WO2019111637A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

Info

Publication number
WO2019111637A1
WO2019111637A1 PCT/JP2018/041810 JP2018041810W WO2019111637A1 WO 2019111637 A1 WO2019111637 A1 WO 2019111637A1 JP 2018041810 W JP2018041810 W JP 2018041810W WO 2019111637 A1 WO2019111637 A1 WO 2019111637A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
air
valve
evaporator
Prior art date
Application number
PCT/JP2018/041810
Other languages
English (en)
Japanese (ja)
Inventor
雄司 川添
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN201880078169.5A priority Critical patent/CN111433538B/zh
Priority to DE112018006208.2T priority patent/DE112018006208T5/de
Publication of WO2019111637A1 publication Critical patent/WO2019111637A1/fr
Priority to US16/892,001 priority patent/US20200292218A1/en

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3229—Cooling devices using compression characterised by constructional features, e.g. housings, mountings, conversion systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
    • F25B1/08—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure using vapour under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3225—Cooling devices using compression characterised by safety arrangements, e.g. compressor anti-seizure means or by signalling devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • Patent Document 1 discloses a refrigeration cycle apparatus provided with a compressor, an outdoor evaporator, an indoor evaporator, and an evaporation pressure control valve.
  • the evaporation pressure control valve functions to adjust the refrigerant evaporation pressure in the indoor evaporator to a pressure equal to or higher than the frost formation suppression pressure in order to suppress frost formation in the indoor evaporator.
  • the evaporation pressure control valve regulates the valve opening degree by a mechanical mechanism.
  • a high pressure side charging port for charging a refrigerant before shipment is disposed on the downstream side of the compressor.
  • a low pressure side charging port for charging a refrigerant after shipment is disposed on the downstream side of the compressor.
  • the evaporation pressure control valve of the refrigeration cycle apparatus of Patent Document 1 is configured to change the valve opening degree by the pressure difference between the refrigerant pressure on the upstream side and the refrigerant pressure on the downstream side. Furthermore, when the refrigerant pressure on the downstream side of the evaporation pressure control valve becomes higher than the refrigerant pressure on the upstream side of the evaporation pressure adjustment valve and the reverse pressure acts on the evaporation pressure adjustment valve, the evaporation pressure adjustment valve is durable There is a risk of deterioration. For this reason, the charging port on the low pressure side is generally disposed upstream of the evaporation pressure control valve.
  • An object of the present disclosure is to provide a refrigeration cycle apparatus in which the degree of freedom of the mounting position of the charging port is improved without deteriorating the durability of the evaporation pressure control valve.
  • a refrigeration cycle apparatus includes: a compressor that compresses and discharges a refrigerant; a heating unit that heats a fluid to be exchanged with heat using the refrigerant discharged from the compressor as a heat source; An outdoor evaporator for exchanging heat with the outside air, an indoor evaporator for exchanging heat between the refrigerant flowing out of the outdoor evaporator and the fluid for heat exchange, and a first for guiding the refrigerant flowing out of the heating unit to the inlet side of the outdoor evaporator A refrigerant passage and a first pressure reducing portion disposed in the first refrigerant passage and capable of changing the opening area of the first refrigerant passage, and guiding the refrigerant flowing out of the outdoor evaporator to the suction side of the compressor via the indoor evaporator A second refrigerant passage, and a second pressure reducing portion which is disposed between an outdoor evaporator and an indoor evaporator in the second refrigerant passage
  • the pressure fluctuation suppressing portion since the pressure fluctuation suppressing portion is provided, when the refrigerant is charged from the charging port to the refrigeration cycle apparatus, the rapid fluctuation of the internal pressure of the second refrigerant passage in which the evaporation pressure adjusting valve is disposed is suppressed. be able to. For this reason, pressure fluctuation on the outlet side of the evaporating pressure regulating valve can be suppressed. Therefore, even if the charging port is disposed on the downstream side of the evaporation pressure control valve, the deterioration of the durability of the evaporation pressure control valve can be suppressed.
  • the air conditioner 1 includes a refrigeration cycle apparatus 10, a heating unit 25, and an indoor air conditioning unit 30.
  • the refrigeration cycle apparatus 10 according to the present disclosure is applied to an air conditioner 1 for a vehicle mounted on an electric vehicle that obtains driving force for traveling the vehicle from a traveling electric motor.
  • the refrigeration cycle apparatus 10 has a function of cooling or heating the air which is blown into the vehicle compartment, which is the space to be air conditioned, in the air conditioner 1. Therefore, the heat exchange target fluid of this embodiment is blowing air.
  • the refrigeration cycle apparatus 10 is configured to be able to switch between a refrigerant circuit in the heating mode, a refrigerant circuit in the cooling mode, a refrigerant circuit in the series dehumidifying heating mode, and a refrigerant circuit in the parallel dehumidifying heating mode.
  • the heating mode is an operation mode in which the blowing air is heated and blown out to a vehicle compartment which is a space to be air conditioned.
  • the series dehumidifying and heating mode and the parallel dehumidifying and heating mode are operation modes for reheating the cooled and dehumidified blowing air and blowing it out to a vehicle compartment which is an air conditioning target space.
  • the cooling mode is an operation mode in which the blowing air is cooled and blown out to a vehicle compartment which is a space to be air conditioned.
  • the flow of the refrigerant in the refrigerant circuit in the heating mode is indicated by a solid arrow
  • the flow of the refrigerant in the refrigerant circuit in the parallel dehumidifying heating mode is indicated by a hatched hatched arrow
  • the series dehumidification mode and the cooling mode are further provided.
  • the flow of the refrigerant in the refrigerant circuit is indicated by a white arrow.
  • a HFC refrigerant (specifically, R134a) is employed as the refrigerant, and the vapor compression subcritical refrigeration cycle in which the high-pressure refrigerant pressure Pd does not exceed the critical pressure of the refrigerant is used.
  • R134a a HFC refrigerant
  • the vapor compression subcritical refrigeration cycle in which the high-pressure refrigerant pressure Pd does not exceed the critical pressure of the refrigerant is used.
  • an HFO-based refrigerant for example, R1234yf
  • the refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates the cycle together with the refrigerant.
  • the refrigeration cycle apparatus 10 includes a compressor 11, a condenser 12, a first pressure reducing valve 15a (first pressure reducing unit), a second pressure reducing valve 15b (second pressure reducing unit), an outdoor evaporator 16, a check valve 17, and indoor evaporation.
  • the evaporation pressure control valve 19 the accumulator 20 (pressure fluctuation suppression unit), the first open / close valve 21 (open / close unit), the second open / close valve 22, the low pressure side charging port 23, and the high pressure side charging port 24 doing.
  • the compressor 11 sucks, compresses and discharges the refrigerant in the refrigeration cycle apparatus 10.
  • the compressor 11 is disposed in the hood of the vehicle.
  • the compressor 11 is configured as an electric compressor that drives, by an electric motor, a fixed displacement type compression mechanism whose discharge displacement is fixed.
  • this compression mechanism various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be adopted.
  • the operation (rotational speed) of the electric motor is controlled by a control signal output from the air conditioning control device, and either type of AC motor or DC motor may be adopted. Then, the refrigerant discharge capacity of the compression mechanism is changed by the air conditioning control device controlling the number of rotations of the electric motor.
  • the refrigerant inlet side of the condenser 12 is connected to the discharge port of the compressor 11.
  • the condenser 12 heats the cooling water by heat exchange between the high-temperature high-pressure discharge refrigerant discharged from the compressor 11 and the cooling water that is the heat exchange fluid flowing through the heating unit 25 at least in the heating mode. Heat exchanger.
  • the high pressure refrigerant condenses when the heat of the high pressure refrigerant is dissipated to the cooling water.
  • the heating unit 25 includes a condenser 12, a cooling water circulation circuit 26, a heater core 27, and a cooling water pump 28.
  • the heating unit 25 heats the blown air, which is a heat exchange fluid, using the high-pressure refrigerant discharged from the compressor 11 as a heat source.
  • a liquid containing at least ethylene glycol, dimethylpolysiloxane or a nanofluid, or an antifreeze liquid is used as the cooling water flowing in the cooling water circulation circuit 26 .
  • the cooling water circulation circuit 26 is an annular flow path for circulating the cooling water between the condenser 12 and the heater core 27.
  • the condenser 12, the heater core 27, and the cooling water pump 28 are arranged in this order.
  • the cooling water pump 28 circulates the cooling water in the cooling water circulation circuit 26 by sucking the cooling water and discharging it to the condenser 12 side.
  • the cooling water pump 28 is an electric pump, and is a cooling water flow rate adjustment unit that adjusts the flow rate of the cooling water circulating in the cooling water circulation circuit 26.
  • the heater core 27 is disposed in a casing 31 described later.
  • the heater core 27 heats the blowing air by heat exchange between the cooling water heated by the condenser 12 and the blowing air which is a fluid for heat exchange.
  • the condenser 12 heats the blowing air through the heater core 27.
  • One inlet / outlet side of the first three-way joint 13 a is connected to the refrigerant outlet of the condenser 12.
  • Such a three-way joint may be formed by joining a plurality of pipes, or may be formed by providing a plurality of refrigerant passages in a metal block or a resin block.
  • the refrigeration cycle apparatus 10 is provided with second to fourth three-way joints 13b to 13d as described later.
  • the basic configuration of the second to fourth three-way joints 13b to 13d is the same as that of the first three-way joint 13a.
  • the three-way joints function as branches or junctions.
  • the first three-way joint 13a in the parallel dehumidifying and heating mode one of the three inlets and outlets is used as an inlet, and the remaining two are used as outlets. Therefore, the first three-way joint 13a in the parallel dehumidifying and heating mode functions as a branch unit that branches the flow of the refrigerant flowing from one inlet and flows out from the two outlets.
  • the fourth three-way joint 13d in the parallel dehumidifying and heating mode functions as a joining portion which joins the refrigerants flowing from the two inlets and causes the refrigerant to flow out from one outlet.
  • a first refrigerant passage 14a for guiding the refrigerant flowing out of the condenser 12 to the refrigerant inlet side of the outdoor evaporator 16 is connected to another inflow / outlet of the first three-way joint 13a. Further, at the other inflow / outlet of the first three-way joint 13a, the inlet side of the second pressure reducing valve 15b disposed in the second refrigerant passage 14b described later (specifically, A fourth refrigerant passage 14d leading to one inflow / outlet of the third three-way joint 13c is connected.
  • a first pressure reducing valve 15a is disposed in the first refrigerant passage 14a.
  • the first pressure reducing valve 15 a is a first pressure reducing portion capable of changing the opening area of the first refrigerant passage 14 a and reducing the pressure of the refrigerant flowing out of the condenser 12 at least in the heating mode.
  • the first pressure reducing valve 15a is a variable throttle mechanism having a valve body configured to be able to change the throttle opening degree, and an electric actuator including a stepping motor that changes the throttle opening degree of the valve body.
  • the first pressure reducing valve 15a is configured as a variable throttle mechanism with a fully open function that functions as a simple refrigerant passage without exerting the refrigerant pressure reducing function by fully opening the throttle opening degree.
  • the operation of the first pressure reducing valve 15a is controlled by a control signal (control pulse) output from the air conditioning controller.
  • the refrigerant inlet side of the outdoor evaporator 16 is connected to the outlet side of the first pressure reducing valve 15a.
  • the outdoor evaporator 16 exchanges heat between the refrigerant flowing out of the first pressure reducing valve 15a (the condenser 12) and the outside air blown from a blowing fan (not shown).
  • the outdoor evaporator 16 is disposed on the front side of the vehicle in the vehicle bonnet.
  • the blower fan is an electric blower whose rotational speed (blowing capacity) is controlled by a control voltage output from the air conditioning control device.
  • the second refrigerant passage 14 b is connected to the refrigerant outlet side of the outdoor evaporator 16.
  • the second refrigerant passage 14 b is a passage that leads the refrigerant flowing out of the outdoor evaporator 16 to the suction side of the compressor 11 via the indoor evaporator 18.
  • the second refrigerant passage 14b, the second three-way joint 13b, the check valve 17, the third three-way joint 13c, and the second pressure reducing valve 15b, the indoor evaporator 18, the evaporation pressure adjusting valve 19, the fourth three-way joint 13d, and the accumulator 20 and the low pressure side charging port 23 are arranged in this order with respect to the refrigerant flow.
  • the end of the second refrigerant passage 14 b is connected to the suction port of the compressor 11.
  • the passage 14c is connected.
  • the fourth refrigerant passage 14d described above is connected to the third three-way joint 13c.
  • the check valve 17 only allows the refrigerant to flow from the second three-way joint 13 b side (outside evaporator 16 side) to the indoor evaporator 18 side.
  • the second pressure reducing valve 15 b is disposed between the outdoor evaporator 16 and the indoor evaporator 18 in the second refrigerant passage 14 b.
  • the second pressure reducing valve 15 b is disposed between the third three-way joint 13 c and the indoor evaporator 18 in the second refrigerant passage 14 b.
  • the second pressure reducing valve 15 b is a second pressure reducing portion capable of changing the opening area of the second refrigerant passage 14 b and reducing the pressure of the refrigerant flowing out of the outdoor evaporator 16 and flowing into the indoor evaporator 18.
  • the basic configuration of the second pressure reducing valve 15b is the same as that of the first pressure reducing valve 15a.
  • the second pressure reducing valve 15b of the present embodiment is configured by a variable throttle mechanism with a fully closing function that closes the refrigerant passage when the throttle opening degree is fully closed.
  • the refrigerant circuit can be switched by fully closing the second pressure reducing valve 15b and closing the second refrigerant passage 14b.
  • the second pressure reducing valve 15b has a function as a refrigerant pressure reducing unit and also has a function as a refrigerant circuit switching device that switches the refrigerant circuit of the refrigerant circulating in the cycle.
  • the indoor evaporator 18 is in the cooling mode, in the series dehumidifying and heating mode, and in the parallel dehumidifying and heating mode, before the heater core 27 which is a heat exchange fluid with the refrigerant flowing out from the second pressure reducing valve 15b (outdoor evaporator 16). It is a heat exchanger for cooling which exchanges heat with air.
  • the blown air is cooled by evaporating the refrigerant decompressed by the second pressure reducing valve 15b to exhibit an endothermic effect.
  • the indoor evaporator 18 is disposed in the casing 31 of the indoor air conditioning unit 30 on the upstream side of the air flow of the heater core 27.
  • the inlet side of the evaporating pressure adjusting valve 19 is connected to the second refrigerant passage 14 b on the refrigerant outlet side of the indoor evaporator 18.
  • the evaporation pressure control valve 19 has a function of adjusting the refrigerant evaporation pressure Pe in the indoor evaporator 18 to be equal to or higher than the frost formation suppression pressure APe in order to suppress frost formation of the indoor evaporator 18.
  • the evaporation pressure control valve 19 functions to adjust the refrigerant evaporation temperature Te in the indoor evaporator 18 to the frost formation suppression temperature ATe or more.
  • R134a is employed as the refrigerant, and the frost formation suppression temperature ATe is set to a value slightly higher than 0 ° C. Therefore, the frost formation suppression pressure APe is set to a value slightly higher than 0.293 MPa, which is the saturation pressure of R134a at 0 ° C.
  • a fourth three-way joint 13 d is connected to the second refrigerant passage 14 b on the outlet side of the evaporation pressure adjusting valve 19.
  • the third refrigerant passage 14c described above is connected to the fourth three-way joint 13d. That is, the terminal end of the third refrigerant passage 14c is connected to the fourth three-way joint 13d which is a joining portion disposed in the second refrigerant passage 14b between the evaporation pressure adjusting valve 19 and the compressor 11.
  • the inlet side of the accumulator 20 is connected to still another inflow / outlet of the fourth three-way joint 13d. That is, the accumulator 20 is disposed between the evaporation pressure control valve 19 and the low pressure side charging port 23 in the second refrigerant passage 14b. In the present embodiment, the accumulator 20 is provided on the downstream side of the fourth three-way joint 13d, which is a junction portion of the third refrigerant passage 14c with the second refrigerant passage 14b.
  • the accumulator 20 has a buffer space 20a formed therein.
  • the accumulator 20 is a gas-liquid separator that separates the gas and liquid of the refrigerant that has flowed into the inside in the buffer space 20a and stores the surplus refrigerant in the cycle.
  • the buffer space 20 a of the accumulator 20 also functions as a liquid storage unit that stores the excess refrigerant in the cycle.
  • the volume of the flow path between the low pressure side charging port 23 and the evaporation pressure control valve 19 is increased by the buffer space 20 a of the accumulator 20 as compared with the case where the buffer space 20 a is not provided. Therefore, the buffer space 20a of the accumulator 20 has a function as a pressure fluctuation suppressing portion that suppresses a rapid fluctuation of the internal pressure of the second refrigerant passage 14b when the refrigerant is charged into the refrigeration cycle apparatus 10 from the low pressure side charging port 23. Play.
  • the suction port side of the compressor 11 is connected to the gas phase refrigerant outlet of the accumulator 20. Therefore, the accumulator 20 suppresses the suction of the liquid-phase refrigerant into the compressor 11 and functions to prevent the liquid compression in the compressor 11.
  • a first on-off valve 21 is disposed in a third refrigerant passage 14c connecting the second three-way joint 13b and the fourth three-way joint 13d.
  • the first on-off valve 21 is an electromagnetic valve as a refrigerant circuit switching device that switches the refrigerant circuit that circulates the refrigerant by opening and closing the third refrigerant passage 14c.
  • the first open / close valve 21 is an open / close unit whose operation is controlled by a control signal output from the air conditioning control device.
  • a second on-off valve 22 is disposed in a fourth refrigerant passage 14d that connects the first three-way joint 13a and the third three-way joint 13c.
  • the second on-off valve 22 is an electromagnetic valve as a refrigerant circuit switching device that switches the refrigerant circuit that circulates the refrigerant by opening and closing the fourth refrigerant passage 14d.
  • the basic configuration of the second on-off valve 22 is the same as that of the first on-off valve 21.
  • the low pressure side charging port 23 is disposed in the second refrigerant passage 14 b downstream of the evaporating pressure adjusting valve 19. In the present embodiment, the low pressure side charging port 23 is disposed between the accumulator 20 and the compressor 11 in the second refrigerant passage 14 b. The low pressure side charging port 23 is for charging the refrigerant into the refrigeration cycle apparatus 10 while operating the compressor 11 after the vehicle (the refrigeration cycle apparatus 10) is shipped.
  • the high pressure side charging port 24 is disposed in the first refrigerant passage 14 a downstream of the condenser 12. In the present embodiment, the high pressure side charging port 24 is disposed in the first refrigerant passage 14a between the first three-way joint 13a and the first pressure reducing valve 15a. The high pressure side charging port 24 is for charging the refrigerant into the refrigeration cycle apparatus 10 before shipment of the vehicle (refrigeration cycle apparatus 10).
  • the indoor air conditioning unit 30 is for blowing out the blowing air whose temperature has been adjusted by the refrigeration cycle apparatus 10 into the vehicle interior which is the space to be air conditioned.
  • the indoor air conditioning unit 30 is disposed inside the instrument panel at the foremost part of the vehicle interior.
  • the indoor air conditioning unit 30 is configured by housing a blower 32, an indoor evaporator 18, and a heater core 27 in a casing 31 forming the outer shell thereof.
  • the casing 31 is an air passage forming portion that forms an air passage for blowing air blown into a vehicle compartment, which is a space to be air conditioned.
  • the casing 31 has a certain degree of elasticity and is molded of a resin (for example, polypropylene) which is excellent in strength.
  • a device 33 is arranged.
  • An air blower (blower) 32 for blowing the air taken in through the inside / outside air switching device 33 into the space to be air-conditioned is disposed downstream of the air flow of the inside / outside air switching device 33.
  • the blower 32 is an electric blower that drives a centrifugal multi-blade fan (sirocco fan) by an electric motor.
  • the number of rotations (air flow rate) of the blower 32 is controlled by the control voltage output from the air conditioning control device.
  • An indoor evaporator 18 is disposed downstream of the air flow of the blower 32 in the air passage formed in the casing 31. Furthermore, the downstream side of the indoor evaporator 18 of the air passage formed in the casing 31 is bifurcated, and the indoor condenser passage 35 and the cold air bypass passage 36 are formed in parallel.
  • a heater core 27 is disposed in the indoor condenser flow passage 35. That is, the indoor condenser flow passage 35 is a flow passage through which the blown air which exchanges heat with the refrigerant in the heater core 27 flows.
  • the indoor evaporator 18 and the heater core 27 are disposed in this order with respect to the blowing air flow. In other words, the indoor evaporator 18 is disposed upstream of the heater core 27 in the flow of the blown air.
  • the cold air bypass passage 36 is a flow passage for flowing the blown air, which has passed through the indoor evaporator 18, to the downstream side by bypassing the heater core 27.
  • An air mix door 34 is disposed on the downstream side of the air flow of the indoor evaporator 18 and on the upstream side of the air flow of the heater core 27.
  • the air mix door 34 is an air volume ratio adjustment unit that adjusts the air volume ratio that allows the heater core 27 to pass through the blown air after passing through the indoor evaporator 18 according to the control signal output from the air conditioning control device.
  • a mixing channel 37 is formed in the casing 31 on the downstream side of the merging portion of the indoor condenser channel 35 and the cold air bypass passage 36. In the mixing flow path 37, the blowing air heated by the heater core 27 and the blowing air not passing through the cold air bypass passage 36 and not heated by the heater core 27 are mixed.
  • a plurality of opening holes are disposed at the most downstream portion of the air flow of the casing 31 for blowing the air (air-conditioned air) mixed in the mixing flow path 37 into the vehicle compartment which is the air conditioning target space.
  • the temperature of the conditioned air mixed in the mixing flow path 37 is adjusted by adjusting the air volume ratio of the air volume passing through the heater core 27 and the air volume passing through the cold air bypass passage 36 by the air mix door 34. As a result, the temperature of the conditioned air blown out from the opening holes into the vehicle compartment, which is the space to be conditioned, is adjusted.
  • the air mix door 34 functions as a temperature control unit that adjusts the temperature of the conditioned air blown into the vehicle compartment, which is the space to be conditioned.
  • the air mix door 34 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 air conditioning controller.
  • the air mix door 34 switches to a flow path in which the blowing air flows in the order of the indoor evaporator 18 ⁇ the heater core 27 in the heating mode, in the series dehumidifying heating mode, and in the parallel dehumidifying heating mode. Furthermore, in the cooling mode, it plays a role as an air passage switching device in which the blown air bypasses the heater core 27 and switches to the flow passage to the indoor evaporator 18.
  • the operation of the air conditioner 1 of the present embodiment will be described.
  • the operation of the heating mode, the cooling mode, the series dehumidifying heating mode, and the parallel dehumidifying heating mode can be switched.
  • the switching of each operation mode is performed by executing an air conditioning control program stored in advance in the air conditioning control device.
  • the air conditioning control device opens the first on-off valve 21 and closes the second on-off valve 22 to place the first pressure reducing valve 15a in the throttling state for exerting the pressure reducing function. Is completely closed.
  • a vapor compression refrigeration cycle in which the refrigerant is circulated in the order of 11 is configured.
  • the air conditioning control device appropriately controls the operation of various air conditioning devices connected to the output side.
  • the control signal output from the air conditioning controller to the electric actuator for driving the air mix door is determined such that the air mix door 34 fully closes the cold air bypass passage 36. That is, this control signal is determined such that the total flow rate of the blown air after passing through the indoor evaporator 18 passes through the air passage on the heater core 27 side.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the refrigerant flowing into the condenser 12 exchanges heat with the cooling water flowing in the cooling water circulation circuit 26 and radiates heat.
  • the cooling water flowing in the cooling water circulation circuit 26 is heated. Since the air mix door 34 opens the air passage on the side of the heater core 27, the blown air which is blown from the blower 32 and passes through the indoor evaporator 18 is heated by the heater core 27.
  • the refrigerant flowing out of the condenser 12 flows out from the first three-way joint 13a toward the first refrigerant passage 14a.
  • the refrigerant that has flowed out to the first refrigerant passage 14a is depressurized until it becomes a low pressure refrigerant by the first pressure reducing valve 15a.
  • the low-pressure refrigerant reduced in pressure by the first pressure reducing valve 15a flows into the outdoor evaporator 16 and absorbs heat from the outside air blown from the blower fan.
  • the refrigerant flowing out of the outdoor evaporator 16 flows out from the second three-way joint 13b to the third refrigerant passage 14c because the first open / close valve 21 is open and the second pressure reducing valve 15b is fully closed.
  • the refrigerant which has flowed out to the third refrigerant passage 14c side flows into the accumulator 20 through the fourth three-way joint 13d and is separated into gas and liquid. Then, the gas phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed by the compressor 11 again.
  • heating the vehicle interior can be performed by blowing the blown air heated by the condenser 12 into the vehicle interior which is the space to be air conditioned.
  • Cooling mode In the cooling mode, the air conditioning control device closes the first on-off valve 21 and closes the second on-off valve 22 to fully open the first pressure reducing valve 15a and to narrow the second pressure reducing valve 15b. .
  • a vapor compression type refrigeration cycle in which the refrigerant is circulated in the order of 15b ⁇ indoor evaporator 18 ⁇ evaporation pressure control valve 19 ⁇ accumulator 20 ⁇ compressor 11 is configured.
  • the air conditioning control device appropriately controls the operation of various air conditioning devices connected to the output side.
  • the air mix door 34 makes the cold air bypass passage 36 fully open, and the total flow of the blown air after passing through the indoor evaporator 18 is cold air. It is decided to pass the bypass passage 36.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12.
  • the air mix door 34 completely closes the air passage on the heater core 27 side, the cooling water flowing into the heater core 27 flows out of the heater core 27 almost without heat exchange with the blowing air.
  • the refrigerant flowing out of the condenser 12 flows out from the first three-way joint 13a toward the first refrigerant passage 14a.
  • the refrigerant that has flowed out to the first refrigerant passage 14a flows into the first pressure reducing valve 15a.
  • the first pressure reducing valve 15a is fully open, the refrigerant flowing out of the condenser 12 flows into the outdoor evaporator 16 without being reduced in pressure by the first pressure reducing valve 15a.
  • the refrigerant that has flowed into the outdoor evaporator 16 dissipates heat to the outside air blown from the blower fan by the outdoor evaporator 16.
  • the refrigerant flowing out of the outdoor evaporator 16 flows into the second refrigerant passage 14b through the second three-way joint 13b because the first open / close valve 21 is closed.
  • the refrigerant flowing into the second refrigerant passage 14b is depressurized until it becomes a low pressure refrigerant by the second pressure reducing valve 15b.
  • the low pressure refrigerant decompressed by the second pressure reducing valve 15 b flows into the indoor evaporator 18, absorbs heat from the air blown from the blower 32, and evaporates. Thereby, the blowing air is cooled.
  • the refrigerant flowing out of the indoor evaporator 18 flows into the accumulator 20 through the evaporation pressure control valve 19 and is separated into gas and liquid. Then, the gas phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed by the compressor 11 again.
  • cooling of the vehicle interior can be performed by blowing out the blown air cooled by the indoor evaporator 18 into the vehicle interior that is the space to be air conditioned.
  • (C) Series dehumidifying and heating mode In the series dehumidifying and heating mode, the air conditioning control device closes the first on-off valve 21, closes the second on-off valve 22, sets the first pressure reducing valve 15a in a throttling state, and the second pressure reducing valve 15b. It will be in the squeezed state. Further, the air conditioning control device displaces the air mix door 34 so that the air passage on the heater core 27 side is fully opened and the cold air bypass passage 36 side is fully closed.
  • the compressor 11 ⁇ the condenser 12 ⁇ (first pressure reducing valve 15a) ⁇ outdoor evaporator 16 ⁇ (check valve 17) ⁇ second pressure reducing valve 15b ⁇ indoor evaporator 18 ⁇ evaporation pressure adjusting valve 19 ⁇ accumulator 20 ⁇ compressor 11
  • a vapor compression type refrigeration cycle in which the refrigerant circulates is configured. That is, a refrigeration cycle in which the outdoor evaporator 16 and the indoor evaporator 18 are connected in series to the refrigerant flow is configured.
  • the refrigeration cycle is configured in which the condenser 12 functions as a radiator and the indoor evaporator 18 functions as an evaporator. Furthermore, when the saturation temperature of the refrigerant in the outdoor evaporator 16 is higher than the outside air temperature Tam, the outdoor evaporator 16 functions as a radiator, and the saturation temperature of the refrigerant in the outdoor evaporator 16 is lower than the outside air temperature Tam In addition, the outdoor evaporator 16 functions as an evaporator.
  • the air conditioning control device appropriately controls the operation of various air conditioning devices connected to the output side.
  • the control signal output from the air conditioning controller to the electric actuator for driving the air mix door is determined so that the air mix door 34 fully closes the cold air bypass passage 36 as in the heating mode. That is, this control signal is determined such that the total flow rate of the blown air after passing through the indoor evaporator 18 passes through the air passage on the heater core 27 side.
  • the dehumidified heating of the vehicle interior can be performed by reheating the blown air cooled and dehumidified by the indoor evaporator 18 by the heater core 27 into the vehicle interior which is the space to be air conditioned. It can be carried out. Furthermore, the heating capacity of the blowing air in the heater core 27 can be adjusted by adjusting the throttle opening degree of the first pressure reducing valve 15a and the second pressure reducing valve 15b.
  • the air conditioning control device opens the first on-off valve 21 and opens the second on-off valve 22 to make the first pressure reducing valve 15a into a throttling state, and the second pressure reducing valve 15b. It will be in the squeezed state.
  • a vapor compression refrigeration cycle in which the refrigerant is circulated in the order of the machine 11 is configured.
  • the flow of the refrigerant flowing out of the condenser 12 is branched by the first three-way joint 13a, and one branched refrigerant is divided into the first pressure reducing valve 15a ⁇ outdoor evaporator 16 ⁇ the compressor 11 While flowing in order, the refrigerant circuit of the other branched refrigerant is made to flow in the order of the second pressure reducing valve 15 b ⁇ the indoor evaporator 18 ⁇ the evaporation pressure adjusting valve 19 ⁇ the compressor 11.
  • the air conditioning control device appropriately controls the operation of various air conditioning devices connected to the output side.
  • the control signal output from the air conditioning controller to the electric actuator for driving the air mix door is determined so that the air mix door 34 fully closes the cold air bypass passage 36 as in the heating mode. That is, this control signal is determined such that the total flow rate of the blown air after passing through the indoor evaporator 18 passes through the air passage on the heater core 27 side.
  • the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12. Since the air mix door 34 opens the air passage on the heater core 27 side, the refrigerant flowing into the condenser 12 exchanges heat with the air that has been blown from the blower 32 and passed through the indoor evaporator 18 as in the heating mode. And dissipate heat. Thereby, the blowing air is heated.
  • the flow of the refrigerant flowing out of the condenser 12 is branched at the first three-way joint 13a because the second on-off valve 22 is open.
  • One refrigerant branched by the first three-way joint 13 a flows out to the first refrigerant passage 14 a side.
  • the refrigerant that has flowed out to the first refrigerant passage 14a is depressurized until it becomes a low pressure refrigerant by the first pressure reducing valve 15a.
  • the low-pressure refrigerant decompressed by the first pressure reducing valve 15a flows into the outdoor evaporator 16 and absorbs heat from the outside air blown by the blower fan.
  • the other refrigerant branched at the first three-way joint 13a flows out to the fourth refrigerant passage 14d side.
  • the refrigerant flowing out to the fourth refrigerant passage 14d side does not flow out to the outdoor evaporator 16 side by the action of the check valve 17, and the second pressure reducing valve via the second on-off valve 22 and the third three-way joint 13c. It flows into 15b.
  • the refrigerant flowing into the second pressure reducing valve 15b is reduced in pressure until it becomes a low pressure refrigerant. Then, the low pressure refrigerant decompressed by the second pressure reducing valve 15 b flows into the indoor evaporator 18, absorbs heat from the air blown from the blower 32, and evaporates. Thereby, the blowing air is cooled.
  • the refrigerant flowing out of the indoor evaporator 18 is depressurized by the evaporation pressure adjusting valve 19 and has a pressure equal to that of the refrigerant flowing out of the outdoor evaporator 16.
  • the refrigerant flowing out of the evaporation pressure adjusting valve 19 flows into the fourth three-way joint 13 d and merges with the refrigerant flowing out of the outdoor evaporator 16.
  • the refrigerant joined at the fourth three-way joint 13d flows into the accumulator 20 and is separated into gas and liquid. Then, the gas phase refrigerant separated by the accumulator 20 is sucked from the suction side of the compressor 11 and compressed by the compressor 11 again.
  • the dehumidified heating of the passenger compartment is performed by reheating the blow air cooled and dehumidified by the indoor evaporator 18 by the condenser 12 and blowing it into the vehicle compartment which is the air conditioning target space. It can be performed.
  • the refrigerant evaporation temperature in the outdoor evaporator 16 can be made lower than the refrigerant evaporation temperature in the indoor evaporator 18. Therefore, the heat absorption amount in the outdoor evaporator 16 can be increased by expanding the temperature difference between the refrigerant evaporation temperature in the outdoor evaporator 16 and the outside air.
  • the heating capacity of the blowing air in the heater core 27 can be increased more than the refrigeration cycle apparatus in which the refrigerant evaporation temperature in the outdoor evaporator 16 is equal to the refrigerant evaporation temperature in the indoor evaporator 18.
  • the refrigeration cycle apparatus 10 of the present embodiment it is possible to realize comfortable heating of the vehicle interior by switching between the heating mode, the cooling mode, the series dehumidifying heating mode, and the parallel dehumidifying heating mode. it can.
  • the first pressure reducing valve 15a and the second pressure reducing valve 15b are fully opened. Furthermore, in a state where the first on-off valve 21 and the second on-off valve 22 are opened, the refrigeration cycle device 10 is evacuated from the high-pressure charging port 24 and the low-pressure charging port 23.
  • This vacuuming is performed to remove the air inside the refrigeration cycle apparatus 10.
  • the reason is that when air is left inside the refrigeration cycle apparatus 10, the moisture in the air may freeze inside the refrigeration cycle apparatus 10 and interfere with the circulation of the refrigerant.
  • the first pressure reducing valve 15a and the second pressure reducing valve 15b are fully opened. Furthermore, the refrigerant cycle device 10 is filled with the refrigerant from the high pressure side charging port 24 in a state where the first on-off valve 21 and the second on-off valve 22 are opened.
  • the first pressure reducing valve 15a and the second pressure reducing valve 15b are fully opened. Furthermore, the refrigerant cycle device 10 is filled with the refrigerant from the low pressure side charging port 23 in a state where the first on-off valve 21 and the second on-off valve 22 are opened and the compressor 11 is operated.
  • the second refrigerant at the time of charging the refrigerant from the low pressure side charging port 23 to the second refrigerant passage 14b between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23 An accumulator 20, which is a pressure fluctuation suppressing portion that suppresses a rapid fluctuation of the internal pressure of the passage 14b, is disposed.
  • the accumulator 20 is provided with the buffer space 20a, when the refrigerant is charged from the low pressure side charging port 23 to the refrigeration cycle apparatus 10 via the second refrigerant passage 14b, the refrigerant in the second refrigerant passage 14b is Abrupt changes in internal pressure can be suppressed. The reason is that the air in the buffer space 20a is compressed. For this reason, pressure fluctuation on the outlet side of the evaporating pressure regulating valve 19 can be suppressed. Therefore, even if the low pressure side charging port 23 is disposed on the downstream side of the evaporation pressure adjustment valve 19, the deterioration in the durability of the evaporation pressure adjustment valve can be suppressed.
  • the degree of freedom of the mounting position of the charging port can be improved without deteriorating the durability of the evaporation pressure control valve.
  • the buffer space 20a is constituted by an accumulator 20 which is a liquid storage unit for storing the surplus refrigerant. According to this, since the buffer space 20a of the accumulator 20 which is a liquid storage section originally provided in the refrigeration cycle apparatus 10 is used as a pressure fluctuation suppression section, it is necessary to newly provide the pressure fluctuation suppression section in the refrigeration cycle apparatus 10 There is not. Therefore, even if the refrigeration cycle apparatus 10 is arranged at the downstream side of the evaporation pressure adjusting valve 19 without increasing the cost and without increasing the size, the evaporation pressure adjusting valve The refrigeration cycle apparatus 10 can be provided in which the durability of No. 19 does not deteriorate.
  • a muffler 51 is disposed in the second refrigerant passage 14 b between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23.
  • the muffler 51 is disposed in the second refrigerant passage 14 b between the accumulator 20 and the low pressure side charging port 23.
  • a buffer space 51a is formed in the muffler 51.
  • the buffer space 51 a is for reducing pressure pulsation accompanying discharge of the refrigerant by the compressor 11.
  • the buffer space 51a also functions as a pressure fluctuation suppressing unit that suppresses pressure fluctuation of the second refrigerant passage 14b when the refrigerant is charged from the low pressure side charging port 23 to the second refrigerant passage 14b.
  • the volume of the flow path through which the refrigerant flows between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23 is increased by the buffer space 51 a of the muffler 51.
  • the air in the buffer space 51a is compressed, thereby further rapidly changing the internal pressure of the second refrigerant passage 14b. It can be suppressed. Therefore, the pressure fluctuation on the outlet side of the evaporating pressure regulating valve 19 can be further suppressed.
  • the buffer space 51 a is configured by the muffler 51 for reducing pressure pulsations accompanying discharge of the refrigerant by the compressor 11. According to this, in the refrigeration cycle apparatus 10 in which the muffler 51 is provided, it is not necessary to newly provide the pressure fluctuation suppression unit in the refrigeration cycle apparatus 10. Therefore, even if the refrigeration cycle apparatus 10 is arranged at the downstream side of the evaporation pressure adjusting valve 19 without increasing the cost and without increasing the size, the evaporation pressure adjusting valve The refrigeration cycle apparatus 10 can be provided in which the durability of No. 19 does not deteriorate. Further, pressure fluctuation on the outlet side of the evaporation pressure adjusting valve 19 can be further suppressed when the refrigerant from the low pressure side charging port 23 is charged into the refrigeration cycle apparatus 10.
  • a buffer space 52 which is a pressure fluctuation suppressing portion, is provided in the second refrigerant passage 14b between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23.
  • the buffer space 52 is provided in the second refrigerant passage 14 b between the accumulator 20 and the low pressure side charging port 23.
  • the buffer space 52 is formed by repeatedly bending the pipe.
  • the buffer space 52 increases the length of the flow path through which the refrigerant flows between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23, and the volume of the flow path through which the refrigerant flows increases.
  • the buffer space 52 may be configured by increasing the volume of the flow path through which the refrigerant flows by branching a plurality of pipes and collecting the plurality of pipes.
  • the volume of the flow path through which the refrigerant flows between the evaporation pressure adjusting valve 19 and the low pressure side charging port 23 is increased by the buffer space 52. Therefore, when the refrigerant is charged from the low pressure side charging port 23 to the refrigeration cycle apparatus 10 via the second refrigerant passage 14b, the air in the buffer space 52 is compressed, whereby the refrigerant in the second refrigerant passage 14b is Abrupt changes in internal pressure can be further suppressed. Therefore, the pressure fluctuation on the outlet side of the evaporating pressure regulating valve 19 can be further suppressed.
  • the buffer space 52 is constituted by piping. According to this, a structure for suppressing pressure fluctuation on the outlet side of the evaporating pressure adjusting valve 19 can be realized at low cost.
  • each component apparatus which comprises the refrigerating cycle apparatus 10 is not limited to what was disclosed by the above-mentioned embodiment.
  • the above-mentioned embodiment explained the example which adopted a motor-ized compressor as compressor 11, it is not limited to this.
  • an engine drive compressor driven by a rotational drive force transmitted from the vehicle travel engine via a pulley, a belt, etc. is adopted as the compressor 11. It is also good.
  • each of the above embodiments may be combined as appropriate in the feasible range.
  • it may be an air conditioner in which the refrigeration cycle apparatus 10 of the second embodiment and the refrigeration cycle apparatus 10 of the third embodiment are combined.
  • a restriction such as an orifice is provided in the low pressure side charging port 23 to further suppress pressure fluctuation on the outlet side of the evaporation pressure adjusting valve 19 when charging the refrigerant from the low pressure side charging port 23 to the refrigeration cycle apparatus 10 May be an embodiment.
  • coolant after shipment of the air conditioning apparatus 1 is not limited to what was disclosed by the above-mentioned embodiment. Another example will be described below.
  • the high pressure side charging port 24 enters the refrigeration cycle apparatus 10 Fill the specified amount of refrigerant.
  • the refrigerant cycle device 10 is filled with the refrigerant from the low pressure side charging port 23 in a state where the compressor 11 is operated.
  • the refrigerant cycle device 10 is filled with a specified amount of refrigerant from the high pressure side charging port 24, the refrigerant is charged from the low pressure side charging port 23.
  • the refrigeration cycle apparatus 10 when the refrigerant is charged into the refrigeration cycle apparatus 10 from the low pressure side charging port 23, the refrigeration cycle apparatus 10 is charged with the specified amount of refrigerant. According to this, it is possible to reduce the pressure difference between the refrigerant charged into the refrigeration cycle device from the low pressure side charging port and the refrigerant in the refrigeration cycle device. Therefore, when the refrigerant is charged into the refrigeration cycle apparatus from the low pressure side charging port, the reverse pressure hardly acts on the evaporation pressure regulating valve 19.
  • the specified amount of refrigerant charged from the high pressure side charging port 24 into the refrigeration cycle apparatus 10 is the outlet of the evaporation pressure adjusting valve 19 when the refrigerant is charged from the low pressure side charging port 23 to the second refrigerant passage 14b. It is a predetermined amount necessary to suppress the rapid fluctuation of the pressure fluctuation on the side.

Landscapes

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

Abstract

Ce dispositif à cycle frigorifique comprend: un évaporateur externe (16) pour échanger de la chaleur entre un fluide frigorigène qui s'écoule hors d'une section de chauffage (25) et l'air extérieur; un évaporateur interne (18) pour échanger de la chaleur entre un fluide frigorigène qui s'écoule hors de l'évaporateur externe et un fluide devant être soumis à un échange de chaleur; une soupape de régulation de pression d'évaporation (19) disposée sur le côté de sortie de fluide frigorigène de l'évaporateur interne et régulant la pression d'évaporation de fluide frigorigène dans l'évaporateur interne; un orifice de charge (23) disposé en aval de la soupape de régulation de pression d'évaporation; et une section de suppression de changement de pression (20, 51, 52) disposée entre la soupape de régulation de pression d'évaporation et l'orifice de chargement et formant un espace tampon (20a, 51a, 52). Pendant la charge d'un fluide frigorigène à partir de l'orifice de chargement, un changement brusque de pression à l'intérieur d'un second passage de fluide frigorigène (14b) dans lequel la soupape de régulation de pression d'évaporation est disposée peut être supprimé en raison de la section de suppression de changement de pression. Par conséquent, le degré de liberté de la position de montage de l'orifice de chargement peut être augmenté sans dégrader la durabilité de la soupape de régulation de pression d'évaporation.
PCT/JP2018/041810 2017-12-05 2018-11-12 Dispositif à cycle frigorifique WO2019111637A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201880078169.5A CN111433538B (zh) 2017-12-05 2018-11-12 制冷循环装置
DE112018006208.2T DE112018006208T5 (de) 2017-12-05 2018-11-12 Kältemittelkreislaufvorrichtung
US16/892,001 US20200292218A1 (en) 2017-12-05 2020-06-03 Refrigeration cycle device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-233196 2017-12-05
JP2017233196A JP2019100644A (ja) 2017-12-05 2017-12-05 冷凍サイクル装置

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/892,001 Continuation US20200292218A1 (en) 2017-12-05 2020-06-03 Refrigeration cycle device

Publications (1)

Publication Number Publication Date
WO2019111637A1 true WO2019111637A1 (fr) 2019-06-13

Family

ID=66751547

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/041810 WO2019111637A1 (fr) 2017-12-05 2018-11-12 Dispositif à cycle frigorifique

Country Status (5)

Country Link
US (1) US20200292218A1 (fr)
JP (1) JP2019100644A (fr)
CN (1) CN111433538B (fr)
DE (1) DE112018006208T5 (fr)
WO (1) WO2019111637A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021204914A1 (fr) * 2020-04-08 2021-10-14 Valeo Systemes Thermiques Systeme de conditionnement thermique pour vehicule automobile
WO2021204915A1 (fr) * 2020-04-08 2021-10-14 Valeo Systemes Thermiques Systeme de conditionnement thermique pour vehicule automobile

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6676682B2 (ja) * 2018-03-09 2020-04-08 マレリ株式会社 空調装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03279015A (ja) * 1990-03-28 1991-12-10 Hitachi Ltd 自動車用空調装置
WO2012118198A1 (fr) * 2011-03-03 2012-09-07 サンデン株式会社 Climatiseur utilisable sur un véhicule
JP2012225637A (ja) * 2011-04-04 2012-11-15 Denso Corp 冷凍サイクル装置
JP2014231948A (ja) * 2013-05-29 2014-12-11 株式会社デンソー ヒートポンプサイクル

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006266636A (ja) * 2005-03-25 2006-10-05 Daikin Ind Ltd 冷凍装置
JP5821756B2 (ja) * 2011-04-21 2015-11-24 株式会社デンソー 冷凍サイクル装置
JP6011484B2 (ja) * 2013-07-31 2016-10-19 株式会社デンソー エジェクタ
JP6295676B2 (ja) * 2014-01-21 2018-03-20 株式会社デンソー ヒートポンプサイクル
JP2016090201A (ja) * 2014-11-11 2016-05-23 株式会社デンソー 冷凍サイクル装置
JP6432339B2 (ja) * 2014-12-25 2018-12-05 株式会社デンソー 冷凍サイクル装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03279015A (ja) * 1990-03-28 1991-12-10 Hitachi Ltd 自動車用空調装置
WO2012118198A1 (fr) * 2011-03-03 2012-09-07 サンデン株式会社 Climatiseur utilisable sur un véhicule
JP2012225637A (ja) * 2011-04-04 2012-11-15 Denso Corp 冷凍サイクル装置
JP2014231948A (ja) * 2013-05-29 2014-12-11 株式会社デンソー ヒートポンプサイクル

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021204914A1 (fr) * 2020-04-08 2021-10-14 Valeo Systemes Thermiques Systeme de conditionnement thermique pour vehicule automobile
WO2021204915A1 (fr) * 2020-04-08 2021-10-14 Valeo Systemes Thermiques Systeme de conditionnement thermique pour vehicule automobile

Also Published As

Publication number Publication date
CN111433538A (zh) 2020-07-17
DE112018006208T5 (de) 2020-09-03
CN111433538B (zh) 2021-09-17
JP2019100644A (ja) 2019-06-24
US20200292218A1 (en) 2020-09-17

Similar Documents

Publication Publication Date Title
JP6295676B2 (ja) ヒートポンプサイクル
JP6015636B2 (ja) ヒートポンプシステム
JP5949648B2 (ja) 冷凍サイクル装置
US20220032732A1 (en) Battery heating device for vehicle
WO2013136693A1 (fr) Dispositif à cycle de réfrigération
WO2014188674A1 (fr) Dispositif à cycle de réfrigération
JP6332560B2 (ja) 車両用空調装置
JP6075058B2 (ja) 冷凍サイクル装置
JP6361830B2 (ja) ヒートポンプサイクル
JP2019045034A (ja) 冷凍サイクル装置
JP6863131B2 (ja) 空調装置
JP6394505B2 (ja) ヒートポンプサイクル
JP2019026110A (ja) 冷凍サイクル装置
JP6711258B2 (ja) 冷凍サイクル装置
WO2013145537A1 (fr) Dispositif de climatisation pour véhicule
WO2019111637A1 (fr) Dispositif à cycle frigorifique
WO2019031221A1 (fr) Dispositif à cycle frigorifique
JP2019217947A (ja) 空調装置
JP6760226B2 (ja) 複合型熱交換器
WO2019065013A1 (fr) Dispositif à cycle frigorifique
WO2014024376A1 (fr) Dispositif à cycles de réfrigération
JP2019105422A (ja) 車両用ジョイントブロック
JP6922856B2 (ja) 冷凍サイクル装置
WO2016136288A1 (fr) Cycle de pompe à chaleur
JP6507453B2 (ja) 車両用空調装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18886677

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 18886677

Country of ref document: EP

Kind code of ref document: A1