflow passage 14 is connected to the reservoir 36 on the lower side, and the inflow passage 12 is connected at a higher point as compared to the liquid-phase outflow passage 14 .
  • the inflow passage 12 is connected at a point higher than the middle of the reservoir 36 in the longitudinal direction.
  • the height of the reservoir 36 is the height until the lower end 90 of the fourth outlet port 74 .
  • the height of the reservoir 36 is defined as a height limit at which liquid refrigerant can be substantially stored.
  • the height of the reservoir 36 is set by stack up “leak over years”, “load fluctuation buffer”, “surplus etc.” on top of each other.
  • Leakage over years refers to an expected amount of refrigerant that leaks from various parts over a number of years of use when the heat exchanger 2 is used for the refrigeration cycle.
  • Load fluctuation buffer is an expected amount of fluctuation in the amount of liquid-phase refrigerant that flows in during the operation of the refrigeration cycle. Since the combined height of “leakage over years” and “load fluctuation buffer” is liquid surface height required in the design of the reservoir 36 , the inflow passage 12 is preferably provided above this height.
  • a partition portion 82 and a buffer portion 83 are provided in the main body portion 81 of the reservoir 36 .
  • the partition portion 82 is a cylindrical portion extending downward from the gas-phase outflow passage 13 .
  • the buffer portion 83 is connected to the lower end of the partition portion 82 and is provided so as to gradually increase in diameter from the lower end of the partition portion 82 .
  • the incoming refrigerant from the inflow passage 12 is substantially liquid-phase refrigerant
  • the incoming refrigerant will hit the buffer portion 83 and then continue toward the liquid surface. Therefore, the refrigerant does not directly hit the liquid surface of the liquid-phase refrigerant accumulated inside, and disturbances of the liquid surface can be suppressed.
  • the interior of the reservoir 36 A is preferably divided into a plurality of spaces.
  • a main reservoir space 811 A and an auxiliary reservoir space 812 A are formed in a main body portion 81 A of the reservoir 36 A.
  • a partition wall 814 A for partitioning the main reservoir space 811 A from the auxiliary reservoir space 812 A is provided high enough to face the inflow passage 12 , and a communication passage 813 A is provided above the partition wall 814 A.
  • the partition wall 814 A is not necessarily provided at a position high enough to face the inflow passage 12 , and may be provided to a lower position instead.
  • a partition portion 82 B and a buffer portion 83 B are provided in the main body portion 81 .
  • the partition portion 82 B is a cylindrical portion extending downward from the gas-phase outflow passage 13 .
  • the buffer portion 83 B is connected to the lower end of the partition portion 82 B, and is configured as a disk-shaped member.
  • the disk-like buffer portion 83 B is formed by a disk member 831 .
  • the disk member 831 is provided with an outflow hole 84 B connected to the gas-phase outflow passage 13 .
  • Four notches 832 are provided along the periphery of the disk member 831 .
  • a buffer portion 83 Ba as shown in FIG. 13 may be formed by a disc member 831 a .
  • the disk member 831 a is provided with four dropdown holes 833 around the outflow hole 84 B.
  • gas-phase refrigerant can be sent out to the gas-phase outflow passage 13 .
  • FIG. 14 shows a reservoir 36 C according to a fourth embodiment.
  • the reservoir 36 C is provided with a partition portion 82 C and a buffer portion 83 C in the main body portion 81 .
  • the partition portion 82 C is a cylindrical portion extending downward from the gas-phase outflow passage 13 .
  • the buffer portion 83 C is provided below the partition portion 82 C, and is a plate member extending from the inner wall of the main body portion 81 .
  • FIG. 15 is a cross-sectional view taken along a cross section orthogonal to the axis passing through a center 815 , which is the central axis of a reservoir 36 D in the longitudinal direction according to a fifth embodiment.
  • the mounting position and the mounting angle of an inflow passage 12 D with respect to the main body 81 is designed so as to reduce disturbances in the liquid surface caused by liquid-phase refrigerant flowing into and vigorously hitting the accumulated liquid-phase refrigerant.
  • the inflow passage 12 D is provided with respect to the main body portion 81 such that if the inflow passage 12 D is extended along a center line 121 D, the inflow passage 12 D does not pass through the center 815 of the reservoir 36 D.
  • the center line 121 D of the inflow passage 12 D is a line that substantially equally divides the width of the inflow passage 12 D along the flow direction of the refrigerant.
  • the inflow passage 12 D is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage 12 D then flows in from an inlet port 81 a D collides with an inner wall surface 816 of the reservoir 36 D and then falls into the liquid-phase refrigerant stored in the reservoir.
  • the reservoir 36 D is provided such that a distance Ld from the inflow port 81 a D to an inner wall surface portion 816 a D of the reservoir 36 D which faces the inflow port 81 a D is shorter than a distance d between the farthest portions of the inner wall surface 816 of the reservoir 36 D.
  • the center 815 is the center of the circular cross section.
  • the distance d between the farthest portions of the inner wall surface 816 of the reservoir 36 D is the diameter of the inner wall surface 816 .
  • the inner wall surface 816 of the reservoir 36 D has a substantially circular cross section, and the distance Ld from the inflow port 81 a D to the inner wall surface 816 a D of the reservoir 36 D which faces the inflow port 81 a D is shorter than the diameter d of the inner wall surface 816 .
  • FIG. 16 shows a reservoir 36 E according to a modified example of the fifth embodiment.
  • an inflow port 81 a E is placed further upward as compared to the inflow port 81 a D shown in FIG. 15 .
  • the inflow port 81 a E is located at a position that directly faces toward the center 815 of the main body portion 81 .
  • the inflow passage 12 E is provided with respect to the main body portion 81 such that if a center line 121 E of the inflow passage 12 E is extended, the inflow passage 12 E does not pass through the center 815 of the reservoir 36 E.
  • the inflow passage 12 E is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage 12 E then flows in from the inlet port 81 a E collides with the inner wall surface 816 of the reservoir 36 E and then falls into the liquid-phase refrigerant stored in the reservoir 36 E.
  • the reservoir 36 E is provided such that a distance Le from the inflow port 81 a E to an inner wall surface portion 816 a E of the reservoir 36 E which faces the inflow port 81 a E is shorter than a distance d between the farthest portions of the inner wall surface 816 of the reservoir 36 E.
  • the center 815 is the center of the circular cross section.
  • the distance d between the farthest portions of the inner wall surface 816 of the reservoir 36 E is the diameter of the inner wall surface 816 .
  • the inner wall surface 816 of the reservoir 36 E has a substantially circular cross section, and the distance Le from the inflow port 81 a E to the inner wall surface 816 a E of the reservoir 36 E which faces the inflow port 81 a E is shorter than the diameter d of the inner wall surface 816 .
  • FIG. 17 shows a reservoir 36 F according to a modified example of the fifth embodiment.
  • an inflow port 81 a F is moved downward in the figure as compared to the inflow port 81 a D shown in FIG. 15 .
  • an inflow passage 12 F is also moved downward in the figure.
  • the inflow passage 12 F is provided with respect to the main body portion 81 such that if a center line 121 F of the inflow passage 12 F is extended, the inflow passage 12 F does not pass through the center 815 of the reservoir 36 F.
  • the inflow passage 12 F is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage 12 F then flows in from the inlet port 81 a F collides with the inner wall surface 816 of the reservoir 36 F and then falls into the liquid-phase refrigerant stored in the reservoir 36 F.
  • the reservoir 36 F is provided such that a distance Lf from the inflow port 81 a F to an inner wall surface portion 816 a F of the reservoir 36 F which faces the inflow port 81 a F is shorter than a distance d between the farthest portions of the inner wall surface 816 of the reservoir 36 F.
  • the inner wall surface 816 of the reservoir 36 F has a substantially circular cross section, and the distance Lf from the inflow port 81 a F to the inner wall surface 816 a F of the reservoir 36 F which faces the inflow port 81 a F is shorter than the diameter d of the inner wall surface 816 .
  • a part of the inner wall surface 122 F of the inflow passage 12 F is disposed so as to follow the tangent of the inner wall surface 816 of the reservoir 36 F.
  • FIG. 18 shows a reservoir 36 G as a modified example of the reservoir 36 A, and shows a cross section corresponding to the cross section shown in FIG. 9
  • An inflow passage 12 G is provided with respect to a main body portion 81 G such that if a center line 121 G of the inflow passage 12 G is extended, the center line 121 G does not pass through a center 812 Ga of an auxiliary reservoir space 812 G. As shown in the cross section view of FIG. 18 , the center line 121 G of the inflow passage 12 G is a line that substantially equally divides the width of the inflow passage 12 G along the flow direction of the refrigerant.
  • the inflow passage 12 G is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage 12 G then flows in from an inlet port 81 a G collides with an inner wall surface 812 Gb of the auxiliary reservoir space 812 G, and then falls into the liquid-phase refrigerant stored in the auxiliary reservoir space 812 G.
  • the auxiliary reservoir space 812 G is provided such that a distance Lg 2 from the inflow port 81 a G to an opposing inner wall surface 812 Gc is shorter than a distance d 2 between the farthest portions of the inner wall surface 812 Gb of the auxiliary reservoir space 812 G.
  • the arrangement of a communication passage 813 G that connects the auxiliary reservoir space 812 G to a main reservoir space 811 G may be designed similarly to the arrangement of the inflow passage 12 G.
  • the communication passage 813 G is provided such that if a center line 813 Ga of the communication passage 813 G is extended, the center line 813 Ga does not pass through a center 811 Ga of the main reservoir space 811 G.
  • the center line 813 Ga of the communication passage 813 G is a line that substantially equally divides the width of the communication passage 813 G along the flow direction of the refrigerant.
  • the center 811 Ga is the center of the circular cross section.
  • the distance d 1 between the farthest portions of an inner wall surface 811 Gb of the main reservoir space 811 G is the diameter of the inner wall surface 811 Gb.
  • the inner wall surface 811 Gb has a substantially circular cross section, and a distance Lg 1 from the inlet port 811 Gc connected to the main reservoir space 811 G to an inner wall surface portion 811 Gd that faces the inlet port 811 Gc is shorter than the diameter d 1 of the inner wall surface 811 Gb.
  • the heat exchanger 300 includes the first heat exchanger 34 which is an upstream heat exchanging portion that exchanges heat between a refrigerant passing through therein and air, the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G that performs gas-liquid separation on a gas-liquid two-phase refrigerant that flows out from the first heat exchanger 34 into a gas-phase refrigerant and a liquid-phase refrigerant, the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G storing the liquid-phase refrigerant, the inflow passage 12 , 12 D, 12 E, 12 F, 12 G that allows the gas-liquid two-phase refrigerant flowing out from the first heat exchanger 34 to flow into the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G, the gas-phase outflow passage 13 that allows the gas-phase refrigerant to flow out from the reservoir 36 ,
  • the inflow passage 12 , 12 D, 12 E, 12 F, 12 G is connected so as to be in communication with the inlet port 81 a , 81 a D, 81 a E, 81 a F, 81 a G which is disposed above a liquid surface of the liquid-phase refrigerant stored in the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G
  • the gas-phase outflow passage 13 is connected so as to be in communication with a gas-phase outlet port 81 b which is disposed above the liquid surface of the liquid-phase refrigerant stored in the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G
  • the liquid-phase outflow passage 14 is connected so as to be in communication with a liquid-phase outlet port 81 c which is disposed below the liquid surface of the liquid-phase refrigerant stored in the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G.
  • gas-phase refrigerant since the refrigerant flows in from above the liquid surface, gas-phase refrigerant does not flow into the liquid-phase refrigerant stored in the reservoir, and it is possible to suppress disturbances in the liquid surface.
  • the reservoir 36 , 36 A, 36 B, 36 C, 36 D, 36 E, 36 F, 36 G includes the partition portion 82 , 82 B, 82 C between the inlet port 81 a and the gas-phase outlet port 81 b.
  • the refrigerant flowing in from the inlet port hits the partition portion before flowing out from the gas-phase outlet port, and continues downward. Therefore, it is possible to suppress the liquid-phase refrigerant from flowing out of the gas-phase outlet port 81 b.
  • the partition portion 82 , 82 B, 82 C is disposed such that at least a portion thereof faces the inlet port 81 a . Due to this facing arrangement, it is possible to ensure that the refrigerant flowing in from the inlet port 81 a collides with the partition portion 82 , 82 B, 82 C.
  • the buffer portion 83 , 83 B, 83 C is provided between the inlet port 81 a and the liquid surface of the liquid-phase refrigerant.
  • the buffer portion 83 , 83 B, 83 C it is possible to prevent the refrigerant flowing in from the inlet port 81 a from directly falling onto the liquid surface, and it is possible to reduce disturbances of the liquid surface.
  • the buffer portion 83 , 83 B, 83 C is arranged between the inlet port 81 a and the liquid-phase outlet port 81 c , and is disposed closer toward the liquid surface as compared to the inlet port 81 a . Due to this positioning, the liquid-phase refrigerant flowing in from the inlet port 81 a will more reliably collide with the buffer portion 83 , 83 B, 83 C, and it is possible to prevent disturbances in the liquid surface.
  • the reservoirs 36 , 36 B, 36 C each have a substantially cylindrical main body portion 81 capable of storing the liquid-phase refrigerant therein, and the body portions 81 to the inner wall is preferably equal to or less than one-third of the radius of the main body 81 .
  • the inflow passage 12 D, 12 E, 12 F, 12 G is disposed such that if the center line 121 D, 121 E, 121 F, 121 G of the inflow passage 12 D, 12 E, 12 F, 12 G is extended, the center line 121 D, 121 E, 121 F, 121 G reaches the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G without passing through the center 815 , 812 Ga of the reservoir 36 D, 36 E, 36 F, 36 G.
  • the gas-liquid two-phase refrigerant flowing in from the inflow passage 12 D, 12 E, 12 F, 12 G is able to hit the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G and then fall down. Accordingly, it is possible to prevent the incoming refrigerant from directly falling into the liquid-phase refrigerant stored in the reservoir 36 D, 36 E, 36 F, 36 G, thereby suppressing disturbances in the liquid surface of the liquid-phase refrigerant.
  • the inflow passage 12 D, 12 E, 12 F, 12 G is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage 12 D, 12 E, 12 F, 12 G then flows in from the inlet port 81 a D, 81 a E, 81 a F, 81 a G collides with the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G and then falls into the liquid-phase refrigerant stored in the reservoir 36 D, 36 E, 36 F, 36 G.
  • the gas-liquid two-phase refrigerant flowing in from the inflow passage 12 D, 12 E, 12 F, 12 G is able to reliably hit the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G and then fall down.
  • the distance Ld, Le, Lf, Lg 1 , Lg 2 from the inlet port 81 a D, 81 a E, 81 a F, 81 a G to an inner wall surface portion 816 a D, 816 a E, 816 a G, 811 Gd, 812 Gc of the reservoir 36 D, 36 E, 36 F, 36 G that faces the inlet port 81 a D, 81 a E, 81 a F, 81 a G is shorter than a distance d, d 1 , d 2 between the farthest portions of the inner wall surface of the reservoir 36 D, 36 E, 36 F, 36 G.
  • the gas-liquid two-phase refrigerant flowing in from the inflow passage 12 D, 12 E, 12 F, 12 G is able to reliably hit the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G and then fall down.
  • the inner wall surface 816 , 812 Gb of the reservoir 36 D, 36 E, 36 F, 36 G has a substantially circular cross section, and the distance Ld, Le, Lf, Lg 1 from the inlet port 81 a D, 81 a E, 81 a F, 81 a G to the inner wall surface portion 816 a D, 816 a E, 816 a G, 811 Gd of the reservoir 36 D, 36 E, 36 F, 36 G that faces the inlet port 81 a D, 81 a E, 81 a F, 81 a G is shorter than the diameter d, d 1 of the reservoir 36 D, 36 E, 36 F, 36 G.
  • the incoming gas-liquid two-phase refrigerant is able to reliably hit the inner wall surface 816 , 811 Gb of the reservoir 36 D, 36 E, 36 F, 36 G and then fall down.
  • a part of the inner wall surface 122 F of the inflow passage 12 F is disposed so as to follow the tangent of the inner wall surface 816 of the reservoir 36 F.
  • the incoming gas-liquid two-phase refrigerant is able to reliably hit the inner wall surface 816 of the reservoir 36 F and then fall down.

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