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CN113453926B - Air conditioner for vehicle - Google Patents

Air conditioner for vehicle Download PDF

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Publication number
CN113453926B
CN113453926B CN202080012854.5A CN202080012854A CN113453926B CN 113453926 B CN113453926 B CN 113453926B CN 202080012854 A CN202080012854 A CN 202080012854A CN 113453926 B CN113453926 B CN 113453926B
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CN
China
Prior art keywords
refrigerant
expansion valve
heat
temperature
air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202080012854.5A
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Chinese (zh)
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CN113453926A (en
Inventor
松村尭之
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
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Publication date
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Publication of CN113453926A publication Critical patent/CN113453926A/en
Application granted granted Critical
Publication of CN113453926B publication Critical patent/CN113453926B/en
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • 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
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • 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
    • 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
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00928—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 a secondary circuit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/326—Cooling devices information from a variable is obtained related to temperature of the refrigerant at a condensing unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/3285—Cooling devices output of a control signal related to an expansion unit
    • 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
    • F25B2700/197—Pressures of 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

Provided is an air conditioner for a vehicle, which can prevent freezing of a heat absorber and realize a target blowout temperature. The control device comprises a compressor (2), a radiator (4), an outdoor expansion valve (6), an outdoor heat exchanger (7), an indoor expansion valve (8) and a heat absorber (9), wherein the control device executes a dehumidification heating mode, in which the refrigerant discharged from the compressor (2) is radiated in the radiator (4), the radiated refrigerant is split, one refrigerant is depressurized by the indoor expansion valve (8), then the one refrigerant is subjected to heat absorption in the heat absorber (9), the other refrigerant is depressurized by the outdoor expansion valve (6), and then the other refrigerant is subjected to heat absorption in the outdoor heat exchanger (7). When the temperature of the heat absorber (9) is lower than a predetermined value, the control device sets the indoor expansion valve (8) to be fully closed.

Description

Air conditioner for vehicle
Technical Field
The present invention relates to a heat pump type air conditioner for conditioning the interior of a vehicle.
Background
In recent years, environmental problems have been developed, and thus hybrid vehicles and electric vehicles have been widely used. Further, as an air conditioner applicable to such a vehicle, an air conditioner including: a compressor that compresses a refrigerant and discharges the compressed refrigerant; a radiator that is provided inside a vehicle interior and that radiates heat from a refrigerant; a heat absorber that is provided inside a vehicle interior and absorbs heat from a refrigerant; and an outdoor heat exchanger provided outside the vehicle cabin and configured to radiate or absorb heat from a refrigerant, wherein the air conditioning apparatus is configured to switch between a heating mode in which the refrigerant discharged from the compressor is radiated to the radiator and a dehumidifying heating mode in which the refrigerant radiated to the radiator is absorbed to the outdoor heat exchanger; in the dehumidification and heating mode, the refrigerant discharged from the compressor is radiated to the radiator, and the refrigerant radiated to the radiator absorbs heat in the heat absorber and the outdoor heat exchanger; in the cooling mode, the refrigerant discharged from the compressor is radiated in the outdoor heat exchanger and absorbed in the heat absorber; in the dehumidification cooling mode, the refrigerant discharged from the compressor is radiated to the radiator and the outdoor heat exchanger, and is absorbed to the heat absorber.
In this case, an outdoor expansion valve is provided at an inlet of the outdoor heat exchanger, and the refrigerant flowing into the outdoor heat exchanger is depressurized through the outdoor expansion valve in the heating mode and the dehumidification heating mode described above. In the dehumidification and heating mode, the refrigerant flowing out of the radiator is split, one of the refrigerant is depressurized by the indoor expansion valve and flows into the heat absorber, the refrigerant absorbs heat in the heat absorber, and the other refrigerant is depressurized by the outdoor expansion valve and flows into the outdoor heat exchanger, so that the refrigerant absorbs heat (for example, refer to patent document 1).
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open publication No. 2014-94673
Disclosure of Invention
Technical problem to be solved by the invention
In the dehumidification and heating mode described above, when the temperature of the heat absorber significantly decreases, the rotation speed of the compressor is reduced to prevent the heat absorber from freezing. However, when the rotation speed of the compressor decreases, the high-pressure decreases, and therefore, the heat dissipation in the radiator decreases, and the target blowout temperature cannot be achieved.
On the other hand, if the rotation speed of the compressor is maintained to achieve the target blowing temperature, the heat absorber freezes, and the amount of air blown into the vehicle interior decreases.
The present invention has been made to solve the problems of the prior art, and an object of the present invention is to provide an air conditioner for a vehicle capable of achieving a target blowout temperature while preventing freezing of a heat absorber in a dehumidification and heating mode.
Technical proposal adopted for solving the technical problems
The air conditioner for a vehicle according to the present invention includes: a compressor that compresses a refrigerant; a radiator for radiating heat from a refrigerant to heat air supplied into a vehicle interior; a heat absorber for absorbing heat from the refrigerant to cool air supplied into the vehicle interior; an outdoor heat exchanger provided outside the vehicle; an outdoor expansion valve for decompressing the refrigerant flowing into the outdoor heat exchanger; an indoor expansion valve for decompressing the refrigerant flowing into the heat absorber; and a control device for performing at least a dehumidification and heating mode in which the refrigerant discharged from the compressor is radiated in the radiator, the radiated refrigerant is split, one refrigerant is depressurized by the indoor expansion valve, the one refrigerant is then absorbed in the heat absorber, the other refrigerant is depressurized by the outdoor expansion valve, and the other refrigerant is then absorbed in the outdoor heat exchanger, wherein the control device sets the indoor expansion valve to be fully closed when the temperature of the heat absorber is lower than a predetermined value.
The air conditioner for a vehicle according to claim 2 is the above invention, wherein the control device controls the rotation speed of the compressor based on an index capable of grasping the temperature of air blown into the vehicle interior.
In the air conditioner for a vehicle according to claim 3, the control device enlarges the valve opening of the outdoor expansion valve as the temperature of the heat absorber decreases, and if the outdoor expansion valve is set to the maximum opening and the temperature of the heat absorber is lower than a predetermined value, the control device fully closes the indoor expansion valve.
In the air conditioner for a vehicle according to claim 4, the control device reduces the valve opening of the indoor expansion valve when the outdoor expansion valve is set to the maximum opening, and sets the indoor expansion valve to be fully closed when the temperature of the heat absorber is lower than a predetermined value.
The air conditioner for a vehicle according to claim 5 is the above-described respective inventions, wherein the control device opens the indoor expansion valve at a predetermined valve opening degree when the temperature of the heat absorber exceeds a predetermined value or exceeds a predetermined value higher than the predetermined value after the indoor expansion valve is fully closed.
The air conditioner for a vehicle according to claim 6 is the above-described respective inventions, and is characterized in that the control device executes a dehumidification cooling mode in which the refrigerant discharged from the compressor is cooled by the expansion valve and the outdoor heat exchanger, and the cooled refrigerant is depressurized by the indoor expansion valve, and then the refrigerant absorbs heat in the heat absorber, and the maximum value of the control of the valve opening degree of the indoor expansion valve in the dehumidification cooling mode is set to be smaller than the maximum value of the control of the valve opening degree of the indoor expansion valve in the dehumidification cooling mode.
Effects of the invention
According to the present invention, an air conditioning apparatus for a vehicle includes: a compressor that compresses a refrigerant; a radiator for radiating heat from a refrigerant to heat air supplied into a vehicle interior; a heat absorber for absorbing heat from the refrigerant to cool air supplied into the vehicle interior; an outdoor heat exchanger provided outside the vehicle; an outdoor expansion valve for decompressing the refrigerant flowing into the outdoor heat exchanger; an indoor expansion valve for decompressing the refrigerant flowing into the heat absorber; and a control device for performing at least a dehumidification and heating mode in which the refrigerant discharged from the compressor is radiated in the radiator, the radiated refrigerant is split, one refrigerant is depressurized by the indoor expansion valve, then the one refrigerant is depressurized by the outdoor expansion valve, the other refrigerant is depressurized by the outdoor expansion valve, and then the other refrigerant is depressurized by the outdoor heat exchanger, wherein the control device sets the indoor expansion valve to be fully closed when the temperature of the heat absorber is lower than a predetermined value, and therefore, the refrigerant can be stopped from flowing to the heat absorber without decreasing the rotation speed of the compressor, and the heat absorber is prevented from being frozen.
In this way, the problem of a decrease in the air volume blown into the vehicle interior is also eliminated, and in particular, as in the invention according to claim 2, when the rotation speed of the compressor is controlled based on an index capable of grasping the temperature of the air blown into the vehicle interior, the target blowing temperature can be smoothly achieved.
In this case, as in the invention of claim 3, if the control device expands the valve opening of the outdoor expansion valve as the temperature of the heat absorber decreases, and if the outdoor expansion valve is set to the maximum opening and the temperature of the heat absorber is lower than the predetermined value, and the indoor expansion valve is set to be fully closed, the control device can cope with the decrease in the temperature of the heat absorber by the outdoor expansion valve while the flow rate of the refrigerant flowing to the heat absorber is being controlled by the control device of the outdoor expansion valve, and can stop the flow of the refrigerant into the heat absorber by the indoor expansion valve when the flow rate of the refrigerant flowing to the heat absorber is reduced by the outdoor expansion valve to the limit.
In particular, as in the invention of claim 4, if the control device reduces the valve opening of the indoor expansion valve when the outdoor expansion valve is set to the maximum opening, and sets the indoor expansion valve to be fully closed when the temperature of the heat absorber is lower than the predetermined value, it is not necessary to set the indoor expansion valve to be fully closed if the temperature of the heat absorber is not lower than the predetermined value by reducing the valve opening of the indoor expansion valve. Therefore, the dehumidification capability of the vehicle interior can be maintained while the heat absorber is prevented from freezing.
Further, as in the invention of claim 5, if the control device opens the indoor expansion valve at a predetermined valve opening when the temperature of the heat absorber exceeds a predetermined value or exceeds a predetermined value higher than the predetermined value after the indoor expansion valve is fully closed, the temperature of the heat absorber increases after the indoor expansion valve is fully closed, whereby it is possible to restart the supply of the refrigerant to the heat absorber without any obstruction and to start dehumidification of the vehicle interior.
Here, as in the invention of claim 6, when the control device sets the maximum value of the control of the valve opening of the indoor expansion valve in the dehumidification and heating mode to be smaller than the maximum value of the control of the valve opening of the indoor expansion valve in the dehumidification and heating mode, the temperature drop of the heat absorber can be suppressed, and in the dehumidification and cooling mode in which the two-stage decompression action by the outdoor expansion valve and the indoor expansion valve is generated, the outdoor expansion valve is controlled to be slightly opened, as compared with the case of the dehumidification and heating mode, the dehumidification and cooling in the vehicle interior can be achieved without any trouble, in which the refrigerant discharged from the compressor is allowed to dissipate heat in the expansion valve and the outdoor heat exchanger, and the refrigerant after the dissipation is decompressed in the indoor expansion valve, and thereafter the refrigerant is allowed to absorb heat in the heat absorber.
Drawings
Fig. 1 is a block diagram of an air conditioner for a vehicle to which an embodiment of the present invention is applied.
Fig. 2 is a block diagram of a circuit of a control device of the vehicle air conditioner of fig. 1.
Fig. 3 is a block diagram of an air conditioner for a vehicle illustrating a heating mode implemented by a heat pump controller of the control device of fig. 2.
Fig. 4 is a block diagram of an air conditioner for a vehicle, illustrating a dehumidification and heating mode performed by a heat pump controller of the control device of fig. 2.
Fig. 5 is a block diagram of an air conditioner for a vehicle, illustrating a dehumidification cooling mode and a cooling mode performed by a heat pump controller of the control device of fig. 2.
Fig. 6 is a block diagram of an air conditioner for a vehicle, which is described as an air conditioner (priority) +battery cooling mode and battery cooling (priority) +air conditioning mode implemented by the heat pump controller of the control device of fig. 2.
Fig. 7 is a block diagram of an air conditioner for a vehicle illustrating a battery cooling (individual) mode implemented by a heat pump controller of the control device of fig. 2.
Fig. 8 is a control block diagram related to the compressor control of the heat pump controller of the control device of fig. 2.
Fig. 9 is a block diagram illustrating control of the outdoor expansion valve in the dehumidification and heating mode performed by the heat pump controller of the control device of fig. 2.
Fig. 10 is a block diagram illustrating control of the indoor expansion valve in the dehumidification and heating mode performed by the heat pump controller of the control device of fig. 2.
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. Fig. 1 is a block diagram showing an air conditioner 1 for a vehicle according to an embodiment of the present invention. A vehicle to which an embodiment of the present invention is applied is an Electric Vehicle (EV) that is not equipped with an engine (internal combustion engine) and that is driven to travel by supplying electric power charged to a battery 55 that is equipped in the vehicle to a travel motor (electric motor, not shown), and a compressor 2, which will be described later, of the vehicle air conditioner 1 of the present invention is also driven by electric power supplied from the battery 55.
That is, in the air conditioner 1 for a vehicle according to the embodiment, in the electric vehicle which cannot heat by using the engine exhaust heat, the respective operation modes of the heating mode, the dehumidification cooling mode, the air conditioner (priority) +the battery cooling mode, the battery cooling (priority) +the air conditioner mode, and the battery cooling (individual) mode are switched and executed by the heat pump operation using the refrigerant circuit R, so that the air conditioning in the vehicle interior and the temperature adjustment of the battery 55 are performed.
The present invention is also effective in so-called hybrid vehicles in which an engine and a running motor are shared, as vehicles not limited to electric vehicles. Further, the vehicle to which the vehicular air conditioning device 1 of the embodiment is applied can charge the battery 55 from an external charger (a quick charger, a normal charger, or the like). The battery 55, the running motor, the inverter for controlling the running motor, and the like are objects to be temperature-controlled, which are mounted on the vehicle, but in the following embodiments, the battery 55 will be described as an example.
In the air conditioner 1 for a vehicle according to the embodiment, in which air conditioning (heating, cooling, dehumidifying, and ventilation) is performed in a vehicle interior of an electric vehicle, the air conditioner 1 is configured such that an electric compressor 2, a radiator 4, an outdoor expansion valve 6, an outdoor heat exchanger 7, an indoor expansion valve 8, a heat absorber 9, a receiver tank 12, and the like are sequentially connected by a refrigerant pipe 13 to form a refrigerant circuit R, the compressor 2 compresses a refrigerant, the radiator 4 is provided in an air flow path 3 of an HVAC unit 10 for circulating air in the vehicle interior, a high-temperature high-pressure refrigerant discharged from the compressor 2 is caused to flow in through a refrigerant pipe 13G, and is caused to dissipate heat in the vehicle interior (release heat of the refrigerant), the outdoor expansion valve 6 is configured such that the refrigerant is depressurized and expanded by an electric valve (electronic expansion valve) at the time of heating, the outdoor heat exchanger 7 performs heat exchange between the refrigerant and an external gas to function as a radiator for the refrigerant at the time of cooling, the radiator 4 is provided as an evaporator for causing the refrigerant to absorb heat at the time of heating, the evaporator 8 is configured such that the refrigerant is caused to function as an evaporator for causing the refrigerant to absorb heat to flow in the air at the time of heating, and the evaporator (heat absorber is caused to flow in the interior of the refrigerant) is configured such that the refrigerant is configured such that it is decompressed and is caused to flow in the air to expand and the evaporator (heat absorber) and is caused to flow from the indoor expansion valve (9) at the time of the refrigerant is configured as the evaporator and the refrigerant to absorb heat at the temperature) at the time of the heat is caused to expand and the refrigerant is configured as an electronic expansion valve.
The outdoor expansion valve 6 also decompresses and expands the refrigerant flowing out of the radiator 4 and into the outdoor heat exchanger 7, and can be set to be fully closed. The indoor expansion valve 8 may also be configured to depressurize and expand the refrigerant flowing into the heat absorber 9, and may be fully closed.
The outdoor heat exchanger 7 is provided with an outdoor fan 15. The outdoor fan 15 is configured to exchange heat between the outdoor air and the refrigerant by forcibly ventilating the outdoor air to the outdoor heat exchanger 7, so that the outdoor air is ventilated to the outdoor heat exchanger 7 even when the vehicle is stopped (i.e., the vehicle speed is 0 km/h).
The refrigerant pipe 13A on the refrigerant outlet side of the outdoor heat exchanger 7 is connected to a refrigerant pipe 13B to which an electromagnetic valve 17 (for cooling) as an on-off valve that opens when the refrigerant flows to the heat absorber 9 is connected, and the refrigerant pipe 13B is connected to the refrigerant inlet side of the heat absorber 9 via a check valve 18 and the indoor expansion valve 8 in this order. The check valve 18 is directed in the forward direction toward the indoor expansion valve 8.
The refrigerant pipe 13A extending from the outdoor heat exchanger 7 branches into a refrigerant pipe 13D, and the branched refrigerant pipe 13D is connected to the refrigerant pipe 13C on the refrigerant outlet side of the heat absorber 9 through a solenoid valve 21 (for heating) as an on-off valve that is opened during heating. Then, the refrigerant pipe 13C is connected to the inlet side of the accumulator 12 via the check valve 35, and the outlet side of the accumulator 12 is connected to the refrigerant pipe 13K on the refrigerant suction side of the compressor 2. The check valve 35 sets the direction of the accumulator 12 to be the forward direction, and the refrigerant pipe 13D is connected to the refrigerant pipe 13C on the upstream side of the refrigerant by the check valve 35.
The filter 19 is connected to the refrigerant pipe 13E on the refrigerant outlet side of the radiator 4, and the refrigerant pipe 13E branches into a refrigerant pipe 13J and a refrigerant pipe 13F in the vicinity of the outdoor expansion valve 6 (on the refrigerant upstream side), and one of the branched refrigerant pipes 13J is connected to the refrigerant inlet side of the outdoor heat exchanger 7 via the outdoor expansion valve 6. The other refrigerant pipe 13F branched is connected to the refrigerant pipe 13B located on the downstream side of the check valve 18 and on the upstream side of the indoor expansion valve 8 via a solenoid valve 22 (for dehumidification) as an on-off valve that is opened at the time of dehumidification.
Thereby, the refrigerant pipe 13F is connected in parallel to the series circuit of the outdoor expansion valve 6, the outdoor heat exchanger 7, and the check valve 18, and forms a bypass circuit that bypasses the outdoor expansion valve 6, the outdoor heat exchanger 7, and the check valve 18.
Further, each of an outside air intake port and an inside air intake port (represented by an intake port 25 in fig. 1) is formed in the air flow path 3 on the air upstream side of the heat absorber 9, and an intake switching damper 26 is provided in the intake port 25, and the intake switching damper 26 switches the air introduced into the air flow path 3 to the inside air (inside air circulation) as the air in the vehicle interior and the outside air (outside air introduction) as the air outside the vehicle interior. An indoor blower (blower fan) 27 is provided on the air downstream side of the suction switching damper 26, and the indoor blower 27 is configured to send the introduced internal air or external air to the air flow path 3.
In the embodiment, an auxiliary heater 23, which is an auxiliary heating device constituted by a PTC heater (electric heater), is provided in the air flow path 3 on the leeward side (air downstream side) of the radiator 4, and can heat the air supplied into the vehicle interior via the radiator 4. An air mixing damper 28 is provided in the air flow path 3 on the air upstream side of the radiator 4, and the air mixing damper 28 adjusts the ratio of air (internal gas or external gas) flowing into the air flow path 3 and passing through the heat absorber 9 in the air flow path 3 to be ventilated to the radiator 4 and the auxiliary heater 23.
Further, a foot-blowing, a ventilation, and a front windshield defogging (represented by a blow-out port 29 in fig. 1) are formed in the air flow path 3 on the air downstream side of the radiator 4, and a blow-out port switching damper 31 is provided in the blow-out port 29, and the blow-out port switching damper 31 performs switching control of blowing out of the air from the respective blow-out ports.
The air conditioner 1 for a vehicle further includes a device temperature adjusting device 61, and the device temperature adjusting device 61 is configured to circulate a heat medium through the battery 55 (subject to temperature adjustment) to adjust the temperature of the battery 55. The apparatus temperature adjustment device 61 of the embodiment includes: a circulation pump 62 as a circulation means, the circulation pump 62 being for circulating the heat medium to the battery 55; a refrigerant-heat medium heat exchanger 64 as a heat exchanger for an object to be temperature-controlled; and a heat medium heater 63 as a heating device, which is connected to the battery 55 in a ring shape by a heat medium pipe 66.
In the example, an inlet of the heat medium heater 63 is connected to the discharge side of the circulation pump 62, and an inlet of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 is connected to an outlet of the heat medium heater 63. An outlet of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 is connected to an inlet of the battery 55, and an outlet of the battery 55 is connected to a suction side of the circulation pump 62.
As the heat medium used in the plant temperature control device 61, for example, water, a refrigerant such as HFO-1234yf, a liquid such as a coolant, and a gas such as air can be used. In addition, in the examples, water was used as the heat medium. The heat medium heater 63 is an electric heater such as a PTC heater. A jacket structure in which a heat medium flows around the battery 55 in a heat exchange relationship with the battery 55 is provided.
Then, when the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 flows to the heat medium heater 63, is heated in this state when the heat medium heater 63 generates heat, and then flows into the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64. The heat medium flowing out of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 flows to the battery 55, where the heat medium exchanges heat with the battery 55. Next, the heat medium having exchanged heat with the battery 55 is sucked into the circulation pump 62 to circulate through the heat medium pipe 66.
On the other hand, one end of a branching pipe 72 serving as a branching circuit is connected to the refrigerant downstream side of the solenoid valve 22 of the refrigerant pipe 13F of the refrigerant circuit R. In the embodiment, the branch pipe 67 is provided with an auxiliary expansion valve 68 constituted by an electric valve (electronic expansion valve). The auxiliary expansion valve 68 may be configured to be fully closed while decompressing and expanding the refrigerant flowing into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, which will be described later.
The other end of the branching pipe 67 is connected to the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, one end of the refrigerant pipe 71 is connected to the outlet of the refrigerant flow path 64B, and the other end of the refrigerant pipe 71 is connected to the refrigerant pipe 13C located on the downstream side of the check valve 35 from the refrigerant upstream side of the accumulator 12. The auxiliary expansion valve 68, the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and the like also constitute a part of the refrigerant circuit R, and also constitute a part of the equipment temperature adjusting device 61.
When the auxiliary expansion valve 68 is opened, the refrigerant (a part or all of the refrigerant) flowing out of the outdoor heat exchanger 7 flows into the branch pipe 67, is depressurized in the auxiliary expansion valve 68, flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and evaporates in the refrigerant flow path 64B. The refrigerant absorbs heat from the heat medium flowing through the heat medium flow path 64A while flowing through the refrigerant flow path 64B, and is then sucked into the compressor 2 from the refrigerant pipe 13K through the refrigerant pipe 71, the refrigerant pipe 13C, and the accumulator 12.
Next, fig. 2 shows a block diagram of the control device 11 of the vehicular air conditioning device 1 of the embodiment. The control device 11 is constituted by an air-conditioning controller 45 and a heat pump controller 32, each of the air-conditioning controller 45 and the heat pump controller 32 is constituted by a microcomputer as an example of a computer including a processor, and the air-conditioning controller 45 and the heat pump controller 32 are connected to a vehicle communication bus 65 constituting CAN (Controller Area Network: controller area network) and LIN (Local Interconnect Network: local internet). The compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heater 63 are also connected to the vehicle communication bus 65, and the air conditioner controller 45, the heat pump controller 32, the compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heater 63 are configured to receive and transmit data via the vehicle communication bus 65.
A vehicle controller 72 (ECU), a Battery controller (BMS: battery MANAGEMENT SYSTEM: battery management system) 73, and a GPS navigation device 74 are connected to the vehicle communication bus 65, the vehicle controller 72 controlling the entire vehicle including running, and the Battery controller 73 controlling charge and discharge of the Battery 55. The vehicle controller 72, the battery controller 73, and the GPS navigation device 74 are also constituted by a microcomputer including an example of a computer as a processor, and the air conditioner controller 45 and the heat pump controller 32 constituting the control device 11 are configured to receive and transmit information (data) with the vehicle controller 72, the battery controller 73, and the GPS navigation device 74 via the vehicle communication bus 65.
The air conditioning controller 45 is a higher-level controller responsible for controlling the air conditioning in the vehicle cabin, and the input of the air conditioning controller 45 is connected to an outside air temperature sensor 33, an outside air humidity sensor 34, a HAVC intake temperature sensor 36, an inside air temperature sensor 37, an inside air humidity sensor 38, an indoor CO 2 concentration sensor 39, a blowout temperature sensor 41, for example, a photo-electric sensor sun shine sensor 51, a vehicle speed sensor 52, and an air conditioning operation unit 53, wherein the outside air temperature sensor 33 detects the outside air temperature Tam of the vehicle, the outside air humidity sensor 34 detects the outside air humidity, the HVAC intake temperature sensor 36 detects the temperature of the air that is taken in from the intake port 25 to the air circulation path 3 and flows into the heat absorber 9, the inside air temperature sensor 37 detects the air temperature (inside air temperature Tin) in the vehicle cabin, the inside air humidity sensor 38 detects the humidity of the air in the vehicle cabin, the indoor CO 2 detects the carbon dioxide concentration in the vehicle interior, and the air temperature sensor detects the air temperature in the vehicle interior air conditioning operation unit 53, and the air temperature sensor is set for the air conditioning operation mode of the vehicle cabin is switched between the air temperature sensor 53 and the air conditioning operation mode. In the figure, a symbol 53A is a display screen as a display output device provided in the air conditioner operation unit 53.
The outdoor blower 15, the indoor blower (blower fan) 27, the suction switching damper 26, the air mixing damper 28, and the outlet switching damper 31 are connected to the output of the air conditioner controller 45, and the air conditioner controller 45 controls the above components.
The heat pump controller 32 is a controller mainly responsible for the control of the refrigerant circuit R, and is connected to the input of the heat pump controller 32 to detect the refrigerant inlet temperature Tcxin of the radiator 4 (the discharge refrigerant temperature of the compressor 2), the radiator outlet temperature sensor 44 to detect the refrigerant outlet temperature Tci of the radiator 4, the suction temperature sensor 46 to detect the suction refrigerant temperature Ts of the compressor 2, the radiator pressure sensor 47 to detect the refrigerant pressure on the refrigerant outlet side of the radiator 4 (the pressure of the radiator 4: the radiator pressure Pci), the auxiliary heater temperature sensor 50B (the passenger seat side), the heat absorber temperature sensor 43 to detect the refrigerant inlet temperature Tcxin of the radiator 4 (the discharge refrigerant temperature of the compressor 2), the heat absorber temperature sensor 48 to detect the refrigerant outlet temperature of the heat exchanger 9 (the heat exchanger 9: the pressure of the radiator 7) to detect the heat absorber pressure Ts, and the auxiliary heater pressure of the auxiliary heater 50B (the heat exchanger 9: the heat exchanger pressure of the heat exchanger 9) to detect the refrigerant outlet temperature of the heat exchanger 7) to detect the heat absorber temperature tsu of the refrigerant of the compressor 2, and the auxiliary heater pressure of the heat absorber pressure sensor 47 to detect the refrigerant outlet temperature of the heat exchanger 9 (the heat exchanger pressure of the heat exchanger 9).
The outdoor expansion valve 6, the solenoid valve 22 (for dehumidification), the solenoid valve 17 (for cooling), the solenoid valve 21 (for heating), the indoor expansion valve 8, and the auxiliary expansion valve 68 are connected to the output of the heat pump controller 32, and the above-described components are controlled by the heat pump controller 32. In addition, the compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heater 63 have controllers built therein, and in the embodiment, the controllers of the compressor 2, the auxiliary heater 23, the circulation pump 62, and the heat medium heater 63 receive and transmit data from and to the heat pump controller 32 via the vehicle communication bus 65, and are controlled by the heat pump controller 32.
The circulation pump 62 and the heat medium heater 63 constituting the device temperature control apparatus 61 may be controlled by the battery controller 73. The battery controller 73 is connected to outputs of a heat medium temperature sensor 76 and a battery temperature sensor 77, the heat medium temperature sensor 76 detects a temperature of the heat medium (heat medium temperature Tw) on the inlet side of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 of the device temperature adjustment apparatus 61, and the battery temperature sensor 77 detects a temperature of the battery 55 (a temperature of the battery 55 itself: a battery temperature Tcell). In the embodiment, information on the remaining amount of the battery 55 (the amount of stored electricity), charging of the battery 55 (information on charging, charging end time, remaining charging time, etc.), heat medium temperature Tw, battery temperature Tcell, the amount of heat generation of the battery 55 (calculated by the battery controller 73 from the amount of electricity, etc.), and the like are transmitted from the battery controller 73 to the air conditioner controller 45, the vehicle controller 72 via the vehicle communication bus 65. The information about the charge end time and the remaining charge time at the time of charging the battery 55 is information supplied from an external charger such as a quick charger. The output Mpower of the travel motor is transmitted from the vehicle controller 72 to the heat pump controller 32 and the air conditioner controller 45.
In this example, the heat pump controller 32 and the air conditioner controller 45 are configured to receive and transmit data from and to each other via the vehicle communication bus 65, and to control each device based on the output of each sensor and the setting input by the air conditioner operation unit 53, and in this case, the heat pump controller 32 is configured such that the outside air temperature sensor 33, the outside air humidity sensor 34, the HVAC intake temperature sensor 36, the inside air temperature sensor 37, the inside air humidity sensor 38, the indoor CO 2 concentration sensor 39, the blowout temperature sensor 41, the solar radiation sensor 51, the vehicle speed sensor 52, the air volume Ga (calculated by the air conditioner controller 45) of the air flowing into the air circulation path 3 and flowing through the air circulation path 3, the voltage (BLV) of the indoor blower 27, the information from the battery controller 73, the information from the GPS navigation device 74, and the output of the air conditioner operation unit 53 are transmitted from the air conditioner controller 45 to the heat pump controller 32 via the vehicle communication bus 65, so that the control by the heat pump controller 32 is performed.
Further, data (information) related to the control of the refrigerant circuit R is also transmitted from the heat pump controller 32 to the air conditioner controller 45 via the vehicle communication bus 65. The air volume ratio SW achieved by the air mixing damper 28 is calculated by the air conditioner controller 45 in the range of 0.ltoreq.sw.ltoreq.1. Further, at sw=1, the air flowing through the heat absorber 9 is entirely ventilated to the radiator 4 and the auxiliary heater 23 by the air mix damper 28.
With the above configuration, the operation of the vehicle air conditioner 1 according to the embodiment will be described. In the present embodiment, the control device 11 (air-conditioning controller 45, heat pump controller 32) switches between the air-conditioning operation, the battery cooling operation, the air-conditioning mode, and the battery cooling operation in the battery cooling (individual) mode, which are performed in the heating mode, the dehumidification cooling mode, the cooling mode, and the air-conditioning (priority) +battery cooling mode.
In the embodiment, the battery 55 is not charged, and each air conditioning operation of the heating mode, the dehumidification cooling mode, the cooling mode, and the air conditioning (priority) +battery cooling mode can be executed when the Ignition (IGN) of the vehicle is turned on and the air conditioning switch of the air conditioning operation unit 53 is turned on. However, in the case of remote operation (pre-air conditioning, etc.), the ignition device can be turned off. In addition, there is no battery cooling requirement even while the battery 55 is in charge, and the air conditioning switch can be implemented when it is on.
On the other hand, each of the battery cooling (priority) +air conditioning mode and battery cooling (individual) mode can be executed when, for example, a plug of a quick charger (external power supply) is connected and the battery 55 is charged. However, the battery cooling (individual) mode can be performed when the air conditioner switch is turned off and there is a battery cooling request (traveling at a high outside air temperature or the like) in addition to during charging of the battery 55.
In the embodiment, when the ignition is turned on or when the battery 55 is still being charged even though the ignition is turned off, the heat pump controller 32 operates the circulation pump 62 of the device temperature adjusting device 61 and circulates the heat medium through the heat medium pipe 66 as indicated by the broken line in fig. 3 to 7. In addition, the heat pump controller 32 of the embodiment also executes a battery heating mode in which the battery 55 is heated by causing the heat medium heater 63 of the device temperature adjustment apparatus 61 to generate heat.
(1) Heating mode
First, a heating mode will be described with reference to fig. 3. In the following description, the heat pump controller 32 is used as a control main body, and control of each device is performed by cooperation of the heat pump controller 32 and the air conditioner controller 45. Fig. 3 shows a flow pattern (solid arrows) of the refrigerant in the refrigerant circuit R in the heating mode. When the heating mode is selected by the heat pump controller 32 (automatic mode) or a manual air conditioning setting operation (manual mode) with respect to the air conditioning operation unit 53 of the air conditioning controller 45, the heat pump controller 32 opens the solenoid valve 21 and closes the solenoid valves 17 and 22. The outdoor expansion valve 6 is opened, the indoor expansion valve 8 and the auxiliary expansion valve 68 are fully closed, the compressor 2 and the blowers 15 and 27 are operated, and the air mixing damper 28 is set in a state in which the ratio of air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23 is adjusted.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the radiator 4 is ventilated with the air in the air flow path 3, the air in the air flow path 3 is heated by exchanging heat with the high-temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by taking heat from the air, and condensed and liquefied.
The refrigerant liquefied in the radiator 4 flows out of the radiator 4 and then flows through the refrigerant pipes 13E and 13J to the outdoor expansion valve 6. The refrigerant flowing into the outdoor expansion valve 6 is depressurized in the outdoor expansion valve 6 and then flows into the outdoor heat exchanger 7. The refrigerant flowing into the outdoor heat exchanger 7 evaporates and draws heat (absorbs heat) from the outside air traveling or ventilated by the outdoor blower 15. That is, the refrigerant circuit R functions as a heat pump. Then, the low-temperature refrigerant flowing out of the outdoor heat exchanger 7 flows through the refrigerant pipe 13A, the refrigerant pipe 13D, and the solenoid valve 21 to the refrigerant pipe 13C, and enters the accumulator 12 through the refrigerant pipe 13C, and after being gas-liquid separated in the accumulator 12, the gas refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K, and the cycle described above is repeated. Since the air heated by the radiator 4 is blown out from the air outlet 29, heating in the vehicle cabin is performed.
The heat pump controller 32 calculates a target radiator pressure PCO from a target heater temperature TCO (a target value of a radiator temperature Thp described later) calculated from a target blow-out temperature TAO, which is a target temperature of air blown out into the vehicle interior (a target value of a temperature of air blown out into the vehicle interior), controls the rotation speed of the compressor 2 based on the target radiator pressure PCO and a radiator pressure Pci (a high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47, and controls the valve opening of the outdoor expansion valve 6 based on a refrigerant outlet temperature Tci of the radiator 4 detected by the radiator outlet temperature sensor 44 and a radiator pressure Pci detected by the radiator pressure sensor 47, thereby controlling the degree of supercooling of the refrigerant at the outlet of the radiator 4.
The radiator pressure Pci is an index that can be grasped as to the temperature of the air blown into the vehicle interior in the present invention, but the blowing temperature blown into the vehicle interior detected by the blowing temperature sensor 41 may be employed as the index.
Further, in the case where the heating capacity (heating capacity) achieved by the radiator 4 is insufficient with respect to the required heating capacity, the heat pump controller 32 compensates for the insufficient amount by the heat generation of the auxiliary heater 23. Thus, even when the outside air temperature is low, the interior of the vehicle can be heated without any trouble.
(2) Dehumidification heating mode
Next, a dehumidification and heating mode will be described with reference to fig. 4. Fig. 4 shows a flow pattern (solid arrows) of the refrigerant in the refrigerant circuit R in the dehumidification and heating mode. In the dehumidification and heating mode, the heat pump controller 32 opens the solenoid valves 21 and 22 and closes the solenoid valve 17. The outdoor expansion valve 6 and the indoor expansion valve 8 are opened, and the auxiliary expansion valve 68 is fully closed. Next, the compressor 2 and the blowers 15 and 27 are operated, and the air mixing damper 28 is set in a state in which the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23 is adjusted.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the radiator 4 is ventilated with the air in the air flow path 3, the air in the air flow path 3 is heated by exchanging heat with the high-temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by taking heat from the air, and condensed and liquefied.
After flowing out from the radiator 4, the refrigerant liquefied in the radiator 4 flows through the refrigerant pipe 13E, and then, partially flows into the refrigerant pipe 13J and flows to the outdoor expansion valve 6. The refrigerant flowing into the outdoor expansion valve 6 is depressurized in the outdoor expansion valve 6 and then flows into the outdoor heat exchanger 7. The refrigerant flowing into the outdoor heat exchanger 7 evaporates and draws heat (absorbs heat) from the outside air traveling or ventilated by the outdoor blower 15. Then, the low-temperature refrigerant flowing out of the outdoor heat exchanger 7 flows through the refrigerant pipe 13A, the refrigerant pipe 13D, and the solenoid valve 21 to the refrigerant pipe 13C, and enters the accumulator 12 through the refrigerant pipe 13C, and after being gas-liquid separated in the accumulator 12, the gas refrigerant is sucked into the compressor 2 from the refrigerant pipe 13K, and the cycle described above is repeated.
On the other hand, the remaining portion of the condensed refrigerant flowing through the radiator 4 and the refrigerant pipe 13E is split, and the split refrigerant flows into the refrigerant pipe 13F and flows into the refrigerant pipe 13B through the solenoid valve 22. Then, the refrigerant flows into the indoor expansion valve 8, is depressurized in the indoor expansion valve 8, flows into the heat absorber 9, and evaporates. At this time, moisture in the air blown from the indoor blower 27 condenses and adheres to the heat absorber 9 by the heat absorption effect of the refrigerant generated by the heat absorber 9, and therefore, the air is cooled and dehumidified.
The refrigerant evaporated in the heat absorber 9 flows out from the refrigerant pipe 13C and merges with the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), passes through the accumulator 12, is sucked into the compressor 2 from the refrigerant pipe 13K, and repeats the above cycle. The air dehumidified by the heat absorber 9 is reheated while passing through the radiator 4 and the auxiliary heater 23 (in the case of heat generation), thereby performing dehumidification and heating in the vehicle cabin.
In the embodiment, the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. In addition, the valve opening degrees of the outdoor expansion valve 6 and the indoor expansion valve 8 are controlled based on the absorber temperature Te, but the control of these outdoor expansion valve 6 and indoor expansion valve 8 in the dehumidification and heating mode will be described in detail below.
In addition, in the case where the heating capacity (heating capacity) achieved by the radiator 4 is insufficient with respect to the heating capacity required in the above-described dehumidification heating mode, the heat pump controller 32 can compensate for the above-described insufficient amount by the heat generation of the auxiliary heater 23. Thus, even when the outside air temperature is low, the interior of the vehicle can be dehumidified and heated without any trouble.
(3) Dehumidification cooling mode
Next, a dehumidification cooling mode will be described with reference to fig. 5. Fig. 5 shows a flow pattern (solid arrows) of the refrigerant in the refrigerant circuit R in the dehumidification cooling mode. In the dehumidification cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 20 and 21. The outdoor expansion valve 6 and the indoor expansion valve 8 are opened, and the auxiliary expansion valve 68 is fully closed. Next, the compressor 2 and the blowers 15 and 27 are operated, and the air mixing damper 28 is set in a state in which the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23 is adjusted.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the radiator 4 is ventilated with the air in the air flow path 3, the air in the air flow path 3 is heated by exchanging heat with the high-temperature refrigerant in the radiator 4. On the other hand, the refrigerant in the radiator 4 is cooled by taking heat from the air, and condensed and liquefied.
The refrigerant flowing out of the radiator 4 flows through the refrigerant pipes 13E and 13J to the outdoor expansion valve 6, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 controlled to be slightly opened (a region having a large valve opening degree) compared with the heating mode and the dehumidification heating mode. The refrigerant flowing into the outdoor heat exchanger 7 is cooled by air in the outdoor heat exchanger 7 by traveling or by using outside air ventilated by the outdoor blower 15, and is condensed. The refrigerant flowing out of the outdoor heat exchanger 7 flows into the refrigerant pipe 13B through the refrigerant pipe 13A, and flows to the indoor expansion valve 8 through the solenoid valve 17 and the check valve 18 in this order. The refrigerant is depressurized in the indoor expansion valve 8, and then flows into the heat absorber 9 to evaporate. At this time, moisture in the air blown from the indoor blower 27 condenses and adheres to the heat absorber 9 by the heat absorption action, and therefore, the air is cooled and dehumidified.
The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C to the accumulator 12, is sucked from the refrigerant pipe 13K to the compressor 2 through the accumulator 12, and repeats the above cycle. The dehumidified air cooled by the heat absorber 9 is reheated (the heating capacity is lower than that in dehumidification heating) while passing through the radiator 4 and the auxiliary heater 23 (in the case of heat generation), and thereby dehumidification cooling in the vehicle cabin is performed.
The heat pump controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO, which is the target temperature of the heat absorber 9 (target value of the heat absorber temperature Te), so that the heat absorber temperature Te becomes the target heat absorber temperature TEO, and controls the valve opening of the outdoor expansion valve 6 so that the radiator pressure Pci becomes the target radiator pressure PCO based on the radiator pressure Pci (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 and the target radiator pressure PCO (target value of the radiator pressure Pci), thereby obtaining the required reheating amount (reheating amount) achieved by the radiator 4.
In addition, in the dehumidification cooling mode described above, when the heating capacity (reheating capacity) achieved by the radiator 4 is insufficient with respect to the required heating capacity, the heat pump controller 32 compensates for the insufficient amount by the heat generation of the auxiliary heater 23. This makes it possible to perform dehumidification cooling while preventing an excessive drop in the temperature in the vehicle interior.
(4) Refrigeration mode
Next, a cooling mode will be described. The flow of the refrigerant in this cooling mode is the same as in fig. 5. That is, even in the cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22. The outdoor expansion valve 6 is fully closed, the indoor expansion valve 8 is opened, and the auxiliary expansion valve is fully closed. Next, the compressor 2 and the blowers 15 and 27 are operated, and the air mixing damper 28 is set in a state in which the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23 is adjusted. In addition, the auxiliary heater 23 is not energized.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Although the air in the air flow path 3 is ventilated to the radiator 4, since the above ratio is small (only for reheating (reheating) in the cooling process), almost only the air passes through the radiator 4, and the refrigerant flowing out of the radiator 4 flows through the refrigerant pipe 13E to the refrigerant pipe 13J. The refrigerant passes through the outdoor expansion valve 6, which is fully opened, flows through and into the outdoor heat exchanger 7, and is then condensed and liquefied by air-cooling by the outside air that is traveling or ventilated by the outdoor blower 15.
The refrigerant flowing out of the outdoor heat exchanger 7 flows into the refrigerant pipe 13B through the refrigerant pipe 13A, and flows to the indoor expansion valve 8 through the solenoid valve 17 and the check valve 18 in this order. The refrigerant is depressurized in the indoor expansion valve 8, and then flows into the heat absorber 9 to evaporate. Under the heat absorption action at this time, the air blown from the indoor blower 27 and heat-exchanged with the heat absorber 9 is cooled.
The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C to the accumulator 12, is sucked from the accumulator 12 through the refrigerant pipe 13K to the compressor 2, and repeats the above cycle. The air cooled by the heat absorber 9 is blown out into the vehicle interior from the air outlet 29, thereby cooling the vehicle interior. In the cooling mode, the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the temperature of the heat absorber 9 (absorber temperature Te) detected by the absorber temperature sensor 48.
(5) Air conditioner (priority) +battery cooling mode
Next, an air conditioner (priority) +battery cooling mode will be described with reference to fig. 6. Fig. 6 shows the flow pattern (solid arrows) of the refrigerant in the refrigerant circuit R in the air-conditioning (priority) +battery cooling mode. In the air conditioning (priority) +battery cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22. The outdoor expansion valve is fully opened, and the indoor expansion valve 8 and the auxiliary expansion valve 68 are opened.
Next, the compressor 2 and the blowers 15 and 27 are operated, and the air mixing damper 28 is set in a state in which the ratio of the air blown from the indoor blower 27 to the radiator 4 and the auxiliary heater 23 is adjusted. In the operation mode, the auxiliary heater 23 is not energized. The heat medium heater 63 is not energized either.
Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Although the air in the air flow path 3 is ventilated to the radiator 4, since the above ratio is small (only for reheating (reheating) in the cooling process), almost only the air passes through the radiator 4, and the refrigerant flowing out of the radiator 4 flows through the refrigerant pipe 13E to the refrigerant pipe 13J. At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant flows into the outdoor heat exchanger 7 in this way, and is condensed and liquefied by air-cooling by the outside air that is traveling or ventilated by the outdoor blower 15.
The refrigerant flowing out of the outdoor heat exchanger 7 flows into the refrigerant pipe 13B through the refrigerant pipe 13A, and is split after passing through the solenoid valve 17 and the check valve 18, and flows directly through the refrigerant pipe 13B to reach the indoor expansion valve 8. The refrigerant flowing into the indoor expansion valve 8 is depressurized in the outdoor expansion valve 6, and then flows into the heat absorber 9 to evaporate. Under the heat absorption action at this time, the air blown from the indoor blower 27 and heat-exchanged with the heat absorber 9 is cooled.
The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C to the accumulator 12, is sucked from the accumulator 12 through the refrigerant pipe 13K to the compressor 2, and repeats the above cycle. The air cooled by the heat absorber 9 is blown out into the vehicle interior from the air outlet 29, thereby cooling the vehicle interior.
On the other hand, the remaining portion of the refrigerant passing through the check valve 18 is branched and flows into the branch pipe 67 and flows to the auxiliary expansion valve 68. Here, after the refrigerant is depressurized, the refrigerant flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and evaporates in the refrigerant flow path 64B. At this time, an endothermic effect is exerted. The refrigerant evaporated in the refrigerant flow path 64B passes through the refrigerant pipe 71, the refrigerant pipe 13C, and the accumulator 12 in this order, is sucked into the compressor 2 from the refrigerant pipe 13K, and repeatedly circulates (indicated by solid arrows in fig. 6).
On the other hand, since the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 passes through the heat medium heater 64, flows through the heat medium pipe 66 to the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64, exchanges heat with the refrigerant evaporated in the refrigerant flow path 64B in the heat medium flow path 64A, absorbs heat, and is cooled. The heat medium flowing out of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 flows into the battery 55, and exchanges heat with the battery 55. Thereby, the battery 55 is cooled, and the heat medium after cooling the battery 55 is sucked into the circulation pump 62, and the above-described circulation (indicated by a broken-line arrow in fig. 6) is repeated.
In the above air conditioning (priority) +battery cooling mode, the heat pump controller 32 maintains a state in which the indoor solenoid valve 8 is opened, and controls the rotation speed NC of the compressor 2 based on the temperature of the heat absorber 9 (absorber temperature Te) detected by the absorber temperature sensor 48. Further, in the embodiment, the auxiliary solenoid valve 68 is controlled to be opened and closed based on the temperature of the heat medium (heat medium temperature Tw: sent from the battery controller 73) detected by the heat medium temperature sensor 76. As an index indicating the temperature of the battery 55 as the temperature target in the embodiment, the heat medium temperature Tw (the same applies hereinafter) may be used.
In this case, the heat pump controller 32 sets the upper limit value tur and the lower limit value TLL with a predetermined temperature difference above and below a predetermined target heat medium temperature Tw, which is a target value of the heat medium temperature Tw, for example. The auxiliary solenoid valve 68 is opened when the heat medium temperature Tw is raised to the upper limit value tur (when the heat medium temperature Tw is greater than the upper limit value tur, or equal to or greater than the upper limit value tur) by heat generation of the battery 55 or the like from the state in which the auxiliary solenoid valve 68 is closed. As a result, the refrigerant flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 and evaporates, and cools the heat medium flowing through the heat medium flow path 64A, so that the battery 55 is cooled by the cooled heat medium.
Subsequently, when the heat medium temperature Tw falls to the lower limit TLL (lower limit TLL or lower limit TLL, the same applies), the assist solenoid valve 68 is opened. Subsequently, the auxiliary solenoid valve 68 is repeatedly opened and closed, and the heat medium temperature Tw is controlled to the target heat medium temperature Tw o while the interior of the vehicle is preferentially cooled, thereby cooling the battery 55.
(6) Switching of air conditioning operation
The heat pump controller 32 calculates the target blowout temperature TAO according to the following expression (I). The target blowout temperature TAO is a target value of the temperature of the air blown out from the blowout port 29 into the vehicle interior.
TAO＝(Tset－Tin)×K+Tbal(f(Tset、SUN、Tam))…(I)
Here, tset is the set temperature in the vehicle interior set by the air conditioner operation unit 53, tin is the temperature of the air in the vehicle interior detected by the inside air temperature sensor 37, K is a coefficient, and Tbal is a balance value calculated based on the set temperature Tset, the insolation amount SUN detected by the insolation sensor 51, and the outside air temperature Tam detected by the outside air temperature sensor 33. In general, the lower the outside air temperature Tam, the higher the target blowout temperature TAO, and the target blowout temperature TAO decreases as the outside air temperature Tam increases.
Further, the heat pump controller 32 selects any one of the above-described air conditioning operations based on the outside air temperature Tam and the target blowout temperature TAO detected by the outside air temperature sensor 33 at the time of startup. After the start-up, the respective air conditioning operations are selected and switched according to the operating conditions such as the outside air temperature Tam, the target blowing temperature TAO, the heat medium temperature Tw, the battery temperature Tcell, the environmental conditions, the change in the setting conditions, and the battery cooling request (mode switching request) from the battery controller 73.
(7) Battery cooling (priority) +air conditioning mode
Next, an operation during charging of the battery 55 will be described. For example, when the battery 55 is charged by connecting a plug for charging of a quick charger (external power supply) (the above information is transmitted from the battery controller 73), the heat pump controller 32 executes the battery cooling (priority) +air conditioning mode whenever there is a battery cooling request and the air conditioning switch of the air conditioning operation section 53 is turned on, regardless of whether the Ignition (IGN) of the vehicle is turned on or off. The flow pattern of the refrigerant in the refrigerant circuit R in the battery cooling (priority) +air conditioning mode is the same as that in the air conditioning (priority) +battery cooling mode shown in fig. 6.
However, in the case of the above-described battery cooling (priority) +air-conditioning mode, in the embodiment, the heat pump controller 32 maintains a state in which the auxiliary solenoid valve 68 is opened, and controls the rotation speed NC of the compressor 2 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 (sent from the battery controller 73). In the embodiment, the indoor solenoid valve 8 is controlled to be opened and closed based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.
In this case, for example, the heat pump controller 32 sets the upper limit value TeUL and the lower limit value TeLL with a predetermined temperature difference above and below the predetermined target absorber temperature TEO, which is the target value of the absorber temperature Te. Further, when the absorber temperature Te increases from the state where the indoor solenoid valve 8 is fully closed to the upper limit value TeUL (the same applies to the case where the absorber temperature Te is greater than the upper limit value TeUL or equal to or greater than the upper limit value TeUL), the indoor solenoid valve 8 is opened. Thereby, the refrigerant flows into the heat absorber 9 and evaporates to cool the air flowing through the air flow path 3.
Subsequently, when the absorber temperature Te falls to the lower limit TLL (lower limit TeLL or lower limit TeLL or lower, the same applies), the indoor solenoid valve 8 is fully closed. Then, the indoor solenoid valve 8 is repeatedly opened and closed, and the cooling of the battery 55 is prioritized, and the heat absorber temperature Te is controlled to the target heat absorber temperature TEO, thereby cooling the vehicle interior.
(8) Battery cooling (individual) mode
Next, the heat pump controller 32 executes the battery cooling (individual) mode when there is a battery cooling request to charge the battery 55 by connecting to the plug for charging of the quick charger in a state where the air conditioning switch of the air conditioning operation unit 53 is turned off, regardless of whether the ignition is turned on or off. However, in addition to the charging process of the battery 55, the operation is performed in a case where the air conditioning switch is turned off and there is a battery cooling request (when traveling at a high outside air temperature, etc.). Fig. 7 shows the flow pattern (solid arrows) of the refrigerant in the refrigerant circuit R in the above-described battery cooling (individual) mode. In the battery cooling (individual) mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valves 21 and 22. The auxiliary expansion valve 68 is opened, and the indoor expansion valve 8 is fully closed.
Next, the compressor 2 and the outdoor fan 15 are operated. The indoor fan 27 is not operated, and the auxiliary heater 23 is not energized. In the operation mode, the heat medium heater 63 is not energized.
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 path 3 is not ventilated to the radiator 4, only the refrigerant flowing out of the radiator 4 passes through the air flow path and reaches the refrigerant pipe 13J through the refrigerant pipe 13E. At this time, since the solenoid valve 6 is fully opened, the refrigerant directly flows into the outdoor heat exchanger 7, and then the outdoor heat exchanger 7 is cooled by the outside air ventilated by the outdoor fan 15, thereby condensing and liquefying the refrigerant.
The refrigerant flowing out of the outdoor heat exchanger 7 flows into the refrigerant pipe 13B through the refrigerant pipe 13A, and after passing through the solenoid valve 17 and the check valve 18 in this order, all flows into the branch pipe 67 and flows to the auxiliary expansion valve 68. Here, after the refrigerant is depressurized, the refrigerant flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and evaporates in the refrigerant flow path 64B. At this time, an endothermic effect is exerted. The refrigerant evaporated in the refrigerant flow path 64B passes through the refrigerant pipe 71, the refrigerant pipe 13C, and the accumulator 12 in this order, is sucked into the compressor 2 from the refrigerant pipe 13K, and repeatedly circulates (indicated by solid arrows in fig. 7).
On the other hand, since the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 flows through the heat medium heater 63 into the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 in the heat medium pipe 66, where it absorbs heat by the refrigerant evaporated in the refrigerant flow path 64B, and the heat medium is cooled. The heat medium flowing out of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 flows into the battery 55, and exchanges heat with the battery 55. Thereby, the battery 55 is cooled, and the heat medium after cooling the battery 55 is sucked into the circulation pump 62, and the above-described circulation (indicated by a broken-line arrow in fig. 7) is repeated.
In the above-described battery cooling (individual) mode, the heat pump controller 32 also controls the rotation speed NC of the compressor 2 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 to cool the battery 55.
(9) Battery heating mode
Further, the heat pump controller 32 performs a battery heating mode when performing an air conditioning operation or when charging the battery 55. In the battery heating mode, the heat pump controller 32 operates the circulation pump 62 and energizes the heat medium heater 63. The auxiliary expansion valve 68 is fully closed.
As a result, the heat medium discharged from the circulation pump 62 flows into the heat medium pipe 66 and flows to the heat medium heater 63. At this time, the heat medium heater 63 generates heat, and therefore, the heat medium, after being heated by the heat medium heater 63 and having a temperature increased, flows into the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64, passes through the heat medium flow path 64A, reaches the battery 55, and exchanges heat with the battery 55. Thereby, the battery 55 is heated, and the heat medium after heating the battery 55 is sucked into the circulation pump 62, and the above-described circulation is repeated.
In the above-described battery heating mode, the heat pump controller 32 controls energization of the heat medium heater 63 based on the heat medium temperature Tw detected by the heat medium temperature sensor 76 so as to adjust the heat medium temperature Tw to a predetermined target heat medium temperature Tw o, thereby heating the battery 55.
(10) Control of compressor 2 in heating mode and dehumidification heating mode
Further, the heat pump controller 32 calculates a target rotation speed (compressor target rotation speed) TGNCh of the compressor 2 based on the radiator pressure Pci in the heating mode and the dehumidification heating mode according to the control block diagram of fig. 8. Fig. 8 is a control block diagram of the heat pump controller 32 that calculates the target rotation speed (compressor target rotation speed) TGNCh of the compressor 2 based on the radiator pressure Pci. The F/F (feedforward) operation amount calculation unit 78 of the heat pump controller 32 calculates the F/F operation amount TGNChff of the compressor target rotation speed based on the outside air temperature Tam obtained from the outside air temperature sensor 33, the blower voltage BLV of the indoor blower 27, the air volume ratio SW determined by the air mix damper 28 obtained by sw= (TAO-Te)/(Thp-Te), the target supercooling degree TGSC that is the target value of the supercooling degree SC of the refrigerant at the outlet of the radiator 4, the aforementioned target heater temperature TCO that is the target value of the heater temperature Thp, and the target radiator pressure PCO that is the target value of the pressure of the radiator 4.
The heater temperature Thp is an air temperature (estimated value) on the leeward side of the radiator 4, and is calculated (estimated) based on the radiator pressure Pci detected by the radiator pressure sensor 47 and the refrigerant outlet temperature Tci detected by the radiator outlet temperature sensor 44. The supercooling degree SC is calculated based on the refrigerant inlet temperature Tcxin and the refrigerant outlet temperature Tci of the radiator 4 detected by the radiator inlet temperature sensor 43 and the radiator outlet temperature sensor 44.
The target value calculation unit 79 calculates the target radiator pressure PCO based on the target supercooling degree TGSC and the target heater temperature TCO. The F/B (feedback) operation amount calculation unit 81 calculates the F/B operation amount TGNChfb of the compressor target rotation speed by PID calculation or PI calculation based on the target radiator pressure PCO and the radiator pressure Pci. The F/F operation amount TGNChff calculated by the F/F operation amount calculating unit 78 and the F/B operation amount TGNChfb calculated by the F/B operation amount calculating unit 81 are added by the adder 82, and input to the limit setting unit 83 as TGNCh 00.
After the limit setting unit 83 sets the limit to the lower limit rotation speed ECNpdLimLo and the upper limit rotation speed ECNPDLIMHI in control as TGNCh, the compressor cut-off control unit 84 determines the compressor target rotation speed TGNCh. In the normal mode, the heat pump controller 32 controls the operation (rotation speed NC) of the compressor 2 based on the compressor target rotation speed TGNCh calculated based on the radiator pressure Pci.
When the compressor target rotation speed TGNCh is the above-described lower limit rotation speed ECNpdLimLo and the radiator pressure Pci increases to a predetermined upper limit PUL set up above and below the target radiator pressure PCO and to a predetermined upper limit PUL in the lower limit PLL (a state greater than the upper limit PUL or a state equal to or greater than the upper limit PUL, the same applies hereinafter), the compressor turn-off control unit 84 enters an on-off mode in which the compressor 2 is stopped and the on-off control of the compressor 2 is performed for a predetermined time period th 1.
In the on-off mode of the compressor 2, when the radiator pressure Pci falls to the lower limit PLL (the same applies to the case where the radiator pressure Pci falls to the lower limit PLL or less), the compressor 2 is started and the compressor target rotation speed TGNCh is operated as the lower limit rotation speed ECNpdLimLo, and when the radiator pressure Pci increases to the upper limit PUL in this state, the compressor 2 is stopped again. That is, the operation (on) and the stop (off) of the compressor 2 at the lower limit rotation speed ECNpdLimLo are repeated. Further, when the radiator pressure pp is lowered to the lower limit value PUL, and then the compressor 2 is started, and when the state in which the radiator pressure pp is not higher than the lower limit value PUL continues for the predetermined time th2, the on-off mode of the compressor 2 is ended, and the normal mode is restored.
(11) Control of the outdoor expansion valve 6 and the indoor expansion valve 8 in the dehumidification and heating mode
Next, an example of control of the outdoor expansion valve 6 and the indoor expansion valve 8 by the heat pump controller 32 in the dehumidification and heating mode will be described with reference to fig. 9 and 10. The heat pump controller 32 controls the rotation speed NC (fig. 8) of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure Pci (high-pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 as described above in the dehumidification and heating mode, but controls the valve opening based on the absorber temperature Te for the outdoor expansion valve 6 and controls the valve opening based on the valve opening of the outdoor expansion valve 6 and the absorber temperature Te for the indoor expansion valve 8.
(11-1) Control of the outdoor expansion valve 6 in the dehumidification heating mode
First, an example of control of the outdoor expansion valve 6 in the dehumidification and heating mode by the heat pump controller 32 will be described with reference to fig. 9. Fig. 9 shows a transition of the valve opening degree of the outdoor expansion valve 6 in the dehumidification and heating mode. In the embodiment, the heat pump controller 32 changes the valve opening of the outdoor expansion valve 6 in three stages based on the change in the absorber temperature Te detected by the absorber temperature sensor 48. First, when the outdoor expansion valve 6 is changed from the fully closed state to the heat absorber temperature Te being lower than the target heat absorber temperature TEO-up>A, the outdoor expansion valve 6 is opened and the valve opening thereof is set to the predetermined valve opening 1. The a is a predetermined positive value. The valve opening 1 is a predetermined opening smaller than a set maximum opening described later.
In a state where the valve opening of the outdoor expansion valve 6 is set to the valve opening 1, when the absorber temperature Te is further reduced and is lower than the target absorber temperature TEO-B, the valve opening of the outdoor expansion valve 6 is set to the set maximum opening. The set maximum opening is a maximum value in control of the outdoor expansion valve 6 set in the dehumidification and heating mode. The above-mentioned B is a relation of A < B. That is, as the absorber temperature Te decreases from the target absorber temperature TEO, the heat pump controller 32 expands the valve opening of the outdoor expansion valve 6.
As the valve opening degree of the outdoor expansion valve 6 increases, the amount of refrigerant diverted to the indoor expansion valve 8 decreases, and therefore, the inflow amount of refrigerant flowing into the heat absorber 9 decreases. Then, in a state where the valve opening of the outdoor expansion valve 6 is set to the maximum opening, the heat absorber temperature Te increases, and when the target heat absorber temperature teo+c increases, the heat pump controller 32 reduces the valve opening of the outdoor expansion valve 6 to the valve opening 1 described above. The above-mentioned C is also a predetermined positive value.
In a state where the valve opening of the outdoor expansion valve 6 is set to the valve opening 1, when the absorber temperature Te further increases and becomes higher than the target absorber temperature teo+d, the outdoor expansion valve 6 is set to be fully closed. The above-mentioned D is a relation of C < D. That is, the heat pump controller 32 reduces the valve opening degree of the outdoor expansion valve 6 as the heat absorber temperature Te increases from the target heat absorber temperature TEO, and therefore, the amount of refrigerant diverted to the indoor expansion valve 8 increases, and the inflow amount of refrigerant flowing into the heat absorber 9 also increases.
In this way, in the dehumidification and heating mode, the heat pump controller 32 basically controls the absorber temperature Te to be in the vicinity of the target absorber temperature TEO by adjusting the valve opening of the outdoor expansion valve 6. This is called the usual control of the outdoor expansion valve 6.
(11-2) Control of the indoor expansion valve 8 in the dehumidification heating mode
Next, an example of control of the indoor expansion valve 8 in the dehumidification and heating mode by the heat pump controller 32 will be described with reference to fig. 10. Fig. 10 shows a transition of the valve opening degree of the indoor expansion valve 8 in the dehumidification and heating mode. When the valve opening of the outdoor expansion valve 6 is not the set maximum opening, the heat pump controller 32 executes the normal control state, and when the valve opening of the outdoor expansion valve 6 is the set maximum opening, the control state is shifted to the opening/closing control state.
That is, in the normal control state, the heat pump controller 32 sets the valve opening of the indoor expansion valve 8 to the predetermined valve opening 2. The valve opening 2 is the maximum value of the control of the indoor expansion valve 8 in the dehumidification and heating mode (the set maximum opening of the indoor expansion valve 8 in the dehumidification and heating mode). The maximum value of the control of the indoor expansion valve 8 in the dehumidification and heating mode is set smaller than the maximum value of the control of the indoor expansion valve 8 in the dehumidification and cooling mode. The reason for this is that two-stage decompression by the outdoor expansion valve 6 and the indoor expansion valve 8 occurs in the dehumidification cooling mode. As in the embodiment, by setting the maximum value in the control of the indoor expansion valve 8, the temperature drop of the heat absorber 9 can be suppressed in the dehumidification and heating mode, and in the dehumidification and cooling mode, the outdoor expansion valve 6 is controlled to be slightly opened as compared with the case of the dehumidification and heating mode, and dehumidification and cooling of the vehicle interior can be achieved without any obstruction.
In this normal control state, when the valve opening degree of the outdoor expansion valve 6 is the set maximum opening degree, the heat pump controller 32 shifts to the opening/closing control state. When the state is shifted to the opening/closing control state, the heat pump controller 32 first reduces the valve opening degree of the indoor expansion valve 8 to the predetermined valve opening degree 3. The valve opening 3 is a predetermined opening smaller than the valve opening 2 described above. That is, when the heat pump controller 32 cannot further control the heat absorber temperature Te due to the valve opening degree of the outdoor expansion valve 6 (because the valve opening degree of the outdoor expansion valve 6 cannot be further increased), the operation is shifted to the opening/closing control state, and the valve opening degree of the indoor expansion valve 8 is reduced to the valve opening degree 3. In this open/close control state, the heat pump controller 32 fixes the outdoor expansion valve 6 to a set maximum opening degree.
In this open/close control state, the heat pump controller 32 performs switching control of the indoor expansion valve 8 between the valve opening 3 and full closure described above based on a change in the absorber temperature Te detected by the absorber temperature sensor 48. That is, even if the outdoor expansion valve 6 is set to the maximum opening degree and the valve opening degree of the indoor expansion valve 8 is reduced to the valve opening degree 3, the heat absorber temperature Te is further reduced to be lower than the predetermined value t1, and the heat pump controller 32 sets the indoor expansion valve 8 to the full-closed state. Thereby, the refrigerant does not further flow into the heat absorber 9, thereby preventing a drop in the heat absorber temperature Te and preventing freezing of the heat absorber 9. The predetermined value t1 is a predetermined lower value equal to or higher than the freezing point (zero degree).
When the indoor expansion valve 8 is fully closed and the temperature of the air blown into the vehicle interior (the blowout temperature) changes, the heat pump controller 32 controls the blowout temperature to a target value in accordance with the change in the blowout temperature in accordance with the rotation speed control of the compressor 2 based on the target radiator pressure PCO and the radiator pressure Pci as described above.
When the heat absorber temperature Te increases beyond the other predetermined value t2 higher than the predetermined value t1 after the indoor expansion valve 8 is fully closed, the heat pump controller 32 opens the indoor expansion valve 8 and sets the valve opening to the valve opening 3 (predetermined valve opening). In addition, in any of the above cases, the indoor expansion valve 8 may be opened when the heat absorber temperature Te exceeds the predetermined value t 1. Thereby, the refrigerant flows into the heat absorber 9, and dehumidification of the vehicle interior is restarted.
After that, when the absorber temperature Te falls below the predetermined value t1 again, the heat pump controller 32 closes the indoor expansion valve 8 again. In such an open/close control state, when a predetermined recovery condition is satisfied, the heat pump controller 32 recovers to the above-described normal control state. The recovery condition is, for example, that the absorber temperature Te rises to a temperature higher than the predetermined value t2, or that a predetermined time has elapsed in addition to this.
As described in detail above, the heat pump controller 32 constituting the control device 11 sets the indoor expansion valve 8 to the fully closed state when the heat sink temperature Te is lower than the predetermined value t1, and therefore, can stop the flow of the refrigerant to the heat sink 9 without decreasing the rotation speed NC of the compressor 2, and avoid the problem that the heat sink 9 freezes.
In this way, the disadvantage of the air volume drop in the vehicle interior is also eliminated, and the target blowout temperature can be smoothly achieved when the rotation speed NC of the compressor 2 is controlled based on the radiator pressure pp (an index capable of grasping the temperature of the air blown into the vehicle interior) as in the example.
In this case, in the embodiment, the heat pump controller 32 enlarges the valve opening degree of the outdoor expansion valve 6 as the heat absorber temperature Te decreases, and when the outdoor expansion valve 6 is set to the maximum opening degree and the heat absorber temperature Te is lower than the predetermined value t1, the indoor expansion valve 8 is set to be fully closed, so that the decrease in the heat absorber temperature Te is handled by the outdoor expansion valve 6 while the flow rate of the refrigerant flowing to the heat absorber 9 can be controlled by the control of the outdoor expansion valve 6, and when the flow rate of the refrigerant flowing to the heat absorber 9 is reduced by the outdoor expansion valve 6 to reach the limit, the flow of the refrigerant into the heat absorber 9 can be stopped by the indoor expansion valve 8.
In particular, in the embodiment, the heat pump controller 32 reduces the opening degree of the indoor expansion valve 8 from the valve opening degree 2 to the valve opening degree 3 when the outdoor expansion valve 6 is set to the maximum opening degree, and sets the indoor expansion valve 8 to be fully closed when the heat absorber temperature Te is lower than the predetermined value t1, so that if the heat absorber temperature Te can be made not lower than the predetermined value t1 by reducing the valve opening degree of the indoor expansion valve 8, it is not necessary to set the indoor expansion valve 8 to be fully closed. Therefore, the dehumidification capability of the vehicle interior can be maintained while preventing the freezing of the heat absorber 9.
In the embodiment, when the indoor expansion valve 8 is fully closed and then the heat absorber temperature Te exceeds the predetermined value t1 or exceeds the predetermined value t2 higher than the predetermined value t1, the heat pump controller 32 opens the indoor expansion valve 8 at the predetermined valve opening 3, and therefore, when the indoor expansion valve 8 is fully closed and then the heat absorber temperature Te increases, it is possible to restart the supply of the refrigerant to the heat absorber 9 without any obstruction and start the dehumidification of the vehicle interior.
The configuration and the numerical values of the refrigerant circuit R described in the embodiment and the conditions for the transition (changeover) related to the control of the outdoor expansion valve 6 and the indoor expansion valve 8 are not limited to these, and may be changed within a range not departing from the gist of the present invention. In the embodiment, the present invention has been described with respect to the vehicle air conditioner 1 having the respective operation modes such as the heating mode, the dehumidification cooling mode, the air conditioner (priority) +the battery cooling mode, but the present invention is not limited thereto, and is also effective in, for example, a vehicle air conditioner capable of performing the dehumidification heating mode and the dehumidification cooling mode.
(Symbol description)
1 Vehicle air conditioner
2 Compressor
3 Air flow path
4 Radiator
6 Outdoor expansion valve
7 Outdoor heat exchanger
8 Indoor expansion valve
9 Heat absorber
11 Control device
32 Heat pump controller
45 Air conditioner controller
R refrigerant circuit.

Claims (5)

1. An air conditioning apparatus for a vehicle, comprising:
a compressor that compresses a refrigerant;
a radiator for radiating heat from a refrigerant to heat air supplied into a vehicle interior;
A heat absorber for absorbing heat from a refrigerant to cool air supplied into the vehicle interior;
an outdoor heat exchanger provided outside the vehicle;
An outdoor expansion valve for decompressing the refrigerant flowing into the outdoor heat exchanger,
An indoor expansion valve for decompressing the refrigerant flowing into the heat absorber; and
The control device is used for controlling the control device,
At least a dehumidification heating mode is executed by the control device,
In the dehumidification and heating mode, the refrigerant discharged from the compressor is cooled in the radiator, the cooled refrigerant is split, one refrigerant is depressurized by the indoor expansion valve, then the one refrigerant is allowed to absorb heat in the heat absorber, the other refrigerant is depressurized by the outdoor expansion valve, then the other refrigerant is allowed to absorb heat in the outdoor heat exchanger,
The control device enlarges the valve opening of the outdoor expansion valve as the temperature of the heat absorber decreases, and sets the indoor expansion valve to be fully closed when the outdoor expansion valve is set to a maximum opening and the temperature of the heat absorber is lower than a predetermined value.
2. The vehicular air-conditioning apparatus according to claim 1, wherein,
The control device controls the rotation speed of the compressor based on an index capable of grasping the temperature of air blown into the vehicle interior.
3. The vehicular air-conditioning apparatus according to claim 1, wherein,
The control device reduces the valve opening of the indoor expansion valve when the outdoor expansion valve is set to a maximum opening, and sets the indoor expansion valve to be fully closed when the temperature of the heat absorber is lower than the predetermined value.
4. The air conditioner for vehicle according to any one of claim 1 to 3,
The control device opens the indoor expansion valve at a predetermined valve opening degree when the temperature of the heat absorber exceeds the predetermined value or exceeds a predetermined value higher than the predetermined value after the indoor expansion valve is fully closed.
5. The air conditioner for vehicle according to any one of claim 1 to 3,
The control device performs a dehumidification cooling mode in which the refrigerant discharged from the compressor is radiated in the expansion valve and the outdoor heat exchanger, and the radiated refrigerant is depressurized in the indoor expansion valve, and then the refrigerant is absorbed in the heat absorber, and
The maximum value of the control of the valve opening degree of the indoor expansion valve in the dehumidification and heating mode is set to be smaller than the maximum value of the control of the valve opening degree of the indoor expansion valve in the dehumidification and cooling mode.
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