WO2020075238A1 - Échangeur de chaleur à plaques et dispositif de pompe à chaleur - Google Patents

Échangeur de chaleur à plaques et dispositif de pompe à chaleur Download PDF

Info

Publication number
WO2020075238A1
WO2020075238A1 PCT/JP2018/037720 JP2018037720W WO2020075238A1 WO 2020075238 A1 WO2020075238 A1 WO 2020075238A1 JP 2018037720 W JP2018037720 W JP 2018037720W WO 2020075238 A1 WO2020075238 A1 WO 2020075238A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
water
flow path
hole
heat exchanger
Prior art date
Application number
PCT/JP2018/037720
Other languages
English (en)
Japanese (ja)
Inventor
博和 南迫
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/037720 priority Critical patent/WO2020075238A1/fr
Priority to US17/265,445 priority patent/US20210231355A1/en
Priority to CN201980062298.XA priority patent/CN112771343A/zh
Priority to EP19872006.2A priority patent/EP3865802B1/fr
Priority to JP2020551096A priority patent/JP7019068B2/ja
Priority to PCT/JP2019/039230 priority patent/WO2020075630A1/fr
Publication of WO2020075238A1 publication Critical patent/WO2020075238A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F25B39/04—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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present invention relates to a plate heat exchanger and a heat pump device.
  • a heat pump device that uses a heat pump cycle
  • a heat pump device that heats water to supply hot water and air conditioning
  • heat exchange between the refrigerant circulating in the refrigerant circuit and the water flowing in the water circuit is performed by a plate-type water-refrigerant heat exchanger to heat the water in the water circuit.
  • a pressure relief valve may be provided in the water circuit (see, for example, Patent Document 1).
  • the temperature of the refrigerant that has entered the water circuit and adiabatically expanded may fall below the freezing point of the water.
  • water is changed to ice by mixing the refrigerant with a temperature below the freezing point of water and the water.
  • the pressure of the refrigerant drops and the refrigerant receives heat from the water, which causes the refrigerant to vaporize.
  • the fluid in which the minute ice is mixed with the refrigerant gas is discharged from the pressure relief valve. If this state continues, ice may gradually adhere to the flow passage in the pressure relief valve, the pressure relief valve may be closed, and water and refrigerant may not be discharged from the pressure relief valve.
  • An object of the present invention is to provide a plate heat exchanger and a heat pump device capable of performing the heat treatment.
  • the plate heat exchanger is provided with a first through hole, a second through hole, a third through hole, and a fourth through hole that penetrate in one direction, and the plate heat exchanger has one direction.
  • a plurality of heat transfer plates for exchanging heat a first through hole connected to the first through hole, for introducing a first fluid into the first flow path, and a second through hole for connecting the first fluid from the first flow path.
  • a connection port for connection with a pressure relief valve is provided, comprising a pair of end plates sandwiching the plurality of heat transfer plates in one direction, a.
  • the compressor, the plate heat exchanger, the expansion mechanism, and the heat source side heat exchanger are connected via a refrigerant pipe, and a refrigerant that circulates the refrigerant.
  • the circuit, the pump, the plate heat exchanger, and the use side heat exchanger are connected via the heat medium pipe, and the heat medium circuit for circulating the heat medium and the heat medium circuit in the plate heat exchanger And a pressure relief valve connected to a connection port provided in a branched manner.
  • the second fluid when the plate heat exchanger is damaged and the first flow path and the second flow path are in communication with each other, the second fluid leaks into the first flow path to cause the flow in the first flow path. Pressure rises and the pressure relief valve opens.
  • the pressure relief valve is provided separately from the first inlet for introducing the first fluid into the first flow passage and the first outlet for leading out the first fluid from the first flow passage, branching from the first flow passage. Is connected to the connection port. Therefore, the second fluid leaking to the first flow path is intensively discharged from the pressure relief valve without being mixed with the first fluid. Therefore, the solidified product of the first fluid can be prevented from closing the pressure relief valve, so that the second fluid leaked to the first flow channel can be more reliably discharged from the first flow channel via the pressure relief valve.
  • the pressure in the heat medium circuit increases due to the refrigerant leaking to the heat medium circuit.
  • the pressure relief valve opens. Since the pressure relief valve is connected to the connection port provided by branching from the heat medium circuit in the plate heat exchanger, the refrigerant leaking to the heat medium circuit hardly mixes the heat medium, Concentrated discharge from the pressure relief valve. Therefore, it is possible to prevent the solidified product of the heat medium from closing the pressure relief valve, so that the refrigerant leaked to the heat medium circuit can be more reliably discharged from the heat medium circuit via the pressure relief valve.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. It is a figure which shows typically the flow of the fluid in the said plate-type heat exchanger. It is a figure which shows typically the flow of the fluid in the said plate-type heat exchanger when a refrigerant leaks. It is a figure which shows schematic structure of the heat pump apparatus which concerns on Embodiment 2 of this invention.
  • Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 6.
  • the same or corresponding parts are designated by the same reference numerals.
  • FIG. 1 is a diagram showing a schematic configuration of a heat pump device 1 according to the present embodiment.
  • the heat pump device 1 includes a refrigerant circuit 10 that circulates a refrigerant, a water circuit (heat medium circuit) 20 that circulates water (heat medium), and a pressure relief valve 30.
  • a compressor 12 In the refrigerant circuit 10, a compressor 12, a plate heat exchanger 40, an expansion valve (expansion mechanism) 13, and an air heat exchanger (heat source side heat exchanger) 14 are connected via a refrigerant pipe 11. Have a configuration.
  • the refrigerant circulating in the refrigerant circuit 10 has an ozone depletion potential (Ozone Depleting Potential; hereinafter referred to as “ODP”) and a global warming potential (Global Warming Potential; hereinafter, “GWP”).
  • ODP ozone Depleting Potential
  • GWP Global Warming Potential
  • a refrigerant having a low property of “.”) Is used.
  • Specific examples of such a refrigerant include R32, which has a lower GWP than R410A and R407C in HFC (hydrofluorocarbon) refrigerants, HFO (hydrofluoroolefin) refrigerants such as HFO-1234yf and HFO-1234ze, propane, and the like.
  • HC (hydrocarbon) type refrigerant such as butane is used.
  • the refrigerant described above has properties of low ODP and low GWP, but also has flammability. Further, the above-mentioned refrigerant may be used as a single refrigerant or may be used as a mixed refrigerant in which two or more kinds are mixed.
  • the compressor 12 compresses the sucked low-pressure refrigerant and discharges it as high-pressure refrigerant.
  • the compressor 12 includes an inverter device or the like, and the capacity of the compressor 12 (the amount of refrigerant discharged per unit time) can be changed by arbitrarily changing the drive frequency.
  • the plate heat exchanger 40 exchanges heat between the refrigerant flowing through the refrigerant circuit 10 and the water flowing through the water circuit 20.
  • the detailed configuration of the plate heat exchanger 40 will be described later.
  • the expansion valve 13 adjusts the flow rate of the refrigerant and, for example, adjusts the pressure of the refrigerant flowing into the air heat exchanger 14 (pressure reduction).
  • the expansion valve 13 is an electronic expansion valve whose opening can be changed based on an instruction from a control device (not shown).
  • the air heat exchanger 14 exchanges heat between the refrigerant flowing through the refrigerant circuit 10 and the air (outside air) blown by the fan.
  • the air heat exchanger 14 is a fin-and-tube heat exchanger made of, for example, copper or aluminum.
  • the heat pump device 1 defrosts the air heat exchanger 14 by causing the refrigerant circuit 10 to perform normal operation of heating the water flowing through the water circuit 20 and causing the refrigerant to flow in the opposite direction to the normal operation. It is configured to be able to perform a defrosting operation for performing.
  • a defrosting operation for performing.
  • the defrosting operation is required under the low temperature environment.
  • a four-way valve 15 is provided in the refrigerant circuit 10 to enable normal operation and defrosting operation.
  • the four-way valve 15 functions as a flow path switching device, and switches the flow direction of the refrigerant in the refrigerant circuit 10 between the normal operation and the defrosting operation.
  • the plate heat exchanger 40 also functions as a radiator (condenser) that heats the water flowing through the water circuit 20 during normal operation, and absorbs heat from the water in the water circuit 20 during defrosting operation (evaporator). Function as.
  • the air heat exchanger 14 functions as a heat absorber (evaporator) during normal operation, and functions as a radiator (condenser) during defrosting operation.
  • the heat pump device 1 is provided with the outdoor unit 51 accommodating the compressor 12, the four-way valve 15, the plate heat exchanger 40, the expansion valve 13, and the air heat exchanger 14 of the refrigerant circuit 10.
  • the outdoor unit 51 is installed outdoors.
  • the outdoor unit 51 is provided with a control device (not shown) that controls the operation of the refrigerant circuit 10. This control device controls, for example, driving of the compressor 12, switching of the flow path of the four-way valve 15, opening of the expansion valve 13, blowing of a fan of the air heat exchanger 14, and the like.
  • the flow direction of the refrigerant in the refrigerant circuit 10 during the normal operation is indicated by a solid arrow
  • the flow direction of the refrigerant during the defrosting operation is indicated by a dashed arrow.
  • the flow path of the refrigerant is switched by the four-way valve 15 as shown by the solid line, and the refrigerant circuit 10 is configured so that the high-temperature and high-pressure refrigerant flows through the plate heat exchanger 40. That is, during normal operation, the refrigerant circulates in the refrigerant circuit 10 in the order of the compressor 12, the four-way valve 15, the plate heat exchanger 40, the expansion valve 13, the air heat exchanger 14, the four-way valve 15, and the compressor 12.
  • gas refrigerant gas-state refrigerant
  • the plate heat exchanger 40 heat exchange between the refrigerant flowing through the refrigerant flow path and the water flowing through the water flow path (first flow path) of the plate heat exchanger 40 is performed, and the condensation heat of the refrigerant is radiated to water. .
  • the refrigerant flowing into the plate heat exchanger 40 is condensed and becomes a high-pressure liquid-state refrigerant (hereinafter, referred to as “liquid refrigerant”).
  • liquid refrigerant high-pressure liquid-state refrigerant
  • the high-pressure liquid refrigerant condensed in the plate heat exchanger 40 flows into the expansion valve 13 and is decompressed to become a low-pressure two-phase refrigerant (hereinafter referred to as “two-phase refrigerant”).
  • the low-pressure two-phase refrigerant flows into the air heat exchanger 14.
  • heat exchange is performed between the refrigerant flowing inside and the air blown by the fan (outside air).
  • the refrigerant flowing into the air heat exchanger 14 absorbs heat from the air and evaporates to become a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant is sucked into the compressor 12 via the four-way valve 15.
  • the refrigerant sucked into the compressor 12 is compressed into a high-temperature and high-pressure gas refrigerant. The above cycle is repeated during normal operation.
  • the flow path of the refrigerant is switched by the four-way valve 15 as shown by the broken line, and the refrigerant circuit 10 is configured so that the high temperature and high pressure refrigerant flows through the air heat exchanger 14. That is, during the defrosting operation, the refrigerant circulates in the refrigerant circuit 10 in this order through the compressor 12, the four-way valve 15, the air heat exchanger 14, the expansion valve 13, the plate heat exchanger 40, the four-way valve 15, and the compressor 12.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 12 flows into the air heat exchanger 14 via the four-way valve 15.
  • the refrigerant flows inside, so that the frost attached to the surface of the air heat exchanger 14 is heated by the condensation heat of the refrigerant and melted.
  • the refrigerant that has flowed into the air heat exchanger 14 is condensed into high-pressure liquid refrigerant.
  • the liquid refrigerant flowing out of the air heat exchanger 14 flows into the expansion valve 13, becomes a two-phase refrigerant, and flows into the plate heat exchanger 40.
  • the two-phase refrigerant flowing into the plate heat exchanger 40 absorbs heat from the water flowing through the water flow path in the plate heat exchanger 40 and evaporates to become a gas refrigerant.
  • the gas refrigerant is sucked into the compressor 12 through the four-way valve 15 and is compressed into a high-temperature and high-pressure gas refrigerant. The above cycle is repeated during the defrosting operation.
  • the water circuit 20 has a configuration in which a pump 22, the plate heat exchanger 40 described above, and a heating terminal (use side heat exchanger) 23 are connected via a water pipe (heat medium pipe) 21. There is.
  • the water circulating in the water circuit 20 is, for example, pure water or tap water.
  • the pump 22 is a device that circulates in the water circuit 20 by applying pressure to the water in the water circuit 20.
  • the heating terminal 23 is installed indoors (indoors) and warms the space 60 that is the target of air conditioning.
  • the heating terminal 23 is, for example, a panel heater, a floor heating panel, or the like, and has a heat exchange section inside.
  • the water in the water circuit 20 heated in the plate heat exchanger 40 flows into the heat exchange section.
  • heat exchange is performed between the inflowing water and the air in the space 60, and heat is radiated from the water to the air in the space 60. This warms the space 60 and cools the water.
  • the water circuit 20 is further provided with an expansion tank 24 and a safety valve 25.
  • the expansion tank 24 is a device for controlling the pressure that changes due to a change in the volume of water in the water circuit 20 due to heating or the like within a certain range.
  • the expansion tank 24 is connected to a pipe branched from the water pipe 21 that connects the pump 22 and the heating terminal 23.
  • the safety valve 25 is provided as a protection device.
  • the safety valve 25 discharges the water in the water circuit 20 to the outside when the pressure in the water circuit 20 exceeds the pressure control range of the expansion tank 24 and becomes high.
  • the safety valve 25 is connected to a pipe branched from the water pipe 21 that connects the plate heat exchanger 40 and the heating terminal 23.
  • the heat pump device 1 is provided with the indoor unit 52 that houses the pump 22, the expansion tank 24, and the safety valve 25 of the water circuit 20.
  • the indoor unit 52 is installed indoors (indoors). Further, the indoor unit 52 is provided with a controller (not shown) that controls the operation of the water circuit 20 such as the driving of the pump 22.
  • the pressure relief valve 30 is connected to the plate heat exchanger 40. More specifically, the pressure relief valve 30 is connected to a connection port 48 of a plate heat exchanger 40 described later.
  • the connection port 48 is provided so as to branch from the water circuit 20 in the plate heat exchanger 40.
  • the pressure relief valve 30 is housed in the outdoor unit 51 together with the plate heat exchanger 40, and is arranged outdoors.
  • the pressure relief valve 30 automatically opens when the pressure of the water circuit 20 exceeds a predetermined set value due to leakage of the refrigerant from the refrigerant circuit 10 in the plate heat exchanger 40 to the water circuit 20, for example, and externally. Emit fluids such as water and refrigerant.
  • the pressure relief valve 30 is automatically closed to stop the discharge of the fluid.
  • FIG. 2 is an exploded perspective view schematically showing the plate heat exchanger 40.
  • FIG. 3 is a front view schematically showing the plate heat exchanger 40.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG.
  • the plate heat exchanger 40 includes a plurality of heat transfer plates 41 and a pair of end plates 43A and 43B.
  • the plurality of heat transfer plates 41 are stacked in a predetermined one direction (hereinafter, referred to as “stacking direction”), and have a water flow path (first flow path) through which water (heat medium, first fluid) flows.
  • a refrigerant flow path (second flow path) through which a refrigerant (second fluid) is circulated is defined, and heat is exchanged between water in the water flow path and the refrigerant in the refrigerant flow path.
  • each heat transfer plate 41 is provided with four through holes that penetrate the stacking direction, that is, a first through hole 42A, a second through hole 42B, a third through hole 42C, and a fourth through hole 42D.
  • the heat transfer plate 41 is formed in a substantially rectangular plate shape when viewed from the stacking direction, and the first through hole 42A, the second through hole 42B, and the third through hole 42C are provided at the four corners of the substantially rectangular shape. And the 4th through-hole 42D is provided, respectively.
  • a heat transfer surface for heat exchange is formed, for example, a plurality of corrugated waveforms that are displaced in the stacking direction are formed in a V shape.
  • the heat transfer plate 41 is produced by pressing a metal plate such as a stainless steel plate.
  • the pair of end plates 43A and 43B sandwich a plurality of heat transfer plates 41 in the stacking direction.
  • the pair of end plates 43A and 43B are provided with a first inlet 44, a first outlet 45, a second inlet 46, a second outlet 47, and a connecting port 48.
  • the first introduction port 44 is connected to the first through hole 42A of the heat transfer plate 41 and is used to introduce water from the water pipe 21 into the water flow path.
  • the first outlet port 45 is connected to the second through hole 42B of the heat transfer plate 41 and is used to lead out water from the water flow path to the water pipe 21.
  • the second introduction port 46 is connected to the third through hole 42C of the heat transfer plate 41 and is used to introduce the refrigerant from the refrigerant pipe 11 into the refrigerant flow path.
  • the second outlet 47 is connected to the fourth through hole 42D of the heat transfer plate 41, and is used to lead out the refrigerant from the refrigerant flow path to the refrigerant pipe 11.
  • the pressure relief valve 30 is connected to the connection port 48.
  • the connection port 48 is connected to the second through hole 42B of the heat transfer plate 41 and is provided so as to branch from the water flow path. In the present embodiment, the connection port 48 is arranged at a position that is continuous with the second through hole 42B of the heat transfer plate 41 and that faces the first outlet port 45.
  • the refrigerant and water flows are described with reference to the normal operation for ease of description. Therefore, for example, during the defrosting operation, the refrigerant is introduced into the plate heat exchanger 40 from the second outlet 47 and is discharged from the second inlet 46.
  • the pair of end plates 43A and 43B are formed in a substantially rectangular plate shape when viewed from the stacking direction.
  • the second inlet port 46, the second outlet port 47, and the connection port 48 out of the four corners of the substantially rectangular shape are the third through hole 42C, the fourth through hole 42D, and the second through hole of the heat transfer plate 41. It is provided at each of the three corners corresponding to the position of 42B.
  • the first inlet 44 and the first outlet 45 are located at two corners of the substantially rectangular four corners corresponding to the positions of the first through hole 42A and the second through hole 42B of the heat transfer plate 41, respectively. It is provided.
  • connection port 48 is provided on an end plate different from the first inlet 44 and the first outlet 45. Further, each of the first inlet 44, the first outlet 45, the second inlet 46, the second outlet 47 and the connecting port 48 is provided with a cylindrical nozzle.
  • the plurality of heat transfer plates 41 and the pair of end plates 43A and 43B are superposed so that the edges of the outer peripheries thereof overlap, and are joined by brazing or the like. As a result, a water flow path and a refrigerant flow path are formed between the adjacent heat transfer plates 41. Further, in the state where the plurality of heat transfer plates 41 are overlapped, the water flow passages and the coolant flow passages are alternately arranged, the first through holes 42A and the second through holes 42B communicate with the water flow passages, and the third through holes 42C. Also, the fourth through hole 42D is configured to communicate with the refrigerant flow path.
  • FIG. 5 is a diagram schematically showing the flow of fluid in the plate heat exchanger 40.
  • the flow of water in the plate heat exchanger 40 is shown by a solid line, and the flow of the refrigerant is shown by a broken line.
  • the water in the water circuit 20 is introduced into the plate heat exchanger 40 from the first inlet 44 and flows through the water flow path formed between the heat transfer plates 41. , Through the first outlet 45.
  • the refrigerant in the refrigerant circuit 10 is introduced into the plate heat exchanger 40 through the second inlet 46, flows through the refrigerant flow path formed between the heat transfer plates 41, and is led out through the second outlet 47. At this time, heat exchange is performed between the water flowing through the water flow path and the refrigerant flowing through the refrigerant flow path.
  • FIG. 6 is a diagram schematically showing the flow of fluid in the plate heat exchanger 40 when the refrigerant leaks.
  • the heat transfer plate 41 may be damaged due to, for example, corrosion of the heat transfer plate 41 or metal fatigue fracture due to deterioration over time.
  • the refrigerant absorbs heat from the water, so the water is cooled.
  • the water temperature is low, the water flowing through the water circuit of the plate heat exchanger 40 may freeze.
  • the heat transfer plate 41 may be deformed and broken due to volume expansion when water freezes.
  • the pressure of water in the water circuit 20 is about 0.3 MPa
  • the pressure of the refrigerant in the refrigerant circuit 10 when flowing into the plate heat exchanger 40 is about 1.0 MPa. Therefore, since the pressure of the refrigerant is higher than the pressure of water, when the heat transfer plate 41 is damaged and the water flow path and the coolant flow path communicate with each other at the communication portion A as shown in FIG. The refrigerant flows into the water flow path through the communication portion A. As a result, the pressure in the water channel increases. When the pressure of the water flow path exceeds the set value of the pressure relief valve 30 connected to the connection port 48, the pressure relief valve 30 opens.
  • the refrigerant flowing into the water flow path from the communication portion A flows toward the pressure relief valve 30 while pushing the water existing between the communication portion A and the pressure relief valve 30, and discharges the water from the pressure relief valve 30. After the water is completely discharged, the pressure relief valve 30 discharges the refrigerant. At this time, there is a possibility that the refrigerant flowing from the communication part A into the water flow path may flow from the first inlet 44 or the first outlet 45 to the water circuit 20. However, since water is incompressible, the flow of the refrigerant to the first inlet 44 or the first outlet 45 is prevented by the water.
  • the path from the communication portion A through the first outlet 45 to the safety valve 25 is a pressure relief valve from the communication portion A. It is much longer than the path to 30 and the pressure loss is large, so that the possibility of the refrigerant flowing toward the safety valve 25 is very small. Therefore, after the pressure relief valve 30 is opened, almost all the refrigerant is discharged from the pressure relief valve 30. On the other hand, since the connection port 48 to which the pressure relief valve 30 is connected is provided separately from the first inlet port 44 and the first outlet port 45, the water in the water circuit 20 flowing into the water flow path is not released by the pressure relief valve.
  • the water can flow from the first inlet 44 through the water flow path to the first outlet 45.
  • the refrigerant prevents water from flowing to the pressure relief valve 30. Therefore, although the water existing between the communication portion A and the pressure relief valve 30 when the pressure relief valve 30 is opened is discharged from the pressure relief valve 30, most of the other water is discharged from the pressure relief valve 30. Is not discharged and flows from the first outlet 45 to the water circuit 20. In this way, the refrigerant that has flowed into the water flow path from the communication portion A is intensively discharged from the pressure relief valve 30 without being mixed with water.
  • the refrigerant that has flowed into the water channel is discharged from the first outlet together with the water in the water channel. Since the refrigerant flows to the water pipe toward the pressure relief valve, the refrigerant is discharged from the pressure relief valve together with water. For this reason, when the refrigerant cools the water, the water changes into ice and adheres to the flow path of the pressure relief valve, and closes the pressure relief valve.
  • the refrigerant that has flowed into the water flow path from the communicating portion A is discharged from the pressure relief valve 30 in a concentrated manner, with almost no mixing of water. Further, since the amount of water discharged from the pressure relief valve 30 is small, even if the refrigerant flowing from the communication portion A into the water flow path adiabatically expands to a temperature below the freezing point of water, the pressure relief valve 30 is closed. I can't let it happen. Therefore, since the pressure relief valve 30 can be prevented from being closed, the refrigerant leaked into the water flow channel can be more reliably discharged from the water flow channel via the pressure relief valve 30.
  • a compressor 12, a plate heat exchanger 40, an expansion valve 13, and an air heat exchanger 14 are connected via a refrigerant pipe 11 to circulate a refrigerant.
  • the circuit 10, the pump 22, the plate heat exchanger 40, and the heating terminal 23 are connected via a water pipe 21, and a water circuit 20 for circulating water and a water circuit 20 in the plate heat exchanger 40 are connected.
  • a pressure relief valve 30 connected to a connection port 48 provided by branching.
  • the refrigerant leaks to the water circuit 20 to increase the pressure in the water circuit 20,
  • the pressure relief valve 30 opens. Since the pressure relief valve 30 is connected to the connection port 48 provided by branching from the water circuit 20 in the plate heat exchanger 40, the refrigerant leaking to the water circuit 20 is almost mixed with water. Instead, it is exhausted intensively from the pressure relief valve 30. Therefore, since it is possible to prevent the ice generated by cooling the water by the refrigerant from closing the pressure relief valve 30, the refrigerant leaked to the water circuit 20 can be more reliably discharged from the water circuit 20 via the pressure relief valve 30. Can be discharged.
  • the plate heat exchanger 40 is provided with a first through hole 42A, a second through hole 42B, a third through hole 42C, and a fourth through hole 42D that penetrate in the stacking direction, A plurality of heat transfer plates 41 that are superposed in the stacking direction and partition a water flow passage for circulating water and a coolant flow passage for flowing a coolant, and exchange heat between the water in the water flow passage and the coolant in the coolant flow passage; A first introduction port 44 connected to the first through hole 42A for introducing water into the water passage, a first introduction port 45 connected to the second through hole 42B for leading out water from the water flow passage, A second introduction port 46 for introducing the refrigerant into the refrigerant passage, which is connected to the three through-holes 42C, a second outlet port 47 for leading out the refrigerant from the refrigerant passage, which is connected to the fourth through hole 42D, Pressure relief valve connected to the second through hole 42B and branched from the water flow path 0
  • the pressure relief valve 30 is a connection port that is provided separately from the water channel, apart from the first inlet port 44 for introducing water into the water channel and the first outlet port 45 for leading out water from the water channel. Connected to 48. Therefore, the refrigerant that has leaked to the water flow path is concentratedly discharged from the pressure relief valve 30 without being mixed with water. Therefore, it is possible to prevent the ice generated by cooling the water by the refrigerant from closing the pressure relief valve, so that the refrigerant leaked to the water channel is more reliably discharged from the water channel via the pressure relief valve 30. be able to.
  • the pressure relief valve 30 is located outdoors. For this reason, when the refrigerant is discharged from the pressure relief valve 30, the refrigerant is discharged outdoors without flowing into the room where the heating terminal 23, the indoor unit 52, etc. are installed. Possibility can be reduced. Further, when the refrigerant has flammability, the refrigerant does not flow into the indoor, so that the possibility that the refrigerant gas burns indoors can be reduced. Therefore, indoor safety can be improved.
  • connection port 48 is arranged at a position which is continuous with the second through hole 42B of the heat transfer plate 41 and faces the first outlet port 45, but is not limited to this.
  • the connection port 48 may be arranged at a position which is continuous with the first through hole 42A and faces the first introduction port 44.
  • the end plate 43A is provided with the second introduction port 46, the second derivation port 47, and the connection port 48, and the end plate 43B is provided with the first introduction port 44 and the first derivation port 45.
  • the arrangement of each inlet and each outlet is not limited to this.
  • the end plate 43A may be provided with only the connection port 48, and the end plate 43B may be provided with the first inlet port 44, the first outlet port 45, the second inlet port 46, and the second outlet port 47. .
  • the plate heat exchanger 40 is housed in the outdoor unit 51 and arranged outdoors, but the invention is not limited to this.
  • the plate heat exchanger 40 may not be housed in the outdoor unit 51 but may be placed outdoors alone. Further, the plate heat exchanger 40 may be placed indoors.
  • the pressure relief valve 30 connected to the plate heat exchanger 40 does not have to be arranged outdoors, and is a discharge for discharging a fluid such as a refrigerant discharged from the pressure relief valve 30 to the outdoors. It suffices that the working pipe is connected to the pressure relief valve 30.
  • the heat medium may be, for example, an antifreeze liquid such as ethylene glycol, or may be water mixed with the antifreeze liquid.
  • the heating side heat exchanger connected to the heat medium circuit is the heating terminal 23, but the present invention is not limited to this.
  • the utilization side heat exchanger may be, for example, a hot water storage tank or the like having a heat exchange section inside to generate and retain hot water.
  • the safety valve 25 is provided in the water circuit 20, but the safety valve 25 is not limited to this, and the safety valve 25 may not be provided in the water circuit 20.
  • the pressure relief valve 30 since the pressure relief valve 30 is connected to the water circuit 20 as shown in FIG. 1, the pressure relief valve 30 can also function as the safety valve 25. That is, for example, even when an abnormal pressure rise occurs in the water circuit 20 due to a cause other than the leakage of the refrigerant in the plate heat exchanger 40, the pressure relief valve 30 opens to remove the water in the water circuit 20 to the outside. By discharging to, it is possible to protect parts and equipment of the water circuit 20 from water pressure breakage.
  • the water circuit 20 When the water circuit 20 is provided with the safety valve 25, the water circuit 20 is protected against water pressure breakage by both the pressure relief valve 30 and the safety valve 25. Therefore, the reliability of the water circuit 20 against water pressure breakage can be improved. For example, even if one of the pressure relief valve 30 and the safety valve 25 fails, the other can protect the water circuit 20. Further, in this case, for example, by setting the setting value of the safety valve 25 to be slightly higher than the setting value of the pressure relief valve 30, the safety valve 25 is released when the refrigerant leaks in the plate heat exchanger 40 and the pressure rises. Instead, the pressure relief valve 30 may be more surely opened.
  • FIG. 7 is a diagram showing a schematic configuration of the heat pump device 2.
  • symbol is attached
  • the heat pump device 2 according to the present embodiment differs from the heat pump device 1 according to the first embodiment in that a check valve 26 is provided in the water circuit 20. As shown in FIG. 7, the check valve 26 is provided in the water circuit 20 between the pump 22 and the plate heat exchanger 40. The check valve 26 always keeps the flow of water in the water circuit 20 in the direction from the pump 22 to the plate heat exchanger 40, and prevents backflow. Further, in the present embodiment, the check valve 26 is housed in the indoor unit 52.

Abstract

La présente invention concerne un échangeur de chaleur à plaques comportant : une pluralité de plaques de transfert de chaleur qui comportent chacune un premier trou traversant, un deuxième trou traversant, un troisième trou traversant, et un quatrième trou traversant pénétrant à travers celles-ci dans une direction, et qui se chevauchent dans une direction et définissent un premier trajet d'écoulement et un second trajet d'écoulement ; et une paire de plaques d'extrémité qui prennent en sandwich la pluralité de plaques de transfert de chaleur entre elles dans une direction et qui ont un premier orifice d'entrée qui est raccordé au premier trou traversant et qui est destiné à introduire un premier fluide dans le premier trajet d'écoulement, un premier orifice de sortie qui est raccordé au deuxième trou traversant et qui est destiné à conduire le premier fluide hors du premier trajet d'écoulement, un second orifice d'entrée qui est raccordé au troisième trou traversant et qui sert à introduire un second fluide dans le second trajet d'écoulement, un second orifice de sortie qui est raccordé au quatrième trou traversant et qui est destiné à conduire le second fluide hors du second trajet d'écoulement, et un orifice de raccordement qui est raccordé au second trou traversant et se ramifie à partir du premier trajet d'écoulement et qui est destiné à être raccordé à une soupape de dégagement de la pression.
PCT/JP2018/037720 2018-10-10 2018-10-10 Échangeur de chaleur à plaques et dispositif de pompe à chaleur WO2020075238A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
PCT/JP2018/037720 WO2020075238A1 (fr) 2018-10-10 2018-10-10 Échangeur de chaleur à plaques et dispositif de pompe à chaleur
US17/265,445 US20210231355A1 (en) 2018-10-10 2019-10-04 Plate heat exchanger and heat pump apparatus
CN201980062298.XA CN112771343A (zh) 2018-10-10 2019-10-04 板式热交换器以及热泵装置
EP19872006.2A EP3865802B1 (fr) 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur
JP2020551096A JP7019068B2 (ja) 2018-10-10 2019-10-04 プレート式熱交換器およびヒートポンプ装置
PCT/JP2019/039230 WO2020075630A1 (fr) 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/037720 WO2020075238A1 (fr) 2018-10-10 2018-10-10 Échangeur de chaleur à plaques et dispositif de pompe à chaleur

Publications (1)

Publication Number Publication Date
WO2020075238A1 true WO2020075238A1 (fr) 2020-04-16

Family

ID=70164042

Family Applications (2)

Application Number Title Priority Date Filing Date
PCT/JP2018/037720 WO2020075238A1 (fr) 2018-10-10 2018-10-10 Échangeur de chaleur à plaques et dispositif de pompe à chaleur
PCT/JP2019/039230 WO2020075630A1 (fr) 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur

Family Applications After (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/039230 WO2020075630A1 (fr) 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur

Country Status (5)

Country Link
US (1) US20210231355A1 (fr)
EP (1) EP3865802B1 (fr)
JP (1) JP7019068B2 (fr)
CN (1) CN112771343A (fr)
WO (2) WO2020075238A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5246041B2 (fr) * 1971-03-30 1977-11-21
JPS59134757U (ja) * 1983-02-25 1984-09-08 株式会社土屋製作所 プレ−ト型の熱交換器
EP1500896A2 (fr) * 2003-07-23 2005-01-26 Invensys Process Systems A/S Elément de couplage pour échangeur de chaleur
CN202630756U (zh) * 2012-06-11 2012-12-26 宁波市哈雷换热设备有限公司 带排气口的板式换热器
JP2014040945A (ja) * 2012-08-21 2014-03-06 Kobe Steel Ltd プレートフィン熱交換器及びプレートフィン熱交換器の補修方法
JP2018136058A (ja) * 2017-02-21 2018-08-30 カルソニックカンセイ株式会社 水冷式コンデンサ

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10336624B4 (de) * 2002-08-23 2017-06-08 Josef Autengruber Vorrichtung zur Entnahme von Wärme aus einem Wärmeträgerspeicher
JP2005188764A (ja) * 2003-12-24 2005-07-14 Sanyo Electric Co Ltd 冷凍装置
JP4263086B2 (ja) 2003-12-24 2009-05-13 三洋電機株式会社 冷凍装置
EP1548377B1 (fr) * 2003-12-24 2013-10-23 Sanyo Electric Co., Ltd. Machine frigorifique avec échangeur de chaleur frigorigène-eau
JP5011713B2 (ja) * 2005-11-22 2012-08-29 株式会社デンソー ヒートポンプ式給湯装置
KR101135809B1 (ko) * 2006-09-01 2012-04-16 엘지전자 주식회사 수냉식 공기조화기
JP4948374B2 (ja) * 2007-11-30 2012-06-06 三菱電機株式会社 冷凍サイクル装置
WO2010078722A1 (fr) * 2009-01-06 2010-07-15 Danfoss Qinbao (Hangzhou) Plate Heat Exchanger Company Limited Échangeur thermique, système de pompe à chaleur et système de climatisation
JP5246041B2 (ja) 2009-05-27 2013-07-24 パナソニック株式会社 温水暖房装置
CN103842761B (zh) * 2011-09-14 2017-11-10 株式会社日阪制作所 板式热交换器
SI2674697T1 (sl) * 2012-06-14 2018-11-30 Alfa Laval Corporate Ab Ploščni toplotni izmenjevalnik
WO2014097439A1 (fr) * 2012-12-20 2014-06-26 三菱電機株式会社 Dispositif de climatisation
JP2015001356A (ja) * 2013-06-18 2015-01-05 パナソニックＩｐマネジメント株式会社 ヒートポンプ熱交換装置
US10161687B2 (en) * 2015-01-22 2018-12-25 Mitsubishi Electric Corporation Plate heat exchanger and heat pump outdoor unit
KR20180064465A (ko) * 2015-10-02 2018-06-14 다나 캐나다 코포레이션 집적된 코어 구조를 갖는 냉동 시스템
KR101777482B1 (ko) * 2015-12-29 2017-09-12 서진욱 안전장치가 구비된 판형 열교환기
WO2017138145A1 (fr) * 2016-02-12 2017-08-17 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif à cycle frigorifique
JP6477636B2 (ja) 2016-09-07 2019-03-06 トヨタ自動車株式会社 内燃機関の制御装置
US20190346191A1 (en) 2016-12-09 2019-11-14 Mitsubishi Electric Corporation Heat pump apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5246041B2 (fr) * 1971-03-30 1977-11-21
JPS59134757U (ja) * 1983-02-25 1984-09-08 株式会社土屋製作所 プレ−ト型の熱交換器
EP1500896A2 (fr) * 2003-07-23 2005-01-26 Invensys Process Systems A/S Elément de couplage pour échangeur de chaleur
CN202630756U (zh) * 2012-06-11 2012-12-26 宁波市哈雷换热设备有限公司 带排气口的板式换热器
JP2014040945A (ja) * 2012-08-21 2014-03-06 Kobe Steel Ltd プレートフィン熱交換器及びプレートフィン熱交換器の補修方法
JP2018136058A (ja) * 2017-02-21 2018-08-30 カルソニックカンセイ株式会社 水冷式コンデンサ

Also Published As

Publication number Publication date
EP3865802B1 (fr) 2023-08-16
CN112771343A (zh) 2021-05-07
WO2020075630A1 (fr) 2020-04-16
JP7019068B2 (ja) 2022-02-14
EP3865802A4 (fr) 2021-12-01
US20210231355A1 (en) 2021-07-29
EP3865802A1 (fr) 2021-08-18
JPWO2020075630A1 (ja) 2021-06-03

Similar Documents

Publication Publication Date Title
JP5818900B2 (ja) ヒートポンプ装置
JP4225304B2 (ja) 冷凍空調装置の制御方法
JP5939828B2 (ja) ヒートポンプサイクル装置
EP2246649B2 (fr) Appareil de réfrigération
WO2018043721A1 (fr) Appareil de congélation
WO2015111175A1 (fr) Appareil de pompe à chaleur
JP2007010207A (ja) 給湯装置
JP2016095130A (ja) ヒートポンプサイクル装置
JP3726541B2 (ja) 冷凍空調装置
EP2647929B1 (fr) Procédé de remplacement de pièce pour dispositif à cycle frigorifique et dispositif à cycle frigorifique
JPWO2018073853A1 (ja) ヒートポンプ利用機器の室内機及びそれを備えたヒートポンプ利用機器
WO2016071955A1 (fr) Appareil de climatisation
EP3379176B1 (fr) Dispositif à cycle frigorifique
WO2018139589A1 (fr) Dispositif de réfrigération
US10852007B2 (en) Heat pump device
WO2020075238A1 (fr) Échangeur de chaleur à plaques et dispositif de pompe à chaleur
JP2020094698A (ja) 冷凍装置
JPWO2016038659A1 (ja) 冷凍サイクル装置
GB2543206A (en) Refrigeration cycle device
JP2018044686A (ja) 冷凍システム
WO2018042490A1 (fr) Dispositif à cycle de réfrigération
WO2019026276A1 (fr) Dispositif à cycle frigorifique
JP2022150675A (ja) ヒートポンプ装置
EP3415841A1 (fr) Dispositif a cycle de réfrigération

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: 18936483

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18936483

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP