WO2013084463A1 - ヒートポンプサイクル - Google Patents
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- Publication number
- WO2013084463A1 WO2013084463A1 PCT/JP2012/007736 JP2012007736W WO2013084463A1 WO 2013084463 A1 WO2013084463 A1 WO 2013084463A1 JP 2012007736 W JP2012007736 W JP 2012007736W WO 2013084463 A1 WO2013084463 A1 WO 2013084463A1
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- WIPO (PCT)
- Prior art keywords
- heat exchanger
- heat
- refrigerant
- temperature
- auxiliary
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00961—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising means for defrosting outside heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
Definitions
- This disclosure relates to a heat pump cycle.
- Patent Document 1 discloses a heat pump cycle and defrost control of the evaporator.
- Patent Documents 2 to 5 disclose a heat exchanger that can flow a plurality of media.
- Patent Document 2 to Patent Document 5 can be used for defrosting.
- Patent Documents 2 to 5 disclose the structure of the heat exchanger, but there is a possibility that defrosting is not performed using an appropriate heat source for defrosting.
- An object of the present disclosure is to provide a heat pump cycle with improved frost suppression and / or defrosting performance.
- Another object of the present disclosure is to provide a heat pump cycle with improved frost suppression and / or defrosting performance without relying solely on an external heat source.
- Still another object of the present disclosure is to provide a heat pump cycle suitable for use of the heat exchanger proposed by the inventors in Japanese Patent Application No. 2011-123199 or Japanese Patent Application No. 2011-82759.
- a compressor that supplies high-pressure refrigerant by sucking and compressing low-pressure refrigerant, and a use-side heat exchange in which high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant in a heating application
- a decompressor that depressurizes the high-pressure refrigerant and supplies the low-pressure refrigerant in the heating application
- an outdoor heat exchanger that exchanges heat between the air and the low-pressure refrigerant in the heating application, and absorbs heat by the low-pressure refrigerant
- an outdoor heat exchanger that supplies heat obtained from a high-temperature refrigerant compressed by the compressor and having a temperature higher than that of the low-pressure refrigerant to the endothermic heat exchanger.
- the heat pump cycle can constitute a cycle in which the low-pressure refrigerant is compressed by the compressor and the high-pressure refrigerant is supplied.
- the heat pump cycle can supply heat absorbed by the endothermic heat exchanger to the use side heat exchanger.
- the heat pump cycle includes an auxiliary heat exchanger that supplies heat to the endothermic heat exchanger.
- the auxiliary heat exchanger supplies heat obtained from a high-temperature refrigerant compressed by the compressor and having a temperature higher than that of the low-pressure refrigerant exchanged by the endothermic heat exchanger to the endothermic heat exchanger.
- the endothermic heat exchanger can be heated by the heat obtained from the high-temperature refrigerant. Therefore, the heat absorption heat exchanger can be heated by the heat of the heat pump cycle without depending only on the external heat source. Thereby, suppression of frost adhesion and / or defrosting are possible.
- the outdoor heat exchanger may include an air passage for flowing air
- the auxiliary heat exchanger may include an air passage for flowing air.
- the auxiliary heat exchanger can also exchange heat with air.
- a heating application that causes the outdoor heat exchanger to function as an endothermic heat exchanger that absorbs heat from the low-pressure refrigerant
- a cooling application that causes the outdoor heat exchanger to function as a radiation heat exchanger that radiates heat from the high-temperature refrigerant to the air
- a cycle switching device for switching the flow path may be provided.
- the auxiliary heat exchanger may radiate the heat obtained from the high-temperature refrigerant to the air in the cooling application.
- a heat pump cycle that can be switched between a heating application and a cooling application can be provided.
- the auxiliary heat exchanger may be used for radiating the heat of the high-temperature refrigerant to the air in cooling applications.
- the auxiliary heat exchanger can be used for both heating and cooling applications.
- a flow rate regulator that increases the flow rate of the high-temperature refrigerant in the cooling application than the flow rate of the high-temperature refrigerant in the heating application may be provided.
- the flow rate of the high-temperature refrigerant in the cooling application can be made larger than the flow rate of the high-temperature refrigerant in the heating application. More heat can be obtained from high temperature refrigerants in cooling applications than heat obtained from high temperature refrigerants in heating applications. As a result, the auxiliary heat exchanger can be fully utilized in cooling applications.
- the outdoor heat exchanger and the auxiliary heat exchanger may constitute a first heat exchanger unit that can be handled as an integral unit.
- an endothermic heat exchanger and an auxiliary heat exchanger can be provided by the first heat exchanger unit that can be handled as an integral unit.
- the outdoor heat exchanger may include a plurality of low temperature medium tubes
- the auxiliary heat exchanger may include a plurality of high temperature medium tubes.
- the low temperature medium tube and the high temperature medium tube may be arranged to be thermally coupled in at least a part of the first heat exchanger unit. In this case, since the low temperature medium tube and the high temperature medium tube are thermally coupled, it is easy to supply the heat of the high temperature medium tube to the vicinity of the low temperature medium tube.
- the low temperature medium tube and the high temperature medium tube may be thermally coupled via fins disposed in the air passage.
- heat exchange between the low-temperature medium tube and the high-temperature medium tube can be performed via the fins.
- the first heat exchanger unit has an upstream row in which tubes are arranged in a row and a downstream row in which tubes are arranged in a row downstream from the upstream row in the air flow direction. May be.
- the upstream row may include a group of a plurality of hot medium tubes. In this case, frost suppression and / or frost removal can be efficiently performed by the high-temperature medium tubes arranged in the upstream row.
- the upstream row may further include a group of a plurality of low-temperature medium tubes.
- a group of a plurality of cold medium tube tubes and a group of a plurality of hot medium tube tubes may be alternately arranged in at least a part of the upstream row. In this case, frost suppression and / or frost removal can be performed efficiently.
- the outdoor heat exchanger and the auxiliary heat exchanger may be separate, and the auxiliary heat exchanger is positioned upstream of the outdoor heat exchanger with respect to the air flow. It may be arranged. In this case, even if the outdoor heat exchanger and the auxiliary heat exchanger are separate bodies, the auxiliary heat exchanger can supply heat from the upstream side of the outdoor heat exchanger.
- the compressor, the use side heat exchanger, the decompressor, and the outdoor heat exchanger may constitute a mainstream circuit.
- the auxiliary heat exchanger may supply heat obtained from the high-temperature refrigerant upstream or downstream of the use side heat exchanger to the outdoor heat exchanger. In this case, heat can be obtained from the high-temperature refrigerant with a simple configuration.
- the compressor, the use-side heat exchanger, the decompressor, and the outdoor heat exchanger may constitute a mainstream circuit. Furthermore, a shunt circuit that shunts from upstream or downstream of the use side heat exchanger may be provided, and the auxiliary heat exchanger may supply the heat obtained from the high-temperature refrigerant in the shunt circuit to the outdoor heat exchanger. In this case, heat can be obtained from the high-temperature refrigerant with a simple configuration.
- the auxiliary heat exchanger supplies heat to the outdoor heat exchanger when the outdoor heat exchanger absorbs heat in order to suppress adhesion of frost to the outdoor heat exchanger. May be.
- frost formation on the outdoor heat exchanger can be suppressed by the heat obtained from the refrigerant.
- the auxiliary heat exchanger may store heat obtained from the high-temperature refrigerant, or may have an auxiliary medium that supplies the stored heat to the outdoor heat exchanger.
- the heat obtained from the high-temperature refrigerant can be stored in the auxiliary medium. For this reason, the heat of the high-temperature refrigerant can be supplied to the outdoor heat exchanger via the auxiliary medium.
- the auxiliary heat exchanger supplies heat from the auxiliary medium to the outdoor heat exchanger after the outdoor heat exchanger absorbs heat in order to defrost the frost attached to the outdoor heat exchanger. May be.
- defrosting can be performed by the heat obtained from the refrigerant.
- the sixteenth example of the present disclosure may further include a heat source heat exchanger that supplies heat from the high-temperature refrigerant to the auxiliary medium.
- the heat of the high-temperature refrigerant can be supplied to the auxiliary medium by the heat source heat exchanger.
- the outdoor heat exchanger and the heat source heat exchanger may constitute a second heat exchanger unit that can be handled as an integral unit.
- an outdoor heat exchanger in which the low-pressure refrigerant flows and a heat source heat exchanger in which the high-temperature refrigerant flows can be provided by the second heat exchanger unit that can be handled as an integral unit.
- the second heat exchanger unit may include a decompressor, and the decompressor may be provided between the heat source heat exchanger and the outdoor heat exchanger.
- the second heat exchanger unit can be provided with a decompressor.
- an auxiliary medium circuit that circulates the auxiliary medium so as to pass through the auxiliary heat exchanger and the heat source heat exchanger, and an external heat source that is provided in the auxiliary medium circuit and supplies heat to the auxiliary medium And may be provided.
- heat from an external heat source can be supplied to the auxiliary medium.
- the auxiliary heat exchanger may flow high-temperature refrigerant and receive heat directly from the high-temperature refrigerant.
- the heat of the high-temperature refrigerant can be directly received.
- the heat of the auxiliary heat exchanger can be supplied through air or a member connecting the outdoor heat exchanger and the auxiliary heat exchanger.
- FIG. 1 It is a mimetic diagram showing heating operation of a heat pump cycle of a 1st embodiment of this indication. It is a schematic diagram which shows the defrost operation of the heat pump cycle of 1st Embodiment. It is a schematic diagram which shows the waste heat recovery driving
- FIG. 7 is a cross-sectional view showing a VIII-VIII cross section of FIG. 6. It is a schematic perspective view which shows the flow of the fluid in the heat exchanger of 1st Embodiment. It is a schematic sectional drawing which shows the XX cross section of FIG. It is a mimetic diagram showing heating operation of a heat pump cycle of a 2nd embodiment of this indication. It is a mimetic diagram showing heating operation of a heat pump cycle of a 3rd embodiment of this indication. It is a mimetic diagram showing heating operation of a heat pump cycle of a 4th embodiment of this indication. It is a mimetic diagram showing heating operation of a heat pump cycle of a 5th embodiment of this indication.
- FIG. 20 is a simplified schematic diagram illustrating a refrigerant circuit corresponding to the heat pump cycle of FIGS. It is the simplified schematic diagram which shows the refrigerant circuit corresponding to the heat pump cycle of FIG.
- FIG. 38 is a simplified schematic diagram illustrating a refrigerant circuit of a heat pump cycle according to a thirty-seventh embodiment of the present disclosure.
- an air conditioner 1 for a vehicle is provided according to the first embodiment of the present disclosure.
- the air conditioner 1 includes a heat pump cycle (HPC) 2 to which the present disclosure is applied.
- the heat pump cycle 2 includes a heat exchanger 70 and a heat exchanger 80 to which the present disclosure is applied.
- the heat pump cycle 2 includes a refrigerant circuit 10 and a cooling water circuit 40.
- the air conditioner 1 is adapted to a so-called hybrid vehicle that obtains driving power from an internal combustion engine (engine) and a motor generator.
- the heat pump cycle 2 uses at least one of an engine, a motor generator, an inverter circuit, a battery, a control circuit, and the like of the hybrid vehicle as an external heat source HS.
- the external heat source HS one of in-vehicle devices that generate heat during operation can be used.
- the external heat source HS supplies heat to the cooling water WT that is an example of the auxiliary medium.
- the cooling water circuit 40 is also a cooling system for cooling the external heat source HS and keeping it at an appropriate temperature.
- the air conditioner 1 can be used for any of a vehicle using only an engine as a power source, a hybrid vehicle, and a vehicle using only an electric motor as a power source. In recent vehicles, there is little waste heat supplied from a power source. For this reason, if it relies only on the waste heat from the power source, it is difficult to suppress frost and / or defrost the outdoor heat exchanger 16.
- This embodiment provides a heat source for frost control and / or defrost to the outdoor heat exchanger 16 without relying solely on waste heat from the power source.
- the air conditioner 1 includes an air conditioning unit 30 that blows air UR toward a vehicle interior that is an air conditioning target space.
- the air conditioner 1 includes a control device (CNTR) 100 that controls the heat pump cycle 2 and the air conditioning unit 30.
- CNTR control device
- the air conditioning unit 30 is arranged in the passenger compartment.
- the air conditioning unit 30 includes a casing 31 that provides a duct for the air UR sent toward the passenger compartment.
- the air conditioning unit 30 is configured by arranging components such as the blower 32, the indoor condenser 12, and the indoor evaporator 20 in a casing 31.
- An inside / outside air switching device 33 that introduces air in the passenger compartment and air outside the passenger compartment selectively or in a mixed manner is disposed at the most upstream portion in the casing 31.
- a blower 32 for blowing air UR is disposed on the downstream side of the inside / outside air switching device 33.
- the indoor evaporator 20 and the indoor condenser 12 are arranged in this order with respect to the flow of the air UR.
- the indoor evaporator 20 is disposed on the upstream side with respect to the indoor condenser 12.
- the indoor evaporator 20 is a cooling heat exchanger that exchanges heat between the refrigerant circulating in the interior and the air UR to cool the air UR.
- the indoor condenser 12 is a heating heat exchanger that exchanges heat between the high-temperature and high-pressure refrigerant flowing through the indoor condenser 12 and the air UR after passing through the indoor evaporator 20.
- An air mix door 34 is arranged on the downstream side of the indoor evaporator 20 and on the upstream side of the indoor condenser 12.
- the air mix door 34 adjusts the ratio of passing through the indoor condenser 12 in the air UR after passing through the indoor evaporator 20.
- a mixing space 35 is provided on the downstream side of the indoor condenser 12. The mixing space 35 mixes the air UR heated by the indoor condenser 12 and the air UR that bypasses the indoor condenser 12 and is not heated.
- the downstream of the mixing space 35 communicates with the vehicle interior via a blowout port.
- the refrigerant circuit 10 is provided by a vapor compression refrigeration cycle capable of reversible operation.
- the temperature refrigerant circuit 10 is a refrigerant cycle for heating the air conditioner 1.
- the refrigerant circuit 10 can additionally serve as a cooling refrigeration cycle.
- the refrigerant circuit 10 provides a narrowly defined heat pump cycle that uses the air AR outside the passenger compartment as a heat source.
- the refrigerant circuit 10 is also called a refrigerant system.
- the refrigerant circuit 10 causes the refrigerant RF to flow through a refrigerant tube 16a described later, and supplies the heat absorbed by the refrigerant RF to the indoor condenser 12.
- the refrigerant RF flowing in the refrigerant circuit 10 is a main functional medium for pumping heat from the heat source.
- the refrigerant circuit 10 is also called a main medium circuit 10.
- frost suppression suppressing frost adhesion in the outdoor heat exchanger 16 of the refrigerant circuit 10, that is, the heat source side heat exchanger, and suppressing the growth of the attached frost are referred to as frost suppression.
- melting and removing frost adhering to the outdoor heat exchanger 16 is called defrosting.
- anti-frosting performance the performance which opposes the fall of the heat exchange performance resulting from frost is called anti-frosting performance.
- anti-frosting performance is provided by frost suppression and / or defrosting.
- the cooling water circuit 40 is a heat source device that supplies heat to the refrigerant circuit 10.
- the cooling water circuit 40 can flow cooling water WT used as a heat carrying medium and a heat storage medium.
- the cooling water circuit 40 including the external heat source HS is called a water system or an external heat source system.
- the cooling water WT flowing in the cooling water circuit 40 is an example of an auxiliary medium for assisting pumping of heat by the main medium circuit 10.
- the cooling water circuit 40 may be used as an example of an auxiliary medium circuit through which an auxiliary medium flows.
- the cooling water circuit 40 is also a heat source device that supplies heat for suppressing frost.
- the cooling water circuit 40 is also called a frost suppression medium circuit 40 for flowing a medium for suppressing frost.
- the cooling water circuit 40 flows cooling water WT for suppressing frost to a water tube 43a described later.
- the cooling water circuit 40 is also a heat source device that supplies heat to the heat exchanger 70 for defrosting.
- the cooling water circuit 40 may be used as an example of a defrosting medium circuit for flowing a medium for defrosting.
- the cooling water circuit 40 flows the cooling water WT for defrosting to the water tube 43a.
- the cooling water circuit 40 maintains the temperature of the cooling water WT and the temperature of the external heat source HS at a temperature higher than the temperature at which the refrigerant in the refrigerant tube 16a absorbs heat.
- the refrigerant circuit 10 heats or cools the air UR blown into the passenger compartment.
- the refrigerant circuit 10 can perform a heating operation for heating the air UR by heating the air UR and a cooling operation for cooling the air UR by cooling the air UR by switching the flow path.
- the refrigerant circuit 10 supplies heat for suppressing frost formation on the outdoor heat exchanger 16 in the heating operation.
- the refrigerant circuit 10 can perform a defrosting operation by melting and removing frost attached to the outdoor heat exchanger 16 that functions as an evaporator that evaporates the refrigerant during the heating operation.
- the refrigerant circuit 10 can execute a waste heat recovery operation in which the heat of the external heat source HS is absorbed by the refrigerant during the heating operation.
- the plurality of operation modes are switched by the control device 100.
- the compressor 11 is disposed in the engine room.
- the compressor 11 sucks low-pressure refrigerant in the refrigerant circuit 10 and compresses it to supply high-pressure refrigerant.
- the compressor 11 includes a compression mechanism 11a such as a scroll type or a vane type, and an electric motor 11b that drives the compression mechanism 11a.
- the electric motor 11b is controlled by the control device 100.
- An indoor condenser 12 is provided on the discharge side of the compressor 11.
- the indoor condenser 12 may be used as an example of a use side heat exchanger to which a high-pressure refrigerant is supplied and heat is supplied from the high-pressure refrigerant.
- a fixed throttle 13 for heating is provided downstream of the indoor condenser 12.
- the fixed throttle 13 decompresses and expands the refrigerant that has flowed out of the indoor condenser 12 during the heating operation.
- the fixed throttle 13 is a decompression means for heating operation.
- the fixed throttle 13 can be provided by an orifice, a capillary tube, or the like.
- the fixed throttle 13 provides a decompressor that decompresses the high-pressure refrigerant and supplies the low-pressure refrigerant.
- An outdoor heat exchanger 16 is provided downstream of the fixed throttle 13. Furthermore, a passage 14 for bypassing the fixed throttle 13 is provided downstream of the indoor condenser 12.
- the passage 14 guides the refrigerant flowing out of the indoor condenser 12 to the outdoor heat exchanger 16 by bypassing the fixed throttle 13.
- An opening / closing valve 15 a that opens and closes the passage 14 is disposed in the passage 14.
- the on-off valve 15a is an electromagnetic valve.
- the pressure loss in the on-off valve 15 a is sufficiently smaller than the pressure loss in the fixed throttle 13. Therefore, when the on-off valve 15a is open, the refrigerant flows exclusively through the passage 14.
- the on-off valve 15a is closed, the refrigerant flows through the fixed throttle 13. Thereby, the on-off valve 15a switches the flow path of the refrigerant circuit 10.
- the on-off valve 15a functions as a refrigerant channel switching means.
- the switching means may be provided by an electric three-way valve.
- the outdoor heat exchanger 16 exchanges heat between the low-pressure refrigerant circulating inside and the air AR.
- the outdoor heat exchanger 16 is disposed in the engine room.
- the outdoor heat exchanger 16 functions as an evaporator that evaporates low-pressure refrigerant and exerts an endothermic effect during heating operation.
- the outdoor heat exchanger 16 provides an endothermic heat exchanger that exchanges heat between the air AR and the low-pressure refrigerant and causes the low-pressure refrigerant to absorb heat.
- the outdoor heat exchanger 16 functions as a radiator that radiates high-pressure refrigerant during cooling operation.
- the outdoor heat exchanger 16 is configured integrally with the radiator 43.
- the outdoor heat exchanger 16 and the radiator 43 constitute a heat exchanger 70.
- the heat exchanger 70 may be used as an example of a first heat exchanger unit that can be handled as an integral unit.
- the cooling water WT flows through the radiator 43.
- the radiator 43 exchanges heat between the cooling water WT of the cooling water circuit 40 and the air AR. Furthermore, the radiator 43 supplies the heat of the cooling water WT to the outdoor heat exchanger 16 and the heat exchanger 70 including the same.
- the cooling water WT stores the heat of the high-pressure refrigerant. Therefore, the radiator 43 stores the cooling water WT that is an example of an auxiliary medium that stores heat obtained from the high-temperature refrigerant and supplies the stored heat to the endothermic heat exchanger.
- the radiator 43 may be used as an example of an auxiliary heat exchanger disposed adjacent to the outdoor heat exchanger 16.
- the auxiliary heat exchanger supplies the outdoor heat exchanger 16 with heat obtained from the high-temperature refrigerant compressed by the compressor 11 and having a temperature higher than that of the low-pressure refrigerant.
- the fan 17 is an electric blower that blows air AR to the outdoor heat exchanger 16.
- the fan 17 provides an outdoor blower that blows the air AR toward both the outdoor heat exchanger 16 and the radiator 43.
- the refrigerant circuit 10 includes a heat exchanger 80 that exchanges heat between the high-temperature refrigerant before being depressurized by the fixed throttle 13 and the cooling water WT of the cooling water circuit 40.
- the heat exchanger 80 may be used as an example of a heat source heat exchanger that supplies heat from the high-temperature refrigerant to the cooling water WT.
- the heat exchanger 80 includes a heat exchange part 81 on the refrigerant circuit 10 side and a heat exchange part 82 on the cooling water circuit 40 side.
- the heat exchanger 80 can be provided by various types of heat exchangers that exchange heat between the refrigerant RF and the cooling water WT.
- the heat exchanger 80 can be configured by a double tube heat exchanger, a tank and tube heat exchanger, a stacked heat exchanger, or the like.
- the heat exchanger 80 is configured separately from the heat exchanger 70, and is connected by piping between them.
- the heat exchanger 80 is provided to give the heat of the high-temperature refrigerant in the refrigerant circuit 10 to the low-temperature portion of the heat exchanger 70.
- the heat of the high-temperature refrigerant is supplied to the heat exchanger 70 via the cooling water WT. Therefore, the heat exchanger 80 can also be referred to as a self-heating heat exchanger that gives the heat of the high-temperature refrigerant in the refrigerant circuit 10 to the low-temperature refrigerant in the refrigerant circuit 10.
- frost adheres and grows in the low temperature portion of the heat exchanger 70.
- the heat provided from the heat exchanger 80 via the cooling water WT suppresses frost adhesion and suppresses frost growth.
- the heat supplied from the heat exchanger 80 suppresses frost formation in the heat exchanger 70.
- the heat obtained from the heat exchanger 80 is stored in the cooling water WT.
- the stored cooling water WT is supplied to the heat exchanger 70 and used for defrosting in the defrosting operation. Therefore, the heat exchanger 80 can also be referred to as a heat source heat exchanger for improving the frosting resistance performance of the heat exchanger 70.
- An electric three-way valve 15 b is connected downstream of the outdoor heat exchanger 16.
- the three-way valve 15b is controlled by the control device 100.
- the three-way valve 15b directly connects the outlet of the outdoor heat exchanger 16 and the inlet of the accumulator 18 without a heat exchanger during heating operation.
- the three-way valve 15b connects the outlet of the outdoor heat exchanger 16 and the inlet of the fixed throttle 19 during cooling operation.
- the fixed throttle 19 is a pressure reducing means for cooling.
- the fixed throttle 19 decompresses and expands the refrigerant that has flowed out of the outdoor heat exchanger 16 during the cooling operation.
- the fixed diaphragm 19 has the same configuration as the fixed diaphragm 13.
- An indoor evaporator 20 is provided downstream of the fixed throttle 19.
- An accumulator 18 is provided downstream of the indoor evaporator 20.
- the flow path that is formed by the three-way valve 15b during the heating operation and directly communicates with the accumulator 18 from the three-way valve 15b constitutes a passage 20a that allows the refrigerant downstream of the outdoor heat exchanger 16 to flow around the indoor evaporator 20. ing.
- the accumulator 18 is a gas-liquid separator for low-pressure refrigerant that separates the gas-liquid of the refrigerant that has flowed into the accumulator 18 and stores excess refrigerant in the cycle.
- a compressor 11 is provided at the gas-phase refrigerant outlet of the accumulator 18. The accumulator 18 functions to prevent liquid compression of the compressor 11 by suppressing the suction of the liquid phase refrigerant into the compressor 11.
- the cooling water circuit 40 is a cooling medium circulation circuit that circulates cooling water through the external heat source HS to cool the external heat source HS.
- the cooling water circuit 40 includes components such as a pump 41, an electric three-way valve 42, a radiator 43, a bypass passage 44 for bypassing the radiator 43 and flowing cooling water, and a flow rate adjusting valve 45.
- the pump 41 is an electric pump that pumps cooling water to the cooling water circuit 40.
- the cooling water circuit 40 may be used as an example of an auxiliary medium circuit that circulates the cooling water WT so as to pass through the radiator 43 and the heat exchanger 80. In the cooling water circuit 40, the pump 41, the heat exchanger 80, and the radiator 43 are arranged in series on the circulation path of the cooling water WT.
- the three-way valve 42 switches the flow path in the cooling water circuit 40.
- the three-way valve 42 switches between a flow path that passes through the external heat source HS and the radiator 43 and a flow path that passes through the external heat source HS and the bypass passage 44.
- the bypass passage 44 provides a flow path that bypasses the radiator 43.
- the radiator 43 is configured integrally with the outdoor heat exchanger 16 and constitutes a heat exchanger 70.
- the cooling water WT is radiated by the radiator 43.
- the cooling water WT gives heat to the air UR and / or the refrigerant.
- the heat given from the high-temperature refrigerant to the cooling water WT by the heat exchanger 80 is given to the heat exchanger 70 in the radiator 43.
- the three-way valve 42 can configure a flow path so as to pass through both the radiator 43 and the bypass passage 44.
- the flow rate adjusting valve 45 adjusts the ratio of the flow rate passing through the radiator 43 and the flow rate passing through the bypass passage 44.
- the cooling water WT flowing in the radiator 43 conveys the heat obtained in the heat exchanger 80 to the heat exchanger 70.
- the cooling water WT flowing through the bypass passage 44 stores the heat obtained in the heat exchanger 80 in the cooling water circuit 40. At this time, the heat supplied from the external heat source HS is also stored in the cooling water circuit 40.
- the heat exchanger 70 provides heat exchange between the refrigerant RF, the coolant WT, and the air AR.
- the heat exchanger 70 provides heat exchange between the refrigerant RF and the cooling water WT, between the refrigerant RF and the air AR, and between the cooling water WT and the air AR.
- the heat exchanger 70 has components such as a plurality of tubes through which refrigerant or cooling water flows, a collection tank and a distribution tank disposed at both ends of the plurality of tubes.
- the outdoor heat exchanger 16 has a plurality of refrigerant tubes 16a through which refrigerant flows.
- the refrigerant tube 16a is a heat exchange tube through which the refrigerant RF that absorbs heat from the air flows.
- the refrigerant tube 16a may be used as an example of a low-temperature medium tube through which the low-temperature medium CMD flows during heating operation.
- the refrigerant tube 16a is a flat tube having a flat cross-sectional shape perpendicular to the longitudinal direction.
- the radiator 43 has a plurality of water tubes 43a for circulating cooling water therein.
- the water tube 43a is a heat exchange tube through which a medium for frost suppression and / or defrosting is passed.
- the water tube 43a may be used as an example of a high-temperature medium tube through which the high-temperature medium HMD flows during heating operation and defrosting operation.
- the heat of the high-temperature medium HMD suppresses frost formation on the heat exchanger 70 during the heating operation. Furthermore, the heat of the high-temperature medium HMD melts the frost on the heat exchanger 70 during the defrosting operation.
- the water tube 43a is a flat tube having a flat cross-sectional shape perpendicular to the longitudinal direction.
- the refrigerant tube 16a and the water tube 43a are referred to as tubes 16a and 43a.
- the plurality of tubes 16a and 43a are arranged such that a wide flat surface of their outer surfaces is substantially parallel to the flow of the air AR.
- the plurality of tubes 16a and 43a are arranged at a predetermined interval from each other.
- Air passages 16b and 43b through which the air AR flows are formed around the plurality of tubes 16a and 43a.
- the air passages 16b and 43b are used as heat dissipation air passages and / or heat absorption air passages.
- the plurality of tubes 16 a and 43 a are arranged to be thermally coupled to at least a part of the heat exchanger 70.
- the plurality of tubes 16a and 43a are arranged in a row in a direction orthogonal to the flow of the air AR. Further, the plurality of tubes 16a and 43a are arranged in multiple rows along the flow direction of the air AR. As illustrated, the plurality of tubes 16a and 43a can be arranged in two rows.
- the plurality of tubes 16a and 43a are arranged so as to form an upstream row located upstream in the flow direction of the air AR and a downstream row located downstream from the upstream row.
- the water tube 43a is arranged in at least a part of the upstream row. In at least a part of the upstream row, the refrigerant tube 16a and the water tube 43a are adjacent to each other. In the upstream row, at least in part, the water tubes 43a can be positioned on both sides of the refrigerant tube 16a. In the upstream row, at least in part, the refrigerant tubes 16a can be positioned on both sides of the water tube 43a. In at least a part of the upstream row, the refrigerant tubes 16a and the water tubes 43a can be alternately positioned.
- the refrigerant tubes 16a and the water tubes 43a are alternately arranged so that the water tubes 43a are positioned on both sides of the refrigerant tube 16a at least in the upstream row. That is, in the heat exchanger 70, on the air AR inflow side, the water tubes 43a are positioned on both sides of the refrigerant tube 16a, and they are arranged side by side.
- the refrigerant tubes can be dispersed over a wide range.
- frost can be dispersed over a wide range.
- the water tube 43a is located next to the refrigerant tube 16a. For this reason, during heating operation, frost adhesion and frost growth in the vicinity of the refrigerant tube 16a can be suppressed.
- the heat supplied from the water tube 43a can be efficiently transmitted to the frost mass grown in the vicinity of the refrigerant tube 16a.
- the refrigerant tube 16a and the water tube 43a can be arranged in the same manner as the upstream row. Instead, only the refrigerant tube 16a or only the water tube 43a may be arranged in the downstream row.
- the plurality of tubes 16a and 43a can be arranged such that a large number of water tubes 43a are located in the upstream row and a small number of water tubes 43a are located in the downstream row. Further, the plurality of tubes 16a and 43a can be arranged such that the water tube 43a is located only in the upstream row.
- the radiator 43 is mainly disposed on the upstream side of the flow of the air AR
- the outdoor heat exchanger 16 is mainly disposed on the downstream side.
- Fins 50 are disposed in the air passages 16b and 43b.
- the fin 50 is an outer fin for promoting heat exchange between the tubes 16a and 43a and the air AR.
- the fin 50 is joined to the two tubes 16a and 43a adjacent in the row. Furthermore, the fin 50 is joined to the two tubes 16a and 43a located in the flow direction of the air AR. Therefore, at least four tubes 16 a and 43 a are joined to one fin 50.
- the fin 50 integrates the outdoor heat exchanger 16 and the radiator 43.
- the fin 50 is made of a thin metal plate having excellent heat conductivity.
- the fin 50 is a corrugated fin obtained by bending a thin plate into a wave shape. The fin 50 promotes heat exchange between the refrigerant RF and the air AR.
- the fin 50 promotes heat exchange between the cooling water WT and the air AR. At least some of the fins 50 are joined to both the refrigerant tube 16a and the water tube 43a.
- the refrigerant tube 16a and the water tube 43a are thermally coupled via the fins 50. Therefore, the fin 50 also functions to enable heat transfer between the refrigerant tube 16a and the water tube 43a.
- the two fins 50 arranged on both sides of one refrigerant tube 16a are corrugated fins in which a plurality of peaks are joined to both surfaces of the refrigerant tube 16a.
- the tank of the outdoor heat exchanger 16 and the tank of the radiator 43 can be formed at least partially from the same member.
- the refrigerant tube 16a, the water tube 43a, the tank, and the fin 50 are made of an aluminum alloy. These parts are brazed.
- the heat exchanger 70 includes a core portion in which the tubes 16a and 43a and the fins 50 are disposed, and tank portions disposed at both ends of the core portion.
- the tubes 16a and 43a arranged in the core portion constitute a plurality of rows including at least an upstream row and a downstream row with respect to the flow direction of the air AR.
- Each of the two tank parts has an inner tank adjacent to the core part and an outer tank located away from the core part.
- the inner tank and the outer tank extend so as to cover almost the entire end of the core at the end of the core. Therefore, the inner tank and the outer tank are stacked on one end of the core portion.
- An inner tank and an outer tank are also stacked on the other end of the core portion.
- the tubes 16a and 43b are arranged in a distributed manner inside the core portion.
- the tube 16a or the tube 43a can be arranged so as to form an uneven distribution inside the core portion.
- positioning of the tubes 16a and 43a in a core part is set so that the performance of the heat exchange requested
- the heat exchanger 70 enables a relatively free arrangement of the tubes 16a and 43a.
- the tubes 16a or the tubes 43a are distributed and arranged in the upstream row and the downstream row along the flow direction of the air AR. In other words, the tubes 16a and the tubes 43a can be mixed in the upstream row or the downstream row.
- the control device 100 is provided by a microcomputer provided with a computer-readable storage medium.
- the storage medium stores a computer-readable program non-temporarily.
- the storage medium can be provided by a semiconductor memory or a magnetic disk.
- the program is executed by the control device 100 to cause the control device 100 to function as a device described in this specification, and to cause the control device 100 to function so as to execute the control method described in this specification.
- the means provided by the control device 100 can also be referred to as a functional block or module that achieves a predetermined function.
- the control device 100 controls the operation of the devices 11, 15a, 15b, 17, 41, 42, and 45.
- a plurality of sensors are connected to the control device 100.
- the plurality of sensors include an inside air sensor as an inside air temperature detecting means for detecting the temperature in the vehicle interior, an outside air sensor for detecting the temperature of the outdoor air, a solar radiation sensor for detecting the amount of solar radiation in the vehicle interior, and a blowout of the indoor evaporator 20
- An evaporator temperature sensor for detecting the air temperature (evaporator temperature) and a discharge refrigerant temperature sensor for detecting the compressor 11 discharge refrigerant temperature can be included.
- the plurality of sensors include an outlet refrigerant temperature sensor 51 that detects the outlet side refrigerant temperature Te of the outdoor heat exchanger 16, and a cooling water temperature detection unit that detects the cooling water temperature Tw flowing into the traveling electric motor MG.
- a coolant temperature sensor 52 may be included.
- the control device 100 provides control means for controlling the amount of refrigerant flowing in the refrigerant circuit 10 and the flow path.
- the amount of refrigerant is controlled by adjusting the refrigerant discharge capacity of the compressor 11.
- the flow path of the refrigerant is switched and controlled by controlling the devices 15a and 15b.
- the heat pump cycle 2 may be used as an example of the cycle switching device for the devices 15a and 15b and the control device 100.
- the cycle switching device (15a, 15b, 100) controls the flow path so that the outdoor heat exchanger 16 functions as an endothermic heat exchanger during heating, and the outdoor heat exchanger 16 functions as a radiant heat exchanger during cooling.
- Heating is a heating application for heating an object.
- Cooling is a cooling application for cooling an object.
- the refrigerant circuit 10 can be switched between a heating application and a cooling application.
- control device 100 provides a control means for controlling the flow and flow path of the cooling water in the cooling water circuit.
- the flow of the cooling water is controlled by controlling the pump 41.
- the flow path of the cooling water is controlled by controlling the three-way valve 42 and the flow rate adjusting valve 45.
- the control device 100 provides frost determination means for determining whether or not frost is generated in the outdoor heat exchanger 16 based on detection signals of a plurality of sensors and / or timers.
- the vehicle speed of the running vehicle is lower than a predetermined reference vehicle speed, for example, 20 km / h
- the outdoor heat exchanger 16 outlet side refrigerant temperature Te is set to a predetermined reference temperature, for example, 0 ° C. When it falls below, it determines with the outdoor heat exchanger 16 having formed frost.
- the control device 100 provides a defrost control unit that performs defrost control for removing frost attached to the outdoor heat exchanger 16.
- the defrosting control unit controls the heat pump cycle 2.
- the control device 100 controls the cooling water circuit 40 so that the temperature of the cooling water falls below a predetermined upper limit temperature and exceeds a predetermined lower limit temperature.
- the control device 100 controls the air conditioner 1 so that the air conditioner 1 selectively provides a cooling operation (COOL) or a heating operation.
- the control apparatus 100 controls the air conditioner 1 to provide a normal heating operation (HEAT1), a defrosting operation (DEFROST), and a waste heat recovery operation (HEAT2) during the heating operation. If frost formation is determined by the frost determination means during the normal heating operation, the operation proceeds to the defrost operation.
- the cooling water temperature Tw detected by the cooling water temperature sensor 52 exceeds the predetermined reference temperature, for example, 60 ° C. during the normal heating operation, the operation proceeds to the waste heat recovery operation. Further, when the return condition is satisfied, the normal heating operation is resumed.
- (A) Normal heating operation (HEAT1)
- HEAT1 Normal heating operation
- the refrigerant circuit 10 is controlled such that the on-off valve 15a is closed, the three-way valve 15b connects the outdoor heat exchanger 16 and the accumulator 18 via the flow path 20a, and the compressor 11 is operated. Thereby, the refrigerant circuit 10 is switched to the refrigerant flow path through which the refrigerant flows as shown by the solid line arrows in FIG.
- the cooling water circuit 40 is controlled so that the pump 41 pumps a predetermined amount of cooling water and the three-way valve 42 flows cooling water to both the radiator 43 and the bypass passage 44.
- the cooling water circuit 40 is switched to a circuit through which the cooling water flows as shown by the broken-line arrows in FIG.
- the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12.
- the refrigerant flowing into the indoor condenser 12 exchanges heat with the air UR that is blown from the blower 32 and passes through the indoor evaporator 20 to dissipate heat. Thereby, the air UR is heated.
- the high-pressure refrigerant that has flowed out of the indoor condenser 12 flows into the heat exchanger 80 and heats the cooling water WT. Thereafter, the high-pressure refrigerant flows into the fixed throttle 13 and is decompressed and expanded.
- the low-pressure refrigerant decompressed and expanded by the fixed throttle 13 flows into the outdoor heat exchanger 16.
- the low-pressure refrigerant that has flowed into the outdoor heat exchanger 16 absorbs heat from the air AR blown by the fan 17 and evaporates.
- the refrigerant flowing out of the outdoor heat exchanger 16 flows into the accumulator 18 and is separated into gas and liquid.
- the gas-phase refrigerant separated by the accumulator 18 is sucked into the compressor 11 and compressed again.
- the cooling water circuit 40 a part of the cooling water WT is supplied to the heat exchanger 70.
- the heat exchanger 70 is warmed by the cooling water WT. Since the heat exchanger 70 is cooled by the outdoor heat exchanger 16, frost may adhere to the surfaces of the constituent members, and the frost may further grow.
- the cooling water WT is supplied to the heat exchanger 70 after being heated in the heat exchanger 80. For this reason, the cooling water WT suppresses frost adhesion and frost growth on the surface of the heat exchanger 70. In other words, since the heat supplied from the high-pressure refrigerant of the refrigerant circuit 10 during the heating operation is indirectly supplied to the constituent members of the heat exchanger 70, frost formation on the constituent members is suppressed.
- the cooling water circuit 40 stores heat supplied from the external heat source HS and heat supplied from the refrigerant circuit 10 in the heat exchanger 80.
- (B) Defrosting operation (DEFROST) During the defrosting operation, the frost adhering to the outdoor heat exchanger 16 is released by the heat obtained from the cooling water circuit 40.
- the control device 100 stops the operation of the compressor 11 and stops the operation of the fan 17. Therefore, during the defrosting operation, the refrigerant flow rate flowing into the outdoor heat exchanger 16 is reduced and the air volume of the air AR flowing into the heat exchanger 70 is reduced as compared with the normal heating operation. Furthermore, the control device 100 switches the three-way valve 42 so that the cooling water passes through the radiator 43 as indicated by the broken-line arrows in FIG.
- the heat of the cooling water flowing through the water tube 43a of the radiator 43 is transferred to the outdoor heat exchanger 16 through the fins 50, and the outdoor heat exchanger 16 is defrosted. That is, defrosting that effectively uses the heat of the cooling water circuit 40 is realized.
- the heat used for defrosting includes waste heat supplied from the external heat source HS and heat stored in the cooling water circuit 40. Further, the heat used for defrosting includes heat given to the cooling water circuit 40 from the refrigerant circuit 10 in the heat exchanger 80 and stored in the cooling water circuit 40 during the heating operation.
- the heat exchanger 70 is provided with fins 50 made of a metal member to enable heat transfer between the refrigerant tube 16a and the water tube 43a. As a result, the heat of the cooling water can be transferred to the outdoor heat exchanger 16 through the fins 50 during the defrosting operation. As a result, it is possible to shorten the defrosting operation time.
- the flow rate of the refrigerant flowing into the outdoor heat exchanger 16 is reduced from before the shift to the defrosting operation, for example, 0 (zero). Therefore, it can suppress that heat is absorbed into the refrigerant
- the heat of the cooling water circuit 40 including the external heat source HS is defrosted. Can be used effectively.
- the air volume of the air AR flowing into the heat exchanger 70 is reduced, for example, 0 (zero). Therefore, it can suppress that heat is absorbed into the air AR.
- the heat of the external heat source HS is stored in the cooling water circuit 40. Therefore, defrosting can be completed in a short time by the stored heat.
- Waste heat recovery operation (HEAT2) Waste heat recovery operation (HEAT2)
- the vehicle interior is heated using the external heat source HS as a heat source.
- the heat of the cooling water circuit 40 can be radiated to the air AR, but when a predetermined condition is satisfied, a waste heat recovery operation is performed to increase the heating capacity by passing the heat of the cooling water circuit 40 to the refrigerant circuit 10.
- a predetermined reference temperature for example, 60 ° C. during the heating operation, the waste heat recovery operation can be executed.
- the three-way valve 15b is controlled similarly to the normal heating operation.
- the three-way valve 42 is controlled similarly to the defrosting operation. Therefore, as indicated by solid line arrows in FIG. 3, the high-pressure refrigerant discharged from the compressor 11 heats the air UR in the indoor condenser 12, flows into the heat exchanger 80, and heats the cooling water WT. Thereafter, the high-pressure refrigerant is decompressed and expanded by the fixed throttle 13 and flows into the outdoor heat exchanger 16. The low-pressure refrigerant that has flowed into the outdoor heat exchanger 16 absorbs both the heat of the air AR and the heat of the cooling water transferred through the fins 50 and evaporates.
- the cooling water circuit 40 supplies heat absorbed by the refrigerant RF that flows through the refrigerant tube 16a.
- the heat absorption to the refrigerant RF of the refrigerant tube 16a is promoted by the cooling water WT flowing in the water tube 43a.
- a large amount of heat can be absorbed by the refrigerant RF in the refrigerant tube 16a.
- Cooling operation During the cooling operation, the passenger compartment is cooled.
- the cooling operation is activated by a switch operated by a vehicle user.
- the refrigerant circuit 10 is controlled such that the on-off valve 15a is opened, the three-way valve 15b connects the outdoor heat exchanger 16 and the fixed throttle 19, and the compressor 11 is operated.
- the refrigerant flows through the refrigerant circuit 10 as indicated by solid line arrows in FIG.
- the cooling water circuit 40 when the cooling water temperature Tw exceeds the reference temperature, the three-way valve 42 causes the cooling water to flow into the radiator 43, and when the cooling water temperature Tw falls below the reference temperature, the three-way valve 42 passes the cooling water to the bypass passage 44. Controlled to bypass.
- FIG. 4 the flow of the cooling water when the cooling water temperature Tw exceeds the reference temperature is indicated by a broken line arrow.
- the high-pressure refrigerant discharged from the compressor 11 flows into the indoor condenser 12, and heats the air UR. Further, the high-pressure refrigerant flows into the heat exchanger 80 and heats the cooling water WT. As a result, the cooling water circuit 40 can also function as an auxiliary heat dissipation device that takes heat away from the refrigerant circuit 10. Thereafter, the high-pressure refrigerant flows into the outdoor heat exchanger 16 through the passage 14. The high-pressure refrigerant that has flowed into the outdoor heat exchanger 16 further dissipates heat to the air AR blown by the fan 17.
- the cooling water WT heated by the high-pressure refrigerant in the heat exchanger 80 may flow into the radiator 43.
- the heat of the high-pressure refrigerant is radiated to the cooling water WT through the heat exchanger 80 and further radiated from the cooling water WT to the air AR in the radiator 43.
- the heat exchanger 80 provides heat exchange between the cooling water WT flowing into the radiator 43 and the high-pressure refrigerant.
- the heat exchanger 70 provides direct heat dissipation from the high-pressure refrigerant to the air AR, and also provides indirect heat dissipation from the high-pressure refrigerant to the air AR via the cooling water WT.
- Direct heat dissipation is provided by the outdoor heat exchanger 16 using the fins 50.
- Indirect heat dissipation is provided by the radiator 43 using the fins 50. Both the outdoor heat exchanger 16 and the radiator 43 are used during heating, and both the outdoor heat exchanger 16 and the radiator 43 are used during cooling.
- the refrigerant flowing out of the outdoor heat exchanger 16 is decompressed and expanded by the fixed throttle 19.
- the refrigerant flowing out from the fixed throttle 19 flows into the indoor evaporator 20 and absorbs heat from the air UR to evaporate. Thereby, the air UR is cooled.
- the refrigerant flowing out of the indoor evaporator 20 flows into the accumulator 18 and is separated into gas and liquid, and is sucked into the compressor 11 and compressed again.
- the cooling water circuit 40 may be actively used as an auxiliary heat dissipation device that takes heat away from the refrigerant circuit 10. .
- the flow rate of the cooling water WT flowing through the radiator 43 is maximized during the cooling operation.
- FIG. 5 is a flowchart showing the control for shifting to the defrost control executed during the heating operation.
- step S100 it is determined whether frost is generated in the outdoor heat exchanger 16 and defrosting is performed.
- step S200 the air conditioning mode of the air conditioning unit 30 is controlled so as to suppress a change in the air conditioning state during the defrosting control.
- step S300 defrost control is executed.
- step S300 the start of the defrost control and the completion of the defrost control are controlled.
- step S400 the air conditioning unit 30 is returned to the air conditioning mode before the start of the defrosting operation.
- step S500 it is determined whether or not a stop of the air conditioner 1 is requested. If the stop of the air conditioner 1 is not requested, the process returns to step S100, and if the stop of the air conditioner 1 is requested, the control is terminated.
- the heat exchanger 70 is a so-called tank-and-tube heat exchanger.
- the refrigerant tubes 16a and the water tubes 43a are arranged in two rows along the flow direction of the air AR.
- the refrigerant tubes 16a and the water tubes 43a are alternately arranged in both the upstream row and the downstream row. Therefore, the air passage 16b for heat absorption and the air passage 43b for heat dissipation are shared.
- Fins 50 are disposed in the common passages 16b and 43b.
- the fin 50 is joined to the tubes 16a and 43a adjacent thereto.
- a plurality of tubes 16a, tubes 43a, and a plurality of fins 50 are stacked and joined to form a heat exchange section.
- This heat exchange part provides heat exchange between a plurality of, for example, three fluids including the refrigerant RF, the cooling water WT, and the air AR.
- a first tank 16c for collecting or distributing refrigerant and cooling water is disposed at one end side in the longitudinal direction of the plurality of tubes 16a and tubes 43a, and below in the drawing.
- the first tank is also referred to as a refrigerant tank because it accepts the refrigerant and discharges the refrigerant.
- the first tank also provides a connecting portion that guides cooling water from one water tube 43a to another water tube 43a.
- the first tank 16c includes a connection plate member 161 connected to the refrigerant tube 16a and the water tube 43a arranged in two rows, an intermediate plate member 162 fixed to the connection plate member 161, and a first tank member 163. .
- the connection plate member 161 is provided with a through-hole penetrating the front and back at portions corresponding to the plurality of tubes 16a and 43a. In these through holes, a plurality of tubes 16a and 43a are disposed and fixed.
- middle plate member 162 is provided with the through-hole 162a which penetrates the front and back.
- the refrigerant tube 16a is disposed through the through hole 162a.
- the refrigerant tube 16a protrudes from the water tube 43a toward the first tank 16c.
- the first tank member 163 is fixed to the connection plate member 161 and the intermediate plate member 162, thereby forming therein a collection space 163a for collecting refrigerant and a distribution space 163b for distributing refrigerant.
- the first tank member 163 is formed in a W shape when viewed from the longitudinal direction by pressing a flat metal.
- a central portion of the first tank member 163 is joined to the intermediate plate member 162.
- the collective space 163a and the distribution space 163b are partitioned as mutually independent spaces.
- a collecting space 163a is disposed on the upstream side of the air AR, and a distribution space 163b is disposed on the downstream side.
- a plate-like lid member is fixed to both ends in the longitudinal direction of the first tank member 163.
- One end of the distribution space 163b is connected to an inlet pipe 164 through which the refrigerant flows.
- An outlet pipe 165 for allowing the refrigerant to flow out is connected to one end of the collective space 163a.
- a second tank 43c for collecting or distributing refrigerant and cooling water is disposed on the other end side in the longitudinal direction of the plurality of tubes 16a and tubes 43a, and in the upper part of the drawing.
- the second tank is also called a water tank because it is responsible for receiving cooling water and discharging cooling water.
- the second tank also provides a connecting portion that guides the refrigerant from one refrigerant tube 16a to another refrigerant tube 16a.
- the second tank 43c basically has the same configuration as the first tank 16c.
- the second tank 43 c includes a connection plate member 431, an intermediate plate member 432, and a second tank member 433.
- a portion of the intermediate plate member 432 corresponding to the water tube 43a is provided with a through hole 432a penetrating the front and back.
- a water tube 43a is disposed through and fixed to the through hole 432a.
- the second tank member 433 forms a collecting space 433a for collecting cooling water and a distributing space 433b for distributing cooling water.
- a distribution space 433b is disposed on the upstream side of the air AR, and a collective space 433a is disposed on the downstream side.
- a plate-like lid member is fixed to both ends of the second tank member 433 in the longitudinal direction.
- An inlet pipe 434 through which cooling water flows is connected to one end of the distribution space 433b.
- An outlet pipe 435 through which cooling water flows out is connected to one end of the collective space 433a.
- a space CNC providing a communication portion is formed between the intermediate plate members 162 and 432 and the connection plate members 161 and 431.
- the intermediate plate members 162 and 432 are formed with a plurality of recessed portions 162b and 432b.
- the plurality of recesses 162b and 432b are formed by the tubes 43a and 16a between the intermediate plate members 162 and 432 and the connection plate members 161 and 431 by fixing the intermediate plate members 162 and 432 to the connection plate members 161 and 431, respectively.
- a plurality of spaces CNC communicated with each other is formed.
- the space CNC formed between the intermediate plate member 162 and the connection plate member 161 allows two water tubes 43a arranged in two rows in the flow direction of the air AR to communicate with each other.
- a space CNC formed between the intermediate plate member 432 and the connection plate member 431 allows two refrigerant tubes 16a arranged in two rows in the flow direction of the air AR to communicate with each other.
- the refrigerant RF and the cooling water WT flow as counterflows in most parts of the heat exchanger 70.
- Solid line arrows indicate the flow of the refrigerant RF.
- Dashed arrows indicate the flow of the cooling water WT.
- the refrigerant RF flows into the distribution space 163b of the first tank 16c via the inlet pipe 164, and flows into the refrigerant tube 16a in the downstream row.
- the refrigerant flows from the bottom to the top in the drawing in the refrigerant tubes 16a in the downstream row.
- the refrigerant that has flowed out of the refrigerant tube 16a in the downstream row flows into the refrigerant tube 16a in the upstream row through the space CNC of the second tank 43c.
- the refrigerant flows from the upper side to the lower side of the refrigerant tube 16a in the upstream row.
- the refrigerant that has flowed out of the refrigerant tube 16a in the upstream row flows out from the outlet pipe 165 after collecting in the collecting space 163a of the first tank 16c. Therefore, in the heat exchanger 70, the refrigerant flows in a U-turn shape from the downstream row to the upstream row.
- the cooling water WT flows into the distribution space 433b of the second tank 43c via the inlet pipe 434, and flows into the upstream water tube 43a.
- the cooling water flows from the top to the bottom in the drawing in the water tube 43a in the upstream row.
- the refrigerant that has flowed out of the upstream water tube 43a flows into the downstream water tube 43a through the space CNC of the first tank 16c.
- the cooling water flows from the bottom to the top of the water tube 43a in the downstream row.
- the cooling water that has flowed out of the water tube 43a in the downstream row flows out from the outlet pipe 435 after collecting in the collecting space 433a of the second tank 43c. Therefore, in the heat exchanger 70, the cooling water flows in a U-turn shape from the upstream row to the downstream row.
- the refrigerant tube 16a and the water tube 43a are arranged next to one refrigerant tube 16a so that one water tube 43a is located via the fin 50.
- This arrangement is effective for efficiently transferring the heat supplied from the water tube 43a to the frost growing in the vicinity of the refrigerant tube 16a.
- one refrigerant tube 16a is disposed between the two water tubes 43a.
- one water tube 43a is disposed between the two refrigerant tubes 16a.
- the refrigerant tubes 16a and the water tubes 43a are alternately arranged at least in the upstream row.
- the refrigerant tubes 16a and the water tubes 43a can be alternately arranged in the downstream row.
- the air passage 16b for the refrigerant tube 16a to absorb heat and the air passage 43b for the water tube 43a to radiate heat are provided by a common air passage. For this reason, the frost which grew in the vicinity of the refrigerant
- coolant tube 16a can be efficiently defrosted with the heat of the water tube 43a.
- the refrigerant tube 16a allows the low-temperature medium CMD to flow during the heating operation.
- a low-pressure refrigerant in the refrigerant circuit 10 may be used as an example.
- the water tube 43a flows a high-temperature medium HMD that is higher in temperature than the low-temperature medium CMD during the heating operation.
- the cooling water WT in the cooling water circuit 40 may be used as an example.
- the high temperature of the high-temperature medium HMD is caused by the heat supplied from the high-pressure refrigerant in the refrigerant circuit 10 via the heat exchanger 80. Therefore, the high temperature of the high-temperature medium HMD is also given by the refrigerant circuit 10 in the same way as the low temperature of the low-temperature medium CMD.
- frost adheres to the surfaces of the refrigerant tubes 16a and the fins 50 and tries to grow.
- the high-temperature medium HMD flows through the water tube 43a, frost adhesion on the constituent members of the heat exchanger 70 such as the tubes 16a and 43a and the fins 50 and the growth of frost are suppressed during the heating operation. .
- the temperature of the high-temperature medium HMD at the time of the defrosting operation is a temperature at which the large frost mass is melted, for example, 60 ° C. or more.
- a sufficient amount of cooling water is supplied to the water tube 43a in order to supply an amount of heat necessary for melting the frost mass.
- the refrigerant tube 16a and the water tube 43a are thermally coupled via the fins 50.
- the fins 50 are used by the refrigerant tube 16a and the water tube 43a.
- the heat exchanger 70 can provide a wide heat exchange area between the refrigerant
- the heat supplied from the high-pressure refrigerant in the refrigerant circuit 10 is supplied to the heat exchanger 70 as an evaporator of the refrigerant circuit 10.
- frost formation is suppressed and defrosting is improved by the refrigerant circuit 10 without depending only on the external heat source HS other than the refrigerant circuit 10.
- the radiator 43 supplies heat to the outdoor heat exchanger 16 when the outdoor heat exchanger 16 absorbs heat in order to suppress the adhesion of frost to the outdoor heat exchanger 16. As a result, frost adhesion and growth on the heat exchanger 70 are suppressed.
- the expansion valve 213 is controlled to a small opening that functions as a throttle during heating, and is controlled to a large opening during cooling.
- the heat exchanger 80 is provided downstream of the indoor condenser 12 in the refrigerant circuit 10. Instead, in this embodiment, a heat exchanger 80 is provided upstream of the indoor condenser 12 as shown in FIG. In this configuration, the high-pressure refrigerant immediately after being discharged from the compressor 11 is supplied to the heat exchanger 80.
- the heat of the high-pressure refrigerant is taken out by the heat exchanger 80 and supplied to the heat exchanger 70. Instead, in this embodiment, as shown in FIG. 13, heat of the intermediate pressure refrigerant having an intermediate pressure between the high pressure refrigerant in the condenser and the low pressure refrigerant in the evaporator is taken out in the heat exchanger 80.
- the refrigerant circuit 10 includes a compressor 411 having a gas injection port.
- the compressor 411 sucks the intermediate pressure refrigerant from the gas injection port.
- the refrigerant circuit 10 includes a decompressor 413 and a gas-liquid separator 422 downstream of the indoor condenser 12.
- the decompressor 413 decompresses the high-pressure refrigerant to an intermediate-pressure refrigerant.
- the intermediate pressure refrigerant is further decompressed to a low pressure refrigerant by the expansion valve 213.
- the gas-liquid separator 422 separates the gas refrigerant and the liquid refrigerant from the intermediate pressure refrigerant.
- the gas refrigerant is supplied to the heat exchanger 80.
- the gas refrigerant that has passed through the heat exchanger 80 is sucked into the compressor 411.
- the liquid refrigerant is supplied to the heat exchanger 70 via the expansion valve 213.
- the gas refrigerant supplied to the heat exchanger 80 is an intermediate pressure refrigerant.
- the gas refrigerant is a high-temperature refrigerant having a temperature higher than that of the low-pressure refrigerant in the evaporator. Therefore, the heat obtained from the intermediate pressure refrigerant in the heat exchanger 80 can heat the outdoor heat exchanger 16 that functions as an evaporator.
- the heat obtained in the heat exchanger 80 was utilized for both suppression of the frost formation at the time of heating operation, and improvement of the defrost performance at the time of a defrost operation. Instead, in this embodiment, the heat obtained in the heat exchanger 80 is used only for improving the defrosting performance during the defrosting operation.
- the cooling water circuit 40 is configured as shown in FIG.
- the cooling water circuit 40 constitutes a closed circuit including the heat exchanger 80, the heat exchanger 70, and the external heat source HS.
- the cooling water circuit 40 includes a pump 46, a bypass passage 44a, and a three-way valve 47 so that a closed circuit including only the heat exchanger 80 can be configured.
- the cooling water circuit 40 includes a pump 41 and a bypass passage 44b so that a closed circuit including only the heat exchanger 70 and the external heat source HS can be configured.
- the cooling water WT is caused to flow through the closed circuit passing through the heat exchanger 80 and the bypass passage 44a by the pump 46.
- coolant obtained in the heat exchanger 80 is stored in the cooling water WT.
- the heat stored in the cooling water during the normal heating operation is supplied to the heat exchanger 70.
- frost formation when the outdoor heat exchanger 16 absorbs heat is suppressed.
- the cooling water WT is caused to flow through the heat exchanger 80, the heat exchanger 70, and the external heat source HS in order. Thereby, the heat stored in the cooling water WT is supplied to the heat exchanger 70, and defrosting is executed.
- the cooling water WT flows through the bypass passage 44b, the heat exchanger 70, and the external heat source HS.
- the heat of the external heat source HS is supplied to the heat exchanger 70.
- the bypass passage 44 is provided so as to bypass the heat exchanger 70.
- the bypass passage 44 c is provided so as to constitute a closed circuit including only the heat exchanger 80.
- a flow rate adjustment valve 48 is provided in the bypass passage 44c.
- a pump 46 is provided in a closed circuit that passes through the heat exchanger 80 and the bypass passage 44c.
- the pump 46 is operated.
- the flow rate adjustment valve 48 adjusts the flow rate so that a part of the cooling water WT flows through the bypass passage 44c and the remaining part of the cooling water WT flows through the heat exchanger 70 and the external heat source HS.
- coolant obtained in the heat exchanger 80 is stored in the cooling water WT.
- a part of the heat obtained in the heat exchanger 80 is supplied to the heat exchanger 70.
- frost formation is suppressed not only by the heat of the external heat source HS but also by the heat obtained in the heat exchanger 80.
- the cooling water WT is caused to flow through the heat exchanger 80, the heat exchanger 70, and the external heat source HS in order. Thereby, the heat stored in the cooling water WT is supplied to the heat exchanger 70, and defrosting is executed.
- the cooling water WT is caused to flow through the heat exchanger 80, the heat exchanger 70, and the external heat source HS in order.
- the heat of the external heat source HS and the heat of the collar multiplier circuit 10 obtained in the heat exchanger 80 are supplied to the heat exchanger 70.
- the heat stored in the cooling water during the normal heating operation is supplied to the heat exchanger 70.
- the bypass passage 44 is provided so as to bypass the heat exchanger 70.
- the cooling water circuit 40 is configured only by a closed circuit.
- the pump 41 is controlled to adjust the flow rate circulating through the cooling water circuit 40.
- the pump 41 is controlled so as to convey the heat obtained in the heat exchanger 80 to the heat exchanger 70.
- the pump 41 is controlled so as to supply the heat stored in the cooling water circuit 40 to the heat exchanger 70.
- the pump 41 is controlled so as to supply heat from the external heat source HS to the heat exchanger 70.
- the pump 41 is controlled so that the heat released from the refrigerant circuit 10 is received by the cooling water WT.
- the cooling water circuit 40 is provided with the external heat source HS.
- a cooling water circuit 40 that does not include the external heat source HS is employed.
- the heat obtained in the heat exchanger 80 can be supplied to the heat exchanger 70 during the heating operation. Further, at the time of defrosting, the heat obtained in the heat exchanger 80 and stored in the cooling water WT can be supplied to the heat exchanger 70.
- a pump is provided in the cooling water circuit 40 in order to circulate the cooling water WT.
- a cooling water circuit 40 in which the cooling water WT circulates naturally is adopted.
- the cooling water circuit 40 constitutes a fluid circuit that can carry the heat obtained by the heat exchanger 80 to the heat exchanger 70.
- the cooling water WT a refrigerant that evaporates in the heat exchanger 80 and condenses in the heat exchanger 70 when the refrigerant circuit 10 is in a heating operation can be used.
- the cooling water circuit 40 can be provided by a heat pipe that conveys the heat of the high temperature part to the low temperature part.
- the cooling water WT conveys the heat of the refrigerant RF obtained in the heat exchanger 80 to the heat exchanger 70 and heats the heat exchanger 70.
- the heat obtained in the heat exchanger 80 can be supplied to the heat exchanger 70 to suppress frost formation.
- the heat obtained from the high-temperature refrigerant in the heat exchanger 80 is mainly used for suppressing frost formation during the heating operation.
- the compressor 11 is stopped and the circulation of the refrigerant in the refrigerant circuit 10 is stopped, the temperature difference between the refrigerant in the heat exchange portion 81 and the refrigerant in the outdoor heat exchanger 16 is rapidly lost.
- frost remains in the heat exchanger 70
- the heat exchanger 70 and the radiator 43 are maintained at a low temperature.
- the heat left in the cooling water WT is supplied from the radiator 43 to the heat exchanger 70, and defrosting is executed by the amount of heat left in the cooling water WT.
- coolant of the refrigerant circuit 10 was supplied to the heat exchanger 70 indirectly via the cooling water WT.
- the heat of the high-pressure refrigerant in the refrigerant circuit 10 may be directly transmitted to the outdoor heat exchanger 16 that functions as an evaporator of the refrigerant circuit 10 and the heat exchanger 70 including the outdoor heat exchanger 16.
- the radiator 43e of the heat exchanger 70 is used as a heat exchange portion 81 for extracting heat from the high-pressure refrigerant.
- the high-pressure refrigerant is supplied to the radiator 43e.
- the components of the heat exchanger 70 are directly warmed by the high-pressure refrigerant.
- the refrigerant that has flowed out of the radiator 43e is introduced into the outdoor heat exchanger 16 via the expansion valve 213. Therefore, the radiator 43e flows the high-pressure refrigerant, that is, the high-temperature refrigerant, and receives heat directly from the high-temperature refrigerant, thereby supplying heat obtained from the high-temperature refrigerant to the heat exchanger 70 and the outdoor heat exchanger 16.
- the radiator 43e disposed adjacent to the outdoor heat exchanger 16 allows the high-temperature refrigerant to flow, the radiator 43e directly receives the heat of the high-temperature refrigerant.
- the heat of the radiator 43e is supplied through air or a member that connects the outdoor heat exchanger 16 and the radiator 43e.
- the heat of the high-pressure refrigerant is directly supplied to the heat exchanger 70.
- frost formation on the heat exchanger 70 is suppressed.
- the heat obtained in the radiator 43e is used only for suppressing frost formation during the heating operation.
- the heat for improving the frost resistance can be supplied only by the refrigerant circuit 10 without depending on the external heat source HS.
- FIG. 20 shows the arrangement of the tubes 16a and 43a of the heat exchanger 70 shown in FIG.
- the high-temperature medium HMD is passed through the water tube 43a.
- a low-temperature medium CMD flows through the refrigerant tube 16a.
- the water tube 43a is disposed upstream of the refrigerant tube 16a with respect to the flow of the air AR. For this reason, the high-temperature medium HMD can be flowed in the upstream part of the heat exchanger where frost easily adheres.
- the high-pressure refrigerant as the high-temperature medium HMD is directly introduced into the radiator 43e of the heat exchanger 70. Instead, in this embodiment, as shown in FIG.
- the intermediate pressure refrigerant is directly introduced into the radiator 43e of the heat exchanger.
- the refrigerant circuit 10 is branched between the indoor condenser 12 and the expansion valve 213.
- the branch passage is provided with a decompressor 23 for intermediate pressure.
- the intermediate pressure refrigerant is supplied to the radiator 43e.
- a decompressor 24 that decompresses the intermediate-pressure refrigerant to a low-pressure refrigerant is provided downstream of the radiator 43e.
- the temperature of the intermediate pressure refrigerant is higher than the temperature of the low pressure refrigerant decompressed by the expansion valve 213. Therefore, the temperature of the intermediate pressure refrigerant in the radiator 43e is higher than the temperature of the low pressure refrigerant in the outdoor heat exchanger 16. Therefore, the outdoor heat exchanger 16 can be heated by the intermediate pressure refrigerant. Even with this configuration, heat for improving the frosting resistance can be supplied only by the refrigerant circuit 10 without depending on the external heat source HS.
- the intermediate pressure refrigerant that has passed through the radiator 43e is decompressed to a low pressure. Instead, in this embodiment, as shown in FIG. 22, the intermediate pressure refrigerant is sucked into the gas injection port of the compressor 411.
- the intermediate pressure refrigerant can be supplied to the radiator 43e without using the decompressor 24.
- coolant tube 16a provided in the heat exchanger 70 and the water tube 43a were thermally connected by the air AR and the fin 50 between them.
- the refrigerant tube 16a and the water tube 43a are in direct contact with each other.
- the refrigerant tube 16a is referred to as a CMD tube 16a
- the water tube 43a is referred to as an HMD tube 43a.
- One CMD tube 16a and one HMD tube 43a are stacked and arranged so as to be adjacent to each other in a direction perpendicular to the flow direction of the air AR. According to this configuration, the heat of the HMD tube 43a is effectively transmitted to the CMD tube 16a. You may arrange
- the HMD tube 43a may be arranged in the CMD tube 16a. According to this configuration, the heat of the HMD tube 43a is effectively transmitted to the CMD tube 16a.
- the CMD tubes 16a and the HMD tubes 43a are arranged side by side so as to constitute a plurality of rows, that is, an upstream row and a downstream row with respect to the flow direction of the air AR.
- the CMD tube 16a and the HMD tube 43a are arranged so as to form a single row with respect to the flow direction of the air AR. Even in this configuration, the frosting performance can be improved by the heat supplied to the HMD tube 43a.
- one CMD tube 16a and one HMD tube 43a are laminated and arranged so as to form a single row in the flow direction of the air AR. ing. Even in this configuration, the frosting performance can be improved by the heat supplied to the HMD tube 43a.
- the CMD tube 16a and the HMD tube 43a are provided by multiple tubes, and the multiple tubes are arranged so as to form a single row with respect to the flow direction of the air AR. . Even in this configuration, the frosting performance can be improved by the heat supplied to the HMD tube 43a.
- the CMD tubes 16a and the HMD tubes 43a are alternately arranged in the upstream row and the downstream row. Instead, in this embodiment, as shown in FIG. 28, only the HMD tubes 43a are arranged in the upstream row, and only the CMD tubes 16a are arranged in the downstream row. According to this structure, the heat
- the fins 50 are arranged so as to connect the upstream row and the downstream row. Instead, in this embodiment, as shown in FIG.
- the fins 50a are arranged in the upstream row, and the fins 50b are arranged in the downstream row.
- the fin 50a of the radiator 43 and the fin 50b of the outdoor heat exchanger 16 are separate bodies.
- the radiator 43 and the outdoor heat exchanger 16 are separate bodies that can be handled separately.
- the outdoor heat exchanger 16 and the radiator 43 are arranged such that the radiator 43 is positioned on the upstream side of the outdoor heat exchanger 16 with respect to the flow of the air AR.
- the heat of the HMD tube 43a is transmitted to the CMD tube 16a and the fins 50b by radiation and heat transfer via the air AR.
- the improvement of frost-proof performance can be aimed at.
- the CMD tubes 16a and the HMD tubes 43a are alternately arranged in the upstream row and the downstream row.
- the CMD tubes 16a and the HMD tubes 43a are alternately arranged only in the upstream row. Only the CMD tubes 16a are arranged in the downstream row. According to this structure, the CMD tube 16a can be reduced in the upstream line. For this reason, frost formation in the upstream line can be suppressed.
- the frost formation in an upstream line can be suppressed with the heat
- the frost that has grown in the upstream row can be effectively melted by the heat of the HMD tubes 43a. Thereby, the improvement of frost-proof performance can be aimed at. (21st Embodiment)
- the heat exchanger 70 and the heat exchanger 80 were comprised separately. Instead, in this embodiment, as shown in FIG. 31, a heat exchanger 70 and a heat exchanger 80 are integrally configured.
- the heat exchanger 70 provides heat exchange between the three media including the air AR, the refrigerant RF, and the cooling water WT.
- the heat exchanger 80 is also provided by the same configuration as the heat exchanger 70.
- the heat exchanger 70 and the heat exchanger 80 are continuously configured by the same component. Both the heat exchanger 70 and the heat exchanger 80 can exchange heat with the air AR. According to this configuration, the heat exchanger 70 and the heat exchanger 80 can be integrated. As a result, the heat pump cycle 2 can be configured compactly.
- the heat exchanger 70 and the heat exchanger 80 are configured as the same tank and tube type heat exchanger as the heat exchanger 70 illustrated in the first embodiment.
- the heat exchanger 70 and the heat exchanger 80 are positioned side by side in a direction perpendicular to the flow direction of the air AR.
- the radiator 43, which is a heat exchange part for the cooling water WT, and the heat exchange part 82 are arranged on the upstream side in the flow direction of the air AR.
- the outdoor heat exchanger 16 and the heat exchange portion 81 that are heat exchange portions for the refrigerant RF are positioned on the downstream side in the flow direction of the air AR.
- the heat exchangers 70 and 80 are provided by an integrally configured second heat exchanger unit 90 that can be handled as an integral unit. At least the outdoor heat exchanger 16 and the heat exchanger 80 constitute a second heat exchanger unit 90.
- the heat exchanger 90 has an upstream portion 91 and a downstream portion 92.
- the radiator 43 and the heat exchange part 82 are provided by the upstream part 91.
- the upstream portion 91 provides the radiator 43 and the heat exchange portion 82 by partitioning the two tanks 93 and 94.
- the outdoor heat exchanger 16 and the heat exchange part 81 are provided by the downstream part 92.
- the downstream portion 92 provides the outdoor heat exchanger 16 and the heat exchange portion 81 by partitioning the two tanks 95 and 96.
- an inlet / outlet 97 for the cooling water WT and an inlet / outlet 98 for the refrigerant RF are shown.
- the doorways 97 and 98 can be arranged on the tanks 93, 94, 95 and 96.
- the entrances 97 and 98 are used as exits or entrances in order to satisfy the performance required for the heat exchangers 70 and 80.
- the second heat exchanger unit 90 is provided with a fixed throttle 13, a bypass passage 14, and an on-off valve 15a to constitute one unit. Therefore, the second heat exchanger unit 90 includes a decompressor, and the decompressor is provided between the heat exchanger 80 and the outdoor heat exchanger 16.
- the heat pump cycle 2 can be configured in a compact manner.
- the fixed throttle 13 is formed by providing a through hole 13 a in the partition wall of the tank 96.
- the heat pump cycle 2 can be configured in a compact manner.
- one unit is configured by mounting an expansion valve 213 on the second heat exchanger unit 90. With this configuration, the heat pump cycle 2 can be configured in a compact manner.
- the tank 94 of the upstream portion 91 is a continuous passage.
- the tank 94 provides a passage of the cooling water circuit 40 that connects the heat exchange portion 82 and the radiator 43.
- a U-turn type flow path is formed in the radiator 43 and the outdoor heat exchanger 16.
- the flow direction of the cooling water WT and the refrigerant RF can be set as a counter flow.
- the outlet of the cooling water WT is provided in the upper tank 93, it is possible to improve the bubble discharge performance.
- a closed circuit of the cooling water circuit 40 is configured in the upstream portion 91. This configuration is suitable for the embodiment shown in FIG.
- Cooling water WT that functions as a working medium for the heat pipe is sealed in the upstream portion 91.
- the cooling water circuit 40 constitutes a heat pipe called a closed circuit type or a circulation type.
- the cooling water WT takes heat from the refrigerant RF in the heat exchange portion 81 in the heat exchange portion 82 and releases heat in the radiator 43.
- the heat released from the radiator 43 warms the outdoor heat exchanger 16 and the components of the radiator 43.
- a partition wall 96 a that partitions the heat exchange portion 81 and the outdoor heat exchanger 16 is provided in the tank 96.
- a through hole 13a is formed in the partition wall 96a.
- the through hole 13a provides a fixed throttle 13 that depressurizes the high-pressure refrigerant and supplies the low-pressure refrigerant.
- a partition wall 96 b that partitions the heat exchange portion 81 and the outdoor heat exchanger 16 is provided in the tank 96.
- the partition wall 96b is provided with a nozzle-like through hole 13b.
- the through hole 13b provides a fixed throttle 13 that depressurizes the high-pressure refrigerant and supplies the low-pressure refrigerant.
- an expansion valve 213 that can be directly attached to the tank 96 is employed.
- a partition wall 96 c that partitions the heat exchange portion 81 and the outdoor heat exchanger 16 is provided in the tank 96.
- a passage 213a is formed in the partition wall 96c.
- the drive unit 213b of the expansion valve 213 is fixed in a liquid-tight manner.
- the drive unit 213b supports the movable valve body 213c.
- the drive unit 213 b and the movable valve body 213 c are inserted into the tank 96 from an opening at one end of the tank 96.
- the drive unit 213b moves the position of the movable valve body 213c in the left-right direction in the drawing.
- the movable valve body 213c changes the opening degree of the passage 213a according to the position.
- the expansion valve 213 can be configured integrally with the heat exchanger 90.
- a cassette type expansion valve 213 is employed.
- the expansion valve 213 includes a cylindrical sleeve 213d extending from the drive unit 213b.
- the sleeve 213 d is disposed in close contact with the inner wall of the tank 96.
- the wall at the tip of the sleeve 213 d provides a partition wall that partitions the heat exchange portion 81 and the outdoor heat exchanger 16 in the tank 96.
- a passage 213a is formed in the wall of the sleeve 213d.
- An opening for introducing a coolant is formed in the outer peripheral wall of the sleeve 213d.
- a movable valve body 213c is supported in the sleeve 213d.
- the expansion valve 213 can be easily assembled to the tank 96.
- a fan 17a for blowing air to the heat exchanger 70 and a fan 17b for blowing air to the heat exchanger 80 are provided.
- the air volume of the fan 17a and the air volume of the fan 17b can be adjusted independently.
- the air volume of the fan 17a and the air volume of the fan 17b are adjusted according to the operation mode of the heat pump cycle 2.
- the air volume of the fan 17b is adjusted to zero (0) or a small air volume.
- the heat exchanger 80 is used as a heat exchanger for heat dissipation, the fan 17b is adjusted to a large air volume.
- the heat exchanger 80 can function as a condenser.
- the heat exchanger 80 can be used not only for improving the anti-frosting performance but also as a part of the condenser.
- the fan 17b may be adjusted to a large air volume when the temperature of the cooling water WT is excessively high. Since the cooling water WT flows through the heat exchange portion 82, heat radiation from the cooling water WT can be promoted by the air AR. As a result, the heat exchanger 80 can be used not only for improving the anti-frosting performance but also for radiating heat from the cooling water circuit 40.
- a common fan 17c for supplying air to both the heat exchanger 70 and the heat exchanger 80 is provided. According to this configuration, the configuration of the heat pump cycle 2 can be simplified.
- hirty-fourth embodiment In this embodiment, as shown in FIG.
- a fan 17d for blowing air to the heat exchanger 70 is provided, but a device for actively blowing air to the heat exchanger 80 is not provided.
- the air AR is blown to the heat exchanger 70 by the plurality of fans 17d.
- the heat exchanger 80 is provided at a site where the flow of the air AR is blocked by the structural member VHB such as a vehicle chassis and a fan shroud.
- the heat exchanger 80 is installed in a portion where the ventilation resistance of the air AR supplied to the heat exchanger 70 is large.
- Means for suppressing the arrival of the air AR to the heat exchanger 80 is provided by a member such as the constituent member VHB.
- the heat exchanger 80 realizes provision of heat for improving anti-frosting performance by mainly providing heat exchange between the refrigerant RF and the cooling water WT. Therefore, heat radiation from the heat exchanger 80 to the air AR is not essential. Therefore, a configuration in which heat radiation from the heat exchanger 80 to the air AR is limited can be employed.
- the plurality of embodiments described above disclose a plurality of configurations for supplying the heat of the high-temperature refrigerant to the outdoor heat exchanger 16. One of them is a configuration in which the heat of the high-temperature refrigerant is indirectly transmitted by the heat exchanger 80 and the radiator 43.
- the heat exchanger 80 can be referred to as a heat receiving heat exchanger that receives the heat of the high-temperature refrigerant and supplies it to the cooling water.
- the other is a configuration in which the heat of the high-temperature refrigerant is directly transmitted by the radiator 43e.
- These heat exchangers 80, 43, and 43e may be used as an example of the auxiliary heat exchanger HEX for taking out the heat of the high-temperature refrigerant and supplying it to the outdoor heat exchanger 16.
- the indoor condenser 12 can be referred to as an indoor heat exchanger in heating applications.
- the indoor evaporator 20 In the cooling application, the indoor evaporator 20 is used. Therefore, the indoor evaporator 20 can be called a utilization side heat exchanger in cooling applications or an indoor heat exchanger in cooling applications. In the following description, a modification of the auxiliary heat exchanger HEX will be described.
- the refrigerant circuit 10 shown in FIGS. 1, 11, and 19 forms a mainstream circuit MP in heating applications.
- a decompressor having a variable opening degree is provided by a fixed throttle 13 and an on-off valve 15a.
- a decompressor having a variable opening degree is provided by the expansion valve 213.
- the outdoor heat exchanger 16 is used as an endothermic heat exchanger.
- the auxiliary heat exchanger HEX is arranged in series with the mainstream circuit MP.
- the high-temperature refrigerant is a high-pressure refrigerant in the refrigerant circuit 10.
- the auxiliary heat exchanger HEX is disposed between the indoor condenser 12 and the expansion valve 213. Therefore, in the illustrated configuration, the heat of the high-temperature refrigerant is extracted from between the indoor condenser 12 and the expansion valve 213 and supplied to the heat exchanger 70, that is, the outdoor heat exchanger 16.
- the refrigerant circuit 10 illustrated in FIG. 12 includes an auxiliary heat exchanger HEX between the compressor 11 and the indoor condenser 12. Therefore, in the illustrated configuration, the heat of the high-temperature refrigerant is extracted from between the compressor 11 and the indoor condenser 12 and supplied to the outdoor heat exchanger 16.
- the auxiliary heat exchanger HEX is disposed between the indoor condenser 12 and the expansion valve 213.
- a decompressor DC having a variable opening degree is disposed between the indoor condenser 12 and the auxiliary heat exchanger HEX.
- the indoor condenser 12, the decompressor DC, the auxiliary heat exchanger HEX, and the outdoor heat exchanger 16 are arranged in the mainstream circuit MP in this order so that the refrigerant flows in this order in the heating application.
- the decompressor DC is used to maintain the high pressure in the indoor condenser 12. Further, the decompressor DC is used to adjust the temperature of the high-temperature refrigerant in the auxiliary heat exchanger HEX in the auxiliary heat exchanger HEX.
- the decompressor DC can also be called a pressure regulator that maintains a high pressure for heating use in the indoor condenser 12 and adjusts the temperature of the auxiliary heat exchanger HEX.
- the pressure reducer DC can be provided by an expansion valve or a throttle.
- the refrigerant that has passed through the auxiliary heat exchanger HEX can be supplied to the compressor 11 and sucked after being decompressed by the expansion valve 213.
- the outdoor heat exchanger 16 is used as a heat radiation heat exchanger.
- the high-temperature refrigerant can be supplied to the auxiliary heat exchanger HEX by controlling the expansion valve 213 so that the high-temperature refrigerant discharged from the compressor 11 reaches the auxiliary heat exchanger HEX.
- the high temperature refrigerant is supplied to the auxiliary heat exchanger HEX and the auxiliary heat exchanger HEX is used in both applications. Can do.
- the compressor 11, the indoor condenser 12, the expansion valve 213, and the outdoor heat exchanger 16 constitute the mainstream circuit MP.
- the auxiliary heat exchanger HEX supplies the heat obtained from the high-temperature refrigerant upstream or downstream of the indoor condenser 12 to the outdoor heat exchanger 16. According to this configuration, heat can be obtained from the high-temperature refrigerant with a simple configuration.
- the refrigerant circuit 10 illustrated in FIG. 13 includes a compressor 411.
- the compressor 411 has a two-stage compression mechanism.
- the gas injection port PT is a suction port for the second-stage compression mechanism, that is, a suction port for intermediate pressure.
- a shunt circuit BP is formed between the decompressor 413 and the expansion valve 213 and between the gas injection port PT.
- the auxiliary heat exchanger HEX is arranged in series on the shunt circuit BP.
- a refrigerant having an intermediate pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigerant circuit 10 flows through the shunt circuit BP. Therefore, in the illustrated configuration, the heat of the high-temperature refrigerant is extracted from the shunt circuit BP and supplied to the outdoor heat exchanger 16.
- the refrigerant circuit 10 illustrated in FIG. 22 includes a decompressor 23 in the shunt circuit BP.
- the auxiliary heat exchanger HEX is arranged in series on the shunt circuit BP.
- this embodiment includes an on-off valve VL that opens and closes the shunt circuit BP.
- the on-off valve VL is provided on the downstream side of the auxiliary heat exchanger HEX.
- the on-off valve VL can intermittently supply the high-temperature refrigerant to the auxiliary heat exchanger HEX.
- the on-off valve VL is controlled to be in an open state for heating applications, and is controlled to be in a closed state for cooling applications. By controlling the on-off valve VL, the temperature of the high-temperature refrigerant in the auxiliary heat exchanger HEX can be adjusted.
- the on-off valve VL may be provided on the upstream side of the auxiliary heat exchanger HEX.
- the on-off valve VL can be employed in the configuration of FIG. (Thirty-seventh embodiment)
- the refrigerant circuit 10 shown in FIG. 21 forms a shunt circuit BP in heating applications.
- one end of the shunt circuit BP that is, the inlet end is communicated between the indoor condenser 12 and the outdoor heat exchanger 16.
- the other end of the shunt circuit BP that is, the outlet end communicates between the outdoor heat exchanger 16 and the compressor 11.
- the shunt circuit BP is formed in parallel with the outdoor heat exchanger 16 without including the compressor 11.
- the auxiliary heat exchanger HEX is provided in series on the shunt circuit BP. Therefore, the auxiliary heat exchanger HEX can communicate between the outdoor heat exchanger 16 and the compressor 11.
- a decompressor 24 is provided between the auxiliary heat exchanger HEX and the compressor 11. In heating applications, the decompressor 24 is adjusted to a narrow opening for decompressing the refrigerant. In the cooling application, the decompressor 24 is adjusted to an opening degree for supplying the high-temperature refrigerant to the auxiliary heat exchanger HEX, for example, fully open.
- one end of the shunt circuit BP communicates with a high pressure portion between the compressor 11 and the outdoor heat exchanger 16.
- the other end of the shunt circuit BP communicates with the outdoor heat exchanger 16 and the indoor condenser in the cooling application, that is, the indoor evaporator 20. Therefore, in the cooling application, the high-temperature refrigerant can flow in parallel to the outdoor heat exchanger 16 and the auxiliary heat exchanger HEX.
- the refrigerant that has passed through the outdoor heat exchanger 16 and the auxiliary heat exchanger HEX can be supplied to the use-side heat exchanger in the cooling application, that is, the indoor evaporator 20. Therefore, high performance can be obtained in cooling applications.
- the decompressor 23 is provided on the mainstream circuit MP upstream of the auxiliary heat exchanger HEX.
- the decompressor 23 decompresses the refrigerant so as to supply the high-temperature refrigerant to the auxiliary heat exchanger HEX.
- the refrigerant is decompressed by both the decompressor 23 and the expansion valve 213 so that the outdoor heat exchanger 16 functions as an endothermic heat exchanger.
- the decompressor 23 is provided on the mainstream circuit MP upstream of the auxiliary heat exchanger HEX.
- the refrigerant is decompressed only by the decompressor 23 so that the outdoor heat exchanger 16 functions as an endothermic heat exchanger.
- a decompressor 24 is provided downstream of the auxiliary heat exchanger HEX. The decompressor 24 generates a pressure loss so as to supply the high-temperature refrigerant to the auxiliary heat exchanger HEX.
- the refrigerant that has passed through the auxiliary heat exchanger HEX can be supplied to the compressor 11 and sucked after being decompressed by the decompressor 24.
- the high-temperature refrigerant can be supplied to the auxiliary heat exchanger HEX by controlling the decompressor 24 so that the high-temperature refrigerant discharged from the compressor 11 reaches the auxiliary heat exchanger HEX. . Therefore, even when the outdoor heat exchanger 16 is switched between the heat absorption application and the heat dissipation application by the cycle switching mechanism, the high-temperature refrigerant is supplied to the auxiliary heat exchanger HEX and the auxiliary heat exchanger HEX is used in both applications.
- the refrigerant circuit 10 forms a shunt circuit BP for heating applications.
- One end that is, the inlet end of the shunt circuit BP communicates between the compressor 11 and the indoor condenser 12.
- the other end of the shunt circuit BP that is, the outlet end, communicates between the indoor condenser 12 and the outdoor heat exchanger 16.
- the shunt circuit BP is formed in parallel with the indoor condenser 12 without including the compressor 11.
- the auxiliary heat exchanger HEX is provided in series on the shunt circuit BP. Therefore, the auxiliary heat exchanger HEX can communicate between the compressor 11 and the outdoor heat exchanger 12.
- the shunt circuit BP provides a hot gas bypass circuit.
- the high-temperature refrigerant before passing through the indoor condenser 12 can be introduced into the auxiliary heat exchanger HEX.
- decompressors DC are provided both before and after the auxiliary heat exchanger HEX.
- the decompressor DC generates a pressure loss so as to supply the high-temperature refrigerant to the auxiliary heat exchanger HEX.
- the pressure control in the auxiliary heat exchanger HEX can be executed completely independently from the pressure control in the indoor condenser 12.
- the refrigerant that has passed through the auxiliary heat exchanger HEX can be supplied to the compressor 11 and sucked after being decompressed by the expansion valve 213.
- the high-temperature refrigerant is supplied to the auxiliary heat exchanger HEX by controlling the expansion valve 213 and the decompressor DC so that the high-temperature refrigerant discharged from the compressor 11 reaches the auxiliary heat exchanger HEX. can do.
- the refrigerant circuit 10 forms a shunt circuit BP for heating applications.
- One end that is, the inlet end of the shunt circuit BP communicates between the compressor 11 and the indoor condenser 12.
- the other end of the shunt circuit BP that is, the outlet end communicates between the outdoor heat exchanger 16 and the compressor 11.
- the shunt circuit BP is formed in parallel only to the compressor 11.
- the auxiliary heat exchanger HEX is provided in series on the shunt circuit BP. Therefore, the auxiliary heat exchanger HEX can communicate between the compressor 11 and the outdoor heat exchanger 16.
- a decompressor DC is provided in series with the auxiliary heat exchanger HEX.
- the decompressor DC is located upstream of the auxiliary heat exchanger HEX in heating applications. (Forty-second embodiment) As illustrated in FIG. 58, in this embodiment, the decompressor DC is located downstream of the auxiliary heat exchanger HEX in heating applications.
- the high-temperature refrigerant is supplied to the auxiliary heat exchanger HEX in both applications.
- An auxiliary heat exchanger HEX can be used.
- the compressor 11, the indoor condenser 12, the expansion valve 213, and the outdoor heat exchanger 16 constitute the mainstream circuit MP.
- the refrigerant circuit 10 includes a branch circuit BP that branches from upstream or downstream of the indoor condenser 12.
- the auxiliary heat exchanger HEX supplies the heat obtained from the high-temperature refrigerant in the shunt circuit BP to the outdoor heat exchanger 16. According to this configuration, heat can be obtained from the high-temperature refrigerant with a simple configuration. Furthermore, the flow rate of the high-temperature refrigerant can be adjusted while suppressing the influence on the mainstream circuit MP. For example, the shunt circuit BP can be closed to shut off the hot medium.
- At least one of the expansion valve 213, the pressure reducers 23 and 24, the DC, and the on-off valve VL is located upstream or downstream of the auxiliary heat exchanger HEX.
- These expansion valve 213, decompressors 23 and 24, DC, and on-off valve VL may be used as an example of a flow regulator.
- the flow regulator is located upstream or downstream of the auxiliary heat exchanger HEX in both heating and cooling applications.
- the flow controller adjusts the flow rate of the high-temperature refrigerant so that the flow rate of the high-temperature refrigerant in the cooling application is larger than the flow rate of the high-temperature refrigerant in the heating application.
- FIG. 59 shows a control process S0 for temperature control applicable to any one of the heat pump cycles of the above-described embodiments.
- the application of the control process S0 provides a new embodiment.
- the control process S0 provides temperature control means for controlling the temperature supplied to the outdoor heat exchanger 16 by the auxiliary heat exchanger HEX.
- step S0 the control device 100 determines whether the heat pump cycle 2 is operated as a heating application or a cooling application. This determination can be provided by determining whether it is heating. When it is a heating use, it progresses to step S2. When it is a cooling use, it progresses to step S8.
- step S2 the control device 100 sets the opening degree of the flow rate regulator arranged in series with the auxiliary heat exchanger HEX, that is, the heat exchanger 80 or the radiator 43e, to the opening degree for the heating operation.
- the flow rate regulator regulates the flow rate of the high-temperature refrigerant supplied to the heat exchanger 80 or the radiator 43e.
- a parallel circuit of the on-off valve 15a and the fixed throttle 13, the expansion valve 213, the pressure reducers 23 and 24, DC, or the on-off valve VL may be used as an example of the flow regulator.
- the opening for heating applications is a relatively narrow opening. Therefore, the flow rate of the high-temperature refrigerant in the heating application is a relatively small flow rate.
- step S3 the control device 100 determines whether or not the outdoor heat exchanger 16 needs to be defrosted. When defrosting is required, it progresses to below-mentioned step S5. In step S5, a process for increasing the temperature of the auxiliary heat exchanger HEX is executed. When defrosting is unnecessary, it progresses to Step S4. When a plurality of conditions are satisfied, the necessity for defrosting can be positively determined. It can be one of the conditions that the temperature of the heat exchanger 70 is low enough to cause frost. One of the conditions can be that the cooling water temperature Tw is relatively high enough to defrost, that is, exceeds a predetermined defrost determination value.
- step S4 the control device 100 executes a process for temperature control of the auxiliary heat exchanger HEX.
- the temperature T43 in the auxiliary heat exchanger HEX is compared with the target Ttg.
- the process proceeds to step S4.
- the process proceeds to step S5.
- the process proceeds to step S6.
- the target Ttg is set to exceed the temperature T16 of the outdoor heat exchanger 16.
- the target Ttg can be a fixed value or a variable value.
- the target Ttg can be set based on the temperature Tar of the air AR, that is, the temperature of the outside air.
- the target Ttg can be set based on the heat pump operation using the heat pump cycle 2, that is, the duration tHEAT of the heating operation.
- the target Ttg can be set higher than the temperature Tar by a predetermined value. Since Tar> T16 when the outdoor heat exchanger 16 is used as an endothermic heat exchanger, the target Tth is set to satisfy Tth> Tar> T16. As a result, the temperature T43 of the auxiliary heat exchanger HEX is feedback controlled so as to satisfy T43> Tar> T16.
- the target Ttg can be set lower than the temperature Tar by a predetermined value. Since Tar> T16 when the outdoor heat exchanger 16 is used as an endothermic heat exchanger, the target Tth is set to satisfy Tar> Tth> T16. As a result, the temperature T43 of the auxiliary heat exchanger HEX is feedback controlled so as to satisfy Tar> T43> T16.
- the target Ttg can be set in proportion to the duration tHEAT.
- the temperature T43 of the auxiliary heat exchanger HEX is feedback controlled so as to gradually increase in proportion to the duration time tHEAT. In other words, the temperature T43 is feedback controlled so that the difference between the temperature T43 and the temperature T16 increases as frost formation on the outdoor heat exchanger 16 proceeds.
- step S5 the control device 100 executes control for increasing the temperature T43 of the auxiliary heat exchanger HEX.
- the refrigerant circuit 10, such as the compressor 11 and / or the decompressor is controlled so as to increase the temperature of the high-temperature refrigerant in the heat exchanger 80 or the radiator 43e.
- the equipment of the cooling water circuit 40 so as to increase the cooling water temperature Tw of the cooling water WT flowing through the radiator 43. Is controlled.
- step S6 the control device 100 executes control for maintaining the temperature T43 of the auxiliary heat exchanger HEX.
- step S7 the control device 100 executes control for lowering the temperature T43 of the auxiliary heat exchanger HEX.
- the refrigerant circuit 10, such as the compressor 11 and / or the decompressor is controlled so as to lower the temperature of the high-temperature refrigerant in the heat exchanger 80 or the radiator 43e.
- the equipment of the cooling water circuit 40 so as to lower the cooling water temperature Tw of the cooling water WT flowing through the radiator 43. Is controlled.
- step S8 the control apparatus 100 sets the opening degree of the flow rate regulator arranged in series with the auxiliary heat exchanger HEX, that is, the heat exchanger 80 or the radiator 43e, to the opening degree for the cooling operation.
- the opening for cooling applications is a relatively large opening. Therefore, the flow rate of the high-temperature refrigerant in the cooling application is a relatively large flow rate.
- the flow rate regulator sets the opening degree for the cooling purpose to be larger than the opening degree for the heating purpose. In other words, the flow rate regulator makes the flow rate of the high-temperature refrigerant in the cooling application larger than the flow rate of the high-temperature refrigerant in the heating application.
- step S9 the control device 100 executes a cooling operation for cooling use.
- the cycle switching device (15a, 15b) is controlled, and the indoor evaporator 20 is used as a use side heat exchanger.
- the temperature T43 is feedback-controlled so that T43> T16, so that frost growth can be suppressed and / or frost can be removed. Further, when the temperature T43 is feedback-controlled so that Tar> T43> T16, heat dissipation from the auxiliary heat exchanger HEX to the air AR is avoided. For this reason, it is possible to suppress frost growth and / or remove frost in the outdoor heat exchanger 16 while maintaining high heating capacity. In addition, a heat transfer path via the radiator 43 is provided between the air AR and the outdoor heat exchanger 16. For this reason, the heat absorption to the outdoor heat exchanger 16 can be promoted.
- control device can be provided by software only, hardware only, or a combination thereof.
- control device may be configured by an analog circuit.
- cooling water or refrigerant is used as the auxiliary medium.
- a fluid that is excellent in heat transportability and can store heat such as oil or gas, may be used.
- the radiator 43 is provided in the cooling water circuit 40.
- a heat exchanger for radiating heat from the cooling water WT by heat exchange between the cooling water WT and the air AR may be provided.
- a heat exchanger for heat dissipation can be provided so as to be in parallel with the radiator 43 and the external heat source HS.
- the heat obtained from the high-temperature refrigerant may be used only to suppress the adhesion of frost to the heat exchanger 70.
- the air passages 16 b and 43 b are provided in both the outdoor heat exchanger 16 and the radiator 43.
- a configuration in which no air passage is provided in the radiator 43 may be employed.
- coolant tube 16a and the water tube 43a can be alternately arrange
- coolant tube 16a and the water tube 43a can be alternately arrange
- coolant tube 16a and the water tube 43a may be arrange
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Abstract
Description
(第1実施形態)
図1において、本開示の第1実施形態によって、車両用の空調装置1が提供される。空調装置1は、本開示を適用したヒートポンプサイクル(HPC)2を備える。ヒートポンプサイクル2は、本開示を適用した熱交換器70および熱交換器80を備える。ヒートポンプサイクル2は、冷媒回路10と、冷却水回路40とを含む。
通常暖房運転時には、車室外の空気ARを熱源として、室内凝縮器12によって空気URを加熱することにより、車室内の暖房が実行される。通常暖房運転は、車両の利用者によって操作されるスイッチによって起動される。冷媒回路10は、開閉弁15aが閉弁し、三方弁15bが室外熱交換器16とアキュムレータ18とを流路20aを介して接続し、圧縮機11が運転するように制御される。これにより、冷媒回路10は、図1の実線矢印に示すように冷媒が流れる冷媒流路に切り替えられる。冷却水回路40は、ポンプ41が所定流量の冷却水を圧送し、三方弁42がラジエータ43とバイパス通路44との両方に冷却水を流すように制御される。冷却水回路40は、図1の破線矢印に示すように冷却水が流れる回路に切り替えられる。
除霜運転時には、冷却水回路40から得られる熱によって室外熱交換器16に付着した霜が解かされる。除霜運転では、制御装置100が圧縮機11の作動を停止させるとともに、ファン17の作動を停止させる。従って、除霜運転時には、通常の暖房運転時に対して、室外熱交換器16へ流入する冷媒流量が減少し、熱交換器70に流入する空気ARの風量が減少する。さらに、制御装置100は、図2の破線矢印に示すように冷却水がラジエータ43を通過するように、三方弁42を切り替える。従って、ラジエータ43の水チューブ43aを流通する冷却水の有する熱がフィン50を介して、室外熱交換器16に伝熱されて、室外熱交換器16の除霜がなされる。つまり、冷却水回路40がもつ熱を有効に利用した除霜が実現される。除霜に利用される熱には、外部熱源HSから供給される廃熱と、冷却水回路40に蓄えられた熱とが含まれる。また、除霜に利用される熱には、暖房運転時に、熱交換器80において冷媒回路10から冷却水回路40に与えられて冷却水回路40に蓄えられた熱が含まれる。
廃熱回収運転時には、外部熱源HSを熱源として、車室内の暖房が実行される。冷却水回路40の熱は、空気ARに放熱することができるが、所定の条件が成立すると、冷却水回路40の熱を冷媒回路10に渡すことにより暖房能力を高める廃熱回収運転が実行される。例えば、暖房運転時に、冷却水温度Twが予め定めた基準温度、例えば60°Cを上回ると、廃熱回収運転を実行することができる。
冷房運転時には、車室内の冷房が実行される。冷房運転は、車両の利用者によって操作されるスイッチによって起動される。冷媒回路10は、開閉弁15aが開き、三方弁15bが室外熱交換器16と固定絞り19とを接続し、圧縮機11が運転されるように制御される。冷媒回路10には、図4の実線矢印に示すように冷媒が流れる。冷却水回路40は、冷却水温度Twが基準温度を上回ると三方弁42が冷却水をラジエータ43へ流入させ、冷却水温度Twが基準温度を下回ると三方弁42が冷却水をバイパス通路44へ迂回させるように制御される。図4では、冷却水温度Twが基準温度を上回った際の冷却水の流れを破線矢印で示している。
(第2実施形態)
以下の説明においては、先行する実施形態からの変更点、相違点を主として説明する。後続の実施形態は、先行する実施形態のいずれかを基礎的形態とする変形例である。上記実施形態では、固定絞り13と開閉弁15aとを用いて熱交換器70に供給される冷媒を高圧冷媒と低圧冷媒とに切替える切替手段を提供した。これに代えて、この実施形態では、図11に示すように、膨張弁213を採用する。膨張弁213は、開度を調節可能な電動型の膨張弁である。膨張弁213は、少なくとも、固定絞り13に相当する小開度から、開閉弁15aの全開開度に相当する大開度にわたる範囲で開度を調節可能である。
(第3実施形態)
上記実施形態では、室内凝縮器12より冷媒回路10における下流に熱交換器80を設けた。これに代えて、この実施形態では、図12に示すように、室内凝縮器12より上流に熱交換器80を備える。この構成では、圧縮機11から吐出された直後の高圧冷媒が熱交換器80に供給される。
(第4実施形態)
上記実施形態では、高圧冷媒の熱を熱交換器80において取り出して熱交換器70に供給した。これに代えて、この実施形態では、図13に示すように、凝縮器における高圧冷媒と蒸発器における低圧冷媒との間の中間圧力をもつ中間圧冷媒の熱を熱交換器80において取り出す。
(第5実施形態)
上記実施形態では、熱交換器80において得られた熱を、暖房運転時の着霜の抑制と、除霜運転時の除霜性能の改善との両方に利用した。これに代えて、この実施形態では、熱交換器80において得られた熱を、除霜運転時の除霜性能の改善だけに利用する。冷却水回路40は、図14に示すように構成される。冷却水回路40は、熱交換器80、熱交換器70、および外部熱源HSを含む閉回路を構成する。さらに、冷却水回路40は、熱交換器80だけを含む閉回路を構成できるように、ポンプ46、バイパス通路44a、および三方弁47を備える。さらに、冷却水回路40は、熱交換器70と外部熱源HSとだけを含む閉回路を構成できるように、ポンプ41およびバイパス通路44bを備える。
(第6実施形態)
上記実施形態では、熱交換器70をバイパスするようにバイパス通路44を設けた。これに代えて、この実施形態では、図15に示すように、熱交換器80だけを含む閉回路を構成するようにバイパス通路44cを設けている。バイパス通路44cには、流量調節弁48が設けられている。熱交換器80とバイパス通路44cとを通る閉回路には、ポンプ46が設けられている。
(第7実施形態)
上記実施形態では、熱交換器70をバイパスするようにバイパス通路44を設けた。これに代えて、この実施形態では、図16に示すように、冷却水回路40を閉回路だけで構成している。ポンプ41は、冷却水回路40を循環する流量を調節するように制御される。
(第8実施形態)
上記実施形態では、冷却水回路40に外部熱源HSを設けた。これに代えて、この実施形態では、図17に示すように、外部熱源HSを備えない冷却水回路40を採用する。この構成においても、暖房運転時には、熱交換器80において得られた熱を熱交換器70に供給することができる。また、除霜時には、熱交換器80において得られ、冷却水WTに蓄えられた熱を熱交換器70に供給することができる。
(第9実施形態)
上記実施形態では、冷却水WTを循環させるために冷却水回路40にポンプを設けた。これに代えて、この実施形態では、図18に示すように、冷却水WTが自然循環する冷却水回路40を採用する。冷却水回路40は、熱交換器80で得られた熱を熱交換器70に運搬することができる流体回路を構成している。冷却水WTとして、冷媒回路10が暖房運転されているときに、熱交換器80において蒸発し、熱交換器70において凝縮する冷媒を使用することができる。冷却水回路40は、高温部の熱を低温部に運搬するヒートパイプによって提供することができる。
(第10実施形態)
上記実施形態では、冷媒回路10の冷媒の熱を、冷却水WTを介して、間接的に熱交換器70に供給した。これに代えて、冷媒回路10の高圧冷媒の熱を、直接的に、冷媒回路10の蒸発器として機能する室外熱交換器16およびそれを含む熱交換器70に伝えてもよい。この実施形態では、図19に示すように、熱交換器70のラジエータ43eを、高圧冷媒から熱を取り出すための熱交換部分81として利用する。高圧冷媒は、ラジエータ43eに供給される。これにより、熱交換器70の構成部品が高圧冷媒によって直接的に暖められる。ラジエータ43eを流出した冷媒は、膨張弁213を経由して室外熱交換器16に導入される。よって、ラジエータ43eは、高圧冷媒、すなわち高温冷媒を流し、高温冷媒から直接に熱を受けることにより、高温冷媒から得られた熱を熱交換器70および室外熱交換器16に供給する補助熱交換器の一例として用いてもよい。
(第11実施形態)
上記実施形態では、熱交換器70のラジエータ43eに、高温媒体HMDとしての高圧冷媒を直接的に導入した。これに代えて、この実施形態では、図21に示すように、中間圧冷媒を熱交換器70のラジエータ43eに直接的に導入する。冷媒回路10は、室内凝縮器12と膨張弁213との間で分岐されている。分岐通路には、中間圧力への減圧器23が設けられている。中間圧冷媒は、ラジエータ43eに供給される。ラジエータ43eの下流には、中間圧冷媒を低圧冷媒に減圧する減圧器24が設けられている。
(第12実施形態)
上記実施形態では、ラジエータ43eを通過した中間圧冷媒を低圧に減圧した。これに代えて、この実施形態では、図22に示すように、中間圧冷媒を、圧縮機411のガスインジェクションポートに吸引させる。この構成によると、減圧器24を用いることなく、ラジエータ43eに中間圧冷媒を供給することができる。
(第13実施形態)
上記実施形態では、熱交換器70に設けられた冷媒チューブ16aと水チューブ43aとを、それらの間の空気ARとフィン50とによって熱的に連結した。これに代えて、この実施形態では、図23に示すように、冷媒チューブ16aと水チューブ43aとを直接的に接触させている。以下、冷媒チューブ16aをCMDチューブ16aと呼び、水チューブ43aをHMDチューブ43aと呼ぶ。
(第14実施形態)
上記実施形態では、CMDチューブ16aとHMDチューブ43aとを並べて配置した。これに代えて、この実施形態では、図24に示すように、CMDチューブ16aとHMDチューブ43aとを多重管によって提供する。図示の例においては、HMDチューブ43aの中に、CMDチューブ16aが配置されている。CMDチューブ16aの中にHMDチューブ43aを配置してもよい。この構成によると、HMDチューブ43aの熱が効果的にCMDチューブ16aに伝達される。
(第15実施形態)
上記実施形態では、空気ARの流れ方向に関して複数の列、すなわち上流列と下流列とを構成するようにCMDチューブ16aとHMDチューブ43aとを並べて配置した。これに代えて、この実施形態では、図25に示すように、空気ARの流れ方向に関して単一の列を構成するように、CMDチューブ16aとHMDチューブ43aとを配置する。この構成においても、HMDチューブ43aに供給される熱によって、耐着霜性能の改善を図ることができる。
(第16実施形態)
この実施形態では、図26に示すように、ひとつのCMDチューブ16aとひとつのHMDチューブ43aとが積層して配置されるとともに、空気ARの流れ方向に関して単一の列を構成するように配置されている。この構成においても、HMDチューブ43aに供給される熱によって、耐着霜性能の改善を図ることができる。
(第17実施形態)
この実施形態では、図27に示すように、CMDチューブ16aとHMDチューブ43aとを多重管によって提供するとともに、空気ARの流れ方向に関して単一の列を構成するように多重管が配置されている。この構成においても、HMDチューブ43aに供給される熱によって、耐着霜性能の改善を図ることができる。
(第18実施形態)
第1実施形態の熱交換器70では、上流列と下流列とにおいてCMDチューブ16aとHMDチューブ43aとを交互に配置した。これに代えて、この実施形態では、図28に示すように、上流列にHMDチューブ43aのみを配置し、下流列にCMDチューブ16aのみを配置している。この構成によると、HMDチューブ43aの熱を、霜が付きやすい上流列に供給することができる。これにより、耐着霜性能の改善を、効果的に図ることができる。
(第19実施形態)
上記実施形態では、上流列と下流列とを連結するようにフィン50を配置した。これに代えて、この実施形態では、図29に示すように、上流列にフィン50aを配置し、下流列にフィン50bを配置している。この実施形態では、ラジエータ43のフィン50aと、室外熱交換器16のフィン50bとが別体である。さらに、ラジエータ43と室外熱交換器16とは、別々に取り扱いが可能な別体である。室外熱交換器16とラジエータ43とは、空気ARの流れに関して、ラジエータ43が室外熱交換器16の上流側に位置するように配置されている。
(第20実施形態)
第1実施形態の熱交換器70では、上流列と下流列とにおいてCMDチューブ16aとHMDチューブ43aとを交互に配置した。これに代えて、この実施形態では、図30に示すように、上流列においてのみ、CMDチューブ16aとHMDチューブ43aとを交互に配置した。下流列には、CMDチューブ16aのみが配置されている。この構成によると、上流列においてCMDチューブ16aを減らすことができる。このため、上流列における着霜を抑制することができる。また、上流列に多くのHMDチューブ43aが配置されるから、HMDチューブ43aの熱によって、上流列における着霜を抑制することができる。また、上流列に多くのHMDチューブ43aが配置されるから、HMDチューブ43aの熱によって、上流列に成長した霜を効果的に融解させることができる。これにより、耐着霜性能の改善を図ることができる。
(第21実施形態)
上記実施形態では、熱交換器70と熱交換器80とを別体に構成した。これに代えて、この実施形態では、図31に示すように、熱交換器70と熱交換器80とを一体的に構成する。熱交換器70は、空気ARと冷媒RFと冷却水WTとを含む3つの媒体の間の熱交換を提供する。この実施形態では、熱交換器80も、熱交換器70と同じ構成によって提供される。熱交換器70と熱交換器80とは、同じ構成部品によって連続的に構成されている。熱交換器70と熱交換器80との両方は、空気ARと熱交換することができる。この構成によると、熱交換器70と熱交換器80とを一体化することができる。この結果、ヒートポンプサイクル2をコンパクトに構成することができる。
(第22実施形態)
この実施形態では、図32に示すように、第2熱交換器ユニット90に、固定絞り13、バイパス通路14、および開閉弁15aを装着することにより、ひとつのユニットを構成している。よって、第2熱交換器ユニット90は、減圧器を含み、減圧器は、熱交換器80と室外熱交換器16との間に設けられている。この構成により、ヒートポンプサイクル2をコンパクトに構成することができる。
(第23実施形態)
この実施形態では、図33に示すように、タンク96の仕切り壁に貫通穴13aを設けることによって固定絞り13を形成した。この構成により、ヒートポンプサイクル2をコンパクトに構成することができる。
(第24実施形態)
この実施形態では、図34に示すように、第2熱交換器ユニット90に、膨張弁213を装着することにより、ひとつのユニットを構成している。この構成により、ヒートポンプサイクル2をコンパクトに構成することができる。
(第25実施形態)
この実施形態では、図35に示すように、上流部分91のタンク94を連続した通路としている。この構成では、熱交換部分82とラジエータ43とを接続する冷却水回路40の通路が、タンク94によって提供される。
(第26実施形態)
この実施形態では、図36に示すように、ラジエータ43および室外熱交換器16において、Uターン型の流路が形成されている。冷却水WTと冷媒RFとの流れ方向を対向流とすることができる。また、冷却水WTの出口が上側のタンク93に設けられるから、気泡の排出性を高めることができる。
(第27実施形態)
この実施形態では、図37に示すように、上流部分91内に冷却水回路40の閉回路を構成している。この構成は、図18に示した実施形態に適している。上流部分91の中には、ヒートパイプの作動媒体として機能する冷却水WTが封入されている。冷却水回路40は、閉回路型または循環型と呼ばれるヒートパイプを構成している。冷却水WTは、熱交換部分82において熱交換部分81の冷媒RFから熱を奪い、ラジエータ43において熱を放出する。ラジエータ43から放出された熱は、室外熱交換器16およびラジエータ43の構成部品を暖める。
(第28実施形態)
この実施形態では、図38に示すように、タンク96内に、熱交換部分81と室外熱交換器16とを仕切る仕切り壁96aが設けられている。仕切り壁96aには、貫通穴13aが開設されている。貫通穴13aは、高圧冷媒を減圧して低圧冷媒を供給する固定絞り13を提供する。
(第29実施形態)
この実施形態では、図39に示すように、タンク96内に、熱交換部分81と室外熱交換器16とを仕切る仕切り壁96bが設けられている。仕切り壁96bには、ノズル状の貫通穴13bが開設されている。貫通穴13bは、高圧冷媒を減圧して低圧冷媒を供給する固定絞り13を提供する。
(第30実施形態)
この実施形態では、図40に示すように、タンク96に直接に装着可能な膨張弁213が採用されている。タンク96内に、熱交換部分81と室外熱交換器16とを仕切る仕切り壁96cが設けられている。仕切り壁96cには、通路213aが開設されている。タンク96の端面には、膨張弁213の駆動部213bが液密に固定されている。駆動部213bは、可動弁体213cを支持している。駆動部213bと可動弁体213cとは、タンク96の一端の開口部からタンク96内に挿入されている。駆動部213bは、可動弁体213cの位置を、図中左右方向に移動させる。可動弁体213cは、その位置に応じて、通路213aの開度を変化させる。この構成によると、膨張弁213を熱交換器90と一体的に構成することができる。
(第31実施形態)
この実施形態では、図41および図42に示すように、カセット型の膨張弁213が採用されている。膨張弁213は、駆動部213bから延びる筒状のスリーブ213dを備える。スリーブ213dは、タンク96の内壁に密着して配置される。スリーブ213dの先端の壁は、タンク96内において熱交換部分81と室外熱交換器16とを仕切る仕切り壁を提供する。スリーブ213dの壁には、通路213aが形成されている。スリーブ213dの外周の壁には、冷媒を導入するための開口が形成されている。スリーブ213d内には、可動弁体213cが支持されている。この構成によると、膨張弁213をタンク96に簡単に組み付けることができる。
(第32実施形態)
この実施形態では、図43に示すように、熱交換器70に送風するためのファン17aと、熱交換器80に送風するためのファン17bとが設けられている。ファン17aの風量と、ファン17bの風量とは、独立して調節可能である。ファン17aの風量と、ファン17bの風量とは、ヒートポンプサイクル2の運転モードに応じて調節される。
(第33実施形態)
この実施形態では、図44に示すように、熱交換器70と熱交換器80との両方に送風するための共通のファン17cが設けられている。この構成によると、ヒートポンプサイクル2の構成を簡単にすることができる。
(第34実施形態)
この実施形態では、図45に示すように、熱交換器70に送風するためのファン17dを備えるが、熱交換器80に積極的に送風する装置を備えない。この構成では、熱交換器70には、複数のファン17dによって空気ARが送風される。一方、熱交換器80は、車両のシャーシおよびファンシュラウドなどの構成部材VHBによって空気ARの流れが遮られる部位に設けられている。言い換えると、熱交換器80は、熱交換器70に供給される空気ARの通風抵抗が大きい部位に設置されている。構成部材VHBなどの部材によって、熱交換器80への空気ARの到達を抑制する手段が提供されている。
(第35実施形態)
上述の複数の実施形態には、高温冷媒の熱を室外熱交換器16に供給するための複数の構成が開示される。そのひとつは、熱交換器80とラジエータ43とによって高温冷媒の熱を間接的に伝達する構成である。この場合、熱交換器80は高温冷媒の熱を受けて冷却水に供給する受熱熱交換器と呼ぶことができる。他のひとつは、ラジエータ43eによって高温冷媒の熱を直接的に伝達する構成である。これら熱交換器80、43、43eは、高温冷媒の熱を取り出し室外熱交換器16に供給するための補助熱交換器HEXの一例として用いてもよい。また、室内凝縮器12は、加熱用途における利用側熱交換器の一例として用いても良い。室内凝縮器12は、加熱用途における室内熱交換器と呼ぶことができる。冷却用途においては室内蒸発器20が使用される。よって、室内蒸発器20は冷却用途における利用側熱交換器、または冷却用途における室内熱交換器と呼ぶことができる。以下の説明では、補助熱交換器HEXの変形例を説明する。
(第36実施形態)
図49に示すように、図13に図示した冷媒回路10は、圧縮機411を備える。圧縮機411は、2段階の圧縮機構を有する。ガスインジェクションポートPTは、2段目の圧縮機構の吸入口、すなわち中間圧力の吸入口である。この構成では、減圧器413と膨張弁213との間と、ガスインジェクションポートPTとの間に分流回路BPが形成される。補助熱交換器HEXは、分流回路BP上に直列に配置されている。分流回路BPには、冷媒回路10における高圧冷媒と低圧冷媒との間の中間圧力の冷媒が流れる。よって、図示の構成では、高温冷媒の熱は、分流回路BPから抽出され、室外熱交換器16に供給される。
(第37実施形態)
図52に示すように、図21に図示した冷媒回路10は、加熱用途において分流回路BPを形成する。加熱用途においては、分流回路BPの一端、すなわち入口端は、室内凝縮器12と室外熱交換器16との間に連通している。分流回路BPの他端、すなわち出口端は、室外熱交換器16と圧縮機11との間に連通している。分流回路BPは、圧縮機11を含むことなく室外熱交換器16と並列に形成されている。補助熱交換器HEXは、分流回路BP上に直列に設けられている。よって、補助熱交換器HEXは、室外熱交換器16と圧縮機11との間に連通可能である。
(第38実施形態)
図54に示すように、この実施形態では、減圧器23は、補助熱交換器HEXより上流側の主流回路MP上に設けられている。この構成では、減圧器23だけによって、室外熱交換器16が吸熱熱交換器として機能するように冷媒が減圧される。補助熱交換器HEXの下流には減圧器24が設けられている。減圧器24は、補助熱交換器HEXに高温冷媒を供給するように圧力損失を発生する。
(第39実施形態)
図55に示すように、この実施形態では、冷媒回路10は、加熱用途において分流回路BPを形成する。分流回路BPの一端、すなわち入口端は、圧縮機11と室内凝縮器12との間に連通している。分流回路BPの他端、すなわち出口端は、室内凝縮器12と室外熱交換器16との間に連通している。分流回路BPは、圧縮機11を含むことなく室内凝縮器12と並列に形成されている。補助熱交換器HEXは、分流回路BP上に直列に設けられている。よって、補助熱交換器HEXは、圧縮機11と室外熱交換器12との間に連通可能である。
(第40実施形態)
図56に示すように、この実施形態では、補助熱交換器HEXの前後両方に減圧器DCが設けられている。減圧器DCは、補助熱交換器HEXに高温冷媒を供給するように圧力損失を発生する。この構成によると、補助熱交換器HEXにおける圧力制御を、室内凝縮器12における圧力制御から完全に独立して実行することができる。
(第41実施形態)
図57に図示されるように、この実施形態では、冷媒回路10は、加熱用途において分流回路BPを形成する。分流回路BPの一端、すなわち入口端は、圧縮機11と室内凝縮器12との間に連通している。分流回路BPの他端、すなわち出口端は、室外熱交換器16と圧縮機11との間に連通している。分流回路BPは、圧縮機11だけに並列に形成されている。補助熱交換器HEXは、分流回路BP上に直列に設けられている。よって、補助熱交換器HEXは、圧縮機11と室外熱交換器16との間に連通可能である。補助熱交換器HEXと直列に減圧器DCが設けられている。減圧器DCは、加熱用途において補助熱交換器HEXの上流側に位置している。
(第42実施形態)
図58に図示されるように、この実施形態では、減圧器DCは、加熱用途において補助熱交換器HEXの下流側に位置している。
(第43実施形態)
第43実施形態では、実施形態に適用可能な細部を説明する。図59は、上述した複数の実施形態のいずれかのヒートポンプサイクルに適用可能な温度制御のための制御処理S0を示す。制御処理S0が適用されることにより、ひとつの新しい実施形態が提供される。制御処理S0は、補助熱交換器HEXが室外熱交換器16に供給する温度を制御するための温度制御手段を提供する。
(他の実施形態)
以上、本開示の好ましい実施形態について説明したが、本開示は上述した実施形態に何ら制限されることなく、本開示の主旨を逸脱しない範囲において種々変形して実施することが可能である。上記実施形態の構造は、あくまで例示であって、本開示はこれらの記載の範囲に限定されるものではない。
また、上記実施形態では、室外熱交換器16とラジエータ43との両方に空気通路16b、43bを設けたが、ラジエータ43に空気通路を設けない構成を採用してもよい。また、冷媒チューブ16aと水チューブ43aとは、熱交換器70の全部または一部において交互に配置することができる。また、冷媒チューブ16aと水チューブ43aとは、熱交換器70の上流列の全部または一部において交互に配置することができる。また、冷媒チューブ16aと、水チューブ43aとは、空気ARの流れ方向に関して3列以上の列を構成するように配置されてもよい。
Claims (20)
- 低圧冷媒を吸入し、圧縮することにより、高圧冷媒を供給する圧縮機(11、411)と、
加熱用途において、前記高圧冷媒が供給され、前記高圧冷媒から熱が供給される利用側熱交換器(12)と、
前記加熱用途において、前記高圧冷媒を減圧し前記低圧冷媒を供給する減圧器(13、213)と、
前記加熱用途において、空気と前記低圧冷媒とを熱交換させ、前記低圧冷媒に吸熱させる室外熱交換器(16)と、
前記室外熱交換器に隣接して配置されており、前記加熱用途において、前記圧縮機によって圧縮され前記低圧冷媒より温度が高い高温冷媒から得られた熱を、前記室外熱交換器に供給する補助熱交換器(43、43e、HEX)とを備えるヒートポンプサイクル。 - 前記室外熱交換器(16)は前記空気を流すための空気通路(16b)を備え、
前記補助熱交換器(43、43e、HEX)は前記空気を流すための空気通路(43b)を備える請求項1に記載のヒートポンプサイクル。 - 前記低圧冷媒に吸熱させる吸熱熱交換器として前記室外熱交換器(16)を機能させる前記加熱用途と、前記高温冷媒から空気へ放熱させる放熱熱交換器として前記室外熱交換器(16)を機能させる冷却用途とに、流路を切換えるサイクル切換装置(15a、15b、213)を備え、
前記補助熱交換器(43、43e、HEX)は、前記冷却用途において、前記高温冷媒から得られた熱を前記空気に放熱する請求項2に記載のヒートポンプサイクル。 - 前記冷却用途における前記高温冷媒の流量を前記加熱用途における前記高温冷媒の流量より多くする流量調節器(15a、213、23、24、DC、VL)を備える請求項3に記載のヒートポンプサイクル。
- 前記室外熱交換器(16)と前記補助熱交換器(43、43e、HEX)とは、一体のユニットとして取り扱いが可能な第1熱交換器ユニット(70)を構成している請求項2から請求項4のいずれかに記載のヒートポンプサイクル。
- 前記室外熱交換器(16)は複数の低温媒体チューブ(16a)を備え、
前記補助熱交換器(43、43e、HEX)は複数の高温媒体チューブ(43a)を備え、
前記低温媒体チューブと前記高温媒体チューブとは、前記第1熱交換器ユニット(70)の少なくとも一部において熱的に結合して配置されている請求項5に記載のヒートポンプサイクル。 - 前記低温媒体チューブと前記高温媒体チューブとは、前記空気通路に配置されたフィン(50)を介して熱的に結合している請求項6に記載のヒートポンプサイクル。
- 前記第1熱交換器ユニット(70)は、チューブが一列に配置された上流列と前記空気の流れ方向に関して前記上流列よりも下流側でチューブが一列に配置された下流列とを有し、
前記上流列は前記複数の高温媒体チューブの1群を含む請求項6または請求項7に記載のヒートポンプサイクル。 - 前記上流列はさらに前記複数の低温媒体チューブの1群を含み、
前記1群の前記複数の低温媒体チューブのチューブと、前記1群の前記複数の高温媒体チューブのチューブとが、前記上流列の少なくとも一部において交互に配置されている請求項8に記載のヒートポンプサイクル。 - 前記室外熱交換器(16)と前記補助熱交換器(43、43e、HEX)とは、別体であり、
前記空気の流れに関して、前記補助熱交換器(43、43e、HEX)が前記室外熱交換器(16)の上流側に位置するように配置されている請求項2から請求項4のいずれかに記載のヒートポンプサイクル。 - 前記加熱用途において、前記圧縮機(11)、前記利用側熱交換器(12)、前記減圧器(13、213)、および前記室外熱交換器(16)は主流回路(MP)を構成し、
前記補助熱交換器(43、43e、HEX)は、前記利用側熱交換器の上流または下流における前記高温冷媒から得られた熱を前記室外熱交換器へ供給する請求項1から請求項10のいずれかに記載のヒートポンプサイクル。 - 前記加熱用途において、前記圧縮機(11)、前記利用側熱交換器(12)、前記減圧器(13、213)、および前記室外熱交換器(16)は主流回路(MP)を構成し、
さらに、前記利用側熱交換器の上流または下流から分流する分流回路(BP)を備え、
前記補助熱交換器(43、43e、HEX)は、前記分流回路における前記高温冷媒から得られた熱を前記室外熱交換器へ供給する請求項1から請求項10のいずれかに記載のヒートポンプサイクル。 - 前記補助熱交換器は、前記室外熱交換器への霜の付着を抑制するために、前記室外熱交換器が吸熱しているときに、前記室外熱交換器に熱を供給する請求項1から請求項12のいずれかに記載のヒートポンプサイクル。
- 前記補助熱交換器は、前記高温冷媒から得られた熱を蓄え、蓄えた熱を前記室外熱交換器に供給する補助媒体を有する請求項1から請求項13のいずれかに記載のヒートポンプサイクル。
- 前記補助熱交換器は、前記室外熱交換器に付着した霜を除霜するために、前記室外熱交換器が吸熱した後に、前記補助媒体から前記室外熱交換器に熱を供給する請求項14に記載のヒートポンプサイクル。
- さらに、前記高温冷媒から前記補助媒体へ熱を供給する熱源熱交換器(80)を備える請求項14または請求項15に記載のヒートポンプサイクル。
- 前記室外熱交換器(16)と前記熱源熱交換器(80)とは、一体のユニットとして取り扱いが可能な第2熱交換器ユニット(90)を構成している請求項16に記載のヒートポンプサイクル。
- 前記第2熱交換器ユニット(90)は、前記減圧器(13、213)を含み、
前記減圧器(13、213)は、前記熱源熱交換器(80)と前記室外熱交換器(16)との間に設けられている請求項17に記載のヒートポンプサイクル。 - さらに、前記補助熱交換器と前記熱源熱交換器とを通るように前記補助媒体を循環させる補助媒体回路(40)と、
前記補助媒体回路に設けられ、前記補助媒体に熱を供給する外部熱源(HS)とを備える請求項14から請求項18のいずれかに記載のヒートポンプサイクル。 - 前記補助熱交換器(43e)は、前記高温冷媒を流し、前記高温冷媒から直接に熱を受ける請求項1から請求項13のいずれかに記載のヒートポンプサイクル。
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Also Published As
Publication number | Publication date |
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JP2013139995A (ja) | 2013-07-18 |
JP5920178B2 (ja) | 2016-05-18 |
DE112012005079B4 (de) | 2019-12-19 |
US9605883B2 (en) | 2017-03-28 |
DE112012005079T5 (de) | 2014-09-04 |
US20140318170A1 (en) | 2014-10-30 |
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