WO2013084462A1 - Cycle de pompe à chaleur - Google Patents

Cycle de pompe à chaleur Download PDF

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Publication number
WO2013084462A1
WO2013084462A1 PCT/JP2012/007735 JP2012007735W WO2013084462A1 WO 2013084462 A1 WO2013084462 A1 WO 2013084462A1 JP 2012007735 W JP2012007735 W JP 2012007735W WO 2013084462 A1 WO2013084462 A1 WO 2013084462A1
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WIPO (PCT)
Prior art keywords
heat
heat exchanger
flow rate
temperature
refrigerant
Prior art date
Application number
PCT/JP2012/007735
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English (en)
Japanese (ja)
Inventor
加藤　吉毅
宏太 阪本
Original Assignee
株式会社デンソー
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Publication of WO2013084462A1 publication Critical patent/WO2013084462A1/fr

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00928—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a secondary circuit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00961—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • 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

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. However, they are difficult to properly utilize limited heat sources for frost control and / or 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 that can effectively use a heat source for frost control and / or defrosting.
  • the purpose 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, a use-side heat exchanger that is supplied with high-pressure refrigerant and is supplied with heat from the high-pressure refrigerant, A decompressor that decompresses the refrigerant and supplies the low-pressure refrigerant, an endothermic heat exchanger that exchanges heat between the air and the low-pressure refrigerant, and absorbs heat by the low-pressure refrigerant, and an endothermic heat exchanger, are arranged adjacent to the endothermic heat exchanger.
  • An auxiliary heat exchanger for supplying heat to the heat exchanger, an auxiliary medium circuit for circulating the auxiliary medium to the auxiliary heat exchanger, an external heat source for supplying heat to the auxiliary medium, and a flow rate of the auxiliary medium supplied to the auxiliary heat exchanger And a control device that controls the flow rate regulator to change the flow rate of the auxiliary medium according to the progress of the heat pump operation that absorbs heat from the endothermic heat exchanger and supplies heat to the use side heat exchanger With.
  • the auxiliary medium supplied to the auxiliary heat exchanger supplies heat to the endothermic heat exchanger, heat pumping, that is, heat pump can be promoted.
  • assistant heat exchanger can suppress adhesion of the frost resulting from an endothermic heat exchanger directly or indirectly.
  • the flow rate is large, the effect of promoting the heat pump and the effect of suppressing frost formation can be increased.
  • the flow rate is low, heat can be stored in the auxiliary medium circuit.
  • the heat stored in the auxiliary medium circuit can be used for promoting a heat pump, suppressing frost adhesion, or defrosting.
  • the flow rate of the auxiliary medium supplied to the auxiliary heat exchanger can be changed as the heat pump operation progresses. For this reason, promotion of a heat pump, suppression of frost formation, and further defrosting performance can be improved during the period of heat pump operation.
  • the endothermic heat exchanger and the auxiliary heat exchanger may constitute a heat exchanger unit that can be handled as an integral unit.
  • an endothermic heat exchanger and an auxiliary heat exchanger can be provided by a heat exchanger unit that can be handled as an integral unit.
  • the endothermic heat exchanger may include a plurality of low temperature medium tubes, and 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 in thermal coupling in at least a part of the heat exchanger unit. According to this configuration, since the low temperature medium tube and the high temperature medium tube are thermally coupled, the heat of the high temperature medium tube can be easily supplied 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 for heat exchange with air. According to this configuration, a thermal coupling between the cold medium tube and the hot medium tube can be provided via the fins. Therefore, the heat of the hot medium tube can be reliably supplied to the cold medium tube.
  • the at least one hot medium tube may be located downstream of the cold medium tube in the air flow direction, and may deviate from a position overlapping the cold medium tube along the air flow direction.
  • the at least one hot medium tube may be disposed adjacent to the cold medium tube in a direction orthogonal to the air flow direction. For this reason, the heat of the high-temperature medium tube can be transmitted to the upstream side of the heat exchanger unit.
  • This arrangement of the hot media tube can provide additional advantages by providing fins with louvers. This additional advantage can be provided by a frost resistant edge formed in the fin.
  • the heat exchanger unit includes an upstream row in which the tubes are arranged in a row and a downstream row in which the tubes are arranged in a row downstream from the upstream row in the air flow direction.
  • the upstream row may include a group of a plurality of cold medium tubes and a group of a plurality of hot medium tubes.
  • the tube of the group of plural cold medium tubes and the tube of the group of plural hot medium tubes may be alternately arranged in at least a part of the upstream row. According to this configuration, heat exchange between the low temperature medium tube and the high temperature medium tube can be promoted in the upstream row.
  • the channel cross-sectional area for the endothermic heat exchanger provided by the plurality of cold medium tubes is the channel cross-sectional area for the auxiliary heat exchanger provided by the plurality of hot medium tubes. It may be larger.
  • the effect of improving the performance by expanding the flow channel area can be greater in the endothermic heat exchanger than in the auxiliary heat exchanger. According to this structure, it can contribute to the performance improvement of a heat exchanger unit by the performance improvement of an endothermic heat exchanger.
  • the flow rate regulator bypasses the auxiliary heat exchanger and flows the auxiliary medium
  • the valve device reduces the flow rate flowing to the auxiliary heat exchanger by flowing the auxiliary medium to the bypass path. And may be provided. According to this configuration, it is possible to selectively or simultaneously perform the supply of the auxiliary medium to the auxiliary heat exchanger and the heat storage to the auxiliary medium while circulating the auxiliary medium in the auxiliary medium circuit.
  • control device may decrease the flow rate of the auxiliary medium according to the progress of the heat pump operation. According to this structure, the effect of promotion of a heat pump and suppression of adhesion of frost can be exhibited largely in the initial stage of heat pump operation. Then, since heat storage to the auxiliary medium is performed, the defrosting performance can be improved.
  • the control device may decrease the flow rate of the auxiliary medium according to the decrease in the heat load of the heat pump operation.
  • the flow rate can be reduced as the heat load decreases. For this reason, at the initial stage of the heat pump operation, the effects of promoting the heat pump and suppressing the adhesion of frost can be exerted greatly. Then, since heat storage to the auxiliary medium is performed, the defrosting performance can be improved. For example, when heat pump operation is used for heating, the flow rate can be reduced as the room temperature increases.
  • the control device supplies a large flow rate to the auxiliary heat exchanger before reaching the boundary between rapid heating and stable heating indicated by the temperature or time of the air heated by the use side heat exchanger.
  • the flow regulator may be controlled to supply to After reaching the boundary, the control device may control the flow rate regulator to supply a limited flow rate that is less than the large flow rate to the auxiliary heat exchanger.
  • the heat pump can be promoted and frost adhesion can be suppressed in rapid heating. Thereafter, heat can be stored in the auxiliary medium in stable heating.
  • control device may increase the flow rate of the auxiliary medium according to the progress of the heat pump operation. According to this configuration, the defrosting performance can be improved because heat is stored in the auxiliary medium in the initial stage of the heat pump operation. Then, the effect of promotion of a heat pump and suppression of adhesion of frost can be exhibited greatly.
  • the control device may increase the flow rate of the auxiliary medium according to an increase in the amount of frost formation on the endothermic heat exchanger.
  • the flow rate can be increased as the amount of frost formation increases. For this reason, heat can be stored in the auxiliary medium in the initial stage of the heat pump operation. Then, the effect of promotion of a heat pump and suppression of adhesion of frost can be exhibited greatly.
  • the amount of frost formation can be known from the temperature or pressure of the refrigerant at the outlet of the endothermic heat exchanger. Since the refrigerant temperature or the refrigerant pressure decreases with an increase in the amount of frost formation, the flow rate can be increased with a decrease in the refrigerant temperature or the refrigerant pressure.
  • control device may increase the flow rate of the auxiliary medium in response to a temperature or time indicating an increase in the amount of frost formation on the endothermic heat exchanger. According to this structure, the capability shortage by the increase in the amount of frost formation of an endothermic heat exchanger can be suppressed.
  • control device may increase the flow rate of the auxiliary medium according to a decrease in the refrigerant temperature or refrigerant pressure of the endothermic heat exchanger.
  • the amount of frost formation increases, the refrigerant temperature or the refrigerant pressure can be lowered. Therefore, flow control according to the amount of frost formation becomes possible.
  • the control device may increase the flow rate of the auxiliary medium when the temperature of the auxiliary medium rises.
  • the flow rate to the auxiliary heat exchanger can be increased. Therefore, the amount of heat released from the auxiliary medium can be increased.
  • the temperature of the auxiliary medium that is, the temperature control of the heat source can be realized.
  • control device may increase the flow rate of the auxiliary medium when the temperature of the auxiliary medium is higher than a predetermined temperature than the flow rate of the auxiliary medium when the temperature of the auxiliary medium is lower than the predetermined temperature.
  • the temperature of the auxiliary medium can be controlled so that the temperature of the heat source is controlled to a temperature corresponding to the predetermined temperature.
  • the control device determines the flow rate of the auxiliary medium after determining that the endothermic heat exchanger needs to be defrosted before determining that the endothermic heat exchanger needs to be defrosted.
  • the flow rate of the auxiliary medium may be increased. According to this configuration, the flow rate can be increased so as to defrost the endothermic heat exchanger.
  • control device may increase the flow rate of the auxiliary medium in response to a temperature or time indicating an increase in the amount of frost formation on the endothermic heat exchanger after reaching the boundary.
  • the control device sets the flow rate of the auxiliary medium when the temperature of the auxiliary medium is higher than the predetermined temperature, and the flow rate of the auxiliary medium when the temperature of the auxiliary medium is lower than the predetermined temperature. You may increase more.
  • control device needs to defrost the endothermic heat exchanger after determining that the endothermic heat exchanger needs to be defrosted after reaching the boundary. You may make it increase rather than the flow volume of the auxiliary
  • the control device controls the flow rate controller so as to supply the auxiliary medium to the auxiliary heat exchanger in order to defrost the frost attached to the endothermic heat exchanger after the heat pump operation is finished. May be.
  • the frost adhering to the endothermic heat exchanger can be defrosted by the heat stored in the auxiliary medium. And defrosting can be performed after completion
  • a hot gas device that introduces high-pressure refrigerant into the endothermic heat exchanger may be further provided, and when the control device cannot defrost only with the auxiliary medium, the high-pressure refrigerant is supplied to the endothermic heat exchanger.
  • the high-pressure refrigerant can be introduced into the endothermic heat exchanger when defrosting cannot be performed using only the auxiliary medium. For this reason, defrosting can be performed without depending on only the heat storage in the auxiliary medium.
  • 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 flowchart which shows control of the cooling water circuit of 1st Embodiment. It is a time chart which shows progress of the heat pump driving
  • 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 2 to which the present disclosure is applied.
  • the heat pump cycle 2 includes a heat exchanger 70 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 pump cycle 2 that can effectively use waste heat from a power source to suppress frost on the outdoor heat exchanger 16 and / or perform defrosting.
  • the air conditioner 1 is a device that uses heat pumped from the air by the heat pump cycle 2.
  • 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 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 through the refrigerant circuit 10 is a main medium for drawing up 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 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 can perform a defrosting operation that melts and removes frost attached to the outdoor heat exchanger 16 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 may exchange heat between the air AR and the low-pressure refrigerant, and may be used as an example of an endothermic heat exchanger that absorbs heat from the low-pressure refrigerant.
  • 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 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 radiator 43 stores the cooling water WT that stores heat and supplies the stored heat to the outdoor heat exchanger 16.
  • the cooling water WT may be used as an example of an auxiliary medium.
  • the radiator 43 may be used as an example of an auxiliary heat exchanger disposed adjacent to the outdoor heat exchanger 16.
  • 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.
  • 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 downstream of 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 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.
  • 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 is also referred to as a defrosting medium circuit 40 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 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, and a bypass passage 44 for bypassing the radiator 43 and flowing cooling water.
  • the pump 41 is an electric pump that pumps cooling water to the cooling water circuit 40.
  • 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 pump 41, the three-way valve 42, and the bypass passage 44 may be used as an example of a flow rate regulator that regulates the flow rate of the cooling water WT supplied to the radiator 43.
  • the flow rate adjuster includes a bypass passage 44 that bypasses the radiator 43 and flows the cooling water WT, and a valve device 42 that reduces the flow rate flowing through the radiator 43 by flowing the cooling water WT through the bypass passage 44.
  • the radiator 43 is a heat exchanger for heat dissipation that is disposed in the engine room and exchanges heat between the cooling water WT and the air AR blown from the fan 17.
  • the radiator 43 is configured integrally with the outdoor heat exchanger 16 and constitutes a heat exchanger 70.
  • 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 refrigerant tube 16a and the water tube 43a are adjacent to each other.
  • the water tubes 43a can be positioned on both sides of the refrigerant tube 16a.
  • the refrigerant tubes 16a can be positioned on both sides of the water tube 43a.
  • 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. 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, and 42.
  • 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 controlled by controlling the devices 15a and 15b.
  • the control apparatus 100 provides the control means which controls the flow of the cooling water in a cooling water circuit, and a flow path.
  • 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.
  • 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 WT 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. Further, the control device 100 controls the air conditioner 1 to provide a normal heating operation (HEAT1), a defrosting operation (HOT-WT), or 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. When a predetermined condition is satisfied during the normal heating operation, the operation shifts to the waste heat recovery operation. Further, when the return condition is satisfied, the normal heating operation is resumed.
  • HEAT1 normal heating operation
  • HEAT-WT defrosting operation
  • HEAT2 waste heat recovery operation
  • (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 cooling water at a predetermined flow rate, and the three-way valve 42 flows cooling water through 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. 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.
  • cooling water circuit 40 since the cooling water WT flows into the bypass passage 44, heat dissipation from the cooling water to the refrigerant and heat absorption from the refrigerant to the cooling water in the heat exchanger 70 are suppressed. In other words, the thermal mutual influence relationship between the cooling water and the refrigerant is suppressed. As a result, heat supplied from the external heat source HS is stored in the cooling water circuit 40.
  • (B) Defrosting operation (HOT-WT) 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. Accordingly, the heat of the cooling water flowing through the water tube 43 a of the radiator 43 is supplied to the heat exchanger 70.
  • heat is transferred to the outdoor heat exchanger 16 through the fins 50 to defrost the outdoor heat exchanger 16. 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.
  • 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 flowing into the outdoor heat exchanger 16 absorbs both the heat of the air AR and the heat of the cooling water WT 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, heats the air UR, flows into the heat exchanger 80, and heats the cooling water WT. 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 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 When the refrigerant circuit 10 is in cooling operation, that is, when the outdoor heat exchanger 16 functions as a condenser, the cooling water circuit 40 may be used as an auxiliary heat radiating device that takes heat away from the refrigerant circuit 10. For example, the flow rate of the cooling water WT flowing through the radiator 43 is maximized during the cooling operation. Thereby, discharge
  • 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, 16b 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 distribution space 433b for distributing cooling medium.
  • 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.
  • the low temperature medium CMD is a low pressure refrigerant in the refrigerant circuit 10.
  • 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 high temperature medium HMD is the cooling water WT in the cooling water circuit 40. Due to the low temperature medium CMD, frost adheres to the surfaces of the refrigerant tubes 16a and the fins 50 and tries to grow.
  • 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 control device 100 adjusts the flow rate of the cooling water WT to the radiator 43 according to the heat load of the air conditioner 1 that is a heat utilization device in the heating operation.
  • the control device 100 controls the three-way valve 42 so that the flow rate of the cooling water WT flowing through the radiator 43 increases as the heat load increases.
  • the control device 100 causes the cooling water WT to flow through the radiator 43 when the heat load exceeds a predetermined value and executes the waste heat recovery operation HEAT2, and when the heat load falls below the predetermined value,
  • the cooling water WT is flowed to perform the normal heating operation HEAT1.
  • the heat load is indicated by, for example, a difference between the temperature to be controlled and the target temperature.
  • the control device 100 executes a control process S610 for controlling the cooling water circuit 40.
  • the step is expressed as S.
  • S611 it is determined whether the heat pump operation HP is in an ON state, that is, whether it is being executed.
  • the process proceeds to S612.
  • S612 the pump 41 is turned on.
  • the cooling water WT flows in the cooling water circuit 40.
  • external heat source control for adjusting the temperature of the external heat source HS is executed.
  • the cooling water temperature Tw is compared with a predetermined threshold temperature, and whether or not the cooling water TW is allowed to flow to the radiator 43 is switched.
  • the amount of heat released from the radiator 43 is adjusted by adjusting the flow rate to the radiator 43 so that the cooling water temperature Tw is maintained in a predetermined temperature range.
  • the coolant temperature Tw is compared with predetermined threshold temperatures Wth1 and Wth2.
  • the threshold temperatures Wth1 and Wth2 provide hysteresis characteristics.
  • the threshold temperature Wth1 is set lower than the threshold temperature Wth2.
  • the threshold temperature Wth1 can be set within a range of 50 ° C to 60 ° C, and the threshold temperature Wth1 is within a range of 60 ° C to 65 ° C. Can be set to
  • the cooling water temperature Tw falls and falls below the threshold temperature Wth2, the cooling water temperature Tw is increased.
  • the process proceeds to subsequent S615 and S616.
  • the heat load of the heat pump operation exceeds a predetermined value.
  • the heat load is an air conditioning load.
  • the determination as to whether the air conditioning load exceeds a predetermined value is also a determination as to whether rapid heating is necessary.
  • the threshold temperature Rth can be a predetermined fixed value, a target temperature in the passenger compartment, or a temperature set based on the target temperature.
  • the process proceeds to S616.
  • the normal heating operation HEAT1 is executed.
  • the three-way valve 42 is switched so that the cooling water WT flows only into the bypass passage 44. Therefore, the heat pump operation is executed using only the air AR as a heat source.
  • the control device 100 increases the flow rate of the cooling water WT flowing through the radiator 43 when the temperature Tw of the cooling water WT rises. According to this configuration, when the temperature of the cooling water WT rises, the flow rate to the radiator 43 increases. Therefore, the amount of heat released from the cooling water WT increases. As a result, the temperature of the cooling water WT, that is, the temperature control of the external heat source HS is realized.
  • FIG. 12 shows changes in the heat pump heat quantity HPQ, the room temperature Tr, and the flow rate Gr of the cooling water WT passing through the radiator 43 after the heat pump operation is started.
  • the solid line indicates this embodiment EMB1.
  • the broken line indicates the comparative example CMP.
  • the heat pump operation is started at time t0.
  • the room temperature Tr is lower than the threshold temperature Rth. Therefore, the control device 100 operates the refrigerant circuit 10 so that the room temperature Tr approaches the threshold temperature Rth, and further, the room temperature Tr is maintained at the threshold temperature Rth.
  • the control device 100 adjusts the flow rate Gr to the maximum value Gr2.
  • the refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT and raises the room temperature.
  • the heat pump heat quantity HPQ rises rapidly.
  • the room temperature Tr also rises rapidly.
  • the heat pump heat quantity HPQ gradually decreases.
  • the flow rate Gr is adjusted to the minimum value Gr1.
  • the minimum value Gr1 can be 0 (zero) or a predetermined small flow rate.
  • the refrigerant circuit 10 absorbs heat mainly from the air AR.
  • the heat pump heat quantity HPQ is stabilized to a value that maintains the room temperature Tr at the threshold temperature Rth.
  • Comparative example CMP shows a case where the flow rate Gr is fixed to the minimum value Gr1. In this case, the heat pump heat quantity HPQ and the room temperature Tr increase slowly. For this reason, the room temperature Tr reaches the threshold temperature Rth at time t2.
  • the cooling water WT is supplied to the radiator 43 at the initial stage of the heat pump operation, in other words, when the heat load is large, the heat of the cooling water circuit 40 is effectively used to assist the start of the heat pump operation. can do.
  • the thermal load is reduced, the flow rate of the cooling water WT flowing through the radiator 43 is reduced and the flow rate of the cooling water WT flowing through the bypass passage 44 is increased, so that the amount of heat stored in the cooling water circuit 40 can be increased. Thereby, the amount of heat for frost suppression and / or defrosting after the heat load is reduced can be stored.
  • FIG. 13 shows a defrosting process S710 executed by the control device 100 after the operation of the vehicle is completed.
  • the defrosting process S710 reduces frost adhering to the outdoor heat exchanger 16, that is, the heat exchanger 70 after the operation of the vehicle is completed, and desirably removes the frost completely.
  • operation can be started from a state with little frost at the time of the next operation start. That is, the rise of the heat pump operation in the next operation is prevented from being hindered due to frost attached to the heat exchanger 70 in the previous operation.
  • S711 it is determined whether or not the operation of the vehicle has ended. Here, it can be determined whether or not the power switch of the vehicle or the ignition switch has been operated to the OFF position. When the operation of the vehicle ends, the process proceeds to S712. In S712, it is determined whether or not defrosting is necessary. For example, it is determined whether or not defrosting is necessary based on the duration of the heat pump operation during the previous operation, the outside air temperature, the temperature of the outdoor heat exchanger 16, the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16, and the like. Can do. When defrosting is required, it progresses to S713.
  • the process proceeds to S714.
  • heat storage defrost HET-WT
  • the pump 14 is operated (ON)
  • the three-way valve 42 is switched to flow the cooling water WT to the radiator 43
  • the fan 17 is stopped (OFF).
  • the heat pump cycle 2 is operated in the state of FIG.
  • the control device 100 absorbs heat from the outdoor heat exchanger 16 and changes the flow rate to the radiator 43 in accordance with the progress of the heat pump operation that supplies heat to the indoor condenser 12. 41, 42).
  • the cooling water WT supplied to the outdoor heat exchanger 16 supplies heat to the outdoor heat exchanger 16, and therefore pumps up heat, that is, promotes a heat pump.
  • the cooling water WT supplied to the outdoor heat exchanger 16 suppresses the adhesion of frost caused by the outdoor heat exchanger 16 directly or indirectly.
  • the flow rate is large, the effect of promoting the heat pump and the effect of suppressing frost formation are large.
  • heat is stored in the cooling water circuit 40.
  • the heat stored in the cooling water circuit 40 can be used for promoting the heat pump, suppressing frost adhesion, or defrosting. According to this configuration, the flow rate of the cooling water WT supplied to the outdoor heat exchanger 16 is changed as the heat pump operation progresses. For this reason, promotion of a heat pump, suppression of frost formation, and the improvement of defrosting performance are achieved during the period of heat pump operation.
  • the control device 100 decreases the flow rate according to the progress of the heat pump operation.
  • the control device 100 decreases the flow rate according to the decrease in the heat load of the heat pump operation.
  • the flow rate is reduced as the room temperature increases.
  • the flow rate decreases as the heat load decreases. For this reason, the effect of promotion of a heat pump and suppression of adhesion of frost is exhibited largely in the initial stage of heat pump operation. Thereafter, heat storage in the cooling water WT is performed, so that the defrosting performance is improved.
  • the control device 100 is a component of the cooling water circuit 40 so as to supply the cooling water WT to the radiator 43 in order to defrost the frost adhering to the outdoor heat exchanger 16 after the heat pump operation ends.
  • the frost adhering to the outdoor heat exchanger 16 is defrosted with the heat stored in the cooling water WT. And defrosting is performed after completion
  • the switching means which switches the refrigerant
  • an expansion valve 213 is employed as shown in FIG.
  • the expansion valve 213 is an electric expansion valve whose opening degree can be adjusted.
  • the opening of the expansion valve 213 can be adjusted at least in a range from a small opening corresponding to the fixed throttle 13 to a large opening corresponding to the fully opened opening of the on-off valve 15a.
  • 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 defrosting after the operation is completed by the heat storage defrosting (HOT-WT).
  • the defrosting after the operation is completed is performed by hot gas defrosting (HOT-GAS) for supplying the high-temperature refrigerant from the refrigerant circuit 10 to the outdoor heat exchanger 16.
  • HET-GAS hot gas defrosting
  • the heat exchanger 70 can be defrosted without depending on the heat of the cooling water circuit 40.
  • the air conditioner 1 can execute the hot gas defrosting (HOT-GAS) illustrated in FIG. 15 in addition to the above embodiment.
  • the control device 100 stops the circulation of the cooling water WT in the cooling water circuit 40 by stopping the pump 41.
  • the refrigerant circuit 10 is operated so as to introduce the high-pressure refrigerant discharged from the compressor 11 directly into the outdoor heat exchanger 16.
  • the on-off valve 15 a is driven to a fully open state so as to introduce high-pressure refrigerant directly into the outdoor heat exchanger 16.
  • the refrigerant that has flowed out of the outdoor heat exchanger 16 is returned to the compressor 11 via the passage 20a.
  • control device 100 drives the air mix door 34 to a position where the passage to the indoor condenser 12 is closed.
  • the fan 32 may be stopped.
  • a hot gas passage for directly introducing the high-pressure refrigerant discharged from the compressor 11 into the outdoor heat exchanger 16 may be provided.
  • the refrigerant discharged from the outdoor heat exchanger 16 may be supplied to the compressor 11 via the indoor evaporator 20.
  • FIG. 16 shows a defrosting process S730 executed by the control device 100 after the operation of the vehicle is completed.
  • the same reference numerals are assigned to the same processes as the defrosting process S710 described above. If it determines with the heat storage amount of the cooling water circuit 40 being insufficient in S713, it will progress to S731.
  • S731 hot gas defrosting (HOT-GAS) is performed.
  • HET-GAS hot gas defrosting
  • the pump 41 is stopped (OFF), and the compressor 11 is operated (ON).
  • hot gas defrosting is performed.
  • This embodiment includes a hot gas device that introduces a high-pressure refrigerant into the outdoor heat exchanger 16.
  • the hot gas device the passage 14 and the on-off valve 15a may be used.
  • an expansion valve 213 or a hot gas passage may be used.
  • the control device 100 controls the hot gas equipment so that the high-pressure refrigerant is introduced into the outdoor heat exchanger 16 when the cooling water WT alone cannot be defrosted.
  • the high-pressure refrigerant is introduced into the outdoor heat exchanger 16 when defrosting cannot be performed only with the cooling water WT. For this reason, defrosting is possible without depending only on the heat storage to the cooling water WT.
  • the flow path of the three-way valve 442 can be configured to pass through both the radiator 43 and the bypass passage 44.
  • a flow rate adjusting valve 45 is provided in 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 flow control valve 45 may be used as an example of a flow controller.
  • 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 heat supplied from the external heat source HS in the cooling water circuit 40.
  • the three-way valve 442 may be used as an example of a flow rate regulator.
  • the control device 100 adjusts the flow rate of the cooling water WT to the radiator 43 according to the heat load of the air conditioner 1 that is a heat utilization device in the heating operation.
  • the control device 100 controls the flow rate adjustment valve 45 so that the flow rate of the cooling water WT flowing through the radiator 43 decreases continuously or stepwise as the heat load increases.
  • the control device 100 increases the opening degree of the flow control valve 45 as the heat load increases. Therefore, the opening degree of the flow control valve 45 is controlled to gradually decrease in the process in which the heat pump operation proceeds and the thermal load gradually decreases. As a result, the flow rate of the cooling water WT flowing through the radiator 43 gradually increases.
  • the flow rate to the radiator 43 is adjusted based on the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 without directly detecting the heat load.
  • the refrigerant temperature Te decreases as the heat pump operation continues and frost formation on the outdoor heat exchanger 16 proceeds. For this reason, the refrigerant temperature Te exhibits a behavior close to a decrease in heat load due to the continuation of the heat pump operation.
  • the refrigerant pressure in the outdoor heat exchanger 16 or the outlet of the outdoor heat exchanger 16 may be used.
  • the refrigerant pressure also decreases as frost formation on the outdoor heat exchanger 16 proceeds.
  • the control device 100 executes a control process S641 for controlling the cooling water circuit 40.
  • the opening degree DV of the flow rate adjustment valve 45 is set based on the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16, and the flow rate adjustment valve 45 is controlled so as to be the opening degree.
  • the refrigerant circuit 10 is controlled such that the room temperature TR approaches and is maintained at a predetermined threshold temperature Rth.
  • the control device 100 feedback-controls the rotation speed of the compressor 11 based on a proportional component that depends on the difference between the room temperature TR and the threshold temperature Rth.
  • the refrigerant in the outdoor heat exchanger 16 absorbs heat necessary for controlling the room temperature TR to the threshold temperature Rth.
  • the refrigerant temperature Te When the outdoor heat exchanger 16 can sufficiently absorb heat, the refrigerant temperature Te is stabilized at a relatively high temperature. However, when the amount of frost on the outdoor heat exchanger 16 increases, the refrigerant temperature Te decreases. Therefore, in the initial stage of the heat pump operation, the refrigerant temperature Te takes a high value, but after the heat pump operation is continued to the extent that frosting occurs, the refrigerant temperature Te takes a low value. Therefore, by setting the opening degree DV based on the refrigerant temperature Te, the opening degree DV corresponding to the progress of the heat pump operation, that is, the flow rate of the radiator 43 can be set.
  • the function f (Te) for setting the opening degree DV based on the refrigerant temperature Te can be given as a composite function of the function f1 and the function f2 illustrated in S641, for example.
  • the function f1 sets the flow rate Gr of the cooling water WT flowing through the radiator 43 according to the refrigerant temperature Te.
  • the function f1 can be set so as to change according to the outside air temperature Tam.
  • the function f1 can be set so that the flow rate Gr decreases as the refrigerant temperature Te increases.
  • the function f1 can be set so that the flow rate Gr increases as the outside air temperature Tam decreases.
  • the plurality of functions f1 shown in the figure can be set for each representative outside air temperature in a region where the outside air temperature Tam is 0 ° C. or less.
  • the function f2 sets the opening degree DV according to the flow rate Gr.
  • the function f2 is set to decrease the opening degree DV as the flow rate Gr increases.
  • the function f2 can be set to reflect the viscosity of the cooling water WT.
  • the function f2 can be set to change according to the outside air temperature Tam that affects the viscosity.
  • the plurality of functions f2 shown in the figure can be set for each representative outside air temperature in a region where the outside air temperature Tam is 0 ° C. or less. In order to correct the functions f, f1, and f2, the cooling water temperature Tw may be used instead of the outside air temperature Tam.
  • a part of the total flow rate of the cooling water circuit 40 flows into the radiator 43 to assist the pumping of heat by the refrigerant circuit 10, and the remainder flows into the bypass passage 44 to the cooling water circuit 40. Run the heat storage.
  • FIG. 19 shows changes in the heat pump heat quantity HPQ, the room temperature Tr, the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 and the flow rate Gr of the cooling water WT passing through the radiator 43 after the heat pump operation is started.
  • the solid line indicates this embodiment EMB4.
  • the broken line indicates the comparative example CMP.
  • the heat pump operation is started at time t0.
  • the room temperature Tr is lower than the threshold temperature Rth. Therefore, the control device 100 operates the refrigerant circuit 10 so that the room temperature Tr approaches the threshold temperature Rth, and further, the room temperature Tr is maintained at the threshold temperature Rth.
  • the control device 100 adjusts the flow rate Gr to the minimum value Gr1.
  • the refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT and raises the room temperature. After time t0, the heat pump heat quantity HPQ rises rapidly. Correspondingly, the room temperature Tr also rises rapidly. As the room temperature Tr approaches the threshold temperature Rth, the heat pump heat quantity HPQ gradually decreases. After the refrigerant temperature Te rapidly decreases to the evaporation temperature, it gradually decreases as the amount of frost attached to the outdoor heat exchanger 16 and the heat exchanger 70 increases. As the refrigerant temperature Te decreases, the flow rate Gr gradually increases from the minimum value Gr1.
  • the refrigerant flow rate decreases and the refrigerant temperature Te slightly increases.
  • the heat pump operation is continued even after time t1.
  • the refrigerant circuit 10 absorbs heat from the air AR and the cooling water WT. For this reason, the amount of frost attached to the outdoor heat exchanger 16 and the heat exchanger 70 gradually increases. Therefore, the refrigerant temperature Te gradually decreases. Therefore, the flow rate Gr gradually increases toward the maximum value Gr2.
  • the heat pump operation is performed by effectively using the heat of the cooling water circuit 40. Can be helped.
  • frost may adhere to the outdoor heat exchanger 16 and the heat exchanger 70 and gradually grow.
  • the flow rate Gr of the cooling water WT flowing through the radiator 43 is increased. For this reason, adhesion of frost during heat pump operation and growth of frost can be suppressed.
  • the cooling water WT is also passed through the bypass passage 44, the amount of heat stored in the cooling water circuit 40 can be increased. Thereby, the calorie
  • finished can be stored.
  • the control device 100 increases the flow rate according to the progress of the heat pump operation. In other words, the control device 100 increases the flow rate according to an increase in the amount of frost on the outdoor heat exchanger 16. Specifically, the control device 100 increases the flow rate according to a decrease in the refrigerant temperature Te or the refrigerant pressure of the outdoor heat exchanger 16. According to this configuration, the flow rate increases as the amount of frost formation increases. For this reason, the heat storage to the cooling water WT is performed at the initial stage of the heat pump operation. Thereafter, the effects of promoting the heat pump and suppressing the adhesion of frost are greatly exhibited. For example, the amount of frost formation can be known from the temperature or pressure of the refrigerant at the outlet of the outdoor heat exchanger 16.
  • the flow rate can be increased with a decrease in the refrigerant temperature or the refrigerant pressure.
  • the heat storage defrost (HOT-WT) and the hot gas defrost (HOT-GAS) are selectively executed. Instead, in this embodiment, a combined defrosting operation (HOT-WT & HOT-GAS) that uses both heat storage defrosting and hot gas defrosting is provided.
  • control device 100 controls the cooling water circuit 40 so as to provide the heat storage defrost.
  • control device 100 controls the refrigerant circuit 10 so as to provide hot gas defrosting.
  • FIG. 21 shows a defrosting process S750 executed by the control device 100 after the operation of the vehicle is completed.
  • S751 it is determined whether the heat storage amount satisfies a predetermined condition.
  • the cooling water temperature Tw is lower than a predetermined threshold temperature Wth3 and the cooling water temperature Tw is higher than the outside air temperature Ta. If the condition is satisfied (Tam ⁇ Tw ⁇ Wth3), the process proceeds to S752. Since the cooling water temperature Tw is lower than the threshold temperature Wth3, it is considered that defrosting using only the cooling water WT is difficult. However, it is considered that the frost can be heated because the cooling water temperature Tw is higher than the outside air temperature Tam. That is, sufficient defrosting is difficult only by heat storage defrosting.
  • S752 combined defrosting (HOT-WT & HOT-GAS) is executed. If the above condition is not satisfied, the process proceeds to S731.
  • hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting.
  • the cooling water WT can be used as a heat source higher than the outside air temperature Tam
  • the heat storage defrost is executed in addition to the hot gas defrost.
  • the heat left in the cooling water WT can be used effectively.
  • two defrosting operations were selectively executed.
  • heat storage defrost, hot gas defrost, and combined defrost are selectively executed.
  • the plurality of defrosting operations are selected according to the amount of heat stored in the cooling water circuit 40.
  • the plurality of defrosting operations are controlled such that hot gas defrosting is additionally or alternatively performed when sufficient defrosting is not possible by heat storage defrosting alone.
  • FIG. 22 shows a defrosting process S760 executed by the control device 100 after the operation of the vehicle is completed.
  • the process proceeds to S751.
  • heat storage defrosting is performed when the amount of stored heat is sufficiently large. Hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting.
  • the cooling water WT can be used as a heat source higher than the outside air temperature Tam, the heat storage defrost is executed in addition to the hot gas defrost. As a result, the heat left in the cooling water WT can be used effectively.
  • FIG. 23 shows the defrosting process S770 executed by the control device 100 after the operation of the vehicle is completed.
  • the process proceeds to S771.
  • the threshold temperature Wth4 is a temperature lower than the threshold temperature Wth3. Therefore, the plurality of threshold temperatures are set to satisfy Wth4 ⁇ Wth3 ⁇ Wth1 ⁇ Wth2.
  • the threshold temperature Wth4 is a threshold for determining whether or not the cooling water WT can contribute to defrosting even a little.
  • the threshold temperature Wth4 can be set to 0 ° C.
  • heat storage defrosting when the amount of stored heat is sufficiently large, heat storage defrosting is performed. Hot gas defrosting is performed when sufficient defrosting cannot be performed only by heat storage defrosting.
  • the cooling water WT can be used as a heat source higher than the outside air temperature Tam
  • the heat storage defrost is executed in addition to the hot gas defrost.
  • the cooling water WT cannot contribute to defrosting, only hot gas defrosting is performed.
  • the fan 17 is stopped when the defrosting operation is performed. Instead, in this embodiment, when the outside air temperature Tam can contribute to defrosting, the fan 17 is operated and the amount of heat of the outside air is used to promote defrosting.
  • FIG. 24 shows the defrosting process S780 executed by the control device 100 after the operation of the vehicle is completed.
  • the above-described S713, S771, and S751 are shown as single steps for determining the amount of heat storage based on the cooling water temperature Tw.
  • S781 it is determined whether or not the outside air temperature Tam can contribute to defrosting.
  • the process proceeds to S782.
  • the fan 17 is operated (ON) to supply outside air to the heat exchanger 70. Thereby, the heat of outside air contributes to raising the temperature of frost.
  • Threshold value Ath can be a fixed value or a variable value.
  • the threshold temperature Ath can be the temperature of the outdoor heat exchanger 16 or the heat exchanger 70 or a refrigerant temperature indicating the temperature.
  • the refrigerant temperature Te at the outlet of the outdoor heat exchanger 16 represents the surface temperature of the outdoor heat exchanger 16. Therefore, the refrigerant temperature Te may be used as the threshold temperature Ath.
  • the cooling water circuit 40 includes the single external heat source HS. Instead, this embodiment includes a plurality of external heat sources. In this embodiment, as shown in FIG. 25, the cooling water circuit 40 is configured such that the battery BT and the cooling water WT can exchange heat.
  • the battery BT and the cooling water WT are thermally coupled directly or indirectly through the temperature control device of the battery BT. For example, the battery BT and the piping of the cooling water WT can be brought into direct contact.
  • the battery BT is provided in parallel with a closed circuit including the external heat source HS and the radiator 43. On the closed circuit, in parallel with the battery BT, a flow rate adjustment valve 46 for flowing the cooling water WT to the battery BT is provided.
  • a temperature sensor 54 that detects a surface temperature representative of the temperature of the battery BT or a cooling water temperature is provided on the surface of the battery BT or a cooling water passage downstream of the battery BT. The temperature detected by the temperature sensor 54 is called the battery temperature Tb.
  • External heat source HS provides the main external heat source.
  • the battery BT also provides an auxiliary external heat source. Cooling water WT takes heat from battery BT and is used to cool battery BT. Cooling water WT is also used to heat battery BT and heat battery BT. According to this configuration, the waste heat of the battery BT can be supplied to the cooling water. As a result, the waste heat of the battery BT can be used for suppressing frost formation and / or defrosting.
  • FIG. 26 shows a defrosting process S790 executed by the control device 100 after the operation of the vehicle is completed. If heat storage defrost is performed in S714, it will progress to S791. In S791, it is determined whether the heat of the battery BT can be further used during the heat storage defrosting. Here, after the operation of the vehicle is finished, the determination as to whether or not the battery BT is charged by an external power source can be used. When the battery BT is charged by an external power source, the battery BT generates heat, so that the heat of charging can be used for defrosting. Moreover, you may utilize determination of whether battery temperature Tb exceeds predetermined threshold temperature Bth. For example, when the battery temperature Tb exceeds the threshold temperature Bth, it can be determined that the heat of the battery BT can be used for defrosting. When the heat of the battery BT can be used for defrosting, the process proceeds to S792.
  • S791 can be configured to proceed to S792 while the battery BT is being charged. Further, S791 may be configured to proceed to S792 after the charging of the battery BT is completed. Further, S791 may be configured to proceed to S792 from when the battery BT is being charged until after the charging is completed. According to these configurations, waste heat during charging can be used for defrosting.
  • the heat of the battery BT is used.
  • the cooling water WT is supplied to the battery BT, the heat of the battery BT is taken out to the cooling water circuit 40, and the heat is supplied to the radiator 43.
  • the battery BT may be provided as shown in FIG.
  • the battery BT is provided in a bypass passage in parallel with the external heat source HS.
  • the flow rate adjusting valve 46 is provided in the bypass passage so as to be positioned in series with the battery BT.
  • the battery BT may be provided as shown in FIG. Also in this configuration, the flow rate of the cooling water WT flowing through the battery BT can be adjusted by the flow rate adjustment valve 46.
  • the battery BT may be provided as shown in FIG.
  • the battery BT is provided in parallel with a closed circuit including the external heat source HS and the radiator 43.
  • a flow rate adjustment valve 46 in parallel with the battery BT and a flow rate adjustment valve 47 in series with the battery BT are provided.
  • the battery BT may be provided as shown in FIG.
  • a flow rate adjustment valve 46 is provided in parallel with the battery BT, and a flow rate adjustment valve 47 is provided in the bypass passage 44.
  • the cooling water WT flows into the bypass passage 44 by opening the flow rate adjustment valve 47.
  • the cooling water WT flows into the radiator 43 by closing the flow rate adjusting valve 47 and opening the flow rate adjusting valve 46.
  • the flow rate adjusting valve 47 is closed and the flow rate adjusting valve 46 is closed, whereby the cooling water WT flows through the battery BT and the radiator 43.
  • the battery BT may be provided as shown in FIG. Also in this configuration, the flow rate of the cooling water WT flowing through the battery BT can be adjusted by the flow rate adjustment valve 46.
  • the cooling water circuit 40 may be provided with a heater core 48 for heating the air UR. The heater core 48 is disposed on the upstream side of the radiator 43. The cooling water circuit 40 is provided with a flow rate adjustment valve 49 in parallel with the heater core 48.
  • the control device 100 controls the flow rate adjustment valve 49 to supply the cooling water WT to the heater core 48 when the cooling water temperature Tw exceeds a predetermined threshold temperature.
  • the heat of the cooling water WT can be directly used for air conditioning.
  • the cooling water WT after passing through the heater core 48 is supplied to the radiator 43, the amount of heat supplied to the radiator 43 can be adjusted.
  • the amount of heat generated by the external heat source HS is large, the amount of heat given to the radiator 43 can be adjusted to an appropriate amount by heat radiation from the heater core 48.
  • a heater core 48 may be provided in parallel with the external heat source HS.
  • the cooling water circuit 40 includes a heater core 48 provided in a passage that bypasses the radiator 43.
  • the control device 100 controls the cooling water circuit 40 so that the cooling water WT flows through the heater core 48 when the amount of heat supplied from the external heat source HS is large. Even in this configuration, the excessive heat stored in the cooling water circuit 40 can be used in the heater core 48.
  • the control device 100 executes the waste heat recovery operation HEAT2 when the heat load of the air conditioner 1 exceeds a predetermined value, and the heat load reaches a predetermined value. When it falls below, normal heating operation HEAT1 was executed. Instead, this embodiment provides continuous or multi-step control over both normal heating and waste heat recovery operations.
  • the control device 100 executes a control process S680 for controlling the cooling water circuit 40.
  • S611 it is determined whether the heat pump operation HP is in an ON state, that is, whether it is being executed.
  • the process proceeds to S681.
  • S681 it is determined whether rapid heating is necessary.
  • S681 it is determined whether it is in the rapid heating state or the stable heating state. For example, it can be determined that the rapid heating state is in a period in which the air conditioner 1 is immediately after startup and the room temperature Tr has not yet reached the target temperature Tset. Thereafter, after the room temperature Tr reaches the target temperature Tset, it can be determined that the room is in the stable heating state.
  • the rapid heating state is in a predetermined time (t0-t1) after the air conditioner 1 is started. After a predetermined time (t0-t1) has elapsed since the air conditioner 1 was started, it can be determined that the stable heating state is present.
  • S682 provides a feedforward control unit that controls the flow rate of the cooling water WT supplied from the cooling water circuit 40 to the radiator 43 in a predictive or feedforward manner.
  • the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is adjusted to the maximum flow rate Gr2. Therefore, the heat pump cycle 2 becomes the waste heat recovery operation HEAT2.
  • Supply of heat from the cooling water circuit 40 to the heat exchanger 70 compensates for a lack of heating capacity.
  • the heat of the cooling water circuit 40 is used for heating in the winter when the temperature of the air AR is low.
  • the power consumption of the compressor 11 for providing the heat pump operation HP is suppressed.
  • the growth of frost in the heat exchanger 70 is suppressed by causing the cooling water WT to flow through the water tube 43a.
  • S613 and S683-S686 provide a feedback control unit that controls the flow rate of the cooling water WT supplied from the cooling water circuit 40 to the radiator 43 in response to a feedback element.
  • the feedback control unit increases the flow rate from the base value in response to a plurality of feedback elements using the limited flow rate Grs for storing heat in the cooling water circuit 40 as a base value.
  • the feedback element may include external heat source information for maintaining the temperature of the external heat source HS at a predetermined value. For example, when the temperature of the external heat source HS is excessive, the flow rate is increased.
  • the feedback element can include information for defrosting in the heat exchanger 70. For example, when defrosting is required, the flow rate is increased.
  • the feedback element can include information indicating an excess or deficiency of capacity for heat pump operation. For example, if the heat pump capacity is insufficient, the flow rate is increased.
  • S613 the flow rate is adjusted so as to control the temperature of the external heat source HS.
  • S613 provides means for increasing the flow rate Gr of the cooling water WT when the cooling water temperature Tw exceeds the predetermined determination values Wth1 and Wth2.
  • S613 is also processing for determining whether or not the amount of heat stored in the coolant circuit 40 is excessive. When the heat storage amount is excessive, the process proceeds to S686 described later. When the heat storage amount is within the appropriate range, the process proceeds to S683.
  • the control device 100 uses a flow rate Gr when the temperature (Tw) of the cooling water WT is higher than the predetermined temperature (Wth1, Wth2), and a flow rate when the temperature (Tw) of the cooling water WT is lower than the predetermined temperature (Wth1, Wth2).
  • Increase (+ Grfb) This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this configuration, the temperature of the cooling water WT is controlled so as to control the temperature of the heat source to a temperature corresponding to the predetermined temperature.
  • defrosting it is determined whether or not defrosting is necessary. When defrosting is required, it progresses to S686. When defrosting is unnecessary, it progresses to S684.
  • 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. It can be one of the conditions that the vehicle is in a state where defrosting can be performed. It can be one of the conditions that the traveling speed of the vehicle is below a predetermined determination value. One of the conditions can be that the vehicle is not operated, for example, that a power switch such as an ignition switch is in the off position.
  • the control device 100 increases the flow rate Gr after determining that the outdoor heat exchanger 16 needs to be defrosted from the flow rate Gr before determining that the outdoor heat exchanger 16 needs to be defrosted (+ Grfb). ).
  • This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this configuration, the flow rate is increased so as to defrost the outdoor heat exchanger 16.
  • the lack of heat pump capability may be determined based on the duration of heat pump operation. As the duration time of the heat pump operation becomes longer, the amount of frost formation on the heat exchanger 70 increases, and the heat pump capacity decreases proportionally.
  • the predetermined time (t0-t3) after the heat pump operation of the refrigerant circuit 10 is started it can be determined that the heat pump capacity is insufficient. After a predetermined time (t0-t3) has elapsed after the start of the heat pump operation, it is possible to affirmatively determine that the heat pump capacity is insufficient.
  • the lack of heat pump capability may be determined based on the temperature of the indoor condenser 12 blown out.
  • TAO necessary blowing temperature
  • a negative determination can be made as to the lack of heat pump capacity. If the blowing temperature of the indoor condenser 12 does not exceed the necessary blowing temperature TAO, an affirmative determination can be made that the heat pump capacity is insufficient.
  • the controller 100 gradually increases the flow rate Gr (+ Grfb) in response to the temperature (Tp, TAO) or time (t0-t3) indicating the increase in the amount of frost on the outdoor heat exchanger 16.
  • This increase amount can be configured to be given after reaching the boundary between rapid heating and stable heating. According to this structure, the capability shortage by the increase in the amount of frost formation of the outdoor heat exchanger 16 can be suppressed.
  • the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is adjusted to the limit flow rate Grs.
  • the flow rate is adjusted stepwise or gradually. For example, when the flow reaches S685 after passing through S682, the flow rate is gradually decreased from the maximum flow rate Gr2 to the limit flow rate Grs.
  • the limited flow rate Grs is a flow rate at which the waste heat of the external heat source HS can be stored in the cooling water circuit 40.
  • the limit flow rate Grs can be the minimum flow rate Gr1.
  • the limit flow rate Grs can be a predetermined value between the minimum flow rate Gr1 and the maximum flow rate Gr2.
  • the control device 100 increases the flow rate (Gr2) before reaching the boundary between rapid heating and stable heating indicated by the temperature (Rth, Tset) or time (t0-t1) of the air UR heated by the indoor condenser 12. Supply. Further, after reaching the boundary, a limited flow rate (Grs, Gr1) smaller than the large flow rate is supplied. According to this structure, promotion of a heat pump and suppression of frost adhesion are achieved in rapid heating. Thereafter, heat is stored in the cooling water WT in stable heating.
  • the flow rate supplied to the radiator 43 by the pump 41 and the three-way valve 42 is increased by the increase amount Grfb.
  • the flow rate is adjusted stepwise or gradually. For example, when the flow reaches S686 after passing through S685, the flow rate is gradually increased from the limit flow rate Grs by the increase amount Grfb.
  • the increase amount Grfb can be set continuously or stepwise according to the feedback element.
  • the increase amount Grfb can be set in proportion to the temperature of the external heat source HS or the heat storage amount of the cooling water circuit 40.
  • the increase amount Grfb can be set proportionally according to the necessity of defrosting.
  • the increase amount Grfb can be set proportionally according to the insufficient amount of heat pump capacity.
  • the increase amount Grfb may be gradually increased in proportion to the duration of the heat pump operation.
  • FIG. 36 shows an example of the progress of the heat pump operation.
  • the progress of the heat pump operation can be shown by the change in the room temperature Tr.
  • the progress of the heat pump operation extends over a period in which the room temperature Tr rises toward the target temperature Tset and a period in which the room temperature Tr is maintained near the target temperature Tset.
  • a broken line QP indicates a heat pump heat amount that the refrigerant circuit 10 can exhibit, that is, a potential amount QP.
  • the solid line QU indicates the heat pump heat quantity that the refrigerant circuit 10 actually uses in order to achieve the target temperature Tset, that is, the used quantity QU.
  • a one-dot chain line QS shows an example in which the potential amount QP continues to decrease.
  • a solid line Gr (EMB) indicates a waveform in this embodiment.
  • a broken line Gr (MOD) indicates a waveform according to the modification.
  • the potential amount QP increases rapidly after time t0. Between the time t0 and the time t1, the potential amount QP exceeds the usage amount QU. This is because the maximum flow rate Gr2 is supplied during this period and the amount of frost formation is small. In a process in which the room temperature Tr approaches the target temperature Tset after the time t0, the usage amount QU gradually decreases. At this time, frost gradually adheres to the heat exchanger 70. The potential amount QP gradually decreases mainly due to an increase in the amount of frost formation.
  • Tset target temperature
  • control called stable heating is provided by S611, S681, S613, S683-S686.
  • the flow rate Gr of the cooling water WT is gradually decreased from the maximum flow rate Gr2 to the limit flow rate Grs, and therefore the potential amount QP gradually decreases.
  • the amount of frost on the heat exchanger 70 gradually increases. As a result, the potential amount QP continues to decrease slowly.
  • the room temperature Tr is maintained at the target temperature Tset by gradually increasing the power consumption of the compressor 11.
  • the target temperature Tset is used as a threshold for determining the end of rapid heating.
  • the time (t0-t1) between the time t0 and the time t1 is a predetermined time that defines the rapid heating period. Therefore, the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is decreased in the process in which the room temperature Tr reaches the threshold value Tset, or in the process in which the rapid heating continues for a predetermined time. As indicated by the broken line Gr (MOD), the flow rate Gr may be decreased gradually or stepwise before and after the room temperature Tr reaches the threshold value Tset, or before and after the rapid heating duration reaches a predetermined time.
  • the flow rate Gr is adjusted to the large flow rate Gr2 at least temporarily during the rapid heating period.
  • the flow rate Gr is adjusted to a limited flow rate Grs that is less than the large flow rate Gr2 at least temporarily within the period of stable heating.
  • the flow rate Gr is decreased in a period including the boundary between rapid heating and stable heating, that is, before and after the time t1.
  • the reduction of the flow rate Gr can be performed gradually or stepwise as shown in the figure.
  • the potential amount QP is less than the usage amount QU.
  • the heat pump capability is insufficient. If the heat pump capability is insufficient, the room temperature Tr is not maintained at the target temperature Tset. As a result, the room temperature Tr gradually decreases.
  • the room temperature Tr falls below the threshold value Tp.
  • the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is increased by S684 and S686.
  • an excessive decrease in the potential amount QP as indicated by the one-dot chain line QS is avoided.
  • the potential amount QP and the usage amount QU increase, and the room temperature Tr increases toward the target temperature Tset.
  • the threshold value Tp is used as a threshold value for determining the lack of heat pump capacity.
  • the time (t0-t3) between time t0 and time t3 is a predetermined time that defines the duration of the heat pump operation that is expected to cause a shortage of heat pump capacity. Therefore, the flow rate Gr of the cooling water WT supplied to the heat exchanger 70 is increased in the process in which the room temperature Tr reaches the threshold value Tp or in the process in which the duration of the heat pump operation reaches a predetermined time.
  • the flow rate Gr may be increased before and after the room temperature Tr reaches the threshold value Tp, or before and after the duration of the heat pump operation reaches a predetermined time.
  • the flow rate Gr is adjusted to the limited flow rate Grs at least temporarily during the stable heating period.
  • the flow rate Gr is increased at least temporarily by the increase amount Grfb during the stable heating period.
  • the flow rate Gr is increased in a boundary including a shortage of heat pump capability, that is, a period including before and after time t3. This increase in the flow rate Gr can be performed gradually or stepwise as shown.
  • the cooling water WT having a large flow rate Gr2 is supplied to the heat exchanger 70 in the initial stage of the heat pump operation. Therefore, the heat pump capability can be supplemented by the cooling water WT. In particular, the heating capacity at low temperatures is supplemented. Further, excessive power consumption by the compressor 11 is suppressed. Moreover, the frost on the heat exchanger 70 can be suppressed.
  • the flow rate Gr is decreased toward the limited flow rate Grs that is smaller than the large flow rate Gr2. Therefore, the heat of the external heat source HS is stored in the coolant circuit 40. Eventually, when the amount of stored heat becomes excessive, the flow rate Gr is increased. As a result, the heat storage amount is feedback controlled within an appropriate range. Further, when the heat exchanger 70 needs to be defrosted, the flow rate Gr is increased. As a result, excessive frost formation on the heat exchanger 70 is suppressed. Further, when the heat pump capability is insufficient, the flow rate Gr is increased. As a result, the heat pump capability can be supplemented by the cooling water WT.
  • the several tubes 16a and 43a were arrange
  • the plurality of tubes 16a and 43a are arranged so that at least one, preferably the plurality of water tubes 43a, can be seen from the upstream surface of the heat exchanger 70 with respect to the flow of the air AR.
  • the refrigerant tubes 16a and the water tubes 43a appear alternately. This configuration is advantageous in that the temperature of the high-temperature medium supplied to the water tube 43a is exerted on the most upstream portion in the flow direction of the air AR in the heat exchanger 70 to suppress the growth of frost.
  • the plurality of tubes 16a and 43a are provided at least in the upstream row with respect to the flow direction of the air AR, and the upstream row. It arrange
  • At least one water tube 43a does not have the refrigerant tube 16a at a position overlapping the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR.
  • the plurality of tubes 16a and 43a are arranged. As shown in the drawing, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR. And the water tube 43a is arrange
  • the adjacent relationship between the refrigerant tube 16a and the water tube 43a in the orthogonal direction is provided by arranging the refrigerant tubes 16a on both sides of one water tube 43a.
  • This arrangement relationship can be provided by arranging the plurality of refrigerant tubes 16a and the plurality of water tubes 43a alternately in the entire heat exchanger 70.
  • the fin 50 is a corrugated fin.
  • the fin 50 has a heat exchange promoting portion for promoting heat exchange with the air AR at the center in the width direction.
  • a louver 50a formed on the fin 50 may be used.
  • the louver 50 a disturbs the flow of the air AR on the surface of the fin 50.
  • the louver 50 a can have a plurality of slit-shaped openings that penetrate the fins 50.
  • the louver 50a is elongated along the flow direction of the air AR.
  • the louver 50a extends between the refrigerant tube 16a and the water tube 43a so as to partition them.
  • the fin 50 is joined to the side surfaces of the refrigerant tube 16a and the water tube 43a by brazing.
  • the fin 50 has the elongate plate-shaped part 50b which does not have the louver 50a along the side surface of the refrigerant
  • the plate-like portion 50b is not cut by the louver 50a. Since the louver 50a is provided by forming a plurality of openings in the fin 50, the louver 50a inhibits heat transfer through the louver 50a. For this reason, the plate-shaped part 50b shows a high heat transfer rate compared with the area
  • the fin 50 has a frost-proof end portion 50c.
  • the frost-resistant end portion 50c is an end portion of the fin 50 on the upstream side with respect to the flow direction of the air AR.
  • the frost-resistant end portion 50c is an end portion located on the water tube 43a side with respect to a direction orthogonal to the flow direction of the air AR.
  • the frost resistant end portion 50c is an upstream end portion of the plate-like portion 50b adjacent to the water tube 43a with respect to the flow direction of the air AR.
  • the deterioration of the performance of the heat exchanger 70 may occur due to a decrease in the amount of air AR introduced due to frost adhering to the upstream portion of the heat exchanger 70 in the flow direction of the air AR.
  • the water tube 43a disposed in the upstream portion of the heat exchanger 70 efficiently suppresses the growth of frost or provides heat for removing the frost.
  • the high temperature of the water tube 43a is transmitted through the plate-like portion 50b as indicated by the solid arrow.
  • the low temperature of the refrigerant tube 16a is transmitted through the louver 50a as shown by the broken arrow.
  • the thermal conductivity that the fin 50 provides between the water tube 43a and the frost-proof end 50c by the plate-like portion 50b is the heat that the fin 50 provides between the refrigerant tube 16a and the frost-proof end 50c by the louver 50a. Higher than conductivity. For this reason, the heat of the water tube 43a facing the upstream surface of the heat exchanger 70 is efficiently transmitted to the frost-resistant end portion 50c of the fin 50 having the louver 50a.
  • the combination of the water tube 43a disposed so as to face the upstream surface of the heat exchanger 70 and the fin 50 having the louver 50a is an end portion of the fin 50 where the heat of the water tube 43a is efficiently transmitted, That is, it contributes to provide the frost-proof end part 50c.
  • the frost-resistant end portion 50c contributes to suppressing a decrease in the amount of air AR introduced due to frost and promoting defrosting.
  • FIG. 38 shows a heat exchanger 70 according to this embodiment.
  • the refrigerant tubes 16a and the water tubes 43a are alternately arranged.
  • the heat exchanger 70 has the water tube 43 a facing the upstream surface of the heat exchanger 70. Therefore, the frost-proof end part 50c is provided.
  • the number of refrigerant tubes 16a is greater than the number of water tubes 43a.
  • the number of refrigerant tubes 16a in the heat exchanger 70 is greater than the number of water tubes 43a.
  • the flow path cross-sectional area for the outdoor heat exchanger 16 provided by the plurality of refrigerant tubes 16a is larger than the flow path cross-sectional area for the radiator 43 provided by the plurality of water tubes 43a.
  • the number of water tubes 43a in the downstream row is zero.
  • the refrigerant tube 16a is positioned on the downstream side in the flow direction of the air AR of the water tube 43a belonging to the upstream row. For this reason, the heat transferred from the water tube 43a to the air AR is transferred from the air AR to the refrigerant tube 16a.
  • the performance of the outdoor heat exchanger 16 in the heat exchanger 70 can be enhanced. Since the number of the refrigerant
  • the water tubes 43a are positioned in the downstream row. Therefore, the water tube 43a is not located in the upstream part of the heat exchanger 70 with respect to the flow direction of the air AR. However, no tube is provided on the upstream side of the water tube 43a. Therefore, the water tube 43a faces the upstream side in the flow direction of the air AR in the heat exchanger 70. From another viewpoint, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR. And the water tube 43a is arrange
  • the number of the refrigerant tubes 16a in the heat exchanger 70 is larger than the number of the water tubes 43a.
  • the flow path cross-sectional area for the outdoor heat exchanger 16 provided by the plurality of refrigerant tubes 16a is larger than the flow path cross-sectional area for the radiator 43 provided by the plurality of water tubes 43a.
  • the high temperature of the water tube 43a is transmitted through the plate-like portion 50b as shown by the solid line arrow.
  • the low temperature of the refrigerant tube 16a is transmitted through the louver 50a as shown by the broken arrow.
  • the thermal conductivity provided by the fin 50 between the water tube 43a and the frost-proof end 50c by the plate-like portion 50b is the heat provided by the louver 50a between the refrigerant tube 16a and the frost-proof end 50c by the fin 50. Higher than conductivity.
  • the combination of the water tube 43a disposed so as to face the upstream surface of the heat exchanger 70 and the fin 50 having the louver 50a is an end portion of the fin 50 where the heat of the water tube 43a is efficiently transmitted, That is, the frost-proof end part 50c is provided.
  • a plurality of tubes 16a and 43a may be arranged as shown in FIG.
  • one thick refrigerant tube 16a is employed instead of the two refrigerant tubes 16a arranged along the flow direction of the air AR. Even in this configuration, the flow path cross-sectional area for the outdoor heat exchanger 16 is larger than the flow path cross-sectional area for the radiator 43.
  • the water tube 43a and the fin 50 provide a frost-resistant end portion 50c.
  • a plurality of tubes 16a, 43a may be arranged as shown in FIG.
  • the water tube 43a is arranged over both the upstream row and the downstream row.
  • the water tube 43a is disposed between the upstream row and the downstream row.
  • the water tube 43a is adjacent to the refrigerant tube 16a in both the upstream row and the downstream row.
  • the water tube 43a faces the upstream side in the flow direction of the air AR in the heat exchanger 70. From another viewpoint, the water tube 43a does not have the refrigerant tube 16a at a position overlapping with the flow direction of the air AR upstream of the water tube 43a itself in the flow direction of the air AR. And the water tube 43a is arrange
  • a plurality of tubes 16a and 43a may be arranged as shown in FIG.
  • a water tube 43a having a wider width than the refrigerant tube 16a is employed.
  • the water tube 43a is arranged over both the upstream row and the downstream row. In the upstream row, the water tubes 43a are adjacent so as to overlap only the downstream portion of the refrigerant tube 16a.
  • the water tubes 43a are adjacent to each other so as to overlap the entire refrigerant tube 16a.
  • the same advantages as those of the above embodiment can be obtained.
  • a plurality of tubes 16a and 43a may be arranged as shown in FIG.
  • one thick refrigerant tube 16a is employed instead of the two refrigerant tubes 16a arranged along the flow direction of the air AR.
  • the same advantages as those of the above embodiment can be obtained.
  • the preferred embodiments of the present disclosure have been described above. However, the present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure.
  • the structure of the said embodiment is an illustration to the last, Comprising: The range of this indication is not limited to the range of these description.
  • 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 air passages 16b and 43b are provided in both the outdoor heat exchanger 16 and the radiator 43, but 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
  • a device that stores heat from an external heat source such as an internal combustion engine and uses the stored heat for improving frost resistance is configured.
  • the apparatus may be configured to store surplus heat obtained from the refrigerant circuit 10.
  • a heat exchanger that transmits heat of the high-temperature refrigerant before and after the indoor condenser 12 to the cooling water WT can be provided. According to this configuration, it is possible to improve the frost resistance without depending on only the external heat source.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

La présente invention concerne un cycle de pompe à chaleur (2) qui comprend un circuit de fluide frigorigène (10) ainsi qu'un circuit d'eau de refroidissement (40). Un échangeur de chaleur (70), qui assure l'échange de chaleur entre un fluide frigorigène (RF), une eau de refroidissement (WT) et l'air (AR), se trouve entre le circuit de fluide frigorigène (10) et le circuit d'eau de refroidissement (40). Cet échangeur de chaleur (70) comporte un échangeur de chaleur extérieur (16) servant d'évaporateur lors d'opérations de chauffage, et un radiateur (43) conçu pour dissiper la chaleur dans l'eau de refroidissement. Le débit de l'eau de refroidissement (WT) qui circule dans le radiateur (43) est ajusté en réponse à la progression du fonctionnement d'une pompe à chaleur. L'eau de refroidissement (WT) délivre une quantité de chaleur lorsque la pompe à chaleur se met en marche. Cette eau de refroidissement (WT) supprime la quantité de givre qui se dépose pendant que la pompe à chaleur continue de fonctionner, et l'eau de refroidissement (WT) accumule de la chaleur pour le dégivrage tandis que la pompe à chaleur continue de fonctionner. Ladite eau de refroidissement (WT) alimente l'échangeur de chaleur extérieur (16) et sert au dégivrage après que la pompe à chaleur s'est arrêtée.
PCT/JP2012/007735 2011-12-05 2012-12-03 Cycle de pompe à chaleur WO2013084462A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2011266141 2011-12-05
JP2011-266141 2011-12-05
JP2012250452A JP6044285B2 (ja) 2011-12-05 2012-11-14 ヒートポンプサイクル
JP2012-250452 2012-11-14

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WO2018055188A1 (fr) * 2016-09-26 2018-03-29 Volkswagen Aktiengesellschaft Dispositif de climatisation pour véhicule automobile et procédé permettant de faire fonctionner ledit dispositif
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US20210276398A1 (en) * 2018-12-14 2021-09-09 Denso Corporation Vehicle heat exchange system

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JP5920178B2 (ja) * 2011-12-05 2016-05-18 株式会社デンソー ヒートポンプサイクル
JP6192434B2 (ja) * 2013-08-23 2017-09-06 サンデンホールディングス株式会社 車両用空気調和装置
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JP6197746B2 (ja) * 2014-06-03 2017-09-20 株式会社デンソー 熱交換器
JP6593375B2 (ja) * 2017-03-13 2019-10-23 トヨタ自動車株式会社 車両用熱管理装置
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