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WO2020050086A1 - Compresseur et dispositif de cycle de réfrigération - Google Patents

Compresseur et dispositif de cycle de réfrigération Download PDF

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Publication number
WO2020050086A1
WO2020050086A1 PCT/JP2019/033285 JP2019033285W WO2020050086A1 WO 2020050086 A1 WO2020050086 A1 WO 2020050086A1 JP 2019033285 W JP2019033285 W JP 2019033285W WO 2020050086 A1 WO2020050086 A1 WO 2020050086A1
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WO
WIPO (PCT)
Prior art keywords
heat
temperature
heat storage
unit
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/033285
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English (en)
Japanese (ja)
Inventor
卓哉 布施
友宏 早瀬
横山　直樹
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of WO2020050086A1 publication Critical patent/WO2020050086A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • the present disclosure relates to a compressor and a refrigeration cycle device.
  • Patent Document 1 discloses a refrigeration cycle device that stores exhaust heat of a compressor in a heat storage material and effectively uses the stored heat for defrosting an outdoor heat exchanger that functions as an evaporator.
  • a heat storage tank filled with a heat storage material is used as a heat storage unit, and the heat storage unit forms a cover that covers the outer periphery of the compressor.
  • the heat stored in the heat storage unit is transferred to the refrigerant by flowing the refrigerant through a refrigerant pipe arranged to be wound around the outer periphery of the compressor.
  • the present disclosure aims to sufficiently store heat generated by a compressor in a heat storage unit in a short time.
  • the present disclosure relates to a refrigeration cycle device that stores and uses heat generated by a compressor in a heat storage unit, and stores the heat generated by the compressor sufficiently in the heat storage unit in a short time to store the heat in the heat storage unit.
  • Another object of the present invention is to provide a refrigeration cycle device that can effectively and effectively use the heat obtained.
  • a compressor includes a compression unit and a cover unit.
  • the compression unit compresses and discharges the fluid.
  • the cover part is arranged on the outer peripheral side of the compression part and covers the compression part.
  • the cover has a heat storage section for storing heat and a heat transfer promoting section having a higher thermal conductivity than the heat storage section.
  • a fluid passage through which a fluid that exchanges heat with the heat storage unit flows is formed in the cover.
  • the heat transfer promoting section is disposed between the compression section and the heat storage section.
  • the heat transfer promoting section having a higher thermal conductivity than the heat storage section is disposed between the compression section and the heat storage section, the thermal resistance between the compression section and the heat storage section can be reduced. Can be. Therefore, the heat generated by the compression unit can be sufficiently stored in the heat storage unit in a short time.
  • the refrigeration cycle device is a refrigeration cycle device having a compressor that compresses and discharges a refrigerant.
  • the compressor includes a compression section and a cover section.
  • the compression unit compresses and discharges the fluid.
  • the cover part is arranged on the outer peripheral side of the compression part and covers the compression part.
  • the cover has a heat storage section for storing heat and a heat transfer promoting section having a higher thermal conductivity than the heat storage section.
  • a fluid passage through which a fluid that exchanges heat with the heat storage unit flows is formed in the cover.
  • the heat transfer promoting section is disposed between the compression section and the heat storage section. Further, the heat generated by the compression unit by the fluid can be transferred.
  • the heat transfer promoting section having a higher thermal conductivity than the heat storage section is disposed between the compression section and the heat storage section, the thermal resistance between the compression section and the heat storage section can be reduced. Can be. Therefore, the heat generated by the compression unit can be sufficiently stored in the heat storage unit in a short time. Further, since the heat generated by the compression section by the fluid is configured to be conveyable, the heat can be conveyed to a desired portion and used efficiently. That is, it is possible to provide a refrigeration cycle device that can effectively and effectively use the heat generated by the compression unit.
  • FIG. 1 is an overall configuration diagram of a refrigeration cycle device of one embodiment. It is a perspective view of the compressor of one embodiment.
  • FIG. 3 is a sectional view taken along the line III-III of FIG. 2. It is sectional drawing of a heat storage material.
  • It is a block diagram showing an electric control part of a refrigeration cycle device. It is a flow chart which shows a part of control flow of a refrigeration cycle device.
  • 6 is a time chart illustrating a relationship between a heat release amount of a compression unit, a heat storage amount of a cover unit, and a temperature of a low-temperature side heat medium flowing into a low-temperature side radiator in a heating mode.
  • a refrigeration cycle device 10 including a compressor 11 according to the present disclosure will be described.
  • the refrigeration cycle device 10 is applied to an electric vehicle that obtains driving power for traveling from an electric motor.
  • the refrigeration cycle device 10 performs air conditioning in a vehicle cabin of an electric vehicle.
  • the refrigeration cycle device 10 is a vapor compression type refrigeration cycle device.
  • the refrigeration cycle apparatus 10 can switch the refrigerant circuit according to the operation mode for air conditioning.
  • the operation modes for air conditioning include a cooling mode, a dehumidifying heating mode, and a heating mode.
  • the cooling mode is an operation mode in which the air blown into the vehicle interior, which is the space to be air-conditioned, is cooled and blown out into the vehicle interior.
  • the dehumidifying and heating mode is an operation mode in which the cooled and dehumidified blast air is reheated and blown into the vehicle interior.
  • the heating mode is an operation mode in which the blown air is heated and blown into the vehicle interior.
  • the refrigeration cycle apparatus 10 constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.
  • the refrigeration cycle apparatus 10 employs an HFC-based refrigerant (specifically, R134a) as the refrigerant.
  • Refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant.
  • Part of the refrigerating machine oil circulates through the cycle together with the refrigerant.
  • the compressor 11 sucks in the refrigerant, compresses and discharges the refrigerant.
  • the compressor 11 is disposed in a driving device room on the front side of the vehicle.
  • the driving device room is a space in which on-vehicle devices such as a traveling electric motor are arranged.
  • the compressor 11 includes a compression unit 110 that draws refrigerant from a suction port 110a, compresses the refrigerant, and discharges the refrigerant through a discharge port 110b, and a cover unit 120 that covers an outer peripheral side of the compression unit 110. .
  • the compression section 110 is an electric compressor configured to house a fixed capacity type compression mechanism having a fixed discharge capacity and an electric motor for rotating the compression mechanism in a housing 111 forming an outer shell thereof. is there.
  • the compression mechanism various compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be adopted. Further, as the electric motor, any of an AC motor and a DC motor may be used. The rotation speed of the electric motor is controlled by a control signal output from a control device 60 described later. Then, the refrigerant discharge capacity of the compression unit 110 is controlled by the rotation speed control.
  • the housing 111 is formed of an iron-based metal.
  • the housing 111 is formed in a bottomed cylindrical shape extending in the rotation axis direction of the electric motor.
  • the cover section 120 has a first heat storage section 121, a second heat storage section 122, and two heat transfer promotion sections 126.
  • the first heat storage section 121 and the second heat storage section 122 are formed of a heat storage material described later.
  • the first heat storage section 121 and the second heat storage section 122 have a substantially circular plate shape.
  • the two heat storage sections 122 are integrally formed into a substantially cylindrical shape.
  • a space 120b is formed in the first heat storage unit 121 and the second heat storage unit 122.
  • a fluid flow path 120a through which a low-temperature side heat medium, which will be described later, which is a fluid, is formed.
  • a partition 120c is disposed in the space 120b in order to increase the flow path length of the fluid flow path 120a.
  • the partition 120c partitions a space 120b between the first heat storage unit 121 and the second heat storage unit 122.
  • a meandering fluid flow path 120a is formed in the space 120b, as indicated by the thick arrow in FIG.
  • the partition wall 120c is formed along the circumferential direction of the first heat storage section 121 and the second heat storage section 122, and is formed so as to partition the space 120b in the axial direction of the compressor 11. At one end or the other end of the partition wall 120c, a communication port 120d that connects the spaces 120b partitioned by the partition wall 120c is formed.
  • an inflow port 121d connected to the start end of the fluid channel 120a of the first heat storage unit 121 is formed.
  • a first connection port 121e that connects to the end of the fluid flow path 120a of the first heat storage unit 121 is formed on the outer peripheral surface of the first heat storage unit 121.
  • a second connection port 122a is formed on the outer peripheral surface of the second heat storage unit 122 to be connected to the start end of the fluid flow path 120a of the second heat storage unit 122.
  • the first connection port 121e and the second connection port 122a are connected by a pipe 123 made of rubber or the like.
  • an outlet 122b connected to the end of the fluid channel 120a of the first heat storage unit 121 is formed on the outer peripheral surface of the second heat storage unit 122.
  • the low-temperature side heat medium flowing from the inflow port 121d flows through the fluid flow path 120a formed in a meandering shape in the first heat storage section 121 and the second heat storage section 122, and flows out of the outflow port 122b. leak.
  • a contact area increasing portion 120h for increasing the contact area with the fluid is formed on the inner peripheral side of the fluid flow path 120a.
  • the contact area increasing portion 120h is formed along the axial direction of the compressor 11 and has a groove shape formed in parallel in the circumferential direction.
  • the heat storage material forming the first heat storage unit 121 and the second heat storage unit 122 will be described.
  • the heat storage material is formed by bonding a large number of fine spherical capsule-shaped heat storage materials 125a with a skeleton material 125b.
  • the skeletal material 125b is a synthetic resin having excellent heat resistance (specifically, polypropylene), and is a sensible heat storage material that does not undergo a phase change when storing heat.
  • the capsule-like heat storage material 125a has a structure in which a latent heat storage material 125d that undergoes a phase change during heat storage is enclosed in a spherical capsule 125c.
  • the capsule 125c is made of the same material as the skeletal material 125b (that is, polypropylene), and is a sensible heat storage material that does not undergo a phase change when storing heat.
  • the heat storage temperature at which the latent heat storage material 125d changes phase to store heat is set to 35 ° C. or more and 60 ° C. or less.
  • a paraffin wax-based heat storage material As the latent heat storage material 125d, a paraffin wax-based heat storage material, a higher alcohol-based heat storage material, an inorganic salt-based heat storage material, or a mixture thereof can be used.
  • Paraffin wax-based heat storage materials include C22 docosane, C24 tetracosane, and C26 hexacosane.
  • Higher alcohol-based heat storage materials include Caprylone and Camphene.
  • the inorganic salt-based heat storage materials include sodium phosphate dibasic dodecahydrate and sodium thiosulfate pentahydrate.
  • the latent heat storage material 125d absorbs or dissipates heat by changing its phase around its own melting point.
  • the latent heat storage material 125d absorbs heat from the low-temperature side heat medium and changes phase in a region where the temperature of the low-temperature side heat medium is higher than its own melting point. Thereby, as compared with the sensible heat storage material, the latent heat storage material 125d stores more heat of the low-temperature side heat medium.
  • the melting point of the latent heat storage material 125d is set lower than the surface temperature of the compression section 110 during operation. Therefore, when the compression unit 110 operates, the latent heat storage material 125d changes its phase from solid to liquid and absorbs heat.
  • the latent heat storage material 125d radiates heat to the low-temperature side heat medium in a region where the temperature of the low-temperature side heat medium is lower than its own melting point, and changes phase.
  • the melting point of the latent heat storage material 125d is set to be higher than the temperature of the low-temperature side heat medium when the heat stored in the cover 120 is transferred to the low-temperature side heat medium. Therefore, when the heat stored in the cover part 120 is transferred to the low-temperature side heat medium, the latent heat storage material 125d changes its phase from liquid to solid and dissipates heat to the low-temperature side heat medium.
  • the melting point of the latent heat storage material 125 d is lower than the surface temperature of the compression unit 110 during operation, and is lower than the temperature of the low-temperature side heat medium when transferring the heat stored in the cover unit 120 to the low-temperature side heat medium. Is also set high.
  • the skeletal material 125b and the capsule 125c have heat resistance. Specifically, in a temperature range assumed for the housing 111, the skeletal material 125b and the capsule 125c are solid. Therefore, the entire cover portion 120 is solid within the temperature range assumed for the housing 111 and is a fixed-shaped member whose appearance does not change. As described above, the latent heat storage material 125d is held by the capsule 125c and the skeletal material 125b, which are sensible heat storage materials.
  • the heat transfer promoting section 126 is made of a metal material having excellent heat conductivity (for example, copper or aluminum). As shown in FIG. 3, the heat transfer promoting section 126 is a substantially arc-shaped plate-shaped member. When the two heat transfer promoting sections 126 are arranged on the outer peripheral side of the compression section 110, the two heat transfer promoting sections 126 Together they form a substantially cylindrical shape.
  • the heat transfer promoting unit 126 is attached to the inner peripheral surface of each of the first heat storage unit 121 and the second heat storage unit 122 so as to be integrated with the first heat storage unit 121 and the second heat storage unit 122.
  • the inner peripheral surface of the heat transfer promoting portion 126 has a shape corresponding to the outer peripheral surface of the housing 111. Between the inner peripheral surface of the heat transfer promoting portion 126 and the outer peripheral surface of the housing 111, a thermal resistance reducing member 127 made of a flexible material having excellent thermal conductivity is arranged.
  • the thermal resistance reducing member 127 is a soft material such as a thermal conductive grease in which a thermal conductive filler such as a metal is dispersed in grease or a thermal conductive sheet in which a thermal conductive filler is dispersed in silicone.
  • the thermal resistance between the outer peripheral surface of the housing 111 and the inner peripheral surface of the heat transfer promoting section 126 is reduced by the thermal resistance reducing member 127.
  • a contact area increasing portion 126a is formed on the outer peripheral surface of the heat transfer promoting portion 126 to increase a contact area between the inner peripheral surface of each of the first heat storage portion 121 and the second heat storage portion 122.
  • the contact area increasing portion 126a has a fin shape protruding toward the first heat storage portion 121 or the second heat storage portion 122, and is formed in a shape extending along the axial direction of the compressor 11. Further, a plurality of contact area increasing portions 126a are formed in parallel in the circumferential direction.
  • the temperature of the refrigerant increases due to the compression work of the compression mechanism and the temperature of the electric motor increases due to Joule heat, so that the temperature of the entire compression unit 110 increases.
  • part of the heat of the compression unit 110, whose temperature has increased, is stored as waste heat in the first heat storage unit 121 and the second heat storage unit 122 from the housing 111 via the heat transfer promotion unit 126.
  • the water-refrigerant heat exchanger 12 has a refrigerant passage through which the high-pressure refrigerant discharged from the compressor 11 flows, and a water passage through which the high-temperature side heat medium circulating through the high-temperature side heat medium circuit 20 flows.
  • the water-refrigerant heat exchanger 12 is a heating heat exchanger that exchanges heat between the high-pressure refrigerant flowing through the refrigerant passage and the high-temperature heat medium flowing through the water passage to heat the high-temperature heat medium. is there. Details of the high-temperature side heat medium circuit 20 will be described later.
  • the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the refrigerant inlet side of the branch portion 13a.
  • the branch portion 13a branches the flow of the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12.
  • the branch portion 13a has a three-way joint structure having three refrigerant inflow ports that communicate with each other. One of the three inflow ports is a refrigerant inflow port, and the other two are refrigerant outflow ports.
  • a refrigerant inlet side of the indoor evaporator 16 is connected to one refrigerant outlet of the branch portion 13a via a cooling expansion valve 14.
  • the inlet side of the refrigerant passage of the chiller 17 is connected to the other refrigerant outlet of the branch portion 13a via an expansion valve 15 for heat absorption.
  • the cooling expansion valve 14 is a cooling pressure reducing unit that reduces the pressure of the refrigerant that has flowed out of the one refrigerant outlet of the branch portion 13a at least in the cooling mode. Further, the cooling expansion valve 14 is a cooling flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing into the indoor evaporator 16 connected to the downstream side.
  • the cooling expansion valve 14 is an electric device having a valve body configured to change the opening degree of the throttle and an electric actuator (specifically, a stepping motor) that changes the opening degree of the valve body. This is a variable aperture mechanism.
  • the operation of the cooling expansion valve 14 is controlled by a control signal (specifically, a control pulse) output from the control device 60.
  • the cooling expansion valve 14 has a fully closed function of closing the refrigerant passage by fully closing the valve opening. With this fully-closed function, the cooling expansion valve 14 can switch between a refrigerant circuit in which the refrigerant flows into the indoor evaporator 16 and a refrigerant circuit in which the refrigerant does not flow into the indoor evaporator 16. That is, the cooling expansion valve 14 also has a function as a circuit switching unit that switches the refrigerant circuit.
  • the indoor evaporator 16 is a heat exchanger that exchanges heat between the low-pressure refrigerant depressurized by the cooling expansion valve 14 and the blown air.
  • the indoor evaporator 16 is a cooling heat exchanger that evaporates the low-pressure refrigerant to cool the blown air at least in the cooling mode.
  • the indoor evaporator 16 is arranged in a casing 51 of the indoor air conditioning unit 50. The details of the indoor air conditioning unit 50 will be described later.
  • the refrigerant outlet of the indoor evaporator 16 is connected to the inlet side of the evaporation pressure regulating valve 18.
  • the evaporation pressure adjustment valve 18 is an evaporation pressure adjustment unit that maintains the refrigerant evaporation pressure in the indoor evaporator 16 at or above a predetermined reference pressure.
  • the evaporating pressure regulating valve 18 is configured by a mechanical variable throttle mechanism that increases the valve opening as the refrigerant pressure on the outlet side of the indoor evaporator 16 increases.
  • the refrigerant evaporation temperature in the indoor evaporator 16 is maintained at a frost formation suppression reference temperature (1 ° C. in the present embodiment) at which frost formation on the indoor evaporator 16 can be suppressed.
  • a frost formation suppression reference temperature (1 ° C. in the present embodiment
  • One outlet side of the merging portion 13b is connected to the outlet of the evaporation pressure regulating valve 18.
  • the junction 13 b joins the flow of the refrigerant flowing out of the evaporation pressure regulating valve 18 with the flow of the refrigerant flowing out of the chiller 17.
  • the joining portion 13b has the same three-way joint structure as the branching portion 13a, and two of the three inlets and outlets are used as refrigerant inlets, and the other one is used as a refrigerant outlet.
  • the inlet of the compressor 11 is connected to the refrigerant outlet of the junction 13b.
  • the heat absorbing expansion valve 15 is a heat absorbing pressure reducing section that reduces the pressure of the refrigerant flowing out of the other refrigerant outlet of the branch portion 13a at least in the heating mode. That is, it is a decompression unit that decompresses the high-pressure refrigerant pressurized by the compressor 11. Further, the heat-absorbing expansion valve 15 is a heat-absorbing flow rate adjusting unit that adjusts the flow rate of the refrigerant flowing into the refrigerant passage of the chiller 17 connected to the downstream side.
  • the basic configuration of the heat absorption expansion valve 15 is the same as that of the cooling expansion valve 14. Therefore, the heat absorbing expansion valve 15 is an electric variable throttle mechanism having a fully closed function. Further, the heat-absorbing expansion valve 15 can switch between a refrigerant circuit in which the refrigerant flows into the refrigerant passage of the chiller 17 and a refrigerant circuit in which the refrigerant does not flow into the refrigerant passage of the chiller 17. That is, the heat absorption expansion valve 15 also has a function as a circuit switching unit, similarly to the cooling expansion valve 14.
  • the chiller 17 has a refrigerant passage through which the low-pressure refrigerant depressurized by the heat absorbing expansion valve 15 flows, and a water passage through which the low-temperature heat medium circulating through the low-temperature heat medium circuit 30 flows. Then, at least in the heating mode, the chiller 17 performs heat exchange between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the water passage, and evaporates the low-pressure refrigerant to exhibit an endothermic effect. It is a heat exchanger.
  • the chiller 17 is an evaporator that evaporates the low-pressure refrigerant by exchanging heat with the low-temperature side heat medium.
  • the other refrigerant inlet side of the junction 13b is connected to the outlet of the refrigerant passage of the chiller 17. The details of the low-temperature side heating medium circuit 30 will be described later.
  • the high temperature side heat medium circuit 20 is a circuit for circulating the high temperature side heat medium.
  • the high-temperature side heat medium a solution containing ethylene glycol, an antifreeze, or the like can be used.
  • the high-temperature heat medium circuit 20 includes a water passage of the water-refrigerant heat exchanger 12, a high-temperature heat medium pump 21, a heater core 22, a high-temperature radiator 23, a high-temperature flow control valve 24, and the like.
  • the high-temperature heat medium pump 21 is a water pump that pumps the high-temperature heat medium to the inlet side of the water passage of the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 21 is an electric pump whose rotation speed (ie, pumping capacity) is controlled by a control voltage output from the control device 60.
  • One inlet / outlet of the high temperature side flow control valve 24 is connected to the outlet of the water passage of the water-refrigerant heat exchanger 12.
  • the high-temperature-side flow control valve 24 is an electric three-way flow control valve that has three inflow / outflow ports and can continuously adjust the passage area ratio of two inflow / outflow ports. The operation of the high temperature side flow control valve 24 is controlled by a control signal output from the control device 60.
  • the heating medium inlet side of the heater core 22 is connected to another inlet / outlet of the high temperature side flow control valve 24.
  • the heating medium inlet side of the high-temperature side radiator 23 is connected to another inflow / outflow port of the high-temperature side flow control valve 24.
  • the high-temperature side flow control valve 24 controls the flow rate of the high-temperature side heat medium flowing into the heater core 22 of the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12. The flow ratio with the flow rate of the high-temperature side heat medium flowing into the radiator 23 is continuously adjusted.
  • the heater core 22 is a heat exchanger that heats the blown air by exchanging heat between the high-temperature side heat medium heated by the water-refrigerant heat exchanger 12 and the blown air that has passed through the indoor evaporator 16.
  • the heater core 22 is disposed in a casing 51 of the indoor air conditioning unit 50.
  • the heat medium outlet of the heater core 22 is connected to the suction port side of the high-temperature side heat medium pump 21.
  • the high-temperature side radiator 23 exchanges heat between the high-temperature side heat medium heated in the water-refrigerant heat exchanger 12 and the outside air blown from an outside air fan (not shown), and radiates heat of the high-temperature side heat medium to the outside air. Heat exchanger.
  • the high-temperature side radiator 23 is disposed on the front side in the driving device room. Therefore, when the vehicle is traveling, the traveling wind can be applied to the high-temperature side radiator 23.
  • the high temperature radiator 23 may be formed integrally with the water-refrigerant heat exchanger 12 and the like.
  • the heat medium outlet of the high-temperature side radiator 23 is connected to the suction port side of the high-temperature side heat medium pump 21.
  • the high-temperature side flow control valve 24 adjusts the flow rate of the high-temperature side heat medium flowing into the heater core 22, so that the heat radiation amount of the high-temperature side heat medium to the blowing air in the heater core 22 is reduced. Can be adjusted. That is, the heating amount of the blown air in the heater core 22 can be adjusted.
  • each component of the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 20 constitutes a heating unit that heats the blown air using the refrigerant discharged from the compressor 11 as a heat source.
  • the low-temperature-side heat medium circuit 30 is a heat medium circuit that circulates the low-temperature-side heat medium.
  • the low-temperature-side heat medium the same fluid as the high-temperature-side heat medium can be used.
  • the low-temperature-side heat medium circuit 30 includes a water passage of the chiller 17, a low-temperature-side heat medium pump 31, a low-temperature-side radiator 33, a low-temperature-side flow control valve 34, and the like.
  • a cooling water passage of the battery 32 is connected to the low-temperature side heat medium circuit 30.
  • the battery 32 supplies electric power to various electric devices mounted on the vehicle.
  • the battery 32 is a chargeable / dischargeable secondary battery (in the present embodiment, a lithium ion battery). This type of battery 32 generates heat during charging and discharging. For this reason, the cooling water passage of the battery 32 is formed so that the entirety of the battery 32 can be cooled by flowing the low-temperature side heat medium.
  • the low-temperature heat medium pump 31 is a water pump that pumps the low-temperature heat medium to the inlet side of the water passage of the chiller 17.
  • the basic configuration of the low-temperature-side heat medium pump 31 is the same as that of the high-temperature-side heat medium pump 21.
  • the heat medium inlet side of the low-temperature radiator 33 is connected to the outlet side of the water passage of the chiller 17.
  • the low-temperature radiator 33 is an outside air heat exchanger that exchanges heat between the low-temperature heat medium flowing out of the chiller 17 and the outside air blown from an outside air fan (not shown).
  • the low-temperature side radiator 33 functions as an external heat exchanger for radiating the heat of the low-temperature side heat medium to the outside air.
  • the low-temperature side heat medium functions as an endothermic outside air heat exchanger for absorbing the heat of the outside air to the low-temperature side heat medium.
  • bypass passage 35 is provided in the low-temperature side heat medium circuit 30.
  • the bypass passage 35 is a passage that guides the low-temperature side heat medium flowing out of the water passage of the chiller 17 to the suction side of the low-temperature side heat medium pump 31, bypassing the low-temperature side radiator 33.
  • the cooling water passage of the battery 32 is connected to the bypass passage 35.
  • a low temperature side flow control valve 34 is disposed at the outlet of the bypass passage 35.
  • the basic configuration of the low temperature side flow control valve 34 is the same as that of the high temperature side flow control valve 24.
  • the low temperature side flow control valve 34 is a flow rate control valve that adjusts the flow rate of the low temperature side heat medium flowing through the bypass passage 35 in the low temperature side heat medium circuit 30.
  • the low-temperature side flow control valve 34 adjusts the flow rate of the low-temperature side heat medium flowing through the bypass passage 35 (that is, the cooling water passage of the battery 32), so that the temperature of the battery 32 increases. Can be adjusted.
  • the refrigeration cycle device 10 also has a first connection flow path 45 that connects the low-temperature side heat medium circuit 30 on the outlet side of the water passage of the chiller 17 to the inlet 121 d of the cover 120. Further, the refrigeration cycle device 10 has a second connection flow path 46 that connects the outlet 122 b of the cover part 120 and the low-temperature heat medium circuit 30 on the inlet side of the low-temperature radiator 33.
  • An on-off valve 47 that opens or closes the inlet of the first connection channel 45 is disposed at the connection between the first connection channel 45 and the low-temperature side heat medium circuit 30.
  • the on-off valve 47 is a three-way valve having three inflow / outflow ports. The operation of the on-off valve 47 is controlled by a control signal output from the control device 60.
  • the indoor air-conditioning unit 50 forms an air passage in the refrigeration cycle device 10 for blowing the blast air whose temperature has been adjusted by the refrigeration cycle device 10 to an appropriate location in the vehicle compartment.
  • the indoor air-conditioning unit 50 is arranged inside the instrument panel (i.e., instrument panel) at the forefront of the passenger compartment in the passenger compartment.
  • the indoor air-conditioning unit 50 has a blower 52, an indoor evaporator 16, a heater core 22, and the like housed in an air passage formed inside a casing 51 forming an outer shell.
  • the casing 51 forms an air passage for blowing air blown into the vehicle interior, and is formed of a resin (specifically, polypropylene) having a certain degree of elasticity and excellent strength.
  • An inside / outside air switching device 53 is arranged on the most upstream side of the casing 51 in the flow of the blown air. The inside / outside air switching device 53 switches and introduces inside air (vehicle interior air) and outside air (vehicle outside air) into the casing 51.
  • the inside / outside air switching device 53 continuously adjusts the opening area of the inside air introduction port for introducing the inside air into the casing 51 and the outside air introduction port for introducing the outside air by the inside / outside air switching door, so that the inside air introduction air volume and the outside air It is possible to change the introduction ratio with the introduced air volume.
  • the inside / outside air switching door is driven by an electric actuator for the inside / outside air switching door. The operation of the electric actuator is controlled by a control signal output from the control device 60.
  • a blower 52 is disposed downstream of the inside / outside air switching device 53 in the flow of the blown air.
  • the blower 52 blows the air taken in through the inside / outside air switching device 53 toward the vehicle interior.
  • the blower 52 is an electric blower that drives a centrifugal multiblade fan with an electric motor.
  • the rotation speed (that is, the blowing capacity) of the blower 52 is controlled by the control voltage output from the control device 60.
  • the indoor evaporator 16 and the heater core 22 are arranged in this order with respect to the flow of the blast air on the downstream side of the blast air flow of the blower 52. That is, the indoor evaporator 16 is disposed on the upstream side of the flow of the blown air from the heater core 22. Further, a cool air bypass passage 55 is formed in the casing 51 so that the air blown through the indoor evaporator 16 flows to the downstream side bypassing the heater core 22.
  • An air mix door 54 is arranged on the downstream side of the air flow of the indoor evaporator 16 and on the upstream side of the air flow of the heater core 22.
  • the air mix door 54 adjusts the ratio of the amount of air that passes through the heater core 22 and the amount of air that passes through the cool air bypass passage 55 in the air that has passed through the indoor evaporator 16.
  • the air mix door 54 is driven by an electric actuator for driving the air mix door.
  • the operation of the electric actuator is controlled by a control signal output from the control device 60.
  • a mixing space 56 for mixing the air heated by the heater core 22 and the air not heated by the heater core 22 through the cool air bypass passage 55 is provided on the downstream side of the air flow of the heater core 22 .
  • a mixing space 56 for mixing the air heated by the heater core 22 and the air not heated by the heater core 22 through the cool air bypass passage 55 is provided on the downstream side of the air flow of the heater core 22 .
  • an opening hole for blowing out the blast air (conditioned air) mixed in the mixing space 56 into the vehicle interior is disposed at the most downstream portion of the blast air flow of the casing 51.
  • the face opening hole is an opening hole for blowing out conditioned air toward the upper body of the occupant in the passenger compartment.
  • the foot opening hole is an opening hole for blowing out conditioned air toward the feet of the occupant.
  • the defroster opening hole is an opening hole for blowing out conditioned air toward the inner surface of the vehicle front window glass.
  • the face opening, the foot opening, and the defroster opening are respectively connected to a face outlet, a foot outlet, and a defroster outlet provided in the vehicle cabin through ducts forming air passages. )It is connected to the.
  • the temperature of the conditioned air mixed in the mixing space 56 is adjusted by the air mix door 54 adjusting the air flow ratio between the air flow passing through the heater core 22 and the air flow passing through the cool air bypass passage 55. Thereby, the temperature of the blast air (conditioned air) blown out from each outlet into the vehicle interior is also adjusted.
  • a face door for adjusting the opening area of the face opening hole, a foot door for adjusting the opening area of the foot opening hole, and a defroster opening are respectively provided on the upstream side of the blown air flow of the face opening hole, the foot opening hole, and the defroster opening hole.
  • a defroster door (both not shown) for adjusting the opening area of the hole is arranged.
  • the face door, the foot door, and the defroster door constitute an air outlet mode switching device that switches an air outlet through which the conditioned air is blown out.
  • the face door, the foot door, and the defroster door are connected to an electric actuator for driving the outlet mode door via a link mechanism or the like, and are rotated in conjunction therewith.
  • the operation of the electric actuator is controlled by a control signal output from the control device 60.
  • the control device 60 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits. Then, various calculations and processes are performed based on the air conditioning control program stored in the ROM, and various control target devices 11, 14, 15, 21, 24, 31, 34, 47, 52 connected to the output side. And the like.
  • an inside air temperature sensor 62a On the input side of the control device 60, as shown in FIG. 5, an inside air temperature sensor 62a, an outside air temperature sensor 62b, a solar radiation sensor 62c, a high pressure sensor 62d, an evaporator temperature sensor 62e, an air conditioning wind temperature sensor 62f, a battery temperature
  • a sensor group for control such as a sensor 62g and a low-temperature-side heat medium temperature sensor 62h, is connected. The detection signals of these sensor groups are input to the control device 60.
  • the internal air temperature sensor 62a is an internal air temperature detecting unit that detects the vehicle interior temperature (internal air temperature) Tr.
  • the outside air temperature sensor 62b is an outside air temperature detection unit that detects a vehicle outside temperature (outside air temperature) Tam.
  • the solar radiation sensor 62c is a solar radiation amount detector that detects the amount of solar radiation As emitted to the vehicle interior.
  • the high-pressure sensor 62d is a refrigerant pressure detection unit that detects the high-pressure refrigerant pressure Pd in the refrigerant flow path from the discharge port side of the compressor 11 to the inlet side of the cooling expansion valve 14 or the heat absorption expansion valve 15.
  • the evaporator temperature sensor 62e is an evaporator temperature detector that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 16.
  • the air-conditioning air temperature sensor 62f is an air-conditioning air temperature detection unit that detects the temperature of the air blown from the mixing space 56 into the vehicle compartment TAV.
  • the battery temperature sensor 62g is a battery temperature detector that detects the temperature Tb of the battery 32.
  • the battery temperature sensor 62g has a plurality of temperature sensors and detects temperatures at a plurality of locations of the battery 32. Therefore, control device 60 employs an average value of the detection values of the plurality of temperature sensors as temperature Tb of battery 32.
  • the low-temperature heat medium temperature sensor 62h is a low-temperature heat medium temperature detection unit that detects the temperature of the low-temperature heat medium flowing through the low-temperature heat medium circuit 30.
  • the low-temperature heat medium temperature sensor 62h detects the temperature of the low-temperature heat medium of the low-temperature heat medium circuit 30 on the inlet side of the low-temperature radiator 33.
  • an operation panel 61 disposed near the instrument panel in the front of the vehicle compartment is connected to the input side of the control device 60, and various operation switches provided on the operation panel 61 An operation signal is input.
  • Specific examples of various operation switches provided on the operation panel 61 include an air-conditioning operation switch, an air volume setting switch, and a temperature setting switch.
  • the air-conditioning operation switch is an air-conditioning operation requesting unit for requesting that an occupant perform air-conditioning of the vehicle interior.
  • the air volume setting switch is an air volume setting unit for the occupant to manually set the air volume of the blower 52.
  • the temperature setting switch is a temperature setting unit for setting a set temperature in the vehicle compartment.
  • the control device 60 of the present embodiment has an integrated control unit for controlling various control target devices connected to the output side. Therefore, the configuration (hardware and software) that controls the operation of each control target device constitutes a control unit that controls the operation of each control target device.
  • control device 60 that controls the operation of the compressor 11 constitutes the compressor control unit 60a.
  • the configuration for controlling the operation of the on-off valve 47 constitutes the on-off valve control unit 60b.
  • each control unit such as the compressor control unit 60a and the on-off valve control unit 60b may be configured separately.
  • the refrigeration cycle device 10 of the present embodiment can switch the refrigerant circuit according to the operation mode for air conditioning.
  • the air-conditioning operation mode is determined by executing an air-conditioning control program stored in the control device 60 in advance.
  • the air-conditioning control program is executed when the air-conditioning operation switch on the operation panel 61 is turned on (ON) while the vehicle system is running.
  • the target blowing temperature TAO of the air blown into the vehicle compartment is calculated based on the detection signal detected by the control sensor group and the operation signal output from the operation panel 61.
  • TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ As + C (F1)
  • Tset is a set temperature set by a temperature setting switch. Tr is the inside air temperature detected by the inside air temperature sensor 62a. Tam is the outside air temperature detected by the outside air temperature sensor 62b. As is the amount of solar radiation detected by the solar radiation sensor 62c. Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.
  • the operation mode is switched based on the target outlet temperature TAO, the detection signal, and the operation signal.
  • control device 60 of the present embodiment the operation of the on-off valve 47 is controlled by executing the control routine shown in FIG. 6 to prevent frost formation on the low-temperature radiator in the heating mode.
  • the control routine shown in FIG. 6 is executed at predetermined intervals as a subroutine of the main routine of the air conditioning control program.
  • step S11 When the operation mode is switched to the heating mode in the main routine in step S11 of the subroutine, the process proceeds to step S12. On the other hand, when the operation mode is not switched to the heating mode in step S11, the process proceeds to step S14, where the on-off valve control unit 60b closes the on-off valve 47 and returns to the main routine.
  • step S12 if the following frosting condition (1) is satisfied, the process proceeds to step S13, where the on-off valve controller 60b opens the on-off valve 47 and returns to the main routine.
  • the frosting condition (1) is a reference condition in the present embodiment.
  • the frosting condition (1) is a condition for determining whether or not the low-temperature side radiator 33 is an operating condition in which frost may occur. The operation of each operation mode will be described below.
  • (A) Cooling Mode In the cooling mode, the control device 60 causes the cooling expansion valve 14 to be in the throttled state for exerting the refrigerant pressure reducing action, and the heat absorption expansion valve 15 to be in the fully closed state.
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of 13b ⁇ the suction port of the compressor 11 is configured.
  • the control device 60 controls the operation of various control target devices connected to the output side.
  • control device 60 determines a control signal to be output to the compressor 11 so that the refrigerant evaporation temperature Tefin detected by the evaporator temperature sensor 62e becomes the target evaporation temperature TEO.
  • the target evaporation temperature TEO is determined based on the target outlet temperature TAO with reference to a cooling mode control map stored in the control device 60 in advance.
  • the target evaporation temperature TEO is increased with the increase of the target blowout temperature TAO so that the blown air temperature TAV detected by the air-conditioning wind temperature sensor 62f approaches the target blowout temperature TAO. Furthermore, the target evaporation temperature TEO is determined to a value within a range (specifically, 1 ° C. or more) in which frost formation on the indoor evaporator 16 can be suppressed.
  • control device 60 controls the output to the cooling expansion valve 14 so that the superheat degree of the refrigerant at the outlet side of the indoor evaporator 16 approaches a predetermined reference superheat degree (3 ° C. in the present embodiment). Determine the signal.
  • the control device 60 activates the high-temperature side heat medium pump 21 so as to exhibit a predetermined pumping capacity in the cooling mode. Further, the control device 60 controls the control signal output to the high temperature side flow control valve 24 so that the entire flow rate of the high temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the high temperature side radiator 23. To determine.
  • Control device 60 determines a control voltage to be output to blower 52 with reference to a control map stored in control device 60 in advance based on target outlet temperature TAO. Specifically, in this control map, the blowing amount of the blower 52 is maximized in the extremely low temperature region (maximum cooling region) and the extremely high temperature region (maximum heating region) of the target outlet temperature TAO, and as the temperature approaches the intermediate temperature region. Reduce the air flow.
  • the control device 60 determines a control signal to be output to the electric actuator for driving the air mix door such that the cold air bypass passage 55 is fully opened and the ventilation passage on the heater core 22 side is closed. Further, the control device 60 appropriately determines a control signal or the like to be output to other various control target devices.
  • control device 60 outputs the control signals and the like determined as described above to various control target devices. Thereafter, until the stop of the air conditioning in the vehicle compartment is requested, the above-described detection signal and operation signal are read at every predetermined control cycle ⁇ calculation of the target outlet temperature TAO ⁇ control signals output to various control target devices, etc. A control routine such as determination ⁇ output of a control signal or the like is repeated. The repetition of such a control routine is similarly performed in other operation modes.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 21 is operating, so that the high-pressure refrigerant and the high-temperature side heat medium exchange heat, the high-pressure refrigerant is cooled and condensed, and the high-temperature side heat medium is heated. Is done.
  • the high-temperature heat medium heated by the water-refrigerant heat exchanger 12 flows into the high-temperature radiator 23 through the high-temperature flow control valve 24.
  • the high-temperature side heat medium that has flowed into the high-temperature side radiator 23 exchanges heat with the outside air and radiates heat. Thereby, the high-temperature side heat medium is cooled.
  • the high-temperature-side heat medium cooled by the high-temperature-side radiator 23 is sucked into the high-temperature-side heat medium pump 21 and is again pumped to the water passage of the water-refrigerant heat exchanger 12.
  • the low-pressure refrigerant that has been decompressed by the cooling expansion valve 14 and is in a gas-liquid two-phase state flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the blown air blown from the blower 52 and evaporates. As a result, the blown air is cooled, and the blown air temperature TAV approaches the target blowout temperature TAO.
  • the refrigerant flowing out of the indoor evaporator 16 is sucked into the compressor 11 via the evaporation pressure regulating valve 18 and the junction 13b, and is compressed again.
  • the air in the vehicle compartment can be cooled by blowing the blast air cooled by the indoor evaporator 16 into the vehicle compartment.
  • the cooling mode is an operation mode executed when the outside temperature Tam is relatively high (for example, when the outside temperature is 25 ° C. or higher). For this reason, there is a possibility that the temperature of the battery 32 may rise above an appropriate temperature range due to self-heating.
  • the control device 60 controls the low-temperature side heat so as to exhibit a predetermined pumping ability.
  • the medium pump 31 is operated.
  • the control device 60 controls the operation of the low temperature side flow control valve 34 so that the temperature Tb of the battery 32 is maintained in an appropriate temperature zone.
  • the temperature adjustment of the electric device by the control device 60 is not limited to the cooling mode, but is performed as needed in the dehumidifying heating mode and the heating mode. Further, if the entire vehicle system is activated, it is executed as necessary regardless of whether or not air conditioning in the vehicle compartment is being performed (that is, whether or not the air conditioning control program is being executed). You.
  • (B) Dehumidifying and heating mode In the dehumidifying and heating mode, the control device 60 sets the cooling expansion valve 14 to a throttled state and sets the heat absorption expansion valve 15 to a throttled state.
  • a vapor compression refrigeration cycle in which the refrigerant circulates in the order of the part 13b and the suction port of the compressor 11 is configured.
  • a vapor compression type in which the refrigerant circulates in the order of the discharge port of the compressor 11, the water-refrigerant heat exchanger 12, the branch portion 13a, the heat absorbing expansion valve 15, the chiller 17, the junction 13b, and the suction port of the compressor 11. Is configured.
  • the indoor evaporator 16 and the chiller 17 are switched to a refrigerant circuit connected in parallel. Then, in this cycle configuration, the control device 60 controls the operation of various control target devices connected to the output side.
  • control device 60 determines a control signal to be output to the compressor 11 so that the high-pressure refrigerant pressure Pd detected by the high-pressure sensor 62d becomes the target high-pressure PCO.
  • the target high pressure PCO is determined based on the target outlet temperature TAO with reference to a control map for the dehumidifying and heating mode stored in the control device 60 in advance.
  • the target high-pressure PCO is increased with the increase of the target outlet temperature TAO such that the blown air temperature TAV approaches the target outlet temperature TAO.
  • control device 60 refers to the control map for the dehumidifying and heating mode stored in the control device 60 in advance based on the target outlet temperature TAO and the outside air temperature Tam, and outputs a control signal output to the cooling expansion valve 14. And the control signal output to the heat absorption expansion valve 15 is determined.
  • the throttle opening of the heat absorption expansion valve 15 is determined so that the refrigerant evaporation temperature in the chiller 17 is at least lower than the outside temperature Tam. Further, the throttle opening of the cooling expansion valve 14 is determined in a range that is larger than the throttle opening of the heat absorption expansion valve 15.
  • the control device 60 activates the high-temperature side heat medium pump 21 so as to exhibit a predetermined pumping capacity in the dehumidifying and heating mode. Further, the control device 60 determines a control signal output to the high-temperature side flow control valve 24 so that the entire flow rate of the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the heater core 22. I do.
  • the control device 60 activates the low-temperature side heat medium pump 31 so as to exhibit a predetermined pumping capacity in the dehumidifying and heating mode.
  • control device 60 determines the control voltage output to the blower 52. Further, control device 60 determines a control signal to be output to the electric actuator for driving the air mix door such that the ventilation passage on the side of heater core 22 is fully opened and the cooling air bypass passage 55 is closed. Further, the control device 60 appropriately determines a control signal or the like to be output to other various control target devices.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 21 is operating, so that the high-pressure refrigerant and the high-temperature side heat medium exchange heat, the high-pressure refrigerant is cooled and condensed, and the high-temperature side heat medium is heated. Is done.
  • the high-temperature heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 22 via the high-temperature flow control valve 24.
  • the high-temperature side heat medium that has flowed into the heater core 22 radiates heat by exchanging heat with the blast air that has passed through the indoor evaporator 16 because the air mix door 54 fully opens the ventilation path on the heater core 22 side.
  • the blast air that has passed through the indoor evaporator 16 is heated, and the temperature of the blast air approaches the target blowing temperature TAO.
  • the high-pressure refrigerant that has flowed out of the refrigerant passage of the water-refrigerant heat exchanger 12 is branched at the branch portion 13a.
  • One of the refrigerants branched at the branch portion 13a flows into the cooling expansion valve 14 and is decompressed.
  • the low-pressure refrigerant that has been decompressed by the cooling expansion valve 14 and is in a gas-liquid two-phase state flows into the indoor evaporator 16.
  • the refrigerant flowing into the indoor evaporator 16 absorbs heat from the blown air blown from the blower 52 and evaporates. Thereby, the blown air is cooled and dehumidified.
  • the refrigerant evaporation temperature in the indoor evaporator 16 is maintained at 1 ° C. or higher by the operation of the evaporation pressure regulating valve 18 irrespective of the refrigerant discharge capacity of the compressor 11. Therefore, frost does not occur on the indoor evaporator 16.
  • the refrigerant flowing out of the indoor evaporator 16 flows into one refrigerant inlet of the junction 13b via the evaporation pressure regulating valve 18.
  • the other refrigerant branched at the branch portion 13a flows into the heat absorbing expansion valve 15 and is decompressed.
  • the throttle opening of the heat absorbing expansion valve 15 is adjusted such that the refrigerant evaporation temperature in the chiller 17 is at least lower than the outside air temperature Tam.
  • the low-pressure refrigerant that has been decompressed by the heat-absorbing expansion valve 15 and is in a gas-liquid two-phase state flows into the chiller 17.
  • the refrigerant flowing into the chiller 17 absorbs heat from the low-temperature side heat medium and evaporates.
  • the low-temperature side heat medium cooled by the chiller 17 flows into the low-temperature side radiator 33.
  • the low-temperature heat medium absorbs heat from the outside air. Thereby, the temperature of the low-temperature side heat medium approaches the outside air temperature Tam.
  • the low-temperature-side heat medium flowing out of the low-temperature-side radiator 33 is sucked into the low-temperature-side heat medium pump 31 and is again pressure-fed to the water passage side of the chiller 17.
  • the refrigerant flowing out of the chiller 17 flows into the other refrigerant inlet of the merging portion 13b, and merges with the refrigerant flowing out of the evaporation pressure regulating valve 18.
  • the refrigerant flowing out of the junction 13b is sucked into the compressor and compressed again.
  • the blast air cooled and dehumidified by the indoor evaporator 16 is reheated by the heater core 22 and blown out into the vehicle interior, whereby dehumidification and heating in the vehicle interior can be performed.
  • (C) Heating Mode In the heating mode, the control device 60 sets the cooling expansion valve 14 to the fully closed state, and sets the heat absorption expansion valve 15 to the throttled state.
  • control device 60 controls the operation of various control target devices connected to the output side.
  • control device 60 determines a control signal to be output to the compressor 11 as in the dehumidifying and heating mode. Further, the control device 60 refers to a heating mode control map stored in the control device 60 in advance based on the target outlet temperature TAO and the outside air temperature Tam, and outputs a control signal output to the heat absorption expansion valve 15. decide. Specifically, in this control map, the refrigerant evaporation temperature in the chiller 17 is determined to be at least equal to or less than the outside temperature Tam.
  • the control device 60 activates the high-temperature side heat medium pump 21 so as to exhibit a predetermined pumping capacity in the heating mode. Further, similarly to the dehumidifying and heating mode, the controller 60 controls the high-temperature side flow control valve 24 so that the entire flow rate of the high-temperature side heat medium flowing out of the water passage of the water-refrigerant heat exchanger 12 flows into the heater core 22. Determine the control signal to be output.
  • the control device 60 operates the low-temperature side heat transfer medium pump 31 so as to exhibit a predetermined pumping capacity in the heating mode.
  • the control device 60 determines the control voltage output to the blower 52. Further, similarly to the dehumidifying and heating mode, the control device 60 determines a control signal to be output to the electric actuator for driving the air mix door so that the ventilation path on the heater core 22 side is fully opened and the cool air bypass passage 55 is closed. . Further, the control device 60 appropriately determines a control signal or the like to be output to other various control target devices.
  • the high-pressure refrigerant discharged from the compressor 11 flows into the water-refrigerant heat exchanger 12.
  • the high-temperature-side heat medium pump 21 is operating, so that the high-pressure refrigerant and the high-temperature side heat medium exchange heat, the high-pressure refrigerant is cooled and condensed, and the high-temperature side heat medium is heated. Is done.
  • the high-temperature heat medium heated by the water-refrigerant heat exchanger 12 flows into the heater core 22 via the high-temperature flow control valve 24.
  • the high-temperature side heat medium that has flowed into the heater core 22 radiates heat by exchanging heat with the blast air that has passed through the indoor evaporator 16 because the air mix door 54 fully opens the ventilation path on the heater core 22 side.
  • the blown air is heated, and the blown air temperature TAV approaches the target blowout temperature TAO.
  • the low-temperature side heat medium cooled by the chiller 17 flows into the low-temperature side radiator 33, similarly to the dehumidifying and heating mode.
  • the low-temperature heat medium absorbs heat from the outside air. Thereby, the temperature of the low-temperature side heat medium approaches the outside air temperature Tam.
  • the low-temperature-side heat medium flowing out of the low-temperature-side radiator 33 is sucked into the low-temperature-side heat medium pump 31 and is again pressure-fed to the water passage side of the chiller 17.
  • the air inside the vehicle compartment can be heated by blowing the blast air heated by the heater core 22 into the vehicle compartment.
  • FIG. 7 shows the relationship between the heat release amount, the heat storage amount, and the temperature of the low-temperature side heat medium when the heating mode is started in the refrigeration cycle device 10 from the state in which the air conditioning by the refrigeration cycle device 10 is not executed. I have.
  • the heat radiation amount of the compression part 110 and the heat storage amount of the cover part 120 in FIG. 7 are the heat amounts (W) per unit time, and do not indicate the heat radiation amount or the integrated value (J) of the heat storage amount.
  • the compression unit 110 When the compression unit 110 starts operating, the compression unit 110 generates heat and radiates heat from the housing 111 to the cover unit 120 via the heat transfer promoting unit 126. With the heat radiation of the compression unit 110, the heat generated by the compression unit 110 is stored in the cover unit 120.
  • the amount of heat storage indicated by a dashed line indicates the amount of heat storage in a compressor provided with a comparative cover that does not include the heat transfer promoting unit 126.
  • the temperature of the low-temperature heat medium flowing through the low-temperature heat medium circuit 30 gradually decreases.
  • the low-temperature side heat medium which has flown through the fluid passage 120a to the cover portion 120 and has risen in temperature flows through the second connection flow path 46, flows into the low-temperature side heat medium circuit 30, and flows into the low-temperature side heat medium circuit 30. Further, the temperature of the low-temperature side heat medium flowing through is further reduced. Therefore, frost formation on the low-temperature side radiator 33 is prevented.
  • the temperature of the low-temperature side heat medium indicated by the broken line represents the temperature of the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 30 in a state where the on-off valve 47 remains closed.
  • the refrigeration cycle apparatus 10 can switch between the cooling mode, the dehumidification heating mode, and the heating mode by switching the refrigerant circuit, thereby providing comfortable air conditioning in the vehicle compartment. Can be realized.
  • the cycle configuration is likely to be complicated.
  • the refrigeration cycle device 10 of the present embodiment there is no switching between the refrigerant circuit for flowing the high-pressure refrigerant and the refrigerant circuit for flowing the low-pressure refrigerant into the same heat exchanger. That is, since it is not necessary to make the high-pressure refrigerant flow into the indoor evaporator 16 when switching to any of the refrigerant circuits, the refrigerant circuit can be switched with a simple configuration without complicating the cycle configuration.
  • the cover 120 in the heating mode, can store and recover the exhaust heat of the compressor 110 in the heating mode. Then, the low-temperature side heat medium is circulated through the cover section 120, and the exhaust heat stored in the cover section 120 is supplied to the low-temperature side radiator 33, so that frost formation on the low-temperature side radiator 33 can be prevented.
  • the heat transfer promoting unit 126 having a higher thermal conductivity than the first heat storage unit 121 and the second heat storage unit 122 includes the compression unit 110, the first heat storage unit 121, and the second heat storage unit. 122. According to this, the thermal resistance between the compression part 110 and the first heat storage part 121 and between the compression part 110 and the second heat storage part 122 can be reduced.
  • the heat generated by the compression unit 110 is sufficiently transferred to the first compressor in a short time by a compressor having a comparative cover unit without the heat transfer promotion unit 126.
  • Heat can be stored in the heat storage unit 121 and the second heat storage unit 122. Therefore, the heat stored in the first heat storage unit 121 and the second heat storage unit 122 can be effectively used. That is, in the heating mode, it can be effectively used to prevent frost formation on the low-temperature radiator 33.
  • the heat transfer promoting section 126 is arranged on the outer peripheral side of the compression section 110 so as to cover the compression section 110. According to this, the heat transfer promoting unit 126 can receive the heat radiated to the outer peripheral side of the compression unit 110. Therefore, the heat generated by the compression unit 110 can be transferred to the first heat storage unit 121 and the second heat storage unit 122 without waste, and stored.
  • the heat transfer promoting unit 126 is in contact with the outer peripheral surface of the compression unit 110, the inner peripheral surface of the first heat storage unit 121, and the inner peripheral surface of the second heat storage unit 122. .
  • the compression unit 110, the first heat storage unit 121, and the second heat storage unit are compared with the case where the heat transfer promotion unit 126 is separated from the compression unit 110, the first heat storage unit 121, and the second heat storage unit 122.
  • the thermal resistance between the portion 122 can be reduced. Therefore, the heat generated by the compression unit 110 can be sufficiently stored in the first heat storage unit 121 and the second heat storage unit 122 in a shorter time.
  • the heat transfer promoting unit 126 protrudes toward the first heat storage unit 121 and the second heat storage unit 122, and has a contact area with the first heat storage unit 121 and the second heat storage unit 122. Is increased. According to this, the thermal resistance between the heat transfer promoting unit 126 and the first heat storage unit 121 and the thermal resistance between the heat transfer promoting unit 126 and the second heat storage unit 122 can be further reduced. Therefore, the heat generated by the compression unit 110 can be sufficiently stored in the first heat storage unit 121 and the second heat storage unit 122 in a shorter time.
  • the heat transfer promoting unit 126 is made of metal. According to this, the heat conductivity of the heat transfer promoting unit 126 can be easily improved. Therefore, the heat generated by the compression unit 110 can be sufficiently stored in the first heat storage unit 121 and the second heat storage unit 122 in a shorter time.
  • the heat storage material is a latent heat storage material 125d that undergoes a phase change during heat storage, and a sensible heat storage material that does not undergo a phase change during the heat storage. And a skeletal material 125b.
  • the latent heat storage material 125d is held by a capsule 125c and a skeletal material 125b, which are sensible heat storage materials.
  • the heat storage material includes the latent heat storage material 125d, efficient heat storage can be realized as compared with a case where the entire heat storage material is formed of the sensible heat storage material. Therefore, the amount of heat that can be stored in the cover 120 can be increased. As a result, frost formation on the low-temperature radiator 33 can be further prevented.
  • the capsule 125c which is a sensible heat storage material
  • the capsule 125c which is a sensible heat storage material
  • the capsule 125c which is a sensible heat storage material
  • the cover part 120 can be easily formed while increasing the heat storage amount of the cover part 120, and the degree of freedom of the shape of the cover part 120 can be improved.
  • the melting point of the latent heat storage material 125d is set lower than the surface temperature of the compression section 110 during operation. According to this, when the compression unit 110 is operated, the latent heat storage material 125d changes its phase from a solid phase to a liquid phase. Therefore, the amount of heat stored in the cover unit 120 can be increased by the amount of heat absorbed by the latent heat storage material 125d due to the phase change of the latent heat storage material 125d.
  • the melting point of the latent heat storage material 125d is higher than the temperature of the low-temperature side heat medium when the heat stored in the cover 120, which is the heat storage material, is transferred to the low-temperature side heat medium. Is set. According to this, when transferring the heat stored in the cover unit 120 to the fluid, the latent heat storage material 125d changes its phase from a liquid phase to a solid phase. For this reason, the heat radiation amount of the cover unit 120 can be increased by the heat radiation of the latent heat storage material 125d due to the phase change of the latent heat storage material 125d.
  • the waste heat of the compression unit 110 can be efficiently stored by using the phase change of the latent heat storage material 125d, and the heat stored in the cover unit 120 can be stored. Can be efficiently dissipated.
  • a soft material that reduces the thermal resistance between the heat transfer promoting unit 126 and the compression unit 110 is provided between the heat transfer promoting unit 126 and the outer peripheral surface of the compression unit 110.
  • the configured thermal resistance reducing member 127 is arranged. According to this, the thermal resistance between the outer peripheral surface of the compression unit 110 and the inner peripheral surfaces of the first heat storage unit 121 and the second heat storage unit 122 can be reduced. Therefore, the heat generated by the compression unit 110 can be sufficiently stored in the first heat storage unit 121 and the second heat storage unit 122 in a shorter time.
  • the fluid passage 120a is formed in the first heat storage unit 121 and the second heat storage unit 122.
  • the low-temperature side heat medium can be brought into direct contact with the first heat storage section 121 and the second heat storage section 122.
  • the heat exchange efficiency between the low-temperature side heat medium and the first heat storage section 121 and the second heat storage section 122 is improved, and the heat stored in the first heat storage section 121 and the second heat storage section 122 is transferred to the low-temperature side heat medium. It can be sufficiently moved to the medium. Therefore, the heat stored in the first heat storage unit 121 and the second heat storage unit 122 can be effectively used. That is, in the heating mode, it can be effectively used to prevent frost formation on the low-temperature radiator 33.
  • the partition 120c that partitions the space 120b of the first heat storage unit 121 and the second heat storage unit 122 is formed in the space 120b so that the meandering fluid flow path 120a is formed.
  • the flow path length of the fluid flow path 120a can be increased by the partition wall 120c.
  • the contact area between the low-temperature side heat medium and the heat storage material can be increased. Therefore, the heat exchange efficiency between the low-temperature side heat medium and the heat storage material can be further improved, and the heat stored in the heat storage material can be sufficiently transferred by the low-temperature side heat medium.
  • the heat stored in the heat storage material can be used more effectively. That is, in the heating mode, it can be effectively used to prevent frost formation on the low-temperature radiator 33.
  • the refrigeration cycle device 10 of the present embodiment is configured to be able to convey the heat generated by the compression unit 110 by the low-temperature side heat medium. Therefore, the heat generated by the compression unit 110 can be effectively and effectively used.
  • the refrigeration cycle apparatus 10 of the present embodiment includes a chiller 17 which is an evaporator for evaporating the refrigerant by exchanging heat with the low-temperature side heat medium, and a heating apparatus in which the low-temperature side heat medium circulates and is heated by the low-temperature side heat medium. And a low-temperature side heat medium circuit 30 in which a low-temperature side radiator 33 as an object is disposed.
  • the heat stored in the cover unit 120 can be used for heating the low-temperature radiator 33 that is the object to be heated. That is, by supplying the heat stored in the cover unit 120 to the low-temperature radiator 33, frost formation on the low-temperature radiator 33 can be prevented. When the low-temperature radiator 33 is frosted, the low-temperature radiator 33 can be defrosted.
  • the on-off valve 47 is opened to exchange the heat with the heat storage material in the fluid flow path 120a and to heat the low-temperature side heat medium to the low-temperature side heat medium. It is distributed to the medium circuit 30.
  • the low-temperature side heat medium heated in the fluid flow path 120a is transferred to the low-temperature side heat medium circuit 30.
  • the heat stored in the cover section 120 can be supplied to the low-temperature radiator 33 by flowing the heat through the cover section 120. Therefore, frost formation on the low-temperature radiator 33 can be prevented.
  • the present invention may be applied to a normal engine vehicle that obtains a driving force for driving a vehicle from an internal combustion engine, or a hybrid vehicle that obtains driving force for driving a vehicle from both an internal combustion engine and an electric motor. Further, the present invention is not limited to a vehicle, and may be applied to a stationary temperature control device or the like.
  • the refrigeration cycle apparatus 10 configured to be able to switch the air-conditioning operation mode is described.
  • the switching of the air-conditioning operation mode is not essential. If at least the heating mode can be executed, the exhaust heat of the compressor 11 can be sufficiently recovered and used effectively.
  • the heat storage material is not limited to this.
  • the heat storage material may be formed of a metal member or the like.
  • the heat storage material may be a chemical heat storage material that undergoes a chemical change during heat storage. Examples of such a chemical heat storage material include a heat storage material for chemically reacting alkali metal chloride and ammonia, a heat storage material for chemically reacting alkaline earth metal chloride and ammonia, and a chemical reaction between transition metal element chloride and ammonia.
  • the heat storage material to be used can be adopted.
  • the skeletal material 125b which is a sensible heat storage material, may be made of an attenuating material (for example, rubber, urethane foam, or the like) that attenuates vibration of the compression unit 110 during operation.
  • an attenuating material for example, rubber, urethane foam, or the like
  • the vibration of the compression unit 110 is attenuated by the cover unit 120, and noise caused by the vibration of the compression unit 110 can be reduced.
  • the on-off valve 47 is opened to move the exhaust heat of the compression unit 110 stored in the cover unit 120 to the low-temperature side heat medium. May be.
  • the temperature of the low-temperature side heat medium flowing through the low-temperature side heat medium circuit 30 increases, the amount of heat absorbed by the low-pressure refrigerant in the chiller 17 increases, and the high-temperature side heat medium in the water-refrigerant heat exchanger 12 increases. The amount of heating increases. As a result, the heating capacity of the refrigeration cycle device 10 in the heating mode is improved.
  • the frosting condition as the reference condition determined in step S12 of FIG. 6 may be the following frosting condition (2) or (3).
  • the frosting condition (2) is a condition for determining whether or not the low-temperature side radiator 33 is an operating condition under which frosting may occur.
  • ⁇ Defrosting condition (3) When the blast air temperature TAV detected by the air-conditioning air temperature sensor 62f is equal to or lower than the specified blast air temperature.
  • the frosting condition (3) is a condition for determining whether or not frost has occurred on the low-temperature side radiator 33.
  • the heating capacity of the refrigeration cycle device 10 decreases, and the blast air temperature TAV detected by the conditioned air temperature sensor 62f decreases. Therefore, in the heating mode, it is possible to determine whether or not frost has formed on the low-temperature radiator 33 by detecting the blast air temperature TAV detected by the conditioned air temperature sensor 62f.
  • Each configuration of the refrigeration cycle device 10 is not limited to the configuration disclosed in the above embodiment.
  • an electric compressor was employed as the compressor 11, but the present invention is not limited to this.
  • an engine-driven compressor may be employed.
  • a variable displacement compressor configured to adjust the refrigerant discharge capacity by changing the discharge capacity may be adopted.
  • the gas-liquid separation unit that separates the gas-liquid of the refrigerant flowing into the inside and stores the excess liquid-phase refrigerant of the cycle may be added to the refrigeration cycle apparatus 10 described in the above embodiment.
  • an accumulator as a gas-liquid separation unit may be arranged in a refrigerant flow path from a refrigerant outlet of the junction 13b to a suction port of the compressor 11.
  • a receiver as a gas-liquid separation unit may be arranged in a refrigerant flow path from the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12 to the refrigerant inlet of the branch part 13a.
  • an electric variable throttle mechanism with a fully closed function is employed as the cooling expansion valve 14 and the heat absorption expansion valve 15 .
  • a temperature-type expansion valve that adjusts the valve opening degree by a mechanical mechanism and an electric open / close valve may be employed.
  • the on-off valve 47 is employed as the flow rate adjustment unit that adjusts the flow rate of the low-temperature side heat medium flowing through the first connection flow channel 45, but the flow rate adjustment unit is not limited to this.
  • a variable throttle mechanism similar to the cooling expansion valve 14 or the heat absorption expansion valve 15 may be employed as the flow rate adjusting unit.
  • the on-off valve 47 is a three-way valve disposed at a connection between the first connection flow path 45 and the low-temperature side heat medium circuit 30.
  • the on-off valve 47 may be a valve arranged in the first connection channel 45 or the second connection channel 46 to open or close the first connection channel 45 or the second connection channel 46.
  • R134a is used as the refrigerant of the refrigeration cycle apparatus 10
  • the refrigerant is not limited to this.
  • R1234yf, R600a, R410A, R404A, R32, R407C, etc. may be adopted.
  • a mixed refrigerant obtained by mixing a plurality of types of these refrigerants may be employed.
  • the heating unit configured to heat the blown air by the water-refrigerant heat exchanger 12 and the high-temperature side heat medium circuit 20 is configured, but the heating unit is not limited to this.
  • an indoor condenser that directly exchanges heat between the refrigerant discharged from the compressor 11 and the blown air may be employed as the heating unit.
  • the low-temperature heat medium circuit 30 capable of adjusting the temperature of the battery 32 has been described.
  • the temperature adjustment target of the low-temperature heat medium circuit 30 is not limited to this.
  • the temperature adjustment target may be an inverter, a charger, a motor generator, or the like. Further, there may be a plurality of temperature adjustment objects.
  • the high-temperature radiator 23 and the low-temperature radiator 33 are not limited to independent configurations.
  • the high-temperature-side radiator 23 and the low-temperature-side radiator 33 described in the first embodiment may be integrated such that the heat of the high-temperature-side heat medium and the heat of the low-temperature-side heat medium can move mutually.
  • the heat mediums may be integrated so as to be heat-transferable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Ce compresseur est pourvu d'une unité de compression (110) et d'une section de recouvrement (120). L'unité de compression comprime et rejette un fluide. La section de recouvrement (120) est disposée sur sur le côté circonférentiel exterieur de l'unité de compression (110) et recouvre l'unité de compression (110). La section de recouvrement (120) comprend des sections de stockage de chaleur (121, 122) pour stocker de la chaleur et une section d'amélioration de transfert de chaleur (126) ayant une conductivité thermique plus élevée que celle des sections de stockage de chaleur (121, 122). Un trajet d'écoulement de fluide (120a) par lequel circule un fluide effectuant un échange thermique avec les sections de stockage de chaleur (121, 122) s'écoule se forme dans la section de recouvrement (120).
PCT/JP2019/033285 2018-09-03 2019-08-26 Compresseur et dispositif de cycle de réfrigération Ceased WO2020050086A1 (fr)

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JP2018-164673 2018-09-03
JP2018164673A JP2020037882A (ja) 2018-09-03 2018-09-03 圧縮機及び冷凍サイクル装置

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Publication number Priority date Publication date Assignee Title
CN114837946A (zh) * 2022-06-18 2022-08-02 华海(北京)科技股份有限公司 一种节能型双级螺旋式空气压缩机控制系统
US11839062B2 (en) 2016-08-02 2023-12-05 Munters Corporation Active/passive cooling system
CN119573290A (zh) * 2025-01-24 2025-03-07 广东美博制冷设备有限公司 一种喷气增焓系统补气回路的加热结构及加热方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7694443B2 (ja) * 2022-04-11 2025-06-18 株式会社Soken 温調装置

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Publication number Priority date Publication date Assignee Title
JPH0367959A (ja) * 1990-03-02 1991-03-22 Hitachi Ltd 空気調和装置
JP2011144695A (ja) * 2010-01-12 2011-07-28 Panasonic Corp 蓄熱装置、ならびにこれを備えた空気調和機
WO2013099164A1 (fr) * 2011-12-26 2013-07-04 パナソニック株式会社 Climatiseur
JP2015178939A (ja) * 2014-03-19 2015-10-08 株式会社東芝 畜熱装置及び空気調和機
EP3244141A1 (fr) * 2016-05-09 2017-11-15 Vaillant GmbH Dégivrage avec de la chaleur générée par moteur de compresseur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0367959A (ja) * 1990-03-02 1991-03-22 Hitachi Ltd 空気調和装置
JP2011144695A (ja) * 2010-01-12 2011-07-28 Panasonic Corp 蓄熱装置、ならびにこれを備えた空気調和機
WO2013099164A1 (fr) * 2011-12-26 2013-07-04 パナソニック株式会社 Climatiseur
JP2015178939A (ja) * 2014-03-19 2015-10-08 株式会社東芝 畜熱装置及び空気調和機
EP3244141A1 (fr) * 2016-05-09 2017-11-15 Vaillant GmbH Dégivrage avec de la chaleur générée par moteur de compresseur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11839062B2 (en) 2016-08-02 2023-12-05 Munters Corporation Active/passive cooling system
US12127380B2 (en) 2016-08-02 2024-10-22 Munters Corporation Active/passive cooling system
CN114837946A (zh) * 2022-06-18 2022-08-02 华海(北京)科技股份有限公司 一种节能型双级螺旋式空气压缩机控制系统
CN119573290A (zh) * 2025-01-24 2025-03-07 广东美博制冷设备有限公司 一种喷气增焓系统补气回路的加热结构及加热方法

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