US20190128577A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- 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
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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- 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
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- 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
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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
- 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
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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
- 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
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—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
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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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
- 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
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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
- 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
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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
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
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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
- 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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Abstract
A heat exchanger includes a heat exchanging portion, a reservoir 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 and stores the liquid-phase refrigerant, and an inflow passage that allows the gas-liquid two-phase refrigerant flowing out from the heat exchanging portion to flow into the reservoir. The inflow passage is connected so as to be in communication with an inlet port of the reservoir which is disposed above a liquid surface of the liquid-phase refrigerant stored in the reservoir.
Description
- This application is based on and claims the benefits of priority of Japanese Patent Application No. 2016-078224 filed on Apr. 8, 2016 and Japanese Patent Application No. 2016-234961 filed on Dec. 2, 2016, the entire disclosure of which is incorporated herein by reference.
- The present disclosure relates to a heat exchanger.
- Conventionally, for example as described in
Patent Document 1 below, a refrigeration cycle device which uses this type of heat exchanger is known. The refrigeration cycle device described inPatent 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. Specifically, 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. Further, 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. According to the gas-liquid separator disclosed inPatent Document 1, the refrigerant is introduced from below. - Patent Literature 1: JP 2014-149123 A
- When refrigerant is introduced from the lower side of the gas-liquid separator as described in
Patent Document 1, during a heating operation the gas-phase refrigerant is blown out into the liquid-phase refrigerant, and the liquid-phase refrigerant becomes mixed with the gas-phase refrigerant, the liquid surface of the liquid-phase refrigerant is not stabilized, and the gas-liquid separator may be unable to function as a reservoir. - It is an object of the present disclosure to provide a heat exchanger that can function as a reservoir by suppressing turbulence in the liquid surface of a reservoir.
- According to the present disclosure, 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, 36A, 36B, 36C, 36D, 36E, 36F, 36G) 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.
- According to the present disclosure, 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.
- Furthermore, according to the present disclosure, a gas-phase outflow passage and a liquid-phase outflow passage are provided, and can function as both a receiver and an accumulator. In particular, when 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.
- Further, according to the present disclosure, the reservoir preferably includes a partition portion (82, 82B, 82C) between the inlet port and the gas-phase outlet port.
- By providing a partition portion 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.
- Further, according to the present disclosure, a buffer portion (83, 83B, 83C) is preferably disposed between the inlet port and the liquid surface of the liquid-phase refrigerant
- In the case where 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.
- Further, according to the present disclosure, 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, 812Gb) of the reservoir (36D, 36E, 36F, 36G) without passing through a center (815, 812Ga) of the reservoir.
- In the case where 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.
- It is noted that the reference numerals in parentheses described in “SUMMARY OF INVENTION” and “CLAIMS” indicate the correspondence relationship with “DESCRIPTION OF EMBODIMENTS” described later, and “SUMMARY OF INVENTION” and “CLAIMS” are not limited to “DESCRIPTION OF EMBODIMENTS”.
-
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 inFIG. 1 is operated in a cooling operation. -
FIG. 3 is a view for explaining a case where the refrigeration cycle shown inFIG. 1 is operated in a heating operation. -
FIG. 4 is a view for further explaining the heat exchanger shown inFIG. 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 ofFIG. 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. - Hereinafter, the present embodiments will be described with reference to the attached drawings. In order to facilitate the ease of understanding, the same reference numerals are attached to the same constituent elements in each drawing where possible, and redundant explanations are omitted.
- As shown in
FIG. 1 , an integratedvalve device 6 is used in avehicle air conditioner 2 which is installed in a vehicle and which performs air conditioning in a passenger compartment. Thevehicle air conditioner 2 includes arefrigeration cycle device 3, awater cycle device 4, and anair conditioning unit 5. Theair conditioning unit 5 is a unit for blowing warm air or cold air into the passenger compartment. Therefrigeration cycle device 3 and thewater cycle device 4 are form a heat pump unit which adjusts the temperature of the air blown out from theair conditioning unit 5. - The
refrigeration cycle device 3 and the integratedvalve device 6 will be described. Therefrigeration cycle device 3 includes arefrigerant flow passage 30, acompressor 31, acondenser 32, afirst heat exchanger 34, asecond heat exchanger 35, areservoir 36, anexpansion valve 37, anevaporator 38, and the integratedvalve device 6. Thefirst heat exchanger 34, thesecond heat exchanger 35, and thereservoir 36 correspond to the heat exchanger of the present invention. - The integrated
valve device 6 includes afixed throttle 61, afirst valve 62, asecond valve 64, and athird valve 63. Thewater cycle device 4 includes awater flow passage 40, awater pump 41, a water-side heat exchanger 42, and aheater core 43. Theair conditioning unit 5 includes acasing 51, anair mix door 52, ablower fan 53, and an inside/outsideair switching door 54. - The
refrigerant flow passage 30 is a flow passage in which refrigerant flows, and connects thecompressor 31, thecondenser 32, thefirst heat exchanger 34, thesecond heat exchanger 35, thereservoir 36, theexpansion valve 37, and theevaporator 38. Here, HFC refrigerant or HFO refrigerant, for example, may be used as refrigerant. Oil for lubricating thecompressor 31 is mixed in the refrigerant. - The
compressor 31 is an electric compressor and includes ansuction port 311 and adischarge port 312. Thecompressor 31 sucks refrigerant from thesuction port 311 and compresses the refrigerant. Thecompressor 31 discharges the refrigerant, which is in an overheated state due to being compressed, from thedischarge port 312. The refrigerant discharged from thedischarge port 312 flows into thecondenser 32. - The
condenser 32 is a conventional heat exchanger and includes aninlet port 321 and anoutlet port 322. Thecondenser 32 is configured to exchange heat with the water-side heat exchanger 42. Since thecondenser 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 thecompressor 31 flows into thecondenser 32 from theinlet port 321. The refrigerant, having flown into thecondenser 32, exchanges heat with water flowing through the water-side heat exchanger 42, and flows out from theoutlet port 322 in a lower temperature state. The refrigerant flowing out from theoutlet port 322 then flows into the fixedthrottle 61 and thefirst valve 62 which form a part of theintegrated valve device 6. - When the
first valve 62 is closed, the refrigerant is decompressed through the fixedthrottle 61. As such, the pressure of the refrigerant is reduced, and this low pressure refrigerant flows into thefirst heat exchanger 34. Conversely, when thefirst valve 62 is opened, the refrigerant is not decompressed and flows into thefirst 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 thefirst heat exchanger 34 exchanges heat with the outside air and then flows into thereservoir 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 thethird valve 63. The gas-phase refrigerant that flows into thethird valve 63 then flows toward thecompressor 31 when thethird valve 63 is opened. Conversely, the separated liquid-phase refrigerant is stored in thereservoir 36 and flows out toward thesecond 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. Thesecond heat exchanger 35 further enhances the heat exchange efficiency of the refrigerant by cooperating with thefirst heat exchanger 34 to exchange heat between the incoming liquid-phase refrigerant and outside air. The refrigerant that flows out from thesecond heat exchanger 35 then flows into thesecond valve 64. - The
second valve 64 is configured as a three-way valve that selectively allows the incoming refrigerant to flow toward either thecompressor 31 or theexpansion valve 37. Theexpansion valve 37 decompresses the incoming refrigerant and then discharges the refrigerant. The refrigerant discharged from theexpansion valve 37 then flows toward theevaporator 38. Theexpansion valve 37 is a temperature-sensitive mechanical expansion valve that decompresses and expands the refrigerant flowing into theevaporator 38 such that the degree of superheating of the refrigerant discharged from theevaporator 38 falls within a predetermined range. - The
evaporator 38 has aninlet port 381 and anoutlet port 382. The refrigerant flowing toward theevaporator 38 flows into the evaporator 38 from theinlet port 381. Since theevaporator 38 is disposed in thecasing 51, theevaporator 38 exchanges heat with the air flowing in thecasing 51. The refrigerant flowing in theevaporator 38 exchanges heat with the air flowing in thecasing 51 and then flows out from theoutlet port 382 toward thecompressor 31. - Next, the
water cycle device 4 will be described. Thewater flow passage 40 is a flow passage in which water flows, and connects thewater pump 41, the water-side heat exchanger 42, and theheater core 43. Thewater pump 41 has aninlet port 411 and adischarge port 412. Thewater pump 41 sucks in water from theinlet port 411 and discharges water from thedischarge port 412. By driving thewater pump 41, it is possible to form a flow of water in thewater flow passage 40. - The water discharged from the
discharge port 412 due to the operation of thewater pump 41 flows toward the water-side heat exchanger 42. As described above, the water-side heat exchanger 42 and thecondenser 32 form a water-refrigerant heat exchanger. The water-side heat exchanger 42 has aninlet port 421 and anoutlet port 422. The water that flows into the water-side heat exchanger 42 from theinlet port 421 is heat exchanged with the refrigerant flowing through thecondenser 32, and then flows out from theoutlet port 422. Since the refrigerant flowing through thecondenser 32 is a high temperature and high pressure refrigerant, the water flowing through the waterside heat exchanger 42 is heated and then flows toward theheater core 43. - The
heater core 43 is disposed in thecasing 51 of theair conditioning unit 5. Theheater core 43 is for exchanging heat with the air flowing in thecasing 51. Theheater core 43 has aninlet port 431 and anoutlet port 432. Water which is heated by flowing through the water-side heat exchanger 42 flows into theinlet port 431. The water flowing into theheater core 43 exchanges heat with the air flowing in thecasing 51. The water flowing in theheater core 43 is reduced in temperature and then flows out from theoutlet port 432 toward thewater pump 41. - Next, the
air conditioning unit 5 will be described. Thecasing 51 forms a flow passage that carries the conditioned air that will flow into the passenger compartment. From an upstream side in thecasing 51, the inside/outsideair switching door 54, theblower fan 53, theevaporator 38, theair mix door 52, and theheater core 43 are arranged. - The inside/outside
air switching door 54 is a door for switching between intaking the air flowing in thecasing 51 from outside the passenger compartment or inside the passenger compartment. Theblower fan 53 generates an air flow in thecasing 51 and sends the conditioned air into the passenger compartment. Theair mix door 52 is a door for switching between whether or not the air flowing in thecasing 51 passes through theheater core 43. - The
vehicle air conditioner 2 is configured to open and close the respective valves of theintegrated valve device 6 to adjust the amount of refrigerant flowing through therefrigeration cycle device 3, to drive thewater pump 41 to adjust the amount of water flowing through thewater cycle device 4, and to drive theblower fan 53 to adjust the amount of air flowing through theair conditioning unit 5, thereby cooling or heating the passenger compartment. - With reference to
FIG. 2 , the operation of thevehicle air conditioner 2 performing a cooling operation will be described. InFIG. 2 , the flow of the refrigerant is indicated by FLc. During the cooling operation, thewater pump 41 is not driven, and as such no water flow is generated in thewater cycle device 4. Accordingly, the high-temperature and high-pressure gas-phase refrigerant discharged from thecompressor 31 flows toward theintegrated valve device 6 without undergoing changes. During the cooling operation, thefirst valve 62 is in an open state. Accordingly, the refrigerant flowing from thecondenser 32 flows toward thefirst 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 thereservoir 36. During the cooling operation, thereservoir 36 mainly functions as a receiver that allows liquid-phase refrigerant to flow out. Thethird valve 63 is closed, and thus the liquid-phase refrigerant flows out from thereservoir 36 to thesecond heat exchanger 35. - During the cooling operation, the
second heat exchanger 35 functions as a subcooler. The refrigerant flowing into thesecond heat exchanger 35 is further cooled through heat exchange with the outside air. During the cooling operation, thefirst heat exchanger 34 and thesecond heat exchanger 35 function as a condenser of therefrigeration cycle device 3. - The liquid-phase refrigerant that flows out from the
second heat exchanger 35 then flows into thesecond valve 64. During the cooling operation, thesecond valve 64 is switched such that the incoming refrigerant is only allowed to flow toward theexpansion valve 37. The refrigerant decompressed by theexpansion valve 37 flows into theevaporator 38. - During the cooling operation, the
blower fan 53 is driven, and theair mix door 52 is positioned so as to close theheater core 43 side. Therefore, the air flowing in thecasing 51 is cooled through heat exchange with the low-temperature refrigerant in theevaporator 38. The cooled air flows in thecasing 51 and is supplied into the passenger compartment. - With reference to
FIG. 3 , the operation of thevehicle air conditioner 2 performing a heating operation will be described. InFIG. 3 , the flow of the refrigerant is indicated by FLh. During the heating operation, thewater pump 41 is driven, and as such a water flow is generated in thewater cycle device 4. Therefore, the high-temperature and high-pressure gas-phase refrigerant discharged from thecompressor 31 flows into in thecondenser 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 theintegrated valve device 6. During the heating operation, thefirst valve 62 is in a closed state. Accordingly, the refrigerant flowing from thecondenser 32 is pressure reduced, and then flows toward thefirst 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 thereservoir 36. In the case of the heating operation, thereservoir 36 mainly functions as an accumulator which allows gas-phase refrigerant to flow out. Thethird valve 63 is opened, and thus the gas-phase refrigerant flows out toward thecompressor 31. - In the
reservoir 36, the incoming refrigerant is separated into gas and liquid-phases, and the liquid-phase refrigerant is stored. The liquid-phase refrigerant flows out toward thesecond heat exchanger 35. Thesecond valve 64 opens a flow passage toward thesuction port 311, and so liquid-phase refrigerant and oil gradually return to thecompressor 31. - During the heating operation, the
blower fan 53 is driven, and theair mix door 52 is positioned so as to open theheater core 43 side. Therefore, the air flowing in thecasing 51 is heated through heat exchange with high temperature water in theheater core 43. The heated air flows in thecasing 51 and is supplied into the passenger compartment. - In the
integrated valve device 6 of the present embodiment, the fixedthrottle 61, thefirst valve 62, thesecond valve 64, and thethird valve 63 are integrally formed, and may be housed inside thereservoir 36. - As shown in
FIG. 4 , when theintegrated valve device 6 is inserted into and positioned within thereservoir 36, aninsertion end portion 90 is inserted to the lowest position. Afourth outlet port 74 is provided so as to extend downward from theinsertion end portion 90. Since thefirst heat exchanger 34 and thesecond heat exchanger 35 are disposed on one side of theintegrated valve device 6, the inlet port and outlet port of theintegrated valve device 6 which allow refrigerant to be exchanged with thefirst heat exchanger 34 and thesecond heat exchanger 35 are disposed toward the side of thefirst heat exchanger 34 and thesecond heat exchanger 35. From this viewpoint, afirst outlet port 76, through which refrigerant flows out to thefirst heat exchanger 34, is arranged above thefirst heat exchanger 34 side. Asecond inlet port 75, through which refrigerant flows in from thesecond heat exchanger 35, is disposed on thesecond heat exchanger 35 side and below thefirst outlet port 76. Afirst inlet port 71, Asecond outlet port 72, and Athird outlet port 73 are provided an opposite side from the side that faces thefirst heat exchanger 34 and thesecond heat exchanger 35. Aninflow 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 toFIG. 5 . Theheat exchanger 300 described with reference toFIG. 5 is described while simplifying the descriptions of thefirst heat exchanger 34, thesecond heat exchanger 35, and thereservoir 36 described with reference toFIGS. 1 to 4 above, and for the sake of convenience, explanations thereof are omitted except where necessary. - The
heat exchanger 300 includes thefirst heat exchanger 34 that is an upstream heat exchanging portion, thesecond heat exchanger 35 that is a downstream heat exchanging portion, and thereservoir 36. Thefirst heat exchanger 34 has anupstream core 342 andheader tanks upstream core 342, but two or more cores may be used. Theupstream 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. - At the upstream side end of the
upstream core 342, theheader tank 341 is attached. At the downstream side end of theupstream core 342, theheader tank 343 is attached. - An
inflow passage 11 is provided in theheader tank 341. Aninflow passage 12 is provided in theheader tank 343. The refrigerant flowing in from theinflow passage 11 flows into theupstream core 342 from theheader tank 341. The refrigerant flowing through theupstream core 342 flows into theheader tank 343. The refrigerant flowing into theheader tank 343 flows out to theinflow passage 12. Theinflow passage 12 is connected to thereservoir 36. The refrigerant flowing out to theinflow passage 12 flows into amain body portion 81 of thereservoir 36. - The
reservoir 36 has themain body portion 81, theinflow passage 12, the liquid-phase outflow passage 14, and the gas-phase outflow passage 13. Themain body portion 81 is a portion that separates the gas-liquid two-phase refrigerant flowing in from theinflow 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 themain body portion 81. Theinflow passage 12 is a passage that connects thefirst heat exchanger 34 to thereservoir 36. Theinflow passage 12 is connected to aninlet port 81 a provided in themain body portion 81. The liquid-phase outflow passage 14 is a flow passage that connects thereservoir 36 to thesecond heat exchanger 35. The liquid-phase outflow passage 14 is connected to a liquid-phase outlet port 81 c provided in themain body portion 81. The liquid-phase refrigerant flowing out from the liquid-phase outflow passage 14 flows into thesecond heat exchanger 35. The gas-phase outflow passage 13 is a flow passage that allows gas-phase refrigerant to flow out from thereservoir 36. The gas-phase outflow passage 13 is connected to a gas-phase outlet port 81 b provided in themain body portion 81 - The
second heat exchanger 35 has aheader tank 351, adownstream core 352, and aheader tank 353. The liquid-phase outflow passage 14 is connected to theheader tank 351. Theheader tank 351 is provided at the upstream end of thedownstream core 352. At the downstream end of thedownstream core 352, theheader tank 353 is provided. Anoutflow passage 15 is connected to theheader tank 353. - Liquid-phase refrigerant flows from the
header tank 351 to thedownstream core 352. Thedownstream 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 thedownstream core 352 is directed to theheader tank 353 while being subcooled. - The liquid-phase refrigerant flowing into the
header tank 353 from thedownstream core 352 then flows out to theoutflow passage 15. Theoutflow passage 15 is connected to an expansion valve included in the refrigeration cycle device, and an evaporator is connected before the expansion valve. - In the present embodiment, the
header tank 341 and theheader tank 353 are formed by partitioning an integrally formed tank with apartitioning portion 356. Similarly, theheader tank 343 and theheader tank 351 are formed by partitioning an integrally formed tank with thepartitioning portion 356. - The liquid-
phase outflow passage 14 is connected to thereservoir 36 on the lower side, and theinflow passage 12 is connected at a higher point as compared to the liquid-phase outflow passage 14. Theinflow passage 12 is connected at a point higher than the middle of thereservoir 36 in the longitudinal direction. InFIG. 4 , the height of thereservoir 36 is the height until thelower end 90 of thefourth outlet port 74. The height of thereservoir 36 is defined as a height limit at which liquid refrigerant can be substantially stored. - As shown in
FIG. 6 , the height of thereservoir 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 theheat 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 thereservoir 36, theinflow passage 12 is preferably provided above this height. - As shown in
FIG. 7 , apartition portion 82 and abuffer portion 83 are provided in themain body portion 81 of thereservoir 36. Thepartition portion 82 is a cylindrical portion extending downward from the gas-phase outflow passage 13. Thebuffer portion 83 is connected to the lower end of thepartition portion 82 and is provided so as to gradually increase in diameter from the lower end of thepartition portion 82. - During the cooling operation, In the case where the incoming refrigerant from the
inflow passage 12 is substantially liquid-phase refrigerant, the incoming refrigerant will hit thebuffer 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. - As shown in
FIG. 8 , during the heating operation, when the refrigerant flowing in from theinflow passage 12 is substantially gas-phase refrigerant, gas-liquid separation is performed while swirling around thepartition portion 82. The gas-liquid separated liquid-phase refrigerant falls down while hitting thebuffer section 83. 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. Since the liquid-phase refrigerant may be separated in this manner, the gas-phase refrigerant enters thepartition portion 82 from the lower end of thebuffer portion 83 and flows out from the gas-phase outflow passage 13. - From the viewpoint of suppressing disturbances of the liquid surface, as shown in
FIGS. 9 and 10 , in areservoir 36A of a second embodiment, the interior of thereservoir 36A is preferably divided into a plurality of spaces. Amain reservoir space 811A and anauxiliary reservoir space 812A are formed in amain body portion 81A of thereservoir 36A. - As shown in
FIG. 10 , when the refrigerant flows in from theinflow passage 12, the refrigerant is distributed to themain reservoir space 811A and theauxiliary reservoir space 812A, and the liquid-phase refrigerant is stored. In the present embodiment, apartition wall 814 A for partitioning themain reservoir space 811A from theauxiliary reservoir space 812A is provided high enough to face theinflow passage 12, and acommunication passage 813A is provided above thepartition wall 814A. Thepartition wall 814A is not necessarily provided at a position high enough to face theinflow passage 12, and may be provided to a lower position instead. - In a
reservoir 36B according to a third embodiment shown inFIG. 11 , apartition portion 82B and abuffer portion 83B are provided in themain body portion 81. Thepartition portion 82B is a cylindrical portion extending downward from the gas-phase outflow passage 13. Thebuffer portion 83B is connected to the lower end of thepartition portion 82B, and is configured as a disk-shaped member. - As shown in
FIG. 12 , which is a view along the direction of the arrow A inFIG. 11 , the disk-like buffer portion 83B is formed by adisk member 831. Thedisk member 831 is provided with anoutflow hole 84B connected to the gas-phase outflow passage 13. Fournotches 832 are provided along the periphery of thedisk member 831. - As a modified example, a buffer portion 83Ba as shown in
FIG. 13 may be formed by adisc member 831 a. Thedisk member 831 a, is provided with fourdropdown holes 833 around theoutflow hole 84B. In this manner, it is possible to stop the swirling flow of the gas-liquid two-phase refrigerant flowing in from theinflow passage 12 while suppressing any gas-liquid separated liquid-phase refrigerant from directly hitting the liquid surface. Accordingly, gas-phase refrigerant can be sent out to the gas-phase outflow passage 13. -
FIG. 14 shows areservoir 36C according to a fourth embodiment. Thereservoir 36C is provided with apartition portion 82C and abuffer portion 83C in themain body portion 81. Thepartition portion 82C is a cylindrical portion extending downward from the gas-phase outflow passage 13. Thebuffer portion 83C is provided below thepartition portion 82C, and is a plate member extending from the inner wall of themain body portion 81. -
FIG. 15 is a cross-sectional view taken along a cross section orthogonal to the axis passing through acenter 815, which is the central axis of areservoir 36D in the longitudinal direction according to a fifth embodiment. According to thereservoir 36D, the mounting position and the mounting angle of aninflow passage 12D with respect to themain 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 12D is provided with respect to themain body portion 81 such that if theinflow passage 12D is extended along acenter line 121D, theinflow passage 12D does not pass through thecenter 815 of thereservoir 36D. As shown in the cross section view ofFIG. 15 , thecenter line 121D of theinflow passage 12D is a line that substantially equally divides the width of theinflow passage 12D along the flow direction of the refrigerant. - The
inflow passage 12D is provided such that the gas-liquid two-phase refrigerant which flows through theinflow passage 12D then flows in from aninlet port 81 aD collides with aninner wall surface 816 of thereservoir 36D and then falls into the liquid-phase refrigerant stored in the reservoir. - The
reservoir 36D is provided such that a distance Ld from theinflow port 81 aD to an innerwall surface portion 816 aD of thereservoir 36D which faces theinflow port 81 aD is shorter than a distance d between the farthest portions of theinner wall surface 816 of thereservoir 36D. - Since the
main body portion 81 is substantially cylindrical, thecenter 815 is the center of the circular cross section. The distance d between the farthest portions of theinner wall surface 816 of thereservoir 36D is the diameter of theinner wall surface 816. Accordingly, theinner wall surface 816 of thereservoir 36D has a substantially circular cross section, and the distance Ld from theinflow port 81 aD to theinner wall surface 816 aD of thereservoir 36D which faces theinflow port 81 aD is shorter than the diameter d of theinner wall surface 816. -
FIG. 16 shows areservoir 36E according to a modified example of the fifth embodiment. In thereservoir 36E, aninflow port 81 aE is placed further upward as compared to theinflow port 81 aD shown inFIG. 15 . When only considering the position of theinflow port 81 aE, theinflow port 81 aE is located at a position that directly faces toward thecenter 815 of themain body portion 81. However, by changing the angle of aninflow passage 12E, theinflow passage 12E is provided with respect to themain body portion 81 such that if acenter line 121E of theinflow passage 12E is extended, theinflow passage 12E does not pass through thecenter 815 of thereservoir 36E. - The
inflow passage 12E is provided such that the gas-liquid two-phase refrigerant which flows through theinflow passage 12E then flows in from theinlet port 81 aE collides with theinner wall surface 816 of thereservoir 36E and then falls into the liquid-phase refrigerant stored in thereservoir 36E. - The
reservoir 36E is provided such that a distance Le from theinflow port 81 aE to an innerwall surface portion 816 aE of thereservoir 36E which faces theinflow port 81 aE is shorter than a distance d between the farthest portions of theinner wall surface 816 of thereservoir 36E. - Since the
main body portion 81 is substantially cylindrical, thecenter 815 is the center of the circular cross section. The distance d between the farthest portions of theinner wall surface 816 of thereservoir 36E is the diameter of theinner wall surface 816. Accordingly, theinner wall surface 816 of thereservoir 36E has a substantially circular cross section, and the distance Le from theinflow port 81 aE to theinner wall surface 816 aE of thereservoir 36E which faces theinflow port 81 aE is shorter than the diameter d of theinner wall surface 816. -
FIG. 17 shows areservoir 36F according to a modified example of the fifth embodiment. In thereservoir 36F, aninflow port 81 aF is moved downward in the figure as compared to theinflow port 81 aD shown inFIG. 15 . Similarly, aninflow passage 12F is also moved downward in the figure. Here, by moving theinflow passage 12F downward in the figure and without changing the angle of theinflow passage 12F, theinflow passage 12F is provided with respect to themain body portion 81 such that if acenter line 121F of theinflow passage 12F is extended, theinflow passage 12F does not pass through thecenter 815 of thereservoir 36F. - The
inflow passage 12F is provided such that the gas-liquid two-phase refrigerant which flows through theinflow passage 12F then flows in from theinlet port 81 aF collides with theinner wall surface 816 of thereservoir 36F and then falls into the liquid-phase refrigerant stored in thereservoir 36F. - The
reservoir 36F is provided such that a distance Lf from theinflow port 81 aF to an innerwall surface portion 816 aF of thereservoir 36F which faces theinflow port 81 aF is shorter than a distance d between the farthest portions of theinner wall surface 816 of thereservoir 36F. - The
inner wall surface 816 of thereservoir 36F has a substantially circular cross section, and the distance Lf from theinflow port 81 aF to theinner wall surface 816 aF of thereservoir 36F which faces theinflow port 81 aF is shorter than the diameter d of theinner wall surface 816. - Further, a part of the
inner wall surface 122F of theinflow passage 12F is disposed so as to follow the tangent of theinner wall surface 816 of thereservoir 36F. - Similar to the
reservoir 36A described with reference toFIGS. 9 and 10 , the same effects can be obtained by designing the arrangement of theinflow passage 12.FIG. 18 shows areservoir 36G as a modified example of thereservoir 36A, and shows a cross section corresponding to the cross section shown inFIG. 9 - An
inflow passage 12G is provided with respect to amain body portion 81G such that if acenter line 121G of theinflow passage 12G is extended, thecenter line 121G does not pass through a center 812Ga of anauxiliary reservoir space 812G. As shown in the cross section view ofFIG. 18 , thecenter line 121G of theinflow passage 12G is a line that substantially equally divides the width of theinflow passage 12G along the flow direction of the refrigerant. - The
inflow passage 12G is provided such that the gas-liquid two-phase refrigerant which flows through theinflow passage 12G then flows in from aninlet port 81 aG collides with an inner wall surface 812Gb of theauxiliary reservoir space 812G, and then falls into the liquid-phase refrigerant stored in theauxiliary reservoir space 812G. - The
auxiliary reservoir space 812G is provided such that a distance Lg2 from theinflow port 81 aG to an opposing inner wall surface 812Gc is shorter than a distance d2 between the farthest portions of the inner wall surface 812Gb of theauxiliary reservoir space 812G. - The arrangement of a
communication passage 813G that connects theauxiliary reservoir space 812G to amain reservoir space 811G may be designed similarly to the arrangement of theinflow passage 12G. Thecommunication passage 813G is provided such that if a center line 813Ga of thecommunication passage 813G is extended, the center line 813Ga does not pass through a center 811Ga of themain reservoir space 811G. As shown in the cross section view ofFIG. 18 , the center line 813Ga of thecommunication passage 813G is a line that substantially equally divides the width of thecommunication passage 813G along the flow direction of the refrigerant. - Since the
main reservoir space 811G is substantially cylindrical, the center 811Ga is the center of the circular cross section. The distance d1 between the farthest portions of an inner wall surface 811Gb of themain reservoir space 811G is the diameter of the inner wall surface 811Gb. Accordingly, the inner wall surface 811Gb has a substantially circular cross section, and a distance Lg1 from the inlet port 811Gc connected to themain reservoir space 811G to an inner wall surface portion 811Gd that faces the inlet port 811Gc is shorter than the diameter d1 of the inner wall surface 811Gb. - As described above, the
heat exchanger 300 according to the present embodiment includes thefirst heat exchanger 34 which is an upstream heat exchanging portion that exchanges heat between a refrigerant passing through therein and air, thereservoir first heat exchanger 34 into a gas-phase refrigerant and a liquid-phase refrigerant, thereservoir inflow passage first heat exchanger 34 to flow into thereservoir phase outflow passage 13 that allows the gas-phase refrigerant to flow out from thereservoir phase outflow passage 14 that allows the liquid-phase refrigerant to flow out from thereservoir inflow passage inlet port reservoir 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 thereservoir 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 thereservoir - According to the present embodiment, 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.
- Further, according to the present embodiment, the
reservoir partition portion inlet port 81 a and the gas-phase outlet port 81 b. - By providing a partition portion 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 81 b. - Further according to the present embodiment, the
partition portion inlet port 81 a. Due to this facing arrangement, it is possible to ensure that the refrigerant flowing in from theinlet port 81 a collides with thepartition portion - Further according to the present embodiment, the
buffer portion inlet port 81 a and the liquid surface of the liquid-phase refrigerant. By providing thebuffer portion inlet port 81 a from directly falling onto the liquid surface, and it is possible to reduce disturbances of the liquid surface. - Further according to the present embodiment, at least part of the
buffer portion inlet port 81 a and the liquid-phase outlet port 81 c, and is disposed closer toward the liquid surface as compared to theinlet port 81 a. Due to this positioning, the liquid-phase refrigerant flowing in from theinlet port 81 a will more reliably collide with thebuffer portion - In the present embodiment, the
reservoirs main body portion 81 capable of storing the liquid-phase refrigerant therein, and thebody portions 81 to the inner wall is preferably equal to or less than one-third of the radius of themain body 81. - With such a configuration, it is possible to suppress disturbances in the liquid surface.
- Further according to the present embodiment, the
inflow passage center line inflow passage center line inner wall surface 816, 812Gb of thereservoir center 815, 812Ga of thereservoir - With such a configuration, the gas-liquid two-phase refrigerant flowing in from the
inflow passage inner wall surface 816, 812Gb of thereservoir reservoir - Further according to the present embodiment, the
inflow passage inflow passage inlet port 81 aD, 81 aE, 81 aF, 81 aG collides with theinner wall surface 816, 812Gb of thereservoir reservoir - With such a configuration, the gas-liquid two-phase refrigerant flowing in from the
inflow passage inner wall surface 816, 812Gb of thereservoir - Further according to the present embodiment, the distance Ld, Le, Lf, Lg1, Lg2 from the
inlet port 81 aD, 81 aE, 81 aF, 81 aG to an innerwall surface portion 816 aD, 816 aE, 816 aG, 811Gd, 812Gc of thereservoir inlet port 81 aD, 81 aE, 81 aF, 81 aG is shorter than a distance d, d1, d2 between the farthest portions of the inner wall surface of thereservoir - With such a configuration, the gas-liquid two-phase refrigerant flowing in from the
inflow passage inner wall surface 816, 812Gb of thereservoir - Further according to the present embodiment, the
inner wall surface 816, 812Gb of thereservoir inlet port 81 aD, 81 aE, 81 aF, 81 aG to the innerwall surface portion 816 aD, 816 aE, 816 aG, 811Gd of thereservoir inlet port 81 aD, 81 aE, 81 aF, 81 aG is shorter than the diameter d, d1 of thereservoir - With such a configuration, the incoming gas-liquid two-phase refrigerant is able to reliably hit the
inner wall surface 816, 811Gb of thereservoir - Further according to the present embodiment, a part of the
inner wall surface 122F of theinflow passage 12F is disposed so as to follow the tangent of theinner wall surface 816 of thereservoir 36F. - With such a configuration, the incoming gas-liquid two-phase refrigerant is able to reliably hit the
inner wall surface 816 of thereservoir 36F and then fall down. - The present embodiments have been described with reference to specific examples above. However, the present disclosure is not limited to these specific examples. Those skilled in the art appropriately design modifications to these specific examples, which are also included in the scope of the present disclosure as long as they have the features of the present disclosure. The elements, the arrangement, the conditions, the shape, etc. of the specific examples described above are not limited to those exemplified and can be appropriately modified. The combinations of elements included in each of the above described specific examples can be appropriately modified as long as no technical inconsistency occurs.
Claims (12)
1. A heat exchanger for a refrigeration cycle, comprising:
a heat exchanging portion that exchanges heat between a refrigerant passing through therein and air;
a reservoir 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 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 that allows the gas-phase refrigerant to flow out from the reservoir; and
a liquid-phase outflow passage that allows the liquid-phase refrigerant to flow out from the reservoir;
wherein
the inflow passage is connected so as to be in communication with an inlet port 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 of the reservoir disposed above the liquid surface of the liquid-phase refrigerant stored in the reservoir, the gas-phase outlet port being disposed so as to be connected to a compressor included in the refrigeration cycle, and
the liquid-phase outflow passage is connected so as to be in communication with a liquid-phase outlet port of the reservoir disposed below the liquid surface of the liquid-phase refrigerant stored in the reservoir.
2. The heat exchanger according to claim 1 , wherein
the reservoir includes a partition portion between the inlet port and the gas-phase outlet port.
3. The heat exchanger according to claim 2 , wherein
the partition portion is disposed such that at least a portion thereof faces the inlet port.
4. The heat exchanger according to claim 1 , wherein
a buffer portion is disposed between the inlet port and the liquid surface of the liquid-phase refrigerant.
5. The heat exchanger according to claim 4 , wherein
at least part of the buffer portion is arranged between the inlet port and the liquid-phase outlet port, and the buffer portion is disposed closer toward the liquid surface as compared to the inlet port.
6. The heat exchanger according to claim 5 , wherein
the reservoir includes a substantially cylindrical main body portion in which the liquid-phase refrigerant can be stored, and
an average distance from the buffer portion to an inner wall of the main body portion is equal to or less than one-third of a radius of the main body portion.
7. The heat exchanger according to claim 1 , wherein
the reservoir includes a substantially cylindrical main body portion in which the liquid-phase refrigerant can be stored, and
the main body portion is formed with a main reservoir space and an auxiliary reservoir space, the auxiliary reservoir space having a smaller liquid surface area than the main reservoir space.
8. The heat exchanger according to claim 1 , wherein
the inflow passage is disposed such that if a center line of the inflow passage is extended, the center line reaches an inner wall surface of the reservoir without passing through a center of the reservoir.
9. The heat exchanger according to claim 8 , wherein
the inflow passage is provided such that the gas-liquid two-phase refrigerant which flows through the inflow passage then flows in from the inlet port collides with the inner wall surface of the reservoir and then falls into the liquid-phase refrigerant stored in the reservoir.
10. The heat exchanger according to claim 8 ,
wherein a distance from the inlet port to an inner wall surface portion of the reservoir that faces the inlet port is shorter than a distance between the farthest portions of the inner wall surface of the reservoir.
11. The heat exchanger according to claim 10 , wherein
the inner wall surface of the reservoir has a substantially circular cross section, and
the distance from the inlet port to the inner wall surface portion of the reservoir that faces the inlet port is shorter than a diameter of the reservoir.
12. The heat exchanger according to claim 11 , wherein
a part of an inner wall surface of the inflow passage is disposed so as to follow the tangent of the inner wall surface of the reservoir.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016-078224 | 2016-04-08 | ||
JP2016078224 | 2016-04-08 | ||
JP2016234961A JP6631489B2 (en) | 2016-04-08 | 2016-12-02 | Heat exchanger |
JP2016-234961 | 2016-12-02 | ||
PCT/JP2017/013975 WO2017175724A1 (en) | 2016-04-08 | 2017-04-03 | Heat exchanger |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2017/013975 A-371-Of-International WO2017175724A1 (en) | 2016-04-08 | 2017-04-03 | Heat exchanger |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US17/098,487 Division US11656014B2 (en) | 2016-04-08 | 2020-11-16 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
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US20190128577A1 true US20190128577A1 (en) | 2019-05-02 |
Family
ID=60085769
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
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US16/091,138 Abandoned US20190128577A1 (en) | 2016-04-08 | 2017-04-03 | Heat exchanger |
US17/098,487 Active 2037-09-27 US11656014B2 (en) | 2016-04-08 | 2020-11-16 | Heat exchanger |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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US17/098,487 Active 2037-09-27 US11656014B2 (en) | 2016-04-08 | 2020-11-16 | Heat exchanger |
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US (2) | US20190128577A1 (en) |
JP (1) | JP6631489B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11280528B2 (en) * | 2017-08-03 | 2022-03-22 | Mitsubishi Electric Corporation | Heat exchanger, and refrigeration cycle apparatus |
CN115200268A (en) * | 2022-06-10 | 2022-10-18 | 智己汽车科技有限公司 | Heat exchange circulation system, air conditioner and vehicle |
US11555660B2 (en) * | 2017-08-03 | 2023-01-17 | Mitsubishi Electric Corporation | Refrigerant distributor, heat exchanger, and refrigeration cycle apparatus |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4187695A (en) * | 1978-11-07 | 1980-02-12 | Virginia Chemicals Inc. | Air-conditioning system having recirculating and flow-control means |
US4199960A (en) * | 1978-10-26 | 1980-04-29 | Parker-Hannifin Corporation | Accumulator for air conditioning systems |
US5787729A (en) * | 1997-06-04 | 1998-08-04 | Automotive Fluid Systems, Inc. | Accumulator deflector |
US6006532A (en) * | 1997-07-10 | 1999-12-28 | Denso Corporation | Refrigerant cycle system |
US20050081559A1 (en) * | 2003-10-20 | 2005-04-21 | Mcgregor Ian A.N. | Accumulator with pickup tube |
US7086248B2 (en) * | 2002-09-27 | 2006-08-08 | Denso Corporation | Ejector cycle device |
US7461519B2 (en) * | 2005-02-03 | 2008-12-09 | Halla Climate Control Canada, Inc. | Accumulator with deflector |
US20090241573A1 (en) * | 2008-03-27 | 2009-10-01 | Denso Corporation | Refrigerant cycle device |
JP2014149123A (en) * | 2013-02-01 | 2014-08-21 | Denso Corp | Refrigeration cycle device |
US10391839B2 (en) * | 2015-08-03 | 2019-08-27 | Denso Corporation | Refrigeration cycle device |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0648280Y2 (en) * | 1989-10-26 | 1994-12-12 | カルソニック株式会社 | Liquid tank for cooling cycle |
JP4032548B2 (en) | 1999-01-22 | 2008-01-16 | 株式会社デンソー | Receiver integrated refrigerant condenser |
JP4069567B2 (en) * | 1999-05-24 | 2008-04-02 | 株式会社デンソー | accumulator |
JP4151345B2 (en) * | 2002-08-09 | 2008-09-17 | 株式会社デンソー | Refrigeration cycle equipment |
JP4626586B2 (en) * | 2006-08-03 | 2011-02-09 | トヨタ紡織株式会社 | Gas-liquid separator |
JP5395358B2 (en) | 2008-01-23 | 2014-01-22 | 日冷工業株式会社 | A gas-liquid separator and a refrigeration apparatus including the gas-liquid separator. |
US8147575B2 (en) * | 2009-09-09 | 2012-04-03 | Ingersoll-Rand Company | Multi-stage oil separation system including a cyclonic separation stage |
JP2011152827A (en) * | 2010-01-26 | 2011-08-11 | Honda Motor Co Ltd | Cooling media accumulating structure of vehicle air conditioning system |
JP5803263B2 (en) * | 2011-05-18 | 2015-11-04 | 富士電機株式会社 | Gas-liquid separator |
WO2015128807A2 (en) | 2014-02-26 | 2015-09-03 | Denso Thermal Systems S.P.A. | Horizontal condenser with coolant accumulator |
JP6432339B2 (en) * | 2014-12-25 | 2018-12-05 | 株式会社デンソー | Refrigeration cycle equipment |
JP6614184B2 (en) * | 2016-04-08 | 2019-12-04 | 株式会社デンソー | Refrigeration cycle apparatus and heat exchanger |
JP6572931B2 (en) * | 2016-04-08 | 2019-09-11 | 株式会社デンソー | Heat exchanger |
-
2016
- 2016-12-02 JP JP2016234961A patent/JP6631489B2/en not_active Expired - Fee Related
-
2017
- 2017-04-03 US US16/091,138 patent/US20190128577A1/en not_active Abandoned
-
2020
- 2020-11-16 US US17/098,487 patent/US11656014B2/en active Active
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4199960A (en) * | 1978-10-26 | 1980-04-29 | Parker-Hannifin Corporation | Accumulator for air conditioning systems |
US4187695A (en) * | 1978-11-07 | 1980-02-12 | Virginia Chemicals Inc. | Air-conditioning system having recirculating and flow-control means |
US5787729A (en) * | 1997-06-04 | 1998-08-04 | Automotive Fluid Systems, Inc. | Accumulator deflector |
US6006532A (en) * | 1997-07-10 | 1999-12-28 | Denso Corporation | Refrigerant cycle system |
US7086248B2 (en) * | 2002-09-27 | 2006-08-08 | Denso Corporation | Ejector cycle device |
US20050081559A1 (en) * | 2003-10-20 | 2005-04-21 | Mcgregor Ian A.N. | Accumulator with pickup tube |
US7461519B2 (en) * | 2005-02-03 | 2008-12-09 | Halla Climate Control Canada, Inc. | Accumulator with deflector |
US20090241573A1 (en) * | 2008-03-27 | 2009-10-01 | Denso Corporation | Refrigerant cycle device |
JP2014149123A (en) * | 2013-02-01 | 2014-08-21 | Denso Corp | Refrigeration cycle device |
US10391839B2 (en) * | 2015-08-03 | 2019-08-27 | Denso Corporation | Refrigeration cycle device |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11280528B2 (en) * | 2017-08-03 | 2022-03-22 | Mitsubishi Electric Corporation | Heat exchanger, and refrigeration cycle apparatus |
US11555660B2 (en) * | 2017-08-03 | 2023-01-17 | Mitsubishi Electric Corporation | Refrigerant distributor, heat exchanger, and refrigeration cycle apparatus |
CN115200268A (en) * | 2022-06-10 | 2022-10-18 | 智己汽车科技有限公司 | Heat exchange circulation system, air conditioner and vehicle |
Also Published As
Publication number | Publication date |
---|---|
JP6631489B2 (en) | 2020-01-15 |
JP2017190940A (en) | 2017-10-19 |
US11656014B2 (en) | 2023-05-23 |
US20210063067A1 (en) | 2021-03-04 |
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