US20130319038A1 - Vehicle cooling system - Google Patents

Vehicle cooling system Download PDF

Info

Publication number
US20130319038A1
US20130319038A1 US14/000,311 US201214000311A US2013319038A1 US 20130319038 A1 US20130319038 A1 US 20130319038A1 US 201214000311 A US201214000311 A US 201214000311A US 2013319038 A1 US2013319038 A1 US 2013319038A1
Authority
US
United States
Prior art keywords
refrigerant
passage
condenser
cooling
heat source
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/000,311
Other languages
English (en)
Inventor
Yasuhiro Kawase
Yuichi Ohno
Kazuhide Uchida
Yoshiaki Kawakami
Yuki Jojima
Eizo Takahashi
Kousuke Sato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Soken Inc
Original Assignee
Nippon Soken Inc
Toyota Motor Corp
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 Nippon Soken Inc, Toyota Motor Corp filed Critical Nippon Soken Inc
Assigned to NIPPON SOKEN, INC., TOYOTA JIDOSHA KABUSHIKI KAISHA reassignment NIPPON SOKEN, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOJIMA, Yuki, KAWAKAMI, YOSHIAKI, KAWASE, YASUHIRO, OHNO, YUICHI, SATO, KOUSUKE, TAKAHASHI, EIZO, UCHIDA, KAZUHIDE
Publication of US20130319038A1 publication Critical patent/US20130319038A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • B60H1/00271—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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/323—Cooling devices using compression characterised by comprising auxiliary or multiple systems, e.g. plurality of evaporators, or by involving auxiliary cooling devices
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • B60H2001/00949—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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2511—Evaporator distribution valves

Definitions

  • the invention relates to a cooling system. More particularly, the invention relates to a cooling system that cools a heat source using a vapor compression refrigeration cycle.
  • JP-A-11-23081 describes a system that cools heat generating equipment with intermediate pressure refrigerant, and is provided with a cooler configured such that intermediate pressure refrigerant of a refrigeration cycle cools heat generating equipment, and electrical expansion valves, the valve opening amounts of which are able to be controlled by external signals, that are arranged one on each of the upstream side and the downstream side of the cooler.
  • JP-A-11-23081 describes a system that cools heat generating equipment with intermediate pressure refrigerant, and is provided with a cooler configured such that intermediate pressure refrigerant of a refrigeration cycle cools heat generating equipment, and electrical expansion valves, the valve opening amounts of which are able to be controlled by external signals, that are arranged one on each of the upstream side and the downstream side of the cooler.
  • JP-A-2005-90862 describes a cooling system provided with heat generating body cooling means for cooling the heat generating body, that is provided in a bypass passage that bypasses a compressor, an evaporator, and a pressure reducer of an air conditioning refrigeration cycle.
  • JP-A-2007-69733 describes a cooling system that cools a heat generating body using refrigerant for an air conditioning system, and in which a heat exchanger that performs heat exchange with air for air conditioning, and a heat exchanger that performs heat exchange with the heat generating body, are arranged in parallel in a refrigerant passage that leads from an expansion valve to a compressor.
  • JP-A-2001-309506 describes a cooling system that circulates refrigerant of a vehicle air conditioning refrigeration cycle system to a cooling member of an inverter circuit portion that drive-controls an electric motor for running a vehicle, and suppresses cooling of air conditioning airflow by an evaporator of the vehicle air conditioning refrigeration cycle system when cooling of the air conditioning airflow is unnecessary.
  • This invention therefore provides a cooling system capable of inhibiting supercooling of a heat source, reducing pressure loss, and reducing power consumption of a compressor.
  • a first aspect of the invention relates to a cooling system that cools a heat source.
  • This cooling system includes a compressor that circulates refrigerant; a condenser that condenses the refrigerant; a first pressure reducer that reduces a pressure of the refrigerant that has been condensed by the condenser; an evaporator that vaporizes the refrigerant that has been reduced in pressure by the first pressure reducer; a first passage through which the refrigerant flows from an outlet of the condenser toward an inlet of the first pressure reducer, and that includes a passage forming portion that forms part of the first passage; a second passage that is connected in parallel with the passage forming portion; a cooling portion that is provided in the second passage and cools the heat source using the refrigerant from the condenser; and a second pressure reducer that is arranged upstream of the cooling portion in the second passage.
  • the cooling system according to this aspect may also include a flow control valve that is arranged in the passage forming portion and regulates a flowrate of the refrigerant that flows through the passage forming portion and a flowrate of the refrigerant that flows through the second passage.
  • the cooling system described above may also include another condenser arranged in the first passage, and the passage forming portion may be provided between the condenser and the other condenser.
  • the condenser may have a greater heat releasing capability to release heat from the refrigerant than the other condenser does.
  • the cooling system described above may also include a pressure increasing device that increases a pressure of the refrigerant that flows from the cooling portion toward the other condenser.
  • the cooling system described above may also include another cooling portion that is provided in a path for the refrigerant that flows from the pressure increasing device toward the other condenser, and that cools another heat source that is different from the heat source, using the refrigerant.
  • FIG. 1 is a view showing a frame format of the structure of a cooling system according to a first example embodiment of the invention
  • FIG. 2 is a Mollier diagram showing the state of refrigerant of a vapor compression refrigeration cycle according to the first example embodiment
  • FIGS. 3A to 3D are views schematically showing opening amount control of a flow control valve according to the first example embodiment
  • FIG. 4 is a view showing a frame format of the structure of a cooling system according to a second example embodiment of the invention.
  • FIG. 5 is a Mollier diagram showing the state of refrigerant of a vapor compression refrigeration cycle according to the second example embodiment
  • FIG. 6 is a view showing a frame format of the structure of a cooling system according to a third example embodiment of the invention.
  • FIG. 7 is a Mollier diagram showing the state of refrigerant of a vapor compression refrigeration cycle according to the third example embodiment
  • FIG. 8 is a view showing a frame format of the structure of a cooling system according to a fourth example embodiment of the invention.
  • FIG. 9 is a Mollier diagram showing the state of refrigerant of a vapor compression refrigeration cycle according to the fourth example embodiment.
  • FIG. 1 is a view of a frame format showing the structure of a cooling system 1 according to a first example embodiment of the invention.
  • the cooling system 1 includes a vapor compression refrigeration cycle 10 .
  • This vapor compression refrigeration cycle 10 is provided in a vehicle in order to cool the interior of the vehicle, for example. Cooling using the vapor compression refrigeration cycle 10 is performed when, for example, a switch for performing cooling is turned on, or when an automatic control mode that automatically adjusts the temperature in the cabin of the vehicle so that it comes to match a set temperature is selected and the temperature in the vehicle cabin is higher than the set temperature.
  • the vapor compression refrigeration cycle 10 includes a compressor 12 , a condenser 14 , an expansion valve 16 that serves as an example of a pressure reducer, and an evaporator 18 .
  • the vapor compression refrigeration cycle 10 also includes a refrigerant passage 21 that communicates the compressor 12 with the condenser 14 , a refrigerant passage 22 that serves as a first passage that communicates the condenser 14 with The expansion valve 16 , a refrigerant passage 23 that communicates the expansion valve 16 with the evaporator 18 , and a refrigerant passage 24 that communicates the evaporator 18 with the compressor 12 .
  • the vapor compression refrigeration cycle 10 is formed by the compressor 12 , the condenser 14 , the expansion valve 16 , and the evaporator 18 being connected together by the refrigerant passages 21 to 24 .
  • the compressor 12 operates with an electric motor or an engine mounted in the vehicle as the power source, and adiabatically compresses refrigerant gas to create superheated refrigerant gas.
  • the compressor 12 draws in and compresses gas-phase refrigerant that flows through the refrigerant passage 24 from the evaporator 18 , and discharges it into the refrigerant passage 21 .
  • the compressor 12 circulates the refrigerant in the vapor compression refrigeration cycle 10 by discharging the refrigerant into the refrigerant passage 21 .
  • the condenser 14 isobarically releases heat from the superheated refrigerant gas that has been compressed in the compressor 12 to an external medium, thus creating refrigerant liquid.
  • the gas-phase refrigerant discharged from the compressor 12 is condensed (i.e., liquefied) by being cooled through releasing its heat to the surroundings in the condenser 14 .
  • the condenser 14 includes a tube through which refrigerant flows, and fins for performing heat exchange between the refrigerant that flows through the tube and the surrounding air in the condense 14 .
  • the condenser 14 performs heat exchange between the refrigerant and cool air supplied by the natural flow of air produced as the vehicle runs. The temperature of the refrigerant drops from the heat exchange in the condenser 14 , and as a result, the refrigerant becomes liquefied.
  • the expansion valve 16 injects the high-pressure liquid-phase refrigerant that flows through the refrigerant passage 22 from a small hole so that it expands and changes to low-temperature, low-pressure atomized refrigerant.
  • the expansion valve 16 reduces the pressure of the refrigerant liquid that has been condensed by the condenser 14 , thereby creating wet vapor of a gas-liquid mixture.
  • the expansion valve 16 functions as a first pressure reducer for reducing the pressure of the refrigerant liquid that flows through the refrigerant passage 22 .
  • the pressure reducers are not limited to being the expansion valves 16 and 33 that throttle and expand. That is, they may be capillaries instead.
  • the evaporator 18 absorbs the heat in the surrounding air that has been introduced so as to contact the evaporator 18 , by the atomized refrigerant that flows through the evaporator 18 being vaporized.
  • the evaporator 18 cools the inside of vehicle cabin by absorbing the vaporization heat when the wet vapor of the refrigerant vaporizes and becomes refrigerant gas from the air in the vehicle cabin that is a portion to be cooled, using the refrigerant that has been reduced in pressure by the expansion valve 16 .
  • the inside of the vehicle cabin is cooled led by the air, whose temperature has been reduced by the heat being absorbed by the evaporator 18 , being returned again into the vehicle cabin.
  • the refrigerant is heated by absorbing heat from the surroundings in the evaporator 18 .
  • the evaporator 18 includes the tube through which refrigerant flows, and the fins for performing heat exchange between the refrigerant that flows through the tube and the surrounding air in the evaporator 18 .
  • Refrigerant in a wet vapor state flows through the tube.
  • the refrigerant flows through the tube, it vaporizes by absorbing the heat of the air inside the vehicle cabin as latent heat of vaporization via the fins, and then becomes superheated vapor by sensible heat.
  • the vaporized refrigerant flows into the compressor 12 through the refrigerant passage 24 , and the compressor 12 compresses the refrigerant that flows in from the evaporator 18 .
  • the refrigerant passage 21 is a passage for leading refrigerant from the compressor 12 to the condenser 14 .
  • the refrigerant flows from the outlet of the compressor 12 toward the inlet of the condenser 14 via the refrigerant passage 21 .
  • the refrigerant passage 22 is a passage for leading refrigerant from the condenser 14 to the expansion valve 16 .
  • the refrigerant flows from the outlet of the condenser 14 toward the inlet of the expansion valve 16 via the refrigerant passage 22 .
  • the refrigerant passage 23 is a passage for leading refrigerant from the expansion valve 16 to the evaporator 18 .
  • the refrigerant flows from the outlet of the expansion valve 16 toward the inlet of the evaporator 18 via the refrigerant passage 23 .
  • the refrigerant passage 24 is a passage for leading refrigerant from the evaporator 18 to the compressor 12 .
  • the refrigerant flows from the outlet of the evaporator 18 toward the inlet of the compressor 12 via the refrigerant passage 24 .
  • Refrigerant flows through points A, B, C, E, and F, in that order, shown in FIG. 1 , inside the vapor compression refrigeration cycle 10 , such that refrigerant circulates to the compressor 12 , the condenser 14 , the expansion valve 16 , and the evaporator 18 .
  • the refrigerant circulates through the vapor compression refrigeration cycle 10 by passing through a refrigerant circulation flow path in which the compressor 12 , the condenser 14 , the expansion valve 16 , and the evaporator 18 are connected in that order by the refrigerant passages 21 to 24 .
  • Carbon dioxide a hydrogen oxide such as propane or isobutane, ammonia, or water, for example, may be used as the refrigerant of the vapor compression refrigeration cycle 10 .
  • the refrigerant passage 22 through which refrigerant flows from the condenser 14 toward the expansion valve 16 includes a passage forming portion 26 .
  • the passage forming portion 26 forms part of the refrigerant passage 22 .
  • Point C shown in FIG. 1 represents an upstream end portion of the passage forming portion 26 , i.e., an end portion of the passage forming portion 26 that is on the side near the condenser 14 .
  • Point E in FIG. 1 represents a downstream end portion of the passage forming portion 26 , i.e., an end portion of the passage forming portion that is on the side near the expansion valve 16 .
  • the cooling system 1 includes a second passage that is connected in parallel with the passage forming portion 26 .
  • a cooling portion 30 is provided in this second passage.
  • the cooling portion 30 is provided in a path for the refrigerant that flows from the condenser 14 toward the expansion valve 16 .
  • the cooling portion 30 includes an HV equipment heat source 31 that is electrical equipment mounted in the vehicle, and a cooling passage 32 that is a conduit through which refrigerant flows.
  • the HV equipment heat source 31 is one example of a heat source.
  • the second passage described above includes the cooling passage 32 .
  • the second passage also includes refrigerant passages 34 , 35 , and 36 that are conduits through which refrigerant flows.
  • the expansion valve 33 that serves as a second pressure reducer that is different from the first pressure reducer (i.e., the expansion valve 16 ) is arranged upstream of the cooling portion 30 in the second passage.
  • the expansion valve 33 expands the high-pressure liquid-phase refrigerant discharged from the condenser 14 , thereby reducing the temperature and the pressure of the refrigerant, just like the expansion valve 16 .
  • the second passage through which refrigerant flows parallel with the passage forming portion 26 from point C toward point E in FIG. 1 is divided into a refrigerant passage 34 that is upstream (i.e., on the side near the condenser 14 ) of the expansion valve 33 , a refrigerant passage 35 that is between the expansion valve 33 and the cooling portion 30 , the cooling passage 32 that is included in the cooling portion 30 , and the refrigerant passage 36 that is downstream (i.e., on the side near the expansion valve 16 ) of the cooling portion 30 .
  • the refrigerant passages 34 and 35 are passages for leading refrigerant from point C to the cooling portion 30 .
  • the refrigerant passage 36 is a passage for leading refrigerant from the cooling portion 30 to point E.
  • Point C is a branch point between the refrigerant passage 22 and the refrigerant passage 34
  • point E is a branch point between the refrigerant passage 22 and the refrigerant passage 36 .
  • Refrigerant that is discharged from the condenser 14 and branches off at point C to flow through the second passage flows toward the cooling portion 30 via the refrigerant passage 34 , the expansion valve 33 , and the refrigerant passage 35 .
  • the refrigerant that has flowed to the cooling portion 30 and through the cooling passage 32 removes heat from the HV equipment heat source 31 that is the heat source, thereby cooling the HV equipment heat source 31 .
  • the cooling portion 30 cools the HV equipment heat source 31 using the low-temperature, low-pressure refrigerant that has been discharged from the condenser 14 and reduced in pressure by the expansion valve 33 .
  • the refrigerant then flows from the cooling portion 30 toward point E via the refrigerant passage 36 , and reaches the expansion valve 16 via the refrigerant passage 22 .
  • the upstream end portion of the cooling passage 32 is connected to the refrigerant passage 35
  • the downstream end portion of the cooling passage 32 is connected to the refrigerant passage 36 .
  • the cooling portion 30 is provided with a structure that enables heat exchange between the refrigerant and the HV equipment heat source 31 at the cooling passage 32 .
  • the cooling portion 30 has the cooling passage 32 that is formed such that an outer peripheral surface of the cooling passage 32 directly contacts the case of the HV equipment heat source 31 .
  • the cooling passage 32 has a portion that is adjacent to the case of the HV equipment heat source 31 . Heat exchange between the refrigerant that flows through the cooling passage 32 and the HV equipment heat source 31 is possible at this portion.
  • the HV equipment heat source 31 is directly connected to the outer peripheral surface of the cooling passage 32 that forms part of the refrigerant path from the condenser 14 to the expansion valve 16 of the vapor compression refrigeration cycle 10 , and is thus cooled.
  • the HV equipment heat source 31 is arranged on an outer portion of the cooling passage 32 , so the HV equipment heat source 31 will not interfere with the flow of refrigerant that flows through the cooling passage 32 . Therefore, pressure loss in the vapor compression refrigeration cycle 10 will not increase, so the HV equipment heat source 31 is able to be cooled without increasing the power of the compressor 12 .
  • the cooling portion 30 may be provided with a suitable well-known heat pipe interposed between the HV equipment heat source 31 and the cooling passage 32 .
  • the HV equipment heat source 31 is connected to an outer peripheral surface of the cooling passage 32 via the heat pipe, and is cooled by heat being transferred from the HV equipment heat source 31 to the cooling passage 32 via the heat pipe.
  • heat-transfer efficiency between the cooling passage 32 and the HV equipment heat source 31 is able to be increased, so cooling efficiency of the HV equipment heat source 31 can be improved.
  • a wick type heat pipe may be used.
  • the heat pipe enables heat to be reliably transferred from the HV equipment heat source 31 to the cooling passage 32 , so there may be distance between the HV equipment heat source 31 and the cooling passage 32 , and there is no need for a complex arrangement of the cooling passage 32 in order to connect the cooling passage 32 to the HV equipment heat source 31 .
  • the degree of freedom in the arrangement of the HV equipment heat source 31 is able to be improved.
  • the HV equipment heat source 31 includes electrical equipment that generates heat as a result of sending and receiving electric power.
  • the electrical equipment includes at least one of, for example, an inverter for converting direct current (DC) electric power into alternating current (AC) electric power, a motor-generator that is a rotary electric machine, a battery that is a power storage device, a converter for stepping up the voltage of the battery, and a DC/DC converter for stepping down the voltage of the battery.
  • the battery is a secondary battery such as a lithium-ion battery or a nickel-metal hydride battery.
  • a capacitor may also be used instead of a battery.
  • FIG. 2 is a Mollier diagram showing the state of refrigerant of the vapor compression refrigeration cycle 10 according to the first example embodiment.
  • the horizontal axis in FIG. 2 represents the specific enthalpy (unit: kJ/kg) of the refrigerant, and the vertical axis in FIG. 2 represents the absolute pressure (unit: MPa) of the refrigerant.
  • the curve in the drawing is a saturated vapor line and a saturated liquid line of the refrigerant.
  • FIG. 2 shows the thermodynamic equation of state of the refrigerant at each point (i.e., points A, B, C, D, E, and F in FIG.
  • refrigerant in a superheated vapor state that is drawn into the compressor 12 (point A) is adiabatically compressed along a geometric entropy line in the compressor 12 .
  • this refrigerant As this refrigerant is compressed, the pressure and temperature of the refrigerant rises, and it becomes high-temperature, high-pressure superheated vapor with a large degree of superheat (point B).
  • the refrigerant then flows to the condenser 14 .
  • the high-pressure refrigerant vapor that has entered the condenser 14 is cooled in the condenser 14 , and changes from the superheated vapor to dry saturated vapor while remaining at constant pressure, such that the refrigerant vapor then releases latent heat of condensation and is gradually liquidized, becoming wet vapor of a gas-liquid mixture.
  • the refrigerant releases sensible heat and becomes supercooled liquid (point C).
  • the liquefied refrigerant flows into the expansion valve 33 via the refrigerant passage 34 .
  • the supercooled liquid-state refrigerant is throttled and expanded, so the temperature and pressure of the refrigerant decrease without the specific enthalpy of the refrigerant changing (point D).
  • the refrigerant that has been reduced in temperature in the expansion valve 33 flows via the refrigerant passage 35 to the cooling passage 32 of the cooling portion 30 , where it cools the HV equipment heat source 31 .
  • the degree to which the refrigerant is supercooled lessens, and the temperature of the refrigerant in the supercooled liquid state rises and approaches a saturation temperature of liquid refrigerant (point E).
  • the refrigerant flows into the expansion valve 16 .
  • the expansion valve 16 the refrigerant in the supercooled liquid state is throttled and expanded, so the temperature and pressure decrease without the specific enthalpy changing, thus creating low-temperature, low-pressure wet vapor of a gas-liquid mixture (point F).
  • point F The heat of the refrigerant in the wet vapor state that is discharged from the expansion valve 16 is absorbed from the outside, so the refrigerant vaporizes while remaining at constant pressure from the latent heat of vaporization in the evaporator 18 .
  • the refrigerant vapor When all of the refrigerant becomes dry saturated vapor, the refrigerant vapor further rises in temperature from the sensible heat and becomes superheated vapor (point A), which is then drawn into the compressor 12 .
  • the refrigerant continuously changes states repeatedly from compressed, to condensed, to throttled and expanded, to vaporized, according to this kind of cycle.
  • refrigerant cools the inside of the vehicle cabin by absorbing, in the evaporator 18 , vaporization heat from the air inside the vehicle cabin.
  • high-pressure liquid refrigerant discharged from the condenser 14 branches off at point C, such that some of the refrigerant flows to the HV equipment heat source 31 and performs heat exchange with the HV equipment heat source 31 , thereby cooling the HV equipment heat source 31 .
  • the cooling system 1 cools the HV equipment heat source 31 that is the heat source mounted in the vehicle, using the vapor compression refrigeration cycle 10 for air-conditioning the inside of the vehicle cabin.
  • the HV equipment heat source 31 is cooled using the vapor compression refrigeration cycle 10 provided to cool the portion to be cooled at the evaporator 18 . Therefore, there is no need to provide equipment such as a special water circulating pump or cooling fan in order to cool the HV equipment heat source 31 . Accordingly, the structure necessary for the cooling system 1 of the HV equipment heat source 31 can be reduced so the structure of the apparatus can be simple, and as a result, the manufacturing cost of the cooling system 1 is able to be reduced. In addition, there is no need to operate a power supply such as a pump or a cooling fan in order to cool the HV equipment heat source 31 , so power does not need to be consumed to operate the power supply. Therefore, the power consumption for cooling the HV equipment heat source 31 is able to be reduced.
  • the HV equipment heat source 31 can be cooled using refrigerant with a temperature that has been lowered by the refrigerant being expanded by the expansion valve 33 , so the HV equipment heat source 31 is able to be cooled more efficiently.
  • the temperature of the refrigerant that cools the HV equipment heat source 31 with the cooling portion 30 can be appropriately regulated by optimally selecting the specifications of the expansion valve 33 . Therefore, the HV equipment heat source 31 can be cooled by supplying the cooling portion 30 with refrigerant of a lower temperature suitable for cooling the HV equipment heat source 31 .
  • the passage forming portion 26 that is a path that does not pass through the cooling portion 30 , and the second passage that is a path for refrigerant that cools the HV equipment heat source 31 via the cooling portion 30 , are provided in parallel as paths through which refrigerant flows from the outlet of the condenser 14 toward the inlet of the expansion valve 16 . Therefore, only some of the refrigerant that is discharged from the condenser 14 flows to the cooling portion 30 . Refrigerant of an amount necessary to cool the HV equipment heat source 31 is made to flow to the cooling portion 30 , such that the HV equipment heat source 31 is able to be appropriately cooled. Accordingly, the HV equipment heat source 31 is able to be inhibited from being supercooled.
  • the refrigerant is cooled in the condenser 14 until it becomes supercooled liquid, and is then heated to a temperature slightly below the saturation temperature by receiving sensible heat from the HV equipment heat source 31 . Then the refrigerant passes through the expansion valve 16 , and as a result, the refrigerant becomes low-temperature, low-pressure wet vapor. At the outlet of the expansion valve 16 , the refrigerant has the temperature and pressure originally required to cool the inside of the vehicle cabin.
  • the heat releasing capability of the condenser 14 is set such that the condenser 14 is able to sufficiently cool the refrigerant.
  • the cooling system 1 in this example embodiment the refrigerant is cooled to a sufficiently supercooled state in the condenser 14 , and high-pressure refrigerant from the outlet of the condenser 14 is used to cool the HV equipment heat source 31 .
  • the HV equipment heat source 31 is able to be cooled without adversely affecting the cooling capability to cool the air inside the vehicle cabin.
  • the temperature required to cool the HV equipment heat source 31 is preferably lower than at least an upper limit value of a target temperature range as the temperature range of the HV equipment heat source 31 .
  • the specifications of the condenser 14 are set such that the temperature of the liquid-phase refrigerant after passing through the condenser 14 is lower than the temperature required to cool the inside of the vehicle cabin.
  • the specifications of the condenser 14 are set such that the refrigerant has a heat discharge that is greater than the condenser of the vapor compression refrigeration cycle when not cooling the HV equipment heat source 31 , by the amount of heat that it is estimated that the refrigerant will receive from the HV equipment heat source 31 .
  • the cooling system 1 provided with the condenser 14 having such specifications is able to appropriately cool the HV equipment heat source 31 without increasing the power of the compressor 12 , while maintaining cooling performance for the inside of the vehicle cabin.
  • the cooling system 1 includes a flow control valve 28 .
  • the flow control valve 28 is provided in the refrigerant passage 22 that leads from the condenser 14 toward the expansion valve 16 .
  • the flow control valve 28 is arranged in the passage forming portion 26 that forms part of the refrigerant passage 22 .
  • the flow control valve 28 appropriately regulates the flowrate of the refrigerant that flows through the passage forming portion 26 and the flowrate of the refrigerant that flows through the second passage that includes the cooling passage 32 , by changing its opening amount (i.e., the opening amount of the flow control valve 28 ) to increase or decrease pressure loss of the refrigerant that flows through the passage forming portion 26 .
  • the flow control valve 28 For example, if the flow control valve 28 is fully closed such that the valve opening amount is 0%, the entire amount of the refrigerant that is discharged from the condenser 14 will flow from point C into the refrigerant passage 34 . If the opening amount of the flow control valve 28 is increased, the flowrate of refrigerant that directly flows to the expansion valve 16 via the passage forming portion 26 , of the refrigerant that flows from the condenser 14 to the refrigerant passage 22 , will increase, and consequently, the flowrate of the refrigerant that flows via the refrigerant passages 34 and 35 to the cooling passage 32 where it cools the HV equipment heat source 31 will decrease.
  • the opening amount of the flow control valve 28 is decreased, the flowrate of refrigerant that directly flows to the expansion valve 16 via the passage forming portion 26 , of the refrigerant that flows from the condenser 14 to the refrigerant passage 22 , will decrease, and consequently, the flowrate of the refrigerant that flows through the cooling passage 32 where it cools the HV equipment heat source 31 will increase.
  • the opening amount of the flow control valve 28 If the opening amount of the flow control valve 28 is increased, the flowrate of the refrigerant that cools the HV equipment heat source 31 will decrease, so the cooling capability for the HV equipment heat source 31 will be reduced. If the opening amount of the flow control valve 28 is decreased, the flowrate of the refrigerant that cools the HV equipment heat source 31 will increase, so the cooling capability for the HV equipment heat source 31 will be improved.
  • the amount of refrigerant that flows to the HV equipment heat source 31 can be optimally regulated using the flow control valve 28 , so supercooling of the HV equipment heat source 31 can be inhibited, and in addition, both pressure loss related to the flow of refrigerant through the second passage, and the power consumption of the compressor 12 for circulating the refrigerant are able to be reduced.
  • FIGS. 3A to 3D are views schematically showing opening amount control of the flow control valve 28 .
  • the horizontal axis shown in the graphs in FIGS. 3A to 3D represents time.
  • the vertical axis of the graph in FIG. 3A represents the valve opening amount when the flow control valve 28 is an electrical expansion valve with a stepping motor.
  • the vertical axis of the graph in FIG. 3B represents the opening amount when the flow control valve 28 is a temperature-type expansion valve that opens and closes according to a change in temperature.
  • the vertical axis of the graph in FIG. 3C represents the temperature of the HV equipment heat source 31 .
  • the vertical axis of the graph in FIG. 3D represents a temperature difference between the inlet and the outlet (i.e., an inlet/outlet temperature difference) of the HV equipment heat Source 31 .
  • the HV equipment heat source 31 is cooled by refrigerant flowing through the cooling portion 30 .
  • the adjustment of the opening amount of the flow control valve 28 is performed by, for example, monitoring the temperature of the HV equipment heat source 31 , or the temperature difference between the outlet temperature and the inlet temperature of the HV equipment heat source 31 .
  • a temperature sensor that intermittently measures the temperature of the HV equipment heat source 31 is provided, and the temperature of the HV equipment heat source 31 is monitored.
  • a temperature sensor that measures the inlet temperature and the outlet temperature of the HV equipment heat source 31 is provided, and the temperature difference between the inlet and outlet of the HV equipment heat source 31 is monitored.
  • the opening amount of the flow control valve 28 will decrease, as shown in the graphs in FIGS. 3A and 3B . Throttling the opening amount of the flow control valve 28 increases the flowrate of the refrigerant that flows to the cooling portion 30 through the refrigerant passages 34 and 35 , as described above, so the HV equipment heat source 31 can be cooled even more effectively.
  • the temperature of the HV equipment heat source 31 can be reduced to equal than or less the target temperature, as shown in the graph in FIG 3 C, or the inlet/outlet temperature difference of the HV equipment heat source 31 can be reduced to equal to or less than the target temperature difference, as shown in the graph in FIG. 3D .
  • FIG. 4 is a view showing a frame format of the structure of the cooling system 1 according to a second example embodiment of the invention.
  • the cooling system 1 of the second example embodiment differs from that of the first example embodiment in that a condenser 15 that is another condenser that is different from the condenser 14 is arranged in the refrigerant passage 22 that joins the condenser 14 and the expansion valve 16 together.
  • the cooling system 1 of the second example embodiment includes the condenser 14 that serves as a first condenser, and the condenser 15 that serves as a second condenser.
  • the condenser 15 is provided, so the refrigerant passage 22 branches into two, i.e., into a refrigerant passage 22 a that is upstream (i.e., on the side near the condenser 14 ) of the condenser 15 , and a refrigerant passage 22 b that is downstream (i.e., on the side near the expansion valve 16 ) of the condenser 15 .
  • high-pressure refrigerant that has been discharged from the compressor 12 is condensed by both the condenser 14 and the condenser 15 .
  • the passage forming portion 26 that forms part of the refrigerant passage 22 is provided in the refrigerant passage 22 a between the condenser 14 and the condenser 15 .
  • a second passage that is a cooling system of the HV equipment heat source 31 that includes the cooling passage 32 is arranged parallel with the passage forming portion 26 .
  • a path for refrigerant that flows from the condenser 14 to the condenser 15 , and a path for refrigerant that flows from the condenser 14 to the condenser 15 via the cooling portion 30 are provided in parallel, and pressure loss when refrigerant flows to the cooling system of the HV equipment heat source 31 is able to be reduced by having only some of the refrigerant flow to the cooling portion 30 .
  • FIG. 5 is a Mollier diagram showing the state of refrigerant of the vapor compression refrigeration cycle 10 according to the second example embodiment.
  • the horizontal axis in FIG. 5 represents the specific enthalpy (unit: kJ/kg) of the refrigerant, and the vertical axis in FIG. 5 represents the absolute pressure (unit: MPa) of the refrigerant.
  • the curve in the drawing is a saturated vapor line and a saturated liquid line of the refrigerant.
  • FIG. 5 shows the thermodynamic equation of state of the refrigerant at each point (i.e., Points A, B, C, D, E, G, and F) in the vapor compression refrigeration cycle 10 , in which refrigerant flows from the refrigerant passage 22 a at the outlet of the condenser 14 to the refrigerant passage 34 via point C and is expanded at the expansion valve 33 , after which it flows through the refrigerant passage 35 , cools the HV equipment heat source 31 , and then returns from the refrigerant passage 36 to the refrigerant passage 22 a at the inlet of the condenser 15 via point E.
  • Points A, B, C, D, E, G, and F the thermodynamic equation of state of the refrigerant at each point (i.e., Points A, B, C, D, E, G, and F) in the vapor compression refrigeration cycle 10 , in which refrigerant flows from the refrigerant passage 22 a at the outlet of the condenser 14
  • the vapor compression refrigeration cycle 10 in the second example embodiment is the same as that in the first example embodiment except for the system from the condenser 14 to the expansion valve 16 . That is, the states of the refrigerant from point G to point B via points F and A in the Mollier diagram in FIG. 5 are the same as the states of the refrigerant from point E to point B via points F and A in the Mollier diagram in FIG. 2 . Therefore, the particular states of the refrigerant from point B to point G in the vapor compression refrigeration cycle 10 of the second example embodiment will be described below.
  • the refrigerant in a supercooled liquid state is throttled and expanded, so the temperature and pressure of the refrigerant decrease without the specific enthalpy of the refrigerant changing, and the refrigerant becomes wet vapor that is a mixture of the saturated liquid and the saturated vapor (point D).
  • the refrigerant that has been reduced in temperature in the expansion valve 33 flows via the refrigerant passage 35 to the cooling passage 32 of the cooling portion 30 , where it cools the HV equipment heat source 31 .
  • Heat exchange with the HV equipment heat source 31 heats the refrigerant and thus increases the degree of dryness of the refrigerant.
  • the refrigerant receives latent heat from the HV equipment heat source 31 and some of this refrigerant consequently vaporizes, such that the ratio of saturated vapor in the refrigerant that is in the wet vapor state increases (point E).
  • the refrigerant flows into the condenser 15 .
  • the wet vapor of the refrigerant is again condensed in the condenser 15 , and when all of the refrigerant condenses, it becomes saturated liquid.
  • the refrigerant releases sensible heat and becomes supercooled liquid that is supercooled (point G).
  • the refrigerant becomes low-temperature, low-pressure wet vapor (point F) by passing through the expansion valve 16 .
  • the refrigerant By sufficiently cooling the refrigerant in the condenser 15 , at the outlet of the expansion valve 16 , the refrigerant has the temperature and pressure originally required to cool the inside of the vehicle cabin. Therefore, the amount of heat that can be received from the outside when the refrigerant vaporizes in the evaporator 18 can be made sufficiently large. Setting the heat releasing capability of the condenser 15 that is able to sufficiently cool the refrigerant in this way enables the HV equipment heat source 31 to be cooled without adversely affecting the cooling capability to cool the air inside the vehicle cabin. Therefore, both the cooling capability for the HV equipment heat source 31 and the vehicle cabin cooling capability are able to be ensured.
  • the condenser 14 is arranged between the compressor 12 and the expansion valve 16 , so it is necessary to further cool the refrigerant from a saturated liquid state in the condenser 14 so that the refrigerant has a predetermined degree of supercooling. If the refrigerant in a supercooled liquid state is cooled, the temperature of the refrigerant will approach atmospheric temperature, and the cooling efficiency of the refrigerant will decrease, so the capacity of the condenser 14 must be increased. As a result, the size of the condenser 14 will increase, which is a drawback for the cooling system 1 that is to be mounted in a vehicle.
  • the condenser 14 is made small in order to mount it in a vehicle, the heat releasing capability of the condenser 14 will also be less, and as a result, the temperature of the refrigerant at the outlet of the expansion valve 16 may not be sufficiently low, so the vehicle cabin cooling capability may be insufficient.
  • the condenser 14 In contrast, with the vapor compression refrigeration cycle 10 according to the second example embodiment, two condensers 14 and 15 are arranged between the compressor 12 and the expansion valve 16 , and the cooling system of the HV equipment heat source 31 is provided between the condenser 14 and the condenser 15 . With the condenser 14 , the refrigerant simply needs to be cooled to a saturated liquid state, as shown in FIG. 5 . Refrigerant that is in a wet vapor state as a result of having received the latent heat of vaporization from the HV equipment heat source 31 such that some of the refrigerant has vaporized is again cooled by the condenser 15 .
  • the refrigerant changes states at a constant temperature.
  • the condenser 15 further cools the refrigerant to a degree of supercooling necessary for cooling the inside of the vehicle cabin. Therefore, compared with the first example embodiment, there is no need to increase the degree of supercooling of the refrigerant, so the capacity of the condensers 14 and 15 can be decreased. Accordingly, the vehicle cabin cooling capability can be ensured, and the size of the condensers 14 and 15 can be reduced, so the cooling system 1 that is small and advantageous for being mounted in a vehicle is able to be obtained.
  • the refrigerant that flows from the condenser 14 to the HV equipment heat source 31 is heated as a result of receiving heat from the HV equipment heat source 31 when it cools the HV equipment heat source 31 .
  • the refrigerant is heated to equal to or greater than a saturated vapor temperature in the HV equipment heat source 31 and all of the refrigerant vaporizes, the amount of heat exchange between the refrigerant and the HV equipment heat source 31 decreases, so the HV equipment heat source 31 is no longer able to be cooled efficiently, and the pressure loss when the refrigerant flows through the conduit increases. Therefore, it is preferable to sufficiently cool the refrigerant in the condenser 14 to the point where not all of the refrigerant will vaporize after cooling the HV equipment heat source 31 .
  • the state of the refrigerant at the outlet of the condenser 14 is made to be a state that is close to saturated liquid, typically, a state in which the refrigerant is on the saturated liquid line at the outlet of the condenser 14 .
  • the condenser 14 has the capability to sufficiently cool the refrigerant in this way, the heat releasing capability to release heat from the refrigerant of the condenser 14 consequently becomes higher than the heat releasing capability of the condenser 15 .
  • FIG. 6 is a view showing a frame format of the structure of the cooling system 1 according to a third example embodiment of the invention.
  • the cooling system 1 in the third example embodiment differs from that in the second example embodiment in that it includes an ejector 38 .
  • the ejector 38 serves as a pressure increasing device that makes the high-pressure refrigerant before passing through the expansion valve 33 into a driven flow and makes the refrigerant after passing through the expansion valve 33 and cooling the HV equipment heat source 31 in the cooling portion 30 into a secondary flow, and mixes the driven flow and the secondary flow to increase the pressure of the low-pressure refrigerant that flows from the cooling portion 30 toward the condenser 15 .
  • a refrigerant passage 37 that branches off from the refrigerant passage 34 on the inlet side of the expansion valve 33 is connected to the ejector 38 .
  • the refrigerant passage 36 that is a flow path of refrigerant that flows through the cooling portion 30 toward the condenser 15 is also connected to the ejector 38 .
  • High-pressure refrigerant that has flowed from the refrigerant passage 37 into the ejector 38 is injected as the driven flow from a nozzle.
  • Refrigerant from the refrigerant passage 36 is drawn into the ejector 38 by negative pressure generated inside of the ejector 38 by the injection of the driven flow, and the viscosity of the driven flow.
  • the refrigerant that has flowed in from the refrigerant passage 37 completely mixes with the refrigerant that has flowed in from the refrigerant passage 36 . Then this mixture is passed through a diffuser so that its pressure increases, and after which it is discharged to a refrigerant passage 39 .
  • the refrigerant that has been reduced in pressure by passing through the expansion valve 33 is increased in pressure by the ejector 38 , and flows to the condenser 15 .
  • FIG. 7 is a Mollier diagram showing the state of refrigerant of the vapor compression refrigeration cycle 10 according to the third example embodiment.
  • the horizontal axis in FIG. 7 represents the specific enthalpy (unit: kJ/kg) of the refrigerant, and the vertical axis in FIG. 7 represents the absolute pressure (unit: MPa) of the refrigerant.
  • the curve in the drawing is a saturated vapor line and a saturated liquid line of the refrigerant.
  • FIG. 7 shows the thermodynamic equation of state of the refrigerant at each point (i.e., points A, B, C, D, H, E, G, and F) in the vapor compression refrigeration cycle 10 , in which refrigerant flows from the refrigerant passage 22 a at the outlet of the condenser 14 to the refrigerant passage 34 via point C and is expanded at the expansion valve 33 , after which it flows through the refrigerant passage 35 , cools the HV equipment heat source 31 , is then increased in pressure by the ejector 38 , and is returned from the refrigerant passage 39 to the refrigerant passage 22 a at the inlet of the condenser 15 via point E.
  • points A, B, C, D, H, E, G, and F in which refrigerant flows from the refrigerant passage 22 a at the outlet of the condenser 14 to the refrigerant passage 34 via point C and is expanded at the expansion valve 33 , after which it flows through the refrigerant passage
  • the vapor compression refrigeration cycle 10 in the third example embodiment is the same as that in the second example embodiment except for the system from the condenser 14 to the expansion valve 16 . That is, the states of the refrigerant from point F to point C via points A and B in the Mollier diagram in FIG. 7 are the same as the states of the refrigerant from point F to point C via points A and B in the Mollier diagram in FIG. 5 . Therefore, the particular states of the refrigerant from point C to point F in the vapor compression refrigeration cycle 10 of the third example embodiment will be described below.
  • the refrigerant in a supercooled liquid state is throttled and expanded, so the temperature and pressure of the refrigerant decrease without the specific enthalpy of the refrigerant changing, and the refrigerant becomes wet vapor that is a mixture of the saturated liquid and the saturated vapor (point D).
  • the refrigerant that has been reduced in temperature in the expansion valve 33 flows via the refrigerant passage 35 to the cooling passage 32 of the cooling portion 30 , where it cools the HV equipment heat source 31 .
  • Heat exchange with the HV equipment heat source 31 heats the refrigerant such that the degree of dryness of the refrigerant increases.
  • the refrigerant receives latent heat from the HV equipment heat source 31 and some of this refrigerant consequently vaporizes, such that the ratio of saturated vapor in the refrigerant that is in the wet vapor state increases (point H).
  • the refrigerant that has been warmed in the cooling portion 30 is increased in pressure by the ejector 38 .
  • the high-pressure refrigerant from the outlet of the condenser 14 is supplied from the refrigerant passage 37 to the ejector 38 , and low-pressure refrigerant that has been reduced in pressure by passing through the expansion valve 33 is supplied from the refrigerant passage 36 to the ejector 38 .
  • the pressure of the low-pressure refrigerant increases, and the temperature of the low-pressure refrigerant rises.
  • the ejector 38 introduces the low-pressure refrigerant into the ejector 38 using the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant, and raises the pressure of the low-pressure refrigerant and discharges the resultant medium-pressure refrigerant that has a higher pressure (point E).
  • the ejector 38 is used as a pressure increasing device for increasing the pressure of the low-pressure refrigerant, so there is no need to increase the pressure of the refrigerant by driving a compressor that consumes power. Therefore, an increase in power consumption can be avoided.
  • the ejector 38 has a simple structure in which a nozzle is combined with a diffuser, and has no working parts, so an extremely durable and reliable pressure increasing device is able to be provided.
  • the refrigerant flows into the condenser 15 .
  • the wet vapor of the refrigerant that has been increased in pressure by passing through the ejector 38 is again condensed-in the condenser 15 , and when all of the refrigerant condenses, it becomes saturated liquid.
  • the refrigerant releases sensible heat and becomes supercooled liquid that is supercooled (point G).
  • the refrigerant becomes low-temperature, low-pressure wet vapor (point F) by passing through the expansion valve 16 .
  • the refrigerant is cooled by heat exchange between the outside air and the refrigerant by the refrigerant releasing heat to the outside air. If the refrigerant pressure is low at this time, the temperature difference with the outside air will be small and the heat releasing capability of the condenser 15 with respect to the outside air will decrease. Unless the refrigerant is able to be sufficiently cooled by the condenser 15 , the amount of heat that the refrigerant is able to receive from the outside air in the evaporator 18 may not be sufficiently large, so the cooling capability to cool the air inside the vehicle cabin may decrease.
  • the refrigerant that flows into the condenser 15 is able to be increased in temperature by raising the pressure of the low-pressure refrigerant that has cooled the HV equipment heat source 31 at the cooling portion 30 , using the ejector 38 .
  • a decrease in the heat releasing capability of the condenser 15 can be avoided, so the efficiency of the condenser 15 can be improved.
  • refrigerant is able to be sufficiently cooled in the condenser 15 , so a decrease in cooling capability can be avoided.
  • FIG. 8 is a view showing a frame format of the structure of the cooling system 1 according to a fourth example embodiment of the invention.
  • the cooling system 1 in the fourth example embodiment differs from that in the third example embodiment in that a cooling portion 40 that is another cooling portion that is different from the cooling portion 30 described above is provided in the refrigerant passage 39 that is a path for refrigerant that has been increased in pressure by the ejector 38 .
  • the cooling portion 40 is provided in the path for refrigerant that flows from the ejector 38 toward the condenser 15 , between the ejector 38 and the condenser 15 .
  • the cooling portion 40 includes an HV equipment heat source 41 that is that is electrical equipment mounted in the vehicle, and a cooling passage 42 that is a conduit through which refrigerant flows.
  • the HV equipment heat source 41 is one example of another heat source that is different from the HV equipment heat source 31 .
  • a passage for refrigerant from the ejector 38 toward point E in FIG. 8 is divided into a refrigerant passage 39 a that is upstream (i.e., on the side near the ejector 38 ) of the cooling portion 40 , the cooling passage 42 that is included in the cooling portion 40 , and a refrigerant passage 39 b that is downstream (i.e., on the side near point E) of the cooling portion 40 .
  • Refrigerant that is discharged from the ejector 38 flows to the cooling portion 40 via the refrigerant passage 39 a, and flows through the cooling passage 42 removes heat from the HV equipment heat source 41 that is a heat source, thereby cooling the HV equipment heat source 41 .
  • the cooling portion 40 cools the HV equipment heat source 41 using the medium-pressure refrigerant discharged from the ejector 38 .
  • Refrigerant also flows from the cooling portion 40 toward point E via the refrigerant passage 39 b, and then to the condenser 15 via the refrigerant passage 22 a.
  • An upstream end portion of the cooling passage 42 is connected to the refrigerant passage 39 a, and a downstream end portion of the cooling passage 42 is connected to the refrigerant passage 39 b.
  • the cooling portion 40 is provided with a structure that enables heat exchange between the refrigerant and the HV equipment heat source 41 at the cooling passage 42 .
  • An outer peripheral surface of the cooling passage 42 may directly contact a case of the HV equipment heat source 41 , or a heat pipe may be interposed between the HV equipment heat source 41 and the outer peripheral surface of the cooling passage 42 .
  • the HV equipment heat source 41 is arranged on an outer portion of the cooling passage 42 , so the HV equipment heat source 41 will not interfere with the flow of refrigerant that flows through the cooling passage 42 . Therefore, pressure loss in the vapor compression refrigeration cycle 10 will not increase, so the HV equipment heat source 41 is able to be cooled without increasing the power of the compressor 12 .
  • FIG. 9 is a Mollier diagram showing the state of refrigerant of the vapor compression refrigeration cycle 10 according to the fourth example embodiment.
  • the horizontal axis in FIG. 9 represents the specific enthalpy (unit: kJ/kg) of the refrigerant, and the vertical axis in FIG. 9 represents the absolute pressure (unit: MPa) of the refrigerant.
  • the curve in the drawing is a saturated vapor line and a saturated liquid line of the refrigerant.
  • the vapor compression refrigeration cycle 10 in the fourth example embodiment is the same as that in the third example embodiment except far the system from the ejector 38 to the condenser 15 . That is, the states of the refrigerant from point G to point H via points F, A, B, C, and D in the Mollier diagram in FIG. 9 are the same as the states of the refrigerant from point G to point H via points F, A, B, C, and D in the Mollier diagram in FIG. 7 . Therefore, the particular states of the refrigerant from point H to point G in the vapor compression refrigeration cycle 10 of the fourth example embodiment will be described below.
  • High-pressure refrigerant discharged from the outlet of the condenser 14 is supplied from the refrigerant passage 37 , and low-pressure refrigerant (point H) that has been reduced in pressure by passing through the expansion valve 33 is supplied from the refrigerant passage 36 .
  • the low-pressure refrigerant is increased in pressure and the resultant medium-pressure refrigerant that has a higher pressure is discharged from the ejector 38 (point I).
  • the refrigerant that has been increased in pressure by the ejector 38 flows via the refrigerant passage 39 a to the cooling passage 42 of the cooling portion 40 , where it cools the HV equipment heat source 41 .
  • Heat exchange with the HV equipment heat source 41 heats the refrigerant such that the degree of dryness of the refrigerant increases.
  • the refrigerant receives latent heat from the HV equipment heat source 41 and some of this refrigerant consequently vaporizes, such that the saturated liquid in the refrigerant that is in the wet vapor state decreases and the saturated vapor increases (point E).
  • the refrigerant flows into the condenser 15 .
  • the wet vapor of the refrigerant that has cooled the HV equipment heat source 41 is again condensed in the condenser 15 , and when all of the refrigerant condenses, it becomes saturated liquid. Moreover, the refrigerant releases sensible heat and becomes supercooled liquid that is supercooled (point G).
  • Both the HV equipment heat source 31 and the HV equipment heat source 41 are cooled using the vapor compression refrigeration cycle 10 , so special equipment for cooling the HV equipment heat sources 31 and 41 is not necessary. Therefore, the structure required to cool the HV equipment heat sources 31 and 41 can be reduced, which in turn enables the manufacturing cost of the cooling system 1 to be reduced. In addition, there is no need to operate a power supply such as a pump or a cooling fan in order to cool the HV equipment heat sources 31 and 41 , so power consumption for cooling the HV equipment heat sources 31 and 41 can be reduced.
  • the temperature suitable for cooling the HV equipment heat source 41 is higher than the temperature suitable for cooling the HV equipment heat source 31 .
  • This kind of HV equipment heat source 41 may also be a transaxle, for example. If a transaxle is cooled too much, the viscosity of ATF (Automatic Transaxle Fluid) inside the transaxle increases, which leads to a decrease in fuel efficiency. Therefore, it is preferable to cool the transaxle by the necessary heat amount in a higher temperature range than the motor-generator and the PCU (Power Control Unit).
  • ATF Automatic Transaxle Fluid
  • the HV equipment heat source 31 is cooled by the low-temperature refrigerant that has been expanded by the expansion valve 33 , and the HV equipment heat source 41 is cooled by the refrigerant that has been discharged from the ejector 38 and increased in temperature.
  • the temperature of the refrigerant that cools the HV equipment heat source 31 at the cooling portion 30 , and the temperature of the refrigerant that cools the HV equipment heat source 41 at the cooling portion 40 can be appropriately regulated. Therefore, the HV equipment heat sources 31 and 41 that have different temperatures suitable for cooling are able to be simultaneously cooled at their respective optimal temperatures.
  • the cooling system 1 that cools electrical equipment mounted in a vehicle, of which the HV equipment heat sources 31 and 41 are given as examples, is described.
  • the electrical equipment is not limited to the electrical equipment described, e.g., an inverter, a motor-generator, a transaxle, and the like. That is, the electrical equipment may be any appropriate electrical equipment as long as it at least generates heat by operating. If a plurality of electrical equipment is to be cooled, the plurality of electrical equipment preferably has a common target temperature range for cooling.
  • the target temperature range for cooling is a temperature range that is suitable as a temperature environment for operating the electrical equipment.
  • the heat source that is cooled by the cooling system 1 of the invention is not limited to electrical equipment mounted in a vehicle, but may be any equipment that generates heat, or any heat-generating portion of equipment.
  • the cooling system of the invention may be applied, with particular advantage, to cooling electrical equipment that uses a vapor compression refrigeration cycle for cooling the inside of a vehicle, in a vehicle such as a hybrid vehicle, a fuel cell vehicle, or an electric vehicle or the like, that is provided with electric equipment such as a motor-generator and an inverter and the like.
US14/000,311 2011-02-22 2012-02-21 Vehicle cooling system Abandoned US20130319038A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2011-035754 2011-02-22
JP2011035754A JP2012172917A (ja) 2011-02-22 2011-02-22 冷却装置
PCT/IB2012/000301 WO2012114182A1 (en) 2011-02-22 2012-02-21 Vehicle cooling system

Publications (1)

Publication Number Publication Date
US20130319038A1 true US20130319038A1 (en) 2013-12-05

Family

ID=45876810

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/000,311 Abandoned US20130319038A1 (en) 2011-02-22 2012-02-21 Vehicle cooling system

Country Status (5)

Country Link
US (1) US20130319038A1 (ja)
EP (1) EP2678175B1 (ja)
JP (1) JP2012172917A (ja)
CN (1) CN103380014B (ja)
WO (1) WO2012114182A1 (ja)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140216085A1 (en) * 2011-08-01 2014-08-07 Toyota Jidosha Kabushiki Kaisha Cooling system
WO2016168569A1 (en) * 2015-04-15 2016-10-20 Carrier Corporation Refrigeration system and cooling method for electric control device thereof
US20170001493A1 (en) * 2015-07-01 2017-01-05 Hanon Systems CHILLER INTEGRATION INTO vCOOL SYSTEM
US20170118872A1 (en) * 2015-04-15 2017-04-27 Carrier Corporation Refrigeration system and cooling method of electronic control unit thereof
EP3327374A1 (en) * 2016-11-25 2018-05-30 Carrier Corporation Refrigeration system and cooling method of electronic control unit thereof
US20190039437A1 (en) * 2017-08-01 2019-02-07 Ford Global Technologies, Llc Method and system for coolant temperature sensor diagnostics
US10407048B1 (en) * 2018-03-12 2019-09-10 Ford Global Technologies, Llc Hybrid vehicle motor cooling
US11131466B2 (en) 2017-02-10 2021-09-28 Daikin Industries, Ltd. Heat source unit and air conditioner having the heat source unit
US11466911B2 (en) * 2016-11-30 2022-10-11 Dc Engineering, Inc. Method and system for improving refrigeration system efficiency

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5669778B2 (ja) * 2012-03-16 2015-02-18 株式会社日本自動車部品総合研究所 冷却装置およびそれを備える車両
CN103486752A (zh) * 2013-09-25 2014-01-01 珠海格力电器股份有限公司 电力电子器件冷却系统及分布式发电系统
CN103486682B (zh) * 2013-09-25 2021-09-28 珠海格力电器股份有限公司 光伏空调系统
JP6005024B2 (ja) * 2013-11-12 2016-10-12 三菱電機株式会社 冷凍サイクル装置
JP6368205B2 (ja) * 2014-09-24 2018-08-01 東芝キヤリア株式会社 ヒートポンプシステム
CN105196859A (zh) * 2015-09-30 2015-12-30 安徽江淮汽车股份有限公司 一种混合动力汽车水泵系统及其控制方法
CN105890210B (zh) * 2016-06-01 2018-09-07 珠海格力电器股份有限公司 一种高温空调机组
JP2018035951A (ja) * 2016-08-29 2018-03-08 株式会社デンソー 冷凍サイクル装置
CN108344080A (zh) * 2017-01-22 2018-07-31 大金工业株式会社 空调系统
DE102017203043A1 (de) * 2017-02-24 2018-08-30 Siemens Aktiengesellschaft Wärmepumpenanordnung und Verfahren zum Betrieb einer Wärmepumpenanordnung
KR102214987B1 (ko) * 2017-03-24 2021-02-10 한온시스템 주식회사 차량용 전장품 냉각 시스템
FR3077241A1 (fr) * 2018-01-30 2019-08-02 Valeo Systemes Thermiques Architecture de pompe a chaleur avec un evaporateur a double etage combine a un ejecteur
JP6972309B2 (ja) * 2018-04-04 2021-11-24 三菱電機株式会社 空気調和装置および空気調和制御装置
CN108731206A (zh) * 2018-06-20 2018-11-02 广东美的暖通设备有限公司 冷媒冷却装置及其控制方法和空调系统
CN109114793A (zh) * 2018-08-23 2019-01-01 珠海格力电器股份有限公司 空调系统及其制冷剂节流降噪装置
CN109398026B (zh) * 2018-09-11 2022-01-28 蔚来控股有限公司 电动汽车及其空调系统
DE102021202339A1 (de) * 2021-03-10 2022-09-15 Psa Automobiles Sa Kühlvorrichtung für ein Kraftfahrzeug

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020184908A1 (en) * 2001-06-09 2002-12-12 Behr Gmbh & Co. Vehicle cooling system for a temperature-raising device and method for the cooling of a temperature-raising device
US20050229629A1 (en) * 2002-12-16 2005-10-20 Behr Gmbh & Co. Kg Refrigerant circuit and a refrigerating system
US20060010906A1 (en) * 2004-07-15 2006-01-19 Taras Michael F Economized dehumidification system
US20060065011A1 (en) * 2004-09-29 2006-03-30 Denso Corporation Vapor-compression refrigerant cycle system with ejector
US20060207285A1 (en) * 2005-03-18 2006-09-21 Denso Corporation Ejector cycle device
US20070137230A1 (en) * 2005-09-16 2007-06-21 Samsung Electronics Co., Ltd. Refrigerator and control method thereof
US20090248212A1 (en) * 2008-03-25 2009-10-01 Cowans Kenneth W Thermal control system and method
US20110154837A1 (en) * 2008-10-02 2011-06-30 Taras Michael F Refrigerant system with adaptive hot gas reheat

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07116616B2 (ja) 1987-11-04 1995-12-13 新日本製鐵株式会社 耐スクラッチ性に優れた化成皮膜付プレコート金属板の製造方法
JPH0493557A (ja) * 1990-08-10 1992-03-26 Toshiba Corp 車両用クーラ
JP4006782B2 (ja) * 1997-07-01 2007-11-14 株式会社デンソー 発熱機器の冷却器を有する空調装置
JP3952545B2 (ja) * 1997-07-24 2007-08-01 株式会社デンソー 車両用空調装置
JP3591304B2 (ja) * 1998-05-25 2004-11-17 株式会社日本自動車部品総合研究所 発熱体冷却装置
JP4075285B2 (ja) 2000-04-25 2008-04-16 株式会社デンソー 車両走行モ−タ駆動用インバータ回路装置
JP3925324B2 (ja) * 2002-06-25 2007-06-06 株式会社デンソー 空調装置
DE10242369B4 (de) * 2002-09-12 2007-09-13 Webasto Ag Klimatisierungssystem für ein Kraftfahrzeug, insbesondere ein Hybridfahrzeug
JP2004198002A (ja) * 2002-12-17 2004-07-15 Denso Corp 蒸気圧縮式冷凍機
JP2004322933A (ja) * 2003-04-25 2004-11-18 Toyota Industries Corp 車両用冷凍サイクル装置
JP2005090862A (ja) 2003-09-17 2005-04-07 Toyota Motor Corp 冷却システム
JP4872195B2 (ja) * 2004-08-17 2012-02-08 トヨタ自動車株式会社 燃料電池及び空調制御システム
JP2006220351A (ja) * 2005-02-10 2006-08-24 Hitachi Ltd 冷凍装置
CN100545546C (zh) * 2005-04-01 2009-09-30 株式会社电装 喷射器型制冷循环
JP4600212B2 (ja) * 2005-08-23 2010-12-15 株式会社デンソー 超臨界冷凍サイクル装置
JP2007069733A (ja) 2005-09-07 2007-03-22 Valeo Thermal Systems Japan Corp 車両用空調装置を利用した発熱体冷却システム
JP2009264710A (ja) * 2008-04-30 2009-11-12 Daikin Ind Ltd ヒートポンプ装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020184908A1 (en) * 2001-06-09 2002-12-12 Behr Gmbh & Co. Vehicle cooling system for a temperature-raising device and method for the cooling of a temperature-raising device
US20050229629A1 (en) * 2002-12-16 2005-10-20 Behr Gmbh & Co. Kg Refrigerant circuit and a refrigerating system
US20060010906A1 (en) * 2004-07-15 2006-01-19 Taras Michael F Economized dehumidification system
US20060065011A1 (en) * 2004-09-29 2006-03-30 Denso Corporation Vapor-compression refrigerant cycle system with ejector
US20060207285A1 (en) * 2005-03-18 2006-09-21 Denso Corporation Ejector cycle device
US20070137230A1 (en) * 2005-09-16 2007-06-21 Samsung Electronics Co., Ltd. Refrigerator and control method thereof
US20090248212A1 (en) * 2008-03-25 2009-10-01 Cowans Kenneth W Thermal control system and method
US20110154837A1 (en) * 2008-10-02 2011-06-30 Taras Michael F Refrigerant system with adaptive hot gas reheat

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9732663B2 (en) * 2011-08-01 2017-08-15 Toyota Jidosha Kabushiki Kaisha Cooling system
US20140216085A1 (en) * 2011-08-01 2014-08-07 Toyota Jidosha Kabushiki Kaisha Cooling system
WO2016168569A1 (en) * 2015-04-15 2016-10-20 Carrier Corporation Refrigeration system and cooling method for electric control device thereof
US10254029B2 (en) * 2015-04-15 2019-04-09 Carrier Corporation Refrigeration system and cooling method of electronic control unit thereof
US20170118872A1 (en) * 2015-04-15 2017-04-27 Carrier Corporation Refrigeration system and cooling method of electronic control unit thereof
CN106314070A (zh) * 2015-07-01 2017-01-11 翰昂系统有限公司 车辆空调设备和对车辆电池控温的方法
US10252596B2 (en) * 2015-07-01 2019-04-09 Hanon Systems Chiller integration into vcool system
US20170001493A1 (en) * 2015-07-01 2017-01-05 Hanon Systems CHILLER INTEGRATION INTO vCOOL SYSTEM
EP3327374A1 (en) * 2016-11-25 2018-05-30 Carrier Corporation Refrigeration system and cooling method of electronic control unit thereof
US11466911B2 (en) * 2016-11-30 2022-10-11 Dc Engineering, Inc. Method and system for improving refrigeration system efficiency
US11131466B2 (en) 2017-02-10 2021-09-28 Daikin Industries, Ltd. Heat source unit and air conditioner having the heat source unit
US20190039437A1 (en) * 2017-08-01 2019-02-07 Ford Global Technologies, Llc Method and system for coolant temperature sensor diagnostics
US10618380B2 (en) * 2017-08-01 2020-04-14 Ford Global Technologies, Llc Method and system for coolant temperature sensor diagnostics
US10407048B1 (en) * 2018-03-12 2019-09-10 Ford Global Technologies, Llc Hybrid vehicle motor cooling

Also Published As

Publication number Publication date
CN103380014B (zh) 2015-11-25
EP2678175B1 (en) 2015-11-25
EP2678175A1 (en) 2014-01-01
JP2012172917A (ja) 2012-09-10
WO2012114182A1 (en) 2012-08-30
CN103380014A (zh) 2013-10-30

Similar Documents

Publication Publication Date Title
EP2678175B1 (en) Vehicle cooling system
US9681590B2 (en) Cooling system with controlled apportioning of the cooled high pressure refrigerant between the condenser and the expansion valve
JP5522275B2 (ja) 冷却装置
CN103998874B (zh) 冷却装置
JP5655954B2 (ja) 冷却装置および冷却装置の制御方法
US9732663B2 (en) Cooling system
US9631544B2 (en) Cooling system and vehicle that includes cooling system
EP2750908B1 (en) Cooling system
WO2013051114A1 (ja) 冷却装置の制御方法
JP2012245856A (ja) 冷却装置
EP2663459B1 (en) Cooling apparatus
JP5618011B2 (ja) 冷却装置の制御方法
JP5917966B2 (ja) 冷却装置およびそれを備える車両
JP2014088997A (ja) 冷却装置
JP2015152244A (ja) 冷却装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: TOYOTA JIDOSHA KABUSHIKI KAISHA, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KAWASE, YASUHIRO;OHNO, YUICHI;UCHIDA, KAZUHIDE;AND OTHERS;REEL/FRAME:031072/0128

Effective date: 20130721

Owner name: NIPPON SOKEN, INC., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KAWASE, YASUHIRO;OHNO, YUICHI;UCHIDA, KAZUHIDE;AND OTHERS;REEL/FRAME:031072/0128

Effective date: 20130721

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION