WO2014175254A1 - 車両用空気調和装置 - Google Patents
車両用空気調和装置 Download PDFInfo
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- WO2014175254A1 WO2014175254A1 PCT/JP2014/061266 JP2014061266W WO2014175254A1 WO 2014175254 A1 WO2014175254 A1 WO 2014175254A1 JP 2014061266 W JP2014061266 W JP 2014061266W WO 2014175254 A1 WO2014175254 A1 WO 2014175254A1
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- radiator
- air
- heat medium
- heat
- heating
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H1/2215—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant the heat being derived from electric heaters
- B60H1/2218—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant the heat being derived from electric heaters controlling the operation of electric heaters
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00357—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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00357—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
- B60H1/00392—Air-conditioning arrangements specially adapted for particular vehicles for vehicles having an electrical drive, e.g. hybrid or fuel cell for electric vehicles having only electric drive means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
- B60H1/14—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant otherwise than from cooling liquid of the plant, e.g. heat from the grease oil, the brakes, the transmission unit
- B60H1/143—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant otherwise than from cooling liquid of the plant, e.g. heat from the grease oil, the brakes, the transmission unit the heat being derived from cooling an electric component, e.g. electric motors, electric circuits, fuel cells or batteries
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L1/00—Supplying electric power to auxiliary equipment of vehicles
- B60L1/02—Supplying electric power to auxiliary equipment of vehicles to electric heating circuits
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H2001/2228—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant controlling the operation of heaters
- B60H2001/2237—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant controlling the operation of heaters supplementary heating, e.g. during stop and go of a vehicle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H2001/2228—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant controlling the operation of heaters
- B60H2001/224—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant controlling the operation of heaters automatic operation, e.g. control circuits or methods
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H2001/2246—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant obtaining information from a variable, e.g. by means of a sensor
- B60H2001/2256—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant obtaining information from a variable, e.g. by means of a sensor related to the operation of the heater itself, e.g. flame detection or overheating
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
- B60H2001/2259—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant output of a control signal
- B60H2001/2265—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant output of a control signal related to the quantity of heat produced by the heater
Definitions
- the present invention relates to a heat pump type air conditioner that air-conditions the interior of a vehicle, and more particularly to an air conditioner that can be applied to a hybrid vehicle or an electric vehicle.
- an air conditioner that can be applied to such a vehicle, a compressor that compresses and discharges the refrigerant, a radiator (condenser) that is provided on the vehicle interior side to dissipate the refrigerant, and the vehicle interior side
- a heat absorber evaporator
- an outdoor heat exchanger that is provided outside the passenger compartment to dissipate or absorb the refrigerant, and dissipates the refrigerant discharged from the compressor in the radiator
- a heating mode in which the heat dissipated in the radiator is absorbed in the outdoor heat exchanger, a dehumidification mode in which the refrigerant discharged from the compressor is dissipated in the radiator, and the refrigerant dissipated in the radiator is absorbed in the heat absorber
- compression A refrigerant that has been radiated in an outdoor heat exchanger and is switched and executed in each cooling mode in
- an injection circuit that diverts the refrigerant that has flowed out of the radiator, decompresses the diverted refrigerant, exchanges heat with the refrigerant that has left the radiator, and returns the refrigerant to the middle of compression.
- the refrigerant discharged from the compressor is increased, and the heating capacity of the radiator is improved.
- the air conditioning apparatus as described above has a problem that when the outdoor heat exchanger is frosted, heat cannot be absorbed from the outside air, so that the required heating capacity cannot be obtained. Moreover, since the temperature of the refrigerant
- the present invention has been made to solve the above-described conventional technical problems, and an object of the present invention is to efficiently and comfortably heat the vehicle interior in a so-called heat pump type air conditioner.
- the vehicle air conditioner of the present invention heats the compressor that compresses the refrigerant, the air flow passage through which the air supplied to the vehicle interior flows, and the air that dissipates the refrigerant and is supplied from the air flow passage to the vehicle interior.
- a heat sink a heat absorber for cooling the air supplied to the vehicle interior from the air flow passage by absorbing the refrigerant
- an outdoor heat exchanger provided outside the vehicle cabin for radiating or absorbing heat
- control means And a heating mode in which at least the refrigerant discharged from the compressor is radiated by the radiator by the control means, and the radiated refrigerant is decompressed and then absorbed by the outdoor heat exchanger.
- an auxiliary heating means for heating the air supplied to the passenger compartment from the air flow passage, and the control means performs the heating by the auxiliary heating means when the heating capacity by the radiator is insufficient. .
- the control means compares the required heating capacity Qtgt, which is the required heating capacity of the radiator, with the heating capacity Qhp generated by the radiator.
- a feature in which the capacity Qhp is less than the required heating capacity Qtgt is supplemented by heating of the auxiliary heating means.
- the heating capacity Qhp is the non-frosting heating capacity QhpNI generated by the radiator when the outdoor heat exchanger is not frosted.
- the heating capacity QhpNI is less than the required heating capacity Qtgt, and is supplemented by heating of the auxiliary heating means.
- an air conditioning apparatus for a vehicle wherein the control means, when the actual heating capacity Qhpr actually generated by the radiator is smaller than the non-frosting heating capacity QhpNI, A difference between the capacity QhpNI and the actual heating capacity Qhpr is added to heat by auxiliary heating means.
- the control means in the invention of claim 3 or claim 4 is such that the actual heating capability Qhpr actually generated by the radiator is smaller than the non-frosting heating capability QhpNI,
- the difference between the non-frosting heating capacity QhpNI and the actual heating capacity Qhpr is larger than a predetermined value, the compressor is stopped and the auxiliary heating means is controlled by the required heating capacity Qtgt.
- the vehicle air conditioner according to a sixth aspect of the present invention is the air conditioning apparatus for a vehicle according to the fourth or fifth aspect, wherein the control means indicates the temperature of the air flowing out from the radiator and the amount of air passing through the radiator.
- the actual heating capacity Qhpr is calculated based on any one of the above, or a combination thereof, the specific heat of the air flowing into the radiator, and an index indicating the density of the air.
- the vehicle air conditioner according to any one of the third to sixth aspects, wherein the control means includes the temperature of the air flowing into the radiator, the temperature of the air flowing out of the radiator, and the heat dissipation.
- the required heating capacity Qtgt is calculated based on any one or a combination of indicators indicating the amount of air passing through the radiator, a specific heat of air flowing into the radiator, and an indicator indicating the density of the air.
- the outside air temperature, the refrigerant flow rate, the air flow rate in the air flow passage, the vehicle speed, the air flow rate through the outdoor heat exchanger, the voltage of the outdoor blower passing through the outdoor heat exchanger, the temperature of the heat absorber, the rotation speed of the compressor Based on any one of the indices indicating the refrigerant pressure at the radiator outlet, the refrigerant temperature at the radiator outlet, the refrigerant pressure at the radiator inlet, and the refrigerant temperature at the radiator inlet, or a combination thereof. And calculates the frost during the heating capacity QhpNI.
- An air conditioner for a vehicle is provided with a heat radiator outside the air flow passage, a heat medium-refrigerant heat exchanger that exchanges heat with the heat radiator, and the air flow passage in each of the above inventions.
- the heat medium-air heat exchanger, the electric heater, and the circulation means, and the heat medium-refrigerant heat exchanger and / or the heat medium heated by the electric heater is heated by the circulation means.
- the auxiliary heating means is composed of a heat medium circulation circuit that circulates in the exchanger.
- an air conditioning apparatus for a vehicle according to the first to seventh aspects of the present invention, wherein the auxiliary heating means is configured by an electric heater that is provided in the air flow passage and heats the air supplied to the passenger compartment.
- a vehicle air conditioner according to a tenth aspect of the present invention is the vehicle air conditioner according to any of the first to seventh aspects, wherein the radiator is provided in the air flow passage, and the heat medium-air heat exchanger provided in the air flow passage;
- the auxiliary heating means is composed of a heat medium circulation circuit that has an electric heater and a circulation means and circulates the heat medium heated by the electric heater to the heat medium-air heat exchanger by the circulation means.
- the vehicle air conditioner according to an eleventh aspect of the present invention is characterized in that, in the above invention, the heat medium circulation circuit includes a heat medium-refrigerant heat exchanger that recovers heat from the refrigerant that has passed through the radiator.
- a vehicle air conditioner according to a twelfth aspect of the present invention is the air conditioner for a vehicle according to the tenth or eleventh aspect of the present invention, although the control means does not have insufficient heating capacity by the radiator, but the radiator is not frosted.
- the difference between the non-frosting heating capacity QhpNI in which heat is generated and the required heating capacity Qtgt which is the required heating capacity of the radiator is reduced to a predetermined value, a preliminary operation for starting heating by the heat medium circulation circuit is executed It is characterized by that.
- the vehicle air conditioner according to the thirteenth aspect of the present invention is characterized in that, in the above invention, the control means reduces the heating capacity of the radiator by the amount heated by the heat medium circulation circuit during the preliminary operation.
- a vehicle air conditioner according to a fourteenth aspect of the present invention is the vehicle air conditioner according to the twelfth or thirteenth aspect of the present invention, wherein the control means performs a preliminary operation when the temperature of the heat medium flowing through the heat medium circuit is lower than a predetermined value
- Heat medium-air heat exchanger is characterized in that it limits the amount of heat medium that is circulated to the heat exchanger.
- a vehicle air conditioner according to a fifteenth aspect of the present invention is the vehicle air conditioner according to the ninth to fourteenth aspects of the present invention, wherein the electric heater or the heat medium-air heat exchanger is connected to the air flow path with respect to the air flow. It is arranged on the downstream side.
- an air conditioning apparatus for a vehicle in which the electric heater or the heat medium-air heat exchanger is connected to the air flow passage with respect to the air flow. It is arranged on the upstream side.
- a compressor for compressing a refrigerant, an air flow passage through which air to be supplied to the vehicle interior flows, and a radiator for heating the air to be radiated from the refrigerant and supplied to the vehicle interior from the air flow passage.
- a heat absorber for cooling the refrigerant to absorb heat and supplying air from the air flow passage to the vehicle interior
- an outdoor heat exchanger that is provided outside the vehicle and radiates or absorbs the refrigerant
- a control means In the vehicle air conditioner that executes a heating mode in which at least the refrigerant discharged from the compressor is radiated by the radiator by this control means, and the radiated refrigerant is depressurized and then absorbed by the outdoor heat exchanger.
- the outdoor heat Comfortable vehicle interior heating can be achieved by heating the air supplied to the passenger compartment by the auxiliary heating means when the heater's heating capability is insufficient, such as when frost is formed on the converter. And the frost formation of the outdoor heat exchanger can be suppressed.
- the heating by the auxiliary heating means is executed under the condition where the heating capacity by the radiator is insufficient, it is possible to minimize the deterioration of the efficiency due to the heating by the auxiliary heating means. Thereby, especially in an electric vehicle, it becomes possible to effectively suppress the disadvantage that the cruising distance decreases.
- the control means compares the required heating capacity Qtgt which is the required heating capacity of the radiator with the heating capacity Qhp generated by the radiator, and this heating capacity Qhp is the required heating capacity.
- the heating capacity Qhp is defined as the non-frosting heating capacity QhpNI generated by the radiator when the outdoor heat exchanger is not frosted, and the non-frosting heating capacity QhpNI is the required heating capacity Qtgt If the shortage is supplemented by the heating of the auxiliary heating means, it is possible to grasp whether the heating capacity of the radiator is insufficient before frosting on the outdoor heat exchanger, and quick auxiliary heating means Thus, it becomes possible to realize more comfortable vehicle interior heating.
- the control means as in the invention of claim 4 and the non-frosting heating capacity QhpNI and the actual heating capacity If heating is performed by the auxiliary heating means by adding the difference in Qhpr, frost is generated in the outdoor heat exchanger, and the actual heating capacity Qhpr actually generated by the radiator is lower than the non-frosting heating capacity QhpNI. In this case, the reduced amount can be supplemented by the auxiliary heating means, and the comfort can be further improved.
- the control means is such that the actual heating capacity Qhpr actually generated by the radiator is smaller than the non-frosting heating capacity QhpNI, and the non-frosting heating capacity QhpNI and the actual heating capacity Qhpr If the difference is larger than the predetermined value, the compressor is stopped and the auxiliary heating means is controlled by the required heating capacity Qtgt, so that the degree of frost formation on the outdoor heat exchanger can be grasped, When it has progressed, it becomes possible to switch to vehicle interior heating using only auxiliary heating means. As a result, it is possible to continue heating the vehicle interior by the auxiliary heating means while preventing further frost growth of the outdoor heat exchanger or promoting frost melting.
- control means as in the invention of claim 6 is any one of an index indicating the temperature of the air flowing out from the radiator and the amount of air passing through the radiator, or a combination thereof.
- the actual heating capacity Qhpr is calculated based on the specific heat of the air flowing into the radiator and an index indicating the density of the air, and the temperature of the air flowing into the radiator as in the invention of claim 7 is calculated from the radiator. Indicates the specific heat of the air flowing into the radiator and the density of the air, and any one of the indices indicating the temperature of the flowing air and the amount of air passing through the radiator, or a combination thereof.
- the required heating capacity Qtgt is calculated based on the index, and the outdoor air temperature, the refrigerant flow rate, the air flow rate in the air flow passage, the vehicle speed, the air flow rate passing through the outdoor heat exchanger, and the outdoor fan that passes through the outdoor heat exchanger are calculated.
- the non-frosting heating capacity QhpNI By calculating the non-frosting heating capacity QhpNI based on any one or a combination thereof, more accurate control of the determination of the heating capacity by the radiator and the heating by the auxiliary heating means when it is insufficient It becomes possible.
- a heat radiator is provided outside the air flow passage, and a heat medium-refrigerant heat exchanger that exchanges heat with the heat radiator, and a heat medium-air heat exchanger provided in the air flow passage.
- an electric heater and a circulation means and the heat medium circulation medium for circulating the heat medium-refrigerant heat exchanger and / or the heat medium heated by the electric heater to the heat medium-air heat exchanger by the circulation means.
- the auxiliary heating means is configured from the circuit, it becomes possible to realize electrically safer vehicle interior heating.
- the air supplied to the vehicle interior is provided in the air flow passage.
- An electric heater for heating may be used.
- a radiator is provided in the air flow passage, and a heat medium-air heat exchanger provided in the air flow passage, an electric heater, and a circulation means are provided. Even if the auxiliary heating means is constituted by a heat medium circulation circuit that circulates the heated heat medium to the heat medium-air heat exchanger by the circulation means, the electrical safety is improved.
- the heat medium circulation circuit is provided with a heat medium-refrigerant heat exchanger for recovering heat from the refrigerant that has passed through the radiator as in the invention of claim 11, the heat of the refrigerant that has exited the radiator is circulated through the heat medium. It is possible to recover the heat medium flowing in the circuit and transport it to the heat medium-air heat exchanger to perform more efficient heating assistance.
- the control means as in the invention of claim 12 does not have insufficient heating capacity by the radiator, but the non-frosting generated by the radiator when the outdoor heat exchanger is not frosted.
- the difference between the hourly heating capacity QhpNI and the required heating capacity Qtgt, which is the required heating capacity of the radiator is reduced to a predetermined value, if a preliminary operation for starting heating by the heat medium circulation circuit is executed, heat dissipation When it is predicted that the heating capacity of the heater will be insufficient, it is possible to warm the heat medium in the heat medium circulation circuit in advance, and it is possible to realize quick heating capacity complementation using the heat medium circulation circuit. It becomes like this.
- control means reduces the heating capacity of the radiator by the amount heated by the heat medium circulation circuit during the preliminary operation as in the invention of claim 13, the preliminary operation of the heat medium circulation circuit is performed.
- the inconvenience that the heating capacity increases more than necessary can be solved.
- the control means as in the invention of the fourteenth aspect of the heat medium circulated to the heat medium-air heat exchanger. If the amount is limited, the circulation to the heat medium-air heat exchanger is suppressed in a situation where the temperature of the heat medium in the heat medium circuit is still low, and the temperature of the air supplied to the passenger compartment is reduced. The temperature of the heat medium is promoted while preventing it, and when the heating capacity of the radiator is insufficient, the air in the air flow passage can be quickly heated and heated by the heat medium-air heat exchanger. It will be.
- the electric heater or the heat medium-air heat exchanger is arranged downstream of the radiator with respect to the air flow in the air flow passage as in the invention of claim 15, the electric heater or the heat As in the case where the medium-air heat exchanger is arranged upstream, the air heated by the electric heater or the heat medium-air heat exchanger does not flow into the radiator, and the heat exchange performance of the radiator is reduced. It becomes possible to prevent the deterioration of the operation efficiency due to the decrease.
- the heat medium-air heat exchanger when the heat medium-air heat exchanger is arranged downstream of the air in the radiator, it is supplied to the passenger compartment at the beginning of energization of the electric heater or when the temperature of the heat medium in the heat medium circuit is still low. Although there is a concern about a decrease in the air temperature, this can be solved by controlling as in the above-described invention of claim 14.
- FIG. 1 It is a block diagram of the air conditioning apparatus for vehicles of one Embodiment to which this invention is applied. It is an enlarged view of the airflow passage part of FIG. It is a block diagram of the electric circuit of the controller of the vehicle air conditioner of FIG. It is a flowchart explaining operation
- FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention.
- a vehicle according to an embodiment to which the present invention is applied is an electric vehicle (EV) in which an engine (internal combustion engine) is not mounted, and travels by driving an electric motor for traveling with electric power charged in a battery.
- EV electric vehicle
- the vehicle air conditioner 1 of the present invention is also driven by the power of the battery. That is, the vehicle air conditioner 1 of the embodiment performs heating by a heat pump operation using a refrigerant circuit in an electric vehicle that cannot be heated by engine waste heat, and further operates in each operation mode such as dehumidifying heating, cooling dehumidification, and cooling. Is selectively executed.
- the present invention is effective not only for electric vehicles but also for so-called hybrid vehicles that use an engine and an electric motor for traveling, and is also applicable to ordinary vehicles that run on an engine. Needless to say.
- the vehicle air conditioner 1 performs air conditioning (heating, cooling, dehumidification, and ventilation) in a vehicle interior of an electric vehicle, and includes an electric compressor 2 that compresses refrigerant and vehicle interior air. Is provided in the air flow passage 3 of the HVAC unit 10 through which air is circulated, and the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows in through the refrigerant pipe 13G, and dissipates the refrigerant into the vehicle compartment.
- an outdoor expansion valve 6 composed of an electric valve that decompresses and expands the refrigerant during heating, and an outdoor heat exchange that functions as a radiator during cooling and performs heat exchange between the refrigerant and the outside air so as to function as an evaporator during heating.
- a heat exchanger 9 an indoor expansion valve 8 including an electric valve for decompressing and expanding the refrigerant, a heat absorber 9 provided in the air flow passage 3 to absorb heat from the outside of the vehicle interior during cooling and dehumidification, and a heat absorber 9.
- Steam to adjust evaporation capacity A capacity control valve 11, the accumulator 12 and the like are sequentially connected by a refrigerant pipe 13, the refrigerant circuit R is formed.
- the outdoor heat exchanger 7 is provided with an outdoor blower 15.
- the outdoor blower 15 exchanges heat between the outside air and the refrigerant by forcibly passing outside air through the outdoor heat exchanger 7, and thereby stops the vehicle (that is, the vehicle speed VSP is 0 km / h).
- the outdoor heat exchanger 7 is configured to ventilate the outside air.
- the outdoor heat exchanger 7 has a receiver dryer section 14 and a supercooling section 16 in order on the downstream side of the refrigerant, and the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is an electromagnetic valve (open / close valve) 17 that is opened during cooling.
- the outlet of the supercooling unit 16 is connected to the indoor expansion valve 8 via a check valve 18.
- the receiver dryer section 14 and the supercooling section 16 structurally constitute a part of the outdoor heat exchanger 7, and the check valve 18 has a forward direction on the indoor expansion valve 8 side.
- the refrigerant pipe 13B between the check valve 18 and the indoor expansion valve 8 is provided in a heat exchange relationship with the refrigerant pipe 13C exiting the evaporation capacity control valve 11 located on the outlet side of the heat absorber 9, and internal heat is generated by both.
- the exchanger 19 is configured.
- the refrigerant flowing into the indoor expansion valve 8 through the refrigerant pipe 13B is cooled (supercooled) by the low-temperature refrigerant that has exited the heat absorber 9 and passed through the evaporation capacity control valve 11.
- the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched, and this branched refrigerant pipe 13D is downstream of the internal heat exchanger 19 via an electromagnetic valve (open / close valve) 21 that is opened during heating.
- the refrigerant pipe 13C is connected in communication.
- the refrigerant pipe 13E on the outlet side of the radiator 4 is branched in front of the outdoor expansion valve 6, and this branched refrigerant pipe 13F is a check valve via an electromagnetic valve (open / close valve) 22 that is opened during dehumidification. 18 is connected to the refrigerant pipe 13B on the downstream side.
- a bypass pipe 13J is connected to the outdoor expansion valve 6 in parallel.
- the bypass pipe 13J is opened in a cooling mode, and is an electromagnetic valve (open / close valve) for bypassing the outdoor expansion valve 6 and flowing refrigerant. ) 20 is interposed.
- the piping between the outdoor expansion valve 6 and the electromagnetic valve 20 and the outdoor heat exchanger 7 is 13I.
- the air flow passage 3 on the air upstream side of the heat absorber 9 is formed with each of an outside air inlet and an inside air inlet (represented by the inlet 25 in FIG. 1). 25 is provided with a suction switching damper 26 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation mode) which is air inside the passenger compartment and the outside air (outside air introduction mode) which is outside the passenger compartment. Yes. Furthermore, an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.
- an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.
- reference numeral 23 denotes a heat medium circulation circuit as auxiliary heating means provided in the vehicle air conditioner 1 of the embodiment.
- the heat medium circulation circuit 23 has a circulation pump 30 constituting a circulation means, a heat medium heating electric heater (indicated by ECH in the drawing) 35, and an air downstream of the radiator 4 with respect to the air flow in the air flow passage 3.
- a heat medium-air heat exchanger 40 provided in the air flow passage 3 on the side is provided, and these are sequentially connected in an annular shape by a heat medium pipe 23A.
- the heat medium circulated in the heat medium circuit 23 for example, water, a refrigerant such as HFO-1234yf, a coolant, or the like is employed.
- the circulation pump 30 When the circulation pump 30 is operated and the heat medium heating electric heater 35 is energized to generate heat, the heat medium heated by the heat medium heating electric heater 35 is circulated to the heat medium-air heat exchanger 40.
- the heat medium-air heat exchanger 40 of the heat medium circulation circuit 23 becomes a so-called heater core, and complements the heating of the passenger compartment.
- an air mix damper 28 is provided in the air flow passage 3 on the air upstream side of the radiator 4 to adjust the degree of flow of inside air and outside air to the radiator 4. Further, in the air flow passage 3 on the downstream side of the radiator 4, foot, vent, and differential air outlets (represented by the air outlet 29 in FIG. 1) are formed. Is provided with a blower outlet switching damper 31 for switching and controlling the blowing of air from each of the blowout ports.
- 32 is a controller (ECU) as a control means constituted by a microcomputer, and an input of the controller 32 detects an outside air temperature sensor 33 for detecting the outside air temperature of the vehicle and an outside air humidity.
- An outside air humidity sensor 34 an HVAC suction temperature sensor 36 that detects the temperature of air sucked into the air flow passage 3 from the suction port 25, an inside air temperature sensor 37 that detects the temperature of the air (inside air) in the vehicle interior, and the vehicle interior
- the inside air humidity sensor 38 that detects the humidity of the air in the vehicle, the indoor CO 2 concentration sensor 39 that detects the carbon dioxide concentration in the vehicle interior, and the blowout temperature sensor 41 that detects the temperature of the air blown from the blowout port 29 into the vehicle interior.
- a discharge pressure sensor 42 for detecting the discharge refrigerant pressure of the compressor 2 for detecting the discharge refrigerant pressure of the compressor 2, a discharge temperature sensor 43 for detecting the discharge refrigerant temperature of the compressor 2, and a compression
- a suction pressure sensor 44 that detects the suction refrigerant pressure 2
- a radiator temperature sensor 46 that detects the temperature of the radiator 4 (the temperature of the air that has passed through the radiator 4, or the temperature of the radiator 4 itself), and the radiator 4, a radiator pressure sensor 47 for detecting the refrigerant pressure (inside the radiator 4 or immediately after leaving the radiator 4), and the temperature of the heat absorber 9 (the temperature of air passing through the heat absorber 9, or
- a heat absorber temperature sensor 48 for detecting the temperature of the heat absorber 9 itself, and a heat absorber pressure for detecting the refrigerant pressure of the heat absorber 9 (the pressure of the refrigerant in the heat absorber 9 or just after leaving the heat absorber 9).
- a photosensor type solar radiation sensor 51 for detecting the amount of solar radiation in the vehicle interior, a vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, and switching between set temperature and operation mode.
- An air conditioning (air conditioner) operation unit 53 for setting;
- An outdoor heat exchanger temperature sensor 54 for detecting the temperature of the external heat exchanger 7 (the temperature of the refrigerant immediately after coming out of the outdoor heat exchanger 7 or the temperature of the outdoor heat exchanger 7 itself), and the outdoor heat exchanger 7
- the outdoor heat exchanger 7 Are connected to the outputs of the outdoor heat exchanger pressure sensor 56 for detecting the refrigerant pressure (the pressure of the refrigerant in the outdoor heat exchanger 7 or immediately after coming out of the outdoor heat exchanger 7).
- the input of the controller 32 further includes the temperature of the heating medium heating electric heater 35 of the heating medium circulation circuit 23 (the temperature of the heating medium immediately after being heated by the heating medium heating electric heater 35 or the heating medium heating electric heater 35.
- the temperature of the electric heater through the heat medium heating air heater 40 (the temperature of the air passing through the heat medium-air heat exchanger 40, Alternatively, the outputs of the heat medium-air heat exchanger temperature sensor 55 for detecting the temperature of the heat medium-air heat exchanger 40 itself are also connected.
- the output of the controller 32 includes the compressor 2, the outdoor fan 15, the indoor fan (blower fan) 27, the suction switching damper 26, the air mix damper 28, the suction port switching damper 31, and the outdoor expansion.
- the valve 6, the indoor expansion valve 8, the electromagnetic valves 22, 17, 21, 20, the circulation pump 30, the heat medium heating electric heater 35, and the evaporation capacity control valve 11 are connected. And the controller 32 controls these based on the output of each sensor, and the setting input in the air-conditioning operation part 53.
- the controller 32 is roughly divided into a heating mode, a dehumidifying heating mode, an internal cycle mode, a dehumidifying cooling mode, and a cooling mode, and executes them.
- a heating mode a dehumidifying heating mode
- an internal cycle mode a dehumidifying cooling mode
- a cooling mode a cooling mode
- the controller 32 opens the solenoid valve 21, and the solenoid valve 17, the solenoid valve 22, and the solenoid valve. 20 is closed. Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state where the air blown out from the indoor blower 27 is passed through the radiator 4 and the heat medium-air heat exchanger 40. . Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4.
- the air in the air flow passage 3 is passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. Deprived, cooled, and condensed into liquid.
- the refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipe 13E.
- the operation and action of the heat medium circulation circuit 23 will be described later.
- the refrigerant flowing into the outdoor expansion valve 6 is decompressed there and then flows into the outdoor heat exchanger 7.
- the refrigerant flowing into the outdoor heat exchanger 7 evaporates, and pumps up heat from the outside air that is ventilated by traveling or by the outdoor blower 15. That is, the refrigerant circuit R becomes a heat pump (indicated by HP in the drawing).
- the low-temperature refrigerant exiting the outdoor heat exchanger 7 enters the accumulator 12 from the refrigerant pipe 13C through the refrigerant pipe 13D and the electromagnetic valve 21, and after being gas-liquid separated there, the gas refrigerant is sucked into the compressor 2. repeat. Since the air heated by the radiator 4 is blown out from the outlet 29 through the heat medium-air heat exchanger 40, the vehicle interior is thereby heated.
- the controller 32 controls the number of revolutions of the compressor 2 based on the high pressure of the refrigerant circuit R detected by the discharge pressure sensor 42 or the radiator pressure sensor 47, and the temperature of the radiator 4 detected by the radiator temperature sensor 46.
- the valve opening degree of the outdoor expansion valve 6 is controlled based on the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47, and the degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled.
- the controller 32 opens the electromagnetic valve 22 in the heating mode.
- a part of the condensed refrigerant flowing through the refrigerant pipe 13E via the radiator 4 is diverted and reaches the indoor expansion valve 8 via the electromagnetic valve 22 and the refrigerant pipes 13F and 13B via the internal heat exchanger 19.
- the refrigerant After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
- the refrigerant evaporated in the heat absorber 9 merges with the refrigerant from the refrigerant pipe 13D in the refrigerant pipe 13C through the evaporation capacity control valve 11 and the internal heat exchanger 19, and then repeats circulation sucked into the compressor 2 through the accumulator 12. . Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed.
- the controller 32 controls the number of revolutions of the compressor 2 based on the high pressure of the refrigerant circuit R detected by the discharge pressure sensor 42 or the radiator pressure sensor 47 and adjusts the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48. Based on this, the valve opening degree of the outdoor expansion valve 6 is controlled.
- coolant piping 13F reaches the indoor expansion valve 8 through the internal heat exchanger 19 from the refrigerant
- the refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C through the evaporation capacity control valve 11 and the internal heat exchanger 19, and repeats circulation sucked into the compressor 2 through the accumulator 12. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidification heating is performed in the vehicle interior, but in this internal cycle mode, the air flow path on the indoor side 3, the refrigerant is circulated between the radiator 4 (heat radiation) and the heat absorber 9 (heat absorption), so that heat from the outside air is not pumped up, and the heating capacity for the power consumption of the compressor 2 Is demonstrated. Since the entire amount of the refrigerant flows through the heat absorber 9 that exhibits the dehumidifying action, the dehumidifying capacity is higher than that in the dehumidifying and heating mode, but the heating capacity is lowered.
- the controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 or the high pressure of the refrigerant circuit R described above. At this time, the controller 32 controls the compressor 2 by selecting the lower one of the compressor target rotational speeds obtained from either calculation, depending on the temperature of the heat absorber 9 or the high pressure.
- the controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 21, the electromagnetic valve 22, and the electromagnetic valve 20. Then, the compressor 2 and the blowers 15 and 27 are operated, and the air mix damper 28 is in a state in which the air blown from the indoor blower 27 is passed through the radiator 4 and the heat medium-air heat exchanger 40. . Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4.
- the air in the air flow passage 3 is passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived and cooled, and condensates.
- the refrigerant that has exited the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipe 13E, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 that is controlled to open.
- the refrigerant flowing into the outdoor heat exchanger 7 is cooled and condensed by running there or by the outside air ventilated by the outdoor blower 15.
- the refrigerant that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 ⁇ / b> A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
- the refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 ⁇ / b> B through the check valve 18, and reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
- the refrigerant evaporated in the heat absorber 9 passes through the evaporation capacity control valve 11 and the internal heat exchanger 19, reaches the accumulator 12 through the refrigerant pipe 13 ⁇ / b> C, and repeats circulation sucked into the compressor 2 through the refrigerant pipe 13 ⁇ / b> C.
- the air cooled and dehumidified by the heat absorber 9 is reheated (having a lower heat dissipation capacity than that during heating) in the process of passing through the radiator 4, thereby dehumidifying and cooling the vehicle interior. .
- the controller 32 controls the number of revolutions of the compressor 2 based on the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48 and controls the valve opening degree of the outdoor expansion valve 6 based on the high pressure of the refrigerant circuit R described above.
- refrigerant pressure of the radiator 4 Radiator pressure PCI
- the controller 32 opens the electromagnetic valve 20 in the dehumidifying and cooling mode state (in this case, the outdoor expansion valve 6 is fully opened (the valve opening is controlled to an upper limit)).
- the air mix damper 28 is in a state in which no air is passed through the radiator 4 and the heat medium-air heat exchanger 40. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is not ventilated to the radiator 4, the air only passes therethrough, and the refrigerant exiting the radiator 4 reaches the electromagnetic valve 20 and the outdoor expansion valve 6 through the refrigerant pipe 13 ⁇ / b> E.
- the refrigerant bypasses the outdoor expansion valve 6 and passes through the bypass pipe 13J, and flows into the outdoor heat exchanger 7 as it is, where it travels or is ventilated by the outdoor fan 15. It is air-cooled by the outside air and is condensed and liquefied.
- the refrigerant that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13 ⁇ / b> A through the electromagnetic valve 17 into the receiver dryer unit 14 and the supercooling unit 16. Here, the refrigerant is supercooled.
- the refrigerant that has exited the supercooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13 ⁇ / b> B through the check valve 18, and reaches the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled.
- the refrigerant evaporated in the heat absorber 9 passes through the evaporation capacity control valve 11 and the internal heat exchanger 19, reaches the accumulator 12 through the refrigerant pipe 13 ⁇ / b> C, and repeats circulation sucked into the compressor 2 through the refrigerant pipe 13 ⁇ / b> C.
- the air that has been cooled and dehumidified by the heat absorber 9 is blown into the vehicle interior from the outlet 29 without passing through the radiator 4, thereby cooling the vehicle interior.
- the controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48.
- TAO (Tset ⁇ Tin) ⁇ K + Tbal (f (Tset, SUN, Tam)) (1)
- Tset is the set temperature in the passenger compartment set by the air conditioning operation unit 53
- Tin is the temperature of the passenger compartment air detected by the inside air temperature sensor 37
- K is a coefficient
- Tbal is the set temperature Tset
- the solar radiation sensor 51 detects This is a balance value calculated from the amount of solar radiation SUN to be performed and the outside air temperature Tam detected by the outside air temperature sensor 33.
- this target blowing temperature TAO is so high that the outside temperature Tam is low, and it falls as the outside temperature Tam rises.
- the controller 32 calculates a target radiator temperature TCO from the target blowing temperature TAO, and then calculates a target radiator pressure PCO based on the target radiator temperature TCO. Then, based on the target radiator pressure PCO and the refrigerant pressure (radiator pressure) Pci of the radiator 4 detected by the radiator pressure sensor 47, the controller 32 calculates the rotation speed Nc of the compressor 2, and this rotation The compressor 2 is operated at several Nc. That is, the controller 32 controls the refrigerant pressure Pci of the radiator 4 by the rotation speed Nc of the compressor 2.
- the controller 32 calculates the target radiator subcooling degree TGSC of the radiator 4 based on the target outlet temperature TAO.
- the controller 32 uses the radiator pressure Pci and the temperature of the radiator 4 (radiator temperature Tci) detected by the radiator temperature sensor 46 to determine the degree of refrigerant supercooling (radiator subcooling degree SC) in the radiator 4. Is calculated.
- the target valve opening degree of the outdoor expansion valve 6 target outdoor expansion valve opening degree TGECCV
- the controller 32 controls the valve opening degree of the outdoor expansion valve 6 to this target outdoor expansion valve opening degree TGECVV.
- the controller 32 calculates the target radiator supercooling degree TGSC so as to increase as the target blowout temperature TAO increases. Alternatively, it may be calculated based on the difference (pressure difference) between the radiator pressure Pci, the target radiator pressure PCO and the radiator pressure Pci. In this case, the controller 32 decreases the target radiator subcooling degree TGSC as the capacity difference is smaller, the pressure difference is smaller, the air volume of the indoor blower 27 is smaller, or the radiator pressure Pci is smaller.
- FIG. 2 shows the temperature of each part in the air flow passage 3 at this time.
- Ga is the mass air volume of air flowing into the air flow passage 3
- Te is the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48 (temperature of the air leaving the heat absorber 9)
- Ga ⁇ SW is mass.
- THhp The value obtained by multiplying the air volume Ga by the opening of the air mix damper 28, THhp is the temperature of the air passing through the radiator 4 detected by the radiator temperature sensor 46 (ie, the radiator temperature Tci), and TH is the heat medium-air heat exchange.
- the temperature of the air passing through the heat medium-air heat exchanger 40 detected by the heater temperature sensor 55 is shown. In the heating mode, the temperature of the air discharged from the outlet 29 through the heat medium-air heat exchanger 40 is shown.
- the target value becomes the target radiator temperature TCO.
- the controller 32 has a required heating capacity Qtgt which is the heating capacity of the radiator 4 required using the formulas (II) and (III), and a non-frosting heating capacity as a heating capacity Qhp that can be generated by the radiator 4.
- QhpNI is calculated.
- the non-frosting heating capacity QhpNI is a predicted value of the heating capacity that can be generated by the radiator 4 at the outdoor temperature Tam when the outdoor heat exchanger 7 is not frosted (non-frosting). Yes (ie, the estimated maximum heating capacity of the heat pump).
- the temperature of air flowing into the radiator 4 or the temperature of air flowing out of the radiator 4 may be adopted instead of or in addition to Qair.
- the rotational speed Nc of the compressor 2 in the formula (III) is an example of an index indicating the refrigerant flow rate
- the blower voltage BLV is an example of an index indicating the air volume in the air flow passage 3
- the heating capacity QhpNI Calculated from the function is an index indicating the amount of air passing through the outdoor heat exchanger 7 when the vehicle is stopped (VSP is 0).
- QhpNI is calculated from any one or a combination of them and the outlet refrigerant pressure of the radiator 4, the outlet refrigerant temperature of the radiator 4, the inlet refrigerant pressure of the radiator 4, and the inlet refrigerant temperature of the radiator 4. May be.
- the controller 32 reads data from each sensor in step S1 of the flowchart of FIG. 4, and calculates the required heating capacity Qtgt using the above formula (II) in step S2.
- the above formula (III) is used to calculate the heating capacity QhpNI (estimated value) when the outdoor heat exchanger 7 is not frosted. Is the required heating capacity Qtgt greater than the heating capacity QhpNI in step S4? Judge whether or not.
- the diagonal line in FIG. 5 shows the limit line of the non-frosting heating capacity QhpNI by the radiator 4 when the outdoor heat exchanger 7 is not frosted, the horizontal axis is the outside air temperature Tam, and the vertical axis is the heating. Shows ability.
- the required heating capacity Qtgt is equal to or less than the non-frosting heating capacity QhpNI (limit line thereof) in FIG. 5, that is, when the non-frosting heating capacity QhpNI of the radiator 4 is sufficient with respect to the required heating capacity Qtgt.
- step S6 heating by the heat medium circulation circuit 23 is stopped (circulation pump 30 is stopped, ECH is stopped when the heat medium heating electric heater 35 is not energized), and the refrigerant circuit R is generated so that the radiator 4 generates the required heating capacity Qtgt.
- the process proceeds from step S4 to step S5, and the cooperative operation of the radiator 4 of the refrigerant circuit R and the heat medium-air heat exchanger 40 (ECH) of the heat medium circulation circuit 23 is executed. That is, the controller 32 operates the circulation pump 30 of the heat medium circulation circuit 23 and energizes the heat medium heating electric heater 35, so that in addition to the heating by the radiator 4 of the refrigerant circuit R, the heat medium-air heat exchanger Start heating by 40.
- the energization of the heat medium heating electric heater 35 and the operation of the circulation pump 30 are controlled so as to achieve the heating capacity QhpNI. That is, the controller 32 supplements the shortage of the non-frosting heating capacity QhpNI with respect to the required heating capacity Qtgt by heating by the heat medium-air heat exchanger 40 of the heat medium circulation circuit 23. Thereby, comfortable vehicle interior heating is implement
- the heating by the heat medium-air heat exchanger 40 of the heat medium circulation circuit 23 is executed under the condition where the heating capacity of the radiator 4 is insufficient, the efficiency deteriorates due to the operation of the heat medium circulation circuit 23. It can be minimized. Thereby, in an electric vehicle like an Example, it becomes possible to suppress effectively the disadvantage that a cruising distance falls.
- the controller 32 compares the required heating capacity Qtgt with the non-frosting heating capacity QhpNI, and supplements the heating capacity of the non-frosting heating capacity QhpNI below the required heating capacity Qtgt by heating of the heat medium circulation circuit 23. Therefore, it is possible to effectively carry out comfortable heating of the vehicle interior and suppress the efficiency reduction, and to grasp whether the heating capacity Qhp of the radiator 4 is insufficient before the outdoor heat exchanger 7 is frosted, and quickly Heating by the heat medium circulation circuit 23 can be started and more comfortable vehicle interior heating can be realized.
- the controller 32 calculates the actual heating capacity Qhpr using the formula (IV).
- Qhpr (THhp ⁇ Te) ⁇ Cpa ⁇ ⁇ ⁇ Qair (IV)
- THhp is the temperature of the air that has passed through the radiator 4 (ie, the radiator temperature Tci) detected by the radiator temperature sensor 46 described above.
- FIG. 6 shows the relationship between the actual heating capacity Qhpr, the non-frosting heating capacity QhpNI, and the required heating capacity Qtgt.
- Qhpr is almost equal to QhpNI.
- Qhpr is lowered, so that it does not adhere as shown in FIG.
- Whether the outdoor heat exchanger 7 is frosted can be determined based on whether or not the difference (QhpNI ⁇ Qhpr) between the frost-time heating capacity QhpNI and the actual heating capacity Qhpr is equal to or greater than a predetermined value (frosting determination threshold).
- the frost formation determination of the outdoor heat exchanger 7 is not limited to this, as shown by (b) in FIG. 6, whether the slope at which the actual heating capacity Qhpr decreases is a certain value or more, or the rotation of the compressor 2
- the determination can also be made by the increase in the number, the decrease in the temperature of the radiator 4, and the like. However, in this embodiment, the determination is made by the method (a).
- the required heating capacity TGQech required heating capacity Qtgt ⁇ non-frosting by the heat medium circuit 23 as in the above-described embodiment (FIG. 4).
- the controller 32 corrects this shortage and controls the heat medium circulation circuit 23.
- the controller 32 reads data from each sensor in the same manner as described above in step S7 of the flowchart of FIG. 7, and calculates the required heating capacity Qtgt using the equation (II) in step S8.
- step S9 using the above formula (III), the outdoor heat exchanger 7 calculates the heating capacity QhpNI (estimated value) at the time of non-frosting.
- step S10 the required heating capacity Qtgt is calculated as the heating capacity QhpNI. Judge whether it is larger.
- step S15 heating by the heat medium circulation circuit 23 is stopped (the circulation pump 30 is stopped, the heat medium heating electric power is supplied).
- step S12 it is determined whether or not the difference between the non-frosting heating capacity QhpNI and the actual heating capacity Qhpr (QhpNI ⁇ Qhpr) is smaller than a predetermined value A.
- the predetermined value A is a value for determining a state where frost formation has occurred in the outdoor heat exchanger 7 but the frost growth has not progressed so much, and is the aforementioned frost determination threshold value. It may be a different value.
- the controller 32 determines that frosting of the outdoor heat exchanger 7 has not yet progressed, and proceeds from step S12 to step S13. 4 and the heat medium-air heat exchanger 40 (ECH) in the heat medium circulation circuit 23 are cooperatively operated. That is, the controller 32 operates the circulation pump 30 of the heat medium circulation circuit 23 and energizes the heat medium heating electric heater 35, so that in addition to the heating by the radiator 4 of the refrigerant circuit R, the heat medium-air heat exchanger Start heating by 40.
- the energization to the heat medium heating electric heater 35 and the operation of the circulation pump 30 are controlled so that the heating capacity QhpNI + ⁇ Qhp.
- the controller 32 when the actual heating capacity Qhpr actually generated by the radiator 4 is smaller than the non-frosting heating capacity QhpNI, the controller 32 has a non-frosting heating capacity QhpNI with respect to the required heating capacity Qtgt.
- the shortage is supplemented by heating by the heat medium-air heat exchanger 40 of the heat medium circulation circuit 23, and a difference ⁇ Qhp between the non-frosting heating capacity QhpNI and the actual heating capacity Qhpr is added to the heat medium circulation circuit 23.
- the heat medium-air heat exchanger 40 is used for heating.
- the reduced amount is also circulated in the heat medium.
- the circuit 23 can be complemented, and the comfort can be further improved.
- the interior of the vehicle compartment only by the heat medium-air heat exchanger 40 of the heat medium circuit 23 is used. Since switching to heating is performed, further growth of frost formation in the outdoor heat exchanger 7 can be prevented, or heating of the vehicle interior can be continued by the heat medium circulation circuit 23 while accelerating frost melting. Become.
- the heat medium circulation circuit 23 as auxiliary heating means circulates the heat medium (high temperature heat medium) heated by the heat medium heating electric heater 35 to the heat medium-air heat exchanger 40 by the circulation pump 30. Since the air in the air flow passage 3 that has passed through the radiator 4 is heated, it takes time to change the heat medium to a heat medium having a temperature suitable for heating (a high-temperature heat medium). Therefore, in the case of this embodiment, the controller 32 executes the preliminary operation of the heat medium circulation circuit 23 from the stage before the heating capability (non-frosting heating capability QhpNI) by the radiator 4 is insufficient.
- FIG. 8 shows the control of the controller 32 in such a case, and the steps denoted by the same reference numerals as in FIG. 7 are the same. That is, in this embodiment, the range indicated by the broken line X in FIG. 8 indicates the preliminary operation of the heat medium circulation circuit 23 added to FIG. Hereinafter, the description will focus on the parts different from FIG. 7.
- the controller 32 proceeds to step S16 if the non-frosting heating capacity QhpNI of the radiator 4 is sufficient with respect to the required heating capacity Qtgt.
- the compressor 2 and other devices in the circuit R are operated to heat the air supplied from the air flow passage 3 to the vehicle interior by the radiator 4 (HP control).
- step S17 it is determined whether or not the difference between the required heating capacity Qtgt and the non-frosting heating capacity QhpNI (Qtgt ⁇ QhpNI) is smaller than 0 and larger than a predetermined value B.
- the predetermined value B is a predetermined negative value having a small absolute value. That is, in step S17, the controller 32 determines whether the non-frosting heating capacity QhpNI is equal to or greater than the required heating capacity Qtgt (step S10), but the difference is smaller than the absolute value of B.
- step S17 When the difference (Qtgt ⁇ QhpNI) is less than or equal to B in step S17, that is, when the non-frosting heating capacity QhpNI is larger than the required heating capacity Qtgt by the absolute value of B, the heating capacity by the radiator 4 is increased.
- the process proceeds to step S15, and the heating by the heat medium circuit 23 is stopped (the circulation pump 30 is stopped and the ECH is stopped when the heat medium heating electric heater 35 is not energized) as in FIG.
- step S17 when the difference (Qtgt ⁇ QhpNI) is smaller than 0 and larger than B in step S17, that is, the non-frosting heating capacity QhpNI is larger than the required heating capacity Qtgt, the difference is reduced and the absolute value of B is reduced. If it is less, it is determined that the preliminary operation of the heat medium circulation circuit 23 is necessary, and the process proceeds to step S18 to start the preliminary operation of the heat medium circulation circuit 23.
- the required heating capacity TGQech by the heat medium circulation circuit 23 required heating capacity Qtgt-non-frosting heating capacity QhpNI
- the energization of the heating medium heating electric heater 35 and the operation of the circulation pump 30 are controlled so that However, the required heating capacity TGQech of the heat medium circulation circuit 23 is larger than the predetermined value C to prevent deterioration of the efficiency of the heat medium circulation circuit 23 itself. As a result, the temperature of the heat medium in the heat medium circuit 23 rises. Therefore, when it is predicted that the heating capacity of the radiator 4 will be insufficient, the heat medium in the heat medium circuit 23 is warmed in advance. Thus, it is possible to realize a quick complement of the heating capacity using the heat medium circulation circuit 23.
- the target heating capacity TGHP of the radiator 4 is the non-frosting heating capacity QhpNI-TGQech, and the heating capacity of the radiator 4 is reduced by the amount of heating by the heat medium circulation circuit 23 during the preliminary operation. That is, the compressor 2 and other devices of the refrigerant circuit R are operated so that the radiator 4 generates QhpNI-TGQech. As a result, the combined heating capacity of the radiator 4 and the heat medium-air heat exchanger 40 is It becomes the required heating capacity Qtgt. Thereby, the disadvantage that the heating capacity increases more than necessary during the preliminary operation of the heat medium circulation circuit 23 can be solved.
- the controller 32 determines the temperature of the heat medium (indicated by ECH water temperature in the flowchart of FIG. 8) that has passed through the heat medium heating electric heater 35 of the heat medium circulation circuit 23 detected by the heat medium heating electric heater temperature sensor 50 in step S19. It is determined whether or not it is higher than a predetermined value (temperature that can be used for heating), and if it is higher, the process proceeds to step S20, and the amount of circulating heat medium by the circulation pump (indicated by WP in the flowchart of FIG.
- step S21 If the amount is equal to or less than the predetermined value, the process proceeds to step S21, and the amount of circulating heat medium to the heat medium-air heat exchanger 40 by the circulation pump 30 is limited and reduced (in the flowchart of FIG. ).
- the control of the circulating heat medium amount is executed by controlling the rotational speed of the circulating pump 30.
- the controller 32 limits the amount of the circulating heat medium to the heat medium-air heat exchanger 40 when the temperature of the heat medium flowing through the heat medium circuit 23 is lower than a predetermined value during the preliminary operation. Therefore, while suppressing the circulation to the heat medium-air heat exchanger 40 in a situation where the temperature of the heat medium in the heat medium circuit 23 is still low, The temperature of the heat medium is promoted, and when the heating capacity of the radiator 4 is insufficient, the air in the air flow passage 3 can be quickly heated by the heat medium-air heat exchanger 40 for heating. .
- the amount of circulating heat medium to the heat medium-air heat exchanger 40 is limited by controlling the number of revolutions of the circulation pump 30.
- the present invention is not limited to this, and a route for bypassing the heat medium-air heat exchanger 40 is separately provided. It is also possible to limit the amount of the circulating heat medium to the heat medium-air heat exchanger 40 by allowing all or part of the heat medium to flow through the bypass path while the temperature of the heat medium is low.
- FIG. 9 shows another configuration diagram of the vehicle air conditioner 1 of the present invention.
- the outdoor heat exchanger 7 is not provided with the receiver dryer section 14 and the supercooling section 16, and the refrigerant pipe 13 ⁇ / b> A exiting from the outdoor heat exchanger 7 is connected via the electromagnetic valve 17 and the check valve 18. It is connected to the refrigerant pipe 13B.
- the refrigerant pipe 13D branched from the refrigerant pipe 13A is connected to the refrigerant pipe 13C on the downstream side of the internal heat exchanger 19 via the electromagnetic valve 21.
- the present invention is also effective in the vehicle air conditioner 1 of the refrigerant circuit R that employs the outdoor heat exchanger 7 that does not include the receiver dryer section 14 and the supercooling section 16.
- FIGS. 10 to 12 show another configuration diagram of the vehicle air conditioner 1 of the present invention.
- the refrigerant circuit R in this embodiment is the same as that shown in FIG.
- the heat medium-air heat exchanger 40 of the heat medium circuit 23 is disposed upstream of the radiator 4 and downstream of the air mix damper 28 with respect to the air flow in the air flow passage 3.
- Other configurations are the same as those in FIG.
- FIG. 11 shows the temperature of each part in the air flow passage 3 at this time.
- FIG. 12 shows the non-frosting heating capacity QhpNI, the required heating capacity TGQech of the heat medium circulation circuit 23, the required heating capacity Qtgt, the heat absorber temperature Te, the temperature THhp of the air leaving the radiator 4, the target radiator The relationship of temperature TCO is shown.
- the same reference numerals as those in FIG. 2 are the same.
- the present invention is also effective in the vehicle air conditioner 1 in which the heat medium-air heat exchanger 40 is arranged on the upstream side of the radiator 4.
- the heat medium in the heat medium circulation circuit 23 is used. The problem caused by the low temperature is not caused. This facilitates cooperative heating with the radiator 4 and eliminates the need for the preliminary operation as shown in FIG. 8, but the air that has passed through the heat medium-air heat exchanger 40 flows into the radiator 4.
- the heat medium-air heat exchanger 40 is arranged on the downstream side of the radiator 4 with respect to the air flow in the air flow passage 3 as shown in FIGS. 1 and 9, the heat medium-air as shown in FIG. Compared with the case where the heat exchanger 40 is arranged upstream, the air heated by the heat medium-air heat exchanger 40 does not flow into the radiator 4, and the temperature difference between the temperature of the radiator 4 and the air Is ensured, and the heat exchange performance of the radiator 4 can be prevented from lowering.
- FIG. 13 shows still another configuration diagram of the vehicle air conditioner 1 of the present invention.
- the basic configurations of the refrigerant circuit R and the heat medium circulation circuit 23 in this embodiment are the same as those in FIG. 1, but a heat medium-refrigerant heat exchanger 70 is provided in the heat medium circulation circuit 23.
- the heat medium-refrigerant heat exchanger 70 exchanges heat between the heat medium pipe 23A exiting the circulation pump 30 and the refrigerant pipe 13E exiting the radiator 4 of the refrigerant circuit R.
- the heat medium discharged from the circulation pump 30 is configured to receive a heating action from the refrigerant discharged from the radiator 4.
- heat can be recovered from the refrigerant that has passed through the radiator 4 to the heat medium that circulates through the heat medium circuit 23.
- the heat medium circulation circuit 23 is provided with the heat medium-refrigerant heat exchanger 70 that recovers heat from the refrigerant that has passed through the radiator 4, so that the heat of the refrigerant that has exited the radiator 4 can be transferred to the heat medium circuit. It is possible to recover the heat medium flowing in the heat transfer medium 23 and transport it to the heat medium-air heat exchanger 40 to perform more efficient heating assistance.
- FIG. 14 shows still another configuration diagram of the vehicle air conditioner 1 of the present invention.
- the refrigerant circuit R and the heat medium circulation circuit 23 of this embodiment are the same as in the case of FIG. 13, but the heat medium-air heat exchanger 40 of the heat medium circulation circuit 23 corresponds to the air flow in the air flow passage 3. Further, it is disposed upstream of the radiator 4 and downstream of the air mix damper 28. Also with such a configuration, the heat of the refrigerant that has exited the radiator 4 is recovered by the heat medium-refrigerant heat exchanger 70 to the heat medium flowing in the heat medium circuit 23, and the heat medium-air heat exchanger 40. It becomes possible to carry out more efficient heating assistance.
- FIG. 15 shows still another configuration diagram of the vehicle air conditioner 1 of the present invention.
- the piping configuration of the refrigerant circuit R and the heat medium circulation circuit 23 in this embodiment is basically the same as that in FIG. 1, but the radiator 4 is not provided in the air flow passage 3 and is arranged outside thereof. Has been. Instead, the radiator 4 is provided with a heat medium-refrigerant heat exchanger 74 in this case in a heat exchange relationship.
- This heat medium-refrigerant heat exchanger 74 is connected to the heat medium pipe 23A between the circulation pump 30 of the heat medium circulation circuit 23 and the heat medium heating electric heater 35, and the heat medium of the heat medium circulation circuit 23-
- the air heat exchanger 40 is provided in the air flow passage 3.
- the heating medium heating electric heater 35 is energized to heat the heating medium flowing in the heating medium circuit 23A.
- the heat medium circulation circuit 23 is employed as the auxiliary heating unit.
- the auxiliary heating unit may be configured by a normal electric heater (for example, a PTC heater) 73.
- the configuration example corresponding to FIG. 1 is FIG. 16, the control flowchart example corresponding to FIG. 4 is FIG. 17, the control flowchart example corresponding to FIG. 7 is FIG. 18, and the configuration example corresponding to FIG. It is. 16 and 19, the heat medium circulation circuit 23 of FIGS. 1 and 9 is replaced with an electric heater 73 in this case.
- Steps S5 and S6 in FIG. 4 are Steps S5A and S6A in FIG. 17 and Steps S13 to S15 in FIG. 7 are Steps S13A to S15A in FIG. 18, but the target TGQech is requested by the electric heater 73. It has been replaced with the heating capacity TGQeh.
- controller 32 controls the energization of the electric heater 73 instead of the circulation pump 30 and the heat medium heating electric heater 35 of the heat medium circulation circuit 23, and the same as described above. Since the heating capacity of the radiator 4 is complemented by heat generation, detailed description thereof is omitted. Thus, the air supplied to the passenger compartment may be heated by the electric heater 73. According to such a configuration, there is an advantage that the configuration is simplified as compared with the case where the heat medium circulation circuit 23 is used.
- the electric heater 73 may be arranged on the air upstream side of the radiator 4 in FIGS. 16 and 19 as in the case of FIG. 10, and in that case, the electric heater 73 is placed in the vehicle interior at the beginning of energization of the electric heater 73. This has the effect of eliminating the inconvenience that the temperature of the supplied air decreases.
- the present invention is applied to the vehicle air conditioner 1 that switches between the heating mode, the dehumidifying and heating mode, the dehumidifying and cooling mode, and the cooling mode.
- the present invention is not limited thereto, and only the heating mode is performed. In addition, the present invention is effective.
- the configuration and each numerical value of the refrigerant circuit R described in the above embodiments are not limited thereto, and it is needless to say that the refrigerant circuit R can be changed without departing from the gist of the present invention.
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Abstract
Description
コントローラ32により或いは空調操作部53へのマニュアル操作により暖房モードが選択されると、コントローラ32は電磁弁21を開放し、電磁弁17、電磁弁22及び電磁弁20を閉じる。そして、圧縮機2、及び、各送風機15、27を運転し、エアミックスダンパ28は室内送風機27から吹き出された空気が放熱器4及び熱媒体-空気熱交換器40に通風される状態とする。これにより、圧縮機2から吐出された高温高圧のガス冷媒は放熱器4に流入する。放熱器4には空気流通路3内の空気が通風されるので、空気流通路3内の空気は放熱器4内の高温冷媒により加熱され、一方、放熱器4内の冷媒は空気に熱を奪われて冷却され、凝縮液化する。
次に、除湿暖房モードでは、コントローラ32は上記暖房モードの状態において電磁弁22を開放する。これにより、放熱器4を経て冷媒配管13Eを流れる凝縮冷媒の一部が分流され、電磁弁22を経て冷媒配管13F及び13Bより内部熱交換器19を経て室内膨張弁8に至るようになる。室内膨張弁8にて冷媒は減圧された後、吸熱器9に流入して蒸発する。このときの吸熱作用で室内送風機27から吹き出された空気中の水分が吸熱器9に凝結して付着するので、空気は冷却され、且つ、除湿される。
次に、内部サイクルモードでは、コントローラ32は上記除湿暖房モードの状態において室外膨張弁6を全閉とする(全閉位置)と共に、電磁弁21も閉じる。この室外膨張弁6と電磁弁21が閉じられることにより、室外熱交換器7への冷媒の流入、及び、室外熱交換器7からの冷媒の流出は阻止されることになるので、放熱器4を経て冷媒配管13Eを流れる凝縮冷媒は電磁弁22を経て冷媒配管13Fに全て流れるようになる。そして、冷媒配管13Fを流れる冷媒は冷媒配管13Bより内部熱交換器19を経て室内膨張弁8に至る。室内膨張弁8にて冷媒は減圧された後、吸熱器9に流入して蒸発する。このときの吸熱作用で室内送風機27から吹き出された空気中の水分が吸熱器9に凝結して付着するので、空気は冷却され、且つ、除湿される。
次に、除湿冷房モードでは、コントローラ32は電磁弁17を開放し、電磁弁21、電磁弁22及び電磁弁20を閉じる。そして、圧縮機2、及び、各送風機15、27を運転し、エアミックスダンパ28は室内送風機27から吹き出された空気が放熱器4及び熱媒体-空気熱交換器40に通風される状態とする。これにより、圧縮機2から吐出された高温高圧のガス冷媒は放熱器4に流入する。放熱器4には空気流通路3内の空気が通風されるので、空気流通路3内の空気は放熱器4内の高温冷媒により加熱され、一方、放熱器4内の冷媒は空気に熱を奪われて冷却され、凝縮液化していく。
次に、冷房モードでは、コントローラ32は上記除湿冷房モードの状態において電磁弁20を開き(この場合、室外膨張弁6は全開(弁開度を制御上限)を含む何れの弁開度でもよい)、エアミックスダンパ28は放熱器4及び熱媒体-空気熱交換器40に空気が通風されない状態とする。これにより、圧縮機2から吐出された高温高圧のガス冷媒は放熱器4に流入する。放熱器4には空気流通路3内の空気は通風されないので、ここは通過するのみとなり、放熱器4を出た冷媒は冷媒配管13Eを経て電磁弁20及び室外膨張弁6に至る。
次に、前記暖房モードにおける圧縮機2及び室外膨張弁6の制御と、当該暖房モードでの熱媒体循環回路23による補助加熱について説明する。
コントローラ32は下記式(I)から目標吹出温度TAOを算出する。この目標吹出温度TAOは、吹出口29から車室内に吹き出される空気温度の目標値である。
TAO=(Tset-Tin)×K+Tbal(f(Tset、SUN、Tam))・・(I)
ここで、Tsetは空調操作部53で設定された車室内の設定温度、Tinは内気温度センサ37が検出する車室内空気の温度、Kは係数、Tbalは設定温度Tsetや、日射センサ51が検出する日射量SUN、外気温度センサ33が検出する外気温度Tamから算出されるバランス値である。そして、一般的に、この目標吹出温度TAOは外気温度Tamが低い程高く、外気温度Tamが上昇するに伴って低下する。
また、コントローラ32は、この暖房モードにおいて放熱器4による暖房能力が不足すると判断した場合、熱媒体加熱電気ヒータ35に通電して発熱させ、循環ポンプ30を運転することにより、熱媒体循環回路23による加熱を実行する。
QhpNI=f(Tam、Nc、BLV、VSP、FANVout、Te)・・(III)
ここで、Teは吸熱器温度センサ48が検出する吸熱器9の温度、Cpaは放熱器4に流入する空気の比熱[kj/kg・K]、ρは放熱器4に流入する空気の密度(比体積)[kg/m3]、Qairは放熱器4を通過する風量[m3/h](室内送風機27のブロワ電圧BLV等から推定)、VSPは車速センサ52から得られる車速、FANVoutは室外送風機15の電圧である。
次に、図6、図7を用いてコントローラ32による熱媒体循環回路23の制御の他の実施例を説明する。前述したように暖房モードでは室外熱交換器7において冷媒が蒸発し、外気からの吸熱が行われる。そのため、特に低外気温環境下では室外熱交換器7に外気中の水分が霜となって付着し、成長するようになる。
Qhpr=(THhp-Te)×Cpa×ρ×Qair ・・(IV)
尚、THhpは前述した放熱器温度センサ46が検出する放熱器4を経た空気の温度(即ち、放熱器温度Tci)である。
次に、図8を用いてコントローラ32による熱媒体循環回路23の制御のもう一つの他の実施例を説明する。この場合の補助加熱手段としての熱媒体循環回路23は、熱媒体加熱電気ヒータ35で加熱された熱媒体(高温の熱媒体)を循環ポンプ30により熱媒体-空気熱交換器40に循環して放熱器4を経た空気流通路3内の空気を加熱するものであるため、熱媒体を暖房に適した温度の熱媒体(高温の熱媒体)にするまでに時間を要する。そこで、この実施例の場合、コントローラ32は放熱器4による暖房能力(非着霜時暖房能力QhpNI)が不足する以前の段階から熱媒体循環回路23の予備運転を実行する。
次に、図9は本発明の車両用空気調和装置1の他の構成図を示している。この実施例では、室外熱交換器7にレシーバドライヤ部14と過冷却部16が設けられておらず、室外熱交換器7から出た冷媒配管13Aは電磁弁17と逆止弁18を介して冷媒配管13Bに接続されている。また、冷媒配管13Aから分岐した冷媒配管13Dは、同様に電磁弁21を介して内部熱交換器19の下流側における冷媒配管13Cに接続されている。
次に、図10~図12は本発明の車両用空気調和装置1のもう一つの他の構成図を示している。尚、この実施例の冷媒回路Rは図9と同様である。但し、この場合、熱媒体循環回路23の熱媒体-空気熱交換器40は、空気流通路3の空気の流れに対して放熱器4の上流側であってエアミックスダンパ28の下流側に配置されている。他の構成は図9と同様である。
次に、図13は本発明の車両用空気調和装置1の更にもう一つの他の構成図を示している。この実施例の冷媒回路R及び熱媒体循環回路23の基本構成は図1と同様であるが、熱媒体循環回路23に熱媒体-冷媒熱交換器70が設けられている。この熱媒体-冷媒熱交換器70は、循環ポンプ30を出た熱媒体配管23Aと冷媒回路Rの放熱器4を出た冷媒配管13Eとを熱交換させるものであり、この熱媒体-冷媒熱交換器70において、循環ポンプ30から吐出された熱媒体は放熱器4から出た冷媒から加熱作用を受けるように構成されている。これにより、放熱器4を経た冷媒から熱媒体循環回路23を循環する熱媒体に熱を回収することができる。
次に、図14は本発明の車両用空気調和装置1の更にもう一つの他の構成図を示している。この実施例の冷媒回路R及び熱媒体循環回路23は図13の場合と同様であるが、熱媒体循環回路23の熱媒体-空気熱交換器40が、空気流通路3の空気の流れに対して放熱器4の上流側であってエアミックスダンパ28の下流側に配置されている。このような構成によっても、放熱器4を出た冷媒が有する熱を熱媒体-冷媒熱交換器70にて熱媒体循環回路23内を流れる熱媒体に回収し、熱媒体-空気熱交換器40に搬送してより効率的な暖房補助を行うことが可能となる。
次に、図15は本発明の車両用空気調和装置1の更にもう一つの他の構成図を示している。この実施例の冷媒回路R及び熱媒体循環回路23の配管構成は図1の場合と基本的に同様であるが、放熱器4は空気流通路3には設けられておらず、その外側に配置されている。その代わりに、この放熱器4にはこの場合の熱媒体-冷媒熱交換器74が熱交換関係に配設されている。
尚、上記各実施例では補助加熱手段として熱媒体循環回路23を採用したが、通常の電気ヒータ(例えば、PTCヒータ)73にて補助加熱手段を構成してもよい。その場合の図1に対応する構成例が図16、図4に対応する制御フローチャートの例が図17、図7に対応する制御フローチャートの例が図18、図9に対応する構成例が図19である。図16、図19では図1、図9の熱媒体循環回路23がこの場合の電気ヒータ73に置き換えられている。また、図4のステップS5及びステップS6が図17のステップS5A及びステップS6A、図7のステップS13~ステップS15が、図18のステップS13A~ステップS15Aとなるが、目標TGQechが電気ヒータ73による要求暖房能力TGQehに置き換えられている。
2 圧縮機
3 空気流通路
4 放熱器
6 室外膨張弁
7 室外熱交換器
8 室内膨張弁
9 吸熱器
11 蒸発能力制御弁
17、20、21、22 電磁弁
23 熱媒体循環回路(補助加熱手段)
26 吸込切換ダンパ
27 室内送風機(ブロワファン)
28 エアミックスダンパ
30 循環ポンプ(循環手段)
32 コントローラ(制御手段)
35 熱媒体加熱電気ヒータ(電気ヒータ)
40 熱媒体-空気熱交換器
70、74 熱媒体-冷媒熱交換器
73 電気ヒータ(補助加熱手段)
R 冷媒回路
Claims (16)
- 冷媒を圧縮する圧縮機と、
車室内に供給する空気が流通する空気流通路と、
冷媒を放熱させて前記空気流通路から前記車室内に供給する空気を加熱するための放熱器と、
冷媒を吸熱させて前記空気流通路から前記車室内に供給する空気を冷却するための吸熱器と、
前記車室外に設けられて冷媒を放熱又は吸熱させる室外熱交換器と、
制御手段とを備え、
該制御手段により少なくとも、前記圧縮機から吐出された冷媒を前記放熱器にて放熱させ、放熱した当該冷媒を減圧した後、前記室外熱交換器にて吸熱させる暖房モードを実行する車両用空気調和装置において、
前記空気流通路から前記車室内に供給する空気を加熱するための補助加熱手段を備え、
前記制御手段は、前記放熱器による暖房能力が不足する場合、前記補助加熱手段による加熱を実行することを特徴とする車両用空気調和装置。 - 前記制御手段は、要求される放熱器の暖房能力である要求暖房能力Qtgtと前記放熱器が発生する暖房能力Qhpとを比較し、該暖房能力Qhpが前記要求暖房能力Qtgtより不足する分を前記補助加熱手段の加熱により補完することを特徴とする請求項1に記載の車両用空気調和装置。
- 前記暖房能力Qhpは、前記室外熱交換器の非着霜時に前記放熱器が発生する非着霜時暖房能力QhpNIであり、該非着霜時暖房能力QhpNIが前記要求暖房能力Qtgtより不足する分を前記補助加熱手段の加熱により補完することを特徴とする請求項2に記載の車両用空気調和装置。
- 前記制御手段は、前記放熱器が実際に発生する実暖房能力Qhprが前記非着霜時暖房能力QhpNIよりも小さい場合、該非着霜時暖房能力QhpNIと実暖房能力Qhprの差を加えて前記補助加熱手段により加熱することを特徴とする請求項3に記載の車両用空気調和装置。
- 前記制御手段は、前記放熱器が実際に発生する実暖房能力Qhprが前記非着霜時暖房能力QhpNIよりも小さく、該非着霜時暖房能力QhpNIと実暖房能力Qhprとの差が所定値より大きい場合、前記圧縮機を停止すると共に、前記要求暖房能力Qtgtにより前記補助加熱手段を制御することを特徴とする請求項3又は請求項4に記載の車両用空気調和装置。
- 前記制御手段は、前記放熱器から流出する空気の温度、及び、該放熱器を通過する風量のそれぞれを示す指標のうちの何れか、若しくは、それらの組み合わせと、前記放熱器に流入する空気の比熱、及び、該空気の密度を示す指標とに基づいて前記実暖房能力Qhprを算出することを特徴とする請求項4又は請求項5に記載の車両用空気調和装置。
- 前記制御手段は、前記放熱器に流入する空気の温度、該放熱器から流出する空気の温度、及び、該放熱器を通過する風量のそれぞれを示す指標のうちの何れか、若しくは、それらの組み合わせと、前記放熱器に流入する空気の比熱、及び、該空気の密度を示す指標とに基づいて前記要求暖房能力Qtgtを算出すると共に、
外気温度、冷媒流量、前記空気流通路内の風量、車速、前記室外熱交換器通過風量、該室外熱交換器に通風する室外送風機の電圧、前記吸熱器の温度、前記圧縮機の回転数、前記放熱器出口の冷媒圧力、前記放熱器出口の冷媒温度、前記放熱器入口の冷媒圧力、及び
、前記放熱器入口の冷媒温度のそれぞれを示す指標のうちの何れか、若しくは、それらの組み合わせに基づいて前記非着霜時暖房能力QhpNIを算出することを特徴とする請求項3乃至請求項6のうちの何れかに記載の車両用空気調和装置。 - 前記空気流通路外に前記放熱器を設けると共に、
該放熱器と熱交換する熱媒体-冷媒熱交換器と、前記空気流通路に設けられた熱媒体-空気熱交換器と、電気ヒータと、循環手段とを有し、前記熱媒体-冷媒熱交換器、及び/又は、前記電気ヒータにより加熱された熱媒体を前記循環手段により前記熱媒体-空気熱交換器に循環させる熱媒体循環回路から前記補助加熱手段を構成したことを特徴とする請求項1乃至請求項7のうちの何れかに記載の車両用空気調和装置。 - 前記空気流通路に設けられ、前記車室内に供給する空気を加熱する電気ヒータにより前記補助加熱手段を構成したことを特徴とする請求項1乃至請求項7のうちの何れかに記載の車両用空気調和装置。
- 前記放熱器を前記空気流通路に設けると共に、
該空気流通路に設けられた熱媒体-空気熱交換器と、電気ヒータと、循環手段とを有し、前記電気ヒータにより加熱された熱媒体を前記循環手段により前記熱媒体-空気熱交換器に循環する熱媒体循環回路から前記補助加熱手段を構成したことを特徴とする請求項1乃至請求項7のうちの何れかに記載の車両用空気調和装置。 - 前記熱媒体循環回路は、前記放熱器を経た冷媒から熱を回収する熱媒体-冷媒熱交換器を有することを特徴とする請求項10に記載の車両用空気調和装置。
- 前記制御手段は、前記放熱器による暖房能力は不足していないが、前記室外熱交換器の非着霜時に前記放熱器が発生する非着霜時暖房能力QhpNIと要求される放熱器の暖房能力である要求暖房能力Qtgtとの差が所定値に縮小した場合、前記熱媒体循環回路による加熱を開始する予備運転を実行することを特徴とする請求項10又は請求項11に記載の車両用空気調和装置。
- 前記制御手段は、前記予備運転を実行中、前記熱媒体循環回路により加熱する分、前記放熱器による暖房能力を低下させることを特徴とする請求項12に記載の車両用空気調和装置。
- 前記制御手段は、前記予備運転を実行中、前記熱媒体循環回路を流れる熱媒体の温度が所定値より低い場合、前記熱媒体-空気熱交換器に循環される熱媒体の量を制限することを特徴とする請求項12又は請求項13に記載の車両用空気調和装置。
- 前記電気ヒータ、又は、前記熱媒体-空気熱交換器を、前記空気流通路の空気の流れに対して前記放熱器の下流側に配置したことを特徴とする請求項9乃至請求項14のうちの何れかに記載の車両用空気調和装置。
- 前記電気ヒータ、又は、前記熱媒体-空気熱交換器を、前記空気流通路の空気の流れに対して前記放熱器の上流側に配置したことを特徴とする請求項9乃至請求項14のうちの何れかに記載の車両用空気調和装置。
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