WO2015033916A1 - 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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- WO2015033916A1 WO2015033916A1 PCT/JP2014/073025 JP2014073025W WO2015033916A1 WO 2015033916 A1 WO2015033916 A1 WO 2015033916A1 JP 2014073025 W JP2014073025 W JP 2014073025W WO 2015033916 A1 WO2015033916 A1 WO 2015033916A1
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- refrigerant
- compressor
- heat exchanger
- outdoor heat
- radiator
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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
- B60H1/00357—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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
- B60H1/00764—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models the input being a vehicle driving condition, e.g. speed
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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
- B60H1/00914—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is a bypass of the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- B60H2001/00957—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 locations with heat exchange within the refrigerant circuit itself, e.g. cross-, counter-, or parallel heat exchange
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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
- B60H2001/00961—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 means for defrosting outside heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
Definitions
- the present invention relates to a heat pump type vehicle air conditioner that air-conditions the interior of a vehicle.
- a compressor that compresses and discharges the refrigerant
- a radiator that is provided in an air flow passage in the passenger compartment and dissipates the refrigerant
- a refrigerant circuit composed of a heat absorber (evaporator) that is provided in the air flow passage and absorbs the refrigerant, and an outdoor heat exchanger that is provided outside the vehicle cabin and dissipates or absorbs the refrigerant, and is discharged from the compressor
- a heat mode in which the radiated refrigerant is dissipated in the radiator and the refrigerant radiated in the radiator is absorbed in the outdoor heat exchanger, and the refrigerant discharged from the compressor is radiated in the radiator, and the refrigerant radiated in the radiator
- a dehumidifying and heating mode in which heat is absorbed only in the heat absorber and
- the refrigerant that has flowed out of the radiator is divided, and after the refrigerant that has been diverted is depressurized, heat is exchanged with the refrigerant that has flowed out of the radiator, and an injection circuit is provided to return to the middle of compression of the compressor, thereby Some have been developed to increase the refrigerant discharged from the compressor and improve the heating capability of the radiator (see, for example, Patent Document 2).
- JP 2012-176660 A Japanese Patent No. 3985384
- the refrigerant absorbs heat from the outside air in the outdoor heat exchanger. That is, since the outdoor heat exchanger becomes an evaporator, moisture in the outside air adheres to the outdoor heat exchanger as frost and grows. When frost is generated in the outdoor heat exchanger, it becomes a heat insulating material and hinders heat exchange between the outside air and the refrigerant.In such a case, the high temperature refrigerant from the compressor is allowed to flow through the outdoor heat exchanger to remove the frost. The frost mode will be executed. In that case, the heat absorption is performed by the heat absorber, so that the air blown into the vehicle interior through the air flow passage is cooled, and heating of the vehicle interior is inhibited. There was a problem.
- the present invention has been made to solve the conventional technical problem, and in the defrosting mode for defrosting the outdoor heat exchanger, the outdoor heat exchanger is removed while maintaining the heating of the vehicle interior.
- An object of the present invention is to provide a vehicle air conditioner that can realize frost without hindrance.
- An air conditioner for a vehicle includes a compressor that compresses a refrigerant, an air flow passage through which air to be supplied to the vehicle interior flows, a radiator that is provided in the air flow passage and radiates heat from the refrigerant, and an air flow A heat absorber that absorbs the refrigerant by being provided in the road, an outdoor heat exchanger that is provided outside the passenger compartment to dissipate or absorb the refrigerant, and a control means, and is discharged from the compressor by the control means.
- the refrigerant is radiated by a radiator, the radiated refrigerant is depressurized, and the outdoor heat exchanger absorbs heat to heat the interior of the vehicle.
- a part of the refrigerant exiting the radiator is shunted.
- An injection circuit for returning to the compressor is provided, and the control means operates the injection circuit to return the refrigerant to the compressor when defrosting by flowing a high-temperature refrigerant to the outdoor heat exchanger.
- the control means when there is a heating request in the vehicle interior, causes the refrigerant discharged from the compressor to radiate heat with a radiator and an outdoor heat exchanger, thereby After depressurizing the refrigerant, a dehumidifying and cooling type defrosting mode in which heat is absorbed by a heat absorber is executed, and an injection circuit is operated.
- a vehicular air conditioner according to the first aspect of the present invention, wherein the control means diverts a part of the refrigerant discharged from the compressor and passes through a radiator when there is a heating request in the passenger compartment.
- the hot gas defrosting mode is performed in which the refrigerant flows into the outdoor heat exchanger without being discharged, and the radiated refrigerant is returned to the compressor, and the injection circuit is operated.
- an air conditioner for a vehicle includes an outdoor fan that ventilates the outdoor heat exchanger in each of the above-described inventions, and the control means defrosts the outdoor heat exchanger when the outdoor heat exchanger is defrosted.
- the outdoor air blower is operated when the temperature of the lamp is equal to or higher than a predetermined value.
- the control means uses the radiator discharged from the compressor and the outdoor heat.
- the dehumidifying and cooling type defrosting mode in which the heat is radiated by the exchanger and the radiated refrigerant is decompressed and then absorbed by the heat absorber is executed, and the injection circuit is not operated.
- an air conditioner for a vehicle according to the second to fifth aspects of the present invention, wherein the control means uses an outdoor heat exchanger to cool the refrigerant discharged from the compressor when there is no request for heating the vehicle interior. Run a simple hot gas defrosting mode that releases heat and returns the released heat to the compressor, does not operate the injection circuit, or diverts part of the refrigerant discharged from the compressor and passes through the radiator. The hot gas defrosting mode is performed in which the refrigerant flows into the outdoor heat exchanger and dissipates heat, and the dissipated refrigerant is returned to the compressor, and the injection circuit is not operated.
- an air conditioning apparatus for a vehicle according to each of the first and second aspects of the present invention, wherein the control means compresses when the power is supplied from an external power source to the compressor or a battery that supplies power to drive the compressor.
- the refrigerant discharged from the machine is radiated with a radiator and an outdoor heat exchanger, and after depressurizing the radiated refrigerant, the dehumidifying and cooling type defrosting mode for absorbing heat with the heat absorber is performed, and the injection circuit is operated.
- a part of the refrigerant discharged from the compressor is diverted to flow into the outdoor heat exchanger without passing through the heat radiator to dissipate the heat, and a hot gas defrosting mode is performed in which the released heat is returned to the compressor.
- the injection circuit is operated and power is not supplied from an external power source, the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is returned to the compressor.
- Run the gas defrosting mode, the injection circuits without operating, or to perform a hot gas defrosting mode the injection circuits is characterized in that it does not operate.
- the vehicle air conditioner according to an eighth aspect of the present invention is the vehicle air conditioner according to the eighth aspect, wherein the control means executes the simple hot gas defrosting mode when power is not supplied from an external power source and the remaining battery level is low.
- the injection circuit is not operated, or the hot gas defrosting mode is executed and the injection circuit is not operated.
- the air conditioner for a vehicle according to the invention of claim 9 is characterized in that, in each of the above inventions, the control means dissipates the heat discharged from the compressor by the outdoor heat exchanger until the vehicle interior temperature becomes lower than a predetermined value. After the decompression of the refrigerant, the reverse cycle defrosting mode is performed in which the heat is absorbed by the heat absorber, the injection circuit is not operated, and the refrigerant discharged from the compressor when the vehicle interior temperature becomes lower than a predetermined value.
- the control means defrosts the outdoor heat exchanger
- the vehicle interior temperature is lower than a predetermined value or the vehicle interior needs to be heated.
- the introduction of outside air into the air flow passage is stopped.
- the vehicle air conditioner according to the invention of claim 12 is characterized in that, in each of the above inventions, the control means defrosts the outdoor heat exchanger when the vehicle speed is a predetermined value or less.
- the compressor that compresses the refrigerant, the air flow passage through which the air supplied to the passenger compartment flows, the radiator that is provided in the air flow passage to dissipate the refrigerant, and the air flow passage are provided.
- the control means allows the refrigerant discharged from the compressor to In a vehicle air conditioner that heats the interior of a vehicle by depressurizing the refrigerant that has been radiated and depressurizing the radiated refrigerant, and then heating the interior of the vehicle by using an outdoor heat exchanger, a part of the refrigerant that has exited the radiator is diverted. And the control means operates the injection circuit to return the refrigerant to the compressor when defrosting by flowing a high-temperature refrigerant to the outdoor heat exchanger.
- the control unit When there is a heating requirement
- the refrigerant discharged from the compressor is radiated by the radiator and the outdoor heat exchanger, and after the decompressed refrigerant is decompressed, the dehumidifying and cooling type defrosting mode is performed in which the heat is absorbed by the heat absorber, and the injection circuit is operated.
- the heating capacity of the radiator can be improved, and the vehicle interior temperature can be maintained.
- the control means when there is a heating request in the vehicle compartment, A part of the refrigerant discharged from the machine is diverted to flow into the outdoor heat exchanger without passing through the radiator to dissipate the heat, and a hot gas defrosting mode is performed in which the released refrigerant is returned to the compressor.
- the heating capacity of the radiator can be improved by the injection circuit without performing heat absorption in the heat absorber, and this is effective particularly in a situation where the vehicle interior temperature is extremely low.
- the outdoor heat exchanger is provided with an outdoor fan for ventilating the outside air as in the invention of claim 4, and when the control means defrosts the outdoor heat exchanger, the temperature of the outdoor heat exchanger is a predetermined value or more.
- the control means radiates the refrigerant discharged from the compressor with a radiator and an outdoor heat exchanger, and depressurizes the radiated refrigerant. After that, if the dehumidifying and cooling type defrosting mode in which heat is absorbed by the heat absorber is executed and the injection circuit is not operated, the injection circuit is operated in an environment where the outside air temperature is high and it is easy to maintain the heating capacity of the vehicle interior. Without this, more refrigerant can be supplied to the outdoor heat exchanger, and defrosting can be promoted.
- the control means as in the sixth aspect of the invention simply dissipates the refrigerant discharged from the compressor in the outdoor heat exchanger and returns the dissipated refrigerant to the compressor.
- Execute hot gas defrosting mode do not operate the injection circuit, or divert part of the refrigerant discharged from the compressor and let it flow into the outdoor heat exchanger without passing through the radiator to dissipate heat. If the hot gas defrosting mode for returning the refrigerant to the compressor is executed and the injection circuit is not operated, the outdoor heat exchanger can be quickly defrosted to minimize power consumption. Thus, it becomes extremely effective in an electric vehicle or the like.
- the control means as in the invention of claim 7 includes: When power is supplied from an external power supply, dehumidifying and cooling type defrosting mode in which the refrigerant discharged from the compressor is dissipated by the radiator and the outdoor heat exchanger, and the radiated refrigerant is decompressed and then absorbed by the heat absorber.
- the injection circuit is operated, or a part of the refrigerant discharged from the compressor is diverted to flow into the outdoor heat exchanger without passing through the radiator to dissipate the heat.
- the refrigerant discharged from the compressor is transferred to the outdoor heat exchanger.
- a hot gas defrosting mode for returning the refrigerant that has been heated and released to the compressor is executed, the injection circuit is operated, and the refrigerant discharged from the compressor is supplied to the outdoor heat exchanger when power is not supplied from an external power source. Execute a simple hot gas defrost mode to return the refrigerant that has been radiated and return it to the compressor and do not operate the injection circuit, or execute the hot gas defrost mode and do not operate the injection circuit.
- the heating of the vehicle interior is maintained while the defrosting of the outdoor heat exchanger is performed in the dehumidifying and cooling type defrosting mode or the hot gas defrosting mode as in the inventions of claims 2 and 3. If not, let all refrigerant flow through the outdoor heat exchanger without operating the injection circuit in the simple hot gas defrost mode or hot gas defrost mode. And defrosting the speed, it is possible to reduce the power consumption.
- the simple hot gas defrosting mode is executed and the injection circuit is operated.
- the hot gas defrosting mode is executed and the injection circuit is not operated, so that when the battery is not plugged in and the remaining battery level is low, the simple hot gas removal that does not operate the injection circuit.
- the frost mode or the hot gas defrost mode is executed, and accurate defrost control that takes into account the remaining battery level in addition to whether or not plugged in is possible.
- control means causes the refrigerant discharged from the compressor to radiate heat in the outdoor heat exchanger until the vehicle interior temperature becomes lower than a predetermined value, and decompresses the radiated refrigerant. Run the reverse cycle defrost mode to absorb heat with the heat absorber, do not operate the injection circuit, execute the dehumidifying and cooling type defrost mode when the passenger compartment temperature is lower than the predetermined value, and also operate the injection circuit If the refrigerant also dissipates heat in the radiator, it is possible to realize control that satisfies both the rapid defrosting of the outdoor heat exchanger and the maintenance of heating in the passenger compartment.
- control means defrosts the outdoor heat exchanger as in the invention of claim 10
- the outside air to the air flow passage is By stopping the introduction, it is possible to stop the introduction of the outside air having a low temperature under the condition where the vehicle interior temperature is low and to maintain the heating capacity.
- the dehumidifying and cooling type defrosting mode or the hot gas defrosting mode is executed as in the invention of the eleventh aspect, if the introduction of the outside air to the air flow passage is stopped, the heating capacity is similarly maintained. Can be achieved.
- control means as in the invention of claim 12 defrosts the outdoor heat exchanger when the vehicle speed is equal to or lower than a predetermined value, thereby performing defrosting in a situation where there is little circulation of outside air to the outdoor heat exchanger, It is possible to improve the defrosting effect.
- FIG. 2 is a Ph diagram in a reverse cycle defrost mode of the vehicle air conditioner of FIG. 1.
- FIG. 2 is a Ph diagram in the first dehumidifying and cooling type defrosting mode of the vehicle air conditioner of FIG. 1.
- It is a control block diagram regarding the compressor control in the reverse cycle defrost mode and the 1st dehumidification cooling type defrost mode by the controller of FIG.
- It is a control block diagram regarding outdoor expansion valve control in the reverse cycle defrost mode and the first dehumidifying and cooling type defrost mode by the controller of FIG.
- FIG. 3 is a control block diagram related to injection expansion valve control in a reverse cycle defrost mode, a first dehumidifying and cooling type defrost mode, and a hot gas defrost mode by the controller of FIG. 2. It is another control block diagram regarding the injection expansion valve control in the reverse cycle defrost mode, the 1st dehumidification cooling type defrost mode, and the hot gas defrost mode by the controller of FIG. It is a figure explaining determination of the target blowing temperature by the controller of FIG. It is a flowchart explaining the operation
- FIG. 6 is a Ph diagram in a simple hot gas defrosting mode of the vehicle air conditioner of FIG. 1 executed in another embodiment of the present invention. It is a control block diagram regarding the compressor control in the simple hot gas defrost mode and the hot gas defrost mode by the controller of FIG. It is a flowchart explaining operation
- FIG. 16 is a Ph diagram of the configuration of FIG. 15 in a hot gas defrost mode. It is a flowchart explaining the operation
- FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention.
- the vehicle of the embodiment to which the present invention is applied is an electric vehicle (EV) that does not have an engine (internal combustion engine), and travels by driving an electric motor for traveling with electric power charged in a battery.
- the vehicle air conditioner 1 of the present invention is also driven by battery power. That is, the vehicle air conditioner 1 according to the embodiment selectively selects each operation mode such as heating, dehumidifying heating, dehumidifying cooling, and cooling by a heat pump operation using a refrigerant circuit in an electric vehicle that cannot be heated by engine waste heat. It is something to execute.
- 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.
- a vehicle air conditioner 1 performs air conditioning (heating, cooling, dehumidification, and ventilation) in a passenger compartment of an electric vehicle, and includes an electric compressor (electric compressor) 2 that compresses refrigerant.
- the radiator 4 is provided in the air flow passage 3 of the HVAC unit 10 through which the passenger compartment air is circulated to dissipate the high-temperature and high-pressure refrigerant discharged from the compressor 2 into the passenger compartment, and the refrigerant is decompressed and expanded during heating.
- An outdoor expansion valve 6 composed of a motor-operated valve, and an outdoor unit that exchanges heat between the refrigerant and the outside air so as to function as a radiator (dissipates the refrigerant) during cooling, and as an evaporator (absorbs heat from the refrigerant) during heating
- the outdoor heat exchanger 7 is provided with an outdoor fan 15 for exchanging heat between the outside air and the refrigerant.
- 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 refrigerant pipe 13I to which the outdoor expansion valve 6 is connected.
- the branched refrigerant pipe 13F is an electromagnetic valve (open / close valve) that is opened during dehumidification. ) 22 and is connected to the refrigerant pipe 13B on the downstream side of the check valve 18.
- a bypass pipe 13J is connected to the refrigerant pipe 13I located between the refrigerant pipe 13E and the outdoor heat exchanger 7 and connected to the outdoor expansion valve 6 in parallel with the outdoor expansion valve 6.
- the bypass pipe 13J is provided with an electromagnetic valve (open / close valve) 20 that is opened in the cooling mode and bypasses the outdoor expansion valve 6 to flow the refrigerant.
- the refrigerant pipe 13E immediately after exiting the radiator 4 (before branching to the refrigerant pipes 13F and 13I) is branched, and the branched refrigerant pipe 13K is provided with an injection expansion valve 30 comprising an electric valve for injection control.
- the compressor 2 is in communication with the compressor 2 during compression.
- coolant piping 13K between the exit side of this injection expansion valve 30 and the compressor 2 is provided in the refrigerant
- the refrigerant circuit 13K, the injection expansion valve 30, and the discharge side heat exchanger 35 constitute an injection circuit 40.
- the injection circuit 40 is a circuit for diverting a part of the refrigerant from the radiator 4 and returning it to the middle of compression of the compressor 2 (gas injection).
- the injection expansion valve 30 opens, and a part of the refrigerant discharged from the radiator 4 is diverted to the refrigerant pipe 13K.
- the injection expansion valve 30 decompresses the refrigerant that has flowed into the refrigerant pipe 13K, and then flows it into the discharge-side heat exchanger 35.
- the refrigerant flowing into the discharge side heat exchanger 35 is discharged from the compressor 2 to the refrigerant pipe 13G, exchanges heat with the refrigerant before flowing into the radiator 4, and absorbs heat from the refrigerant flowing through the refrigerant pipe 13G to evaporate. It is said that.
- Gas refrigerant to the compressor 2 is performed by evaporating the refrigerant diverted to the refrigerant pipe 13K in the discharge side heat exchanger 35.
- 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.
- 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 air downstream side of the radiator 4, each of a foot (blowing toward the passenger's feet), a vent (blowing toward the upper body of the occupant), and a differential (blowing to the inner surface of the windshield) are provided.
- a blower outlet (represented by a blower outlet 29 in FIG. 1) is formed, and the blower outlet 29 is provided with a blower outlet switching damper 31 that performs switching control of air blowing from each of the blower outlets. .
- reference numeral 32 in FIG. 2 denotes a controller (ECU) as a control means constituted by a microcomputer, and an input to the controller 32 is an outside air temperature sensor 33 for detecting the outside air temperature of the vehicle, and an outside air humidity is detected.
- ECU controller
- an input to the controller 32 is an outside air temperature sensor 33 for detecting the outside air temperature of the vehicle, and an outside air humidity is detected.
- 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
- the blowout temperature sensor 41 that detects the temperature of the air blown from the blowout port 29 into the vehicle interior.
- a sensor 48 a heat absorber pressure sensor 49 for detecting the refrigerant pressure of the heat absorber 9 (the pressure of the refrigerant in the heat absorber 9 or immediately after leaving the heat absorber 9), and the amount of solar radiation into the passenger compartment.
- a photosensor-type solar radiation sensor 51 and the moving speed (vehicle speed) of the vehicle are detected.
- Vehicle speed sensor 52 an air conditioning (air conditioner) operation unit 53 for setting a set temperature and switching of operation modes, the temperature of the outdoor heat exchanger 7 (the temperature of the refrigerant immediately after coming out of the outdoor heat exchanger 7, Alternatively, the outdoor heat exchanger temperature sensor 54 that detects the temperature of the outdoor heat exchanger 7 itself, and the refrigerant pressure of the outdoor heat exchanger 7 (in the outdoor heat exchanger 7 or immediately after exiting from the outdoor heat exchanger 7).
- the outputs of the outdoor heat exchanger pressure sensor 56 for detecting the refrigerant pressure) are connected.
- the input of the controller 32 further includes an injection pressure sensor 50 that detects the pressure of the injection refrigerant that flows into the refrigerant pipe 13K of the injection circuit 40 and returns to the middle of the compression of the compressor 2 via the discharge side heat exchanger 35;
- Each output of an injection temperature sensor 55 that detects the temperature of the injection refrigerant is also connected.
- the input of the compressor 32 is also connected to the output of an occupant sensor 57 that detects whether or not an occupant is in the passenger compartment.
- 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 injection expansion valve 30, 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 and cooling mode, and an air conditioning operation mode of the cooling mode, and the defrosting mode is switched.
- each air conditioning operation mode will be described.
- 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, a part of the refrigerant is diverted to the refrigerant pipe 13K of the injection circuit 40, and mainly reaches the outdoor expansion valve 6 via the refrigerant pipe 13E.
- the functional operation of the injection circuit 40 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 that has flowed into the outdoor heat exchanger 7 evaporates, and pumps heat from the outside air that is ventilated by traveling or by the outdoor blower 15 (heat pump).
- 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 air outlet 29, the vehicle interior is thereby heated.
- the controller 32 controls the compressor 2 based on the refrigerant pressure Pci of the radiator 4 (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 (or the discharge pressure sensor 42) and the target radiator pressure PCO. While controlling the number of revolutions, the valve opening degree of the outdoor expansion valve 6 is controlled based on the passing air volume of the radiator 4 and a target blowing temperature described later, and the degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled. The valve opening degree of the outdoor expansion valve 6 may be controlled based on the temperature of the radiator 4 or the outside air temperature instead of or in addition to them.
- 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 to reach 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 has a refrigerant pressure Pci (high pressure of the refrigerant circuit R) of the radiator 4 and a target radiator pressure PCO detected by the radiator pressure sensor 47 (or the discharge pressure sensor 42) detected by the radiator pressure sensor 47.
- the target heat absorber temperature TEO which is a target value of the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the temperature of the heat absorber 9, is controlled. 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. Even in this internal cycle mode, gas injection by the injection circuit 40 is not performed, so the injection expansion valve 30 is fully closed (fully closed position).
- 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 sets the air blown out from the indoor blower 27 to the heat radiator 4. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 through the discharge-side heat exchanger 35. Since 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. To control the refrigerant pressure of the radiator 4 (radiator pressure Pci). In addition, since the gas injection by the injection circuit 40 is not performed even in this dehumidifying and cooling mode, the injection expansion valve 30 is fully closed (fully closed position).
- 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.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 through the discharge-side heat exchanger 35. 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. 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. In this cooling mode, since the gas injection by the injection circuit 40 is not performed, the injection expansion valve 30 is fully closed (fully closed position).
- Air-conditioning operation mode switching control The controller 32 selects the operation mode based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target outlet temperature TAO at the time of activation. Further, after the start-up, each of the operation modes is selected and switched according to changes in the environment such as the outside air temperature Tam and the target blowing temperature TAO and the set conditions. In this case, the controller 32 basically shifts from the heating mode to the dehumidifying heating mode, or from the dehumidifying heating mode to the heating mode, and from the dehumidifying heating mode to the dehumidifying cooling mode, or from the dehumidifying cooling mode to the dehumidifying heating mode.
- shifting to the transition is made via the internal cycle mode.
- the cooling mode is changed to the internal cycle mode, and the internal cycle mode is changed to the cooling mode.
- the heating capacity of the radiator 4 is improved. Moreover, since the refrigerant
- the controller 32 monitors the degree of superheat of the refrigerant toward the middle of compression of the compressor 2 from the pressure and temperature of the refrigerant after the discharge-side heat exchanger 35 detected by the injection pressure sensor 50 and the injection temperature sensor 55, respectively.
- the valve opening degree of the injection expansion valve 30 is controlled so that a predetermined degree of superheat is obtained by heat exchange with the discharged refrigerant.
- the discharge side heat exchanger 35 discharges from the compressor 2.
- the heating capacity can be improved.
- Example 1 the defrost mode of the vehicle air conditioner 1 according to the embodiment will be described with reference to FIGS. 3 to 11.
- the controller 32 has a reverse cycle defrost mode, a first dehumidifying and cooling type defrosting mode, and a second dehumidifying and cooling type defrosting mode as the defrosting modes, and switches them according to the situation. And execute.
- the first dehumidifying and cooling type defrosting mode and the second dehumidifying and cooling type defrosting mode are both included in the dehumidifying and cooling type defrosting mode of the present invention (for the simple hot gas defrosting mode and the hot gas defrosting mode). It will be described in another embodiment).
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 through the discharge-side heat exchanger 35, but the air in the air flow passage 3 is not vented to the radiator 4. Only passes, and the refrigerant exiting the radiator 4 reaches the electromagnetic valve 20 and the outdoor expansion valve 6 through the refrigerant pipe 13E. At this time, since the solenoid valve 20 is opened, the refrigerant bypasses the outdoor expansion valve 6 and passes through the bypass pipe 13J, flows into the outdoor heat exchanger 7 as it is, dissipates heat, and is condensed and liquefied. The frost adhering to the outdoor heat exchanger 7 is melted by the heat radiation at this time.
- the refrigerant that has exited the outdoor heat exchanger 7 passes through the refrigerant pipe 13A through the electromagnetic valve 17 and the receiver dryer section 14 and the supercooling section 16 in sequence, enters the refrigerant pipe 13B through the check valve 18, and enters the internal heat exchanger 19.
- the indoor expansion valve 8 After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9, evaporates, absorbs heat from the air passing through the air flow passage 3, passes through the evaporation capacity control valve 11, and the internal heat exchanger 19, and then the refrigerant.
- the circulation reaches the accumulator 12 through the pipe 13C and is sucked into the compressor 2 therethrough.
- the injection circuit 40 is not operated (step S15 of FIG. 10).
- the reverse cycle defrosting mode is performed, and the injection circuit is used at that time. 40 may be operated.
- FIG. 3 shows a Ph diagram in the reverse cycle defrosting mode in that case.
- the gas injection is not performed on the left side (reverse cycle defrosting mode of an example described later), the gas injection is performed on the right side. Shows each time. A portion indicated by 13K in the figure indicates the refrigerant to be gas-injected.
- the refrigerant flow in the first dehumidifying and cooling type defrosting mode is the same as that in the dehumidifying and cooling mode described above. That is, in the first dehumidifying and cooling type defrosting mode, 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 (MH) in which all the air blown out from the indoor blower 27 is passed through the radiator 4.
- MH state
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 through the discharge-side heat exchanger 35. Since 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 dissipates heat and condenses into liquid.
- the frost adhering to the outdoor heat exchanger 7 is melted by the heat radiation at this time.
- the refrigerant that has exited the outdoor heat exchanger 7 sequentially flows from the refrigerant pipe 13A through the solenoid valve 17 to the receiver dryer section 14 and the supercooling section 16, and then enters the refrigerant pipe 13B through the check valve 18 to enter the internal heat exchanger 19. Then, the indoor expansion valve 8 is reached. After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9, evaporates, absorbs heat from the air passing through the air flow passage 3, passes through the evaporation capacity control valve 11, and the internal heat exchanger 19, and then the refrigerant. The circulation reaches the accumulator 12 through the pipe 13C and is sucked into the compressor 2 therethrough.
- FIG. 4 shows a Ph diagram when gas injection is performed in the first dehumidifying and cooling type defrosting mode. When the gas injection is not performed on the left side (dehumidifying cooling mode), the gas injection is performed on the right side. Each time is shown. A portion indicated by 13K in the figure indicates the refrigerant to be gas-injected.
- the heating capacity by the radiator 4 and the defrosting capacity of the outdoor heat exchanger 7 are improved when the gas injection is performed by the injection circuit 40 (right side) and when it is not performed (left side). (Upper side of Ph diagram). On the other hand, it can be seen that the cooling action (the lower side of the Ph diagram) does not change much.
- FIG. 5 shows the compressor 2 for the reverse cycle defrosting mode and the first dehumidifying and cooling type defrosting mode.
- the F / B (feedback) manipulated variable calculator 59 calculates the F / B manipulated variable TGNCcfb of the compressor target rotational speed based on the target heat absorber temperature TEO and the heat absorber temperature Te. Then, the F / F manipulated variable TGNCcff computed by the F / F manipulated variable computing unit 58 and the F / B manipulated variable TGNCcfb computed by the F / B manipulated variable computing unit 59 are added by the adder 61, and the compressor OFF control unit After the limit of the control upper limit value and the control lower limit value is set by the limit setting unit 63 after 62 (the minimum rotation speed at which the compressor 2 can be operated is specified), it is determined as the compressor target rotation speed TGNCc. In the reverse cycle defrost mode and the first dehumidifying and cooling type defrost mode, the controller 32 controls the rotation speed of the compressor 2 based on the compressor target rotation speed TGNCc.
- FIG. 6 shows an outdoor expansion valve in reverse cycle defrosting mode and first dehumidifying and cooling type defrost mode.
- 6 is a control block diagram of a controller 32 for determining a target opening 6 (outdoor expansion valve target opening) TGECCVpc.
- the F / F manipulated variable calculation unit 64 of the controller 32 adjusts the target radiator temperature TCO, the blower voltage BLV, the outside air temperature Tam, the air mix damper opening SW, the target heat absorber temperature TEO, and the target radiator pressure PCO. Based on this, the F / F manipulated variable TGECCVpcff of the outdoor expansion valve target opening is calculated.
- the F / B manipulated variable calculator 66 calculates the F / B manipulated variable TGECCVpcfb of the outdoor expansion valve target opening based on the target radiator pressure PCO and the radiator pressure PCI. Then, the F / F manipulated variable TGECCVpcff computed by the F / F manipulated variable computing unit 64 and the F / B manipulated variable TGECCVpcfb computed by the F / B manipulated variable computing unit 66 are added by the adder 67, and the limit setting unit 68 After the control upper limit value and the control lower limit value are set, the outdoor expansion valve target opening degree TGECCVpc is determined. In the reverse cycle defrosting mode and the first dehumidifying and cooling type defrosting mode, the controller 32 controls the valve opening degree of the outdoor expansion valve 6 based on the outdoor expansion valve target opening degree TGECCVpc.
- FIG. 7 shows the target opening (injection expansion valve target opening) TGECCVsh of the injection expansion valve 30 of the injection circuit 40 when the rotation speed NC of the compressor 2 is lower than the predetermined value N1 (in the case of a low rotation speed). It is a control block diagram of the controller 32 to determine.
- gas injection is performed in the first dehumidifying and cooling type defrosting mode (including the case of performing gas injection in the above-described reverse cycle defrosting mode) and the hot gas defrosting mode.
- the injection refrigerant superheat degree calculation unit 69 of the controller 32 performs the compression of the compressor 2 from the injection circuit 40 based on the difference between the temperature of the injection refrigerant (injection refrigerant temperature Tinj) detected by the injection temperature sensor 55 and the saturation temperature Tsatinj.
- the degree of superheat (injection refrigerant superheat) SHinj of the returned injection refrigerant is calculated.
- the F / B manipulated variable calculation unit 71 calculates the injection refrigerant superheat degree SHinj calculated by the injection refrigerant superheat degree calculation unit 69 and the target value of the superheat degree of the injection refrigerant returned from the injection circuit 40 during the compression of the compressor 2. Based on (target injection refrigerant superheat degree TGSHinj), the F / B manipulated variable TGECCVshfb of the injection expansion valve target opening is calculated.
- the F / B manipulated variable calculation unit 71 operates when a predetermined injection request flag fINJONreq is “1” (set), and stops calculation when it is “0” (reset).
- the F / B operation amount TGECCVshfb calculated by the F / B operation amount calculation unit 71 and the F / F operation amount TGECCVshff of the injection expansion valve 30 determined in advance are added by the adder 72, and the limit setting unit 73 After the control upper limit value and the control lower limit value are set, they are input to the injection possibility switching unit 74. Further, “0” (the injection expansion valve 30 is fully closed) is input to the injection possibility switching unit 74. When the injection request flag fINJONreq is “1” (set), the value passed through the limit setting unit 73 is the injection value.
- the expansion valve target opening degree TGECCVsh is determined and output.
- the injection availability switching unit 74 When the injection request flag fINJONreq is “0” (reset), the injection availability switching unit 74 outputs “0” as the injection expansion valve target opening TGECCVsh. That is, when the rotational speed NC of the compressor 2 is a low rotational speed lower than the predetermined value N1, when the injection request flag fINJONreq is set to “1”, the controller 32 determines the superheating degree SHinj of the injection refrigerant and the target injection refrigerant superheat.
- the injection expansion valve target opening TGECCVsh of the injection expansion valve 30 is determined based on the degree TGSHinj, the valve opening is controlled, and when the injection request flag fINJONreq is reset to “0”, the injection expansion valve 30 Is closed (fully closed when the valve opening is “0”), and the gas injection by the injection circuit 40 is stopped.
- FIG. 8 shows the target opening (injection expansion valve target opening) TGECCVpc of the injection expansion valve 30 of the injection circuit 40 when the rotation speed NC of the compressor 2 is equal to or higher than a predetermined value N1 (in the case of a high rotation speed). It is a control block diagram of the controller 32 to determine.
- the gas injection in this case is also executed in the first dehumidifying and cooling type defrosting mode (including the case of performing gas injection in the above-described reverse cycle defrosting mode) and the hot gas defrosting mode.
- the F / B manipulated variable calculator 76 calculates the F / B manipulated variable TGECCVpcfb of the target target opening of the injection expansion valve based on the target radiator pressure PCO and the radiator pressure PCI.
- the F / B manipulated variable calculator 76 operates when the injection request flag fINJONreq is “1” (set), and stops calculating when it is “0” (reset). Then, the F / B manipulated variable TGECCVpcfb computed by the F / B manipulated variable computing unit 76 and the F / F manipulated variable TGECCVpcff in this case of the injection expansion valve 30 determined in advance are added by the adder 77 to set a limit.
- the limit value is input to the injection availability switching unit 79. Further, “0” (the injection expansion valve 30 is fully closed) is input to the injection availability switching unit 79. When the injection request flag fINJONreq is “1” (set), the value passed through the limit setting unit 78 is The injection expansion valve target opening degree TGECCVpc is determined and output.
- the injection availability switching unit 79 When the injection request flag fINJONreq is “0” (reset), the injection availability switching unit 79 outputs “0” as the injection expansion valve target opening TGECCVpc. That is, when the rotational speed NC of the compressor 2 is a high rotational speed equal to or higher than the predetermined value N1, when the injection request flag fINJONreq is set to “1”, the controller 32 sets the target radiator pressure PCO and the radiator pressure PCI.
- the injection expansion valve target opening degree TGECCVpc of the injection expansion valve 30 is determined on the basis of the above, and the valve opening degree is controlled.
- the target blowing temperature TAO is a target value of the air temperature blown from the blowout port 29 into the vehicle interior, and is calculated by the controller 32 from the following formula (I).
- 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, as shown in FIG. 9, and it falls as the outside temperature Tam rises.
- the controller 32 calculates the target radiator temperature TCO from the target blowing temperature TAO.
- the controller 32 obtains the outdoor heat exchanger temperature of the outdoor heat exchanger 7 obtained from the outdoor heat exchanger temperature sensor 54 (for example, the refrigerant evaporation temperature at the outlet of the outdoor heat exchanger 7) TXO, and the outside air has low humidity. Based on the outdoor heat exchanger temperature (also the refrigerant evaporation temperature at the outlet of the outdoor heat exchanger 7) TXObase at the time of non-frosting when the outdoor heat exchanger 7 is not frosted in the environment. The frosting state of the heat exchanger 7 is detected. The controller 32 in this case determines the outdoor heat exchanger temperature TXObase at the time of no frost formation using the following formula (II).
- Tam which is a parameter of the formula (II)
- NC is the rotation speed of the compressor 2
- BLV is the blower voltage of the indoor blower 27
- VSP is the vehicle speed obtained from the vehicle speed sensor 52.
- K1 to k4 are coefficients, which are obtained in advance by experiments.
- the outside air temperature Tam is an index indicating the intake air temperature of the outdoor heat exchanger 7.
- the index indicating the intake air temperature of the outdoor heat exchanger 7 is not limited to the outdoor air temperature Tam.
- the rotational speed NC of the compressor 2 is an index indicating the refrigerant flow rate in the refrigerant circuit R. The higher the rotational speed NC (the higher the refrigerant flow rate), the lower the TXObase. Therefore, the coefficient k2 is a negative value.
- the blower voltage BLV is an index indicating the amount of air passing through the radiator 4.
- the index indicating the amount of air passing through the radiator 4 is not limited to this and may be the blower air amount of the indoor blower 27 or the air mix damper 28 opening SW.
- the vehicle speed VSP is an index indicating the passing air speed of the outdoor heat exchanger 7. The lower the vehicle speed VSP (the lower the passing air speed of the outdoor heat exchanger 7), the lower the TXObase. Therefore, the coefficient k4 is a positive value.
- the index indicating the passing air speed of the outdoor heat exchanger 7 is not limited to this, and the voltage of the outdoor blower 15 may be used.
- the outdoor air temperature Tam, the rotational speed NC of the compressor 2, the blower voltage BLV of the indoor blower 27, and the vehicle speed VSP are used as parameters of the formula (II).
- One load may be added as a parameter.
- the target blowout temperature TAO, the rotational speed NC of the compressor 2, the blower air volume of the indoor blower 27, the inlet air temperature of the radiator 4 and the radiator temperature Tci of the radiator 4 can be considered.
- the larger the value the lower the TXObase.
- the parameters of the formula (II) are not limited to all of the above, and any one of them or a combination thereof may be used.
- ⁇ TXO the difference ⁇ TXO
- the solid line in FIG. 11 shows the change in the outdoor heat exchanger temperature TXO
- the broken line shows the change in the outdoor heat exchanger temperature TXObase when there is no frost formation.
- the outdoor heat exchanger temperature TXO is high and exceeds the outdoor heat exchanger temperature TXObase when there is no frost formation.
- the temperature in the passenger compartment is warmed and the load on the vehicle air conditioner 1 is reduced. Therefore, the refrigerant flow rate and the air flow rate through the radiator 4 are also reduced.
- the calculated TXObase (broken line in FIG. 11) rises.
- the controller 32 causes the outdoor heat exchanger 7 to It determines that frost has occurred and defrost is necessary and issues a defrost request.
- the outdoor heat exchanger temperature TXO is used to detect the frosting state.
- the present invention is not limited to this, and the current refrigerant evaporation pressure of the outdoor heat exchanger 7 obtained from the outdoor heat exchanger pressure sensor 56 ( Outdoor heat exchanger pressure) PXO and frost state of outdoor heat exchanger 7 based on outdoor heat exchanger pressure PXObase at the time of non-frosting when the outside air is not frosted in the low humidity environment May be detected.
- the means for detecting the frosted state of the outdoor heat exchanger 7 is not limited to the above, and the dew point temperature detected by the outdoor air temperature sensor 33 and the outdoor air humidity sensor 34 and the refrigerant evaporation temperature of the outdoor heat exchanger 7 (outdoor heat exchange).
- the controller 32 may detect (estimate) the frosting state of the outdoor heat exchanger 7 based on the temperature of the vessel.
- step S2 determines whether or not the current outside air temperature Tam detected by the outside air temperature sensor 34 is lower than a predetermined value T2.
- the predetermined value T2 is a predetermined temperature value that can determine whether the outside air temperature Tam is low or high. If the outside air temperature Tam is lower than T2 in step S3, the controller 32 proceeds to step S4, and determines whether or not an occupant is currently in the passenger compartment based on the output of the occupant sensor 57.
- step S5 determines whether there is a heating request. If the current air-conditioning operation mode is the heating mode (or dehumidifying heating mode) and the vehicle interior needs to be heated, the controller 32 determines that there is a heating request and proceeds to step S6, where the target radiator pressure (Target high pressure) PCO is set to a predetermined value P1 (high pressure).
- step S7 the process proceeds to step S7, and the first dehumidifying and cooling type defrosting mode described above is executed. That is, the refrigerant is radiated by the radiator 4 and the outdoor heat exchanger 7, and the heat absorber 9 absorbs the heat. Thereby, the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH.
- the indoor blower (blower) 27 is controlled in coordination with the blowout temperature to avoid occupant discomfort, and the suction switching damper 26 is set to the inside air circulation mode.
- step S8 the controller 32 performs F / B control of the compressor 2 based on the target heat absorber temperature TEO as in the control block of FIG. 5 described above (the same as the cooling and dehumidifying cooling modes). Further, the injection circuit 40 is operated to perform gas injection during the compression of the compressor 2. In that case, when the rotational speed NC of the compressor 2 is a low rotational speed equal to or less than a predetermined value N1, as shown in the control blocks of FIGS. 7 and 8, the controller 32 performs injection injection valve 30 based on the injection superheat degree SHinj as shown in FIG. The valve opening is controlled by F / B to control the amount of gas injection.
- the valve opening degree of the injection expansion valve 30 is F / B controlled based on the target radiator pressure PCO as shown in FIG. Control the amount.
- the injection superheat degree SHinj is higher than 10 deg to prevent liquid back to the compressor 2.
- step S9 the controller 32 proceeds to step S9, and when the outdoor heat exchanger temperature TXO is equal to or higher than a predetermined value TX1 (for example, + 25 ° C.), the outdoor blower 15 is operated (ON), and the outdoor heat exchanger 7 is forced to ventilate the outside air. To do.
- a predetermined value TX1 for example, + 25 ° C.
- TX2 for example, + 20 ° C. having a predetermined hysteresis with respect to TX1
- the outdoor blower 15 is stopped (OFF).
- step S5 when there is no heating request in step S5, the controller 32 proceeds to step S10, sets the target radiator pressure PCO to a predetermined value P2 (medium pressure, P1 ⁇ P2), and then proceeds to step S11 to perform the first dehumidification described above.
- the cooling type defrost mode is executed.
- step S8 and step S9 are sequentially executed.
- step S4 the controller 32 proceeds from step S4 to step S12 to set the target radiator pressure PCO to P2 (medium pressure), and then to step It progresses to S13 and it is judged whether vehicle interior temperature is lower than predetermined value T1 (for example, +5 degreeC). If the passenger compartment temperature is relatively high immediately after the passenger gets off and is equal to or higher than the predetermined value T1, the controller 32 proceeds from step S13 to step S14, and executes the above-described reverse cycle defrosting mode.
- predetermined value T1 for example, +5 degreeC
- step S15 the controller 32 performs F / B control of the compressor 2 based on the target heat absorber temperature TEO as in the control block of FIG. 5 described above (the same as the cooling and dehumidifying cooling modes). However, the injection circuit 40 is not operated (OFF), and gas injection to the compressor 2 is not performed.
- step S13 the controller 32 proceeds from step S13 to step S11, step S8, and step S9, and switches to the first dehumidifying and cooling type defrosting mode described above (the air mix damper 28 is MH), controlling the compressor 2 and the injection expansion valve 30 and the like so that the temperature of the outdoor heat exchanger 7 becomes a predetermined value (+ 25 ° C. to + 30 ° C.), and defrosting the outdoor heat exchanger 7. Heating by heat radiation of the radiator 4 is resumed by gas injection to raise the passenger compartment temperature.
- step S3 if the outside air temperature Tam is a high environment equal to or higher than the predetermined value T2, the controller 32 proceeds from step S3 to step S16, and sets the target radiator pressure PCO to the predetermined value P3 (low pressure, P1 ⁇ P2 ⁇ P3). And it progresses to step S17 and performs the 2nd dehumidification cooling type defrost mode mentioned above. That is, the refrigerant is radiated by the radiator 4 and the outdoor heat exchanger 7, and the heat absorber 9 absorbs the heat. Thereby, the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH. Further, the indoor blower (blower) 27 is operated at a predetermined voltage V3 (V1 ⁇ V3), and the suction switching damper 26 is set to the inside air circulation mode.
- step S15 the controller 32 performs F / B control of the compressor 2 based on the target heat absorber temperature TEO as in the control block of FIG. 5 described above (the same as the cooling and dehumidifying cooling modes). Further, the injection circuit 40 is not operated (OFF), and gas injection to the compressor 2 is not performed. As a result, more high-temperature refrigerant flows through the outdoor heat exchanger 7. At this time, the injection circuit 40 does not operate, but since the outside air temperature Tam is high, there is no problem with the vehicle interior temperature.
- the controller 32 operates the injection circuit 40 to return the refrigerant in the middle of compression of the compressor 2 when defrosting by flowing the high-temperature refrigerant to the outdoor heat exchanger 7, and there is a request for heating in the vehicle interior.
- the refrigerant discharged from the compressor 2 in step S7 is radiated by the radiator 4 and the outdoor heat exchanger 7, and the radiated refrigerant is depressurized, and then the first dehumidifying and cooling type heat absorber 9 absorbs heat. Since the frost mode is executed and the injection circuit 40 is operated in step S8, part of the refrigerant that has exited the radiator 4 by the injection circuit 40 is returned to the middle of compression of the compressor 2 to improve the heating capacity of the radiator 4.
- the vehicle interior temperature can be maintained.
- the outdoor heat exchanger temperature TXO of the outdoor heat exchanger 7 is equal to or higher than a predetermined value TX1, and the outdoor air is passed through the outdoor heat exchanger 7. Since the outdoor blower 15 is operated and stopped when it is lower than the predetermined value TX2, it is possible to prevent or suppress inconvenience that water vapor generated by defrosting reattaches to the outdoor heat exchanger 7.
- the controller 32 executes the second dehumidifying and cooling type defrosting mode in step S17, so that the outside air temperature Tam is high and it is easy to maintain the heating capacity of the vehicle interior. Then, more refrigerant can be supplied to the outdoor heat exchanger 7 without operating the injection circuit 40, and defrosting can be promoted.
- the controller 32 executes the reverse cycle defrosting mode described above in step S14 until the vehicle interior temperature becomes lower than the predetermined value T1, and if the vehicle interior temperature becomes lower than the predetermined value T1, the controller 32 executes the above-described operation in step S11. Since the first dehumidifying and cooling type defrosting mode is executed to dissipate the refrigerant in the radiator 4 as well, the control satisfying both the rapid defrosting of the outdoor heat exchanger 7 and the maintenance of heating in the vehicle interior is realized. Is possible.
- the controller 32 defrosts the outdoor heat exchanger 7 when the vehicle interior temperature is lower than the predetermined value T1 or when it is necessary to heat the vehicle interior, the first dehumidifying and cooling type removal in step S11 or step S7. Since the suction switching damper 26 is set to the inside air circulation mode in the frost mode and the introduction of the outside air into the air flow passage 3 is stopped, the introduction of the outside air having a low temperature is stopped in a situation where the vehicle interior temperature is low, and the heating capacity is maintained. Will be able to.
- the intake switching damper 26 is set to the inside air circulation mode to stop the introduction of outside air into the air flow passage 3, so that the heating capacity is similarly maintained. It becomes possible.
- the controller 32 has a simple hot gas defrosting mode as the defrosting mode in addition to the first dehumidifying cooling type defrosting mode and the second dehumidifying cooling type defrosting mode described above. Switch between them according to.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 through the discharge-side heat exchanger 35, but the air in the air flow passage 3 is not vented to the radiator 4. Only passes, and the refrigerant exiting the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipe 13E. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through the outdoor expansion valve 6 and the refrigerant pipe 13I, flows into the outdoor heat exchanger 7 as it is, radiates heat, and is condensed and liquefied. The frost adhering to the outdoor heat exchanger 7 is melted by the heat radiation at this time.
- the refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13D from the refrigerant pipe 13A, and flows into the refrigerant pipe 13C on the downstream side of the internal heat exchanger 19 through the electromagnetic valve 21. Then, it is sucked into the compressor 2 through the accumulator 12. That is, the refrigerant does not flow through the heat absorber 9 in the simple hot gas defrosting mode.
- the controller 32 when executing this simple hot gas defrosting mode, the controller 32 does not operate the injection circuit 40 and uses all of the refrigerant from the radiator 4 for defrosting the outdoor heat exchanger 7.
- FIG. 12 shows a Ph diagram in the simple hot gas defrosting mode. In this case, the shape is a triangle as shown in FIG.
- FIG. 13 shows the simple hot gas defrost mode (including a hot gas defrost mode described later).
- the F / F manipulated variable calculator 82 of the controller 32 has an outside air temperature Tam obtained from the outside air temperature sensor 33, a blower voltage BLV of the indoor blower 27, the air mix damper opening SW of the air mix damper 28 described above, and a target heat release. Based on the compressor temperature TCO and the target radiator pressure PCO, the F / F manipulated variable TGNChff of the compressor target rotational speed is calculated.
- the target radiator pressure PCO is calculated by the target value calculator 82 based on the radiator temperature TCO. Further, the F / B operation amount calculation unit 83 calculates the F / B operation amount TGNChfb of the compressor target rotation speed based on the target radiator pressure PCO and the radiator pressure PCI. Then, the F / F manipulated variable TGNCnff computed by the F / F manipulated variable computing unit 82 and the TGNChfb computed by the F / B manipulated variable computing unit 83 are added by the adder 84, and the control upper limit value and the control are controlled by the limit setting unit 86. After the lower limit is set, it is determined as the compressor target rotational speed TGNCh. In the simple hot gas defrosting mode and the hot gas defrosting mode described later, the controller 32 controls the rotation speed of the compressor 2 based on the compressor target rotation speed TGNCh.
- step S21 If the controller 32 makes a defrost request in step S21, the process proceeds from step S21 to step S22, and determines whether or not the vehicle is currently plugged in.
- the battery In an electric vehicle or a hybrid vehicle having a plug-in function, the battery can be charged from an external power source while the vehicle is stopped.
- the controller 32 operates the compressor 2 (power supply from the battery or external power source). It is assumed that the compressor 2 has a function of operating by direct power supply from When the plug-in is in progress, the process proceeds from step S22 to step S23.
- step S31 it is determined whether or not the remaining amount of the battery is lower than a predetermined value.
- This predetermined value is a threshold that can sufficiently realize defrosting and heating by discharging the battery. And also when the battery remaining amount remains more than predetermined value, it progresses to step S23.
- step S23 the controller 32 determines whether or not the current outside air temperature Tam detected by the outside air temperature sensor 34 is lower than the aforementioned predetermined value T2. If it is determined in step S23 that the outside air temperature Tam is lower than T2, the controller 32 proceeds to step S24 and determines whether an occupant is currently in the passenger compartment based on the output of the occupant sensor 57.
- step S24 the controller 32 proceeds to step S25 and determines whether there is a heating request. If it is determined that there is a heating request as described above, the controller 32 proceeds to step S26 and sets the target radiator pressure (target high pressure) PCO to the predetermined value P1 (high pressure) described above.
- target radiator pressure target high pressure
- step S27 the process proceeds to step S27, and the first dehumidifying and cooling type defrosting mode described above is executed. That is, the refrigerant is radiated by the radiator 4 and the outdoor heat exchanger 7, and the heat absorber 9 absorbs the heat. Thereby, the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH.
- the indoor blower (blower) 27 is controlled in coordination with the blowout temperature, and the suction switching damper 26 is set to the inside air circulation mode.
- step S28 the controller 32 performs F / B control of the compressor 2 based on the target heat absorber temperature TEO as in the control block of FIG. 5 described above (same as the cooling and dehumidifying cooling modes). Further, the injection circuit 40 is operated to perform gas injection during the compression of the compressor 2. In that case, when the rotational speed NC of the compressor 2 is a low rotational speed equal to or less than a predetermined value N1, as shown in the control blocks of FIGS. 7 and 8, the controller 32 performs injection injection valve 30 based on the injection superheat degree SHinj as shown in FIG. The valve opening is controlled by F / B to control the amount of gas injection.
- the valve opening degree of the injection expansion valve 30 is F / B controlled based on the target radiator pressure PCO as shown in FIG. Control the amount.
- the injection superheat degree SHinj is set higher than 10 deg as described above.
- the controller 32 proceeds to step S29, and when the outdoor heat exchanger temperature TXO is equal to or higher than a predetermined value TX1 (for example, + 25 ° C.) as described above, the outdoor fan 15 is operated (ON), and the outdoor heat exchanger 7 Forcibly ventilate.
- a predetermined value TX1 for example, + 25 ° C.
- TX2 for example, + 20 ° C. having a predetermined hysteresis with respect to TX1
- the outdoor blower 15 is stopped (OFF).
- step S25 the controller 32 proceeds to step S30, sets the target radiator pressure PCO to the above-described predetermined value P2 (medium pressure. P1 ⁇ P2), and then proceeds to step S33 to perform the above-described simple process.
- Execute hot gas defrosting mode That is, the refrigerant is radiated by only the outdoor heat exchanger 7 and returned to the compressor 2 without passing through the heat absorber 9. Thereby, the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is fully opened, and the air mix damper 28 is MC.
- the indoor blower (blower) 27 stops.
- step S34 the controller 32 performs F / B control of the compressor 2 based on the target radiator temperature PCO as in the control block of FIG. 13 described above (same as in the heating mode). Further, the injection circuit 40 is not operated (OFF), and the high-temperature refrigerant from the compressor 2 is used to defrost the outdoor heat exchanger 7. Next, the controller 32 proceeds to step S29, and controls the operation of the outdoor fan 15 as described above.
- step S24 If the occupant is not in step S24 and if the remaining battery level is lower than the predetermined value in step S31, the controller 32 proceeds to step S32 and sets the target radiator pressure PCO to P2 (medium pressure). Then, the process proceeds to step S33 to execute the simple hot gas defrosting mode. That is, when the occupant is not in the vehicle or when the remaining battery level is low, the high-temperature refrigerant is concentrated on the defrosting of the outdoor heat exchanger 7.
- step S23 If the outside air temperature Tam is a high environment equal to or higher than the predetermined value T2 in step S23, the controller 32 proceeds from step S23 to step S35 to determine again whether or not the occupant is on board. It progresses to step S32 and step S33.
- the routine proceeds to step S36, where the target radiator pressure PCO is set to the aforementioned predetermined value P3 (low pressure, P1 ⁇ P2 ⁇ P3), and the routine proceeds to step S37, where the second dehumidifying and cooling type removal described above is performed. Run the frost mode.
- the refrigerant is dissipated by the radiator 4 and the outdoor heat exchanger 7 and the heat absorber 9 absorbs heat.
- the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH.
- the indoor blower (blower) 27 is operated at a predetermined voltage V3, and the suction switching damper 26 is set to the inside air circulation mode.
- step S37 the controller 32 carries out F / B control of the compressor 2 based on target heat absorber temperature TEO like the control block of FIG. 5 mentioned above (same as a cooling and dehumidification cooling mode). Further, the injection circuit 40 is not operated (OFF), and gas injection to the compressor 2 is not performed. As a result, more high-temperature refrigerant flows through the outdoor heat exchanger 7. At this time, the injection circuit 40 does not operate, but since the outside air temperature Tam is high, there is no problem with the vehicle interior temperature.
- the controller 32 when the outside air temperature Tam is equal to or higher than the predetermined value T2, the controller 32 causes the refrigerant discharged from the compressor 2 in step S37 to dissipate heat in the radiator 4 and the outdoor heat exchanger 7, After depressurizing the radiated refrigerant, the second dehumidifying and cooling type defrosting mode in which heat is absorbed by the heat absorber 9 is executed, and the injection circuit 40 is not operated in step S38. Therefore, the outside air temperature Tam is high and the heating capacity in the vehicle interior is increased. In an environment where it is easy to maintain, it is possible to supply more refrigerant to the outdoor heat exchanger 7 without operating the injection circuit 40 and to promote defrosting.
- the controller 32 causes the refrigerant discharged from the compressor 2 in step S33 to radiate heat only by the outdoor heat exchanger 7, and the radiated refrigerant is not transferred through the heat absorber 9 to the compressor 2. Since the simple hot gas defrosting mode is returned to step S34 and the injection circuit 40 is not operated in step S34, the outdoor heat exchanger 7 can be quickly defrosted to minimize power consumption. It is extremely effective for electric vehicles and the like.
- the refrigerant discharged from the compressor 2 in step S27 is radiated by the radiator 4 and the outdoor heat exchanger 7, and the radiated refrigerant is depressurized.
- the first dehumidifying and cooling type defrosting mode for absorbing heat is executed, the injection circuit 40 is operated in step S28, and when power is not supplied from an external power source, the refrigerant discharged from the compressor 2 in step S33 is subjected to outdoor heat exchange. Since the simple hot gas defrosting mode is performed in which the heat is radiated by the cooler 7 and the radiated refrigerant is returned to the compressor 2 without going through the heat sink 9 and the injection circuit 40 is not operated in step S34.
- the controller 32 executes the simple hot gas defrosting mode when the plug-in is not being performed in step S22 (the power is not supplied from the external power source) and the remaining battery level is low in step S31.
- the injection circuit 40 is not operated, or the hot gas defrosting mode is executed and the injection circuit 40 is not operated. Therefore, when the battery is not plugged in and the remaining battery level is low, the injection circuit 40 is not operated.
- the simple hot gas defrosting mode or the hot gas defrosting mode is executed, and accurate defrosting control that takes into consideration the remaining battery level in addition to whether or not the plug-in is performed becomes possible.
- FIG. 15 the same reference numerals as those in FIG. 1 have the same or similar functions.
- the refrigerant pipe 13G on the discharge side of the compressor 2 branches to a hot gas pipe (refrigerant pipe) 13H, and this branched hot gas pipe 13H is used when the outdoor heat exchanger 7 is defrosted.
- the high-temperature refrigerant (hot gas) that has been opened and discharged from the compressor 2 flows directly into the outdoor heat exchanger 7 and is expanded outdoors via a flow rate adjusting valve (hot gas valve) 87 for adjusting the flow rate.
- a flow rate adjusting valve hot gas valve
- a refrigerant pipe 13I between the valve 6 and the outdoor heat exchanger 7 is connected in communication. Further, an electromagnetic valve 88 that is closed during defrosting and stops the refrigerant from moving toward the outdoor expansion valve 6 is attached to the refrigerant pipe 13E after exiting the radiator 4 and branching to the injection circuit 40 (FIG. 2). Added with a dashed line).
- the controller 32 uses the hot gas pipe 13H as the defrost mode in addition to the first dehumidifying and cooling type defrosting mode, the second dehumidifying and cooling type defrosting mode, and the simple hot gas defrosting mode. It has a hot gas defrosting mode using and switches between them depending on the situation.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is divided and flows directly into the outdoor heat exchanger 7 through the flow rate adjusting valve 87 and the hot gas pipe 13H. And it heat-radiates with the outdoor heat exchanger 7, and the adhering frost is melt
- the refrigerant that has exited the outdoor heat exchanger 7 returns from the accumulator 12 to the compressor 2 through the refrigerant pipe 13A, the electromagnetic valve 21, and the refrigerant pipes 13D and 13C.
- FIG. 16 shows a Ph diagram when gas injection is performed in this hot gas defrosting mode. In this case, a portion flowing in the injection circuit 40 appears in addition to FIG. Indicated by 13K).
- step S41 If the controller 32 makes a defrost request in step S41, the controller 32 proceeds from step S41 to step S42, and determines whether or not the vehicle is currently plugged in. When the plug-in is in progress, the process proceeds from step S42 to step S43. When the plug-in is not in progress, the process proceeds to step S55, and it is determined whether or not the remaining battery level is lower than a predetermined value as described above. And also when the battery remaining amount remains more than predetermined value, it progresses to step S43.
- step S43 the controller 32 determines whether or not the current outside air temperature Tam detected by the outside air temperature sensor 34 is lower than the aforementioned predetermined value T2. If the outside air temperature Tam is lower than T2 in step S43, the controller 32 proceeds to step S44 and determines whether or not an occupant is currently in the passenger compartment based on the output of the occupant sensor 57.
- step S45 determines whether there is a heating request.
- the controller 32 determines whether the vehicle interior temperature detected by the inside air temperature sensor 37 is lower than a predetermined value T2 (for example, 0 ° C.). If the current vehicle interior is cold and the vehicle interior temperature is lower than the predetermined value T2, the controller 32 proceeds to step S47, and the target radiator pressure (target high pressure) PCO is set to the aforementioned predetermined value P1A (P1A ⁇ P1). ).
- step S48 the outdoor expansion valve 6 is fully closed, and the air mix damper 28 is MH.
- the indoor blower (blower) 27 is controlled in coordination with the blowout temperature, and the suction switching damper 26 is set to the inside air circulation mode.
- step S49 the controller 32 controls the compressor 2 based on the target radiator temperature PCO as shown in the control block of FIG. Further, the flow rate adjusting valve (hot gas valve) 87 is fully opened, and a part of the high-temperature refrigerant discharged from the compressor 2 is directly flowed into the outdoor heat exchanger 7 from the hot gas pipe 13H to release heat and defrost. Moreover, after operating the injection circuit 40 and radiating the remainder of the refrigerant
- the controller 32 performs F / B control on the opening degree of the injection expansion valve 30 based on the injection superheat degree SHinj as in the control block of FIG. 7, and controls the gas injection
- the controller 32 proceeds to step S50, and when the outdoor heat exchanger temperature TXO is equal to or higher than a predetermined value TX1 (for example, + 25 ° C.) as described above, the outdoor fan 15 is operated (ON), and the outdoor heat exchanger 7 Forcibly ventilate.
- a predetermined value TX1 for example, + 25 ° C.
- TX2 for example, + 20 ° C. having a predetermined hysteresis with respect to TX1
- the outdoor blower 15 is stopped (OFF).
- step S51 sets the target radiator pressure (target high pressure) PCO to the predetermined value P1 (high pressure) described above.
- step S52 and step S53 performs the 1st dehumidification cooling type defrost mode mentioned above. That is, the refrigerant is radiated by the radiator 4 and the outdoor heat exchanger 7, and the heat absorber 9 absorbs the heat. Thereby, the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH.
- the indoor blower (blower) 27 is controlled in coordination with the blowout temperature, and the suction switching damper 26 is set to the inside air circulation mode.
- step S53 the controller 32 performs F / B control of the compressor 2 based on the target heat absorber temperature TEO as in the control block of FIG. 5 described above (the same as the cooling and dehumidifying cooling modes). Further, the injection circuit 40 is operated to perform gas injection during the compression of the compressor 2. In that case, when the rotational speed NC of the compressor 2 is a low rotational speed equal to or less than a predetermined value N1, as shown in the control blocks of FIGS. 7 and 8, the controller 32 performs injection injection valve 30 based on the injection superheat degree SHinj as shown in FIG. The valve opening is controlled by F / B to control the amount of gas injection.
- the valve opening degree of the injection expansion valve 30 is F / B controlled based on the target radiator pressure PCO as shown in FIG. Control the amount.
- the injection superheat degree SHinj is set higher than 10 deg as described above.
- the controller 32 proceeds to step S50 and controls the operation of the outdoor fan 15 as described above.
- step S45 the controller 32 proceeds to step S54, sets the target radiator pressure PCO to the aforementioned predetermined value P2 (medium pressure, P1 ⁇ P2), and then proceeds to step S57 and step S58.
- P2 medium pressure, P1 ⁇ P2
- step S57 the outdoor expansion valve 6 is fully opened, and the air mix damper 28 may be anywhere.
- the indoor blower (blower) 27 stops.
- step S58 the controller 32 performs F / B control of the compressor 2 based on the target radiator temperature PCO as in the control block of FIG. Further, the flow rate adjusting valve (hot gas valve) 87 is fully opened, and a part of the high-temperature refrigerant discharged from the compressor 2 is directly flowed into the outdoor heat exchanger 7 from the hot gas pipe 13H to release heat and defrost. In addition, the injection circuit 40 is not operated (OFF), and the outdoor heat exchanger 7 is defrosted using all the high-temperature refrigerant from the compressor 2. Next, the controller 32 proceeds to step S50, and controls the operation of the outdoor fan 15 as described above.
- the flow rate adjusting valve (hot gas valve) 87 is fully opened, and a part of the high-temperature refrigerant discharged from the compressor 2 is directly flowed into the outdoor heat exchanger 7 from the hot gas pipe 13H to release heat and defrost.
- the injection circuit 40 is not operated (OFF), and the outdoor heat exchanger 7 is defrosted
- step S44 If the occupant is not in step S44 and if the remaining battery level is lower than the predetermined value in step S55, the controller 32 proceeds to step S56 and sets the target radiator pressure PCO to P2 (medium pressure). Then, the process proceeds to step S57 to execute the hot gas defrosting mode. That is, when the occupant is not in the vehicle or when the remaining battery level is low, the high-temperature refrigerant is concentrated on the defrosting of the outdoor heat exchanger 7.
- step S43 determines again whether or not the occupant is on board. It progresses to step S56 and step S57.
- the process proceeds to step S60, and the target radiator pressure PCO is set to the above-described predetermined value P3 (low pressure. P1A ⁇ P1 ⁇ P2 ⁇ P3), and then the process proceeds to step S61 and step S62. 2
- the dehumidifying and cooling type defrosting mode is executed.
- the refrigerant is dissipated by the radiator 4 and the outdoor heat exchanger 7 and the heat absorber 9 absorbs heat.
- the outdoor heat exchanger 7 is defrosted.
- the outdoor expansion valve 6 is F / B controlled based on the target radiator pressure PCO as in the control block of FIG. 6 described above, and the air mix damper 28 is set to MH.
- the indoor blower (blower) 27 is operated at a predetermined voltage V3, and the suction switching damper 26 is set to the inside air circulation mode.
- step S62 the controller 32 carries out F / B control of the compressor 2 based on target heat absorber temperature TEO like the control block of FIG. 5 mentioned above (same as a cooling and dehumidification cooling mode). Further, the injection circuit 40 is not operated (OFF), and gas injection to the compressor 2 is not performed. As a result, more high-temperature refrigerant flows through the outdoor heat exchanger 7. At this time, the injection circuit 40 does not operate, but since the outside air temperature Tam is high, there is no problem with the vehicle interior temperature.
- the hot gas pipe 13H that can directly supply the refrigerant discharged from the compressor 2 to the outdoor heat exchanger 7 is provided, and the controller 32 starts from the compressor 2 when there is a heating request.
- a part of the discharged refrigerant is diverted to flow into the outdoor heat exchanger 7 through the hot gas pipe 13H without passing through the radiator 4 to dissipate the heat, and the dissipated refrigerant is returned to the compressor 2 and the remaining refrigerant. Since the hot gas defrosting mode in which the heat is dissipated by the radiator 4 is executed and the injection circuit 40 is operated, the heating capacity of the radiator 4 can be improved by the injection circuit 40 without performing heat absorption in the heat absorber 9. It becomes effective especially in a situation where the temperature in the passenger compartment is extremely low.
- the controller 32 causes the refrigerant discharged from the compressor 2 in step S61 to radiate heat at the radiator 4 and the outdoor heat exchanger 7, thereby radiating the refrigerant. Since the second dehumidifying and cooling type defrosting mode in which heat is absorbed by the heat absorber 9 is executed and the injection circuit 40 is not operated, the outside air temperature Tam is high and the heating capacity in the passenger compartment is easily maintained. More refrigerant can be supplied to the outdoor heat exchanger 7 without operating the injection circuit 40, and defrosting can be promoted.
- the controller 32 diverts a part of the refrigerant discharged from the compressor 2 in step S57, and the outdoor heat exchanger 7 without passing through the radiator 4 by the hot gas pipe 13H.
- the hot gas defrosting mode is performed in which the refrigerant that has radiated heat is returned to the compressor 2 and the remaining refrigerant is radiated by the radiator 4, and the injection circuit 40 is not operated. Therefore, the outdoor heat exchanger 7 The defrosting can be performed quickly to minimize power consumption, which is extremely effective in an electric vehicle or the like.
- the hot gas defrosting mode described above is executed in step S48 when the vehicle interior temperature is low, and the refrigerant discharged from the compressor 2 in step S52 when the vehicle interior temperature is high. Is radiated by the radiator 4 and the outdoor heat exchanger 7, and after the decompressed refrigerant is decompressed, the first dehumidifying and cooling type defrosting mode in which heat is absorbed by the heat absorber 9 is executed to operate the injection circuit 40. In the case where power is not supplied from the external power source, a part of the refrigerant discharged from the compressor 2 is diverted in step S57 and flows into the outdoor heat exchanger 7 through the hot gas pipe 13H without passing through the radiator 4.
- the hot gas defrosting mode is performed in which the heat is radiated, the radiated refrigerant is returned to the compressor 2 and the remaining refrigerant is radiated by the radiator 4, and the injection circuit 40 is not operated.
- the plug-in is in the hot gas defrosting mode or the first dehumidifying and cooling type defrosting mode, the outdoor heat exchanger 7 is defrosted while maintaining the heating in the vehicle interior, and when not plugged in, Without operating the injection circuit 40 in the hot gas defrosting mode, all the refrigerant is allowed to flow through the outdoor heat exchanger 7 to quickly defrost and reduce power consumption.
- FIG. 18 shows other control blocks of the controller 32 for determining the target rotational speed (compressor target rotational speed) TGNChg (in this case) of the compressor 2 for the hot gas defrosting mode and the simple hot gas defrosting mode.
- the compressor target rotational speed TGNCh is calculated based on the target radiator temperature PCO and the radiator temperature PCI, but the target outdoor heat exchanger temperature of the outdoor heat exchanger temperature TXO of the outdoor heat exchanger 7 is calculated.
- the target rotational speed of the compressor 2 may be calculated based on TGTXO and the outdoor heat exchanger temperature TXO.
- the F / F manipulated variable calculation unit 91 of the controller 32 in this case is based on the outside air temperature Tam obtained from the outside air temperature sensor 33, the vehicle speed VSP obtained from the vehicle speed sensor 52, and the target outdoor heat exchanger temperature TGTXO. In this case, the F / F manipulated variable TGNChgff of the compressor target rotational speed is calculated.
- the target outdoor heat exchanger temperature TGTXO is set to about + 25 ° C. in consideration of the predetermined value TX1 that is the threshold value for operating the outdoor fan 15 described above.
- the F / B manipulated variable calculator 92 calculates the F / B manipulated variable TGNChgfb of the compressor target rotational speed in this case based on the target outdoor heat exchanger temperature TGTXO and the outdoor heat exchanger temperature TXO. . Then, the F / F manipulated variable TGNCngff calculated by the F / F manipulated variable calculator 91 and TGNChgfb calculated by the F / B manipulated variable calculator 92 are added by the adder 93, and the limit setting unit 94 controls the control upper limit value and the control. After the lower limit is set, it is determined as the compressor target speed TGNChg in this case.
- the controller 32 sets the target outdoor heat exchanger temperature TGTXO and the outdoor heat exchanger temperature TXO as described above.
- the rotational speed of the compressor 2 is subjected to F / B control based on the compressor target rotational speed TGNChg calculated based on the above.
- the simple hot gas defrosting mode is executed in step S34 in the flowchart of FIG. 14 and step S57 in the flowchart of FIG. 17, but the present invention is not limited to this, and the hot gas defrosting mode is executed. You may do it.
- the defrosting control of each embodiment may be executed when the vehicle speed detected by the vehicle speed sensor 52 is a predetermined value or less. That is, the outdoor heat exchanger 7 may be defrosted by the controller 32 only when the vehicle speed is lower than a predetermined value (for example, 10 km / h). In that case, it is possible to perform defrosting in a situation where the flow of outside air to the outdoor heat exchanger 7 is small, and to improve the defrosting effect (in the case where there is a shutter grill in front of the outdoor heat exchanger 7) Shall be closed during defrosting).
- a predetermined value for example, 10 km / h
- the present invention is applied to the vehicle air conditioner 1 that is switched and executed between the heating mode, the dehumidifying heating mode, the dehumidifying 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.
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Abstract
Description
コントローラ32により(オート)、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吐出側熱交換器35を経た後、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吐出側熱交換器35を経て放熱器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吐出側熱交換器35を経て放熱器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。
コントローラ32は起動時には外気温度センサ33が検出する外気温度Tamと目標吹出温度TAOとに基づいて運転モードを選択する。また、起動後は外気温度Tamや目標吹出温度TAO等の環境や設定条件の変化に応じて前記各運転モードを選択し、切り換えていく。この場合、コントローラ32は基本的には暖房モードから除湿暖房モードへ、或いは、除湿暖房モードから暖房モードへと移行し、除湿暖房モードから除湿冷房モードへ、或いは、除湿冷房モードから除湿暖房モードへと移行し、除湿冷房モードから冷房モードへ、或いは、冷房モードから除湿冷房モードへと移行するものであるが、除湿暖房モードから除湿冷房モードへ移行する際、及び、除湿冷房モードから除湿暖房モードへ移行する際には、前記内部サイクルモードを経由して移行する。また、冷房モードから内部サイクルモードへ、内部サイクルモードから冷房モードへ移行する場合もある。
次に、インジェクション回路40による圧縮機2へのガスインジェクションについて説明する。インジェクション膨張弁30が開いているとき、放熱器4を出て冷媒配管13Eに入り、その後、分流されてインジェクション回路40の冷媒配管13Kに流入した冷媒は、インジェクション膨張弁30で減圧された後、吐出側熱交換器35に入り、そこで圧縮機2の吐出冷媒(圧縮機2から吐出されて放熱器4に流入する前の冷媒)と熱交換し、吸熱して蒸発する。蒸発したガス冷媒は、その後、圧縮機2の圧縮途中に戻り、アキュムレータ12から吸い込まれて圧縮されている冷媒と共に更に圧縮された後、再度圧縮機2から冷媒配管13Gに吐出されることになる。
次に、図3乃至図11を参照しながら実施例の車両用空気調和装置1の除霜モードについて説明する。上記暖房モードや除湿暖房モードでは室外熱交換器7で冷媒が蒸発するため、霜が成長する。室外熱交換器7に霜が成長すると外気との熱交換が阻害されるため、以下に説明する室外熱交換器7の除霜モードを実行する。この実施例の場合、コントローラ32は除霜モードとして、逆サイクル除霜モード、第1除湿冷房型除霜モード及び第2除湿冷房型除霜モードを有しており、状況に応じてそれらを切り換えて実行する。尚、第1除湿冷房型除霜モード及び第2除湿冷房型除霜モードは、何れも本発明における除湿冷房型除霜モードに含まれる(簡易ホットガス除霜モード及びホットガス除霜モードについては他の実施例で説明する)。
先ず、逆サイクル除霜モードの冷媒の流れについて説明する。この逆サイクル除霜モードにおける冷媒の流れ方は前述した冷房モードと同様である。即ち、逆サイクル除霜モードでは、コントローラ32は電磁弁20、及び、電磁弁17を開放し、電磁弁21、及び、電磁弁22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は放熱器4に空気が通風されない状態(MC)とする。
次に、第1除湿冷房型除霜モードの冷媒の流れについて説明する。この第1除湿冷房型除霜モードにおける冷媒の流れ方は前述した除湿冷房モードと同様である。即ち、第1除湿冷房型除霜モードでは、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全て放熱器4に通風される状態(MH)とする。
尚、第2除湿冷房型除霜モードの冷媒の流れは前述した除湿冷房モードの場合と全く同様(但し、第2除湿冷房型除霜モードでは後述する如くガスインジェクション無し)となるので、説明を省略する。
一方、図5は逆サイクル除霜モードと第1除湿冷房型除霜モード用の圧縮機2の目標回転数(圧縮機目標回転数)TGNCcを決定するコントローラ32の制御ブロック図である。コントローラ32のF/F(フィードフォワード)操作量演算部58は外気温度Tamと、ブロワ電圧BLVと、放熱器4の温度の目標値である目標放熱器温度TCOと、SW=(TAO-Te)/(TH-Te)で得られるエアミックスダンパ28のエアミックスダンパ開度SWと、吸熱器9の温度の目標値である目標吸熱器温度TEOに基づいて圧縮機目標回転数のF/F操作量TGNCcffを演算する。
次に、図6は逆サイクル除霜モード及び第1除湿冷房型除霜モードにおける室外膨張弁6の目標開度(室外膨張弁目標開度)TGECCVpcを決定するコントローラ32の制御ブロック図である。コントローラ32のF/F操作量演算部64は目標放熱器温度TCOと、ブロワ電圧BLVと、外気温度Tamと、エアミックスダンパ開度SWと、目標吸熱器温度TEOと、目標放熱器圧力PCOに基づいて室外膨張弁目標開度のF/F操作量TGECCVpcffを演算する。
次に、図7は圧縮機2の回転数NCが所定値N1より低い場合(低回転数の場合)におけるインジェクション回路40のインジェクション膨張弁30の目標開度(インジェクション膨張弁目標開度)TGECCVshを決定するコントローラ32の制御ブロック図である。尚、実施例では後述する如くガスインジェクションは、第1除湿冷房型除霜モード(前述した逆サイクル除霜モードでガスインジェクションする場合を含む)と、ホットガス除霜モードで実行される。コントローラ32のインジェクション冷媒過熱度演算部69は、インジェクション温度センサ55が検出するインジェクション冷媒の温度(インジェクション冷媒温度Tinj)と、飽和温度Tsatuinjの差に基づき、インジェクション回路40から圧縮機2の圧縮途中に戻されるインジェクション冷媒の過熱度(インジェクション冷媒過熱度)SHinjを算出する。
次に、図8は圧縮機2の回転数NCが所定値N1以上の場合(高回転数の場合)におけるインジェクション回路40のインジェクション膨張弁30の目標開度(インジェクション膨張弁目標開度)TGECCVpcを決定するコントローラ32の制御ブロック図である。尚、この場合のガスインジェクションも、第1除湿冷房型除霜モード(前述した逆サイクル除霜モードでガスインジェクションする場合を含む)と、ホットガス除霜モードで実行される。
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は図9に示すように外気温度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、この目標吹出温度TAOから前記目標放熱器温度TCOを算出する。
次に、図10のフローチャートを参照しながら暖房モードにおけるコントローラ32による具体的な除霜モードの制御について説明する。コントローラ32は図10のステップS1で各センサからデータを読み込み、ステップS2で室外熱交換器7の除霜要求があるか否か判断する。
=k1×Tam+k2×NC+k3×BLV+k4×VSP・・(II)
また、上記圧縮機2の回転数NCは冷媒回路R内の冷媒流量を示す指標であり、回転数NCが高い程(冷媒流量が多い程)、TXObaseは低くなる傾向となる。従って、係数k2は負の値となる。
また、上記ブロワ電圧BLVは放熱器4の通過風量を示す指標であり、ブロワ電圧BLVが高い程(放熱器4の通過風量が大きい程)、TXObaseは低くなる傾向となる。従って、係数k3は負の値となる。尚、放熱器4の通過風量を示す指標としてはこれに限らず、室内送風機27のブロワ風量やエアミックスダンパ28開度SWでもよい。
また、上記車速VSPは室外熱交換器7の通過風速を示す指標であり、車速VSPが低い程(室外熱交換器7の通過風速が低い程)、TXObaseは低くなる傾向となる。従って、係数k4は正の値となる。尚、室外熱交換器7の通過風速を示す指標としてはこれに限らず、室外送風機15の電圧でもよい。
次に、図12~図14を参照しながら、本発明の車両用空気調和装置1の他の実施例を説明する。この実施例の場合、コントローラ32は除霜モードとして、前述した第1除湿冷房型除霜モード、第2除湿冷房型除霜モードの他に、簡易ホットガス除霜モードを有しており、状況に応じてそれらを切り換えて実行する。
先ず、この場合の簡易ホットガス除霜モードの冷媒の流れについて説明する。この簡易ホットガス除霜モードでは、コントローラ32は電磁弁21を開放し、電磁弁17、電磁弁20、及び、電磁弁22を閉じる。また、室外膨張弁6は全開とする。そして、圧縮機2、及び、室外送風機15を運転し、室内送風機27は停止し、エアミックスダンパ28は放熱器4に空気が通風されない状態(MC)とする。
次に、図13は上記簡易ホットガス除霜モード(後述するホットガス除霜モードを含む)用の圧縮機2の目標回転数(圧縮機目標回転数)TGNChを決定するコントローラ32の制御ブロック図である。コントローラ32のF/F操作量演算部82は外気温度センサ33から得られる外気温度Tamと、室内送風機27のブロワ電圧BLVと、前述したエアミックスダンパ28のエアミックスダンパ開度SWと、目標放熱器温度TCOと、目標放熱器圧力PCOに基づいて圧縮機目標回転数のF/F操作量TGNChffを演算する。
次に、図14のフローチャートを参照しながら暖房モードにおけるコントローラ32によるこの場合の具体的な除霜モードの制御について説明する。コントローラ32は図14のステップS20で各センサからデータを読み込み、ステップS21で室外熱交換器7の除霜要求があるか否か判断する。尚、この場合の室外熱交換器7の着霜状態の検知は前述した図10のステップS2の場合と同様であるので説明を省略する。
次に、図15~図17を参照しながら、本発明の車両用空気調和装置1のもう一つの他の実施例を説明する。尚、図15において図1と同一符号は同一若しくは同様の機能を奏するものとする。この場合、車両用空気調和装置1では圧縮機2の吐出側の冷媒配管13Gはホットガス配管(冷媒配管)13Hに分岐し、この分岐したホットガス配管13Hは室外熱交換器7の除霜時に開放されて圧縮機2から吐出された高温冷媒(ホットガス)を直接室外熱交換器7に流入させ、且つ、その流量を調整するための流量調整弁(ホットガス弁)87を介して室外膨張弁6と室外熱交換器7間の冷媒配管13Iに連通接続されている。また、放熱器4を出てインジェクション回路40に分岐した後の冷媒配管13Eには除霜時に閉じられて冷媒が室外膨張弁6方向に向かうのを止める電磁弁88が取り付けられている(図2に破線で追加)。
先ず、この場合のホットガス除霜モードの冷媒の流れについて説明する。このホットガス除霜モードでは、コントローラ32は電磁弁21を開放し、電磁弁17、電磁弁20、電磁弁22、及び、電磁弁88を閉じる。また、室外膨張弁6は全閉とし、流量調整弁87は開度が調整される。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は放熱器4に全ての空気が通風される状態(MH)とする。
次に、図17のフローチャートを参照しながら暖房モードにおけるコントローラ32によるこの場合の具体的な除霜モードの制御について説明する。コントローラ32は図17のステップS40で各センサからデータを読み込み、ステップS41で室外熱交換器7の除霜要求があるか否か判断する。尚、この場合の室外熱交換器7の着霜状態の検知も前述した図10のステップS2の場合と同様であるので説明を省略する。
次に、図18は前記ホットガス除霜モード及び簡易ホットガス除霜モード用の圧縮機2の目標回転数(圧縮機目標回転数)TGNChg(この場合)を決定するコントローラ32の制御ブロックの他の実施例を示している。前記図13の例では、目標放熱器温度PCOと放熱器温度PCIに基づいて圧縮機目標回転数TGNChを算出したが、室外熱交換器7の室外熱交換器温度TXOの目標室外熱交換器温度TGTXOと、室外熱交換器温度TXOに基づいて圧縮機2の目標回転数を算出するようにしてもよい。
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、88 電磁弁
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
32 コントローラ(制御手段)
30 インジェクション膨張弁
40 インジェクション回路
35 吐出側熱交換器
87 流量調整弁
R 冷媒回路
Claims (12)
- 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、
該空気流通路に設けられて冷媒を放熱させる放熱器と、
前記空気流通路に設けられて冷媒を吸熱させる吸熱器と、
前記車室外に設けられて冷媒を放熱又は吸熱させるための室外熱交換器と、
制御手段とを備え、
該制御手段により、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て前記車室内を暖房する車両用空気調和装置において、
前記放熱器を出た冷媒の一部を分流して前記圧縮機に戻すインジェクション回路を備え、
前記制御手段は、前記室外熱交換器に高温冷媒を流して除霜する際、前記インジェクション回路を動作させて前記圧縮機に冷媒を戻すことを特徴とする車両用空気調和装置。 - 前記制御手段は、前記車室内の暖房要求がある場合、前記圧縮機から吐出された冷媒を前記放熱器と室外熱交換器にて放熱させ、放熱した当該冷媒を減圧した後、前記吸熱器にて吸熱させる除湿冷房型除霜モードを実行すると共に、前記インジェクション回路を動作させ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。
- 前記制御手段は、前記車室内の暖房要求がある場合、前記圧縮機から吐出された冷媒の一部を分流して前記放熱器を経ること無く前記室外熱交換器に流入させて放熱させ、放熱した当該冷媒を前記圧縮機に戻すホットガス除霜モードを実行すると共に、前記インジェクション回路を動作させ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。
- 前記室外熱交換器に外気を通風する室外送風機を備え、
前記制御手段は、前記室外熱交換器を除霜する際、当該室外熱交換器の温度が所定値以上で前記室外送風機を運転し、所定値より低い場合には停止することを特徴とする請求項1乃至請求項3のうちの何れかに記載の車両用空気調和装置。 - 前記制御手段は、外気温度が所定値以上である場合、前記圧縮機から吐出された冷媒を前記放熱器と室外熱交換器にて放熱させ、放熱した当該冷媒を減圧した後、前記吸熱器にて吸熱させる除湿冷房型除霜モードを実行すると共に、前記インジェクション回路は動作させないことを特徴とする請求項2又は請求項3に記載の車両用空気調和装置。
- 前記制御手段は、前記車室内の暖房要求がない場合、前記圧縮機から吐出された冷媒を前記室外熱交換器にて放熱させ、放熱した当該冷媒を前記圧縮機に戻す簡易ホットガス除霜モードを実行し、前記インジェクション回路は動作させず、又は、前記圧縮機から吐出された冷媒の一部を分流して前記放熱器を経ること無く前記室外熱交換器に流入させて放熱させ、放熱した当該冷媒を前記圧縮機に戻すホットガス除霜モードを実行し、前記インジェクション回路は動作させないことを特徴とする請求項2乃至請求項5のうちの何れかに記載の車両用空気調和装置。
- 前記制御手段は、外部電源から前記圧縮機、若しくは、当該圧縮機を駆動するために電力を供給するバッテリに給電されている場合、前記圧縮機から吐出された冷媒を前記放熱器と室外熱交換器にて放熱させ、放熱した当該冷媒を減圧した後、前記吸熱器にて吸熱させる除湿冷房型除霜モードを実行し、前記インジェクション回路を動作させ、又は、前記圧縮機から吐出された冷媒の一部を分流して前記放熱器を経ること無く前記室外熱交換器に流入させて放熱させ、放熱した当該冷媒を前記圧縮機に戻すホットガス除霜モードを実行し、前記インジェクション回路を動作させると共に、
前記外部電源から給電されていない場合、前記圧縮機から吐出された冷媒を前記室外熱交換器にて放熱させ、放熱した当該冷媒を前記圧縮機に戻す簡易ホットガス除霜モードを実行し、前記インジェクション回路は動作させず、又は、前記ホットガス除霜モードを実行し、前記インジェクション回路は動作させないことを特徴とする請求項1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。 - 前記制御手段は、前記外部電源から給電されていない場合であって、前記バッテリの残量が少ない場合に、前記簡易ホットガス除霜モードを実行し、前記インジェクション回路は動作させず、又は、前記ホットガス除霜モードを実行し、前記インジェクション回路は動作させないことを特徴とする請求項7に記載の車両用空気調和装置。
- 前記制御手段は、前記車室内温度が所定値より低くなるまで前記圧縮機から吐出された冷媒を前記室外熱交換器にて放熱させ、放熱した当該冷媒を減圧した後、前記吸熱器にて吸熱させる逆サイクル除霜モードを実行すると共に、前記インジェクション回路は動作させず、
前記車室内温度が所定値より低くなった場合は、前記圧縮機から吐出された冷媒を前記放熱器と室外熱交換器にて放熱させ、放熱した当該冷媒を減圧した後、前記吸熱器にて吸熱させる除湿冷房型除霜モードを実行し、前記インジェクション回路を動作させることを特徴とする請求項1乃至請求項8のうちの何れかに記載の車両用空気調和装置。 - 前記制御手段は、前記室外熱交換器を除霜する際、前記車室内温度が所定値より低い場合又は車室内を暖房する必要がある場合、前記空気流通路への外気の導入を停止することを特徴とする請求項1乃至請求項9のうちの何れかに記載の車両用空気調和装置。
- 前記制御手段は、前記除湿冷房型除霜モード又は前記ホットガス除霜モードを実行する際、前記空気流通路への外気の導入を停止することを特徴とする請求項2、請求項3、又は、請求項5のうちの何れかに記載の車両用空気調和装置。
- 前記制御手段は、車速が所定値以下の場合に前記室外熱交換器を除霜することを特徴とする請求項1乃至請求項11のうちの何れかに記載の車両用空気調和装置。
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US10220678B2 (en) | 2019-03-05 |
CN105517824B (zh) | 2018-05-18 |
US20180236845A1 (en) | 2018-08-23 |
DE112014004045T5 (de) | 2016-07-14 |
CN105517824A (zh) | 2016-04-20 |
US10279654B2 (en) | 2019-05-07 |
US20160201961A1 (en) | 2016-07-14 |
JP2015048041A (ja) | 2015-03-16 |
JP6223753B2 (ja) | 2017-11-01 |
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