WO2020153060A1 - 温度調整装置 - Google Patents

温度調整装置 Download PDF

Info

Publication number
WO2020153060A1
WO2020153060A1 PCT/JP2019/049725 JP2019049725W WO2020153060A1 WO 2020153060 A1 WO2020153060 A1 WO 2020153060A1 JP 2019049725 W JP2019049725 W JP 2019049725W WO 2020153060 A1 WO2020153060 A1 WO 2020153060A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat medium
heat
pump
cooling water
temperature
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.)
Ceased
Application number
PCT/JP2019/049725
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
恒吏 高橋
真野　貴光
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Priority to DE112019006723.0T priority Critical patent/DE112019006723T5/de
Publication of WO2020153060A1 publication Critical patent/WO2020153060A1/ja
Anticipated expiration legal-status Critical
Ceased 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
    • B60H1/00357—Air-conditioning arrangements specially adapted for particular vehicles
    • B60H1/00385—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell
    • B60H1/004—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell for vehicles having a combustion engine and electric drive means, e.g. hybrid electric vehicles
    • 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
    • B60H1/00507—Details, e.g. mounting arrangements, desaeration devices
    • B60H1/00585—Means for monitoring, testing or servicing the air-conditioning
    • 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
    • B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
    • 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
    • B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
    • B60H1/03—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant and from a source other than the propulsion plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P2005/105—Using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/08—Cabin heater

Definitions

  • the present disclosure relates to a temperature adjustment device that adjusts the temperature of a temperature adjustment target fluid.
  • Patent Document 1 discloses a temperature adjusting device applied to a vehicle heat utilization device.
  • the temperature control device of Patent Document 1 heats the air blown into the vehicle interior, which is the space to be air-conditioned, to heat the vehicle interior. Therefore, the temperature control target fluid in the temperature control device of Patent Document 1 is blown air.
  • the temperature adjustment device of Patent Document 1 includes a heat medium circulation circuit that circulates cooling water of an internal combustion engine (that is, an engine). Further, an engine cooling water passage, a heater core, a water-refrigerant heat exchanger of a heat pump cycle, a three-way valve, etc. are connected to the heat medium circulation circuit.
  • the heater core is a heating heat exchange unit that heats the blast air by exchanging heat between the cooling water that is the heat medium and the blast air that is the fluid whose temperature is to be adjusted.
  • the heat pump cycle is a temperature adjusting unit that heats the cooling water using the high pressure refrigerant as a heat source.
  • the three-way valve is a switching unit that switches a cooling water flow pattern (in other words, a circuit configuration) in the heat medium circulation circuit.
  • the cooling water is switched to a normal mode pattern in which the cooling water is circulated between the cooling water passage of the engine and the heater core. Further, when the temperature of the cooling water is lower than the predetermined temperature, the heat pump cycle is operated to switch to the warm air mode pattern in which the cooling water is circulated between the water-refrigerant heat exchanger and the heater core.
  • the temperature control device of Patent Document 1 can heat the blown air to achieve heating of the passenger compartment regardless of the operating state of the engine.
  • this type of check valve does not open unless an appropriate differential pressure across the front and back is secured. Therefore, in the heat medium circulation circuit having the check valve, it is difficult to sufficiently remove the air in the heat medium circulation circuit when injecting the cooling water into the heat medium circulation circuit. Furthermore, when the temperature of the blown air is adjusted, if the air remaining in the heat medium circulation circuit moves into the heat exchanger such as the heater core, the heat exchange performance of the heat exchanger such as the heater core is adversely affected. there is a possibility.
  • the present disclosure has an object to provide a temperature adjusting device capable of suppressing air from remaining in a heat medium circulation circuit for circulating a heat medium.
  • a temperature adjusting device includes a heat medium circulation circuit, a main temperature adjusting unit, a sub temperature adjusting unit, a heat exchanging unit, a main pump, a sub pump, and a switch. And a section.
  • the heat medium circulation circuit circulates the heat medium.
  • the main temperature adjusting unit adjusts the temperature of the heat medium.
  • the sub-temperature adjusting unit adjusts the temperature of the heat medium.
  • the heat exchange unit heat-exchanges the heat medium whose temperature has been adjusted with at least one of the main temperature adjustment unit and the sub temperature adjustment unit with the temperature adjustment target fluid, and adjusts the temperature of the temperature adjustment target fluid.
  • the main pump operates at least when the heat medium whose temperature has been adjusted by the main temperature adjusting unit is pressure-fed to the heat exchanging unit.
  • the sub-pump operates at least when the heat medium whose temperature is adjusted by the sub-temperature adjustment unit is pressure-fed to the heat exchange unit.
  • the switching unit switches the circuit configuration of the heat medium circulation circuit to the first pattern, the second pattern, and the third pattern.
  • the first pattern circulates the heat medium pumped by the sub pump between the sub temperature adjustment unit and the heat exchange unit.
  • the second pattern circulates the heat medium pumped by the main pump between the main temperature adjusting unit and the heat exchanging unit.
  • the heat medium pumped by at least one of the main pump and the sub pump is changed to a flow path through which the heat medium flows when switched to the first pattern and the heat medium when switched to the second pattern. It can be supplied to both of the flowing channels.
  • the switching unit since the switching unit is provided, the circuit configuration of the heat medium circulation circuit can be switched to the first pattern and the second pattern even if the heat medium circulation circuit does not have a check valve. ..
  • the temperature of the heat medium can be reliably adjusted by switching between the first pattern and the second pattern according to the temperature adjusting ability of the heat medium of the main temperature adjusting unit and the sub temperature adjusting unit.
  • the temperature of the fluid whose temperature is to be adjusted can be appropriately adjusted in the heat exchange section.
  • the switching unit can switch the circuit configuration of the heat medium circulation circuit to the third pattern.
  • the heat medium can be supplied to both the flow channel in which the heat medium flows when switched to the first pattern and the flow channel in which the heat medium flows when switched to the second pattern.
  • the temperature adjusting device 1 of the present embodiment is applied to a hybrid vehicle that obtains a driving force for traveling from an engine (that is, an internal combustion engine) EG and an electric motor for traveling. Further, the hybrid vehicle of the present embodiment is a so-called plug-in hybrid vehicle capable of charging the battery with the electric power supplied from the external power source (for example, commercial power source) when the vehicle is stopped.
  • the external power source for example, commercial power source
  • the driving mode For this type of plug-in hybrid vehicle, you can switch the driving mode. Specifically, when the remaining battery charge SOC of the battery is equal to or greater than a predetermined reference remaining charge KSOC, the EV traveling mode is set.
  • the EV traveling mode is a traveling mode in which the vehicle travels mainly by the driving force of the traveling electric motor.
  • the HV traveling mode is set.
  • the HV traveling mode is a traveling mode in which the vehicle travels mainly by the driving force of the engine EG.
  • the engine EG is operated to assist the driving electric motor.
  • the traveling electric motor is operated to assist the engine EG.
  • the plug-in hybrid vehicle by switching between the EV traveling mode and the HV traveling mode in this way, it is possible to improve the vehicle fuel consumption as compared with an ordinary vehicle that obtains the driving force for vehicle traveling only from the engine EG.
  • the temperature adjustment device 1 of the present embodiment heats the air blown into the vehicle interior, which is the space to be air-conditioned, to heat the vehicle interior. Therefore, the blown air is the temperature control target fluid of the temperature control device 1.
  • the temperature adjusting device 1 also includes a heat medium circulation circuit 10 that circulates the cooling water of the engine EG that is a heat medium.
  • a solution containing ethylene glycol, dimethylpolysiloxane, a nanofluid or the like, an antifreeze liquid, or the like can be adopted.
  • the heat medium circulation circuit 10 includes a cooling water passage 11 of the engine EG, a three-way valve 13, a water-refrigerant heat exchanger 14a of the heat pump cycle 14, a heater core 15, a first pump 16a, a second pump 16b, a radiator 17, and a thermostat 18. Etc. are connected.
  • the cooling water passage 11 of the engine EG is formed in a cylinder block and a cylinder head that form the engine EG. Therefore, when the cooling water is circulated in the cooling water passage 11 during the operation of the engine EG, the cooling water can absorb the exhaust heat of the engine EG to cool the engine EG.
  • the cooling water is heated by the exhaust heat of the engine EG when flowing through the cooling water passage 11. Therefore, the engine EG of the present embodiment serves as a main temperature adjusting unit that adjusts the temperature of the cooling water.
  • the cooling water outlet of the cooling water passage 11 is connected to the inlet of the branch portion 12a.
  • the branch portion 12a is formed of a three-way joint.
  • the branch portion 12a branches the flow of the cooling water flowing out from the cooling water passage 11.
  • One inflow/outlet side of the three-way valve 13 is connected to one outflow port of the branch portion 12a.
  • the cooling water inlet side of the radiator 17 is connected to the other outlet of the branch portion 12a.
  • the three-way valve 13 is a switching unit that switches the flow pattern (in other words, circuit configuration) of the cooling water in the heat medium circulation circuit 10.
  • the three-way valve 13 is an electric switching valve that has three inlets and outlets and connects at least two of the three inlets and outlets. The operation of the three-way valve 13 is controlled by a control signal output from the control device 30 described later. The detailed configuration of the three-way valve 13 will be described later.
  • the cooling water inlet side of the water-refrigerant heat exchanger 14a of the heat pump cycle 14 is connected to another inflow/outflow port of the three-way valve 13.
  • the water-refrigerant heat exchanger 14a heats the cooling water by exchanging heat between the high pressure refrigerant of the heat pump cycle 14 and the cooling water.
  • the heat pump cycle 14 is a vapor compression refrigeration cycle including a compressor, a water-refrigerant heat exchanger 14a, an expansion valve, an evaporator and the like.
  • the heat pump cycle 14 of the present embodiment serves as a sub temperature adjusting unit that adjusts the temperature of the cooling water.
  • the heating capacity of the heat pump cycle 14 is controlled by a control signal output from the control device 30.
  • the cooling water inlet of the heater core 15 is connected to the cooling water outlet of the water-refrigerant heat exchanger 14a.
  • the heater core 15 exchanges heat between the cooling water heated in the cooling water passage 11 of the engine EG or the water-refrigerant heat exchanger 14a of the heat pump cycle 14 and the blown air blown into the vehicle interior from an indoor blower (not shown). To heat the blown air. Therefore, the heater core 15 is a heat exchange part for heating.
  • the cooling water outlet of the heater core 15 is connected to one inlet side of the merging portion 12b.
  • the merging portion 12b is formed of a three-way joint similar to the branching portion 12a.
  • the merging portion 12b merges the flow of the cooling water flowing out from the cooling water outlet of the heater core 15 and the flow of the cooling water flowing out from the cooling water outlet of the radiator 17. Further, the merging unit 12b causes the combined cooling water to flow out to the suction port side of the first pump 16a.
  • the first pump 16a is a water pump that pumps cooling water to the cooling water passage 11 of the engine EG.
  • the first pump 16a is an electric impeller pump that drives an impeller (that is, an impeller) with an electric motor.
  • the number of rotations (pressure feeding capacity) of the first pump 16a is controlled by a control signal output from the control device 30.
  • the first pump 16a does not have a check mechanism that prohibits the cooling water flowing from the discharge port from flowing out from the suction port. Therefore, the first pump 16a simply serves as a cooling water passage when it is not operating. That is, in the non-operating first pump 16a, the cooling water that has flowed in from the discharge port can flow out from the suction port.
  • the cooling water inlet side of the cooling water passage 11 of the engine EG is connected to the discharge port of the first pump 16a. Therefore, the first pump 16a serves as a main pump that operates when at least the cooling water heated in the cooling water passage 11 of the engine EG is pressure-fed to the heater core 15 side.
  • the radiator 17 is an outdoor heat exchanger for exchanging heat between the cooling water flowing out from the other outlet of the branch portion 12a and the outside air. That is, the radiator 17 can radiate the exhaust heat of the engine EG absorbed by the cooling water to the outside air.
  • the radiator 17 has a so-called closed type reserve tank 17a.
  • the radiator 17 is also provided with a water injection port 17b for injecting cooling water into the heat medium circulation circuit 10.
  • the water injection port 17b is arranged at the top of the heat medium circulation circuit 10. Therefore, the cooling water injected from the water injection port 17b flows into the heat medium circulation circuit 10 due to the difference in the lift.
  • the cooling water outlet of the radiator 17 is connected to the other inlet side of the merging portion 12b via a thermostat 18.
  • the thermostat 18 is a flow rate adjusting valve that increases the passage cross-sectional area of the cooling water flow path from the cooling water outlet of the radiator 17 to the confluence portion 12b as the temperature of the cooling water flowing out from the radiator 17 rises.
  • the thermostat 18 is a mechanical mechanism that displaces the valve body by thermowax, the volume of which changes according to the temperature change of the cooling water.
  • the thermostat 18 adjusts the passage cross-sectional area so that the temperature of the cooling water sucked from the radiator 17 side to the first pump 16a approaches a predetermined reference temperature KTw.
  • the thermostat 18 of the present embodiment has a configuration in which the cooling water passage is not completely closed in order to appropriately detect the temperature of the cooling water flowing out from the radiator 17.
  • the heat medium circulation circuit 10 has a parallel passage 10a that guides the cooling water flowing out from the heater core 15 to the other one inflow/outflow side of the three-way valve 13 by bypassing the cooling water passage 11 of the engine EG.
  • the second pump 16b is arranged in the parallel path 10a. The second pump 16b sucks the cooling water flowing out from the heater core 15 and pumps it to the three-way valve 13 side.
  • the basic configuration of the second pump 16b is the same as that of the first pump 16a. Therefore, the second pump 16b simply serves as a cooling water passage when it is not operating. Further, in this embodiment, as the first pump 16a, a pump having a maximum pumping capacity of cooling water larger than that of the second pump 16b is adopted. Therefore, when the first pump 16a and the second pump 16b are rotated at the same rotation speed, the discharge flow rate of the first pump 16a becomes larger than the discharge flow rate of the second pump 16b.
  • the cooling water pumped from the second pump 16b flows into the heater core 15 via the three-way valve 13 and the water-refrigerant heat exchanger 14a. Therefore, the second pump 16b serves as a sub-pump that operates at least when the cooling water heated by the water-refrigerant heat exchanger 14a of the heat pump cycle 14 is pressure-fed to the heater core 15 side.
  • the three-way valve 13 is, as shown in FIG. 1, a cooling water outlet side of the cooling water passage 11 of the engine EG, a cooling water inlet side of the water-refrigerant heat exchanger 14a of the heat pump cycle 14, and one of the parallel passages 10a. Connected to the exit. Then, two or more of these cooling water inlets and outlets are connected.
  • the cooling water outlet of the water-refrigerant heat exchanger 14a is connected to the cooling water inlet side of the heater core 15. Therefore, the three-way valve 13 is indirectly connected to the cooling water inlet side of the heater core 15 via the water-refrigerant heat exchanger 14a.
  • the three-way valve 13 includes a cylindrical rotary valve portion 131, a body portion 132 that houses the rotary valve portion 131, and a drive portion (not shown). doing. 2 to 4 are axially vertical cross sections of the three-way valve 13.
  • the body portion 132 houses the rotary valve portion 131 rotatably around the central axis.
  • the drive unit is an electric actuator (specifically, a stepping motor) that rotates the rotary valve unit 131 around an axis.
  • the drive portion rotationally displaces the rotary valve portion 131 about the axis, as shown in FIG. Can be connected.
  • the cooling water outlet side of the cooling water passage 11 and the cooling water inlet side of the water-refrigerant heat exchanger 14a can be connected.
  • the cooling water outlet of the cooling water passage 11, the cooling water inlet of the water-refrigerant heat exchanger 14a, and one inflow outlet of the parallel passage 10a can be connected to each other.
  • the control device 30 is composed of a well-known microcomputer including a CPU, a ROM, a RAM and the like and its peripheral circuits. Then, various calculations and processing are performed based on the control program stored in the ROM, and the operations of the various controlled devices 13, 14, 16a, 16b and the like connected to the output side are controlled.
  • An engine side temperature sensor 31, a heating unit side temperature sensor 32, etc. are connected to the input side of the control device 30.
  • the detection signals of these sensor groups are input to the control device 30.
  • the engine-side temperature sensor 31 is a temperature detection unit that detects the first temperature T1 at the outlet side of the cooling water passage 11 of the engine EG.
  • the engine side temperature sensor 31 is attached to the engine EG. Therefore, even if the cooling water does not flow through the cooling water passage 11, the temperature of the engine EG can be detected.
  • the heating unit side temperature sensor 32 is a temperature detection unit that detects the second temperature T2 of the cooling water flowing out from the water-refrigerant heat exchanger 14a.
  • an operation panel (not shown) is connected to the input side of the control device 30.
  • An operation signal is input to the control device 30 from an operation switch provided on the operation panel.
  • ⁇ Operation switches include heating switch, air volume setting switch, temperature setting switch, etc.
  • the heating switch is a request unit that requests execution or stop of heating.
  • the air volume setting switch is a setting unit that sets the air volume of the air blown into the vehicle interior.
  • the temperature setting switch is a setting unit that sets the temperature inside the vehicle compartment.
  • control device 30 of the present embodiment is integrally configured with a control unit that controls various control target devices connected to the output side. Therefore, in the control device 30, the configuration (hardware and software) that controls the operation of each control target device serves as a control unit that controls the operation of each control target device.
  • the configuration for controlling the pumping capacity of the first pump 16a constitutes the first pump control unit.
  • the configuration for controlling the pumping capacity of the second pump 16b constitutes a second pump control section.
  • the configuration that controls the operation of the heat pump cycle 14 constitutes a heat pump cycle control unit.
  • the operation of the temperature adjusting device 1 of the present embodiment having the above configuration will be described.
  • the temperature adjustment device 1 of the present embodiment in order to heat the vehicle interior, it is possible to switch between operation in the auxiliary heat source mode and operation in the main heat source mode.
  • the vehicle runs in the EV running mode.
  • the EV traveling mode is a traveling mode in which the vehicle is traveling mainly by the driving force of the traveling electric motor, and therefore the engine EG is rarely operated. Therefore, the first temperature T1 is unlikely to rise when traveling in the EV traveling mode.
  • the control device 30 performs heating in the auxiliary heat source mode when execution of heating of the passenger compartment is requested when the first temperature T1 is lower than the predetermined first reference temperature KT1.
  • the heat pump cycle 14 which is the sub-temperature adjusting unit is operated to perform heating by using the cooling water heated by the water-refrigerant heat exchanger 14a as a heat source.
  • the HV traveling mode is a traveling mode in which the vehicle travels mainly by the driving force of the engine EG. Therefore, when traveling in the HV traveling mode, the first temperature T1 is higher than that in the EV traveling mode.
  • the control device 30 performs heating in the main heat source mode.
  • the heat pump cycle 14 that is the sub temperature adjusting unit is stopped, and heating is performed using the cooling water heated in the cooling water passage 11 of the engine EG that is the main temperature adjusting unit as the heat source.
  • the first reference temperature KT1 is set so that the temperature of the cooling water is a temperature that can be sufficiently used as a heat source for heating the passenger compartment.
  • each operation mode will be described.
  • the control device 30 switches the flow pattern of the cooling water in the heat medium circulation circuit 10 to the first pattern.
  • the controller 30 connects the one inflow/outlet side of the parallel path 10a and the cooling water inlet side of the water-refrigerant heat exchanger 14a so as to connect the three-way valve 13 to each other. Control operation. As a result, the parallel passage 10a is opened, and the cooling water flowing out from the heater core 15 can flow into the parallel passage 10a.
  • control device 30 operates the heat pump cycle 14. At this time, the control device 30 adjusts the heating capacity of the heat pump cycle 14 so that the second temperature approaches the target temperature.
  • the target temperature is determined based on the set temperature set by the occupant using the temperature setting switch, the outside air temperature, and the like, with reference to the control map stored in advance by the control device 30.
  • control device 30 stops the first pump 16a and operates the second pump 16b so as to exert a predetermined pumping capacity. Therefore, in the heat medium circulation circuit 10 of the first pattern, the cooling water pumped from the second pump 16b circulates between the cooling water passage of the water-refrigerant heat exchanger 14a and the heater core 15.
  • the cooling water pumped from the second pump 16b flows into the cooling water passage of the water-refrigerant heat exchanger 14a via the three-way valve 13.
  • the cooling water that has flowed into the cooling water passage of the water-refrigerant heat exchanger 14a is heated by exchanging heat with the high-pressure refrigerant of the heat pump cycle 14.
  • the cooling water heated by the water-refrigerant heat exchanger 14a flows into the heater core 15.
  • the cooling water that has flowed into the heater core 15 exchanges heat with the air blown from the indoor blower to radiate heat. Thereby, the blown air is heated.
  • the cooling water flowing out from the heater core 15 flows into the parallel path 10a, is sucked into the second pump 16b, and is pumped again.
  • the blast air heated by the heater core 15 can be blown into the vehicle interior to heat the vehicle interior even when the engine EG is stopped.
  • FIG. 5 is a drawing corresponding to FIG. 1, and shows the flow of the cooling water by a thick solid line arrow. Further, in FIG. 5, for clarity of illustration, illustration of signal lines and power lines connecting the control device 30 and various control target devices, and signal lines connecting the control device 30 and various sensors is omitted. doing. This also applies to the overall configuration diagram for explaining the following flow pattern.
  • (B) Main heat source mode In the main heat source mode, the control device 30 switches the flow pattern of the cooling water in the heat medium circulation circuit 10 to the second pattern.
  • control device 30 controls the three-way valve 13 to connect the cooling water outlet side of the cooling water passage 11 and the cooling water inlet side of the water-refrigerant heat exchanger 14a. Control operation. As a result, the parallel path 10a is closed.
  • control device 30 stops the heat pump cycle 14. Further, the control device 30 operates the first pump 16a and stops the second pump 16b so as to exert a predetermined pressure feeding capability. Therefore, in the heat medium circulation circuit 10 of the second pattern, the cooling water pumped from the first pump 16a circulates between the cooling water passage 11 of the engine EG and the heater core 15.
  • the cooling water pumped from the first pump 16a flows into the cooling water passage 11 of the engine EG, as shown by the thick solid line in FIG.
  • the cooling water flowing into the cooling water passage 11 of the engine EG absorbs the exhaust heat of the engine EG and its temperature rises. As a result, the engine EG is cooled.
  • the cooling water flowing out from the cooling water passage 11 of the engine EG flows into the cooling water passage of the water-refrigerant heat exchanger 14a via the three-way valve 13.
  • the heat pump cycle 14 is stopped. Therefore, the cooling water flowing into the cooling water passage of the water-refrigerant heat exchanger 14a flows out without being heated.
  • the cooling water flowing out from the water-refrigerant heat exchanger 14a flows into the heater core 15.
  • the cooling water that has flowed into the heater core 15 exchanges heat with the air blown from the indoor blower to radiate heat. Thereby, the blown air is heated.
  • the cooling water that has flowed out of the heater core 15 is sucked into the first pump 16a via the merging portion 12b and is pressure-fed again.
  • the first pump 16a is operating. Therefore, the passage cross-sectional area of the thermostat 18 is adjusted according to the temperature of the cooling water flowing out from the radiator 17. Therefore, a part of the cooling water branched at the branch portion 12a flows into the radiator 17 as shown by the thin arrow in FIG. Then, the temperature of the cooling water that flows out from the radiator 17 and is sucked into the first pump 16a approaches the reference temperature KTw.
  • the blast air heated by the heater core 15 can be blown into the vehicle interior to heat the vehicle interior.
  • the temperature control device 1 of the present embodiment includes the three-way valve 13
  • the flow patterns of the cooling water in the heat medium circulation circuit 10 are set to the first pattern and the second pattern when heating the vehicle interior. You can switch to the pattern and. That is, even if the heat medium circulation circuit 10 does not have a check valve, the flow patterns can be switched.
  • the temperature of the cooling water can be sufficiently utilized as a heat source for heating the passenger compartment. It can be reliably adjusted to the temperature. As a result, the temperature of the blown air can be appropriately adjusted by the heater core 15 regardless of the operating state of the engine EG.
  • the temperature adjusting device 1 of the present embodiment can be operated in the air bleeding mode as the operation mode for injecting the cooling water into the heat medium circulation circuit 10.
  • the air bleeding mode is executed when a service tool (not shown) is connected to a dedicated connector provided in the control device 30. Note that the service tool does not have to be always provided in the vehicle, and may be prepared in a maintenance shop or the like that injects cooling water.
  • the air bleeding mode will be described below.
  • (C) Air bleeding mode First, prior to the air bleeding mode, cooling water is injected from the water injection port 17b of the radiator 17. As described above, the water injection port 17b is arranged at the top of the heat medium circulation circuit 10. Therefore, the injected cooling water flows into almost the entire area of the heat medium circulation circuit 10 due to the difference in head. After that, by connecting the service tool to the dedicated connector, the operation in the air bleeding mode is executed.
  • control device 30 switches the cooling water flow pattern in the heat medium circulation circuit 10 to the third pattern.
  • the controller 30 connects the cooling water outlet of the cooling water passage 11, the cooling water inlet of the water-refrigerant heat exchanger 14a, and one inflow outlet of the parallel passage 10a to each other.
  • the operation of the three-way valve 13 is controlled so that As a result, the parallel passage 10a opens, and the cooling water pumped by the first pump 16a can flow into both the water-refrigerant heat exchanger 14a and the parallel passage 10a.
  • control device 30 stops the heat pump cycle 14. Further, the control device 30 operates the first pump 16a and stops the second pump 16b so as to exert a predetermined pressure feeding capability.
  • the cooling water pumped by the first pump 16a can flow from the three-way valve 13 into the water-refrigerant heat exchanger 14a. Further, the cooling water pumped by the first pump 16a can flow from the three-way valve 13 into the parallel passage 10a. At this time, the cooling water flowing from the three-way valve 13 into the parallel passage 10a flows backward in the parallel passage 10a with respect to the second pattern.
  • the cooling water pumped by the first pump 16a flows through the cooling water when switched to the first pattern, and the cooling water flows when switched to the second pattern. Can be supplied to both of the flow paths.
  • the cooling water injected from the water injection port 17b of the radiator 17 is sucked into the first pump 16a.
  • the cooling water pumped from the first pump 16a flows through the cooling water passage 11 of the engine EG and is branched at the branch portion 12a.
  • One flow of the cooling water branched at the branch portion 12a is further divided by the three-way valve 13.
  • the one cooling water branched by the three-way valve 13 flows in the order of the water-refrigerant heat exchanger 14 a and the heater core 15.
  • the other cooling water branched by the three-way valve 13 flows through the parallel path 10a.
  • the cooling water flowing from the discharge port of the second pump 16b flows backward through the second pump 16b and flows out from the suction port.
  • the cooling water flowing out of the heater core 15 merges with the cooling water flowing out of the parallel path 10a, and is sucked into the first pump 16a via the merging portion 12b.
  • the other cooling water branched at the branch portion 12a flows into the radiator 17.
  • excess cooling water in the heat medium circulation circuit 10 is stored in the reserve tank 17a.
  • the cooling water flowing out from the radiator 17 is sucked into the first pump 16a via the confluence portion 12b.
  • the three-way valve 13 can switch the flow pattern of the cooling water in the heat medium circulation circuit 10 to the third pattern.
  • the cooling water can be simultaneously supplied to both the flow channel through which the cooling water flows when switched to the first pattern and the flow channel through which the cooling water flows when switched to the second pattern.
  • the heat medium circulation circuit 10 of the present embodiment does not have a check valve. Therefore, in the temperature control device 1 of the present embodiment, it is possible to prevent air from remaining in the heat medium circulation circuit 10 when pouring cooling water into the heat medium circulation circuit 10.
  • the temperature control device 1 of the present embodiment is provided with the parallel path 10a and employs the three-way valve 13 that opens and closes the parallel path 10a as the switching unit. According to this, the flow pattern of the cooling water in the heat medium circulation circuit 10 can be reliably switched to the above-described first to third patterns.
  • the flow direction of the cooling water in the parallel path 10a in the first pattern and the flow direction of the cooling water in the parallel path 10a in the third pattern are different directions. Thereby, the flow direction of the cooling water in the heater core 15 in the first pattern and the flow direction of the cooling water in the heater core 15 in the second pattern can be made the same direction.
  • the second pump 16b which serves as a cooling water passage when not in operation is arranged in the parallel passage 10a. Therefore, even if the heat medium circulation circuit 10 is switched between the first pattern and the second pattern in order to heat the vehicle interior, the cooling water does not flow backward through the second pump 16b. That is, when heating the vehicle interior, the second pump 16b does not increase the pressure loss of the cooling water.
  • the first pump 16a one having a maximum pumping capacity larger than that of the second pump 16b is adopted. According to this, when switching to the third pattern, it is possible to pump the cooling water so that the first pump 16a having a high pumping capability is used to cause the second pump 16b to flow backward. Therefore, it is possible to prevent air from remaining in the second pump 16b.
  • the three-way valve 13 having the rotary valve portion 131 is adopted as the switching portion. According to this, even if there is a pressure difference in the cooling water flowing in and out of each of the outflow and outflow ports of the three-way valve 13, the operation of the rotary valve portion 131 is hardly affected. That is, the first to third patterns can be switched without causing an unnecessary increase in driving force.
  • the three-way valve 13 having the rotary valve portion 131 is adopted, it is possible to easily realize a switching portion that connects two or all of the three outflow inlets.
  • the switching unit is changed from the first embodiment.
  • the first opening/closing valve 13a and the second opening/closing valve 13b are used as the switching unit.
  • the first on-off valve 13a and the second on-off valve 13b are electromagnetic valves that are opened and closed by a control voltage output from the control device 30.
  • the first opening/closing valve 13a is arranged in the cooling water passage extending from the branch portion 12a to the connecting portion 12c at one inflow/outlet side of the parallel passage 10a.
  • the connecting portion 12c is formed of a three-way joint similar to the branching portion 12a and the joining portion 12b.
  • the second opening/closing valve 13b is arranged in the cooling water passage extending from the discharge port of the second pump 16b to the connecting portion 12c.
  • Other configurations are similar to those of the first embodiment.
  • the operation of the temperature adjusting device 1 of the present embodiment having the above configuration will be described.
  • the auxiliary heat source mode, the main heat source mode, and the air bleeding mode can be executed.
  • each operation mode will be described.
  • the control device 30 closes the first on-off valve 13a and opens the second on-off valve 13b, as shown in FIG.
  • Other operations are similar to those of the auxiliary heat source mode of the first embodiment. Therefore, even in the auxiliary heat source mode of this embodiment, the flow pattern of the cooling water in the heat medium circulation circuit 10 can be switched to the first pattern.
  • (B) Main heat source mode In the main heat source mode, the control device 30 opens the first on-off valve 13a and closes the second on-off valve 13b, as shown in FIG. Other operations are similar to those in the main heat source mode of the first embodiment. Therefore, even in the main heat source mode of this embodiment, the flow pattern of the cooling water in the heat medium circulation circuit 10 can be switched to the second pattern.
  • (C) Air bleeding mode In the air bleeding mode, the control device 30 opens the first on-off valve 13a and the second on-off valve 13b, as shown in FIG. Other operations are the same as in the air bleeding mode of the first embodiment. Therefore, even in the air bleeding mode of this embodiment, the flow pattern of the cooling water in the heat medium circulation circuit 10 can be switched to the third pattern.
  • the temperature adjusting device 1 of the present embodiment operates in the same manner as the temperature adjusting device 1 described in the first embodiment, and the same effect can be obtained.
  • the second pump 16b is arranged in the cooling water passage extending from the three-way valve 13 to the cooling water inlet of the water-refrigerant heat exchanger 14a.
  • the second pump 16b is arranged so as to suck the cooling water flowing out from the three-way valve 13 and send it to the cooling water inlet side of the water-refrigerant heat exchanger 14a under pressure.
  • the temperature adjusting device 1 of the present embodiment operates in the same manner as the temperature adjusting device 1 described in the first embodiment, and the same effect can be obtained.
  • the second pump 16b may be operated even in the air bleeding mode.
  • the temperature adjusting device 1a is applied to a vehicle air conditioning device 20 shown in the overall configuration diagram of FIG. 14
  • the vehicle air conditioner 20 heats the passenger compartment by using the heat medium heated by the heat pump cycle 14 as a heat source. Further, the vehicle air conditioner 20 cools the vehicle interior by using the heat medium cooled by the heat pump cycle 14 as a cold heat source.
  • the heat pump cycle 14 has a compressor 14d, a water-refrigerant heat exchanger 14a as a radiator, an expansion valve 14b, and a chiller 14c as an evaporator.
  • the compressor 14d is an electric compressor that sucks low-pressure refrigerant, compresses it, and discharges it.
  • the water-refrigerant heat exchanger 14a is a main temperature adjusting unit that heats the heat medium by exchanging heat between the high-pressure refrigerant discharged from the compressor 14d and the heat medium pumped from the first pump 16a.
  • the expansion valve 14b is a thermal expansion valve that decompresses the high-pressure refrigerant flowing out of the water-refrigerant heat exchanger 14a until it becomes a low-pressure refrigerant.
  • the chiller 14c is a sub-temperature adjusting unit that cools the heat medium by exchanging heat between the low pressure refrigerant decompressed by the expansion valve 14b and the heat medium pumped from the second pump 16b.
  • the heat medium circulation circuit 10 of the present embodiment has the first sub circulation path 101 for circulating the heat medium pumped from the first pump 16a between the water-refrigerant heat exchanger 14a and the heater core 15. There is. Further, the heat medium circulation circuit 10 has a second auxiliary circulation path 102 for circulating the heat medium pumped from the second pump 16b between the chiller 14c and the cooler core 15a.
  • the heater core 15 is a heat exchanger that heats the blown air by exchanging heat between the heat medium heated by the water-refrigerant heat exchanger 14a and the blown air blown into the passenger compartment from an indoor blower (not shown).
  • the cooler core 15a is a heat exchanger that cools the blown air by exchanging heat between the heat medium cooled by the chiller 14c and the blown air blown into the vehicle interior from the indoor blower.
  • an outdoor heat exchanger 19 is connected to the first sub circulation path 101 via a three-way valve 13. More specifically, in the heat medium circulation circuit 10, the heat medium flowing out from the water-refrigerant heat exchanger 14a flows into at least one of the heater core 15 and the outdoor heat exchanger 19 via the three-way valve 13. Further, the first pump 16a sucks the heat medium flowing out from at least one of the heater core 15 and the outdoor heat exchanger 19.
  • the outdoor heat exchanger 19 is connected to the second auxiliary circulation path 102 via the second three-way valve 13c. More specifically, in the heat medium circulation circuit 10, the heat medium flowing out from the chiller 14c flows into at least one of the cooler core 15a and the outdoor heat exchanger 19 via the second three-way valve 13c. Further, the second pump 16b sucks the heat medium flowing out from at least one of the cooler core 15a and the outdoor heat exchanger 19.
  • both the first three-way valve 13 and the second three-way valve 13c constitute a switching unit that switches the circuit configuration of the heat medium circulation circuit 10.
  • the basic structure of the outdoor heat exchanger 19 is the same as that of the radiator 17 described in the first embodiment. Therefore, the outdoor heat exchanger 19 is provided with a water injection port 19b for injecting cooling water into the heat medium circulation circuit 10.
  • the water injection port 19b is arranged at the top of the heat medium circulation circuit 10.
  • the vehicle air conditioner 20 of this embodiment can perform heating and cooling of the vehicle interior.
  • the heating mode and the cooling mode will be described below.
  • (A) Heating Mode In the heating mode, the control device 30 operates the heat pump cycle 14. Further, the control device 30 operates both the first pump 16a and the second pump 16b.
  • control device 30 controls the operation of the first three-way valve 13 so that the heat medium pumped from the first pump 16a circulates between the water-refrigerant heat exchanger 14a and the heater core 15. Further, the control device 30 controls the operation of the second three-way valve 13c so that the heat medium pumped from the second pump 16b circulates between the chiller 14c and the outdoor heat exchanger 19.
  • the high-pressure refrigerant discharged from the compressor 14d radiates heat to the heat medium on the side of the first sub circulation path 101, which is pumped from the first pump 16a by the water-refrigerant heat exchanger 14a. As a result, the heat medium on the first sub circulation path 101 side is heated.
  • the heat medium heated by the water-refrigerant heat exchanger 14a flows into the heater core 15 via the first three-way valve 13.
  • the heat medium flowing into the heater core 15 exchanges heat with the blown air and radiates heat to the blown air. Thereby, the blown air is heated.
  • the heat medium flowing out from the heater core 15 is sucked into the first pump 16a and again sent under pressure to the water-refrigerant heat exchanger 14a.
  • the low-pressure refrigerant whose pressure has been reduced by the expansion valve 14b absorbs heat from the heat medium on the side of the second auxiliary circulation path 102 that is pressure-fed from the second pump 16b when it is evaporated by the chiller 14c. As a result, the heat medium on the second sub circulation path 102 side is cooled.
  • the heat medium cooled by the chiller 14c flows into the outdoor heat exchanger 19 via the second three-way valve 13c.
  • the heat medium flowing into the outdoor heat exchanger 19 exchanges heat with the outside air and absorbs heat from the outside air. In other words, the outdoor heat exchanger 19 cools the outside air.
  • the heat medium that has flowed out of the outdoor heat exchanger 19 is sucked into the second pump 16b and is again pressure-fed to the chiller 14c.
  • (B) Cooling Mode In the cooling mode, the control device 30 operates the heat pump cycle 14. Further, the control device 30 operates both the first pump 16a and the second pump 16b.
  • control device 30 controls the operation of the first three-way valve 13 so that the heat medium pumped from the first pump 16a circulates between the water-refrigerant heat exchanger 14a and the outdoor heat exchanger 19. To do. Further, the control device 30 controls the operation of the second three-way valve 13c so that the heat medium pumped from the second pump 16b circulates between the chiller 14c and the cooler core 15a.
  • the high-pressure refrigerant discharged from the compressor 14d radiates heat to the heat medium on the first sub circulation path 101 side, which is pumped from the first pump 16a in the water-refrigerant heat exchanger 14a. As a result, the heat medium on the first sub circulation path 101 side is heated.
  • the heat medium heated by the water-refrigerant heat exchanger 14a flows into the outdoor heat exchanger 19 via the first three-way valve 13.
  • the heat medium that has flowed into the outdoor heat exchanger 19 exchanges heat with the outside air and radiates heat to the outside air.
  • the outdoor heat exchanger 19 heats the outside air.
  • the heat medium flowing out from the outdoor heat exchanger 19 is sucked into the first pump 16a and is again sent to the water-refrigerant heat exchanger 14a under pressure.
  • the low-pressure refrigerant whose pressure has been reduced by the expansion valve 14b absorbs heat from the heat medium on the side of the second auxiliary circulation path 102 that is pressure-fed from the second pump 16b when it is evaporated by the chiller 14c. As a result, the heat medium on the second sub circulation path 102 side is cooled.
  • the heat medium cooled by the chiller 14c flows into the cooler core 15a via the second three-way valve 13c.
  • the heat medium flowing into the cooler core 15a exchanges heat with the blown air and absorbs heat from the blown air. Thereby, the blown air is cooled.
  • the heat medium flowing out from the cooler core 15a is sucked into the second pump 16b and again sent under pressure to the chiller 14c.
  • the heat absorbed by the heat medium on the second sub circuit 102 side from the blower air in the cooler core 15a is moved to the heat medium on the first sub circuit 101 side by the heat pump cycle 14.
  • the heat transferred to the heat medium on the side of the first sub circulation path 101 is radiated to the outside air by the outdoor heat exchanger 19. Therefore, the air in the vehicle compartment can be cooled by blowing the blast air cooled by the cooler core 15a into the vehicle interior.
  • the flow pattern of the cooling water in the heat medium circulation circuit 10 is switched by the first three-way valve 13 and the second three-way valve 13c to heat and cool the vehicle interior. be able to.
  • the temperature adjusting device 1a of the present embodiment can be operated in the air bleeding mode as in the first embodiment.
  • the heat medium is injected from the water injection port 19b of the outdoor heat exchanger 19 prior to the air bleeding mode.
  • the control device 30 stops the heat pump cycle 14. Further, the control device 30 operates either the first pump 16a or the second pump 16b.
  • control device 30 controls the operation of the first three-way valve 13 so that the heat medium pumped from the first pump 16a flows into both the heater core 15 and the outdoor heat exchanger 19. Further, the control device 30 controls the operation of the second three-way valve 13c so that the heat medium pumped from the second pump 16b flows into both the cooler core 15a and the outdoor heat exchanger 19.
  • the air bleeding mode the heat medium pumped by at least one of the first pump 16a and the second pump 16b is divided into a flow path through which the heat medium flows in the cooling mode and a flow path through which the heat medium flows in the heating mode. It becomes possible to supply to both. Therefore, the air bleeding mode can be performed also in the heat medium circulation circuit 10 of the present embodiment.
  • the outdoor heat exchanger 19 of the present embodiment in the cooling mode, the outside air is heated by the heat medium heated by the water-refrigerant heat exchanger 14a which is the main temperature adjusting unit. Can be expressed. Further, in the outdoor heat exchanger 19 of the present embodiment, as described above, it can be said that in the heating mode, the outside air is cooled by the heat medium cooled by the chiller 14c that is the sub-temperature adjusting unit. ..
  • the outside air is the fluid whose temperature is to be adjusted and the outdoor heat exchanger 19 is the heat exchange section.
  • the heat medium circulation circuit 10 in the heating mode is switched to the first pattern in which the heat medium pumped by the second pump 16b is circulated between the chiller 14c and the outdoor heat exchanger 19.
  • the heat medium circulation circuit 10 in the cooling mode is switched to the second pattern in which the heat medium pumped by the first pump 16a is circulated between the water-refrigerant heat exchanger 14a and the outdoor heat exchanger 19. ..
  • the heat medium circulation circuit 10 in the air bleeding mode includes a flow path through which the heat medium flows when the heat medium pumped by at least one of the first pump 16a and the second pump 16b is switched to the first pattern.
  • the second pattern it is switched to the third pattern in which the heat medium can be supplied to both of the flow paths.
  • the temperature of the temperature adjustment target fluid can be adjusted appropriately. Furthermore, it is possible to prevent air from remaining in the heat medium circulation circuit 10 when pouring the heat medium into the heat medium circulation circuit 10.
  • the temperature adjusting devices 1 and 1a according to the present disclosure are used to perform air conditioning in a vehicle, but the application targets of the temperature adjusting devices 1 and 1a are not limited to this.
  • the present invention is widely applicable to a temperature adjustment device that changes the flow pattern of the heat medium in the heat medium circulation circuit 10 in order to adjust the temperature of the temperature adjustment target fluid.
  • the heat pump cycle 14 is adopted as the sub temperature adjusting unit
  • the main temperature adjusting unit and the sub temperature adjusting unit are not limited to those disclosed in the above embodiments.
  • an electric heater that generates heat when supplied with electric power may be used as the sub-temperature adjustment unit of the first embodiment.
  • a Peltier element may be used instead of the heat pump cycle 14. Then, the surface on the heat radiation side may be used as the main temperature adjustment section, and the surface on the heat absorption side may be used as the sub temperature adjustment section. Furthermore, in the fifth embodiment, the chiller 14c serves as the main temperature adjusting unit, the second pump 16b serves as the main pump, the water-refrigerant heat exchanger 14a serves as the sub-temperature adjusting unit, and the first pump 16a serves as the sub-pump. Good.
  • the main temperature adjusting unit and the sub temperature adjusting unit are not limited to those that heat the heat medium.
  • the heat medium may be cooled like the chiller 14c of the fifth embodiment.
  • the operation panel may be provided with a dedicated switch for requesting execution of the air bleeding mode.
  • the air bleeding mode may be executed by a combination of long pressing of existing switches and simultaneous pressing of a plurality of switches.
  • the so-called racing may be performed in which the engine is operated at a relatively low rotation speed during the water injection work or the air bleeding mode described in the above embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2019/049725 2019-01-23 2019-12-19 温度調整装置 Ceased WO2020153060A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112019006723.0T DE112019006723T5 (de) 2019-01-23 2019-12-19 Temperatureinstellungsvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019009393A JP7225830B2 (ja) 2019-01-23 2019-01-23 温度調整装置
JP2019-009393 2019-01-23

Publications (1)

Publication Number Publication Date
WO2020153060A1 true WO2020153060A1 (ja) 2020-07-30

Family

ID=71735705

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/049725 Ceased WO2020153060A1 (ja) 2019-01-23 2019-12-19 温度調整装置

Country Status (3)

Country Link
JP (1) JP7225830B2 (enrdf_load_stackoverflow)
DE (1) DE112019006723T5 (enrdf_load_stackoverflow)
WO (1) WO2020153060A1 (enrdf_load_stackoverflow)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7125455B2 (ja) * 2020-09-24 2022-08-24 本田技研工業株式会社 温調装置及び車両
JP7158445B2 (ja) * 2020-09-24 2022-10-21 本田技研工業株式会社 温調装置及び車両
KR102669124B1 (ko) 2021-11-08 2024-05-23 엘지전자 주식회사 에너지 저장장치
JP7609915B2 (ja) 2023-03-31 2025-01-07 本田技研工業株式会社 バッテリ温度調整装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02120120A (ja) * 1988-10-28 1990-05-08 Nippon Denso Co Ltd 自動車用空気調和装置
JP2001260640A (ja) * 2000-03-21 2001-09-26 Calsonic Kansei Corp 車両用暖房装置
JP2017065635A (ja) * 2015-10-02 2017-04-06 株式会社デンソー 車両用熱管理装置
JP2018149925A (ja) * 2017-03-13 2018-09-27 トヨタ自動車株式会社 車両用熱管理装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007223418A (ja) 2006-02-22 2007-09-06 Toyota Motor Corp 車両用熱利用装置
JP6953201B2 (ja) 2017-06-28 2021-10-27 キヤノン株式会社 光学装置及び画像形成装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02120120A (ja) * 1988-10-28 1990-05-08 Nippon Denso Co Ltd 自動車用空気調和装置
JP2001260640A (ja) * 2000-03-21 2001-09-26 Calsonic Kansei Corp 車両用暖房装置
JP2017065635A (ja) * 2015-10-02 2017-04-06 株式会社デンソー 車両用熱管理装置
JP2018149925A (ja) * 2017-03-13 2018-09-27 トヨタ自動車株式会社 車両用熱管理装置

Also Published As

Publication number Publication date
DE112019006723T5 (de) 2021-09-30
JP2020117048A (ja) 2020-08-06
JP7225830B2 (ja) 2023-02-21

Similar Documents

Publication Publication Date Title
US10532630B2 (en) HVAC system of vehicle
US8959936B2 (en) Method for operation of an HVAC system
JP5526982B2 (ja) 内燃機関冷却装置
WO2019138731A1 (ja) 熱管理システム
WO2020153060A1 (ja) 温度調整装置
KR101703667B1 (ko) 차량용 공조장치
US20210387506A1 (en) In-vehicle temperature control system
WO2015011918A1 (ja) 車両用空調装置
CN106285906A (zh) 内燃机的冷却装置
KR20210009488A (ko) 차량용 열관리시스템 및 통합열관리모듈
US11780293B2 (en) In-vehicle temperature control system
JP5633199B2 (ja) 内燃機関の冷却システム
JP7042362B2 (ja) 温度調整回路
US11618301B2 (en) Vehicle air conditioner
JP2013160058A (ja) 内燃機関温度調整システム
US20040187505A1 (en) Integrated cooling system
WO2017163659A1 (ja) 車両用空調装置
WO2023024604A1 (zh) 热管理系统及其控制方法
CN223199818U (zh) 热管理系统及车辆
US20240270045A1 (en) Temperature control system
CN119175975A (zh) 热管理系统及车辆
GB2581474A (en) Engine cooling circuit and method of cooling an engine
WO2023243367A1 (ja) 車両用空調装置
WO2025070100A1 (ja) 温調装置
WO2023162549A1 (ja) 熱マネジメントシステム

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19911797

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 19911797

Country of ref document: EP

Kind code of ref document: A1