WO2014073689A1 - 車両用空気調和装置 - Google Patents
車両用空気調和装置 Download PDFInfo
- Publication number
- WO2014073689A1 WO2014073689A1 PCT/JP2013/080474 JP2013080474W WO2014073689A1 WO 2014073689 A1 WO2014073689 A1 WO 2014073689A1 JP 2013080474 W JP2013080474 W JP 2013080474W WO 2014073689 A1 WO2014073689 A1 WO 2014073689A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- outdoor heat
- compressor
- radiator
- Prior art date
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—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
-
- 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
-
- 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
- B60H1/00978—Control systems or circuits characterised by failure of detection or safety means; Diagnostic methods
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
- B60H1/3213—Control means therefor for increasing the efficiency in a vehicle heat pump
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3225—Cooling devices using compression characterised by safety arrangements, e.g. compressor anti-seizure means or by signalling devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- 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
- F25B49/005—Arrangement or mounting of control or safety devices of safety devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
-
- 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
-
- 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
-
- 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
-
- 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
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
-
- 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
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/01—Timing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2519—On-off valves
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/02—Humidity
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/195—Pressures of the condenser
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
-
- 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
- F25B40/02—Subcoolers
-
- 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
Definitions
- the present invention relates to a heat pump type air conditioner that air-conditions the interior of a vehicle, and more particularly to an air conditioner that can be applied to a hybrid vehicle or an electric vehicle.
- an air conditioner that can be applied to such a vehicle, a compressor that compresses and discharges the refrigerant, a radiator that is provided on the vehicle interior side and dissipates the refrigerant, and is provided on the vehicle interior side.
- a heating cycle, a cooling cycle in which the refrigerant discharged from the compressor dissipates heat in the outdoor heat exchanger and absorbs heat in the heat absorber, and a refrigerant discharged from the compressor in the radiator Is radiated in fine outdoor heat exchanger, which executes each operation mode of the dehumidifying cooling cycle to heat absorption have been developed in the heat sink (
- control is basically performed so as to prevent the refrigerant from flowing into the outdoor heat exchanger and the refrigerant from the outdoor heat exchanger. Therefore, immediately before the mode switching from the operation mode of the dehumidification heating cycle (hereinafter referred to as dehumidification heating mode) to the internal cycle mode, or from the operation mode of the dehumidification cooling cycle (hereinafter referred to as dehumidification cooling mode) to the internal cycle mode.
- dehumidification heating mode the operation mode of the dehumidification heating cycle
- dehumidification cooling mode the operation mode of the dehumidification cooling cycle
- the present invention has been made to solve the conventional technical problem, and provides an air conditioner for a vehicle that can effectively eliminate the occurrence of excess or deficiency of the circulating refrigerant amount in the internal cycle mode.
- the purpose is to do.
- An air conditioner for a vehicle includes a compressor that compresses a refrigerant, an air flow passage through which air supplied to the passenger compartment flows, and a radiator that is provided in the air flow passage and radiates heat from the refrigerant.
- a heat absorber that is provided in the air flow passage and absorbs the refrigerant; an outdoor heat exchanger that is provided outside the vehicle cabin to dissipate or absorb heat; and an expansion valve that depressurizes the refrigerant flowing into the outdoor heat exchanger;
- Dehumidifying heating mode in which the discharged refrigerant is radiated by a radiator, the radiated refrigerant is depressurized and then absorbed by a heat absorber and an outdoor heat exchanger, the inflow of refrigerant to the outdoor heat exchanger, and the outdoor heat Prevents refrigerant from flowing out of exchanger
- the internal cycle mode in which the refrigerant discharged from the compressor is dissipated by a radiator, the refrigerant that has been radiated is depressurized, and the heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is exchanged with the radiator and the outdoor heat
- dehumidifying and cooling mode in which heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is depressurized.
- control unit performs switching between the cooling mode in which heat is absorbed by the heat absorber, and the control unit includes a refrigerant enclosure that encloses the refrigerant in the outdoor heat exchanger when the circulating refrigerant amount is excessive in the internal cycle mode.
- the refrigerant discharge mode for discharging the refrigerant from the outdoor heat exchanger is executed.
- the control means determines whether or not the circulating refrigerant amount is excessive based on the refrigerant supercooling degree of the radiator, and discharges the refrigerant overheated by the compressor. It is characterized by determining whether or not the amount of circulating refrigerant is insufficient based on the degree.
- An air conditioner for a vehicle includes a compressor that compresses the refrigerant, an air flow passage through which air supplied to the passenger compartment flows, and a radiator that is provided in the air flow passage and radiates the refrigerant.
- a heat absorber that is provided in the air flow passage and absorbs the refrigerant; an outdoor heat exchanger that is provided outside the vehicle cabin to dissipate or absorb heat; and an expansion valve that depressurizes the refrigerant flowing into the outdoor heat exchanger;
- Dehumidifying heating mode in which the discharged refrigerant is radiated by a radiator, the radiated refrigerant is depressurized and then absorbed by a heat absorber and an outdoor heat exchanger, the inflow of refrigerant to the outdoor heat exchanger, and the outdoor heat Prevents refrigerant from flowing out of exchanger
- the internal cycle mode in which the refrigerant discharged from the compressor is dissipated by a radiator, the refrigerant that has been radiated is depressurized, and the heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is exchanged with the radiator and the outdoor heat
- dehumidifying and cooling mode in which heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is depressurized.
- control unit performs switching between the cooling mode in which heat is absorbed by the heat absorber, and the control means closes the expansion valve for reducing the pressure of the refrigerant flowing into the outdoor heat exchanger in the internal cycle mode.
- the refrigerant is prevented from flowing into the storage unit and discharged from the outdoor heat exchanger at a predetermined time interval.
- an air conditioning apparatus for a vehicle, wherein the control means adjusts a timing and / or a discharge amount of the refrigerant from the outdoor heat exchanger based on a refrigerant flow rate.
- An air conditioner for a vehicle includes a compressor that compresses the refrigerant, an air flow passage through which air supplied to the passenger compartment flows, and a radiator that is provided in the air flow passage and radiates heat from the refrigerant.
- a heat absorber that is provided in the air flow passage and absorbs the refrigerant; an outdoor heat exchanger that is provided outside the vehicle cabin to dissipate or absorb heat; and an expansion valve that depressurizes the refrigerant flowing into the outdoor heat exchanger;
- Dehumidifying heating mode in which the discharged refrigerant is radiated by a radiator, the radiated refrigerant is depressurized and then absorbed by a heat absorber and an outdoor heat exchanger, the inflow of refrigerant to the outdoor heat exchanger, and the outdoor heat Prevents refrigerant from flowing out of exchanger
- the internal cycle mode in which the refrigerant discharged from the compressor is dissipated by a radiator, the refrigerant that has been radiated is depressurized, and the heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is exchanged with the radiator and the outdoor heat
- dehumidifying and cooling mode in which heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is depressurized.
- the control means is executed by switching the cooling mode in
- An air conditioner for a vehicle includes a compressor that compresses the refrigerant, an air flow passage through which air supplied to the passenger compartment flows, and a radiator that is provided in the air flow passage and dissipates the refrigerant.
- a heat absorber that is provided in the air flow passage and absorbs the refrigerant; an outdoor heat exchanger that is provided outside the vehicle cabin to dissipate or absorb heat; and an expansion valve that depressurizes the refrigerant flowing into the outdoor heat exchanger;
- Dehumidifying heating mode in which the discharged refrigerant is radiated by a radiator, the radiated refrigerant is depressurized and then absorbed by a heat absorber and an outdoor heat exchanger, the inflow of refrigerant to the outdoor heat exchanger, and the outdoor heat Prevents refrigerant from flowing out of exchanger
- the internal cycle mode in which the refrigerant discharged from the compressor is dissipated by a radiator, the refrigerant that has been radiated is depressurized, and the heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is exchanged with the radiator and the outdoor heat
- dehumidifying and cooling mode in which heat is absorbed by the heat absorber, and the refrigerant discharged from the compressor is radiated by the outdoor heat exchanger, and the radiated refrigerant is depressurized. Thereafter, the control means switches between the cooling mode in which heat
- the inflow of the refrigerant to the outdoor heat exchanger and the outflow of the refrigerant from the outdoor heat exchanger are prevented, and the refrigerant discharged from the compressor is used as the radiator. If the amount of circulating refrigerant is excessive in the internal cycle mode in which the heat dissipated and the heat dissipated is depressurized and then absorbed by the heat absorber, the refrigerant enclosing mode for enclosing the refrigerant in the outdoor heat exchanger is executed and circulated.
- the refrigerant discharge mode for releasing the refrigerant from the outdoor heat exchanger is executed, so the refrigerant sealed in the outdoor heat exchanger according to the state immediately before the mode switching to the internal cycle mode. Even if the amount changes and the circulating refrigerant amount becomes excessive or insufficient, it is possible to appropriately adjust the circulating refrigerant amount to ensure the necessary air conditioning performance, or to avoid the occurrence of high pressure abnormality due to excessive refrigerant. Possible
- control means determines whether or not the circulating refrigerant amount is excessive based on the refrigerant supercooling degree of the radiator, and the circulating refrigerant quantity based on the discharge refrigerant superheating degree of the compressor. If it is determined whether or not the amount of refrigerant is insufficient, it is possible to accurately determine the excess or deficiency of the circulating refrigerant amount and adjust the circulating refrigerant amount in the internal cycle mode with high accuracy.
- the refrigerant flowing into the outdoor heat exchanger and the refrigerant flowing out of the outdoor heat exchanger are prevented, and the refrigerant discharged from the compressor is used as the radiator.
- the control means releases the refrigerant from the outdoor heat exchanger at predetermined time intervals, the expansion valve that decompresses the refrigerant flowing into the outdoor heat exchanger is closed to prevent the refrigerant from flowing into the outdoor heat exchanger.
- control means adjusts the timing and / or the discharge amount of the refrigerant from the outdoor heat exchanger based on the refrigerant flow rate as in the invention of claim 4, the refrigerant discharge from the outdoor heat exchanger. It becomes possible to control the amount more accurately and adjust the circulating refrigerant amount with high accuracy.
- the refrigerant flowing into the outdoor heat exchanger and the refrigerant flowing out of the outdoor heat exchanger are prevented, and the refrigerant discharged from the compressor is used as the radiator.
- the control means delays the timing of preventing the refrigerant from flowing out of the outdoor heat exchanger when shifting to the internal cycle mode in which the heat dissipated and the heat dissipated is decompressed and then absorbed by the heat absorber. It is possible to avoid the shortage of the circulating refrigerant amount that occurs after shifting to the internal cycle mode, and to ensure the required air conditioning performance.
- the inflow of the refrigerant to the outdoor heat exchanger and the outflow of the refrigerant from the outdoor heat exchanger are prevented, and the refrigerant discharged from the compressor is used as the radiator.
- the control means delays the timing of preventing the refrigerant from flowing into the outdoor heat exchanger when shifting to the internal cycle mode in which the refrigerant that has been radiated is depressurized and depressurized, and then absorbed by the heat absorber. Therefore, it is possible to avoid an excessive amount of circulating refrigerant that occurs after the transition to the internal cycle mode, and to eliminate the occurrence of a high-pressure abnormality.
- FIG. 6 is a view for explaining still another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller of FIG. 2.
- FIG. 10 is a diagram for explaining still another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller of FIG. 2.
- FIG. 10 is a diagram for explaining still another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller of FIG. 2.
- 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.
- the vehicle air conditioner 1 of the embodiment performs heating by a heat pump operation using a refrigerant circuit in an electric vehicle that cannot be heated by engine waste heat, and further operates in each operation mode such as dehumidifying heating, cooling dehumidification, and cooling. Is selectively executed.
- the present invention is not limited to an electric vehicle as a vehicle, but is also applicable to a so-called hybrid vehicle that uses an engine and an electric motor for traveling, and is also applicable to a normal vehicle that travels with an engine.
- An air conditioner 1 for a vehicle performs air conditioning (heating, cooling, dehumidification, and ventilation) in a passenger compartment of an electric vehicle, and an electric compressor 2 that compresses and boosts a refrigerant.
- a radiator 4 provided in the air flow passage 3 of the HVAC unit 10 through which air in the passenger compartment 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 an electric valve, an outdoor heat exchanger 7 that functions as a radiator during cooling and functions as an evaporator during heating, and performs heat exchange between the refrigerant and outside air, and decompresses and expands the refrigerant.
- An indoor expansion valve 8 composed of an electric valve, a heat absorber 9 provided in the air flow passage 3 to absorb heat from the outside of the vehicle interior during cooling and dehumidifying heating, and an evaporation capacity control for adjusting the evaporation capacity in the heat absorber 9 Valve 11 and Accum Over data 12 and the like are sequentially connected by a refrigerant pipe 13, the refrigerant circuit R is formed.
- the outdoor heat exchanger 7 is provided with an outdoor blower 15 for exchanging heat between the outside air and the refrigerant when the vehicle is stopped.
- the outdoor heat exchanger 7 has a header portion 14 and a supercooling portion 16 in order on the downstream side of the refrigerant, and the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 has 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 header portion 14 and the supercooling portion 16 structurally constitute a part of the outdoor heat exchanger 7, and the check valve 18 has a forward direction on the indoor expansion valve 8 side.
- the refrigerant pipe 13B between the check valve 18 and the indoor expansion valve 8 is provided in a heat exchange relationship with the refrigerant pipe 13C exiting the evaporation capacity control valve 11 located on the outlet side of the heat absorber 9, and internal heat is generated by both.
- the exchanger 19 is configured.
- the refrigerant flowing into the indoor expansion valve 8 through the refrigerant pipe 13B is cooled (supercooled) by the low-temperature refrigerant that has exited the heat absorber 9 and passed through the evaporation capacity control valve 11.
- the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched, and this branched refrigerant pipe 13D is downstream of the internal heat exchanger 19 via an electromagnetic valve (open / close valve) 21 that is opened during heating.
- the refrigerant pipe 13C is connected in communication.
- the refrigerant pipe 13E on the outlet side of the radiator 4 is branched in front of the outdoor expansion valve 6, and this branched refrigerant pipe 13F is a check valve via an electromagnetic valve (open / close valve) 22 that is opened during dehumidification. 18 is connected to the refrigerant pipe 13B on the downstream side.
- the refrigerant pipe 13G on the discharge side of the compressor 2 branches, and the branched refrigerant pipe 13H is opened when the outdoor heat exchanger 7 is defrosted and directly receives the high-temperature refrigerant (hot gas) discharged from the compressor 2. It is connected to a refrigerant pipe 13I between the outdoor expansion valve 6 and the outdoor heat exchanger 7 through an electromagnetic valve (open / close valve) 23 and a check valve 24 for flowing into the outdoor heat exchanger 7.
- the check valve 24 has a forward direction in the direction of the refrigerant pipe 13I.
- each of the inside air suction port and the outside air suction port (represented by the suction port 25 in FIG. 1) is formed.
- 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.
- 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.
- 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 downstream side of the radiator 4, foot, vent, and differential air outlets (represented by the air outlet 29 in FIG. 1) are formed. Is provided with a blower outlet switching damper 31 for switching and controlling the blowing of air from each of the blowout ports.
- 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 for detecting the temperature sucked into the air flow passage 3 from the suction port 25, an inside air temperature sensor 37 for detecting the temperature of the air (inside air) in the passenger compartment, and the air in the passenger compartment
- An indoor air humidity sensor 38 for detecting the humidity of the vehicle
- an indoor CO 2 concentration sensor 39 for detecting the carbon dioxide concentration in the passenger compartment
- an outlet temperature sensor 41 for detecting the temperature of the air blown from the outlet 29 into the passenger compartment
- a discharge pressure sensor 42 for detecting the discharge refrigerant pressure of the compressor 2
- a discharge temperature sensor 43 for detecting the discharge refrigerant temperature of the compressor 2
- a suction pressure sensor 44 for detecting the refrigerant pressure
- a radiator temperature sensor 46 for detecting the temperature of the radiator 4 (the temperature of the radiator 4 itself, or the temperature of the air heated by the radiator 4), and heat dissipation.
- a radiator pressure sensor 47 for detecting the refrigerant pressure of the radiator 4 (in the radiator 4 or the pressure of the refrigerant exiting the radiator 4) and the temperature of the heat absorber 9 (the heat absorber 9 itself or the heat absorber 9).
- a heat absorber temperature sensor 48 for detecting the temperature of the cooled air
- a heat absorber pressure sensor 49 for detecting the refrigerant pressure of the heat absorber 9 (the pressure of the refrigerant in or out of the heat absorber 9).
- a photosensor-type solar radiation sensor 51 for detecting the amount of solar radiation into the vehicle interior
- a vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, and switching of temperature and operation mode are set.
- the temperature of the operation unit 53 and the outdoor heat exchanger 7 are detected.
- the outputs of the outdoor heat exchanger temperature sensor 54 and the outdoor heat exchanger pressure sensor 56 that detects the refrigerant pressure of the outdoor heat exchanger 7 are connected.
- the output of the controller 32 includes the compressor 2, the outdoor blower 15, the indoor blower (blower fan) 27, the suction switching damper 26, the air mix damper 28, the suction port switching damper 31, and the outdoor expansion valve 6.
- the indoor expansion valve 8, the electromagnetic valves 23, 22, 17, 21 and the evaporation capacity control valve 11 are connected.
- an electrical heater 57 provided in the air flow passage 3 on the air downstream side of the radiator 4 is connected to the output of the controller 32 to complement heating by the radiator 4, and the controller 32 outputs the output of each sensor. These are controlled based on the settings input at the operation unit 53.
- the controller 32 is roughly divided into a heating mode, a dehumidifying heating mode, an internal cycle mode, a dehumidifying cooling mode, and a cooling mode, and executes them.
- a heating mode a dehumidifying heating mode
- an internal cycle mode a dehumidifying cooling mode
- a cooling mode a cooling mode
- (1) Heating mode When the heating mode is selected by the controller 32 or by manual operation to the operation unit 53, the controller 32 opens the electromagnetic valve 21, and closes the electromagnetic valve 17, the electromagnetic valve 22, and the electromagnetic valve 23. 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. 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. Deprived, cooled, and condensed into liquid.
- the refrigerant liquefied in the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipe 13E, 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 number of revolutions of the compressor 2 based on the high pressure of the refrigerant circuit R detected by the discharge pressure sensor 42 or the radiator pressure sensor 47, and the temperature of the radiator 4 detected by the radiator temperature sensor 46.
- the valve opening degree of the outdoor expansion valve 6 is controlled based on the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47, and the degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled.
- the controller 32 opens the electromagnetic valve 22 in the heating mode.
- a part of the condensed refrigerant flowing through the refrigerant pipe 13E via the radiator 4 is diverted and reaches the indoor expansion valve 8 via the electromagnetic valve 22 and the refrigerant pipes 13F and 13B via the internal heat exchanger 19.
- the refrigerant After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.
- the refrigerant evaporated in the heat absorber 9 merges with the refrigerant from the refrigerant pipe 13D in the refrigerant pipe 13C through the evaporation capacity control valve 11 and the internal heat exchanger 19, and then repeats circulation sucked into the compressor 2 through the accumulator 12. . Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed.
- the controller 32 controls the number of revolutions of the compressor 2 based on the high pressure of the refrigerant circuit R detected by the discharge pressure sensor 42 or the radiator pressure sensor 47 and adjusts the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48. Based on this, the valve opening degree of the outdoor expansion valve 6 is controlled.
- the controller 32 fully closes the outdoor expansion valve 6 in the dehumidifying and heating mode state (fully closed position) and also closes the electromagnetic valve 21. Since the outdoor expansion valve 6 and the electromagnetic valve 21 are closed, the inflow of refrigerant to the outdoor heat exchanger 7 and the outflow of refrigerant from the outdoor heat exchanger 7 are blocked. All the condensed refrigerant flowing through the refrigerant pipe 13E through the refrigerant flows through the electromagnetic valve 22 to the refrigerant pipe 13F. And the refrigerant
- 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 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 as described later.
- the controller 32 opens the solenoid valve 17, and closes the solenoid valve 21, the solenoid valve 22, and the solenoid valve 23. 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. 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 into the header section 14 and the supercooling section 16 from the refrigerant pipe 13A through the electromagnetic valve 17. 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.
- a radiator pressure PCI to be described later.
- Cooling Mode in the cooling mode, the controller 32 fully opens the outdoor expansion valve 6 (the valve opening is the upper limit of control) in the dehumidifying and cooling mode, and the air mix damper 28 allows air to flow to the radiator 4. It is assumed that it will not be done. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is not ventilated to the radiator 4, it only passes here, and the refrigerant exiting the radiator 4 reaches the outdoor expansion valve 6 via the refrigerant pipe 13E.
- the controller 32 fully opens the outdoor expansion valve 6 (the valve opening is the upper limit of control) in the dehumidifying and cooling mode, and the air mix damper 28 allows air to flow to the radiator 4. It is assumed that it will not be done. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is not ventilated to the radiator 4, it only passes here,
- the refrigerant flows into the outdoor heat exchanger 7 as it is, where it is cooled by air or by the outside air ventilated by the outdoor blower 15 to be condensed and liquefied.
- the refrigerant that has exited the outdoor heat exchanger 7 sequentially flows into the header section 14 and the supercooling section 16 from the refrigerant pipe 13A through the electromagnetic valve 17.
- 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 control block diagram of the compressor 2 and the outdoor expansion valve 6 by the controller 32 in FIG. FIG. 3 is a control block diagram of the controller 32 for determining the target rotational speed (compressor target rotational speed) TGNCh of the compressor 2 for the heating mode and the dehumidifying heating mode.
- the F / F manipulated variable TGNChff of the compressor target rotational speed is calculated based on the compressor temperature TCO and the target radiator pressure PCO which is the target value of the pressure of the radiator 4.
- TAO is a target outlet temperature which is a target value of the air temperature from the outlet 29
- TH is the temperature of the radiator 4 (heat radiator temperature) obtained from the radiator temperature sensor 46
- Te is obtained from the heat absorber temperature sensor 48.
- the air mix damper opening SW changes in the range of 0 ⁇ SW ⁇ 1, and the air mix fully closed state in which the ventilation to the radiator 4 is 0 and 1 is 1 The air mix is fully opened when all the air in the air flow passage 3 is ventilated to the radiator 4.
- the target radiator pressure PCO is calculated by the target value calculator 59 based on the target supercooling degree TGSC and the target radiator temperature TCO. Further, the F / B (feedback) manipulated variable calculator 60 calculates the F / B manipulated variable TGNChfb of the compressor target rotational speed based on the target radiator pressure PCO and the radiator pressure PCI that is the refrigerant pressure of the radiator 4. To do.
- the F / F manipulated variable TGNCnff computed by the F / F manipulated variable computing unit 58 and the TGNChfb computed by the F / B manipulated variable computing unit 60 are added by the adder 61, and the control upper limit value and the control are controlled by the limit setting unit 62. After the lower limit is set, it is determined as the compressor target rotational speed TGNCh.
- the controller 32 controls the rotational speed of the compressor 2 based on the compressor target rotational speed TGNCh.
- FIG. 4 is a control block diagram of the controller 32 for determining the target rotational speed (compressor target rotational speed) TGNCc of the compressor 2 for the cooling mode and the dehumidifying cooling mode.
- the F / F operation amount calculation unit 63 of the controller 32 performs F / F operation of the compressor target rotation speed based on the outside air temperature Tam, the blower voltage BLV, and the target heat absorber temperature TEO that is the target value of the temperature of the heat absorber 9.
- the quantity TGNCcff is calculated.
- the F / B manipulated variable calculator 64 calculates the F / B manipulated variable TGNCcfb of the compressor target rotation 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 63 and the F / B manipulated variable TGNCcfb computed by the F / B manipulated variable computing unit 64 are added by the adder 66, and the limit setting unit 67 After the control upper limit value and the control lower limit value are set, the compressor target rotational speed TGNCc is determined. In the cooling mode and the dehumidifying cooling mode, the controller 32 controls the rotational speed of the compressor 2 based on the compressor target rotational speed TGNCc.
- the controller 32 calculates the compressor target rotational speed TGNCh calculated for the heating mode and the dehumidifying heating mode, and the compressor target rotational speed TGNCc calculated for the cooling mode and the dehumidifying cooling mode.
- the rotational speed of the compressor 2 is controlled by using the smaller one of the operation amounts.
- FIG. 5 is a control block diagram of the controller 32 for determining the target opening degree (outdoor expansion valve target opening degree) TGECCVpc of the outdoor expansion valve 6 in the dehumidifying and cooling mode.
- the F / F manipulated variable calculation unit 68 of the controller 32 performs the F / F manipulated variable TGECCVpcff of the outdoor expansion valve target opening based on the outside air temperature Tam, the blower voltage BLV, the target radiator temperature TCO, and the target radiator pressure PCO. Is calculated.
- the F / B manipulated variable calculator 69 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 68 and the F / B manipulated variable TGECCVpcfb computed by the F / B manipulated variable computing unit 69 are added by the adder 71, and the limit setting unit 72 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 dehumidifying and cooling 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.
- the air flowing through the air flow passage 3 is blown out from the outlet 29 into the vehicle interior in response to cooling from the heat absorber 9 and heating from the heat radiator 4 (adjusted by the air mix damper 28) in each operation mode.
- the controller 32 detects the outside air temperature Tam detected by the outside air temperature sensor 33, the vehicle interior temperature detected by the inside air temperature sensor 37, the blower voltage, the amount of solar radiation detected by the solar radiation sensor 51, and the vehicle set by the operation unit 53.
- a target blowout temperature TAO is calculated based on the indoor target vehicle cabin temperature (set temperature), and the temperature of the air blown from the blowout outlet 29 is controlled to this target blowout temperature TAO by switching each operation mode as will be described later. Is.
- the controller 32 selects an operation mode as shown in FIG. That is, in this embodiment, 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 blowing temperature TAO.
- a broken line L3 is a hysteresis line set above a predetermined value (3 deg).
- the controller 32 selects the heating mode. Further, when the outside air temperature Tam is higher than 0 ° C. and the target blowing temperature TAO is equal to or lower than the HVAC suction temperature, the cooling mode is selected. Further, when the outside air temperature Tam is higher than 0 ° C. and not higher than a predetermined value (for example, 20 ° C.) and the target blowing temperature TAO is higher than the HVAC suction temperature, the dehumidifying heating mode is set, and the outdoor air temperature Tam is further lower than the predetermined value. When it is high, the dehumidifying and cooling mode is set. If the outside humidity detected by the outside air humidity sensor 34 is a predetermined value (for example, 50% or less) under the condition for selecting the dehumidifying heating mode, the heating mode is selected.
- a predetermined value for example, 50% or less
- each operation mode in FIG. 6 is selected and switched according to changes in the environment and setting conditions such as the outside air temperature Tam and the target blowing temperature TAO.
- 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 is changed to the cooling mode.
- the “circulation refrigerant amount” is the amount of refrigerant circulated by the compressor 2 in a region other than the outdoor heat exchanger 7 (actually, the region from the outdoor expansion valve 6 to the electromagnetic valve 21). Means.
- the controller 32 controls the outdoor expansion valve 6 and the electromagnetic valve 21 on the basis of the refrigerant supercooling degree SC at the outlet of the radiator 4 and the discharged refrigerant superheat degree SHd of the compressor 2, whereby the refrigerant circuit R
- the refrigerant enclosing mode for enclosing the refrigerant in the outdoor heat exchanger 7 and the refrigerant releasing mode for releasing the refrigerant from the outdoor heat exchanger 7 to the refrigerant circuit R are executed.
- FIG. 7 is a diagram for explaining the transition between the normal operation, the refrigerant charging mode, and the refrigerant discharge mode in the internal cycle mode
- FIG. 8 is a timing chart for explaining the operation of each part in that case.
- the controller 32 places the outdoor expansion valve 6 in the fully closed position and closes the electromagnetic valve 21 as described above.
- the refrigerant supercooling degree SC of the radiator 4 is obtained from the radiator temperature TH detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47.
- the discharge refrigerant superheat degree SHd of the compressor 2 is obtained from the discharge refrigerant temperature of the compressor 2 detected by the discharge temperature sensor 42 and the discharge refrigerant pressure of the compressor 2 detected by the discharge pressure sensor 43.
- the controller 32 increases the refrigerant supercooling degree SC of the radiator 4 and becomes equal to or greater than the SC first threshold (for example, 6 deg). Is determined to be excessive, and the mode shifts to the refrigerant charging mode ((I) in FIG. 7).
- the controller 32 opens the outdoor expansion valve 6 at the minimum control opening degree with the electromagnetic valve 21 closed (open position at the control lower limit value).
- a part of the refrigerant flowing out of the radiator 4 and flowing through the refrigerant pipe 13 ⁇ / b> E is diverted from that directed toward the electromagnetic valve 22, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6.
- the controller 32 determines that the circulating refrigerant amount has fallen to an appropriate amount, returns the outdoor expansion valve 6 to the fully closed position, and performs normal operation. Return to (II) of FIG. Thereby, the refrigerant
- the absolute value of the difference between the target radiator pressure PCO and the radiator pressure PCI is less than a predetermined value (for example, 0.05 MPa), that is, the operation state of the compressor 2 is stabilized.
- a predetermined value for example, 0.05 MPa
- the controller 32 Is determined to be insufficient (too few), and the mode shifts to the refrigerant discharge mode ((III) in FIG. 7).
- the controller 32 opens the electromagnetic valve 21 for a predetermined time (for example, 500 ms) with the outdoor expansion valve 6 in the fully closed position.
- a predetermined time for example, 500 ms
- the refrigerant confined in the outdoor heat exchanger 7 flows out into the refrigerant pipe 13D, joins the refrigerant flowing through the refrigerant pipe 13C, and is sucked into the compressor 2 from the accumulator 12.
- the controller 32 executes the refrigerant discharge mode again. ((III) in FIG. 7).
- coolant sealed in the outdoor heat exchanger 7 is discharge
- FIG. 9 shows another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller 32.
- the outdoor expansion valve 6 composed of an electric valve slightly leaks refrigerant even when in the fully closed position. Therefore, even if the internal cycle mode is executed with the circulating refrigerant amount being in an appropriate state (the normal operation state described above) and the outdoor expansion valve 6 is controlled to the fully closed position, the outdoor heat exchanger 7 has no refrigerant. There is a danger that it will be sealed and eventually fall into a state where the amount of circulating refrigerant is insufficient (too little).
- the controller 32 in the internal cycle mode, periodically opens the solenoid valve 21 at predetermined timing (predetermined time 1 in FIG. 9) at a timing every predetermined time (predetermined time 2 in FIG. 9), The refrigerant is discharged from the heat exchanger 7 to the refrigerant circuit R.
- the predetermined time 1 (refrigerant release amount) and the predetermined time 2 (refrigerant release timing) are physical quantities correlated to the refrigerant flow rate in the refrigerant circuit R, for example, the rotation speed of the compressor 2 (the above-described TGNCh). Or you may adjust based on TGNCc).
- the predetermined time 1 is lengthened and / or the predetermined time 2 is shortened so that the amount of refrigerant to be released increases, and conversely, the refrigerant flow rate
- the predetermined time 1 is shortened and / or the predetermined time 2 is lengthened to reduce the amount of refrigerant discharged.
- the timing and / or the amount of discharge of the refrigerant from the outdoor heat exchanger 7 is adjusted based on the refrigerant flow rate in the refrigerant circuit R, the amount of refrigerant discharged from the outdoor heat exchanger 7 can be reduced. It is possible to control more accurately and adjust the amount of circulating refrigerant with high accuracy.
- FIGS. 10 and 11 show still another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller 32. 7 and 8, the refrigerant is enclosed in the outdoor heat exchanger 7 and the refrigerant is discharged from the outdoor heat exchanger 7 based on the refrigerant supercooling degree of the radiator 4 and the refrigerant refrigerant superheated degree of the compressor 2. However, if only the shortage of the refrigerant needs to be avoided, the timing for closing the electromagnetic valve 21 may be delayed as shown in FIGS.
- the controller 21 switches the outdoor expansion valve 6 from the cooling or dehumidifying cooling mode to the fully closed position, opens the electromagnetic valve 22, closes the electromagnetic valve 17, and shifts to the internal cycle mode.
- the valve 21 is opened for a predetermined time (2 seconds in the embodiment) after the outdoor expansion valve 6 is in the fully closed position.
- the controller 21 sets the outdoor expansion valve 6 from the dehumidifying and heating mode to the fully closed position and closes the electromagnetic valve 21 to shift to the internal cycle mode.
- the solenoid valve 21 is closed after a time delay (2 sec in the embodiment).
- the timing for preventing the refrigerant from flowing out from the outdoor heat exchanger 7 is delayed, and thus occurs after shifting to the internal cycle mode. It becomes possible to avoid the shortage of the circulating refrigerant amount and to ensure the required air conditioning performance.
- FIGS. 12 and 13 show still another example of the circulating refrigerant amount adjustment control in the internal cycle mode by the controller 32.
- the timing for setting the outdoor expansion valve 6 to the fully closed position may be delayed as shown in FIGS.
- the controller 21 sets the outdoor expansion valve 6 from the cooling or dehumidifying cooling mode to the fully closed position, opens the electromagnetic valve 22, closes the electromagnetic valve 17, and shifts to the internal cycle mode.
- the outdoor expansion valve 6 is set to the fully closed position after a predetermined time (2 sec in the embodiment) after switching. Further, in FIG. 13, the controller 21 sets the outdoor expansion valve 6 from the dehumidifying and heating mode to the fully closed position, closes the solenoid valve 21 and shifts to the internal cycle mode, and then closes the solenoid valve 21 for a predetermined time (in the embodiment). 2 sec) with delay, the outdoor expansion valve 6 is fully closed.
- the timing for preventing the refrigerant from flowing into the outdoor heat exchanger 7 is delayed, and thus occurs after shifting to the internal cycle mode.
- An excessive amount of circulating refrigerant can be avoided in advance, and the occurrence of high pressure abnormality can be eliminated.
Abstract
Description
制御手段が所定時間毎のタイミングで室外熱交換器から冷媒を放出するようにしたので、室外熱交換器に流入する冷媒を減圧する膨張弁を閉じて室外熱交換器への冷媒の流入を阻止するときの、膨張弁の漏れによって生じる室外熱交換器への冷媒流入による循環冷媒量の不足を、所定時間毎の冷媒放出によって解消し、必要な空調性能を確保することが可能となる。
コントローラ32により或いは操作部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23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23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室外膨張弁6を全開(弁開度を制御上限)とし、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とする。これにより、圧縮機2から吐出された高温高圧のガス冷媒は放熱器4に流入する。放熱器4には空気流通路3内の空気は通風されないので、ここは通過するのみとなり、放熱器4を出た冷媒は冷媒配管13Eを経て室外膨張弁6に至る。
モードと除湿冷房モードにおいては、コントローラ32はこの圧縮機目標回転数TGNCcに基づいて圧縮機2の回転数を制御する。
次に、図6を参照しながらコントローラ32による上記各運転モードの切換制御について説明する。コントローラ32は起動時に図6に示すように運転モードを選択する。即ち、この実施例でコントローラ32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。この図6において破線L1は目標吹出温度TAO=外気温度Tamの線であり、実線L2は目標吹出温度TAO=HVAC吸込温度(吸込口25から空気流通路3に吸い込まれる温度)の線である。また、破線L3はそれより所定値(3deg)上に設定したヒステリシスの線である。
しかしながら、この内部サイクルモードでは室外膨張弁6が全閉位置とされ、電磁弁21も閉じられ、室外熱交換器7への冷媒の流入と室外熱交換器7からの冷媒の流出が阻止されるため、除湿暖房モードから内部サイクルモードへ、或いは、除湿冷房モードから内部サイクルモードへの運転モードの切換直前に室外熱交換器7内を流れている冷媒の状態によって、当該室外熱交換器7内に封じ込まれる冷媒の量が変わってくる。そのために運転モードの切換後に実行される内部サイクルモードにおける冷媒回路R内の循環冷媒量に過不足が生じてくる。
次に、図9のタイミングチャートは、コントローラ32による内部サイクルモードにおける循環冷媒量調整制御の他の例を示している。電動弁から構成される室外膨張弁6は、全閉位置としても僅かに冷媒漏れが生じる。従って、循環冷媒量が適正の状態(前述した通常運転の状態)で内部サイクルモードが実行され、室外膨張弁6を全閉位置に制御していたとしても、室外熱交換器7には冷媒が封入されていき、やがては循環冷媒量が不足(過少)する状態に陥る危険性がある。
次に、図10及び図11のタイミングチャートは、コントローラ32による内部サイクルモードにおける循環冷媒量調整制御の更に他の例を示している。前記図7及び図8の例では放熱器4の冷媒過冷却度と圧縮機2の吐出冷媒過熱度に基づいて室外熱交換器7への冷媒の封入と室外熱交換器7からの冷媒の放出を制御したが、冷媒不足のみを回避すればよい場合には、図10及び図11に示すように電磁弁21を閉じるタイミングを遅延させればよい。
次に、図12及び図13のタイミングチャートは、コントローラ32による内部サイクルモードにおける循環冷媒量調整制御の更にもう一つの他の例を示している。上記実施例とは逆に冷媒過多のみを回避すればよい場合には、図12及び図13に示すように室外膨張弁6を全閉位置とするタイミングを遅延させればよい。
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、21、22、23 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)
57 電気ヒータ
R 冷媒回路
Claims (6)
- 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室外熱交換器と、
該室外熱交換器に流入する冷媒を減圧させる膨張弁と、
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る暖房モードと、
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、前記吸熱器と前記室外熱交換器にて吸熱させる除湿暖房モードと、
前記室外熱交換器への冷媒の流入と当該室外熱交換器からの冷媒の流出を阻止し、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、前記吸熱器にて吸熱させる内部サイクルモードと、
前記圧縮機から吐出された冷媒を前記放熱器及び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モードと、
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冷房モードとを切り換えて実行する車両用空気調和装置において、
前記制御手段は、前記内部サイクルモードにおいて、循環冷媒量が過多である場合、前記室外熱交換器に冷媒を封入する冷媒封入モードを実行し、循環冷媒量が不足している場合は、前記室外熱交換器から冷媒を放出する冷媒放出モードを実行することを特徴とする車両用空気調和装置。 - 前記制御手段は、前記放熱器の冷媒過冷却度に基づいて循環冷媒量が過多であるか否かを判断し、前記圧縮機の吐出冷媒過熱度に基づいて循環冷媒量が不足しているか否かを判断することを特徴とする請求項1に記載の車両用空気調和装置。
- 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室外熱交換器と、
該室外熱交換器に流入する冷媒を減圧させる膨張弁と、
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る暖房モードと、
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、前記吸熱器と前記室外熱交換器にて吸熱させる除湿暖房モードと、
前記室外熱交換器への冷媒の流入と当該室外熱交換器からの冷媒の流出を阻止し、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、前記吸熱器にて吸熱させる内部サイクルモードと、
前記圧縮機から吐出された冷媒を前記放熱器及び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モードと、
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冷房モードとを切り換えて実行する車両用空気調和装置において、
前記制御手段は、前記内部サイクルモードにおいて、前記室外熱交換器に流入する冷媒を減圧する膨張弁を閉じて当該室外熱交換器への流入を阻止すると共に、
所定時間毎のタイミングで前記室外熱交換器から冷媒を放出することを特徴とする車両用空気調和装置。 - 前記制御手段は、冷媒流量に基づいて前記室外熱交換器から冷媒を放出するタイミング及び/又は放出量を調整することを特徴とする請求項3に記載の車両用空気調和装置。
- 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室外熱交換器と、
該室外熱交換器に流入する冷媒を減圧させる膨張弁と、
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る暖房モードと、
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、前記吸熱器と前記室外熱交換器にて吸熱させる除湿暖房モードと、
前記室外熱交換器への冷媒の流入と当該室外熱交換器からの冷媒の流出を阻止し、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、前記吸熱器にて吸熱させる内部サイクルモードと、
前記圧縮機から吐出された冷媒を前記放熱器及び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モードと、
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冷房モードとを切り換えて実行する車両用空気調和装置において、
前記制御手段は、前記内部サイクルモードに移行する際、前記室外熱交換器からの冷媒の流出を阻止するタイミングを遅延させることを特徴とする車両用空気調和装置。 - 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室外熱交換器と、
該室外熱交換器に流入する冷媒を減圧させる膨張弁と、
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る暖房モードと、
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、前記吸熱器と前記室外熱交換器にて吸熱させる除湿暖房モードと、
前記室外熱交換器への冷媒の流入と当該室外熱交換器からの冷媒の流出を阻止し、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、前記吸熱器にて吸熱させる内部サイクルモードと、
前記圧縮機から吐出された冷媒を前記放熱器及び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モードと、
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冷房モードとを切り換えて実行する車両用空気調和装置において、
前記制御手段は、前記内部サイクルモードに移行する際、前記室外熱交換器への冷媒の流入を阻止するタイミングを遅延させることを特徴とする車両用空気調和装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112013005347.0T DE112013005347T5 (de) | 2012-11-09 | 2013-11-11 | Fahrzeugklimaanlage |
CN201380058543.2A CN104853942B (zh) | 2012-11-09 | 2013-11-11 | 车辆用空调装置 |
US14/441,139 US10421337B2 (en) | 2012-11-09 | 2013-11-11 | Vehicle air conditioner |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012-247513 | 2012-11-09 | ||
JP2012247513A JP6073651B2 (ja) | 2012-11-09 | 2012-11-09 | 車両用空気調和装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014073689A1 true WO2014073689A1 (ja) | 2014-05-15 |
Family
ID=50684780
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/080474 WO2014073689A1 (ja) | 2012-11-09 | 2013-11-11 | 車両用空気調和装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US10421337B2 (ja) |
JP (1) | JP6073651B2 (ja) |
CN (1) | CN104853942B (ja) |
DE (1) | DE112013005347T5 (ja) |
WO (1) | WO2014073689A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2017013652A (ja) * | 2015-07-01 | 2017-01-19 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5999637B2 (ja) * | 2012-11-09 | 2016-09-28 | サンデンホールディングス株式会社 | 車両用空気調和装置 |
EP3023716B1 (en) * | 2013-07-18 | 2022-05-18 | Hangzhou Sanhua Research Institute Co., Ltd. | Method for controlling vehicle air-conditioning system, and vehicle air-conditioning system |
JP6271195B2 (ja) * | 2013-09-18 | 2018-01-31 | サンデンホールディングス株式会社 | 車両用空気調和装置 |
JP6207958B2 (ja) * | 2013-10-07 | 2017-10-04 | サンデンホールディングス株式会社 | 車両用空気調和装置 |
JP6233009B2 (ja) * | 2013-12-26 | 2017-11-22 | 株式会社デンソー | 車両用空調装置 |
JP6496958B2 (ja) | 2014-09-19 | 2019-04-10 | サンデンホールディングス株式会社 | 車両用空気調和装置 |
KR102343081B1 (ko) * | 2015-02-25 | 2021-12-24 | 삼성전자주식회사 | 공조 장치 및 상기 공조 장치의 제어 방법 |
CN104776630B (zh) * | 2015-04-28 | 2017-05-03 | 广东美的暖通设备有限公司 | 多联机系统 |
TWI588424B (zh) * | 2015-11-06 | 2017-06-21 | 財團法人工業技術研究院 | 熱泵空調系統及其控制方法 |
JP6710061B2 (ja) * | 2016-02-26 | 2020-06-17 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
JP6692678B2 (ja) | 2016-04-14 | 2020-05-13 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
JP6680601B2 (ja) * | 2016-04-14 | 2020-04-15 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
JP6605131B2 (ja) * | 2016-05-09 | 2019-11-13 | 三菱電機株式会社 | 冷凍装置 |
WO2017212629A1 (ja) * | 2016-06-10 | 2017-12-14 | 三菱電機株式会社 | 車両用空調装置及び列車通信システム |
WO2017212631A1 (ja) * | 2016-06-10 | 2017-12-14 | 三菱電機株式会社 | 車両用空調装置及び車両用空調装置の異常検知システム |
DE102016213619A1 (de) * | 2016-07-25 | 2018-01-25 | Bayerische Motoren Werke Aktiengesellschaft | Verfahren zum betrieb eines klimasystems sowie klimasystem |
JP6692723B2 (ja) * | 2016-09-02 | 2020-05-13 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
US10561044B2 (en) * | 2017-02-02 | 2020-02-11 | Ford Global Technologies, Llc | Fluid management for autonomous vehicle sensors |
JP6875163B2 (ja) * | 2017-03-24 | 2021-05-19 | サンデンホールディングス株式会社 | 空気調和装置 |
US10955175B2 (en) * | 2017-12-04 | 2021-03-23 | Lennox Industries Inc. | Heating, ventilation, air-conditioning, and refrigeration system |
JP6925288B2 (ja) * | 2018-01-30 | 2021-08-25 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
JP2019131038A (ja) * | 2018-01-31 | 2019-08-08 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
CN113167520B (zh) * | 2018-11-29 | 2022-04-29 | 大金工业株式会社 | 制冷剂泄漏判定系统以及冷冻循环装置 |
JP7312617B2 (ja) * | 2019-06-18 | 2023-07-21 | 株式会社Subaru | 車両の空調装置 |
JP2021038891A (ja) * | 2019-09-04 | 2021-03-11 | 株式会社デンソー | 車両用空調装置 |
JP7379960B2 (ja) | 2019-09-04 | 2023-11-15 | 株式会社デンソー | 車両用空調装置 |
CN111976422B (zh) * | 2020-08-31 | 2022-09-09 | 安徽江淮汽车集团股份有限公司 | 一种热泵空调系统的控制方法 |
CN116026052B (zh) * | 2023-02-15 | 2023-05-30 | 中联云港数据科技股份有限公司 | 具有除湿功能的空调制冷系统 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05272817A (ja) * | 1992-01-30 | 1993-10-22 | Nippondenso Co Ltd | 空調装置 |
JP2009115324A (ja) * | 2007-11-01 | 2009-05-28 | Mitsubishi Electric Corp | 冷凍空調装置への冷媒充填方法、冷凍空調装置への冷媒充填装置 |
JP2011178372A (ja) * | 2010-03-04 | 2011-09-15 | Calsonic Kansei Corp | 車両用空気調和装置及びその運転切替方法 |
JP2012007856A (ja) * | 2010-06-28 | 2012-01-12 | Daikin Industries Ltd | 空気調和機 |
WO2012063289A1 (ja) * | 2010-11-11 | 2012-05-18 | 三菱電機株式会社 | 冷凍サイクル装置及び冷媒充填方法 |
JP2012176659A (ja) * | 2011-02-25 | 2012-09-13 | Sanden Corp | 車両用空気調和装置 |
Family Cites Families (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101241222B1 (ko) * | 2011-07-21 | 2013-03-13 | 기아자동차주식회사 | 차량용 히트펌프 시스템 제어방법 |
US4483156A (en) * | 1984-04-27 | 1984-11-20 | The Trane Company | Bi-directional variable subcooler for heat pumps |
US5598887A (en) * | 1993-10-14 | 1997-02-04 | Sanden Corporation | Air conditioner for vehicles |
JP3305883B2 (ja) * | 1994-07-06 | 2002-07-24 | サンデン株式会社 | 車両用空気調和装置 |
JP3305508B2 (ja) * | 1994-08-24 | 2002-07-22 | アイシン精機株式会社 | 冷却装置 |
JPH09295506A (ja) | 1996-05-01 | 1997-11-18 | Sanden Corp | 車両用空調装置 |
JP4311115B2 (ja) * | 2002-09-17 | 2009-08-12 | 株式会社デンソー | 空調装置 |
JP3841039B2 (ja) * | 2002-10-25 | 2006-11-01 | 株式会社デンソー | 車両用空調装置 |
JP2005053325A (ja) * | 2003-08-04 | 2005-03-03 | Calsonic Kansei Corp | 車両用空調装置 |
US7987679B2 (en) * | 2005-02-24 | 2011-08-02 | Mitsubishi Denki Kabushiki Kaisha | Air conditioning apparatus |
JP3988780B2 (ja) | 2005-09-09 | 2007-10-10 | ダイキン工業株式会社 | 冷凍装置 |
JP4258553B2 (ja) * | 2007-01-31 | 2009-04-30 | ダイキン工業株式会社 | 熱源ユニット及び冷凍装置 |
JP4245064B2 (ja) * | 2007-05-30 | 2009-03-25 | ダイキン工業株式会社 | 空気調和装置 |
CN101762133B (zh) | 2007-11-01 | 2012-02-01 | 三菱电机株式会社 | 面向冷冻空调装置的制冷剂填充方法 |
CN101839580A (zh) * | 2009-03-20 | 2010-09-22 | 珠海格力电器股份有限公司 | 空调系统及判断制冷剂灌注量是否合适的方法 |
JP2011005982A (ja) * | 2009-06-26 | 2011-01-13 | Denso Corp | 車両用空調装置 |
FR2958018A1 (fr) * | 2010-03-24 | 2011-09-30 | Valeo Systemes Thermiques | Boucle de chauffage, ventilation et/ou climatisation et installation de chauffage, ventilation et/ou climatisation comprenant une telle boucle de chauffage, ventilation et/ou climatisation |
FR2963665B1 (fr) * | 2010-08-05 | 2015-10-16 | Valeo Systemes Thermiques | Boucle de climatisation comprenant un dispositif de reception d'un fluide refrigerant |
JP5522264B2 (ja) * | 2010-10-06 | 2014-06-18 | 日産自動車株式会社 | 車両用空調装置 |
CN103328238B (zh) | 2011-01-21 | 2015-11-25 | 三电有限公司 | 车辆用空气调节装置 |
CN103534539B (zh) | 2011-03-03 | 2016-01-20 | 三电有限公司 | 车辆用空气调节装置 |
KR101241223B1 (ko) * | 2011-03-23 | 2013-03-25 | 기아자동차주식회사 | 차량용 히트펌프 시스템 및 그 제어방법 |
JP5821756B2 (ja) * | 2011-04-21 | 2015-11-24 | 株式会社デンソー | 冷凍サイクル装置 |
KR101339226B1 (ko) * | 2011-06-20 | 2013-12-09 | 기아자동차 주식회사 | 차량용 히트펌프 시스템 및 그 제어방법 |
JP5798402B2 (ja) * | 2011-08-01 | 2015-10-21 | トヨタ自動車株式会社 | 冷却装置 |
JP5450694B2 (ja) * | 2012-03-05 | 2014-03-26 | 本田技研工業株式会社 | 車両用空調装置 |
-
2012
- 2012-11-09 JP JP2012247513A patent/JP6073651B2/ja active Active
-
2013
- 2013-11-11 CN CN201380058543.2A patent/CN104853942B/zh active Active
- 2013-11-11 US US14/441,139 patent/US10421337B2/en active Active
- 2013-11-11 DE DE112013005347.0T patent/DE112013005347T5/de not_active Ceased
- 2013-11-11 WO PCT/JP2013/080474 patent/WO2014073689A1/ja active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05272817A (ja) * | 1992-01-30 | 1993-10-22 | Nippondenso Co Ltd | 空調装置 |
JP2009115324A (ja) * | 2007-11-01 | 2009-05-28 | Mitsubishi Electric Corp | 冷凍空調装置への冷媒充填方法、冷凍空調装置への冷媒充填装置 |
JP2011178372A (ja) * | 2010-03-04 | 2011-09-15 | Calsonic Kansei Corp | 車両用空気調和装置及びその運転切替方法 |
JP2012007856A (ja) * | 2010-06-28 | 2012-01-12 | Daikin Industries Ltd | 空気調和機 |
WO2012063289A1 (ja) * | 2010-11-11 | 2012-05-18 | 三菱電機株式会社 | 冷凍サイクル装置及び冷媒充填方法 |
JP2012176659A (ja) * | 2011-02-25 | 2012-09-13 | Sanden Corp | 車両用空気調和装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2017013652A (ja) * | 2015-07-01 | 2017-01-19 | サンデン・オートモーティブクライメイトシステム株式会社 | 車両用空気調和装置 |
US20180194191A1 (en) * | 2015-07-01 | 2018-07-12 | Sanden Automotive Climate Systems Corporation | Air Conditioner For Vehicle |
US10703166B2 (en) * | 2015-07-01 | 2020-07-07 | Sanden Automotive Climate Systems Corporation | Air conditioner for vehicle |
Also Published As
Publication number | Publication date |
---|---|
CN104853942B (zh) | 2019-11-12 |
CN104853942A (zh) | 2015-08-19 |
DE112013005347T5 (de) | 2015-07-23 |
US10421337B2 (en) | 2019-09-24 |
JP2014094674A (ja) | 2014-05-22 |
JP6073651B2 (ja) | 2017-02-01 |
US20150298525A1 (en) | 2015-10-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6073651B2 (ja) | 車両用空気調和装置 | |
JP6073653B2 (ja) | 車両用空気調和装置 | |
WO2018198581A1 (ja) | 車両用空気調和装置 | |
JP6241595B2 (ja) | 車両用空気調和装置 | |
JP6223753B2 (ja) | 車両用空気調和装置 | |
JP6271195B2 (ja) | 車両用空気調和装置 | |
WO2018193770A1 (ja) | 車両用空気調和装置 | |
JP5999637B2 (ja) | 車両用空気調和装置 | |
JP6073652B2 (ja) | 車両用空気調和装置 | |
JP6607638B2 (ja) | 車両用空気調和装置 | |
JP6005484B2 (ja) | 車両用空気調和装置 | |
WO2014192741A1 (ja) | 車両用空気調和装置 | |
JP2019038352A (ja) | 車両用空気調和装置 | |
JP2014094677A5 (ja) | ||
WO2016208337A1 (ja) | 車両用空気調和装置 | |
WO2018198582A1 (ja) | 車両用空気調和装置 | |
JP2014094673A5 (ja) | ||
JP2015229370A (ja) | 車両用空気調和装置 | |
JP6571430B2 (ja) | 車両用空気調和装置 | |
WO2017179594A1 (ja) | 車両用空気調和装置 | |
WO2020026690A1 (ja) | 車両用空気調和装置 | |
WO2018159141A1 (ja) | 車両用空気調和装置 | |
WO2022064946A1 (ja) | 車両用空調装置 | |
WO2019150832A1 (ja) | 車両用空気調和装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 13852412 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14441139 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120130053470 Country of ref document: DE Ref document number: 112013005347 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 13852412 Country of ref document: EP Kind code of ref document: A1 |