WO2012160426A1 - Système de refroidissement - Google Patents

Système de refroidissement Download PDF

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Publication number
WO2012160426A1
WO2012160426A1 PCT/IB2012/000942 IB2012000942W WO2012160426A1 WO 2012160426 A1 WO2012160426 A1 WO 2012160426A1 IB 2012000942 W IB2012000942 W IB 2012000942W WO 2012160426 A1 WO2012160426 A1 WO 2012160426A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
line
heat exchanger
cooling
heat
Prior art date
Application number
PCT/IB2012/000942
Other languages
English (en)
Inventor
Yoshiaki Kawakami
Yuki JOJIMA
Eizo Takahashi
Kousuke Sato
Kazuhide Uchida
Yuichi Ohno
Original Assignee
Toyota Jidosha Kabushiki Kaisha
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Jidosha Kabushiki Kaisha filed Critical Toyota Jidosha Kabushiki Kaisha
Publication of WO2012160426A1 publication Critical patent/WO2012160426A1/fr

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Classifications

    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00907—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant changes and an evaporator becomes condenser
    • 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
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • 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
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/61—Types of temperature control
    • H01M10/613—Cooling or keeping cold
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/66—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells
    • H01M10/663—Heat-exchange relationships between the cells and other systems, e.g. central heating systems or fuel cells the system being an air-conditioner or an engine
    • 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
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00935—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising four way valves for controlling the fluid direction
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
    • 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
    • B60H2001/3286—Constructional features
    • B60H2001/3298—Ejector-type refrigerant circuits
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries

Definitions

  • the invention relates to a cooling system and, more particularly, to a cooling system that utilizes a vapor compression refrigeration cycle to cool a charger used to charge a storage battery.
  • Japanese Patent Application Publication No. 9-290622 (.TP 9-290622 A) describes a technique for effectively improving heating performance at a low outside air temperature while suppressing an increase in power consumption by causing gas injection refrigerant to absorb heat waste recovered from heat generating components mounted on a vehicle.
  • Japanese Patent Application Publication No. 11 -223406 (JP 11-223406 A) describes a configuration that heat waste from a heat generating element, such as a power transistor, is absorbed by refrigerant in a heat pump cycle.
  • JP 2007-69733 (JP 2007-69733 A) describes a system in which a heat exchanger that exchanges heat with air-conditioning air and a heat exchanger that exchanges heat with a heat generating element are arranged in parallel with each other in a refrigerant line routed from an expansion valve to a compressor and refrigerant for an air conditioner is utilized to cool the heat generating element.
  • JP 2005-90862 describes a cooling system in which a heat generating element cooling unit for cooling a heat generating element is provided in a bypass line that bypasses the decompressor, evaporator and compressor of an air-conditioning refrigeration cycle.
  • Japanese Patent Application Publication No. 2001 -309506 describes a cooling system that circulates refrigerant of a vehicle air-conditioning refrigeration cycle through a cooling member of an inverter circuit portion that executes drive control over a vehicle drive motor and, when cooling air-conditioning air stream is not required, cooling of air-conditioning air stream by an evaporator of the vehicle air-conditioning refrigeration cycle is suppressed.
  • refrigerant at intermediate pressure is evaporated with heat waste from the heat generating components, and is then gas-injected into the compressor to thereby suppress the compressing power of the compressor.
  • gas-injected refrigerant is directly introduced into the compressor, so the amount of refrigerant supplied to an indoor heat exchanger reduces during cooling operation and, as a result, cooling performance decreases. Cooling perfomiance may be ensured if the flow rate of refrigerant is increased; however, the power consumption of the compressor increases accordingly.
  • the invention provides a cooling system for a heat generating source, which is able to reduce the power consumption of a compressor while ensuring air-conditioning performance and cooling performance for cooling the heat generating source.
  • An aspect of the invention provides a cooling system that cools a heat generating source.
  • the cooling system includes: a compressor that compresses and circulates refrigerant in the cooling system; a first heat exchanger that exchanges heat between the refrigerant and outside air; a first decompressor that reduces a pressure of the refrigerant; a second heat exchanger that exchanges heat between the refrigerant and air-conditioning air; a four-way valve that switches between flow of the refrigerant from the compressor toward the first heat exchanger and flow of the refrigerant from the compressor toward the second heat exchanger; a first line that is a path of the refrigerant, connected between the first heat exchanger and the decompressor; a second line that is a path of the refrigerant, connected between the first heat exchanger and the first decompressor in parallel with the first line; a cooling portion that is provided in the second line and that uses the refrigerant to cool the heat generating source; a first communication line that provides
  • the cooling system may further include a third heat exchanger that is provided in a path of the refrigerant flowing between the cooling portion and the first decompressor, and that exchanges heat between the refrigerant and outside air.
  • the cooling system may further include a second decompressor that is provided in a path of the refrigerant flowing between the first heat exchanger and the cooling portion.
  • the cooling system may further include a gas-liquid separator that is arranged in the second line closer to the first heat exchanger than the cooling portion.
  • One end of the first communication line may be arranged in a gaseous phase of the gas- liquid separator.
  • the cooling system may further include a booster that increases a pressure of the refrigerant flowing from the cooling portion toward the first communication line.
  • the cooling system may further include a first three-way valve that is provided at a portion at which the second communication line meets in a middle of the second line, and that switches between flow and interruption of the refrigerant among upstream and downstream sides of the second line and the second communication line.
  • the cooling system may further include a third decompressor that is arranged in the second communication line.
  • the cooling system may further include a second three-way valve that is provided at a portion at which the first communication line meets in a middle of the second line, and that switches between flow and interruption of the refrigerant among upstream and downstream sides of the second line and the first communication line.
  • the cooling system may further include a fourth decompressor that is arranged in the first communication line.
  • FIG. 1 is a schematic view that shows the configuration of a cooling system according to a first embodiment of the invention
  • FIG. 2 is a Mollier chart that shows the state of refrigerant during cooling operation of a vapor compression refrigeration cycle according to the first embodiment
  • FIG. 3 is a schematic view that shows the cooling system according to the first embodiment in a state where a four-way valve is switched;
  • FIG. 4 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle according to the first embodiment
  • FIG. 5 is a schematic view that shows the configuration of a cooling system according to a second embodiment of the invention.
  • FIG. 6 is a Mollier chart that shows the state of refrigerant during cooling operation of a vapor compression refrigeration cycle according to the second embodiment
  • FIG. 7 is a schematic view that shows the cooling system according to the second embodiment in a state where a four-way valve is switched;
  • FIG. 8 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle according to the second embodiment
  • FIG. 9 is a schematic view that shows the configuration of a cooling system according to a third embodiment of the invention.
  • FIG. 10 is a Mollier chart that shows the state of refrigerant during heating operation of a vapor compression refrigeration cycle according to the third embodiment
  • FIG. 1 1 is a schematic view that shows the configuration of a cooling system according to a fourth embodiment of the invention.
  • FIG. 12 is a schematic view that shows the cooling system according to the fourth embodiment in a state where a four-way valve is switched.
  • FIG. 13 is a Mollier chart that shows the state of refrigerant during heating operation of a vapor compression refrigeration cycle according to the fourth embodiment.
  • FIG. 1 is a schematic view that shows the configuration of a cooling system 1 according to a first embodiment.
  • the cooling system 1 includes a vapor compression refrigeration cycle 10.
  • the vapor compression refrigeration cycle 10 is, for example, mounted on a vehicle in order to cool or heat the cabin of the vehicle. Cooling using the vapor compression refrigeration cycle 10 is performed, for example, when a switch for cooling is turned on or when an automatic control mode in which the temperature in the cabin of the vehicle is automatically adjusted to a set temperature is selected and the temperature in the cabin is higher than the set temperature.
  • Heating using the vapor compression refrigeration cycle 1 0 is performed, for example, when a switch for heating is turned on or when the automatic control mode is selected and the temperature in the cabin is lower than the set temperature.
  • the vapor compression refrigeration cycle 10 includes a compressor 12, a heat exchanger 14 that serves as a first heat exchanger, an expansion valve 16 that is an example of a decompressor, and a heat exchanger 18 that serves as a second heat exchanger 18.
  • the vapor compression refrigeration cycle 10 further includes a four- way valve 13.
  • the four- way valve 13 is arranged so as to be able to switch between flow of refrigerant from the compressor 12 toward the heat exchanger 14 and flow of refrigerant from the compressor 12 toward the heat exchanger 18.
  • the compressor 12 is actuated by a motor or engine equipped for the vehicle as a power source, and adiabatically compresses refrigerant gas to obtain superheated refrigerant gas.
  • the compressor 12 introduces and compresses gaseous refrigerant flowing during operation of the vapor compression refrigeration cycle 10, and discharges high-temperature and high-pressure gaseous refrigerant.
  • the compressor 12 discharges refrigerant to circulate refrigerant in the vapor compression refrigeration cycle 10.
  • Each of the heat exchangers 14 and 18 includes a tube and fins.
  • the tube flows refrigerant.
  • the fins are used to exchange heat between refrigerant flowing through the tube and air around the heat exchanger 14 or 18.
  • Each of the heat exchangers 14 and 18 exchanges heat between refrigerant and air stream supplied by natural draft generated as the vehicle runs or air stream supplied by a fan.
  • the expansion valve 16 causes high-pressure liquid refrigerant to be sprayed through a small hole to expand into low-temperature and low-pressure atomized refrigerant.
  • the expansion valve 16 decompresses condensed refrigerant liquid into wet steam in a gas-liquid mixing state.
  • a decompressor for decompressing refrigerant liquid is not limited to the expansion valve 16 that carries out throttle expansion; instead, the decompressor may be a capillary tube.
  • the vapor compression refrigeration cycle 10 further includes refrigerant lines 21 to 26.
  • the refrigerant line 21 provides fluid communication between the compressor 12 and the four- way valve 13. Refrigerant flows from the compressor 12 toward the four-way valve 13 via the refrigerant line 21 .
  • the refrigerant line 22 provides fluid communication between the four-way valve 13 and the heat exchanger 14. Refrigerant flows from one of the four- way valve 13 and the heat exchanger 14 toward the other via the refrigerant line 22.
  • the refrigerant line 23 provides fluid communication between the heat exchanger 14 and the expansion valve 16. Refrigerant flows from one of the heat exchanger 14 and the expansion valve 16 toward the other via the refrigerant line 23.
  • the refrigerant line 24 provides fluid communication between the expansion valve 16 and the heat exchanger 18. Refrigerant flows from one of the expansion valve 16 and the heat exchanger 18 toward the other via the refrigerant line 24.
  • the refrigerant line 25 provides fluid communication between the heat exchanger 1 8 and the four-way valve 1 3. Refrigerant flows from one of the heat exchanger 18 and the four-way valve 13 toward the other via the refrigerant line 25.
  • the refrigerant line 26 provides fluid communication between the four-way valve 13 and the compressor 12. Refrigerant flows from the four- way valve 13 toward the compressor 12 via the refrigerant line 26.
  • the vapor compression refrigeration cycle 10 is formed such that the compressor 12, the heat exchanger 14, the expansion valve 16 and the heat exchanger 18 are coupled by the refrigerant lines 21 to 26.
  • refrigerant used in the vapor compression refrigeration cycle 10 may be, for example, carbon dioxide, hydrocarbon, such as propane and isobutane, ammonia, water, or the like.
  • a refrigerant line 23a which serves as a first line, and a second line are connected in parallel with each other in the path of refrigerant flowing between the heat exchanger 14 and the expansion valve 16.
  • the refrigerant line 23a forms part of the refrigerant line 23 that forms the path of refrigerant flowing between the heat exchanger 14 and the expansion valve 16.
  • a cooling portion 30 is provided in the second line.
  • the cooling portion 30 is provided in the path of refrigerant flowing between the heat exchanger 14 and the expansion valve 16.
  • the cooling portion 30 includes a hybrid vehicle (HV) device 3 1 and a cooling line 32.
  • the HV device 3 1 is an electrical device mounted on the vehicle.
  • the cooling line 32 is a line through which refrigerant flows.
  • the HV device 31 is an example of a heat generating source.
  • the path of refrigerant between the heat exchanger 14 and the expansion valve 16 branches off, and part of refrigerant flows to the cooling portion 30.
  • refrigerant lines 33, 34, 35 and 36 are provided as a path for flowing refrigerant to the cooling line 32.
  • One end portion of the cooling line 32 is connected to the refrigerant line 34.
  • the other end portion of the cooling line 32 is connected to the refrigerant line 35.
  • the refrigerant line 33 and the refrigerant line 34 are in fluid communication with each other via a three-way valve 42.
  • the refrigerant line 35 and the refrigerant line 36 are in fluid communication with each other via a three-way valve 46.
  • Refrigerant flows from the refrigerant line 23 to the cooling line 32 via one of the pair of refrigerant lines 33 and 34 and the pair of refrigerant lines 35 and 36.
  • Refrigerant flows through the cooling line 32 and exchanges heat with the HV device 3 1 , and then returns to the refrigerant line 23 via the other one of the pair of refrigerant lines 33 and 34 and the pair of refrigerant lines 35 and 36.
  • the second line connected in parallel with the refrigerant line 23a includes the refrigerant lines 33 and 34 closer to the heat exchanger 14 than the cooling portion 30, the cooling line 32 included in the cooling portion 30, and the refrigerant lines 35 and 36 closer to the expansion valve 16 than the cooling portion 30.
  • Refrigerant flows between the refrigerant line 23 and the cooling portion 30 via the refrigerant lines 33 and 34.
  • Refrigerant flows between the cooling portion 30 and the refrigerant line 23 via the refrigerant lines 35 and 36.
  • Refrigerant flowing between the heat exchanger 14 and the expansion valve 16 flows via the cooling line 32.
  • the cooling portion 30 is configured to be able to exchange heat between the HV device 3 1 and refrigerant because of the cooling line 32.
  • the cooling portion 30, for example, has the cooling line 32 that is formed such that the outer peripheral surface of the cooling line 32 is in direct contact with the casing of the HV device 3 1 .
  • the cooling line 32 has a portion adjacent to the casing of the HV device 31. At that portion, heat is exchangeable between refrigerant, flowing through the cooling line 32, and the HV device 3 1.
  • the HV device 3 1 is directly connected to the outer peripheral surface of the cooling line 32 that fonns part of the path of refrigerant flowing between the heat exchanger 14 and expansion valve 16 of the vapor compression refrigeration cycle 10, and is cooled.
  • the HV device 31 is arranged on the outside of the cooling line 32, so the HV device 31 does not interfere with flow of refrigerant flowing inside the cooling line 32. Therefore, the pressure loss of the vapor compression refrigeration cycle 10 does not increase, so the HV device 31 may be cooled without increasing the power of the compressor 12.
  • the cooling portion 30 may include a selected known heat pipe that is interposed between the HV device 3 1 and the cooling line 32.
  • the HV device 3 1 is connected to the outer peripheral surface of the cooling line 32 via the heat pipe, and heat is transferred from the HV device 3 1 to the cooling line 32 via the heat pipe to thereby cool the HV device 3 1 .
  • the HV device 3 1 serves as a heating portion for heating the heat pipe
  • the cooling line 32 serves as a cooling portion for cooling the heat pipe to thereby increase the heat-transfer efficiency between the cooling line 32 and the HV device 31 , so the cooling efficiency of the HV device 3 1 may be improved.
  • a Wick heat pipe may be used.
  • Heat may be reliably transferred from the HV device 3 1 to the cooling line 32 by the heat pipe, so there may be a distance between the HV device 3 1 and the cooling line 32, and complex arrangement of the cooling line 32 is not required to bring the cooling line 32 into contact with the HV device 3 1. As a result, it is possible to improve the flexibility of arrangement of the HV device 31.
  • the refrigerant lines 33 to 36 and the cooling line 32 that form the path of refrigerant that passes through the cooling portion 30 and the refrigerant line 23a that is the path of refrigerant that does not pass through the cooling portion 30 are provided in parallel with each other as the paths through which refrigerant flows between the heat exchanger 14 and the expansion valve 16.
  • a cooling system for cooling the HV device 31 including the refrigerant lines 33 to 36 and the cooling line 32, is connected in parallel with the refrigerant line 23a.
  • the path of refrigerant flowing between the heat exchanger 14 and the expansion valve 16 without passing though the cooling portion 30 and the path of refrigerant flowing via the cooling portion 30 are provided in parallel with each other, and only part of refrigerant is caused to flow to the refrigerant lines 33 to 36. By so doing, only part of refrigerant flowing between the heat exchanger 14 and the expansion valve 16 flows to the cooling portion 30.
  • Refrigerant in an amount required to cool the HV device 3 1 in the cooling portion 30 is caused to flow to the refrigerant lines 33 to 36, and not the entire refrigerant flows to the cooling portion 30.
  • the HV device 3 1 is appropriately cooled, and it is possible to prevent excessive cooling of the HV device 31 .
  • the HV device 31 includes an electrical device that exchanges electric power to generate heat.
  • the electrical device includes at least any one of, for example, an inverter used to convert direct-current power to alternating-current power, a motor generator that is a rotating electrical machine, a battery that is an electrical storage device, a converter used to step up the voltage of the battery and a DC/DC converter used to step down the voltage of the battery.
  • the battery is a secondary battery, such as a lithium ion battery and a nickel metal hydride battery. A capacitor may be used instead of the battery.
  • the heat exchanger 18 is arranged inside a duct 90 through which air flows.
  • the heat exchanger 18 exchanges heat between refrigerant and air-conditioning air flowing through the duct 90 to adjust the temperature of air-conditioning air.
  • the duct 90 has a duct inlet 91 and a duct outlet 92.
  • the duct inlet 91 is an inlet through which air-conditioning air flows into the duct 90.
  • the duct outlet 92 is an outlet through which air-conditioning air flows out from the duct 90.
  • a fan 93 is arranged near the duct inlet 91 inside the duct 90.
  • Air flowing into the duct 90 may be outside air or may be air in the cabin of the vehicle.
  • the arrow 95 in FIG. 1 indicates flow of air-conditioning air that flows via the heat exchanger 1 8 and exchanges heat with refrigerant in the vapor compression refrigeration cycle 10.
  • air-conditioning air is cooled in the heat exchanger 18, and refrigerant receives heat transferred from air-conditioning air to be heated.
  • heating operation air-conditioning air is heated in the heat exchanger 18, and refrigerant transfers heat to air-conditioning air to be cooled.
  • the arrow 96 indicates flow of air-conditioning air that is adjusted in temperature by the heat exchanger 18 and that flows out from the duct 90 via the duct outlet 92.
  • refrigerant flows in the vapor compression refrigeration cycle 10 so as to sequentially pass through points A, B, C, D and E shown in FIG. 1 , and refrigerant circulates among the compressor 12, the heat exchanger 14, the expansion valve 16 and the heat exchanger 18.
  • Refrigerant passes through a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 14, the expansion valve 16 and the heat exchanger 18 by the refrigerant lines 21 to 26 to circulate in the vapor compression refrigeration cycle 10.
  • FIG. 2 is a Mollier chart that shows the state of refrigerant during cooling operation of the vapor compression refrigeration cycle 10 according to the first embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 2 shows the thermodynamic state of refrigerant at points (that is, points A, B, C, D and E) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 into the refrigerant line 23 via the heat exchanger 14, cools the HV device 3 1 , returns to the refrigerant line 23, and returns to the compressor 12 via the expansion valve 16 and the heat exchanger 1 8.
  • refrigerant (point A) in a superheated steam state introduced into the compressor 12, is adiabatically compressed in the compressor 12 along a constant specific entropy line.
  • the pressure and temperature of refrigerant increase as the refrigerant is compressed, the refrigerant becomes high-temperature and high-pressure superheated steam having a high degree of superheat (point B), and then the refrigerant flows to the heat exchanger 14.
  • High-pressure refrigerant steam flowing into the heat exchanger 14 exchanges heat with outside air in the heat exchanger 14 to be cooled.
  • Refrigerant becomes dry saturated steam from superheated steam with a constant pressure, releases latent heat of condensation to gradually liquefy into wet steam in a gas-liquid mixing state, becomes saturated liquid as the entire refrigerant condenses, and further releases sensible heat to become supercooled liquid (point C).
  • the heat exchanger 14 causes superheated refrigerant gas. compressed in the compressor 12, to release heat to an external medium with a constant pressure and to become refrigerant liquid.
  • Gaseous refrigerant discharged from the compressor 12 releases heat to the surroundings to be cooled in the heat exchanger 14 to thereby condense (liquefy). Owing to heat exchange in the heat exchanger 14, the temperature of refrigerant decreases, and refrigerant liquefies.
  • High-pressure liquid refrigerant liquefied in the heat exchanger 14 flows to the cooling portion 30 via the refrigerant line 33, the three-way valve 42 and the refrigerant line 34 sequentially, and cools the HV device 3 1.
  • a degree of supercooling of refrigerant reduces. That is, the temperature of refrigerant in a supercooled liquid state increases to approach the saturation temperature of liquid refrigerant as the refrigerant receives sensible heat from the HV device 31 , and then the refrigerant is heated to a temperature slightly lower than the saturation temperature (point D).
  • refrigerant returns to the refrigerant line 23 via the refrigerant line 35, the three-way valve 46 and the refrigerant line 36 sequentially, and flows into the expansion valve 16 via the refrigerant line 23.
  • Refrigerant in a supercooled liquid state is throttle-expanded as it passes through the expansion valve 16. the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to become low-temperature and low-pressure wet steam in a gas-liquid mixing state (point E).
  • Refrigerant in a wet steam state from the expansion valve 16 flows into the heat exchanger 18 via the refrigerant line 24.
  • Refrigerant in a wet steam state flows into the tube of the heat exchanger 18.
  • the refrigerant absorbs heat of air-conditioning air as latent heat of vaporization via the fins to evaporate with a constant pressure.
  • point A the refrigerant steam further increases in temperature by sensible heat to become superheated steam (point A).
  • Refrigerant absorbs heat from the surroundings in the heat exchanger 18 to be heated.
  • Vaporized refrigerant flows into the four-way valve 13 via the refrigerant line 25, and is further introduced into the compressor 12 via the refrigerant line 26.
  • the compressor 12 compresses refrigerant flowing from the heat exchanger 18. Refrigerant continuously repeats changes among the compressed state, the condensed state, the throttle-expanded state and the evaporated state in accordance with the above described cycle.
  • atomized refrigerant flowing inside the heat exchanger 18 vaporizes to absorb heat of ambient air introduced so as to contact with the heat exchanger 18.
  • the heat exchanger 18 uses low-temperature and low-pressure refrigerant throttle-expanded and decompressed by the expansion valve 16 to absorb heat of vaporization, required at the time when wet steam of refrigerant evaporates into refrigerant gas, from air-conditioning air flowing to the cabin of the vehicle to thereby cool the cabin of the vehicle.
  • Air-conditioning air of which heat is absorbed by the heat exchanger 1 8 to decrease its temperature flows into the cabin of the vehicle to cool the cabin of the vehicle.
  • refrigerant absorbs heat of vaporization from air-conditioning air in the heat exchanger 18 to thereby cool the cabin.
  • high-pressure liquid refrigerant from the heat exchanger 14 flows to the cooling portion 30 and exchanges heat with the HV device 3 1 to thereby cool the HV device 31 .
  • the cooling system 1 cools the HV device 31. which is the heat generating source mounted on the vehicle,' by utilizing the vapor compressio refrigeration cycle 10 for air-conditioning the cabin of the vehicle.
  • the temperature required to cool the HV device 31 is desirably at least lower than the upper limit of a target temperature range of the HV device 3 1.
  • the cooling system 1 includes a flow regulating valve 5 1 .
  • the flow regulating valve 51 is arranged in the refrigerant line 23a that forms part of the refrigerant line 23 between the heat exchanger 14 and the expansion valve 16.
  • the flow regulating valve 51 changes its valve opening degree to increase or reduce a pressure loss of refrigerant flowing in the refrigerant line 23a to thereby selectively adjust the flow rate of refrigerant flowing in the refrigerant line 23a and the flow rate of refrigerant flowing in the refrigerant lines 33 to 36 and the cooling line 32.
  • the flow regulating valve 5 1 As the flow regulating valve 5 1 is fully closed to set the valve opening degree at 0%, the entire amount of refrigerant flowing between the heat exchanger 14 and the expansion valve 16 flows into the refrigerant lines 33 to 36 and the cooling line 32.
  • the valve opening degree of the flow regulating valve 51 When the valve opening degree of the flow regulating valve 51 is increased, the flow rate of refrigerant flowing via the refrigerant line 23a increases and the flow rate of refrigerant that flows via the refrigerant lines 33 to 36 and the cooling line 32 to cool the HV device 31 reduces within refrigerant that flows between the heat exchanger 14 and the expansion valve 16.
  • valve opening degree of the flow regulating valve 51 As the valve opening degree of the flow regulating valve 51 is increased, the flow rate of refrigerant that cools the HV device 3 1 reduces, so cooling performance for cooling the HV device 31 decreases. As the valve opening degree of the flow regulating valve 51 reduces, the flow rate of refrigerant that cools the HV device 31 increases, so cooling performance for cooling the HV device 3 1 improves.
  • the flow regulating valve 51 is used to make it possible to optimally adjust the amount of refrigerant flowing to the cooling portion 30, so it is possible to reliably prevent excessive cooling of the HV device 3 1 , and, in addition, it is possible to reliably reduce pressure loss associated with flow of refrigerant in the refrigerant lines 33 to 36 and the cooling line 32 and the power consumption of the compressor 12 for circulating refrigerant.
  • the cooling system 1 includes a refrigerant line 41 that serves as a first communication line.
  • One end of the refrigerant line 41 is connected to the refrigerant line 22 that is the path of refrigerant between the compressor 12 and the heat exchanger 14. Because the refrigerant line 41 is connected to the refrigerant line 22, the refrigerant line 22 is divided into a refrigerant line 22a closer to the four-way valve 13 than the connection portion betwee the refrigerant line 22 and the refrigerant line 41 and a refrigerant line 22b closer to the heat exchanger 14 than the connection portion.
  • the other end of the refrigerant line 41 is connected to the three-way valve 42.
  • the refrigerant line 41 is connected via the three-way valve 42 to the refrigerant lines 33 and 34 that are the path of refrigerant closer to the heat exchanger 14 than the cooling portion 30 within the second line that flows refrigerant to the cooling portion 30.
  • the refrigerant line 41 provides fluid communication between the refrigerant line 22 and the refrigerant lines 33 and 34.
  • An expansion valve 47 is provided in the refrigerant line 41.
  • the expansion valve 47 is arranged in the first communication line.
  • the cooling system 1 includes refrigerant lines 43 and 45 and an expansion valve 44, which constitute a second communication line.
  • the refrigerant line 43 and the refrigerant line 45 are in fluid communication with each other via the expansion valve 44.
  • the expansion valve 44 that serves as another decompressor different from the decompressor (expansion valve 16), as well as the expansion valve 16, throttle-expands refrigerant, and decreases the temperature and pressure of refrigerant without varying the specific enthalpy of the refrigerant.
  • the expansion valve 44 is arranged in the second communication line.
  • One end of the refrigerant line 43 is connected to the expansion valve 44, and the other end is connected to the refrigerant line 24 that is the path of refrigerant between the expansion valve 16 and the heat exchanger 18. Because the refrigerant line 43 is connected to the refrigerant line 24, the refrigerant line 24 is divided into a refrigerant line 24a closer to the expansion valve 16 than the connection portion between the refrigerant line 24 and the refrigerant line 43 and a refrigerant line 24b closer to the heat exchanger 1 8 than the connection portion.
  • One end of the refrigerant line 45 is connected to the expansion valve 44, and the other end is connected to the three-way valve 46.
  • the refrigerant line 45 is connected via the three-way valve 46 to the refrigerant lines 35 and 36 that are the paths of refrigerant closer to the expansion valve 16 than the cooling portion 30 within the second line that flows refrigerant to the cooling portion 30.
  • the second communication line that includes the refrigerant lines 43 and 45 and the expansion valve 44 provides fluid communication between the refrigerant line 24 and the refrigerant lines 35 and 36.
  • FIG. 3 is a schematic view that shows the cooling system 1 in a state where the four- way valve 13 is switched.
  • the four-way valve 1 3 is rotated by 90° to switch the path along which refrigerant flowing into the four- way valve 13 via the outlet of the compressor 12 flows out from the four-way valve 13.
  • refrigerant compressed in the compressor 12 flows from the compressor 12 toward the heat exchanger 14.
  • refrigerant compressed in the compressor 12 flows from the compressor 12 toward the heat exchanger 18.
  • the three-way valve 42 that serves as a first valve is set so as to provide fluid communication between the refrigerant line 33 and the refrigerant line 34 and so as to interrupt fluid communication between the refrigerant line 41 and the refrigerant lines 33 and 34.
  • the three-way valve 46 that serves as a second valve is set so as to provide fluid communication between the refrigerant line 35 and the refrigerant line 36 and so as to interrupt fluid communication between the refrigerant line 45 and the refrigerant lines 35 and 36.
  • the three-way valve 42 prohibits flow of refrigerant between the refrigerant lines 33 and 34, included in the second line that is the path of refrigerant flowing to the cooling portion 30, and the refrigerant line 41 that serves as the first communication line.
  • the three-way valve 46 prohibits flow of refrigerant between the refrigerant lines 35 and 36 included in the second line and the refrigerant lines 43 and 45 included in the second communication line.
  • the three-way valve 42 is set so as to provide fluid communication between the refrigerant line 34 and the refrigerant line 41 and so as to interrupt fluid communication between the refrigerant line 33 and the refrigerant lines 34 and 41 .
  • the three-way valve 46 is switched so as to provide fluid communication between the refrigerant line 35 and the refrigerant line 45 and so as to interrupt fluid communication between the refrigerant line 36 and the refrigerant lines 35 and 45.
  • the three-way valve 42 allows flow of refrigerant between the refrigerant line 34 and the refrigerant line 41.
  • the three-way valve 46 allows flow of refrigerant between the refrigerant line 35 and the refrigerant lines 43 and 45.
  • refrigerant that has been adiabatically compressed in the compressor 12 and that has exchanged heat with air-conditioning air in the heat exchanger 18 flows from the refrigerant line 24b into two branching lines, that is, the refrigerant line 24a and the refrigerant line 43.
  • Refrigerant flowing into the refrigerant line 24a passes through the expansion valve 16, flows through the refrigerant line 23, and reaches the refrigerant line 22b via the heat exchanger 14.
  • Refrigerant flowing into the refrigerant line 43 passes through the expansion valve 44. flows through the refrigerant lines 45 and 35, flows through the refrigerant line 34 via the cooling portion 30, and reaches the refrigerant line 41 via the three-way valve 42.
  • Refrigerant flowing through the refrigerant line 22b and refrigerant flowing through the refrigerant line 41 meet at the connection portion between the refrigerant lines 22 and 41 , and flows to the refrigerant line 22a.
  • refrigerant flows in the vapor compression refrigeration cycle 10 so as to sequentially pass through points A, B, E, D, C and J shown in FIG. 3 to circulate through the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30, and refrigerant flows so as to sequentially pass through points A, B, E, F and G shown in FIG. 3 to circulate through the compressor 12, the heat exchanger 18, the expansion valve 16 and the heat exchanger 14.
  • Refrigerant passes through a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30 and a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 18, the expansion valve 16 and the heat exchanger 14, thus circulating in the vapor compression refrigeration cycle 10.
  • FIG. 4 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle 10 according to the first embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 4 shows the thermodynamic state of refrigerant at points (that is, points A, B, E.
  • FIG. 4 also shows the thermodynamic state of refrigerant at points (that is, points A, B, E, F and G) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 via the heat exchanger 18, the expansion valve 16 and the heat exchanger 14 sequentially and returns to the compressor 1 2.
  • refrigerant in a superheated steam state (point A), introduced into the compressor 12, is adiabatically compressed in the compressor 12 along a constant specific entropy line. As refrigerant is compressed, the refrigerant increases in pressure and temperature into high-temperature and high-pressure superheated steam having a high degree of superheat (point B), and then the refrigerant flows to the heat exchanger 18.
  • High-pressure refrigerant steam in the heat exchanger 18 is cooled in the heat exchanger 18, becomes dry saturated steam from superheated steam with a constant pressure, releases latent heat of condensation to gradually liquefy into wet steam in a gas-liquid mixing state, becomes saturated liquid as the entire refrigerant condenses, and further releases sensible heat to become supercooled liquid (point E).
  • the heat exchanger 18 causes superheated refrigerant gas, compressed in the compressor 12, to release heat to an external medium with a constant pressure to become refrigerant liquid. Gaseous refrigerant discharged from the compressor 12 releases heat to the surroundings to be cooled in the heat exchanger 18 to thereby condense (liquefy). Owing to heat exchange in the heat exchanger 1 8, the temperature of refrigerant decreases, and refrigerant liquefies. Refrigerant releases heat to the surroundings in the heat exchanger 18 to be cooled.
  • High-pressure liquid refrigerant liquefied in the heat exchanger 18 branches off from the refrigerant line 24b to the refrigerant line 24a and to the refrigerant line 43. Part of liquid refrigerant flowing to the refrigerant line 24a flows into the expansion valve 16 via the refrigerant line 24a.
  • refrigerant in a supercooled liquid state is throttle-expanded, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to become low-temperature and low-pressure wet steam in a gas-liquid mixing state (point F).
  • Refrigerant of which the temperature is decreased in the expansion valve 16 flows into the heat exchanger 14 via the refrigerant line 23.
  • Refrigerant in a wet steam state flows into the tube of the heat exchanger 14.
  • the refrigerant absorbs heat of outside air via the fins as latent heat of vaporization to be heated, evaporates with a constant pressure, and the dryness of the refrigerant increases.
  • the temperature of refrigerant steam further increases by sensible heat to become superheated steam (point G).
  • Refrigerant in a wet steam state flowing from the cooling portion 30 through the refrigerant line 34, flows into the expansion valve 47 via the refrigerant line 41 .
  • refrigerant is throttle-expanded, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged (point J).
  • the pressure of refrigerant that has passed through the expansion valve 47 is equal to the pressure of refrigerant that flows without passing through the cooling portion 30 after the pressure is decreased by passing through the expansion valve 16.
  • Refrigerant in a wet steam state flowing through the refrigerant line 41 after passing tlirough the expansion valve 47, is equal in pressure to refrigerant in a superheated steam state, flowing through the refrigerant line 22b via the heat exchanger 14. Therefore, refrigerant flowing through the refrigerant line 41 and refrigerant flowing through the refrigerant line 22b both flow into the refrigerant line 22a and are mixed.
  • the mixed refrigerant has a pressure equal to the pressures at points J and G shown in FIG. 4.
  • the specific enthalpy of the mixed refrigerant is determined depending on the ratio of the specific enthalpies and the ratio of the flow rates of refrigerants flowing through the respective refrigerant lines 22b and 41 . For example, when the flow rate of refrigerant flowing through the refrigerant line 22b is equal to the flow rate of refrigerant flowing tlirough the refrigerant line 41 , the mixed refrigerant has the middle specific enthalpy (point A) between the specific enthalpy at point J and the specific enthalpy at point G.
  • Refrigerant flowing tlirough the refrigerant line 22a is equal in pressure to refrigerant flowing through the refrigerant lines 22b and 41 , and has a specific enthalpy smaller than or equal to that of refrigerant flowing through the refrigerant line 22b and larger than or equal to that of refrigerant flowing tlirough the refrigerant line 41.
  • refrigerant is introduced into the compressor 12 via the four- way valve 13 and the refrigerant line 26.
  • the compressor 12 compresses refrigerant flowing from the refrigerant line 26.
  • Refrigerant continuously repeats changes among the compressed state, the condensed state ⁇ the throttle-expanded state and the evaporated state in accordance with the above described cycle.
  • refrigerant steam flowing inside the heat exchanger 18 condenses to release heat to ambient air introduced so as to contact with the heat exchanger 18.
  • the heat exchanger 18 uses high-temperature and high-pressure refrigerant adiabatically compressed in the compressor 12 to release heat of condensation, required at the time when refrigerant gas condenses into wet steam of refrigerant, to air-conditioning air flowing to the cabin of the vehicle to thereby heat the cabin of the vehicle.
  • Air-conditioning air that receives heat from the heat exchanger 18 to increase its temperature flows into the cabin of the vehicle to thereby heat the cabin of the vehicle.
  • the cooling system 1 includes the vapor compression refrigeration cycle 10 that is provided in order to exchange heat with air-conditioning air in the heat exchanger 18 to thereby air-condition the cabin of the vehicle.
  • the single heat exchanger 18 is used to be able to appropriately adjust the temperature of air-conditioning air flowing into the cabin of the vehicle during both cooling operation and heating operation. It is not required to arrange two heat exchangers that exchange heat with air-conditioning air, so the cost of the cooling system 1 may be reduced, and the size of the cooling system 1 may be reduced.
  • refrigerant flows to the cooling portion 30, and exchanges heat with the HV device 3 1 to cool the HV device 3 1.
  • the cooling system 1 cools the ' HV device 3 1 , which is the heat generating source mounted on the vehicle, by utilizing the vapor compression refrigeration cycle 10 for air-conditioning the cabin of the vehicle.
  • the vapor compression refrigeration cycle 10 that is provided in order to exchange heat with air-conditioning air in the heat exchanger 18 to air-condition the cabin of the vehicle is utilized to cool the HV device 31 .
  • components required for the cooling system 1 to cool the HV device 31 may be reduced to make it possible to simplify the system configuration, so the manufacturing cost of the cooling system 1 may be reduced.
  • it is not necessary to operate a power source, such as a pump and a cooling fan, in order to cool the HV device 31 and power consumption for operating the power source is not required.
  • refrigerant has a temperature and a pressure that are originally required to cool the cabin of the vehicle at the outlet of the expansion valve 16.
  • the heat radiation performance of the heat exchanger 14 is set so as to be able to sufficiently cool refrigerant.
  • refrigerant after passing through the expansion valve 16 is used to cool the HV device 31 , the cooling performance of air-conditioning air in the heat exchanger 18 reduces and the cooling performance for cooling the cabin decreases; however, in the cooling system 1 according to the present embodiment, refrigerant is sufficiently cooled into a supercooled state in the heat exchanger 14, and high-pressure refrigerant at the outlet of the heat exchanger 14 is used to cool the HV device 31 . Therefore, it is possible to cool the HV device 3 1 without any influence on the cooling performance for cooling air in the cabin.
  • the specification of the heat exchanger 14 (that is, the size or heat exchanging performance of the heat exchanger 14) is set such that the temperature of liquid refrigerant after passing through the heat exchanger 14 becomes lower than the temperature required to cool the cabin.
  • the specification of the heat exchanger 14 is set so as to have the amount of heat radiation larger by the amount of heat that refrigerant presumably receives from the HV device 3 1 than that of the heat exchanger of a vapor compression refrigeration cycle when the HV device 3 1 is not cooled.
  • the cooling system 1 that includes the heat exchanger 14 having such specification is able to appropriately cool the HV device 31 without increasing the power of the compressor 12 while maintaining excellent cooling performance for cooling the cabin of the vehicle.
  • refrigerant absorbs heat from outside air in the heat exchanger 14 to be heated, and absorbs heat from the HV device 3 1 in the cooling portion 30 to be heated.
  • refrigerant absorbs heat from outside air in the heat exchanger 14 to be heated, and absorbs heat from the HV device 3 1 in the cooling portion 30 to be heated.
  • refrigerant that passes through the cooling portion 30 to cool the HV device 3 1 is allowed to directly flow to the refrigerant line 22 between the compressor 12 and the heat exchanger 14 via the refrigerant line 41 , and does not flow to the heat exchanger 14.
  • the suction pressure of the compressor 12 is increased.
  • the broken line shown in FIG. 4 shows the thermodynamic state of refrigerant in the case where the refrigerant line 41 is not provided and the entire refrigerant flows to the heat exchanger 14.
  • the pressure of refrigerant at the inlet of the compressor 12 is increased.
  • FIG. 5 is a schematic view that shows the configuration of a cooling system 1 according to the second embodiment.
  • the cooling system 1 according to the second embodiment includes a heat exchanger 15 that serves as a third heat exchanger arranged in the path of refrigerant between the cooling portion 30 and the expansion valve 16.
  • the path of refrigerant between the heat exchanger 14 and the expansion valve 16 is divided into a refrigerant line 23 closer to the heat exchanger 14 than the heat exchanger 15 and a refrigerant line 27 closer to the expansion valve 16 than the heat exchanger 15.
  • the refrigerant line 23 is provided as the path of refrigerant that flows between the heat exchanger 14 and the heat exchanger 1 5.
  • the second line that is the cooling system for cooling the HV device 3 1 including the cooling line 32, is connected in parallel with the refrigerant line 23a that forms part of the refrigerant line 23.
  • the cooling system 1 further includes a gas-liquid separator 60 that separates refrigerant in a wet steam state, mixedly containing saturated liquid and saturated steam, into gaseous refrigerant and liquid refrigerant.
  • the gas-liquid separator 60 separates refrigerant into liquid-state refrigerant liquid 62 and gaseous refrigerant steam 61 and temporarily stores them. Inside the gas-liquid separator 60, the refrigerant liquid 62 accumulates at the lower side and the refrigerant steam 61 accumulates at the upper side.
  • the path of refrigerant that flows between the heat exchanger 14 and the cooling portion 30 includes a refrigerant line 33 closer to the heat exchanger 14 and a refrigerant line 34 closer to the cooling portion 30.
  • One end portion of the refrigerant line 33 is arranged at the ceiling side in the gas-liquid separator 60, and is arranged in the refrigerant steam 61.
  • One end portion of the refrigerant line 34 is arranged at the bottom side in the gas-liquid separator 60, and is immersed in the refrigerant liquid 62.
  • refrigerant in a wet steam gas-liquid two-phase state flows out from the heat exchanger 14, and is supplied to the gas-liquid separator 60 via the refrigerant line 33.
  • the gas-liquid separator 60 separates refrigerant, flowing out from the heat exchanger 14 and flowing through the refrigerant line 33, into the refrigerant steam 61 that is gaseous refrigerant and the refrigerant liquid 62 that is liquid refrigerant.
  • the separated refrigerant liquid 62 flows out to the outside of the gas-liquid separator 60 via the refrigerant line 34.
  • the end portion of the refrigerant line 34 arranged in liquid inside the gas-liquid separator 60 forms an outlet port through which liquid refrigerant flows out from the gas-liquid separator 60. Only the refrigerant liquid 62 is delivered from the bottom side of the gas-liquid separator 60 to the outside of the gas-liquid separator 60 via the refrigerant line 34.
  • One end of the refrigerant line 41 is connected to the refrigerant line 22.
  • the other end of the refrigerant line 41 is arranged in the refrigerant steam 61 inside the gas-liquid separator 60, and is configured to be able to reliably flow only the refrigerant steam 61 from the gas-liquid separator 60 via the refrigerant line 41.
  • the expansion valve 47 is provided in the refrigerant line 41 .
  • the expansion valve 47 throttle-expands refrigerant to decrease the temperature and pressure of refrigerant.
  • a refrigerant line 48 provides fluid communication between the gas-liquid separator 60 and the refrigerant line 24a.
  • One end of the refrigerant line 48 is arranged inside the gas-liquid separator 60, and is immersed in the refrigerant liquid 62.
  • the other end of the refrigerant line 48 is connected to the refrigerant line 24a.
  • An on-off valve 49 is provided in the refrigerant line 48.
  • the on-off valve 49 allows or prohibits flow of refrigerant to the refrigerant line 48. During cooling operation, both the expansion valve 47 and the on-off valve 49 are closed.
  • the cooling system 1 further includes an on-off valve 37 and an expansion valve 38 in the path of refrigerant between the heat exchanger 14 and the cooling portion 30.
  • the on-off valve 37 provides or interrupts fluid communication in the refrigerant line 33.
  • the expansion valve 38 serves as a second decompressor different from the first decompressor (expansion valve 16).
  • the cooling system 1 further includes a refrigerant line 72 and an on-off valve 71.
  • the refrigerant line 72 is the path of refrigerant that bypasses the expansion valve 38.
  • the on-off valve 71 is provided in the refrigerant line 72, and switches flow of refrigerant to the refrigerant line 72.
  • the on-off valve 37 is open, and the on-off valve 71 is closed.
  • Refrigerant condensed in the heat exchanger 14 flows toward the cooling portion 30 via the refrigerant line 33, the gas-liquid separator 60, the refrigerant line 34 and the expansion valve 38.
  • Refrigerant that flows to the cooling portion 30 and that flows via the cooling line 32 takes heat from the HV device 3 1 to cool the HV device 3 1 .
  • the cooling portion 30 uses low-temperature and low-pressure refrigerant, flowing out from the gas-liquid separator 60 and decompressed by the expansion valve 38, to cool the HV device 31.
  • refrigerant flows in the vapor compression refrigeration cycle 10 so as to sequentially pass through points A, B, H, C, D, F and E shown in FIG. 5, and refrigerant circulates among the compressor 12, the heat exchangers 14 and 15, the expansion valve 16 and the heat exchanger 18.
  • Refrigerant passes through a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchangers 14 and 15, the expansion valve 16 and the heat exchanger 18 to circulate in the vapor compression refrigeration cycle 10.
  • FIG. 6 is a Mollier chart that shows the state of refrigerant during cooling operation of the vapor compression refrigeration cycle 10 according to the second embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 6 shows the thermodynamic state of refrigerant at points (that is, points A, B, H, C, D, F and E) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 into the cooling portion 30 via the heat exchanger 14 and the gas-liquid separator 60, cools the HV device 3 1 , and returns to the compressor 12 via the heat exchanger 15, the expansion valve 16 and the heat exchanger 18.
  • the vapor compression refrigeration cycle 10 according to the second embodiment is the same as that of the first embodiment except a line from the heat exchanger 14 to the expansion valve 16. That is, the state of refrigerant from point E to point B via point A in the Mollier chart shown in FIG. 2 is the same as the state of refrigerant from point E to point B via point A in the Mollier chart shown in FIG. 6. Therefore, the state of refrigerant from point B to point E, which is peculiar to the vapor compression refrigeration cycle 10 according to the second embodiment, will be described below.
  • refrigerant in a gas-liquid two-phase state is separated into gas and liquid, only the refrigerant liquid 62 that is liquid refrigerant flows out from the gas-liquid separator 60, flows to the refrigerant line 34 (point H), and flows into the expansion valve 38.
  • refrigerant in a saturated liquid state is throttle-expanded, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to thereby become wet steam mixedly containing saturated liquid and saturated steam (point C).
  • Refrigerant of which the temperature is decreased in the expansion valve 38 is supplied to the cooling line 32 of the cooling portion 30.
  • refrigerant flows into the heat exchanger 15.
  • Wet steam of refrigerant exchanges heat with outside air in the heat exchanger 15 to condense again, becomes saturated liquid as the entire refrigerant condenses, and further releases sensible heat to become supercooled liquid (point F).
  • refrigerant in a supercooled liquid state is throttle-expanded as it passes through the expansion valve 16, the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to become low-temperature and low-pressure wet steam in a gas-liquid mixing state (point E).
  • Liquid refrigerant flowing out from the gas-liquid separator 60 is refrigerant in a just saturated liquid state.
  • the performance of the heat exchanger 14 arranged on the upstream side of the gas-liquid separator 60 may be fully utilized to cool the HV device 3 1 , so it is possible to provide the cooling system 1 having improved cooling performance for cooling the HV device 31 .
  • the HV device 3 1 may be cooled by using refrigerant that is expanded in the expansion valve 38 to decrease its temperature, so it is possible to further efficiently cool the HV device 31 .
  • refrigerant that is expanded in the expansion valve 38 to decrease its temperature, so it is possible to further efficiently cool the HV device 31 .
  • the HV device 3 1 may be cooled by supplying refrigerant having a lower temperature, suitable for cooling the HV device 31. to the cooling portion 30.
  • the heat exchanger 14 is arranged between the compressor 12 and the expansion valve 16, and, during cooling operation, heat exchange corresponding to cooling operation and cooling the HV device 31 needs to be performed in the heat exchanger 14. Therefore, refrigerant is required to be further cooled from the state of saturated liquid in the heat exchanger 14 until refrigerant has a predetermined degree of supercooling.
  • refrigerant in a supercooled liquid state is cooled, the temperature of refrigerant approaches an atmospheric temperature, and the cooling efficiency of refrigerant decreases, so the capacity of the heat exchanger 14 needs to be increased.
  • the size of the heat exchanger 14 increases, and the flexibility of design relatively reduces as the vehicle-mounted cooling system 1.
  • the heat radiation performance of the heat exchanger 14 also reduces, and. as a result, the temperature of refrigerant at the outlet of the expansion valve 16 cannot be sufficiently decreased, so the cooling performance for cooling the cabin may be insufficient.
  • two-stage heat exchangers 14 and 15 are arranged between the compressor 12 and the expansion valve 16, and the cooling portion 30 that is the cooling system for cooling the HV device 31 is provided between the heat exchanger 14 and the heat exchanger 15.
  • refrigerant just needs to be cooled into a wet steam state.
  • Refrigerant in a saturated liquid state separated from refrigerant in a wet steam state into gas and liquid, passes through the expansion valve 38 to decrease in temperature and pressure, and exchanges heat with the HV device 31 in the cooling portion 30.
  • Refrigerant in a wet steam state which receives latent heat of vaporization from the HV device 31 to be partially vaporized, is cooled again in the heat exchanger 15.
  • Refrigerant changes in state at a constant temperature until the refrigerant in a wet steam state completely condenses into saturated liquid.
  • the heat exchanger 15 further cools refrigerant to a degree of supercooling required to cool the cabin of the vehicle.
  • a degree of supercooling of refrigerant does not need to be increased, and the capacity of each of the heat exchangers 14 and 1 5 may be reduced:
  • the cooling performance for cooling the cabin may be ensured, and the size of each of the heat exchangers 14 and 1 5 may be reduced, so it is possible to obtain the cooling system 1 that is reduced in size and that is advantageous in installation on the vehicle.
  • FIG. 7 is a schematic view that shows the cooling system 1 according to the second embodiment in a state where the four- way valve 13 is switched.
  • the four-way valve 1 3 is rotated by 90° to switch the path along which refrigerant flowing into the four- way valve 13 via the outlet of the compressor 12 flows out from the four-way valve 13, as in the case of the first embodiment.
  • the three-way valve 46 is switched so as to provide fluid communication between the refrigerant line 35 and the refrigerant line 45 and so as to interrupt fluid communication between the refrigerant line 36 and the refrigerant lines 35 and 45.
  • the on-off valve 37 is closed, the expansion valve 38 is fully closed (opening degree 0%), the opening degree of the expansion valve 47 is adjusted in order to appropriately throttle-expand refrigerant, and the on-off valves 49 and 71 are opened.
  • refrigerant that has exchanged heat with air-conditioning air in the heat exchanger 18 flows from the refrigerant line 24b into two branching lines, that is, the refrigerant line 24a and the refrigerant line 43.
  • Refrigerant flowing into the refrigerant line 24a passes through the expansion valve 16, flows through the refrigerant line 23, and reaches the refrigerant line 22b via the heat exchangers 15 and 14.
  • Refrigerant flowing into the refrigerant line 43 passes through the expansion valve 44, flows through the refrigerant lines 45 and 35, flows through the refrigerant lines 34 and 71 via the cooling portion 30, and flows into the gas-liquid separator 60.
  • the refrigerant steam 61 separated by the gas-liquid separator 60 into gas and liquid flows out from the gas-liquid separator 60 and flows through the refrigerant line 41.
  • Refrigerant flowing through the refrigerant line 22b and refrigerant flowing through the refrigerant line 41 meet at the connection portion between the refrigerant lines 22 and 41 , and flows to the refrigerant line 22a.
  • the refrigerant liquid 62 separated by the gas-liquid separator 60 into gas and liquid flows out from the gas-liquid separator 60, flows through the refrigerant line 48, and is supplied to the expansion valve 16 via the refrigerant line 24a.
  • refrigerant flows in the vapor compression refrigeration cycle 10 so as to sequentially pass through points A, B, E, D. H, K and J shown in FIG. 7 to circulate through the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30, and refrigerant flows so as to sequentially pass through points A, B, E. M. N, F. I and G shown in FIG. 7 to circulate through the compressor 12, the heat exchanger 1 8, the expansion valve 16 and the heat exchangers 15 and 14.
  • Refrigerant passes through a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30 and a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 18, the expansion valve 16 and the heat exchangers 15 and 14, thus circulating in the vapor compression refrigeration cycle 10.
  • a flow regulating valve 52 and an expansion valve 1 7 are arranged in the refrigerant line 24a between the connection point, between the refrigerant line 24a and the refrigerant line 43, and the connection point between the refrigerant line 24a and the refrigerant line 48.
  • the flow regulating valve 52 changes its valve opening degree to increase or reduce a pressure loss of refrigerant flowing through the refrigerant line 24a to thereby selectively adjust the flow rate of refrigerant flowing in the refrigerant line 24a and the flow rate of refrigerant flowing sequentially through the refrigerant lines 43, 45 and 35, the cooling line 32, the refrigerant lines 34 and 71 , the gas-liquid separator 60 and the refrigerant line 41.
  • the flow regulating valve 52 is used to make it possible to optimally adjust the amount of refrigerant flowing through the cooling portion 30, so it is possible to reliably prevent excessive cooling of the HV device 3 1 .
  • the flow rate of refrigerant passing through the expansion valve 16 and the flow rate of refrigerant passing through the expansion valve 44 may be adjusted where appropriate, so the suction pressure of the compressor 12 is set optimally to make it possible to reduce power consumption for adiabatically compressing refrigerant in the compressor 12 during heating operation.
  • FIG. 8 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle 10 according to the second embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 8 shows the thermodynamic state of refrigerant at points (that is, points A. B. E, D. H.
  • FIG. 8 also shows the thermodynamic state of refrigerant at points (that is, points A, B, E, M, N, F, I and G) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 via the heat exchanger 18, the expansion valve 16 and the heat exchangers 15 and 14 sequentially and returns to the compressor 12.
  • the vapor compression refrigeration cycle 10 according to the second embodiment is the same as that of the first embodiment except a line from the outlet of the heat exchanger 18 to the inlet of the compressor 12. That is, the state of refrigerant from point A to point E via point B in the Mollier chart shown in FIG. 4 is the same as the state of refrigerant from point A to point E via point B in the Mollier chart shown in FIG. 8. Therefore, the state of refrigerant from point E to point A, which is peculiar to the vapor compression refrigeration cycle 10 according to the second embodiment, will be described below.
  • Refrigerant in a supercooled liquid state that has exchanged heat with air-conditioning air in the heat exchanger 18 to be liquefied branches off from the refrigerant line 24b into the refrigerant line 24a and the refrigerant line 43.
  • Refrigerant in a wet steam state flowing out from the cooling portion 30, flows into the gas-liquid separator 60 via the refrigerant lines 34 and 72.
  • refrigerant in a gas-liquid two-phase state is separated into the refrigerant steam 61 and the refrigerant liquid 62.
  • the gas-liquid separator 60 separates refrigerant, flowing out from the cooling portion 30 and flowing through the refrigerant line 34, into gaseous refrigerant and liquid refrigerant.
  • the gas-liquid separator 60 separates refrigerant vaporized in the cooling portion 30 into the liquid-state refrigerant liquid 62 and the gaseous refrigerant steam 61 and temporarily stores them.
  • the refrigerant steam 61 in a saturated steam state flows out from the gas-liquid separator 60 into the refrigerant line 41 , and flows into the expansion valve 47.
  • refrigerant is throttle-expanded, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged (point J).
  • the refrigerant liquid 62 in a saturated liquid state flows out from the gas-liquid separator 60, and flows to the refrigerant line 24a via the refrigerant line 48.
  • Refrigerant flowing from the gas-liquid separator 60 to the refrigerant line 24a via the refrigerant line 48 and refrigerant directly flowing from the refrigerant line 24b to the refrigerant line 24a are mixed in the refrigerant line 24a at the inlet of the expansion valve 16.
  • the mixed refrigerant is equal in pressure to those at points L and M shown in FIG. 8.
  • the specific enthalpy of the mixed refrigerant is determined depending on the ratio of the specific enthalpies and the ratio of the flow rates of refrigerants before mixing. For example, when the flow rates of refrigerants before mixing are equal to each other, the mixed refrigerant has the middle specific enthalpy (point N) between the specific enthalpy at point L and the specific enthalpy at point M.
  • Refrigerant at point N is equal in pressure to refrigerants at points L and M, and has a specific enthalpy larger than or equal to that of refrigerant in a saturated liquid state at point L and smaller than or equal to that of refrigerant in a gas-liquid mixing state at point M.
  • the mixed refrigerant flows to the expansion valve 16, and passes through the expansion valve 16 to be throttle-expanded into low-temperature and low-pressure wet steam in a gas-liquid mixing state (point F).
  • Refrigerant of which the temperature is decreased in the expansion valve 16 flows into the heat exchanger 15 via the refrigerant line 27.
  • Refrigerant in a wet steam state flows into the tube of the heat exchanger 15.
  • the refrigerant absorbs heat of outside air via the fins as latent heat of vaporization to evaporate with a constant pressure.
  • Refrigerant exchanges heat with outside air in the heat exchanger 15 to be heated, and the dryness of the refrigerant increases.
  • Part of refrigerant receives latent heat in the heat exchanger 1 5 to vaporize, so the percentage of saturated steam contained in the refrigerant in a wet steam state increases (point I).
  • Refrigerant in a wet steam state flowing out from the heat exchanger 1 5, flows into the heat exchanger 14 via the refrigerant line 23.
  • Refrigerant in a wet steam state flows into the tube of the heat exchanger 14.
  • the refrigerant absorbs heat of outside air via the fins as latent heat of vaporization to be heated, evaporates with a constant pressure, and the dryness of the refrigerant increases.
  • the temperature of refrigerant steam further increases by sensible heat to become superheated steam (point G).
  • Refrigerant (point J) that is throttle-expanded in the expansion valve 47 and that is decreased in pressure is equal in pressure to refrigerant in a superheated steam state (point G), flowing to the refrigerant line 22b via the heat exchanger 14. Therefore, refrigerant flowing through the refrigerant line 41 and refrigerant flowing through the refrigerant line 22b both flow into the refrigerant line 22a and are mixed.
  • the mixed refrigerant is equal in pressure to those at points J and G shown in FIG. 8.
  • the specific enthalpy of the mixed refrigerant is determined depending on the ratio of the specific enthalpies and the ratio of the flow rates of refrigerants flowing through the respective refrigerant lines 22b and 41 . For example, when the flow rates of refrigerants before mixing are equal to each other, the mixed refrigerant has the middle specific enthalpy (point A) between the specific enthalpy at point J and the specific enthalpy at point G.
  • Refrigerant in a saturated liquid state at the outlet of the gas-liquid separator 60 is caused to flow to the refrigerant line 34 during cooling operation and is caused to flow to the refrigerant line 48 during heating operation to thereby make it possible to suppress flow of gaseous refrigerant steam into the refrigerant lines 34 and 48. Therefore, it is possible to suppress an increase in pressure loss due to an increase in flow rate of refrigerant, and the power consumption of the compressor 12 for flowing refrigerant may be reduced, so it is possible to avoid deterioration of the performance of the vapor compression refrigeration cycle 10.
  • the refrigerant liquid 62 in a saturated liquid state is stored inside the gas-liquid separator 60.
  • the gas-liquid separator 60 functions as a reservoir that temporarily stores the refrigerant liquid 62 inside.
  • the flow rate of refrigerant flowing from the gas-liquid separator 60 to the cooling portion 30 may be maintained at the time of switching from heating operation to cooling operation.
  • the gas-liquid separator 60 has the function of storing liquid, fluctuations in refrigerant flow rate, that is, the flow rate of refrigerant flowing from the heat exchanger 14 to the gas-liquid separator 60 temporarily decreases at the time of switching between cooling operation and heating operation, may be absorbed.
  • the cooling performance for cooling the HV device 3 1 may be stabilized.
  • the path of refrigerant is formed such that only part of refrigerant flows through the heat exchanger 14 to increase the pressure of refrigerant at the inlet of the compressor 12 to thereby make it possible to suppress operation of the compressor 12 under the condition of low compression efficiency, so it is possible to reduce the power consumption for adiabatically compressing refrigerant in the compressor 12 during heating operation.
  • refrigerant flowing out from the heat exchanger 14 needs to be mixed with refrigerant in a wet steam state, flowing out from the cooling portion 30. Therefore, in order to flow refrigerant in a superheated steam state through the refrigerant line 22a, the refrigerant needs to be further heated from the state of dry saturated steam in the heat exchanger 14 so as to have a predetermined degree of superheat. Therefore, the capacity of the heat exchanger 14 needs to be increased, the size of the heat exchanger 14 increases, and the flexibility of design relatively reduces as the vehicle-mounted cooling system 1.
  • refrigerant flowing out from the heat exchanger 14 is mixed with refrigerant in a dry saturated steam state, separated in the gas-liquid separator 60, and is used to increase the suction pressure of the compressor 12, so it is not necessary to increase a degree of superheat of refrigerant at the outlet of the heat exchanger 14.
  • a degree of superheat of refrigerant at the outlet of the heat exchanger 14 may be adjusted so as to be in a superheated steam state having a specific enthalpy substantially equal to the specific enthalpy of refrigerant that is throttle-expanded in the expansion valve 47 (point J).
  • the capacity of each of the heat exchangers 14 and 15 may be further reduced.
  • the size of each of the heat exchangers 14 and 15 may be reduced, so it is possible to obtain the cooling system 1 that is reduced in size and that is advantageous in installation on the vehicle.
  • the two-stage heat exchangers 14 and 15 are arranged between the compressor 12 and the expansion valve 16, so refrigerant absorbs heat from outside air in both the heat exchangers 14 and 15 to be heated during heating operation.
  • refrigerant absorbs heat from outside air in both the heat exchangers 14 and 15 to be heated during heating operation.
  • By heating refrigerant in both the cooling portion 30 and the heat exchangers 14 and 15 it is possible to reduce the heat exchange capacity of each of the heat exchangers 14 and 1 5.
  • Refrigerant may be heated into a sufficient superheated steam state at the outlet of the heat exchanger 14, so the excellent heating performance for heating the cabin of the vehicle may be maintained.
  • the cooling system 1 that includes the expansion valve 38 and the refrigerant line 72 that bypasses the expansion valve 38 is described.
  • the expansion valve 38 may be configured such that refrigerant flowing to the cooling portion 30 is throttle-expanded in the expansion valve 38 during cooling operation and the pressure loss may be reduced at the time when refrigerant passes through the expansion valve 38 during heating operation, the refrigerant line 72 may be omitted.
  • FIG. 9 is a schematic view that shows the configuration of a cooling system 1 according to a third embodiment of the invention.
  • the cooling system 1 according to the third embodiment has the same configuration as that of the second embodiment except that, during heating operation, the on-off valve 49 is closed, the expansion valve 16 is fully closed (opening degree 0%) and the expansion valve 47 is fully open (opening degree 100%).
  • the entire refrigerant that has been adiabatically compressed in the compressor 12 and that has exchanged heat with air-conditioning air in the heat exchanger 18 flows from the refrigerant line 24b into the refrigerant line 43.
  • Refrigerant flowing into the refrigerant line 43 passes through the expansion valve 44 to be throttle-expanded, flows through the cooling line 32 of the cooling portion 30 to cool the HV device 3 1 , and is separated into gas and liquid in the gas-liquid separator 60, and then only the refrigerant steam 61 flows out from the gas-liquid separator 60 and returns to the compressor 12 via the refrigerant lines 41 and 22a.
  • refrigerant flows in the vapor compression refrigeration cycle 10 so as to sequentially pass through points A, B, E, D and H shown in FIG. 9 to circulate through the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30.
  • Refrigerant passes through a refrigerant circulation path that is formed by sequentially connecting the compressor 12, the heat exchanger 18, the expansion valve 44 and the cooling portion 30, thus circulating in the vapor compression refrigeration cycle 10.
  • FIG. 10 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle 10 according to the third embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 10 shows the thermodynamic state of refrigerant at points (that is, points A, B, E, D and H) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 via the heat exchanger 18, the expansion valve 44 and the cooling portion 30 sequentially and returns to the compressor 12.
  • refrigerant is in a dry saturated steam state (point A) at the inlet of the compressor 12.
  • Refrigerant in a dry saturated steam state is introduced into the compressor 12, and is adiabatically compressed in the compressor 12 along a constant specific entropy line.
  • point B the refrigerant increases in pressure and temperature into high-temperature and high-pressure superheated steam having a high degree of superheat (point B), and then the refrigerant flows to the heat exchanger 18.
  • High-pressure refrigerant steam in the heat exchanger 18 is cooled in the heat exchanger 18, becomes dry saturated steam from superheated steam with a constant pressure, releases latent heat of condensation to gradually liquefy into wet steam in a gas-liquid mixing state, becomes saturated liquid as the entire refrigerant condenses, and further releases sensible heat to become supercooled liquid (point E).
  • Refrigerant in a supercooled liquid state, flowing into the refrigerant line 43. is throttle-expanded in the expansion valve 44, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to become low-temperature and low-pressure wet steam in a gas-liquid mixing state (point D).
  • Refrigerant is heated by exchanging heat with the HV device 31 , and the dryness of the refrigerant increases. Part of refrigerant receives latent heat from the HV device 31 to vaporize, so the percentage of saturated steam contained in the refrigerant in a wet steam state increases (point H).
  • Refrigerant in a wet steam state, flowing out from the cooling portion 30, is separated into the refrigerant steam 61 and the refrigerant liquid 62 in the gas-liquid separator 60. Only the refrigerant steam 61 in a saturated steam state flows out from the gas-liquid separator 60 and flows to the refrigerant line 41 , and is introduced into the compressor 12 via the refrigerant line 22a, the four- way valve 13 and the refrigerant line 26 (point A). The compressor 12 compresses refrigerant flowing from the refrigerant line 26. Refrigerant continuously repeats changes among the compressed state, the condensed state, the throttle-expanded state and the evaporated state in accordance with the above described cycle.
  • the entire refrigerant may be caused to flow from the refrigerant line 24b to the refrigerant line 43. That is, during heating operation, low-temperature and low-pressure refrigerant that has passed through the expansion valve 16 may be configured so as not to flow through the heat exchangers 15 and 14.
  • valve open/close settings are switched such that refrigerant does not flow through the heat exchangers 14 and 15 during heating operation as described in the third embodiment.
  • refrigerant is caused to flow through the cooling portion 30 to make it possible to ensure cooling of the HV device 31 , and air-conditioning air may be sufficiently warmed in the heat exchanger 18 to thereby make it possible to ensure heating performance.
  • air-conditioning air may be sufficiently warmed in the heat exchanger 18 to thereby make it possible to ensure heating performance.
  • FIG. 1 1 is a schematic view that shows the configuration of a cooling system 1 according to a fourth embodiment.
  • the cooling system 1 according to the fourth embodiment differs from that of the second embodiment in that an ejector 80 is provided.
  • a refrigerant line 81 , a refrigerant line 83 and a refrigerant line 85 are connected to the ejector 80.
  • the refrigerant line 81 branches off from the refrigerant line 43.
  • the refrigerant line 83 branches off from the refrigerant line 34, which is the path of refrigerant flowing between the gas-liquid separator 60 and the cooling portion 30, at the side closer to the cooling portion 30 than the expansion valve 38.
  • the refrigerant line 85 branches off from the refrigerant line 34 at the side closer to the gas-liquid separator 60 than the expansion valve 38.
  • An on-off valve 82 is arranged in the refrigerant line 81 .
  • the on-off valve 82 allows or prohibits flow of refrigerant via the refrigerant line 81 .
  • An on-off valve 84 is arranged in the refrigerant line 83.
  • the on-off valve 84 allows or prohibits flow of refrigerant via the refrigerant line 83.
  • An on-off valve 86 is arranged in the refrigerant line 85. The on-off valve 86 allows or prohibits flow of refrigerant via the refrigerant line 85.
  • the HV device 31 may be cooled by using refrigerant that is decreased in temperature such that only liquid refrigerant is taken out from the gas-liquid separator 60 and is expanded in the expansion valve 38. so it is possible to further efficiently cool the HV device 31 .
  • FIG. 12 is a schematic view that shows the cooling system 1 according to the fourth embodiment in a state where the four- way valve 13 is switched.
  • the on-off valves 82, 84 and 86 all are open, and the expansion valve 38 is fully closed. Therefore, refrigerant flows to the ejector 80.
  • the ejector 80 functions as a booster such that high-pressure refrigerant before passing through the expansion valve 44 is used as driving stream, refrigerant after passing through the expansion valve 44 and having cooled the HV device 31 in the cooling portion 30 is used as secondary stream, and the driving stream and the secondary stream are mixed to increase the pressure of low-pressure refrigerant flowing from the cooling portion 30 toward the gas-liquid separator 60.
  • High-pressure refrigerant flowing from the refrigerant line 43 into the ejector 80 via the refrigerant line 81 is used as driving stream and is sprayed from a nozzle, and refrigerant is drawn into the ejector 80 from the refrigerant line 83 by a negative pressure generated inside the ejector 80 because of the sprayed driving stream and the viscosity of the driving stream.
  • refrigerant flowing from the refrigerant line 81 is completely mixed with refrigerant flowing from the refrigerant line 83, and then, passes through a diffuser to be increased in pressure, and is released to the refrigerant line 85.
  • Refrigerant of which the pressure is decreased as it passes through the expansion valve 44 is increased in pressure in the ejector 80, and flows to the gas-liquid separator 60 via the refrigerant lines 85 and 34.
  • FIG. 13 is a Mollier chart that shows the state of refrigerant during heating operation of the vapor compression refrigeration cycle 10 according to the fourth embodiment.
  • the abscissa axis represents the specific enthalpy (unit: kJ/kg) of refrigerant
  • the ordinate axis represents the absolute pressure (unit: MPa) of refrigerant.
  • the curve in the chart is the saturation vapor line and saturation liquid line of refrigerant.
  • FIG. 13 shows the thermodynamic state of refrigerant at points (that is, points A, B. E. D. C. H. K and J) in the vapor compression refrigeration cycle 10 when refrigerant flows from the outlet of the heat exchanger 18 into the refrigerant line 43, is throttle-expanded in the expansion valve 44, and is increased in pressure in the ejector 80 after cooling the HV device 31 , the refrigerant steam 61 separated in the gas-liquid separator 60 into gas and liquid flows out from the gas-liquid separator 60 and returns to the compressor 12 via the refrigerant lines 41 and 22a.
  • FIG. 1 3 also shows the thennodynamic state of refrigerant at points (that is, points A, B, E, M. N, F, I and G) in the vapor compression refrigeration cycle 10 when refrigerant flows from the compressor 12 via the heat exchanger 18, the expansion valve 16 and the heat exchangers 15 and 14 sequentially and returns to the compressor 12.
  • refrigerant in a superheated steam state (point A), introduced into the compressor 12, is adiabatically compressed in the compressor 12 along a constant specific entropy line. As refrigerant is compressed, the refrigerant increases in pressure and temperature into high-temperature and high-pressure superheated steam having a high degree of superheat (point B), and then the refrigerant flows to the heat exchanger 18.
  • High-pressure refrigerant steam in the heat exchanger 18 is cooled in the heat exchanger 18, becomes dry saturated steam from superheated steam with a constant pressure, releases latent heat of condensation to gradually liquefy into wet steam in a gas-liquid mixing state, becomes saturated liquid as the entire refrigerant condenses, and further releases sensible heat to become supercooled liquid (point E).
  • High-pressure liquid refrigerant liquefied in the heat exchanger 1 8 branches off from the refrigerant line 24b to the refrigerant line 24a and the refrigerant line 43.
  • Refrigerant warmed in the cooling portion 30 is increased in pressure in the ejector 80.
  • High-pressure refrigerant that has not passed through the expansion valve 44 is supplied from the refrigerant line 81 to the ejector 80, and low-pressure refrigerant of which the pressure is decreased as it passes through the expansion valve 44 is supplied from the refrigerant line 83 to the ejector 80.
  • the pressure of low-pressure refrigerant is increased, and the temperature of low-pressure refrigerant increases.
  • the ejector 80 uses high-pressure refrigerant as driving gas and low-pressure refrigerant as suction gas to utilize the differential pressure between high-pressure refrigerant and low-pressure refrigerant to introduce low-pressure refrigerant into the ejector 80, increases the pressure of the low-pressure refrigerant and discharges refrigerant having a higher pressure (point H).
  • the ejector 80 is used as the booster for increasing the pressure of low-pressure refrigerant, so it is not necessary to drive a compressor that requires power consumption to increase the pressure of refrigerant. Therefore, it is possible to avoid an increase in power consumption.
  • the ejector 80 has a simple structure such that a nozzle and a diffuser are combined with each other, and has no moving portion, so it is possible to provide a booster having excellent durability and reliability.
  • refrigerant flows into the gas-liquid separator 60 via the refrigerant lines 85 and 34.
  • refrigerant in a gas-liquid two-phase state is separated into the refrigerant steam 61 and the refrigerant liquid 62.
  • the refrigerant steam 61 in a dry saturated steam state (point K), separated in the gas-liquid separator 60. flows out from the gas-liquid separator 60, flows into the refrigerant line 41 , and flows out to the expansion valve 47.
  • refrigerant is throttle-expanded, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged (point J).
  • the refrigerant liquid 62 in a saturated liquid state (point L) flows out from the gas-liquid separator 60, and flows to the refrigerant line 24a via the refrigerant line 48.
  • Refrigerant flowing from the gas-liquid separator 60 to the refrigerant line 24a via the refrigerant line 48 and refrigerant directly flowing from the refrigerant line 24b to the refrigerant line 24a are mixed in the refrigerant line 24a at the inlet of the expansion valve 16.
  • the mixed refrigerant is equal in pressure to those at points L and M shown in FIG. 13.
  • the specific enthalpy of the mixed refrigerant is determined depending on the ratio of the specific enthalpies and the ratio of the flow rates of refrigerants before mixing. For example, when the flow rates of refrigerants before mixing are equal to each other, the mixed refrigerant has the middle specific enthalpy (point N) between the specific enthalpy at point L and the specific enthalpy at point M.
  • Refrigerant at point N is equal in pressure to refrigerants at points L and M, and has a specific enthalpy larger than or equal to that of refrigerant in a saturated liquid state at point L and smaller than or equal to that of refrigerant in a gas-liquid mixing state at point M.
  • the mixed refrigerant flows to the expansion valve 16, and passes through the expansion valve 16 to be throttle-expanded in the expansion valve 16, and the refrigerant decreases in temperature and pressure with the specific enthalpy of the refrigerant unchanged to thereby become wet steam in a gas-liquid mixing state (point F).
  • Refrigerant of which the temperature is decreased in the expansion valve 16 flows into the heat exchanger 1 5 via the refrigerant line 27.
  • Refrigerant receives latent heat from outside air in the heat exchanger 15 to be heated, and part of the refrigerant vaporizes, so the percentage of saturated steam contained in the refrigerant in a wet steam state increases, and the dryness of the refrigerant increases (point I).
  • Refrigerant in a wet steam state flowing out from the heat exchanger 15, flows into the heat exchanger 14 via the refrigerant line 23.
  • refrigerant flows through the heat exchanger 14.
  • refrigerant absorbs heat of outside air as latent heat of vaporization to be heated, so the refrigerant evaporates with a constant pressure, and the dryness of the refrigerant increases.
  • point G the temperature of refrigerant steam further increases by sensible heat to become superheated steam
  • Refrigerant (point J) that is throttle-expanded in the expansion valve 47 and that is decreased in pressure is equal in pressure to refrigerant in a superheated steam state (point G), flowing to the refrigerant line 22b via the heat exchanger 14. Therefore, refrigerant flowing tlirough the refrigerant line 41 and refrigerant flowing through the refrigerant line 22b both flow into the refrigerant line 22a and are mixed. The mixed refrigerant is equal in pressure to those at points J and G shown in FIG. 13.
  • the specific enthalpy of the mixed refrigerant is determined depending on the ratio of the specific enthalpies and the ratio of the flow rates of refrigerants flowing through the respective refrigerant lines 22b and 41 .
  • the mixed refrigerant has the middle specific enthalpy (point A) between the specific enthalpy at point J and the specific enthalpy at point G.
  • refrigerant is introduced into the compressor 12 via the four- way valve 13 and the refrigerant line 26.
  • the compressor 12 compresses refrigerant flowing from the refrigerant line 26.
  • the amount of heat given from the HV device 3 1 to refrigerant increases in the cooling portion 30, so the amount of heat absorbed from outside air by the refrigerant in the heat exchangers 14 and 15 may be relatively reduced.
  • the difference in temperature between outside air and refrigerant may be reduced, so the temperature and pressure of the refrigerant flowing via the expansion valve 16 and the heat exchangers 15 and 14 may be relatively increased. That is, when FIG. 13 is compared with FIG. 8, the pressure of refrigerant from point F to point G is higher in FIG. 13.
  • the pressure of refrigerant flowing through the. refrigerant line 41 is equal to the pressure of refrigerant flowing through the refrigerant line 22b.
  • the pressure of refrigerant flowing into the compressor 12 is adjusted to the pressure of refrigerant at point G. Therefore, when FIG. 13 is compared with FIG. 8, the pressure at point A is higher in FIG. 1 3.
  • Refrigerant after cooling the HV device 3 1 in the cooling portion 30 is increased in pressure using the ejector 80 to thereby make it possible to further increase the pressure of refrigerant at the inlet of the compressor 12.
  • the power consumption of the compressor 12 may be further reduced.
  • the cooling system 1 that cools an electrical device mounted on the vehicle is described using the HV device 3 1 as an example.
  • the electrical device is not limited to the illustrated electrical devices, such as an inverter and a motor generator.
  • the electrical device may be any electrical device as long as it generates heat when it is operated.
  • the plurality of electrical devices desirably have a common cooling target temperature range.
  • the cooling target temperature range is an appropriate temperature range within which the electrical device is operated.
  • the heat generating source cooled by the cooling system 1 is not limited to the electrical device mounted on the vehicle; instead, it may be any device that generates heat or may be a heat generating portion of any device.
  • the cooling system according to the aspect of the invention may be particularly advantageously applied to cooling of an electrical device, such as a motor generator and an inverter, using a vapor compression refrigeration cycle for cooling a cabin, in a vehicle, such as a hybrid vehicle, a fuel-cell vehicle and an electric vehicle, equipped with the electrical device.
  • an electrical device such as a motor generator and an inverter
  • a vapor compression refrigeration cycle for cooling a cabin, in a vehicle, such as a hybrid vehicle, a fuel-cell vehicle and an electric vehicle, equipped with the electrical device.

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  • Manufacturing & Machinery (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Power Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un système de refroidissement (1) qui refroidit un dispositif de type véhicule hybride (31) comprenant un compresseur (12), des échangeurs de chaleur (14, 18) et une vanne de détente (16). Le système de refroidissement (1) comprend par ailleurs un robinet à quatre voies (13) qui sélectionne l'écoulement du fluide frigorigène au cours d'une opération de conditionnement d'air. Le système de refroidissement (1) comprend par ailleurs une première conduite et une seconde conduite qui sont des trajectoires du fluide frigorigène raccordées en parallèle entre l'échangeur de chaleur (14) et la vanne de détente (16) ; une partie de refroidissement (30) qui est mise en œuvre dans la seconde conduite et qui refroidit le dispositif de type véhicule hybride (31) ; une conduite de fluide frigorigène (41) et une conduite de fluide frigorigène (43, 45). La conduite de fluide frigorigène (41) permet une communication fluidique entre une trajectoire de fluide frigorigène, entre le compresseur (12) et l'échangeur de chaleur (14) ; et la seconde conduite plus proche de l'échangeur de chaleur (14) que de la partie de refroidissement (30). La conduite de fluide frigorigène (43, 45) permet une communication fluidique entre une trajectoire de fluide frigorigène, entre la vanne de détente (16) et l'échangeur de chaleur (18), et la seconde conduite plus proche de la vanne de détente (16) que de la partie de refroidissement (30).
PCT/IB2012/000942 2011-05-26 2012-05-15 Système de refroidissement WO2012160426A1 (fr)

Applications Claiming Priority (2)

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JP2011118275A JP2012245856A (ja) 2011-05-26 2011-05-26 冷却装置
JP2011-118275 2011-05-26

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FR3040563A1 (fr) * 2015-08-25 2017-03-03 Valeo Systemes De Controle Moteur Systeme pour vehicule automobile
EP3361191A1 (fr) * 2017-02-10 2018-08-15 Daikin Europe N.V. Unité de source de chaleur et climatiseur comportant l'unité de source de chaleur
CN108583348A (zh) * 2018-06-08 2018-09-28 上海加冷松芝汽车空调股份有限公司 能为新能源汽车充电电池提供预热和冷却的充电站
WO2020055462A1 (fr) * 2018-09-10 2020-03-19 Carrier Corporation Fonctionnement de pompe à chaleur à éjecteur
FR3129628A1 (fr) * 2021-11-29 2023-06-02 Psa Automobiles Sa Système de ventilation pour véhicule automobile
CN116742200A (zh) * 2023-08-08 2023-09-12 江苏中关村科技产业园节能环保研究有限公司 基于制冷剂喷射循环的车用冷却系统及其工作方法

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JPH09290622A (ja) 1996-04-24 1997-11-11 Denso Corp 車両用空調装置
JPH11223406A (ja) 1998-02-05 1999-08-17 Nippon Soken Inc ヒートポンプサイクル
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Publication number Priority date Publication date Assignee Title
FR3040563A1 (fr) * 2015-08-25 2017-03-03 Valeo Systemes De Controle Moteur Systeme pour vehicule automobile
US11530827B2 (en) 2017-02-10 2022-12-20 Daikin Industries, Ltd. Heat source unit and air conditioner having the heat source unit
EP3361191A1 (fr) * 2017-02-10 2018-08-15 Daikin Europe N.V. Unité de source de chaleur et climatiseur comportant l'unité de source de chaleur
WO2018147413A1 (fr) * 2017-02-10 2018-08-16 Daikin Industries, Ltd. Unité de source de chaleur et climatiseur ayant l'unité de source de chaleur
CN110291348A (zh) * 2017-02-10 2019-09-27 大金工业株式会社 热源单元和具有该热源单元的空气调节器
CN110291348B (zh) * 2017-02-10 2021-12-24 大金工业株式会社 热源单元和具有该热源单元的空气调节器
CN108583348A (zh) * 2018-06-08 2018-09-28 上海加冷松芝汽车空调股份有限公司 能为新能源汽车充电电池提供预热和冷却的充电站
CN108583348B (zh) * 2018-06-08 2023-08-18 上海加冷松芝汽车空调股份有限公司 能为新能源汽车充电电池提供预热和冷却的充电站
EP3926256A1 (fr) * 2018-09-10 2021-12-22 Carrier Corporation Fonctionnement de pompe à chaleur d'éjecteur
WO2020055462A1 (fr) * 2018-09-10 2020-03-19 Carrier Corporation Fonctionnement de pompe à chaleur à éjecteur
US11781791B2 (en) 2018-09-10 2023-10-10 Carrier Corporation Ejector heat pump operation
FR3129628A1 (fr) * 2021-11-29 2023-06-02 Psa Automobiles Sa Système de ventilation pour véhicule automobile
CN116742200A (zh) * 2023-08-08 2023-09-12 江苏中关村科技产业园节能环保研究有限公司 基于制冷剂喷射循环的车用冷却系统及其工作方法
CN116742200B (zh) * 2023-08-08 2023-11-03 江苏中关村科技产业园节能环保研究有限公司 基于制冷剂喷射循环的车用冷却系统及其工作方法

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