EP3865802B1 - Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur - Google Patents

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

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Publication number
EP3865802B1
EP3865802B1 EP19872006.2A EP19872006A EP3865802B1 EP 3865802 B1 EP3865802 B1 EP 3865802B1 EP 19872006 A EP19872006 A EP 19872006A EP 3865802 B1 EP3865802 B1 EP 3865802B1
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EP
European Patent Office
Prior art keywords
port
refrigerant
heat exchanger
flow passage
plate
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Application number
EP19872006.2A
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German (de)
English (en)
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EP3865802A1 (fr
EP3865802A4 (fr
Inventor
Hirokazu Minamisako
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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 disclosure relates to a plate heat exchanger and a heat pump apparatus.
  • a heat pump apparatus that heats water to supply hot water or to condition air
  • a water-refrigerant plate heat exchanger causes heat exchange to be performed between refrigerant that circulates in a refrigerant circuit and water that flows in a water circuit, thereby heating the water in the water circuit.
  • the water may be expanded by heating. Therefore, in some cases, a pressure relief valve is provided in the water circuit (for example, see Patent Literature 1).
  • Document EP 3 012 551 A1 discloses a heat pump apparatus comprising a compressor, a plate heat exchanger, a decompressor and an evaporator in order to improve the heat exchange efficiency of the plate heat exchanger.
  • Document EP 2 674 697 A1 discloses a plate heat exchanger comprising a plate package which includes a first and second heat exchanger plates which are joined to each other and arranged side by side in such a way that first and second plate interspaces are formed. At least two injectors are provided and at least one valve is arranged to control the supply of the first fluid to the at least two injectors.
  • Document JP 2018 136058 A on which the preamble of claim 1 is based, discloses a water cooled condenser with a relief valve provided to the outside of the water cooled condenser so that when refrigerant leaks in a cooling water flow passage, pressure of fluid in the cooling water flow passage can be prevented from becoming not less than a predetermined value, as compared to a case where the relief valve is mounted on a vehicle.
  • the water cooled condenser is capable of enhancing degree of freedom for layout.
  • Document WO 2018/105102 A1 discloses a pressure-regulating valve disposed in a heat pump device.
  • a piping which connects a compressor, a heat source exchanger, an expansion mechanism and an intermediate heat exchanger is disclosed, through which a refrigerant is circulated.
  • the pressure-regulating valve is connected to the piping for connecting between an outlet of the intermediate heat exchanger and an inlet of a load heat exchanger and is configured to shut off the fluid channel for the fluid in the case of increasing fluid pressure as a result of a refrigerant leakage into the fluid.
  • Embodiment 1 of the present disclosure will be described with reference to Figs. 1 to 6 .
  • components that are the same as those in a previous figure or figures are denoted by the same reference signs.
  • Fig. 1 is a schematic view illustrating a configuration of a heat pump apparatus 1 according to Embodiment 1.
  • the heat pump apparatus 1 includes a refrigerant circuit 10 that causes refrigerant to circulate, a water circuit (heat medium circuit) 20 that causes water (heat medium) to circulate, and a pressure relief valve 30.
  • refrigerants have a low ODP and a low GWP, but are flammable. Furthermore, any of the refrigerants may be used as a single-component refrigerant, or two or more of the refrigerants may be mixed and used as mixed refrigerant
  • the compressor 12 compresses sucked low-pressure refrigerant into high-pressure refrigerant and then discharges the high-pressure refrigerant.
  • the compressor 12 includes an inverter device and other components, and a capacity (the amount of refrigerant that is sent per unit time) of the compressor 12 can be changed by arbitrarily changing a driving frequency.
  • the expansion valve 13 adjusts the flow rate of the refrigerant, and for example, adjusts (reduces) the pressure of the refrigerant that flows into the air heat exchanger 14.
  • the expansion valve 13 is an electronic expansion valve whose opening degree can be changed in response to an instruction from a controller not illustrated.
  • the heat pump apparatus 1 is configured such that in the refrigerant circuit 10, a normal operation and a defrosting operation can be performed.
  • a normal operation water that flows in the water circuit 20 is heated, and in the defrosting operation, the refrigerant is caused to flow in the opposite direction to the flow direction of the refrigerant in the normal operation, to defrost the air heat exchanger 14.
  • dew condensation water may freeze in the air heat exchanger 14, and frost may adhere to a surface of the air heat exchanger 14.
  • the frost grows when the normal operation continues, and reduces the heat exchange efficiency of the air heat exchanger 14. Therefore, the defrosting operation is necessary for the environment in which the temperature of the outside air is low.
  • the heat pump apparatus 1 includes an outdoor unit 51 that houses 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 in an outdoor space.
  • the outdoor unit 51 includes a controller not illustrated that controls an operation of the refrigerant circuit 10. The controller controls, for example, driving of the compressor 12, switching of a flow passage by the four-way valve 15, the opening degree of the expansion valve 13, and air-sending by a fan provided in the air heat exchanger 14.
  • Fig. 1 the flow direction of the refrigerant in the refrigerant circuit 10 during the normal operation is indicated by solid arrows, and the flow direction of the refrigerant during the defrosting operation is indicated by dashed arrows.
  • the flow passage for the refrigerant is changed by the four-way valve 15 to a flow passage indicated by solid lines, and high-temperature and high-pressure refrigerant flows into the plate heat exchanger 40. That is, during the normal operation, in the refrigerant circuit 10, the refrigerant circulates through 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 in this order.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 12 while being in a gas state flows into a refrigerant flow passage (second flow passage) in the plate heat exchanger 40 through the four-way valve 15.
  • gas refrigerant flows into a refrigerant flow passage (second flow passage) in the plate heat exchanger 40 through the four-way valve 15.
  • heat exchange is performed between the refrigerant that flows through the refrigerant flow passage and the water that flows in a water flow passage (first flow passage) in the plate heat exchanger 40, and condensation heat of the refrigerant is transferred to the water.
  • the refrigerant that has flowed into the plate heat exchanger 40 is condensed to change into high-pressure refrigerant being in a liquid state (which will hereinafter be referred to as "liquid refrigerant").
  • liquid refrigerant The water that flows in the water flow passage of the plate heat exchanger 40 is heated by the heat transferred from the refrigerant.
  • the high-pressure liquid refrigerant condensed in the plate heat exchanger 40 flows into the expansion valve 13, and is reduced in pressure to change into low-pressure refrigerant being in a two-phase state (which will hereinafter be 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 that flows in the air heat exchanger 14 and air (outside air) sent by the fan.
  • the refrigerant that has flowed into the air heat exchanger 14 receives heat from the air, and evaporates to change into low-pressure gas refrigerant.
  • the flow passage for the refrigerant is changed by the four-way valve 15 to the flow passage indicated by dashed lines, and the high-temperature and high-pressure refrigerant flows into the air heat exchanger 14.
  • the refrigerant circulates 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 in this order.
  • the two-phase refrigerant that has flowed into the plate heat exchanger 40 receives heat from water that flows through the water flow passage in the plate heat exchanger 40, and evaporates to change into the gas refrigerant.
  • the gas refrigerant is sucked into the compressor 12 through the four-way valve 15, and is compressed into high-temperature and high-pressure gas refrigerant. During the defrosting operation, the above cycle is repeated.
  • the water circuit 20 further includes an expansion tank 24 and a safety valve 25.
  • the expansion tank 24 is a device configured to control within a predetermined range, a pressure that changes because of a volume change of the water in the water circuit 20 that is made by, for example, heating.
  • the expansion tank 24 is connected to a pipe that branches off from the water pipe 21 connecting the pump 22 and the heating terminal 23.
  • the safety valve 25 is provided as a protection device. In the case where the pressure in the water circuit 20 rises to exceed a pressure control range of the expansion tank 24, the safety valve 25 causes the water in the water circuit 20 to flow out from the water circuit 20 to the outside.
  • the safety valve 25 is connected to a pipe that branches off from the water pipe 21 connecting the plate heat exchanger 40 and the heating terminal 23.
  • the heat pump apparatus 1 includes an indoor unit 52 that houses the pump 22, the expansion tank 24, and the safety valve 25 that are provided in the water circuit 20.
  • the indoor unit 52 is installed in the room (indoor space).
  • the indoor unit 52 further includes a controller not illustrated that controls an operation of the water circuit 20, such as 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 the plate heat exchanger 40 that will be described below.
  • the connection port 48 is provided in such a manner as to branch off (from part of the water circuit 20 that is located in the plate heat exchanger 40.
  • the pressure relief valve 30 is housed together with the plate heat exchanger 40 in the outdoor unit 51, and is located in the outdoor space.
  • Fig. 2 is an exploded perspective view schematically illustrating the plate heat exchanger 40.
  • Fig. 3 is a front view schematically illustrating the plate heat exchanger 40.
  • Fig. 4 is a sectional view taken along line IV-IV in Fig. 3 .
  • the plate heat exchanger 40 includes a plurality of heat transfer plates 41 and a pair of end plates 43A and 43B.
  • the four through-holes are a first through-hole 42A, a second through-hole 42B, a third through-hole 42C, and a fourth through-hole 42D.
  • each of the heat transfer plates 41 is formed in the shape of a substantially rectangular plate as viewed from the stacking direction, and the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D are provided in respective four corners of each heat transfer plate 41 formed in the shape of the substantially rectangular plate.
  • a surface of each heat transfer plate 41 is a heat transfer surface for heat exchange. In the heat transfer surface, for example, a plurality of waveforms that are offset relative to each other in the stacking direction and are V-shaped are provided.
  • Each of the heat transfer plates 41 is made by, for example, pressing a metal plate such as a stainless steel plate.
  • the pair of end plates 43A and 43B are provided such that the plurality of heat transfer plates 41 are sandwiched between the end plates 43A and 43B in the stacking direction.
  • a first inlet port 44, a first outlet port 45, a second inlet port 46, a second outlet port 47, and a connection port 48 are provided in the end plates 43A and 43B.
  • the first inlet port 44 is continuous with the first through-holes 42A of the heat transfer plates 41, and is used as a port through which the water flows from the water pipe 21 into the water flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B of the heat transfer plates 41, and is used as a port through which the water flows from the water flow passage into the water pipe 21.
  • the second inlet port 46 is continuous with the third through-holes 42C of the heat transfer plates 41, and is used as a port through which the refrigerant flows from the refrigerant pipe 11 into the refrigerant flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D of the heat transfer plates 41, and is used as a port through which the refrigerant flows from the refrigerant flow passage to the refrigerant pipe 11.
  • the connection port 48 is connected to the pressure relief valve 30. Furthermore, the connection port 48 is continuous with the second through-holes 42B of the heat transfer plates 41, and branches off from the water flow passage.
  • connection port 48 is located continuous with the second through-holes 42B of the heat transfer plates 41 and also opposite to the first outlet port 45.
  • the flow of the refrigerant and the flow of the water are described with respect to the flows of the refrigerant and the water during the normal operation. Therefore, for example, during the defrosting operation, the refrigerant is caused to flow into the plate heat exchanger 40 through the second outlet port 47, and flow out from the plate heat exchanger 40 through the second inlet port 46.
  • each of the pair of end plates 43A and 43B is formed in the shape of a substantially rectangular plate as viewed from the stacking direction.
  • the second inlet port 46, the second outlet port 47, and the connection port 48 are provided in respective three of four corners of the end plate 43A, which correspond to the positions of the third through-holes 42C, the fourth through-holes 42D, and the second through-holes 42B of the heat transfer plates 41.
  • the heat transfer plates 41 and the end plates 43A and 43B are stacked and joined together by, for example, brazing, such that each of the outer peripheral edges of each of the heat transfer plates 41 and the end plates 43A and 43B is aligned with corresponding ones of the outer peripheral edges of the others of the heat transfer plates 41 and the end plates 43A and 43B.
  • the water flow passage and the refrigerant flow passage are provided between adjacent ones of the heat transfer plates 41.
  • the waver flow passage and the refrigerant flow passage are alternately located in a plurality of spaces between the heat transfer plates 41, the first through-holes 42A and the second through-holes 42B communicate with the water flow passage, and the third through-holes 42C and the fourth through-holes 42D communicate with the refrigerant flow passage.
  • Fig. 5 is a schematic diagram illustrating the flow of the fluid in the plate heat exchanger 40.
  • the flow of the water in the plate heat exchanger 40 is indicated by solid lines, and the flow of the refrigerant is indicated by dashed lines.
  • the water in the water circuit 20 flows from the first inlet port 44 into the plate heat exchanger 40, then flows through the water flow passage provided between the heat transfer plates 41, and flows out from the first outlet port 45.
  • the refrigerant in the refrigerant circuit 10 flows from the second inlet port 46 into the plate heat exchanger 40, then flows through the refrigerant flow passage provided between the heat transfer plates 41, and then flows out from the second outlet port 47.
  • heat exchange is performed between the water that flows through the water flow passage and the refrigerant that flows through the refrigerant flow passage.
  • Fig. 6 is a schematic diagram illustrating the flow of the fluid in the plate heat exchanger 40 in the case where the refrigerant leaks.
  • the heat transfer plates 41 may be damaged because of, for example, corrosion that occurs at the heat transfer plates 41 and metal fatigue caused by aged deterioration.
  • the refrigerant receives heat from the water and the water is thus cooled.
  • the heat transfer plates 41 may be deformed and broken because of volume expansion of the water that occurs when the water freezes.
  • the pressure of the water in the water circuit 20 is approximately 0.3 MPa
  • the pressure of the refrigerant in the refrigerant circuit 10 at the time when the refrigerant flows into the plate heat exchanger 40 is approximately 1.0 MPa.
  • the pressure of the refrigerant is higher than that of the water.
  • the refrigerant that has flowed from the communication portion A into the water flow passage flows toward the pressure relief valve 30 while pushing water that is present between the communication portion A and the pressure relief valve 30, and thus causes the water to flow out from the pressure relief valve 30. After the water completely flows out, the refrigerant flows out from the pressure relief valve 30. At this time, there is a possibility that the refrigerant that has flowed from the communication portion A into the water flow passage may flow from the first inlet port 44 or the first outlet port 45 to the water circuit 20. However, actually, since the water is incompressible, the water prevents the refrigerant from flowing to the first inlet port 44 or the first outlet port 45.
  • the safety valve 25 is opened to allow the water and the refrigerant to flow out from the safety valve 25, the possibility with which the refrigerant will flow toward the safety valve 25 is very low because a passage from the communication portion A to the safety valve 25 through the first outlet port 45 is far longer than a passage from the communication portion A to the pressure relief valve 30, and a pressure loss is increased. Therefore, after the pressure relief valve 30 is opened, the refrigerant substantially completely flows out from the pressure relief valve 30.
  • connection port 48 connected to the pressure relief valve 30 is provided separately from the first inlet port 44 and the first outlet port 45, the water in the water circuit 20 that flows into the water flow passage can flow from the first inlet port 44 to the first outlet port 45 through the water flow passage even after the pressure relief valve 30 is opened.
  • the pressure of the water is lower than the pressure of the refrigerant that flows toward the pressure relief valve 30, the refrigerant prevents the water from flowing toward the pressure relief valve 30. Therefore, although water that is present between the communication portion A and the pressure relief valve 30 when the pressure relief valve 30 is opened flows out from the pressure relief valve 30, most of remaining water flows from the first outlet port 45 to the water circuit 20 without flowing out from the pressure relief valve 30. In such a manner, the refrigerant that has flowed from the communication portion A into the water flow passage concentratedly flows out from the pressure relief valve 30, with the water hardly mixed with the refrigerant.
  • the refrigerant that has flowed into the water flow passage flows together with the water in the water flow passage from the first outlet port toward the pressure relief valve through the water pipe, and the refrigerant thus flows out together with the water from the pressure relief valve. Therefore, the water is cooled by the refrigerant to change into ice, and the ice adheres to the flow passage in the pressure relief valve to close the pressure relief valve.
  • the refrigerant that has flowed from the communication portion A into the water flow passage concentratedly flows out from the pressure relief valve 30, with the water hardly mixed with the refrigerant, as described above.
  • the pressure relief valve 30 since the amount of water that flows out from the pressure relief valve 30 is small, even when the refrigerant that has flowed from the communication portion A into the water flow passage adiabatically expands and the temperature of the refrigerant falls below the freezing point of the water, the refrigerant does not close the pressure relief valve 30. It is therefore possible to prevent the pressure relief valve 30 from being closed, and thus possible to more reliably cause the refrigerant that has leaked to the water flow passage to flow out of the water flow passage through the pressure relief valve 30.
  • the heat pump apparatus 1 includes: the refrigerant circuit 10 in which the compressor 12, the plate heat exchanger 40, the expansion valve 13, and the air heat exchanger 14 are connected by the refrigerant pipes 11 to cause the refrigerant to circulate; the water circuit 20 in which the pump 22, the plate heat exchanger 40, and the heating terminal 23 are connected by the water pipes 21 to cause the water to circulate; and the pressure relief valve 30 connected to the connection port 48 that branches off from part of the water circuit 20 that is located in the plate heat exchanger 40.
  • the pressure relief valve 30 is opened. Since the pressure relief valve 30 is connected to the connection port 48 branching off from the part of the water circuit 20 that is located in the plate heat exchanger 40, the refrigerant that has leaked to the water circuit 20 concentratedly flows out from the pressure relief valve 30, with the water hardly mixed with the refrigerant. Thus, it is possible to prevent the water from being cooled by the refrigerant, and thus from changing into ice, that is, ice does not close the pressure relief valve 30. It is therefore possible to more reliably cause the refrigerant that has leaked to the water circuit 20, to flow out from the water circuit 20 through the pressure relief valve 30.
  • the plate heat exchanger 40 according to Embodiment 1 includes the plurality of the heat transfer plates 41 and the pair of end plates 43A and 43B.
  • Each of the heat transfer plates 41 includes the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D that extend through the heat transfer plate 41 in the stacking direction.
  • the heat transfer plates 41 are stacked together in the stacking direction, isolate the water flow passage through which the water flows and the refrigerant flow passage through which the refrigerant flows, and cause heat exchange to be performed between the water in the water flow passage and the refrigerant in the refrigerant flow passage.
  • the pair of end plates 43A and 43B include the first inlet port 44, the first outlet port 45, the second inlet port 46, the second outlet port 47, and the connection port 48, and are located such that the heat transfer plates 41 are sandwiched between the end plates 43A and 43B in the stacking direction.
  • the first inlet port 44 is continuous with the first through-holes 42A and located as a port through which the water flows into the water flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B and located as a port through which the water flows out from the water flow passage.
  • the second inlet port 46 is continuous with the third through-holes 42C and located as a port through which the refrigerant flows into the refrigerant flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D and located as a port through which the refrigerant flows out from the refrigerant flow passage.
  • the connection port 48 is continuous with the second through-holes 42B, branches off from the water flow passage, and is connected to the pressure relief valve 30.
  • the refrigerant leaks to the water flow passage, the pressure in the water flow passage id thus raised, and the pressure relief valve 30 is opened.
  • the pressure relief valve 30 is connected to the connection port 48 that branches off from the water flow passage, not the first inlet port 44 through which the water flows into the water flow passage or the first outlet port 45 through which the water flows out from the water flow passage.
  • the pressure relief valve 30 is located in the outdoor space. Therefore, when flowing out of the pressure relief valve 30, the refrigerant flows out to the outdoor space without flowing into the indoor space where the heating terminal 23, the indoor unit 52, and other devices are installed. It is therefore possible to reduce the possibility that suffocation will be caused by the refrigerant gas in the indoor space. Furthermore, in the case where the refrigerant is combustible, it is possible to reduce the possibility that the refrigerant gas will burn in the indoor space because the refrigerant does not flow into the indoor space. Thus, the safety in the indoor space can be improved.
  • connection port 48 is provided continuous with the second through-holes 42B of the heat transfer plates 41 and opposite to the first outlet port 45; it is not limiting.
  • the connection port 48 may be provided continuous with the first through-holes 42A and opposite to the first inlet port 44.
  • the end plate 43A includes the second inlet port 46, the second outlet port 47, and the connection port 48, and the end plate 43B includes the first inlet port 44 and the first outlet port 45; however, the arrangement of these inlet and outlet ports is not limited to the above arrangement.
  • the end plate 43A may include only the connection port 48, and the end plate 43B may include 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 is located in the outdoor space; however, the position of the plate heat exchanger 40 is not limited to the above position.
  • the plate heat exchanger 40 may be provided solely in the outdoor space without being housed in the outdoor unit 51.
  • the plate heat exchanger 40 may be provided in the indoor space.
  • the pressure relief valve 30 connected to the plate heat exchanger 40 may not be located in the outdoor space, and it suffices that a pipe that allows the fluid such as the refrigerant to flow out from the pressure relief valve 30 to the outdoor space is connected to the pressure relief valve 30.
  • the heat medium may be, for example, an antifreeze solution such as ethylene glycol, or water mixed with the antifreeze solution.
  • the heating terminal 23 is used as the use-side heat exchanger connected to the heat medium circuit, it is not limiting.
  • the use-side heat exchanger may be, for example, a hot water storage tank that internally includes a heat exchange unit to generate hot water and accumulates the hot water.
  • the safety valve 25 is provided in the water circuit 20; however, 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 illustrated in Fig. 1 , the pressure relief valve 30 can also fulfill the function of the safety valve 25. In other words, for example, even in the case where the pressure in the water circuit 20 is abnormally raised by a cause other than leakage of the refrigerant in the plate heat exchanger 40, the pressure relief valve 30 is opened to cause the water in the water circuit 20 to flow out to the outside, to thereby protect components, devices, etc., in the water circuit 20 against a water pressure.
  • the water circuit 20 is protected against the water pressure, by both the pressure relief valve 30 and the safety valve 25. It is therefore possible to improve the reliability of the water circuit 20 with respect to protection of the water circuit 20 against the water pressure. For example, even if a failure occurs at one of the pressure relief valve 30 and the safety valve 25, the water circuit 20 can be protected by the other of the pressure relief valve 30 and the safety valve 25.
  • the set value of the safety valve 25 may be made slightly higher than the set value of the pressure relief valve 30, whereby not the safety valve 25 but the pressure relief valve 30 is more reliably opened, when the refrigerant leaks and the pressure rises in the plate heat exchanger 40.
  • Fig. 7 is a schematic diagram illustrating a configuration of the heat pump apparatus 2.
  • components that have the same configurations as those of the above heat pump apparatus 1 according to Embodiment 1 will be denoted by the same reference signs, and their detailed descriptions will be omitted.
  • a check valve 26 is provided in the water circuit 20.
  • the heat pump apparatus according to Embodiment 2 is different from the heat pump apparatus 1 according to Embodiment 1.
  • the check valve 26 is provided between the pump 22 and the plate heat exchanger 40 in the water circuit 20.
  • the check valve 26 maintains at all times the flow direction of the water in the water circuit that flows in a direction from the pump 22 toward the plate heat exchanger 40, thereby preventing the water from flowing backward.
  • the check valve 26 is housed in the indoor unit 52.
  • the plate heat exchanger 40 if the heat transfer plates 41 are damaged, and the water flow passage and the refrigerant flow passage communicate with each other, the refrigerant flows into the water flow passage, and the pressure in the water flow passage is raised. Consequently, a pressure is applied to the check valve 26 of the water circuit 20 in a back-flow direction. At this time, the check valve 26 is closed to prevent the water in the water circuit 20 from flowing in the back-flow direction, and stops the flow of the water. Therefore, the refrigerant that has flowed into the water flow passage does not easily flow from the first inlet port 44 to the water circuit 20. It is therefore possible to cause the refrigerant that has flowed into the water flow passage to flow out more concentratedly from the pressure relief valve 30.
  • Fig. 8 is a sectional view taken along line IV-IV in Fig. 3 in a state where the pressure relief valve is attached.
  • the connection between the pressure relief valve 30 and the plate heat exchanger 40 of the heat pump apparatus 1 as described in Embodiment 1 will be described in more detail. Therefore, regarding Embodiment 3, components that have the same configurations as those in the above heat pump apparatus 1 according to Embodiment 1 will be denoted by the same reference signs, and their detailed descriptions will be omitted.
  • the pressure relief valve 30 includes a first opening port 30a, a second opening port 30b, an internal valve flow-passage portion 30c, and a valve body 30d.
  • the first opening port 30a is connected to the connection port 48 of the plate heat exchanger 40.
  • the second opening port 30b serves as an outlet port through which the refrigerant or the water in the water circuit 20 flows out in the case where the pressure relief valve 30 is opened.
  • the outflow pipe is connected to the second opening port 30b.
  • the internal valve flow-passage portion 30c forms a flow passage that causes the first opening port 30a and the second opening port 30b to communicate with each other.
  • the valve body 30d is provided in an intermediate portion of the internal valve flow-passage portion 30c.
  • the valve body 30d closes the flow passage formed by the internal valve flow-passage portion 30c.
  • the pressure relief valve 30 is closed, the second opening port 30b and the water circuit 20 do not communicate with each other, and the refrigerant or the water in the water circuit 20 does not flow out from the second opening port 30b.
  • the valve body 30d opens the flow passage formed by the internal valve flow-passage portion 30c.
  • the pressure relief valve 30 in the case where the pressure in the water circuit 20 exceeds the set value, the pressure relief valve 30 is in the opened state, the second opening port 30b and the water circuit 20 communicate with each other, and the water or the refrigerant in the water circuit 20 flows out from the second opening port 30b. Furthermore, when the pressure in the water circuit 20 exceeds the set value and the valve body 30d is opened, and then when the pressure in the water circuit 20 is reduced lower than or equal to the set value, the state of the valve body 30d is returned to a closed state in which the valve body 30d closes the flow passage formed by the internal valve flow-passage portion 30c.
  • connection port 48 is provided to extend from the end plate 43A toward the outside of the plate heat exchanger 40. Furthermore, the first opening port 30a of the pressure relief valve 30 is connected to a front end of the connection port 48. In other words, the connection port 48 is connected to the pressure relief valve 30 provided separately from the plate heat exchanger 40. Moreover, the entire pressure relief valve 30 is located further outward of the plate heat exchanger 40 than the end plate 43A.
  • the plurality of heat transfer plates 41 and the pair of end plates 43 are provided.
  • the plurality of heat transfer plates 41 are stacked together in a single direction, isolate the first flow passage that allows the first fluid (heat medium) to flow and the second flow passage that allows the second fluid (refrigerant) to flow, and cause heat exchange to be performed between the first fluid in the first flow passage and the second fluid in the second flow passage.
  • the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D are formed to extend through the heat transfer plate 41 in the stacking direction.
  • the first inlet port 44, the first outlet port 45, the second inlet port 46, the second outlet port 47, and the connection port 48 are provided, and the pair of end plates 43A and 43B are located such that the heat transfer plates 41 are sandwiched between the end plates 43A and 43B in the above single direction.
  • the first inlet port 44 is continuous with the first through-holes 42A and located as a port through which the first fluid flows into the first flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B and located as a port through which the first fluid flows out from the first flow passage.
  • the second inlet port 46 is continuous with the third through-holes 42C and located as a port through which the second fluid flows into the second flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D and located as a port through which the second fluid flows out from the second flow passage.
  • the connection port 48 is continuous with the first through-holes 42A or the second through-holes 42B, branches off from the first flow passage, and is connected to the pressure relief valve 30 provided separately the plate heat exchanger 40. In this configuration, since the pressure relief valve 30 provided separately from the plate heat exchanger 40 is connected to the connection port 48, as the pressure relief valve 30, an appropriate valve can be selected from a larger number of kinds of valves, and the pressure relief valve 30 can be more flexibly designed.
  • the heat pump apparatus 1 includes: the refrigerant circuit 10 in which the compressor 12, the plate heat exchanger 40, the expansion mechanism 13, and the heat-source-side heat exchanger are connected by the refrigerant pipes 11 to circulate the refrigerant; the heat medium circuit in which the pump 22, the plate heat exchanger 40, and the use-side heat exchanger are connected by the heat medium pipes to circulate the heat medium; and the pressure relief valve 30 that is connected to the connection port 48 branching off from the heat medium circuit in the plate heat exchanger 40, and that is provided separately from the plate heat exchanger 40.
  • the pressure relief valve 30 is provided separately from the plate heat exchanger 40, as the pressure relief valve 30, an appropriate valve can be selected from a larger number of kinds of valves, and the pressure relief valve 30 can be more flexibly designed.
  • the plate heat exchanger 40 include the plurality of heat transfer plates 41 and the pair of end plates 43.
  • the heat transfer plates 41 are stacked together in the single direction, isolate the first flow passage (heat medium circuit) through which the first fluid (heat medium) flows and the second flow passage (refrigerant circuit) through which the second fluid (refrigerant) flows, and cause heat exchange to be performed between the first fluid in the first flow passage and the second fluid in the second flow passage.
  • Each of the heat transfer plates 41 includes the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D that extend through the heat transfer plate 41 in the single direction.
  • the end plates 43 include the first inlet port 44, the first outlet port 45, the second inlet port 46, the second outlet port 47, and the connection port 48, and are located such that the heat transfer plates 41 are sandwiched between the end plates 43.
  • the first inlet port 44 is continuous with the first through-holes 42A and located as a port through which the first fluid flows into the first flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B and located as a port through which the first fluid flows from the first flow passage.
  • the second inlet port 46 is continuous with the third through-holes 42C and located as a port through which the second fluid flows into the second flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D and located as a port through which the second fluid flows out from the second flow passage.
  • the connection port 48 is continuous with the first through-holes 42A or the second through-holes 42B and being branched from the first flow passage.
  • the heat pump apparatus 1 according to Embodiment 3 has as another additional configuration the following configuration: in the case where the pressure in the heat medium circuit exceeds the predetermined set value, the pressure relief valve 30 is opened, and in the case where the pressure in the heat medium circuit is less than or equal to the set value after the pressure relief valve 30 is opened, the pressure relief valve 30 is closed. Because of provision of this additional configuration, the heat pump apparatus according to Embodiment 3 can reduce the outflow amount of the heat medium or refrigerant. In particular, this is more advantageous in the case where the refrigerant is combustible.
  • the outflow amount of the refrigerant can be reduced, it is possible to reduce the probability with which the density of staying refrigerant reaches a density at which the refrigerant burns, by reducing the outflow amount of the refrigerant.
  • the heat pump apparatus 1 according to Embodiment 3 has as a further additional configuration the following configuration: in which the entire pressure relief valve 30 is located outside the plate heat exchanger 40. If part of the pressure relief valve is located in the plate heat exchanger, the pressure relief valve may block the flow of the fluid that flows through the heat transfer plates, thus reducing the heat exchange efficiency of the plate heat exchanger.
  • the pressure relief valve does not block the flow of the fluid that flows through the heat transfer plates, and the heat exchange efficiency is not reduced.
  • the heat pump apparatus 1 according to Embodiment 3 has as still another configuration the following configuration: the pressure relief valve 30 is provided in the outdoor space. Because of this configuration, the heat pump apparatus 1 according to Embodiment 3 can reduce the possibility with which in the indoor space, suffocation may be caused by the refrigerant gas as described in Embodiment 1. In particular, this is more advantageous in the case where the refrigerant is combustible. That is, since the refrigerant does not flow into the indoor space, it is possible to reduce the possibility that the refrigerant gas will burn in the indoor space.
  • the heat pump apparatus 1 according to Embodiment 3 has as a still further additional configuration the following configuration: the outflow pipe through which the fluid that has flowed out from the pressure relief valve 30 flows out to the outdoor space is connected to the pressure relief valve 30. Because of this additional configuration, the heat pump apparatus 1 according to Embodiment 3 can reduce the possibility with which suffocation may be caused by the refrigerant gas in the indoor space, as described in Embodiment 1. In particular, this is more advantageous in the case where the refrigerant is combustible. That is, since the refrigerant does not flow to the indoor space, it is possible to reduce the possibility with which refrigerant gas may burn in the indoor space.
  • the check valve 26 as described regarding Embodiment 2 may be provided in the heat pump apparatus 1 according to Embodiment 3.
  • a heat pump apparatus of the modification of Embodiment 3 has as an additional configuration the following configuration: in the heat medium circuit, the check valve is provided between the pump and the plate heat exchanger. Because of this additional configuration, in the heat pump apparatus of the modification of Embodiment 3, it is possible to cause the refrigerant that has flowed into the heat medium flow passage to flow out more concentratedly from the pressure relief valve, as described regarding Embodiment 2.
  • a flow-passage sectional area of the first opening port 30a, a flow-passage sectional area of the second opening port 30b, and a flow-passage sectional area of the flow passage formed by the internal valve flow-passage portion 30c be each greater than a flow-passage sectional area of the connection port 48.
  • the flow-passage sectional area means a sectional area at a surface perpendicular to the flow direction of the water or the refrigerant that flows through the flow passage.
  • the flow direction of the water or the refrigerant that flows through the first opening port 30a, the second opening port 30b, and the flow passage formed by the internal valve flow-passage portion 30c is the flow direction of the water or the refrigerant that flows out from the second opening port 30b, with the pressure relief valve 30 opened.
  • the heat pump apparatus has as an additional configuration the following configuration: the pressure relief valve includes the first opening port connected to the connection port, the second opening port through which the heat medium or the refrigerant flows out, and the internal valve flow-passage portion forming the flow passage through which the first opening port and the second opening port communicate with each other; and the flow-passage sectional area of the first opening port, the flow-passage sectional area of the second opening port, and the flow-passage sectional area of the flow passage formed by the internal valve flow-passage portion are each greater than the flow-passage sectional area of the connection port. Because of this additional configuration, even when ice adheres to the flow passage in the pressure relief valve, the pressure relief valve is not easily closed.
  • connection port 48 and the pressure relief valve 30 are directly connected to each other; however, the connection between the connection port and the pressure relief valve is not limited to such a direct connection.
  • the connection port and the pressure relief valve may be connected by a connection pipe.
  • the heat pump apparatus of the modification of Embodiment 3 has as another additional configuration the following configuration: the connection port and the pressure relief valve are connected by the connection pipe. Because of this additional configuration, in the heat pump apparatus of the modification of Embodiment 3, the location of the pressure relief valve is further flexible. In particular, this is more advantageous in the case where the refrigerant is combustible. That is, the pressure relief valve can be provided far from a component that can become an ignition source, such as an electric circuit. It is therefore possible to reduce the possibility that the refrigerant may burn.
  • the flow-passage sectional area of the connection pipe should be greater than the flow-passage sectional area of the connection port 48. That is, the heat pump apparatus of the modification of Embodiment 3 has as a further additional configuration the following configuration: the flow-passage sectional area of the connection pipe is greater than the flow-passage sectional area of the connection port. Because of this additional configuration, even if ice adheres to the flow passage in the pressure relief valve, the pressure relief valve is not easily closed.
  • the flow-passage sectional area of the connection port 48 and the flow-passage sectional area of the first outlet port 45 are substantially equal to each other; however, the relationship between the flow-passage sectional areas of the connection port 48 and the first outlet port 45 is not limited to the above relationship.
  • the flow-passage sectional area of the connection port may be made greater than the flow-passage sectional area of the first outlet port. That is, the plate heat exchanger or the heat pump apparatus of the modification of Embodiment 3 has as still another additional configuration the following configuration: the flow-passage sectional area of the connection port is greater than the flow-passage sectional area of the first outlet port.
  • the refrigerant easily flows out from an outflow port having a large flow-passage sectional area.
  • the flow-passage sectional area of the connection port is greater than the flow-passage sectional area of the first outlet port, the refrigerant that has leaked to the heat medium circuit easily flows out to the connection port having a large flow-passage sectional area than the first outlet port having a small flow-passage sectional area. Therefore, because of this additional configuration, in the plate heat exchanger or the heat pump apparatus of the modification of Embodiment 3, when the refrigerant leaks to the heat medium circuit, this leak refrigerant easily flows out to the connection port 48, and can be made to promptly flow out to the outside.
  • Fig. 9 is a schematic front view illustrating a plate heat exchanger according to Embodiment 4 of the present disclosure.
  • Fig. 10 is a sectional view taken along line X-X in Fig. 9 . It should be noted that components that have the same configurations as those in the above heat pump apparatus 1 according to Embodiment 1 will be denoted by the same reference signs, and their detailed descriptions will thus be omitted.
  • a temperature sensor 31 is attached to the plate heat exchanger 40.
  • the heat pump apparatus according to Embodiment 4 is different from the heat pump apparatus 1 according to Embodiment 1.
  • a thermistor is used as the temperature sensor 31, for example, a thermistor is used.
  • the temperature sensor 31 is provided on a surface of the end plate 43A.
  • the end plate 43A includes the connection port 48 connected to the pressure relief valve 30, the second inlet port 46, and the second outlet port 47. Furthermore, the temperature sensor 31 is provided close to the connection port 48. Therefore, the distance between the temperature sensor 31 and the connection port 48 is smaller than the distance between the temperature sensor 31 and the second inlet port 46 and the distance between the temperature sensor 31 and the second outlet port 47.
  • the distance between the temperature sensor 31 and the connection port 48 is smaller than the distance between the temperature sensor 31 and the first inlet port 44 and the distance between the temperature sensor 31 and the first outlet port 45.
  • the temperature sensor 31 is located between the connection port 48 and an end portion 43A1 of the end plate 43A.
  • the second inlet port 46 and the second outlet port 47 are not located between the connection port 48 and the end portion 43A1 of the end plate 43A. That is, the temperature sensor 31 is located between the connection port 48 and the end portion 43A1 of the end plate 43A, and the other inlet port and outlet port provided in the end plate 43A are not located between the connection port 48 and the end portion 43A1 of the end plate 43A.
  • the temperature sensor 31 detects the temperature of the surface of the end plate 43A.
  • the temperature of the surface of the end plate 43A follows the temperature of the water that flows in the plate heat exchanger 40, that is, as the temperature of the water that flows in the plate heat exchanger 40 rises or drops, the temperature of the surface of the end plate 43A also rises or drops. Therefore, the temperature sensor 31 detects a temperature related to the water that flows in the plate heat exchanger 40.
  • the temperature sensor 31 is connected to a controller not illustrated such that the temperature sensor 31 can communicate with the controller. Information on the temperature detected by the temperature sensor 31 is transmitted to the controller.
  • the controller is connected to at least the compressor 12 such that the controller can communicate with the compressor 12.
  • the controller can control the compressor 12 based on the received information on the temperature detected by the temperature sensor 31. In the case where the temperature detected by the temperature sensor 31 that is indicated by the received information is less than a predetermined threshold, the controller stops an operation of the compressor 12. Furthermore, the controller finally stops the pump, the fan, and the other components included in the heat pump apparatus. Also, it is preferable that the controller include a notification unit that notifies a user of detection of refrigerant leakage.
  • the controller includes a processor that executes a control program, a memory that stores the control program to be executed by the processor, and a hardware interface that connects the processor or the memory to the temperature sensor 31 and the compressor 12 such that the processor or the memory can communicate with the temperature sensor 31 and the compressor 12.
  • the plate heat exchanger 40 according to Embodiment 4 includes the plurality of the heat transfer plates 41 and the pair of end plates 43.
  • Each of the heat transfer plates 41 includes the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D that extend through the heat transfer plate 41 in the single direction.
  • the heat transfer plates 41 are stacked together in the single direction, isolate the first flow passage (heat medium circuit) through which the first fluid (heat medium) flows and the second flow passage (refrigerant circuit) through which the second fluid (refrigerant) flows, and cause heat exchange to be performed between the first fluid in the first flow passage and the second fluid in the second flow passage.
  • the pair of end plates 43A and 43B include the first inlet port 44, the first outlet port 45, the second inlet port 46, the second outlet port 47, and the connection port 48, and are located such that the heat transfer plates 41 are sandwiched between the end plates 43 in the single direction.
  • the first inlet port 44 is continuous with the first through-holes 42A and located as a port through which the first fluid flows into the first flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B and located as a port through which the first fluid flows out from the first flow passage.
  • the second inlet port 46 is continuous with the third through-holes 42C and located as a port through which the second fluid flows into the second flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D and located as a port through which the second fluid flows out from the second flow passage.
  • the connection port 48 is continuous with the first through-holes 42A or the second through-holes 42B, branches off from the first flow passage, and is a port for connection of the pressure relief valve 30. Because of the above configuration, the plate heat exchanger 40 according to Embodiment 4 can prevent the water from being cooled by the refrigerant, and thus prevent ice from being made, thereby preventing the pressure relief valve from being closed by ice, as described in Embodiment 1.
  • the plate heat exchanger 40 according to Embodiment 4 includes as an additional configuration a temperature sensor that detects a temperature related to the heat medium that flows in the plate heat exchanger 40. Because of this additional configuration, in the plate heat exchanger 40 according to Embodiment 4, the temperature sensor 31 can detect the temperature related to the refrigerant that flows in the plate heat exchanger 40. If the plate heat exchanger 40 is damaged and a refrigerant leak occurs, this leak refrigerant is made to flow out from the pressure relief valve 30 attached to the plate heat exchanger 40 to the outside. Therefore, in the entire flow passage in the water circuit 20 in the heat pump apparatus 1, the temperature of the water flow passage in the plate heat exchanger 40 drops first. Therefore, because of the additional configuration, when a refrigerant leak occurs, the plate heat exchanger 40 according to Embodiment 4 can early detect the refrigerant leak.
  • the plate heat exchanger 40 according to Embodiment 4 has as another additional configuration the following configuration: the temperature sensor 31 is attached to the end plate 43A having the connection port 48. In the case where a refrigerant leakage occur, this leak refrigerant is made to flow out from the pressure relief valve 30 connected to the connection port 48 to the outside. Therefore, because of this additional configuration, since the temperature of the end plate 43A including the connection port 48 remarkably drops as compared with the temperature of the other end plate 43B, the plate heat exchanger 40 according to Embodiment 4 can more reliably detect the refrigerant leak.
  • the plate heat exchanger 40 according to Embodiment 4 has as a further additional configuration the following configuration: in the end plate 43A having the connection port 48, at least one of the first inlet port 44, the first outlet port 45, the second inlet port 46, and the second outlet port 47 is provided, and the distance between the connection port 48 and the temperature sensor 31 is smaller than a distance between the temperature sensor 31 and each of the first inlet port 44, the first outlet port 45, the second inlet port 46, and the second outlet port 47 in the end plate 43A having the connection port 48.
  • the temperature detected by the temperature sensor 31 is not easily influenced by the temperature of the fluid that flows through the other inlet port or outlet port, and is greatly influenced by the temperature of the fluid located close to the connection port 48 that is reduced by the refrigerant leak. Therefore, the plate heat exchanger 40 according to Embodiment 4 can more reliably detect the refrigerant leak.
  • the plate heat exchanger 40 according to Embodiment 4 has as still another configuration the following configuration: as viewed from a direction perpendicular to the surface of the end plate 43A having the connection port 48, the temperature sensor 31 is located between the connection port 48 and the end portion 43A1 of the end plate 43A, and none of the first inlet port 44, the first outlet port 45, the second inlet port 46, and the second outlet port 47 is located between the connection port 48 and the end portion 43A1 of the end plate 43A. Because of this additional configuration, the temperature detected by the temperature sensor 31 is not easily influenced by the temperature of the fluid that flows through the other inlet port or outlet port, and is greatly influenced by the temperature of the fluid located close to the connection port 48 that is reduced by a refrigerant leak. Therefore, the plate heat exchanger 40 according to Embodiment 4 can more reliably detect the refrigerant leak.
  • the heat pump apparatus 1 includes: the refrigerant circuit 10 in which the compressor 12, the plate heat exchanger 40, the expansion mechanism 13, and the heat-source-side heat exchanger are connected by the refrigerant pipes 11 to circulate the refrigerant; the heat medium circuit in which the pump 22, the plate heat exchanger 40, and the use-side heat exchanger are connected by the heat medium pipes to circulate the heat medium; and the pressure relief valve 30 connected to the connection port 48 that branches off from the heat medium circuit in the plate heat exchanger 40.
  • the heat pump apparatus 1 includes as a still further additional configuration the controller that is connected to the temperature sensor 31 and the compressor 12 such that the controller can communicate with the temperature sensor 31 and the compressor 12, and when the temperature detected by the temperature sensor 31 is less than a predetermined threshold, the controller stops the compressor 12. Because of this additional configuration, when a refrigerant leak occurs, the compressor can be automatically stopped, and it is possible to reduce the influence of the refrigerant leak.
  • the controller finally stops the pump, the fan, and the other components that are included in the heat pump apparatus, and because of this additional configuration, the heat pump apparatus can be automatically stopped when a refrigerant leak occurs, and the influence of the refrigerant leak can be reduced; and secondly, preferably, the controller should include the notification unit that notifies the user of detection of the refrigerant leak, and because of the above additional configuration, it is possible to notify the user of occurrence of the refrigerant leak.
  • the plate heat exchanger 40 according to Embodiment 4 includes the plurality of the heat transfer plates 41 and the pair of end plates 43.
  • Each of the heat transfer plates 41 includes the first through-hole 42A, the second through-hole 42B, the third through-hole 42C, and the fourth through-hole 42D that extend through the heat transfer plate 41 in the single direction.
  • the heat transfer plates 41 are stacked together in the single direction, isolate the first flow passage (heat medium circuit) through which the first fluid (heat medium) flows and the second flow passage (refrigerant circuit) through which the second fluid (refrigerant) flows, and cause heat exchange to be performed between the first fluid in the first flow passage and the second fluid in the second flow passage.
  • the pair of end plates 43A and 43B include the first inlet port 44, the first outlet port 45, the second inlet port 46, the second outlet port 47, and the connection port 48, and are located such that the heat transfer plates 41 are sandwiched between the end plates 43 in the single direction.
  • the first inlet port 44 is continuous with the first through-holes 42A and located as a port through which the first fluid flows into the first flow passage.
  • the first outlet port 45 is continuous with the second through-holes 42B and located as a port through which the first fluid flows out from the first flow passage.
  • the second inlet port 46 is continuous with the third through-holes 42C and located as a port through which the second fluid flows into the second flow passage.
  • the second outlet port 47 is continuous with the fourth through-holes 42D and located as a port through which the second fluid flows out from the second flow passage.
  • the connection port 48 is continuous with the first through-holes 42A or the second through-holes 42B, branches off from the first flow passage, and is connected to the pressure relief valve 30 provided separately from the plate heat exchanger 40.
  • the heat pump apparatus 1 includes: the refrigerant circuit 10 in which the compressor 12, the plate heat exchanger 40, the expansion mechanism 13, and the heat-source-side heat exchanger are connected by the refrigerant pipes 11 to circulate the refrigerant; the heat medium circuit in which the pump 22, the plate heat exchanger 40, and the use-side heat exchanger are connected by the heat medium pipes to circulate the heat medium; and the pressure relief valve 30 that is connected to the connection port 48 branching off from the heat medium circuit in the plate heat exchanger 40, and that is provided separately from the plate heat exchanger 40.
  • Fig. 11 is a sectional view of a plate heat exchanger according to a modification of Embodiment 4 taken along line X-X in Fig. 9 .
  • the temperature sensor 31 may be provided at the heat transfer plate 41 located on a side surface of the plate heat exchanger 40.
  • the plate heat exchanger of the modification of Embodiment 4 has as an additional configuration the following configuration in which the temperature sensor is attached to the heat transfer plate located on the side surface of the plate heat exchanger. Because of this additional configuration, the plate heat exchanger of the modification of Embodiment 4 can directly detect the temperature of the surface of the heat transfer plate 41; that is, it does not detect the temperature of the surface of the heat transfer plate 41 through the end plate 43A.
  • the temperature sensor 31 be provided at one of the stacked heat transfer plates 41 that is located close to the connection port 48.
  • the temperature of the surface of the heat transfer plate 41 can be directly detected, and the temperatures of the leak refrigerant and the water on an outflow side can be detected. It is therefore possible to earlier detect the refrigerant leak.
  • the plate heat exchanger of the modification of Embodiment 4 has as another additional configuration the following configuration: the distance between the connection port 48 and the temperature sensor 31 is smaller than the distance between the first inlet port 44 and the temperature sensor 31, the distance between the first outlet port 45 and the temperature sensor 31, the distance between the second inlet port 46 and the temperature sensor 31, and the distance between the second outlet port 47 and the temperature sensor 31. Because of this additional configuration, the temperature of the fluid that flows through the other inlet port or outlet port does not greatly influence the temperature detected by the temperature sensor 31, whereas the temperature of the fluid located close to the connection port 48 that is reduced by a refrigerant leak greatly influences the temperature detected by the temperature sensor 31. Therefore, the plate heat exchanger 40 of the modification of Embodiment 4 can more reliably detect refrigerant leakage.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (12)

  1. Échangeur de chaleur à plaques (40) comprenant :
    une pluralité de plaques de transfert de chaleur (41) dans chacune desquelles un premier trou traversant (42A), un deuxième trou traversant (42B), un troisième trou traversant (42C) et un quatrième trou traversant (42D) sont prévus pour s'étendre à travers la plaque de transfert de chaleur (41) dans une direction unique, la pluralité de plaques de transfert de chaleur (41) étant empilées ensemble dans la direction unique, conçues pour isoler un premier passage d'écoulement à travers lequel un premier fluide s'écoule et un second passage d'écoulement à travers lequel un second fluide s'écoule, et conçu pour provoquer un échange de chaleur entre le premier fluide dans le premier passage d'écoulement et le second fluide dans le second passage d'écoulement ; une paire de plaques d'extrémité (43A, 43B) dans lesquelles un premier orifice d'entrée (44), un premier orifice de sortie (45), un second orifice d'entrée (46), un second orifice de sortie (47) et un orifice de raccordement (48) sont prévus, la paire de plaques d'extrémité (43A, 43B) étant prévue de telle sorte que la pluralité de plaques de transfert de chaleur (41) sont prises en sandwich entre la paire de plaques d'extrémité (43A, 43B) dans la direction unique, le premier orifice d'entrée (44) étant continu avec les premiers trous traversants (42A) et situé en tant qu'orifice à travers lequel le premier fluide s'écoule dans le premier passage d'écoulement, le premier orifice de sortie (45) étant continu avec les deuxièmes trous traversants (42B) et situé en tant qu'orifice à travers lequel le premier fluide s'écoule hors du premier passage d'écoulement, le second orifice d'entrée (46) étant continu avec les troisièmes trous traversants (42C) et situé en tant qu'orifice à travers lequel le second orifice d'entrée s'écoule dans le second passage d'écoulement, le second orifice de sortie (47) étant continu avec les quatrièmes trous traversants (42D) et situé en tant qu'orifice à travers lequel le second fluide s'écoule hors du premier passage d'écoulement, le second orifice de raccordement (48) étant continu avec les premiers trous traversants (42A) ou les seconds trous traversants (42B), et dérivant du premier passage d'écoulement,
    dans lequel l'orifice de raccordement (48) est relié à une soupape de décharge (30) prévue séparément de l'échangeur de chaleur à plaques (40),
    caractérisé en ce que l'échangeur de chaleur à plaques (40) comprend en outre un capteur de température (31) configuré pour détecter une température liée au premier fluide qui s'écoule dans l'échangeur de chaleur à plaques (40),
    dans lequel le capteur de température (31) est fixé à l'une des plaques d'extrémité (43A, 43B) qui comporte l'orifice de raccordement (48).
  2. Échangeur de chaleur à plaques (40) selon la revendication 1, dans lequel le premier orifice d'entrée (44) et le premier orifice de sortie (45) sont prévus dans une même des plaques d'extrémité (43A, 43B), et l'orifice de raccordement (48) est prévu dans une plaque restante des plaques d'extrémité (43A, 43B).
  3. Échangeur de chaleur à plaques (40) selon la revendication 1 ou 2, dans lequel dans la plaque d'extrémité (43A) comportant l'orifice de raccordement (48), au moins l'un du premier orifice d'entrée (44), du premier orifice de sortie (45), du second orifice d'entrée (46) et du second orifice de sortie (47) est prévu, et
    une distance entre l'orifice de raccordement (48) et le capteur de température (31) est inférieure à une distance entre le capteur de température (31) et chacun du premier orifice d'entrée (44), du premier orifice de sortie (45), du second orifice d'entrée (46) et du second orifice de sortie (47) qui sont prévus dans la plaque d'extrémité comportant l'orifice de raccordement (48).
  4. Échangeur de chaleur à plaques (40) selon l'une quelconque des revendications 1 à 3, dans lequel, comme observé depuis une direction perpendiculaire à une surface de la plaque d'extrémité (43A) comportant l'orifice de raccordement (48), le capteur de température (31) est situé entre l'orifice de raccordement (48) et une partie d'extrémité de la plaque d'extrémité (43A), et aucun du premier orifice d'entrée (44), du premier orifice de sortie (45), du second orifice d'entrée (46), et du second orifice de sortie (47) n'est prévu entre l'orifice de raccordement (48) et la partie d'extrémité de la plaque d'extrémité (43A).
  5. Échangeur de chaleur à plaque (40) selon l'une quelconque des revendications 1 à 4, dans lequel une zone de section de passage d'écoulement de l'orifice de raccordement (48) est supérieure à une zone de section de passage d'écoulement du premier orifice de sortie (45).
  6. Appareil de pompe à chaleur (1) comprenant :
    un circuit de fluide frigorigène dans lequel un compresseur (12), un échangeur de chaleur à plaques (40), un mécanisme d'expansion et un échangeur de chaleur côté source de chaleur sont reliés par des tuyaux de frigorigènes (11) pour faire circuler un frigorigène ;
    un circuit de milieu thermique dans lequel une pompe (22), l'échangeur de chaleur à plaques (40) et un échangeur de chaleur côté utilisation sont reliés par des tuyaux de milieu thermique pour faire circuler un milieu thermique ; et
    une soupape de décharge (30) reliée à un orifice de raccordement (48) qui dérive à partir d'une partie du circuit de milieu thermique qui est située dans l'échangeur de chaleur à plaques (40), la soupape de décharge (30) étant prévue séparément de l'échangeur de chaleur à plaques (40),
    dans lequel l'échangeur de chaleur à plaques (40) comporte une pluralité de plaques de transfert de chaleur (41) dans chacune desquelles un premier trou traversant (42A), un deuxième trou traversant (42B), un troisième trou traversant (42C) et un quatrième trou traversant (42D) sont prévus pour s'étendre à travers la plaque de transfert de chaleur dans une direction unique, la pluralité de plaques de transfert de chaleur (41) étant empilées ensemble dans la direction unique, conçues pour isoler un premier passage d'écoulement à travers lequel le milieu thermique s'écoule et un second passage d'écoulement à travers lequel le frigorigène s'écoule, et conçu pour provoquer un échange de chaleur entre le milieu thermique dans le premier passage d'écoulement et le frigorigène dans le second passage d'écoulement, et
    une paire de plaques d'extrémité (43A, 43B) dans lesquelles un premier orifice d'entrée (44), un premier orifice de sortie (45), un second orifice d'entrée (46), un second orifice de sortie (47) et l'orifice de raccordement (48) sont prévus, le premier orifice d'entrée (44) étant continu avec les premiers trous traversants (42A) et situé en tant qu'orifice à travers lequel le milieu thermique s'écoule depuis le tuyau de milieu thermique jusque dans le premier passage d'écoulement, le premier orifice de sortie (45) étant continu avec les seconds trous traversants (42B) et situé en tant qu'orifice à travers lequel le milieu thermique s'écoule hors du premier passage d'écoulement vers le tuyau de milieu thermique, le second orifice d'entrée (46) étant continu avec les troisièmes trous traversants (42C) et situé en tant que port à travers lequel le frigorigène s'écoule depuis le tuyau de frigorigène vers le second passage d'écoulement, le second orifice de sortie (47) étant continu avec les quatrièmes trous traversants (42D) et en tant qu'orifice à travers lequel le frigorigène s'écoule depuis le second passage d'écoulement au tuyau de frigorigène, l'orifice de raccordement (48) étant situé en continu avec les premiers trous traversants (42A) et opposé au premier orifice d'entrée (44) ou étant situé en continu avec les seconds trous traversants (42B) et opposé au premier orifice de sortie (45), caractérisé par un capteur de température (31) configuré pour détecter une température liée au milieu thermique qui s'écoule dans l'échangeur de chaleur à plaques (40), dans lequel le capteur de température (31) est fixé à une (43A) des plaques d'extrémité (43A, 43B) qui comporte l'orifice de raccordement (48).
  7. Appareil de pompe à chaleur (1) selon la revendication 6, dans lequel l'échangeur de chaleur à plaques (40), le premier orifice d'entrée (44) et le premier orifice de sortie (45) sont prévus dans une même (43B) des plaques d'extrémité (43A, 43B), et l'orifice de raccordement (48) est prévu dans une partie restante (43A) des plaques d'extrémité (43A, 43B).
  8. Appareil de pompe à chaleur (1) selon la revendication 6 ou 7, comprenant en outre :
    un capteur de température (31) configuré pour détecter une température liée au milieu thermique qui s'écoule dans l'échangeur de chaleur à plaques (40) ; et
    un dispositif de commande connecté au capteur de température (31) et au compresseur (12) de telle sorte que le dispositif de commande est autorisé à communiquer avec le capteur de température (31) et le compresseur (12),
    dans lequel le dispositif de commande arrête le compresseur (12) lorsqu'une température détectée par le capteur de température (31) est inférieure à un seuil prédéterminé.
  9. Appareil de pompe à chaleur (1) selon l'une quelconque des revendications 6 à 8, dans lequel la soupape de décharge (30) est ouverte lorsqu'une pression dans le circuit de milieu thermique dépasse une valeur définie prédéterminée, et la soupape de décharge (30) est fermée lorsque la pression dans le circuit de milieu thermique est inférieure ou égale à la valeur définie après que la soupape de décharge (30) est ouverte.
  10. Appareil de pompe à chaleur (1) selon l'une quelconque des revendications 6 à 9, dans lequel la soupape de décharge (30) est prévue dans un espace extérieur.
  11. Appareil de pompe à chaleur (1) selon l'une quelconque des revendications 6 à 10, dans lequel un tuyau de sortie conçu pour permettre à un fluide qui s'écoule hors de la soupape de décharge (30) de s'écouler vers un espace extérieur est relié à la soupape de décharge (30).
  12. Appareil de pompe à chaleur (1) selon l'une quelconque des revendications 6 à 11, dans lequel, dans le milieu thermique, un clapet anti-retour (26) est prévu entre la pompe (22) et l'échangeur de chaleur à plaques (40).
EP19872006.2A 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur Active EP3865802B1 (fr)

Applications Claiming Priority (2)

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
PCT/JP2019/039230 WO2020075630A1 (fr) 2018-10-10 2019-10-04 Échangeur de chaleur de type à plaques et dispositif de pompe à chaleur

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EP3865802A4 EP3865802A4 (fr) 2021-12-01
EP3865802B1 true EP3865802B1 (fr) 2023-08-16

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

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EP3865802A1 (fr) 2021-08-18
CN112771343A (zh) 2021-05-07
WO2020075238A1 (fr) 2020-04-16
EP3865802A4 (fr) 2021-12-01
WO2020075630A1 (fr) 2020-04-16
JPWO2020075630A1 (ja) 2021-06-03
JP7019068B2 (ja) 2022-02-14
US20210231355A1 (en) 2021-07-29

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