WO2015178005A1 - Stacked heat exchanger - Google Patents

Stacked heat exchanger Download PDF

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Publication number
WO2015178005A1
WO2015178005A1 PCT/JP2015/002482 JP2015002482W WO2015178005A1 WO 2015178005 A1 WO2015178005 A1 WO 2015178005A1 JP 2015002482 W JP2015002482 W JP 2015002482W WO 2015178005 A1 WO2015178005 A1 WO 2015178005A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
plate
gas
cooling water
members
Prior art date
Application number
PCT/JP2015/002482
Other languages
French (fr)
Japanese (ja)
Inventor
高橋　栄三
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN201580026632.8A priority Critical patent/CN106461298B/en
Priority to US15/309,219 priority patent/US20170122669A1/en
Priority to DE112015002434.4T priority patent/DE112015002434T5/en
Publication of WO2015178005A1 publication Critical patent/WO2015178005A1/en

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    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements

Definitions

  • the present disclosure relates to a stacked heat exchanger that exchanges heat between a refrigerant and a heat medium in a refrigeration cycle.
  • Patent Document 1 discloses an integrated cylindrical modulator that separates the gas-liquid refrigerant flowing out of the heat exchanger and stores the refrigerant.
  • the stacked heat exchanger includes a first heat exchange unit that exchanges heat between the refrigerant of the refrigeration cycle and the first heat medium.
  • the first heat exchange unit is provided between the plurality of first plate-like members stacked and joined to each other and the plurality of first plate-like members, and is arranged in the stacking direction of the plurality of first plate-like members.
  • the plurality of first refrigerant flow paths through which the refrigerant flows and the plurality of first plate-like members are arranged in the stacking direction of the plurality of first plate-like members, and the plurality of the first heat medium flows therethrough. First heat medium flow path.
  • the stacked heat exchanger includes a second end plate joined to a first end plate disposed at the outermost side in the stacking direction at one of a plurality of first plate-shaped members, a first end plate, and two ends.
  • the apparatus further includes a gas-liquid separation unit that has a space provided between the plates and separates the gas-liquid of the refrigerant that has flowed into the plate and stores excess refrigerant in the refrigeration cycle.
  • the second end plate was joined to the first end plate so as to form a space with the first end plate, and the gas-liquid separation part was configured by the space.
  • a gas-liquid separation part can be provided only by adding a plate-shaped second end plate to the first heat exchange part. For this reason, it is possible to reduce the size of the stacked heat exchanger and reduce the dead space on mounting.
  • FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. It is sectional drawing which shows a part of heat exchanger which concerns on 1st Embodiment. It is a perspective view which shows the offset fin in 1st Embodiment. It is a side view showing a heat exchanger concerning a 2nd embodiment of this indication. It is a schematic diagram showing a heat exchanger concerning a 3rd embodiment of this indication. It is IX arrow line view of FIG. FIG.
  • FIG. 10 is a sectional view taken along line XX in FIG. 9. It is a schematic diagram showing a heat exchanger concerning a 4th embodiment of this indication. It is the schematic which shows the heat exchanger which concerns on 5th Embodiment of this indication. It is the schematic which shows the flow of the refrigerant
  • the heat exchanger 10 is a condenser that condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle.
  • the cooling water of the present embodiment corresponds to the first heat medium of the present disclosure.
  • cooling water for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid can be used.
  • ethylene glycol antifreeze (LLC) is used as the cooling water.
  • the heat exchanger 10 is integrally formed by laminating and joining a large number of first plate members 11 (hereinafter simply referred to as plate members 11).
  • the laminating direction of the plate-like member 11 (vertical direction in the example of FIG. 1) is referred to as the plate laminating direction
  • one end side in the plate laminating direction (the upper end side in the example of FIG. 1) is referred to as one end side of the plate laminating direction.
  • the other end side in the plate stacking direction (the lower end side in the example of FIG. 1) is referred to as the other end side in the plate stacking direction.
  • the plate-like member 11 is an elongated, substantially rectangular plate material.
  • a specific material for example, a clad material in which a brazing material is clad on an aluminum core material is used.
  • an overhanging portion 111 is formed that protrudes in a substantially plate lamination direction (in other words, a direction substantially orthogonal to the plate surface of the plate-like member 11).
  • Many plate-like members 11 are joined to each other by brazing in a state where the plate-like members 11 are laminated with each other.
  • the many plate-like members 11 are arranged so that the protruding tips of the overhanging portions 111 face the same side (substantially downward in the example of FIG. 1).
  • a large number of plate-like members 11 include a first heat exchange section 12 (hereinafter simply referred to as a heat exchange section 12), a first tank space for refrigerant 13, a second tank space for refrigerant 14, and a first tank space for cooling water. 15 and the second tank space 16 for cooling water are formed.
  • the heat exchange unit 12 includes a plurality of first refrigerant flow paths 121 (hereinafter simply referred to as refrigerant flow paths 121) and a plurality of first cooling water flow paths 122 (hereinafter simply referred to as cooling water flow paths 122). ing.
  • the cooling water passage 122 of the present embodiment corresponds to the first heat medium passage of the present disclosure.
  • the plurality of refrigerant channels 121 and the plurality of cooling water channels 122 are formed between a large number of plate-like members 11.
  • the longitudinal directions of the refrigerant flow path 121 and the cooling water flow path 122 coincide with the longitudinal direction of the plate-like member 11.
  • the refrigerant channel 121 and the cooling water channel 122 are alternately stacked one by one in the plate stacking direction (in parallel).
  • the plate-like member 11 serves as a partition wall that partitions the coolant channel 121 and the cooling water channel 122. Heat exchange between the refrigerant flowing through the refrigerant flow path 121 and the cooling water flowing through the cooling water flow path 122 is performed via the plate-like member 11.
  • the first tank space for refrigerant 13 and the first tank space for cooling water 15 are arranged on one side (right side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12.
  • the second tank space for refrigerant 14 and the second tank space for cooling water 16 are arranged on the other side (left side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12.
  • the first tank space for refrigerant 13 and the second tank space for refrigerant 14 distribute and collect the refrigerant with respect to the plurality of refrigerant flow paths 121.
  • the first tank space for cooling water 15 and the second tank space for cooling water 16 distribute and collect the cooling water to the plurality of cooling water flow paths 122.
  • the refrigerant first tank space 13, the refrigerant second tank space 14, the cooling water first tank space 15, and the cooling water second tank space 16 are configured by communication holes formed at the four corners of the plate-like member 11. ing.
  • the first tank space 13 for refrigerant and the second tank space 14 for refrigerant are provided at two corners on the diagonal line among the four corners of the substantially rectangular plate-like member 11, and the remaining A cooling water first tank space 15 and a cooling water second tank space 16 are provided at two corners.
  • the first joint 21 and the first cooling water pipe 22 are attached to the outermost plate-like member 17 located closest to the one end side in the plate stacking direction among the many plate-like members 11 constituting the heat exchange unit 12. .
  • the first joint 21 is a member for joining refrigerant pipes, and forms the refrigerant inlet 101 of the heat exchanger 10.
  • the first cooling water pipe 22 forms the cooling water outlet 102 of the heat exchanger 10.
  • the first joint 21 is provided on one end side in the longitudinal direction of the outermost plate member 17 (right side in the example of FIG. 1).
  • the first cooling water pipe 22 is provided on the other end side in the longitudinal direction of the outermost plate member 17 (left side in the example of FIG. 1).
  • the first ceiling plate 18 located on the other end side in the plate stacking direction, that is, the outermost side in the plate stacking direction, Compared with the plate-like member 11, the length of the overhanging portion 111 in the plate stacking direction is longer.
  • a plate-like second ceiling plate 19 (second end plate) is joined to the first ceiling plate 18 by brazing so as to form a space between the first ceiling plate 18 and the first ceiling plate 18. This space may be used as an example of the gas-liquid separation unit 30 that separates the gas-liquid of the refrigerant flowing into the interior and stores excess refrigerant in the refrigeration cycle.
  • a refrigerant inflow portion 181 for allowing the refrigerant flowing through the refrigerant flow path 121 of the heat exchange unit 12 to flow into the gas-liquid separation unit 30 is provided in the lower portion of the first ceiling plate 18 in the gravity direction. It has been.
  • the refrigerant inflow portion 181 is a through hole provided in the first ceiling plate 18. More specifically, the refrigerant inflow portion 181 is located on the lower side in the gravitational direction than the liquid surface of the liquid-phase refrigerant stored in the gas-liquid separator 30 (see FIG. 2).
  • the refrigerant inflow portion 181 may be provided in the lower half region of the first ceiling plate 18 in the direction of gravity.
  • a first through hole 182 into which a first internal cooling water pipe 41 to be described later is inserted is formed on the upper side in the gravity direction of the first ceiling plate 18. More specifically, the first through hole 182 is disposed on the upper side in the gravitational direction than the liquid level of the liquid refrigerant stored in the gas-liquid separator 30. In the present embodiment, both the refrigerant inflow portion 181 and the first through hole 182 are arranged on one end side in the longitudinal direction of the first ceiling plate 18 (right side in the example of FIG. 2).
  • a refrigerant outflow portion 191 for allowing the liquid-phase refrigerant to flow out from the gas-liquid separation unit 30 to the outside is provided at a lower portion in the gravity direction of the second ceiling plate 19.
  • the refrigerant outflow portion 191 is a through hole provided in the second ceiling plate 19. More specifically, the refrigerant outflow portion 191 is located on the lower side in the gravity direction than the liquid surface of the liquid-phase refrigerant stored in the gas-liquid separation portion 30. Further, the refrigerant outflow portion 191 may be provided in the lower half region of the second ceiling plate 19 in the direction of gravity.
  • a second through hole 192 into which a first internal cooling water pipe 41 to be described later is inserted is formed on the upper side in the gravity direction of the second ceiling plate 19.
  • the inner peripheral surface of the second through hole 192 and the outer surface of the first internal cooling water pipe 41 are joined by brazing.
  • the second through hole 192 is disposed on the upper side in the gravity direction with respect to the liquid level of the liquid-phase refrigerant stored in the gas-liquid separator 30.
  • the second through hole 192 is disposed on one end side in the longitudinal direction of the second ceiling plate 19 (right side in the example of FIG. 3).
  • the refrigerant outflow portion 191 is disposed on the other end side in the longitudinal direction of the second ceiling plate 19 (left side in the example of FIG. 2).
  • a protrusion 193 for absorbing stress applied to the second ceiling plate 19 due to an increase in internal pressure of the gas-liquid separation unit 30 on the lower side in the gravity direction of the second ceiling plate 19. is provided.
  • the projection 193 the rigidity of the gas-liquid separation unit 30 can be improved.
  • a desiccant 31 for removing moisture in the liquid-phase refrigerant is provided below the gas-liquid separator 30 in the gravity direction.
  • a second joint 23 and a second cooling water pipe 24 are attached to the second ceiling plate 19.
  • the second joint 23 is a member for joining refrigerant pipes and forms the refrigerant outlet 103 of the heat exchanger 10.
  • the second cooling water pipe 24 forms the cooling water inlet 104 of the heat exchanger 10.
  • the refrigerant inlet 101 communicates with the first tank space 13 for refrigerant.
  • the refrigerant first tank space 13 communicates with the gas-liquid separation unit 30 via the refrigerant inflow portion 181.
  • the gas-liquid separator 30 communicates with the refrigerant outlet 103 via the refrigerant outlet 191.
  • a first internal cooling water passage 40 is provided in the gas-liquid separation unit 30 to allow the cooling water to flow and to connect the cooling water inlet 104 and the first cooling water tank space 15. It has been. Specifically, a first internal cooling water pipe 41 that connects the second cooling water pipe 24 and the first tank space 15 for cooling water is provided inside the gas-liquid separator 30. The first internal cooling water passage 40 is configured by the first internal cooling water pipe 41.
  • the cooling water inlet 104 communicates with the first tank space 15 for cooling water via the first internal cooling water passage 40.
  • the cooling water outlet 102 communicates with the cooling water second tank space 16.
  • a large number of plate-like members 11 constituting the heat exchanging portion 12 protrude toward one end side or the other end side in the plate stacking direction at the four corners of the plate-like member 11. It has a substantially cylindrical protrusion 11f.
  • a first tank space 13 for refrigerant, a second tank space 14 for refrigerant, a first tank space 15 for cooling water, and a second tank space 16 for cooling water are formed by the protrusion 11f.
  • the central plate-like member 11 ⁇ / b> A located at a substantially central portion in the plate stacking direction closes the protruding portion 11 f constituting the first tank space 13 for refrigerant. It has a blocking part 11g. Thereby, the first tank space 13 for refrigerant is partitioned into two spaces in the plate stacking direction.
  • the closing portion 11g is formed integrally with the protruding portion 11f, that is, the central plate member 11A.
  • the refrigerant that has flowed from the refrigerant inlet 101 moves from the first tank space 13 for refrigerant to the second tank space 14 for refrigerant through the refrigerant flow path 121 on one end side in the plate stacking direction.
  • the refrigerant flows in the refrigerant flow path 121 on the other end side in the plate stacking direction from the refrigerant second tank space 14 toward the refrigerant first tank space 13, and flows from the refrigerant inflow portion 181 into the gas-liquid separation portion 30.
  • the heat exchanger 10 is configured such that the refrigerant flow makes a U-turn once.
  • the refrigerant flowing into the gas-liquid separation unit 30 is gas-liquid separated, and the liquid-phase refrigerant flows out from the refrigerant outlet 103 to the outside.
  • cooling water flowing in from the cooling water inlet 104 flows through the cooling water flow path 122 from the cooling water first tank space 15 toward the cooling water second tank space 16 as shown by a one-dot chain arrow in FIG. And flows out from the cooling water outlet 102 to the outside.
  • offset fins 50 shown in FIG. 6 are arranged between the plate-like members 11.
  • the offset fins 50 are inner fins that are interposed between the plate-like members 11 and promote heat exchange between the refrigerant and the cooling water.
  • the offset fin 50 is a plate-like member in which a cut and raised portion 50a that is partially cut and raised is formed. A large number of the cut-and-raised portions 50a are formed in the direction F1 (that is, the longitudinal direction of the plate-like member 11) parallel to the flow direction of the refrigerant and the cooling water.
  • the cut-and-raised portions 50a adjacent to each other in the direction F1 parallel to the flow direction of the refrigerant and the cooling water are offset from each other.
  • the large number of cut-and-raised portions 50a are staggered in a direction F1 parallel to the flow direction of the refrigerant and the cooling water.
  • the offset fins 50 are joined to both adjacent plate-like members 11 by brazing.
  • the second ceiling plate 19 is joined to the first ceiling plate 18 so as to form a space between the first ceiling plate 18 and the first ceiling plate 18.
  • the gas-liquid separation unit 30 is configured by the space.
  • the gas-liquid separation part 30 can be comprised only by adding the plate-shaped 2nd ceiling board 19 with respect to the 1st heat exchange part 12. FIG. For this reason, it is possible to reduce the size of the heat exchanger 10 in which the gas-liquid separation unit 30 is integrated, and to reduce the dead space on mounting.
  • coolant outflow part 191 of the gas-liquid separation part 30 is arrange
  • the heat exchanger 10 of the present embodiment is mounted so that the longitudinal direction of the plate-like member 11, that is, the longitudinal directions of the first ceiling plate 18 and the second ceiling plate 19 coincide with the direction of gravity. Has been. At this time, the refrigerant inflow portion 181 and the refrigerant outflow portion 191 are disposed on the lower side in the gravitational direction than the liquid level of the liquid-phase refrigerant stored in the gas-liquid separation portion 30 (see FIG. 7).
  • the space below the gravity direction in the gas-liquid separation part 30 communicates with a space communicating with the refrigerant inflow part 181 and the refrigerant outflow part 191.
  • a baffle plate 32 is provided to divide the space into the space.
  • a plurality of through holes are formed in the baffle plate 32, and a space communicating with the refrigerant inflow portion 181 and a space communicating with the refrigerant outflow portion 191 communicate with each other.
  • the baffle plate 32 extends substantially parallel to the gravity direction from the lower end in the gravity direction of the gas-liquid separator 30 toward the upper side.
  • the upper end of the baffle plate 32 in the direction of gravity is disposed below the liquid level of the liquid-phase refrigerant stored in the gas-liquid separator 30.
  • the refrigerant outflow portion 191 of the gas-liquid separation unit 30 is It arrange
  • the liquid-phase refrigerant can reliably flow out from the refrigerant outflow portion 191.
  • the liquid phase refrigerant that has flowed out of the gas-liquid separator 30 and the low-pressure refrigerant in the refrigeration cycle are heat-exchanged to supercool the liquid phase refrigerant.
  • a second heat exchange unit 62 that functions as a cooling unit is connected. Note that the low-pressure refrigerant of the present embodiment corresponds to the second heat medium of the present disclosure.
  • the second heat exchange part 62 is integrally formed by laminating and joining a plurality of second plate-like members 61 to each other.
  • the multiple second plate-like members 61 include a second heat exchange section 62, a liquid tank first tank space 63, a liquid refrigerant second tank space 64, and a low pressure refrigerant first tank space 65.
  • the second tank space 66 for low-pressure refrigerant is formed.
  • the second heat exchanging unit 62 includes a plurality of second refrigerant flow paths 621 through which liquid phase refrigerant flows and a plurality of low pressure refrigerant flow paths 622 through which low-pressure refrigerant flows.
  • the low-pressure refrigerant channel 622 of the present embodiment corresponds to the second heat medium channel of the present disclosure.
  • the plurality of second refrigerant channels 621 and the plurality of low-pressure refrigerant channels 622 are formed between a large number of second plate-like members 61.
  • the longitudinal directions of the second refrigerant channel 621 and the low-pressure refrigerant channel 622 coincide with the longitudinal direction of the second plate member 61.
  • the length in the flow direction of the liquid phase refrigerant in the second plate member 61 is shorter than the length in the flow direction of the refrigerant in the first plate member 11. That is, the length of the second plate member 61 in the longitudinal direction is shorter than the length of the first plate member 11 in the longitudinal direction. Further, the stacking direction of the second plate-like member 61 is parallel to the stacking direction of the first plate-like member 11.
  • the second refrigerant flow path 621 and the low-pressure refrigerant flow path 622 are alternately laminated (parallel arrangement) one by one in the plate lamination direction.
  • the second plate member 61 serves as a partition that partitions the second refrigerant flow path 621 and the low-pressure refrigerant flow path 622. Heat exchange between the refrigerant flowing through the second refrigerant channel 621 and the low-pressure refrigerant flowing through the low-pressure refrigerant channel 622 is performed via the second plate member 61.
  • the first tank space 63 for liquid-phase refrigerant and the first tank space 65 for low-pressure refrigerant are on one side of the second refrigerant flow path 621 and the low-pressure refrigerant flow path 622 with respect to the second heat exchange section 62 (example in FIG. 8). In the right side).
  • the second tank space for liquid phase refrigerant 64 and the second tank space for low pressure refrigerant 66 are on the other side of the second refrigerant flow path 621 and the low pressure refrigerant flow path 622 with respect to the second heat exchange section 62 (example in FIG. 8). In the left side).
  • the first tank space 63 for liquid phase refrigerant and the second tank space 64 for liquid phase refrigerant distribute and collect the liquid phase refrigerant with respect to the plurality of second refrigerant flow paths 621.
  • the first tank space for low-pressure refrigerant 65 and the second tank space for low-pressure refrigerant 66 distribute and collect the low-pressure refrigerant with respect to the plurality of low-pressure refrigerant flow paths 622.
  • the first tank space 63 for liquid phase refrigerant, the second tank space for liquid phase refrigerant 64, the first tank space for low pressure refrigerant 65, and the second tank space for low pressure refrigerant 66 are formed at the four corners of the second plate member 61. It is constituted by a communication hole.
  • a second tank space 64 is provided.
  • a first tank space 65 for low-pressure refrigerant and a second tank space 66 for low-pressure refrigerant are provided.
  • the second outermost member located on the one end side in the plate stacking direction (the upper side in the example of FIG. 8) among the multiple second plate members 61 constituting the second heat exchange unit 62.
  • the end plate member 67 is joined to the second ceiling plate 19 by brazing.
  • the second endmost plate member 67 is formed with a liquid-phase refrigerant inflow hole 671 through which the liquid-phase refrigerant from the gas-liquid separator 30 flows.
  • the liquid-phase refrigerant inflow hole 671 is formed at a portion corresponding to the refrigerant outflow portion 191.
  • the liquid-phase refrigerant in the gas-liquid separation unit 30 is transferred to the second heat exchange unit 62 (specifically, the first tank space 63 for liquid-phase refrigerant) via the refrigerant outflow portion 191 and the liquid-phase refrigerant inflow hole 671. ).
  • the second plate-like member 61 constituting the second heat exchanging part 62 is located on the other end side in the plate stacking direction (the lower side in the example of FIG. 8).
  • a second joint 23, a third joint 71, and a fourth joint 72 are attached to the third outermost plate member 68.
  • the third joint 71 is a member for joining the low-pressure refrigerant pipe, and forms the low-pressure refrigerant inlet 701 of the second heat exchange unit 62.
  • the low-pressure refrigerant inlet 701 may be connected to the low-pressure side of the refrigeration cycle, and the low-pressure refrigerant of the refrigeration cycle may flow into the low-pressure refrigerant inlet 701.
  • the low-pressure refrigerant flowing into the second heat exchange unit 62 has a lower pressure than the refrigerant flowing into the first heat exchange unit 12.
  • the fourth joint 72 is a member for joining the low-pressure refrigerant pipe, and forms a low-pressure refrigerant outlet 702 of the second heat exchange unit 62.
  • the fourth joint 72 is provided on one end side in the longitudinal direction of the third outermost plate member 68 (right side in the example of FIG. 9).
  • the second joint 23 and the third joint 71 are provided on the other end side in the longitudinal direction of the third outermost plate member 68 (left side in the example of FIG. 9). Further, the second joint 23 is provided above the third joint 71 in the gravity direction.
  • Refrigerant flowing from the gas-liquid separator 30 flows through the second refrigerant flow path 621 from the first liquid-phase refrigerant tank space 63 toward the second liquid-phase refrigerant tank space 64, as indicated by solid arrows in FIG. And flows out from the refrigerant outlet 103 to the outside.
  • the low-pressure refrigerant that has flowed in from the low-pressure refrigerant inlet 701 passes through the low-pressure refrigerant flow path 622 from the second tank space 66 for low-pressure refrigerant toward the first tank space 65 for low-pressure refrigerant, as indicated by the broken-line arrows in FIG. It flows out from the low pressure refrigerant outlet 702 to the outside.
  • the second heat exchange unit 62 that functions as a supercooling unit is connected to the second ceiling plate 19 of the heat exchanger 10. Thereby, the rigidity of the gas-liquid separation part 30 can be improved.
  • the length of the second plate member 61 in the flow direction of the liquid phase refrigerant is shorter than the length of the first plate member 11 in the flow direction of the refrigerant.
  • a space is formed on one end side (right side in the example of FIG. 8) of the second heat exchange unit 62 in the refrigerant flow direction. Since this space can be effectively used as the arrangement space for the second cooling water pipe 24, it is possible to reduce the dead space on mounting.
  • a condensing part in a fin-and-tube heat exchanger that cools the refrigerant by exchanging heat between the refrigerant that circulates in the tube and the cooling air that flows outside the tube, a condensing part (this embodiment)
  • a gas-liquid separation unit is provided between the supercooling unit (corresponding to the second heat exchanging unit 62 of the present embodiment).
  • the gas-liquid separation unit since the gas-liquid separation unit is set at a position where the cooling air (running air) always hits, the state of the refrigerant in the gas-liquid separation unit changes depending on the temperature of the cooling air. There is a fear.
  • the heat exchanger 10 of the present embodiment is a water-cooled stacked heat exchanger, traveling air does not hit the gas-liquid separator 30. Therefore, it can suppress that the state of the refrigerant
  • the gas-liquid separation unit is arranged to be rigid between the condensing unit and the supercooling unit in order to arrange the gas-liquid separation unit.
  • the gas-liquid separation unit is arranged to be rigid between the condensing unit and the supercooling unit in order to arrange the gas-liquid separation unit.
  • the heat exchanger 10 of this embodiment since the gas-liquid separation part 30 can be comprised by two plate-shaped members, ie, the 1st ceiling board 18 and the 2nd ceiling board 19, manufacturing cost is reduced. It becomes possible to do.
  • the fourth embodiment is configured such that the second heat exchange unit 62 is a supercooling unit that supercools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant and the cooling water.
  • the cooling water of the present embodiment corresponds to the second heat medium of the present disclosure.
  • a large number of second plate-like members 61 include a second heat exchange unit 62, a liquid-phase refrigerant first tank space 63, a liquid-phase refrigerant second tank space 64, a cooling unit.
  • a third tank space for water 650 and a fourth tank space for cooling water 660 are formed.
  • the second heat exchange unit 62 includes a plurality of second refrigerant flow paths 621 through which liquid phase refrigerant flows and a plurality of second cooling water flow paths 623 through which cooling water flows.
  • the second cooling water channel 623 of the present embodiment corresponds to the second heat medium channel of the present disclosure.
  • the plurality of second refrigerant passages 621 and the plurality of second cooling water passages 623 are formed between a large number of second plate members 61.
  • the longitudinal directions of the second refrigerant channel 621 and the second cooling water channel 623 coincide with the longitudinal direction of the second plate member 61.
  • the second refrigerant flow path 621 and the second cooling water flow path 623 are alternately stacked one by one in the plate stacking direction (parallel arrangement).
  • the second plate-like member 61 serves as a partition that partitions the second refrigerant channel 621 and the second cooling water channel 623. Heat exchange between the refrigerant flowing through the second refrigerant flow path 621 and the cooling water flowing through the second cooling water flow path 623 is performed via the second plate member 61.
  • the first tank space 63 for liquid phase refrigerant and the third tank space for cooling water 650 are on one side of the second refrigerant flow path 621 and the second cooling water flow path 623 with respect to the second heat exchange section 62 (see FIG. 11). In the example, it is arranged on the right side).
  • the second tank space for liquid phase refrigerant 64 and the fourth tank space for cooling water 660 are on the other side of the second refrigerant flow path 621 and the second cooling water flow path 623 with respect to the second heat exchange section 62 (see FIG. 11). In the example, it is arranged on the left side).
  • the cooling water third tank space 650 and the cooling water fourth tank space 660 distribute and collect the cooling water to the plurality of second cooling water flow paths 623.
  • the first tank space 63 for liquid phase refrigerant, the second tank space for liquid phase refrigerant 64, the third tank space for cooling water 650, and the fourth tank space for cooling water 660 are formed at the four corners of the second plate member 61. It is constituted by a communication hole.
  • the third tank space for cooling water 650 and the fourth tank space for cooling water 660 are provided at two corners on the diagonal line among the four corners of the substantially rectangular second plate-shaped member 61. Yes.
  • the second endmost plate member 67 is formed with a through hole (not shown) into which a second internal cooling water pipe 81 described later is inserted. This through hole is brazed to the outer surface of the second internal cooling water pipe 81. Further, the through hole is provided at an end portion on the opposite side to the liquid-phase refrigerant inflow hole 671 in the longitudinal direction of the second outermost plate member 67.
  • the second joint 23 and the third cooling water pipe 73 are attached to the third outermost plate member 68.
  • the third cooling water pipe 73 forms a cooling water inlet 703 of the second heat exchange unit 62.
  • the third cooling water pipe 73 is provided on one end side in the longitudinal direction of the third outermost plate member 68 (right side in the example of FIG. 11).
  • the second joint 23 is provided on the other end side in the longitudinal direction of the third outermost plate member 68 (left side in the example of FIG. 8).
  • the second internal cooling water passage 80 that allows the cooling water to circulate and communicates the fourth tank space for cooling water 660 and the second tank space for cooling water 16 is provided. .
  • a second internal cooling water pipe 81 that connects the fourth cooling water tank space 660 and the second cooling water tank space 16 is provided inside the gas-liquid separation unit 30.
  • the second internal cooling water pipe 81 constitutes a second internal cooling water passage 80.
  • the plate-shaped member 11 located in the 1st ceiling board 18 side rather than the approximate center part of a plate lamination direction.
  • the 1st tank space 15 for cooling water is divided into two spaces in the board lamination direction.
  • the plate-like member 11 located between the substantially central portion in the plate stacking direction and the outermost plate-like member 17 is cooled.
  • a second closing part (not shown) for closing a protruding part (not shown) constituting the second tank space 16 for water is provided. Thereby, the cooling water second tank space 16 is partitioned into two spaces in the plate stacking direction.
  • the cooling water that has flowed into the cooling water third tank space 650 from the cooling water inlet 703 of the second heat exchanging unit 62 flows through the cooling water flow path 623, It flows into the 4-tank space 660.
  • the cooling water flowing into the fourth cooling water tank space 660 flows through the second internal cooling water passage 80 and flows into the second cooling water tank space 16 of the first heat exchange unit 12.
  • the cooling water flowing into the cooling water first tank space 15 from the cooling water inlet 104 of the heat exchanger 10 via the first internal cooling water passage 40 is the other side in the plate stacking direction (in the example of FIG. Side) first cooling water flow path 122 and flows into the cooling water second tank space 16.
  • the heat exchanger 10 of this embodiment passes the 2nd heat exchange part 62 with the cooling water which flowed in from the cooling water inlet 104 of the heat exchanger 10 in the 2nd tank space 16 for cooling water.
  • the cooling water is configured to merge.
  • the cooling water flowing into the second cooling water tank space 16 flows from the second cooling water tank space 16 toward the first cooling water tank space 15 through the first cooling water flow path 122 at the center side in the plate stacking direction. Thereafter, the coolant flows through the first cooling water flow path 122 on one end side in the plate stacking direction (upper side in the example of FIG. 11) from the first cooling water tank space 15 toward the second cooling water tank space 16, and the cooling water outlet. It flows out from 102. That is, the first heat exchange unit 12 is configured such that the flow of the cooling water makes a U-turn twice.
  • the cooling water that has flowed into the first heat exchange unit 12 from the cooling water inlet 104 of the heat exchanger 10 and the second heat exchange unit 62 are passed through. Both cooling water and water are introduced. That is, the cooling water can be allowed to flow in parallel to the first heat exchange unit 12. For this reason, it is possible to reduce the pressure loss of the cooling water in the first heat exchange unit 12 and to improve the heat exchange efficiency of the first heat exchange unit 12.
  • the fifth embodiment abolishes the cooling water inlet 104 and the first internal cooling water pipe 41 and passes through the second heat exchange unit 62 in the first heat exchange unit 12. The point which heat-exchanges a later cooling water and a refrigerant
  • the central plate-like member 11A among the multiple first plate-like members 11 constituting the first heat exchanging portion 12 is a protruding portion (not shown) constituting the second tank space 16 for cooling water.
  • a closing portion (not shown) that closes the opening).
  • the cooling water that has flowed into the second cooling water tank space 16 cools the first cooling water flow path 122 on the other side in the plate stacking direction (downward in the example of FIG. 12) from the second cooling water tank space 16.
  • the first cooling water flow path 122 on one end side in the plate stacking direction passes through the first cooling water flow path 122 from the first cooling water tank space 15. It flows toward the tank space 16 and flows out from the cooling water outlet 102 to the outside. That is, the first heat exchange unit 12 is configured such that the flow of the cooling water makes a U-turn once.
  • the cooling water after passing through the second heat exchange unit 62 is caused to flow into the first heat exchange unit 12. That is, the entire amount of cooling water that flows into the heat exchanger 10 is circulated through the second heat exchange unit 62. For this reason, the supercooling of the liquid-phase refrigerant separated by the gas-liquid separation unit 30 can be performed preferentially.
  • the condensation mode is a mode for causing the heat exchanger 10 to function as a condenser for condensing the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle.
  • the evaporation mode is a mode in which the heat exchanger 10 functions as an evaporator that exchanges heat between the low-pressure side refrigerant and the cooling water of the refrigeration cycle to evaporate the low-pressure side refrigerant.
  • the solid arrow indicates the refrigerant flow in the condensation mode
  • the two-dot chain arrow indicates the refrigerant flow in the evaporation mode
  • the one-dot chain arrow indicates the cooling water flow. .
  • the second joint 23 of the present embodiment forms a first refrigerant outlet 103 through which the refrigerant flows out from the second heat exchanging unit 62 during the condensation mode.
  • the second joint 23 is disposed on the uppermost side in the gravity direction of the third endmost plate-like member 68.
  • the third cooling water pipe 73 is also arranged on the upper side in the gravity direction of the third outermost plate member 68.
  • a fifth joint 75 is attached to the end of the second ceiling plate 19 on the side close to the refrigerant inflow portion 181 in the longitudinal direction.
  • the fifth joint 75 is a member for joining the refrigerant pipes, and forms a second refrigerant outlet 705 that allows the refrigerant to flow out from the gas-liquid separator 30 in the evaporation mode.
  • the refrigerant inflow portion 181 and the fifth joint 75 are disposed on the upper side in the gravity direction of the second ceiling plate 19.
  • the refrigerant that has flowed from the refrigerant inflow portion 181 into the gas-liquid separation portion 30 is separated into gas and liquid by the gas-liquid separation portion 30.
  • the liquid-phase refrigerant that has been gas-liquid separated by the gas-liquid separation unit 30 flows into the liquid-phase refrigerant first tank space 63 from the liquid-phase refrigerant inflow hole 671.
  • the refrigerant that has flowed into the first liquid phase refrigerant tank space 63 flows from the first liquid phase refrigerant tank space 63 toward the second liquid phase refrigerant tank space 64 through the second refrigerant flow path 621, and the refrigerant outlet 103. Out to the outside.
  • the refrigerant that has flowed from the refrigerant inflow portion 181 to the gas-liquid separation portion 30 flows out from the second refrigerant outlet 705 to the outside.
  • the gas-liquid separation unit 30 has a refrigerant passage that allows the refrigerant flowing from the first heat exchange unit 12 to flow out to the second heat exchange unit 62 in the condensation mode, and the first heat exchange unit 12 to flow in the evaporation mode. And a refrigerant passage through which the refrigerant flows out.
  • switching of the refrigerant flow path in the heat exchanger 10 can be performed by a valve or the like provided outside the heat exchanger 10 (more specifically, on the refrigerant outlet side).
  • the evaporation mode and the condensation mode can be switched.
  • the heat exchanger 10 of the present embodiment is capable of forming the refrigerant flow in the condensation mode and the refrigerant flow in the evaporation mode inside the heat exchanger 10.
  • the heat exchanger 10 of this embodiment can be used suitably as an outdoor unit of a heat pump cycle.
  • water cooling of the outdoor unit can be achieved, and from this, the refrigerant behavior is stabilized by the heat storage effect of the cooling water, and COP control can be easily performed.
  • the gas-liquid separator 30 of this embodiment is integrally formed by stacking and joining a plurality of third plate-like members 91 to each other.
  • the lamination direction of the third plate member 91 is parallel to the lamination direction (plate lamination direction) of the first plate member 11.
  • the third plate-like member 91 is equal in length to the first plate-like member 11 in the arrangement direction and in the width direction.
  • the multiple third plate-like members 91 are arranged so that the protruding tips of the overhang portions 911 face the same side.
  • the first plate-like member 11 is arranged so that the protruding tip of the overhanging portion 111 faces the side opposite to the gas-liquid separation portion 30 (the upper side in the example of FIG. 19).
  • the second plate-like member 61 and the third plate-like member 91 are such that the protruding tips of the overhang portions 611 and 911 face the opposite side to the first heat exchange portion 12 (the lower side in the example of FIG. 19), respectively. Is arranged.
  • a plurality of gas-liquid separation passages 92 through which the refrigerant flowing from the first refrigerant channel 121 of the first heat exchange unit 12 flows are formed between the plurality of third plate-like members 91. ing.
  • the 3rd plate-shaped member 91 is provided with the 1st through-hole 912, and the gas-liquid separation channel
  • the third plate-like member 91 located closest to one end side in the plate stacking direction is the third ceiling plate 93 (third end plate).
  • the third plate-like member 91 located closest to the other end side in the plate stacking direction is referred to as a fourth ceiling plate 94 (fourth end plate).
  • the third ceiling plate 93 is joined to the surface of the first ceiling plate 18 on the other end side in the plate stacking direction.
  • the second ceiling plate 19 is joined to the surface on the other end side in the plate stacking direction of the overhanging portion 911 of the fourth ceiling plate 94.
  • the third ceiling plate 93 is thicker than the other third plate member 91.
  • the third plate-like member 91 is provided with a second through hole 913 through which the first internal cooling water pipe 41 passes and a third through hole (not shown) through which the second internal cooling water pipe 81 passes.
  • the first internal cooling water pipe 41 is formed integrally with the second cooling water pipe 24.
  • the insertion for inserting the desiccant 95 into the gas-liquid separation unit 30 is performed on the second ceiling plate 19 other than the part where the second heat exchange unit 62 is joined.
  • a mouth 96 is provided.
  • the insertion port 96 is closed by a plug portion 97.
  • the desiccant 95 is one in which granular zeolite for water absorption is stored inside the bag body, and absorbs moisture in the refrigerant. This is to prevent each functional component constituting the refrigeration cycle from being corroded by moisture in the refrigerant, or freezing in the pores of the expansion valve to stagnate the refrigerant flow.
  • the desiccant 95 is disposed inside the gas-liquid separator 30, that is, at a portion corresponding to the insertion port 96 in the gas-liquid separation passage 92. In the present embodiment, the desiccant 95 is disposed in the vicinity of the first through hole 912.
  • the third ceiling plate 93 of the present embodiment is provided with a recess.
  • the recess is formed by denting a part of the third ceiling plate 93 toward the other side in the plate stacking direction.
  • a gap is formed between the first ceiling plate 18 and the third ceiling plate 93, that is, between the first heat exchange unit 12 and the gas-liquid separation unit 30. Can do.
  • the gas-liquid separation space in the gas-liquid separation unit 30 is configured by a large number of third plate members 91. Therefore, since a refrigerant
  • the desiccant 95 is installed in the gas-liquid separator 30. In order to do this, it is necessary to add dedicated parts. For this reason, there exists a problem that manufacturing cost increases.
  • the length of the second plate member 61 in the refrigerant flow direction is shorter than the length of the first plate member 11 in the refrigerant flow direction.
  • an insertion port 96 for inserting the desiccant 95 into the gas-liquid separation unit 30 is provided at a portion of the second ceiling plate 19 other than the portion where the second heat exchange unit 62 is joined. According to this, it is possible to insert the desiccant 95 into the gas-liquid separator 30 without adding a dedicated part for installing the desiccant 95.
  • the offset fin 50 is arrange
  • the third plate-like member 91 is cooled by the liquid phase refrigerant in the gas-liquid separation unit 30, even when bubbles (gas phase refrigerant) are slightly mixed when flowing into the gas-liquid separation unit 30, The bubbles are cooled and condensed by exchanging heat with the third plate-like member 91.
  • the gas-liquid separation property of the gas-liquid separation unit 30 can be improved.
  • a recess is provided in the third ceiling plate 93 so that a gap is formed between the first heat exchange unit 12 and the gas-liquid separation unit 30.
  • cooling water cooled by a radiator (not shown) is caused to flow from the cooling water inlet 104 into the first heat exchange section 12 via the first internal cooling water passage 40 and from the cooling water inlet 703 to the first. 2
  • the heat exchange section 62 is made to flow. Therefore, by controlling the amount of cooling water flowing in from the two cooling water inlets 104 and 703, flow distribution control of the water flow rate to the first heat exchange unit 12 and the water flow rate to the second heat exchange unit 62 is performed. It can be carried out.
  • the condensation performance of the refrigerant can be improved and the condensation capacity can be increased.
  • the water flow rate to the second heat exchange unit 62 it is possible to improve the supercooling performance of the refrigerant and increase the degree of supercooling of the refrigerant.
  • a dedicated radiator for cooling the cooling water heated in the second heat exchange unit 62 may be provided, and the cooling water cooled by the dedicated radiator may flow into the second heat exchange unit 62. According to this, the degree of supercooling of the refrigerant can be further increased.
  • a heat exchanger that cools the refrigerant by air exchange that is, heat exchange between the refrigerant and air, in which the condensing unit and the supercooling unit are arranged on the same heat radiation surface, the heat exchanger
  • the refrigerant pressure increases, so it is difficult to substantially control the degree of supercooling of the refrigerant.
  • the refrigerant is supercooled by performing flow rate distribution control of the water flow rate to the first heat exchange unit 12 and the water flow rate to the second heat exchange unit 62. It is possible to control the degree.
  • the method of switching the refrigerant flow path is not limited to this.
  • the refrigerant flow that causes the refrigerant that has flowed out from the first heat exchange unit 12 to flow to the outside in the gas-liquid separation unit 30 of the heat exchanger 10 and the refrigerant that has flowed out from the first heat exchange unit 12 to the second heat exchange You may provide the valve

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  • Physics & Mathematics (AREA)
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Abstract

This stacked heat exchanger is provided with a first heat exchanger unit (12) that exchanges heat between cooling water and a refrigerant. The first heat exchanger unit (12) includes: a plurality of first plate-shaped members (11) that are stacked together and joined; and a plurality of first refrigerant flow paths (121) and a plurality of cooling water flow paths (122) disposed between the plurality of first plate-shaped members (11). The plurality of first refrigerant flow paths (121) and the plurality of cooling water flow paths (122) are aligned in the direction of stacking of the plurality of first plate-shaped members (11). The stacked heat exchanger is further provided with a gas-liquid separation unit (30) that has a first top plate (18) disposed at the outermost side in the direction of stacking of the plurality of first plate-shaped members (11), a second top plate (19) joined to the first top plate (18), and a space between the first top plate (18) and second top plate (19), said gas-liquid separation unit separating the gas and liquid of the refrigerant flowing therewithin and storing the surplus refrigerant in a refrigeration cycle. As a result, the stacked heat exchanger provided with the gas-liquid separation unit that separates the gas and liquid of the refrigerant has greater body compactness and less installation dead space.

Description

積層型熱交換器Laminate heat exchanger 関連出願の相互参照Cross-reference of related applications
　本出願は、当該開示内容が参照によって本出願に組み込まれた、２０１４年５月２３日に出願された日本特許出願２０１４－１０７１１７および、２０１４年１０月３０日に出願された日本特許出願２０１４－２２１４９７を基にしている。 This application includes Japanese Patent Application No. 2014-107117 filed on May 23, 2014, and Japanese Patent Application No. 2014-2014 filed on October 30, 2014, the disclosures of which are incorporated herein by reference. Based on 221497.
　本開示は、冷凍サイクルの冷媒と熱媒体とを熱交換する積層型熱交換器に関する。 The present disclosure relates to a stacked heat exchanger that exchanges heat between a refrigerant and a heat medium in a refrigeration cycle.
　従来、複数の略平板状の伝熱プレートを間隔をおいて重ね合わせることにより、伝熱プレート間に冷媒流路と熱媒体流路とを交互に形成して、冷媒と熱媒体とを熱交換させる積層型熱交換器が知られている。このような積層型熱交換器において、当該熱交換器から流出する冷媒の気液を分離するとともに冷媒を蓄える円筒状のモジュレータを一体化させたものが、特許文献１に開示されている。 Conventionally, a plurality of substantially flat plate-shaped heat transfer plates are overlapped at an interval to alternately form a refrigerant channel and a heat medium channel between the heat transfer plates to exchange heat between the refrigerant and the heat medium. A laminated heat exchanger is known. In such a stacked heat exchanger, Patent Document 1 discloses an integrated cylindrical modulator that separates the gas-liquid refrigerant flowing out of the heat exchanger and stores the refrigerant.
　しかしながら、特許文献１に記載の積層型熱交換器では、略筐体形状の熱交換器の外側に円筒状のモジュレータを一体化させている。このため、体格が大型化するとともに、搭載時に何も配置されないスペース、いわゆるデットスペースが発生するおそれがある。さらに、このようなモジュレータ一体型の熱交換器に対し、モジュレータから流出した液相冷媒を過冷却する過冷却部を追加する場合、体格がますます大型化する場合がある。 However, in the stacked heat exchanger described in Patent Document 1, a cylindrical modulator is integrated on the outside of a substantially case-shaped heat exchanger. For this reason, the physique increases in size, and a space where nothing is arranged at the time of mounting, that is, a so-called dead space may occur. Furthermore, when a supercooling section for supercooling the liquid-phase refrigerant flowing out of the modulator is added to such a modulator-integrated heat exchanger, the size of the heat exchanger may become larger.
独国特許出願公開第１０２０１１０７８１３６号明細書German Patent Application Publication No. 102011078136
　本開示は上記点に鑑みて、冷媒の気液を分離する気液分離部を備える積層型熱交換器において、体格の小型化を図るとともに、搭載上のデッドスペースを小さくすることを目的とする。 In view of the above points, it is an object of the present disclosure to reduce the size of the physique and reduce the dead space on the mounting in a stacked heat exchanger including a gas-liquid separator that separates the gas and liquid of the refrigerant. .
　本開示の一態様によれば、積層型熱交換器は、冷凍サイクルの冷媒と第１熱媒体とを熱交換させる第１熱交換部を備える。第１熱交換部は、互いに積層されて接合された複数の第１板状部材と、複数の第１板状部材の間に設けられて、複数の第１板状部材の積層方向に並んでおり、冷媒が流れる複数の第１冷媒流路と、複数の第１板状部材の間に設けられて、複数の第１板状部材の積層方向に並んでおり、第１熱媒体が流れる複数の第１熱媒体流路と、を含む。積層型熱交換器は、複数の第１板状部材のうちの１つで積層方向の最外側に配置される第１端板に接合された第２端板と、第１端板と２端板との間に設けられた空間を有し、内部に流入した冷媒の気液を分離するとともに冷凍サイクル内の余剰冷媒を蓄える気液分離部と、をさらに備えている。 According to one aspect of the present disclosure, the stacked heat exchanger includes a first heat exchange unit that exchanges heat between the refrigerant of the refrigeration cycle and the first heat medium. The first heat exchange unit is provided between the plurality of first plate-like members stacked and joined to each other and the plurality of first plate-like members, and is arranged in the stacking direction of the plurality of first plate-like members. The plurality of first refrigerant flow paths through which the refrigerant flows and the plurality of first plate-like members are arranged in the stacking direction of the plurality of first plate-like members, and the plurality of the first heat medium flows therethrough. First heat medium flow path. The stacked heat exchanger includes a second end plate joined to a first end plate disposed at the outermost side in the stacking direction at one of a plurality of first plate-shaped members, a first end plate, and two ends. The apparatus further includes a gas-liquid separation unit that has a space provided between the plates and separates the gas-liquid of the refrigerant that has flowed into the plate and stores excess refrigerant in the refrigeration cycle.
　これによれば、第１端板に、当該第１端板との間に空間を形成するように第２端板を接合するとともに、その空間により気液分離部を構成した。これにより、第１熱交換部に対して板状の第２端板を追加するだけで、気液分離部を設けることができる。このため、積層型熱交換器の小型化を図るとともに、搭載上のデッドスペースを小さくすることが可能となる。 According to this, the second end plate was joined to the first end plate so as to form a space with the first end plate, and the gas-liquid separation part was configured by the space. Thereby, a gas-liquid separation part can be provided only by adding a plate-shaped second end plate to the first heat exchange part. For this reason, it is possible to reduce the size of the stacked heat exchanger and reduce the dead space on mounting.
本開示の第１実施形態に係る熱交換器を示す概略図である。It is a schematic diagram showing a heat exchanger concerning a 1st embodiment of this indication. 第１実施形態における第１天井板を第２天井板から見た図である。It is the figure which looked at the 1st ceiling board in a 1st embodiment from the 2nd ceiling board. 図１のＩＩＩ矢視図である。It is a III arrow directional view of FIG. 図３のＩＶ－ＩＶ断面図である。FIG. 4 is a sectional view taken along line IV-IV in FIG. 3. 第１実施形態に係る熱交換器の一部を示す断面図である。It is sectional drawing which shows a part of heat exchanger which concerns on 1st Embodiment. 第１実施形態におけるオフセットフィンを示す斜視図であるIt is a perspective view which shows the offset fin in 1st Embodiment. 本開示の第２実施形態に係る熱交換器を示す側面図である。It is a side view showing a heat exchanger concerning a 2nd embodiment of this indication. 本開示の第３実施形態に係る熱交換器を示す概略図である。It is a schematic diagram showing a heat exchanger concerning a 3rd embodiment of this indication. 図８のＩＸ矢視図である。It is IX arrow line view of FIG. 図９のＸ－Ｘ断面図である。FIG. 10 is a sectional view taken along line XX in FIG. 9. 本開示の第４実施形態に係る熱交換器を示す概略図である。It is a schematic diagram showing a heat exchanger concerning a 4th embodiment of this indication. 本開示の第５実施形態に係る熱交換器を示す概略図である。It is the schematic which shows the heat exchanger which concerns on 5th Embodiment of this indication. 本開示の第６実施形態に係る熱交換器の凝縮モードにおける冷媒の流れを示す概略図である。It is the schematic which shows the flow of the refrigerant | coolant in the condensation mode of the heat exchanger which concerns on 6th Embodiment of this indication. 図１３のＸＩＶ矢視図である。It is a XIV arrow line view of FIG. 図１４のＸＶ－ＸＶ断面図である。It is XV-XV sectional drawing of FIG. 図１４のＸＶＩ－ＸＶＩ断面図である。It is XVI-XVI sectional drawing of FIG. 図１４のＸＶＩＩ－ＸＶＩＩ断面図である。It is XVII-XVII sectional drawing of FIG. 第６実施形態に係る熱交換器の蒸発モードにおける冷媒の流れを示す概略図である。It is the schematic which shows the flow of the refrigerant | coolant in the evaporation mode of the heat exchanger which concerns on 6th Embodiment. 本開示の第７実施形態に係る熱交換器を示す概略図である。It is a schematic diagram showing a heat exchanger concerning a 7th embodiment of this indication. 図２０のＸＸ矢視図である。It is XX arrow line view of FIG. 図２０のＸＸＩ－ＸＸＩ断面図である。It is XXI-XXI sectional drawing of FIG.
　以下に、図面を参照しながら本開示を実施するための複数の形態を説明する。各形態において先行する形態で説明した事項に対応する部分には同一の参照符号を付して重複する説明を省略する場合がある。各形態において構成の一部のみを説明している場合は、構成の他の部分については先行して説明した他の形態を適用することができる。各実施形態で具体的に組合せが可能であることを明示している部分同士の組合せばかりではなく、特に組合せに支障が生じなければ、明示してなくとも実施形態同士を部分的に組み合せることも可能である。
（第１実施形態）
　本開示の第１実施形態について図１～図６に基づいて説明する。図１に示す熱交換器１０は、車両用空調装置の冷凍サイクルを構成している。熱交換器１０は、冷凍サイクルの高圧側冷媒と冷却水とを熱交換して高圧側冷媒を凝縮させる凝縮器である。なお、本実施形態の冷却水が、本開示の第１熱媒体に相当している。 Hereinafter, a plurality of modes for carrying out the present disclosure will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not explicitly stated unless there is a problem with the combination. Is also possible.
(First embodiment)
A first embodiment of the present disclosure will be described with reference to FIGS. A heat exchanger 10 shown in FIG. 1 constitutes a refrigeration cycle of a vehicle air conditioner. The heat exchanger 10 is a condenser that condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle. Note that the cooling water of the present embodiment corresponds to the first heat medium of the present disclosure.
　冷却水としては、例えば、少なくともエチレングリコール、ジメチルポリシロキサンもしくはナノ流体を含む液体、または不凍液体等を用いることができる。本実施形態では、冷却水として、エチレングリコール系の不凍液（ＬＬＣ）が用いられている。 As the cooling water, for example, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid can be used. In this embodiment, ethylene glycol antifreeze (LLC) is used as the cooling water.
　熱交換器１０は、多数の第１板状部材１１（以下、単に板状部材１１と略称する）が積層されて接合されることによって一体的に形成されている。以下では、板状部材１１の積層方向（図１の例では上下方向）を板積層方向と言い、板積層方向の一端側（図１の例では上端側）を板積層方向一端側と言い、板積層方向の他端側（図１の例では下端側）を板積層方向他端側と言う。 The heat exchanger 10 is integrally formed by laminating and joining a large number of first plate members 11 (hereinafter simply referred to as plate members 11). Hereinafter, the laminating direction of the plate-like member 11 (vertical direction in the example of FIG. 1) is referred to as the plate laminating direction, and one end side in the plate laminating direction (the upper end side in the example of FIG. 1) is referred to as one end side of the plate laminating direction. The other end side in the plate stacking direction (the lower end side in the example of FIG. 1) is referred to as the other end side in the plate stacking direction.
　板状部材１１は細長の略矩形状の板材であり、具体的材質としては、例えば、アルミニウム芯材にろう材をクラッドしたクラッド材が用いられる。 The plate-like member 11 is an elongated, substantially rectangular plate material. As a specific material, for example, a clad material in which a brazing material is clad on an aluminum core material is used.
　略矩形状の板状部材１１の外周縁部には、略板積層方向（換言すれば、板状部材１１の板面と略直交する方向）に突出する張出部１１１が形成されている。多数の板状部材１１は、互いに積層された状態で張出部１１１同士がろう付けにより接合されている。多数の板状部材１１は、張出部１１１の突出先端が互いに同じ側（図１の例では略下方側）を向くように配置されている。 On the outer peripheral edge of the substantially rectangular plate-like member 11, an overhanging portion 111 is formed that protrudes in a substantially plate lamination direction (in other words, a direction substantially orthogonal to the plate surface of the plate-like member 11). Many plate-like members 11 are joined to each other by brazing in a state where the plate-like members 11 are laminated with each other. The many plate-like members 11 are arranged so that the protruding tips of the overhanging portions 111 face the same side (substantially downward in the example of FIG. 1).
　多数の板状部材１１は、第１熱交換部１２（以下、単に熱交換部１２と略称する）、冷媒用第１タンク空間１３、冷媒用第２タンク空間１４、冷却水用第１タンク空間１５および冷却水用第２タンク空間１６を形成している。 A large number of plate-like members 11 include a first heat exchange section 12 (hereinafter simply referred to as a heat exchange section 12), a first tank space for refrigerant 13, a second tank space for refrigerant 14, and a first tank space for cooling water. 15 and the second tank space 16 for cooling water are formed.
　熱交換部１２は、複数の第１冷媒流路１２１（以下、単に冷媒流路１２１と略称する）および複数の第１冷却水流路１２２（以下、単に冷却水流路１２２と略称する）で構成されている。なお、本実施形態の冷却水流路１２２が、本開示の第１熱媒体流路に相当している。 The heat exchange unit 12 includes a plurality of first refrigerant flow paths 121 (hereinafter simply referred to as refrigerant flow paths 121) and a plurality of first cooling water flow paths 122 (hereinafter simply referred to as cooling water flow paths 122). ing. Note that the cooling water passage 122 of the present embodiment corresponds to the first heat medium passage of the present disclosure.
　複数の冷媒流路１２１および複数の冷却水流路１２２は、多数枚の板状部材１１同士の間に形成されている。冷媒流路１２１および冷却水流路１２２の長手方向は、板状部材１１の長手方向と一致している。 The plurality of refrigerant channels 121 and the plurality of cooling water channels 122 are formed between a large number of plate-like members 11. The longitudinal directions of the refrigerant flow path 121 and the cooling water flow path 122 coincide with the longitudinal direction of the plate-like member 11.
　冷媒流路１２１および冷却水流路１２２は板積層方向に１本ずつ交互に積層配置（並列配置）されている。板状部材１１は、冷媒流路１２１と冷却水流路１２２とを仕切る隔壁の役割を果たしている。冷媒流路１２１を流れる冷媒と、冷却水流路１２２を流れる冷却水との熱交換は、板状部材１１を介して行われる。 The refrigerant channel 121 and the cooling water channel 122 are alternately stacked one by one in the plate stacking direction (in parallel). The plate-like member 11 serves as a partition wall that partitions the coolant channel 121 and the cooling water channel 122. Heat exchange between the refrigerant flowing through the refrigerant flow path 121 and the cooling water flowing through the cooling water flow path 122 is performed via the plate-like member 11.
　冷媒用第１タンク空間１３および冷却水用第１タンク空間１５は、熱交換部１２に対して、冷媒流路１２１および冷却水流路１２２の一方側（図１の例では右方側）に配置されている。冷媒用第２タンク空間１４および冷却水用第２タンク空間１６は、熱交換部１２に対して、冷媒流路１２１および冷却水流路１２２の他方側（図１の例では左方側）に配置されている。 The first tank space for refrigerant 13 and the first tank space for cooling water 15 are arranged on one side (right side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12. Has been. The second tank space for refrigerant 14 and the second tank space for cooling water 16 are arranged on the other side (left side in the example of FIG. 1) of the refrigerant flow path 121 and the cooling water flow path 122 with respect to the heat exchange unit 12. Has been.
　冷媒用第１タンク空間１３および冷媒用第２タンク空間１４は、複数の冷媒流路１２１に対して冷媒の分配および集合を行う。冷却水用第１タンク空間１５および冷却水用第２タンク空間１６は、複数の冷却水流路１２２に対して冷却水の分配および集合を行う。 The first tank space for refrigerant 13 and the second tank space for refrigerant 14 distribute and collect the refrigerant with respect to the plurality of refrigerant flow paths 121. The first tank space for cooling water 15 and the second tank space for cooling water 16 distribute and collect the cooling water to the plurality of cooling water flow paths 122.
　冷媒用第１タンク空間１３、冷媒用第２タンク空間１４、冷却水用第１タンク空間１５および冷却水用第２タンク空間１６は、板状部材１１の四隅に形成された連通孔によって構成されている。本実施形態では、略矩形状の板状部材１１の四隅のうち対角線上にある２つの隅部に、冷媒用第１タンク空間１３および冷媒用第２タンク空間１４が設けられており、残りの２つの隅部に冷却水用第１タンク空間１５および冷却水用第２タンク空間１６が設けられている。 The refrigerant first tank space 13, the refrigerant second tank space 14, the cooling water first tank space 15, and the cooling water second tank space 16 are configured by communication holes formed at the four corners of the plate-like member 11. ing. In the present embodiment, the first tank space 13 for refrigerant and the second tank space 14 for refrigerant are provided at two corners on the diagonal line among the four corners of the substantially rectangular plate-like member 11, and the remaining A cooling water first tank space 15 and a cooling water second tank space 16 are provided at two corners.
　熱交換部１２を構成する多数枚の板状部材１１のうち最も板積層方向一端側に位置する最端板状部材１７には、第１ジョイント２１および第１冷却水パイプ２２が取り付けられている。第１ジョイント２１は、冷媒配管を接合するための部材であり、熱交換器１０の冷媒入口１０１を形成している。第１冷却水パイプ２２は、熱交換器１０の冷却水出口１０２を形成している。 The first joint 21 and the first cooling water pipe 22 are attached to the outermost plate-like member 17 located closest to the one end side in the plate stacking direction among the many plate-like members 11 constituting the heat exchange unit 12. . The first joint 21 is a member for joining refrigerant pipes, and forms the refrigerant inlet 101 of the heat exchanger 10. The first cooling water pipe 22 forms the cooling water outlet 102 of the heat exchanger 10.
　本実施形態では、第１ジョイント２１は、最端板状部材１７の長手方向における一端側（図１の例では右方側）に設けられている。また、第１冷却水パイプ２２は、最端板状部材１７の長手方向における他端側（図１の例では左方側）に設けられている。 In the present embodiment, the first joint 21 is provided on one end side in the longitudinal direction of the outermost plate member 17 (right side in the example of FIG. 1). The first cooling water pipe 22 is provided on the other end side in the longitudinal direction of the outermost plate member 17 (left side in the example of FIG. 1).
　熱交換部１２を構成する多数枚の板状部材１１のうち、最も板積層方向他端側、すなわち板積層方向の最外側に位置する第１天井板１８（第１端板）は、他の板状部材１１と比較して、張出部１１１の板積層方向の長さが長くなっている。第１天井板１８には、当該第１天井板１８との間に空間を形成するように、板状の第２天井板１９（第２端板）がろう付けにより接合されている。この空間は、内部に流入した冷媒の気液を分離するとともに冷凍サイクル内の余剰冷媒を蓄える気液分離部３０の一例として用いられても良い。 Among the many plate-like members 11 constituting the heat exchange unit 12, the first ceiling plate 18 (first end plate) located on the other end side in the plate stacking direction, that is, the outermost side in the plate stacking direction, Compared with the plate-like member 11, the length of the overhanging portion 111 in the plate stacking direction is longer. A plate-like second ceiling plate 19 (second end plate) is joined to the first ceiling plate 18 by brazing so as to form a space between the first ceiling plate 18 and the first ceiling plate 18. This space may be used as an example of the gas-liquid separation unit 30 that separates the gas-liquid of the refrigerant flowing into the interior and stores excess refrigerant in the refrigeration cycle.
　図２および図４に示すように、第１天井板１８における重力方向下方部には、熱交換部１２の冷媒流路１２１を流れる冷媒を気液分離部３０に流入させる冷媒流入部１８１が設けられている。冷媒流入部１８１は、第１天井板１８に設けられた貫通孔である。より詳細には、冷媒流入部１８１は、気液分離部３０に蓄えられている液相冷媒の液面（図２参照）よりも、重力方向下方側に位置している。また、冷媒流入部１８１は、第１天井板１８における重力方向下半分の領域に設けられてもよい。 As shown in FIGS. 2 and 4, a refrigerant inflow portion 181 for allowing the refrigerant flowing through the refrigerant flow path 121 of the heat exchange unit 12 to flow into the gas-liquid separation unit 30 is provided in the lower portion of the first ceiling plate 18 in the gravity direction. It has been. The refrigerant inflow portion 181 is a through hole provided in the first ceiling plate 18. More specifically, the refrigerant inflow portion 181 is located on the lower side in the gravitational direction than the liquid surface of the liquid-phase refrigerant stored in the gas-liquid separator 30 (see FIG. 2). In addition, the refrigerant inflow portion 181 may be provided in the lower half region of the first ceiling plate 18 in the direction of gravity.
　第１天井板１８における重力方向上方側には、後述する第１内部冷却水パイプ４１が挿入される第１貫通孔１８２が形成されている。より詳細には、第１貫通孔１８２は、気液分離部３０に蓄えられている液相冷媒の液面よりも、重力方向上方側に配置されている。本実施形態では、冷媒流入部１８１および第１貫通孔１８２は、ともに、第１天井板１８の長手方向における一端側（図２の例では右方側）に配置されている。 A first through hole 182 into which a first internal cooling water pipe 41 to be described later is inserted is formed on the upper side in the gravity direction of the first ceiling plate 18. More specifically, the first through hole 182 is disposed on the upper side in the gravitational direction than the liquid level of the liquid refrigerant stored in the gas-liquid separator 30. In the present embodiment, both the refrigerant inflow portion 181 and the first through hole 182 are arranged on one end side in the longitudinal direction of the first ceiling plate 18 (right side in the example of FIG. 2).
　図３および図４に示すように、第２天井板１９における重力方向下方部には、気液分離部３０から液相冷媒を外部へ流出させる冷媒流出部１９１が設けられている。冷媒流出部１９１は、第２天井板１９に設けられた貫通孔である。より詳細には、冷媒流出部１９１は、気液分離部３０に蓄えられている液相冷媒の液面よりも、重力方向下方側に位置している。また、冷媒流出部１９１は、第２天井板１９における重力方向下半分の領域に設けられてもよい。 As shown in FIGS. 3 and 4, a refrigerant outflow portion 191 for allowing the liquid-phase refrigerant to flow out from the gas-liquid separation unit 30 to the outside is provided at a lower portion in the gravity direction of the second ceiling plate 19. The refrigerant outflow portion 191 is a through hole provided in the second ceiling plate 19. More specifically, the refrigerant outflow portion 191 is located on the lower side in the gravity direction than the liquid surface of the liquid-phase refrigerant stored in the gas-liquid separation portion 30. Further, the refrigerant outflow portion 191 may be provided in the lower half region of the second ceiling plate 19 in the direction of gravity.
　第２天井板１９における重力方向上方側には、後述する第１内部冷却水パイプ４１が挿入される第２貫通孔１９２が形成されている。第２貫通孔１９２の内周面と第１内部冷却水パイプ４１の外表面とは、ろう付けにより接合されている。 A second through hole 192 into which a first internal cooling water pipe 41 to be described later is inserted is formed on the upper side in the gravity direction of the second ceiling plate 19. The inner peripheral surface of the second through hole 192 and the outer surface of the first internal cooling water pipe 41 are joined by brazing.
　より詳細には、第２貫通孔１９２は、気液分離部３０に蓄えられている液相冷媒の液面よりも、重力方向上方側に配置されている。本実施形態では、第２貫通孔１９２は、第２天井板１９の長手方向における一端側（図３の例では右方側）に配置されている。一方、冷媒流出部１９１は、第２天井板１９の長手方向における他端側（図２の例では左方側）に配置されている。 More specifically, the second through hole 192 is disposed on the upper side in the gravity direction with respect to the liquid level of the liquid-phase refrigerant stored in the gas-liquid separator 30. In the present embodiment, the second through hole 192 is disposed on one end side in the longitudinal direction of the second ceiling plate 19 (right side in the example of FIG. 3). On the other hand, the refrigerant outflow portion 191 is disposed on the other end side in the longitudinal direction of the second ceiling plate 19 (left side in the example of FIG. 2).
　本実施形態では、図３に示すように、第２天井板１９における重力方向下方側には、気液分離部３０の内圧の上昇により第２天井板１９にかかる応力を吸収するための突起１９３が設けられている。この突起１９３を設けることにより、気液分離部３０の剛性を向上させることができる。また、気液分離部３０の重力方向下方側には、液相冷媒中の水分を除去する乾燥剤３１が設けられている。 In the present embodiment, as shown in FIG. 3, a protrusion 193 for absorbing stress applied to the second ceiling plate 19 due to an increase in internal pressure of the gas-liquid separation unit 30 on the lower side in the gravity direction of the second ceiling plate 19. Is provided. By providing the projection 193, the rigidity of the gas-liquid separation unit 30 can be improved. In addition, a desiccant 31 for removing moisture in the liquid-phase refrigerant is provided below the gas-liquid separator 30 in the gravity direction.
　図１および図４に示すように、第２天井板１９には、第２ジョイント２３および第２冷却水パイプ２４が取り付けられている。第２ジョイント２３は、冷媒配管を接合するための部材であり、熱交換器１０の冷媒出口１０３を形成している。第２冷却水パイプ２４は、熱交換器１０の冷却水入口１０４を形成している。 As shown in FIGS. 1 and 4, a second joint 23 and a second cooling water pipe 24 are attached to the second ceiling plate 19. The second joint 23 is a member for joining refrigerant pipes and forms the refrigerant outlet 103 of the heat exchanger 10. The second cooling water pipe 24 forms the cooling water inlet 104 of the heat exchanger 10.
　冷媒入口１０１は、冷媒用第１タンク空間１３に連通している。冷媒用第１タンク空間１３は、冷媒流入部１８１を介して、気液分離部３０に連通している。気液分離部３０は、冷媒流出部１９１を介して、冷媒出口１０３に連通している。 The refrigerant inlet 101 communicates with the first tank space 13 for refrigerant. The refrigerant first tank space 13 communicates with the gas-liquid separation unit 30 via the refrigerant inflow portion 181. The gas-liquid separator 30 communicates with the refrigerant outlet 103 via the refrigerant outlet 191.
　図４に示すように、気液分離部３０の内部には、冷却水が流通するとともに、冷却水入口１０４と冷却水用第１タンク空間１５とを連通させる第１内部冷却水通路４０が設けられている。具体的には、気液分離部３０の内部には、第２冷却水パイプ２４と冷却水用第１タンク空間１５とを接続する第１内部冷却水パイプ４１が設けられている。この第１内部冷却水パイプ４１により、第１内部冷却水通路４０が構成されている。 As shown in FIG. 4, a first internal cooling water passage 40 is provided in the gas-liquid separation unit 30 to allow the cooling water to flow and to connect the cooling water inlet 104 and the first cooling water tank space 15. It has been. Specifically, a first internal cooling water pipe 41 that connects the second cooling water pipe 24 and the first tank space 15 for cooling water is provided inside the gas-liquid separator 30. The first internal cooling water passage 40 is configured by the first internal cooling water pipe 41.
　したがって、図１および図４に示すように、冷却水入口１０４は、第１内部冷却水通路４０を介して、冷却水用第１タンク空間１５に連通している。また、冷却水出口１０２は、冷却水用第２タンク空間１６に連通している。 Therefore, as shown in FIGS. 1 and 4, the cooling water inlet 104 communicates with the first tank space 15 for cooling water via the first internal cooling water passage 40. The cooling water outlet 102 communicates with the cooling water second tank space 16.
　図５に示すように、本実施形態では、熱交換部１２を構成する多数枚の板状部材１１は、当該板状部材１１の四隅に板積層方向の一端側または他端側に向かって突出する略円筒状の突出部１１ｆを有している。この突出部１１ｆにより、冷媒用第１タンク空間１３、冷媒用第２タンク空間１４、冷却水用第１タンク空間１５および冷却水用第２タンク空間１６が、それぞれ形成されている。 As shown in FIG. 5, in the present embodiment, a large number of plate-like members 11 constituting the heat exchanging portion 12 protrude toward one end side or the other end side in the plate stacking direction at the four corners of the plate-like member 11. It has a substantially cylindrical protrusion 11f. A first tank space 13 for refrigerant, a second tank space 14 for refrigerant, a first tank space 15 for cooling water, and a second tank space 16 for cooling water are formed by the protrusion 11f.
　熱交換部１２を構成する多数枚の板状部材１１のうち、板積層方向の略中央部に位置する中央板状部材１１Ａは、冷媒用第１タンク空間１３を構成する突出部１１ｆを閉塞する閉塞部１１ｇを有している。これにより、冷媒用第１タンク空間１３は板積層方向に２つの空間に仕切られている。なお、閉塞部１１ｇは、突出部１１ｆ、すなわち中央板状部材１１Ａと一体に形成されている。 Of the many plate-like members 11 constituting the heat exchanging portion 12, the central plate-like member 11 </ b> A located at a substantially central portion in the plate stacking direction closes the protruding portion 11 f constituting the first tank space 13 for refrigerant. It has a blocking part 11g. Thereby, the first tank space 13 for refrigerant is partitioned into two spaces in the plate stacking direction. The closing portion 11g is formed integrally with the protruding portion 11f, that is, the central plate member 11A.
　したがって、図１の実線矢印に示すように、冷媒入口１０１から流入した冷媒は、板積層方向一端側の冷媒流路１２１を冷媒用第１タンク空間１３から冷媒用第２タンク空間１４へ向かって流れた後、板積層方向他端側の冷媒流路１２１を冷媒用第２タンク空間１４から冷媒用第１タンク空間１３へ向かって流れて、冷媒流入部１８１から気液分離部３０へ流入する。すなわち、熱交換器１０は、冷媒の流れが１回Ｕターンするように構成されている。気液分離部３０へ流入した冷媒は気液分離され、液相冷媒が冷媒出口１０３から外部へ流出する。 Therefore, as indicated by the solid line arrow in FIG. 1, the refrigerant that has flowed from the refrigerant inlet 101 moves from the first tank space 13 for refrigerant to the second tank space 14 for refrigerant through the refrigerant flow path 121 on one end side in the plate stacking direction. After flowing, the refrigerant flows in the refrigerant flow path 121 on the other end side in the plate stacking direction from the refrigerant second tank space 14 toward the refrigerant first tank space 13, and flows from the refrigerant inflow portion 181 into the gas-liquid separation portion 30. . That is, the heat exchanger 10 is configured such that the refrigerant flow makes a U-turn once. The refrigerant flowing into the gas-liquid separation unit 30 is gas-liquid separated, and the liquid-phase refrigerant flows out from the refrigerant outlet 103 to the outside.
　また、冷却水入口１０４からから流入した冷却水は、図１の一点鎖線矢印に示すように、冷却水流路１２２を冷却水用第１タンク空間１５から冷却水用第２タンク空間１６へ向かって流れて、冷却水出口１０２から外部へ流出する。 Further, the cooling water flowing in from the cooling water inlet 104 flows through the cooling water flow path 122 from the cooling water first tank space 15 toward the cooling water second tank space 16 as shown by a one-dot chain arrow in FIG. And flows out from the cooling water outlet 102 to the outside.
　ところで、板状部材１１同士の間には、図６に示すオフセットフィン５０が配置されている。オフセットフィン５０は、板状部材１１同士の間に介在し、冷媒と冷却水との間での熱交換を促進させるインナーフィンである。 Incidentally, offset fins 50 shown in FIG. 6 are arranged between the plate-like members 11. The offset fins 50 are inner fins that are interposed between the plate-like members 11 and promote heat exchange between the refrigerant and the cooling water.
　オフセットフィン５０は、部分的に切り起こされた切り起こし部５０ａが形成された板状の部材である。切り起こし部５０ａは、冷媒および冷却水の流れ方向と平行な方向Ｆ１（すなわち、板状部材１１の長手方向）に多数個形成されている。 The offset fin 50 is a plate-like member in which a cut and raised portion 50a that is partially cut and raised is formed. A large number of the cut-and-raised portions 50a are formed in the direction F1 (that is, the longitudinal direction of the plate-like member 11) parallel to the flow direction of the refrigerant and the cooling water.
　冷媒および冷却水の流れ方向と平行な方向Ｆ１に隣り合う切り起こし部５０ａ同士は、互いにオフセットされている。図６の例では、多数個の切り起こし部５０ａは、冷媒および冷却水の流れ方向と平行な方向Ｆ１に千鳥配置されている。オフセットフィン５０は、隣り合う両方の板状部材１１にろう付けにより接合されている。 The cut-and-raised portions 50a adjacent to each other in the direction F1 parallel to the flow direction of the refrigerant and the cooling water are offset from each other. In the example of FIG. 6, the large number of cut-and-raised portions 50a are staggered in a direction F1 parallel to the flow direction of the refrigerant and the cooling water. The offset fins 50 are joined to both adjacent plate-like members 11 by brazing.
　以上説明したように、本実施形態の熱交換器１０では、第１天井板１８に、当該第１天井板１８との間に空間を形成するように第２天井板１９を接合するとともに、その空間により気液分離部３０を構成している。これにより、第１熱交換部１２に対して板状の第２天井板１９を追加するだけで、気液分離部３０を構成することができる。このため、気液分離部３０が一体化された熱交換器１０の小型化を図るとともに、搭載上のデッドスペースを小さくすることが可能となる。 As described above, in the heat exchanger 10 of the present embodiment, the second ceiling plate 19 is joined to the first ceiling plate 18 so as to form a space between the first ceiling plate 18 and the first ceiling plate 18. The gas-liquid separation unit 30 is configured by the space. Thereby, the gas-liquid separation part 30 can be comprised only by adding the plate-shaped 2nd ceiling board 19 with respect to the 1st heat exchange part 12. FIG. For this reason, it is possible to reduce the size of the heat exchanger 10 in which the gas-liquid separation unit 30 is integrated, and to reduce the dead space on mounting.
　また、本実施形態では、気液分離部３０の冷媒流出部１９１は、気液分離部３０に蓄えられている液相冷媒の液面よりも重力方向下方側に配置されている。このため、冷媒流出部１９１から液相の冷媒を確実に流出させることができる。
（第２実施形態）
　次に、本開示の第２実施形態について図７に基づいて説明する。本第２実施形態は、上記第１実施形態と比較して、熱交換器１０の搭載方向が異なるものである。 Moreover, in this embodiment, the refrigerant | coolant outflow part 191 of the gas-liquid separation part 30 is arrange | positioned rather than the liquid level of the liquid-phase refrigerant | coolant stored in the gas-liquid separation part 30 below the gravity direction. For this reason, the liquid-phase refrigerant can be reliably caused to flow out from the refrigerant outflow portion 191.
(Second Embodiment)
Next, a second embodiment of the present disclosure will be described based on FIG. The second embodiment differs from the first embodiment in the mounting direction of the heat exchanger 10.
　図７に示すように、本実施形態の熱交換器１０は、板状部材１１の長手方向、すなわち第１天井板１８および第２天井板１９の長手方向が、重力方向と一致するように搭載されている。このとき、冷媒流入部１８１および冷媒流出部１９１は、気液分離部３０に蓄えられている液相冷媒の液面（図７参照）よりも重力方向下方側に配置されている。 As shown in FIG. 7, the heat exchanger 10 of the present embodiment is mounted so that the longitudinal direction of the plate-like member 11, that is, the longitudinal directions of the first ceiling plate 18 and the second ceiling plate 19 coincide with the direction of gravity. Has been. At this time, the refrigerant inflow portion 181 and the refrigerant outflow portion 191 are disposed on the lower side in the gravitational direction than the liquid level of the liquid-phase refrigerant stored in the gas-liquid separation portion 30 (see FIG. 7).
　気液分離部３０における冷媒流入部１８１および冷媒流出部１９１との間には、気液分離部３０内の重力方向下方側の空間を冷媒流入部１８１に連通する空間と冷媒流出部１９１に連通する空間とに区画するバッフル板３２が設けられている。バッフル板３２には、複数の貫通孔（図示せず）が形成されており、冷媒流入部１８１に連通する空間と冷媒流出部１９１に連通する空間とが連通している。 Between the refrigerant inflow part 181 and the refrigerant outflow part 191 in the gas-liquid separation part 30, the space below the gravity direction in the gas-liquid separation part 30 communicates with a space communicating with the refrigerant inflow part 181 and the refrigerant outflow part 191. A baffle plate 32 is provided to divide the space into the space. A plurality of through holes (not shown) are formed in the baffle plate 32, and a space communicating with the refrigerant inflow portion 181 and a space communicating with the refrigerant outflow portion 191 communicate with each other.
　バッフル板３２は、気液分離部３０の重力方向下方側端部から上方側に向かって、重力方向と略平行に延びている。本実施形態では、バッフル板３２の重力方向上方側端部は、気液分離部３０に蓄えられている液相冷媒の液面よりも下方側に配置されている。 The baffle plate 32 extends substantially parallel to the gravity direction from the lower end in the gravity direction of the gas-liquid separator 30 toward the upper side. In the present embodiment, the upper end of the baffle plate 32 in the direction of gravity is disposed below the liquid level of the liquid-phase refrigerant stored in the gas-liquid separator 30.
　以上説明したように、本実施形態では、板状部材１１の長手方向が重力方向と一致するように熱交換器１０を搭載した場合において、気液分離部３０の冷媒流出部１９１を、気液分離部３０に蓄えられている液相冷媒の液面よりも重力方向下方側に配置している。これにより、冷媒流出部１９１から液相の冷媒を確実に流出させることができる。 As described above, in the present embodiment, when the heat exchanger 10 is mounted so that the longitudinal direction of the plate-like member 11 coincides with the direction of gravity, the refrigerant outflow portion 191 of the gas-liquid separation unit 30 is It arrange | positions in the gravity direction lower side rather than the liquid level of the liquid phase refrigerant | coolant stored in the separation part 30. As a result, the liquid-phase refrigerant can reliably flow out from the refrigerant outflow portion 191.
　また、気液分離部３０における冷媒流入部１８１および冷媒流出部１９１との間にバッフル板３２を設けることで、気液分離性を向上させることができる。さらに、バッフル板３２により、気液分離部３０の剛性を向上させることができる。
（第３実施形態）
　次に、本開示の第３実施形態について図８～図１０に基づいて説明する。本第３実施形態は、上記第１実施形態と比較して、熱交換器１０に第２熱交換部６２を設けた点が異なるものである。 Further, by providing the baffle plate 32 between the refrigerant inflow part 181 and the refrigerant outflow part 191 in the gas-liquid separation part 30, gas-liquid separation can be improved. Furthermore, the baffle plate 32 can improve the rigidity of the gas-liquid separator 30.
(Third embodiment)
Next, a third embodiment of the present disclosure will be described with reference to FIGS. The third embodiment is different from the first embodiment in that the second heat exchange unit 62 is provided in the heat exchanger 10.
　図８に示すように、本実施形態の第２天井板１９には、気液分離部３０から流出した液相冷媒と冷凍サイクルの低圧冷媒とを熱交換させて液相冷媒を過冷却する過冷却部として機能する第２熱交換部６２が接続されている。なお、本実施形態の低圧冷媒が、本開示の第２熱媒体に相当している。 As shown in FIG. 8, in the second ceiling plate 19 of the present embodiment, the liquid phase refrigerant that has flowed out of the gas-liquid separator 30 and the low-pressure refrigerant in the refrigeration cycle are heat-exchanged to supercool the liquid phase refrigerant. A second heat exchange unit 62 that functions as a cooling unit is connected. Note that the low-pressure refrigerant of the present embodiment corresponds to the second heat medium of the present disclosure.
　第２熱交換部６２は、複数の第２板状部材６１を互いに積層されて接合されることによって一体的に形成されている。具体的には、多数の第２板状部材６１は、第２熱交換部６２、液相冷媒用第１タンク空間６３、液相冷媒用第２タンク空間６４、低圧冷媒用第１タンク空間６５および低圧冷媒用第２タンク空間６６を形成している。 The second heat exchange part 62 is integrally formed by laminating and joining a plurality of second plate-like members 61 to each other. Specifically, the multiple second plate-like members 61 include a second heat exchange section 62, a liquid tank first tank space 63, a liquid refrigerant second tank space 64, and a low pressure refrigerant first tank space 65. The second tank space 66 for low-pressure refrigerant is formed.
　第２熱交換部６２は、液相冷媒が流通する複数の第２冷媒流路６２１、および、低圧冷媒が流通する複数の低圧冷媒流路６２２で構成されている。なお、本実施形態の低圧冷媒流路６２２が、本開示の第２熱媒体流路に相当している。 The second heat exchanging unit 62 includes a plurality of second refrigerant flow paths 621 through which liquid phase refrigerant flows and a plurality of low pressure refrigerant flow paths 622 through which low-pressure refrigerant flows. Note that the low-pressure refrigerant channel 622 of the present embodiment corresponds to the second heat medium channel of the present disclosure.
　複数の第２冷媒流路６２１および複数の低圧冷媒流路６２２は、多数枚の第２板状部材６１同士の間に形成されている。第２冷媒流路６２１および低圧冷媒流路６２２の長手方向は、第２板状部材６１の長手方向と一致している。 The plurality of second refrigerant channels 621 and the plurality of low-pressure refrigerant channels 622 are formed between a large number of second plate-like members 61. The longitudinal directions of the second refrigerant channel 621 and the low-pressure refrigerant channel 622 coincide with the longitudinal direction of the second plate member 61.
　第２板状部材６１における液相冷媒の流れ方向の長さは、第１板状部材１１における冷媒の流れ方向の長さよりも短くなっている。すなわち、第２板状部材６１の長手方向の長さは、第１板状部材１１の長手方向の長さよりも短くなっている。また、第２板状部材６１の積層方向は、第１板状部材１１の積層方向と平行になっている。 The length in the flow direction of the liquid phase refrigerant in the second plate member 61 is shorter than the length in the flow direction of the refrigerant in the first plate member 11. That is, the length of the second plate member 61 in the longitudinal direction is shorter than the length of the first plate member 11 in the longitudinal direction. Further, the stacking direction of the second plate-like member 61 is parallel to the stacking direction of the first plate-like member 11.
　第２冷媒流路６２１および低圧冷媒流路６２２は板積層方向に１本ずつ交互に積層配置（並列配置）されている。第２板状部材６１は、第２冷媒流路６２１と低圧冷媒流路６２２とを仕切る隔壁の役割を果たしている。第２冷媒流路６２１を流れる冷媒と、低圧冷媒流路６２２を流れる低圧冷媒との熱交換は、第２板状部材６１を介して行われる。 The second refrigerant flow path 621 and the low-pressure refrigerant flow path 622 are alternately laminated (parallel arrangement) one by one in the plate lamination direction. The second plate member 61 serves as a partition that partitions the second refrigerant flow path 621 and the low-pressure refrigerant flow path 622. Heat exchange between the refrigerant flowing through the second refrigerant channel 621 and the low-pressure refrigerant flowing through the low-pressure refrigerant channel 622 is performed via the second plate member 61.
　液相冷媒用第１タンク空間６３および低圧冷媒用第１タンク空間６５は、第２熱交換部６２に対して、第２冷媒流路６２１および低圧冷媒流路６２２の一方側（図８の例では右方側）に配置されている。液相冷媒用第２タンク空間６４および低圧冷媒用第２タンク空間６６は、第２熱交換部６２に対して、第２冷媒流路６２１および低圧冷媒流路６２２の他方側（図８の例では左方側）に配置されている。 The first tank space 63 for liquid-phase refrigerant and the first tank space 65 for low-pressure refrigerant are on one side of the second refrigerant flow path 621 and the low-pressure refrigerant flow path 622 with respect to the second heat exchange section 62 (example in FIG. 8). In the right side). The second tank space for liquid phase refrigerant 64 and the second tank space for low pressure refrigerant 66 are on the other side of the second refrigerant flow path 621 and the low pressure refrigerant flow path 622 with respect to the second heat exchange section 62 (example in FIG. 8). In the left side).
　液相冷媒用第１タンク空間６３および液相冷媒用第２タンク空間６４は、複数の第２冷媒流路６２１に対して液相冷媒の分配および集合を行う。低圧冷媒用第１タンク空間６５および低圧冷媒用第２タンク空間６６は、複数の低圧冷媒流路６２２に対して低圧冷媒の分配および集合を行う。 The first tank space 63 for liquid phase refrigerant and the second tank space 64 for liquid phase refrigerant distribute and collect the liquid phase refrigerant with respect to the plurality of second refrigerant flow paths 621. The first tank space for low-pressure refrigerant 65 and the second tank space for low-pressure refrigerant 66 distribute and collect the low-pressure refrigerant with respect to the plurality of low-pressure refrigerant flow paths 622.
　液相冷媒用第１タンク空間６３、液相冷媒用第２タンク空間６４、低圧冷媒用第１タンク空間６５および低圧冷媒用第２タンク空間６６は、第２板状部材６１の四隅に形成された連通孔によって構成されている。 The first tank space 63 for liquid phase refrigerant, the second tank space for liquid phase refrigerant 64, the first tank space for low pressure refrigerant 65, and the second tank space for low pressure refrigerant 66 are formed at the four corners of the second plate member 61. It is constituted by a communication hole.
　本実施形態では、図９に示すように、略矩形状の第２板状部材６１の四隅のうち対角線上にある２つの隅部に、液相冷媒用第１タンク空間６３および液相冷媒用第２タンク空間６４が設けられている。そして、第２板状部材６１の残りの２つの隅部に、低圧冷媒用第１タンク空間６５および低圧冷媒用第２タンク空間６６が設けられている。 In the present embodiment, as shown in FIG. 9, the first tank space 63 for liquid phase refrigerant and the liquid phase refrigerant for two corners on the diagonal line among the four corners of the substantially rectangular second plate-like member 61. A second tank space 64 is provided. In the remaining two corners of the second plate-like member 61, a first tank space 65 for low-pressure refrigerant and a second tank space 66 for low-pressure refrigerant are provided.
　図８および図１０に示すように、第２熱交換部６２を構成する多数枚の第２板状部材６１のうち最も板積層方向一端側（図８の例では上側）に位置する第２最端板状部材６７は、第２天井板１９にろう付けにより接合されている。第２最端板状部材６７には、気液分離部３０からの液相冷媒を流入させる液相冷媒流入孔６７１が形成されている。液相冷媒流入孔６７１は、冷媒流出部１９１に対応する部位に形成されている。これにより、気液分離部３０内の液相冷媒は、冷媒流出部１９１および液相冷媒流入孔６７１を介して第２熱交換部６２（具体的には、液相冷媒用第１タンク空間６３）に流入する。 As shown in FIGS. 8 and 10, the second outermost member located on the one end side in the plate stacking direction (the upper side in the example of FIG. 8) among the multiple second plate members 61 constituting the second heat exchange unit 62. The end plate member 67 is joined to the second ceiling plate 19 by brazing. The second endmost plate member 67 is formed with a liquid-phase refrigerant inflow hole 671 through which the liquid-phase refrigerant from the gas-liquid separator 30 flows. The liquid-phase refrigerant inflow hole 671 is formed at a portion corresponding to the refrigerant outflow portion 191. As a result, the liquid-phase refrigerant in the gas-liquid separation unit 30 is transferred to the second heat exchange unit 62 (specifically, the first tank space 63 for liquid-phase refrigerant) via the refrigerant outflow portion 191 and the liquid-phase refrigerant inflow hole 671. ).
　図８および図９に示すように、第２熱交換部６２を構成する多数枚の第２板状部材６１のうち最も板積層方向他端側（図８の例では下側）に位置する第３最端板状部材６８には、第２ジョイント２３、第３ジョイント７１および第４ジョイント７２が取り付けられている。第３ジョイント７１は、低圧冷媒配管を接合するための部材であり、第２熱交換部６２の低圧冷媒入口７０１を形成している。低圧冷媒入口７０１は、冷凍サイクルの低圧側に接続されてもよく、冷凍サイクルの低圧冷媒が低圧冷媒入口７０１へ流入してもよい。第２熱交換部６２に流入する低圧冷媒は、第１熱交換部１２に流入する冷媒よりも圧力が低くなる。第４ジョイント７２は、低圧冷媒配管を接合するための部材であり、第２熱交換部６２の低圧冷媒出口７０２を形成している。 As shown in FIGS. 8 and 9, the second plate-like member 61 constituting the second heat exchanging part 62 is located on the other end side in the plate stacking direction (the lower side in the example of FIG. 8). A second joint 23, a third joint 71, and a fourth joint 72 are attached to the third outermost plate member 68. The third joint 71 is a member for joining the low-pressure refrigerant pipe, and forms the low-pressure refrigerant inlet 701 of the second heat exchange unit 62. The low-pressure refrigerant inlet 701 may be connected to the low-pressure side of the refrigeration cycle, and the low-pressure refrigerant of the refrigeration cycle may flow into the low-pressure refrigerant inlet 701. The low-pressure refrigerant flowing into the second heat exchange unit 62 has a lower pressure than the refrigerant flowing into the first heat exchange unit 12. The fourth joint 72 is a member for joining the low-pressure refrigerant pipe, and forms a low-pressure refrigerant outlet 702 of the second heat exchange unit 62.
　本実施形態では、第４ジョイント７２は、第３最端板状部材６８の長手方向における一端側（図９の例では右方側）に設けられている。第２ジョイント２３および第３ジョイント７１は、第３最端板状部材６８の長手方向における他端側（図９の例では左方側）に設けられている。また、第２ジョイント２３は、第３ジョイント７１よりも重力方向上方側に設けられている。 In the present embodiment, the fourth joint 72 is provided on one end side in the longitudinal direction of the third outermost plate member 68 (right side in the example of FIG. 9). The second joint 23 and the third joint 71 are provided on the other end side in the longitudinal direction of the third outermost plate member 68 (left side in the example of FIG. 9). Further, the second joint 23 is provided above the third joint 71 in the gravity direction.
　続いて、本実施形態における第２熱交換部６２の液相冷媒および低圧冷媒の流れについて説明する。 Subsequently, the flow of the liquid-phase refrigerant and the low-pressure refrigerant in the second heat exchange unit 62 in the present embodiment will be described.
　気液分離部３０から流入した冷媒は、図８の実線矢印に示すように、第２冷媒流路６２１を液相冷媒用第１タンク空間６３から液相冷媒用第２タンク空間６４へ向かって流れて、冷媒出口１０３から外部へ流出する。また、低圧冷媒入口７０１からから流入した低圧冷媒は、図８の破線矢印に示すように、低圧冷媒流路６２２を低圧冷媒用第２タンク空間６６から低圧冷媒用第１タンク空間６５へ向かって流れて、低圧冷媒出口７０２から外部へ流出する。 Refrigerant flowing from the gas-liquid separator 30 flows through the second refrigerant flow path 621 from the first liquid-phase refrigerant tank space 63 toward the second liquid-phase refrigerant tank space 64, as indicated by solid arrows in FIG. And flows out from the refrigerant outlet 103 to the outside. The low-pressure refrigerant that has flowed in from the low-pressure refrigerant inlet 701 passes through the low-pressure refrigerant flow path 622 from the second tank space 66 for low-pressure refrigerant toward the first tank space 65 for low-pressure refrigerant, as indicated by the broken-line arrows in FIG. It flows out from the low pressure refrigerant outlet 702 to the outside.
　以上説明したように、本実施形態では、熱交換器１０の第２天井板１９に、過冷却部として機能する第２熱交換部６２を接続している。これにより、気液分離部３０の剛性を向上させることができる。 As described above, in the present embodiment, the second heat exchange unit 62 that functions as a supercooling unit is connected to the second ceiling plate 19 of the heat exchanger 10. Thereby, the rigidity of the gas-liquid separation part 30 can be improved.
　また、本実施形態では、第２板状部材６１における液相冷媒の流れ方向の長さを、第１板状部材１１における冷媒の流れ方向の長さよりも短くしている。これにより、第２熱交換部６２の冷媒流れ方向の一端側（図８の例では右方側）にスペースが形成される。このスペースを、第２冷却水パイプ２４を配置スペースとして有効活用することができるので、搭載上のデッドスペースを小さくすることが可能となる。 Further, in the present embodiment, the length of the second plate member 61 in the flow direction of the liquid phase refrigerant is shorter than the length of the first plate member 11 in the flow direction of the refrigerant. Thereby, a space is formed on one end side (right side in the example of FIG. 8) of the second heat exchange unit 62 in the refrigerant flow direction. Since this space can be effectively used as the arrangement space for the second cooling water pipe 24, it is possible to reduce the dead space on mounting.
　ところで、比較例として、チューブ内を流通する冷媒とチューブ外を流通する冷却風とを熱交換させて冷媒を冷却するフィンアンドチューブ型の熱交換器において、放熱コア部の凝縮部（本実施形態の第１熱交換部１２に相当）と過冷却部（本実施形態の第２熱交換部６２に相当）との間に気液分離部を設けたものがある。この比較例に係る熱交換器では、冷却風（走行風）が常に当たる位置に気液分離部が設定されているため、冷却風の温度により気液分離部内の冷媒の状態が変化してしまうおそれがある。 By the way, as a comparative example, in a fin-and-tube heat exchanger that cools the refrigerant by exchanging heat between the refrigerant that circulates in the tube and the cooling air that flows outside the tube, a condensing part (this embodiment) There is one in which a gas-liquid separation unit is provided between the supercooling unit (corresponding to the second heat exchanging unit 62 of the present embodiment). In the heat exchanger according to this comparative example, since the gas-liquid separation unit is set at a position where the cooling air (running air) always hits, the state of the refrigerant in the gas-liquid separation unit changes depending on the temperature of the cooling air. There is a fear.
　これに対し、本実施形態の熱交換器１０は水冷式の積層型熱交換器であるため、気液分離部３０に走行風が当たることはない。したがって、気液分離部３０の冷媒の状態が変化することを抑制できる。 On the other hand, since the heat exchanger 10 of the present embodiment is a water-cooled stacked heat exchanger, traveling air does not hit the gas-liquid separator 30. Therefore, it can suppress that the state of the refrigerant | coolant of the gas-liquid separation part 30 changes.
　また、比較例に係る熱交換器では、剛性が低いフィンアンドチューブ型の熱交換器において気液分離部を凝縮部と過冷却部との間に配置するために、気液分離部の剛性を向上させる必要がある。このため、押出成形により形成された押出チューブ等で気液分離部構成する必要があり、製造コストが上昇してしまう。 In addition, in the heat exchanger according to the comparative example, in the fin-and-tube heat exchanger having low rigidity, the gas-liquid separation unit is arranged to be rigid between the condensing unit and the supercooling unit in order to arrange the gas-liquid separation unit. There is a need to improve. For this reason, it is necessary to comprise a gas-liquid separation part with the extrusion tube etc. which were formed by extrusion molding, and a manufacturing cost will rise.
　これに対し、本実施形態の熱交換器１０では、気液分離部３０を２つの板状部材、すなわち第１天井板１８および第２天井板１９により構成することができるため、製造コストを低減することが可能となる。
（第４実施形態）
　次に、本開示の第４実施形態について図１１に基づいて説明する。本第４実施形態は、上記第３実施形態と比較して、第２熱交換部６２を、液相冷媒と冷却水とを熱交換させて液相冷媒を過冷却する過冷却部とした点が異なるものである。なお、本実施形態の冷却水が、本開示の第２熱媒体に相当している。 On the other hand, in the heat exchanger 10 of this embodiment, since the gas-liquid separation part 30 can be comprised by two plate-shaped members, ie, the 1st ceiling board 18 and the 2nd ceiling board 19, manufacturing cost is reduced. It becomes possible to do.
(Fourth embodiment)
Next, a fourth embodiment of the present disclosure will be described based on FIG. Compared with the third embodiment, the fourth embodiment is configured such that the second heat exchange unit 62 is a supercooling unit that supercools the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant and the cooling water. Are different. Note that the cooling water of the present embodiment corresponds to the second heat medium of the present disclosure.
　図１１に示すように、本実施形態では、多数の第２板状部材６１は、第２熱交換部６２、液相冷媒用第１タンク空間６３、液相冷媒用第２タンク空間６４、冷却水用第３タンク空間６５０および冷却水用第４タンク空間６６０を形成している。 As shown in FIG. 11, in the present embodiment, a large number of second plate-like members 61 include a second heat exchange unit 62, a liquid-phase refrigerant first tank space 63, a liquid-phase refrigerant second tank space 64, a cooling unit. A third tank space for water 650 and a fourth tank space for cooling water 660 are formed.
　第２熱交換部６２は、液相冷媒が流通する複数の第２冷媒流路６２１、および、冷却水が流通する複数の第２冷却水流路６２３で構成されている。なお、本実施形態の第２冷却水流路６２３が、本開示の第２熱媒体流路に相当している。 The second heat exchange unit 62 includes a plurality of second refrigerant flow paths 621 through which liquid phase refrigerant flows and a plurality of second cooling water flow paths 623 through which cooling water flows. Note that the second cooling water channel 623 of the present embodiment corresponds to the second heat medium channel of the present disclosure.
　複数の第２冷媒流路６２１および複数の第２冷却水流路６２３は、多数枚の第２板状部材６１同士の間に形成されている。第２冷媒流路６２１および第２冷却水流路６２３の長手方向は、第２板状部材６１の長手方向と一致している。 The plurality of second refrigerant passages 621 and the plurality of second cooling water passages 623 are formed between a large number of second plate members 61. The longitudinal directions of the second refrigerant channel 621 and the second cooling water channel 623 coincide with the longitudinal direction of the second plate member 61.
　第２冷媒流路６２１および第２冷却水流路６２３は板積層方向に１本ずつ交互に積層配置（並列配置）されている。第２板状部材６１は、第２冷媒流路６２１と第２冷却水流路６２３とを仕切る隔壁の役割を果たしている。第２冷媒流路６２１を流れる冷媒と、第２冷却水流路６２３を流れる冷却水との熱交換は、第２板状部材６１を介して行われる。 The second refrigerant flow path 621 and the second cooling water flow path 623 are alternately stacked one by one in the plate stacking direction (parallel arrangement). The second plate-like member 61 serves as a partition that partitions the second refrigerant channel 621 and the second cooling water channel 623. Heat exchange between the refrigerant flowing through the second refrigerant flow path 621 and the cooling water flowing through the second cooling water flow path 623 is performed via the second plate member 61.
　液相冷媒用第１タンク空間６３および冷却水用第３タンク空間６５０は、第２熱交換部６２に対して、第２冷媒流路６２１および第２冷却水流路６２３の一方側（図１１の例では右方側）に配置されている。液相冷媒用第２タンク空間６４および冷却水用第４タンク空間６６０は、第２熱交換部６２に対して、第２冷媒流路６２１および第２冷却水流路６２３の他方側（図１１の例では左方側）に配置されている。冷却水用第３タンク空間６５０および冷却水用第４タンク空間６６０は、複数の第２冷却水流路６２３に対して冷却水の分配および集合を行う。 The first tank space 63 for liquid phase refrigerant and the third tank space for cooling water 650 are on one side of the second refrigerant flow path 621 and the second cooling water flow path 623 with respect to the second heat exchange section 62 (see FIG. 11). In the example, it is arranged on the right side). The second tank space for liquid phase refrigerant 64 and the fourth tank space for cooling water 660 are on the other side of the second refrigerant flow path 621 and the second cooling water flow path 623 with respect to the second heat exchange section 62 (see FIG. 11). In the example, it is arranged on the left side). The cooling water third tank space 650 and the cooling water fourth tank space 660 distribute and collect the cooling water to the plurality of second cooling water flow paths 623.
　液相冷媒用第１タンク空間６３、液相冷媒用第２タンク空間６４、冷却水用第３タンク空間６５０および冷却水用第４タンク空間６６０は、第２板状部材６１の四隅に形成された連通孔によって構成されている。本実施形態では、略矩形状の第２板状部材６１の四隅のうち対角線上にある２つの隅部に、冷却水用第３タンク空間６５０および冷却水用第４タンク空間６６０が設けられている。 The first tank space 63 for liquid phase refrigerant, the second tank space for liquid phase refrigerant 64, the third tank space for cooling water 650, and the fourth tank space for cooling water 660 are formed at the four corners of the second plate member 61. It is constituted by a communication hole. In the present embodiment, the third tank space for cooling water 650 and the fourth tank space for cooling water 660 are provided at two corners on the diagonal line among the four corners of the substantially rectangular second plate-shaped member 61. Yes.
　第２最端板状部材６７には、後述する第２内部冷却水パイプ８１が挿入される貫通孔（図示せず）が形成されている。この貫通孔は、第２内部冷却水パイプ８１の外表面にろう付け接合されている。また、この貫通孔は、第２最端板状部材６７の長手方向における液相冷媒流入孔６７１と反対側の端部に設けられている。 The second endmost plate member 67 is formed with a through hole (not shown) into which a second internal cooling water pipe 81 described later is inserted. This through hole is brazed to the outer surface of the second internal cooling water pipe 81. Further, the through hole is provided at an end portion on the opposite side to the liquid-phase refrigerant inflow hole 671 in the longitudinal direction of the second outermost plate member 67.
　第３最端板状部材６８には、第２ジョイント２３および第３冷却水パイプ７３が取り付けられている。第３冷却水パイプ７３は、第２熱交換部６２の冷却水入口７０３を形成している。 The second joint 23 and the third cooling water pipe 73 are attached to the third outermost plate member 68. The third cooling water pipe 73 forms a cooling water inlet 703 of the second heat exchange unit 62.
　本実施形態では、第３冷却水パイプ７３は、第３最端板状部材６８の長手方向における一端側（図１１の例では右方側）に設けられている。第２ジョイント２３は、第３最端板状部材６８の長手方向における他端側（図８の例では左方側）に設けられている。 In the present embodiment, the third cooling water pipe 73 is provided on one end side in the longitudinal direction of the third outermost plate member 68 (right side in the example of FIG. 11). The second joint 23 is provided on the other end side in the longitudinal direction of the third outermost plate member 68 (left side in the example of FIG. 8).
　気液分離部３０の内部には、冷却水が流通するとともに、冷却水用第４タンク空間６６０と冷却水用第２タンク空間１６とを連通させる第２内部冷却水通路８０が設けられている。具体的には、気液分離部３０の内部には、冷却水用第４タンク空間６６０と冷却水用第２タンク空間１６とを接続する第２内部冷却水パイプ８１が設けられている。この第２内部冷却水パイプ８１により、第２内部冷却水通路８０が構成されている。 Inside the gas-liquid separation unit 30, the second internal cooling water passage 80 that allows the cooling water to circulate and communicates the fourth tank space for cooling water 660 and the second tank space for cooling water 16 is provided. . Specifically, a second internal cooling water pipe 81 that connects the fourth cooling water tank space 660 and the second cooling water tank space 16 is provided inside the gas-liquid separation unit 30. The second internal cooling water pipe 81 constitutes a second internal cooling water passage 80.
　ところで、本実施形態では、第１熱交換部１２を構成する多数枚の第１板状部材１１のうち、板積層方向の略中央部よりも第１天井板１８側に位置する板状部材１１は、冷却水用第１タンク空間１５を構成する突出部（図示せず）を閉塞する第１閉塞部（図示せず）を有している。これにより、冷却水用第１タンク空間１５は板積層方向に２つの空間に仕切られている。 By the way, in this embodiment, among the many 1st plate-shaped members 11 which comprise the 1st heat exchange part 12, the plate-shaped member 11 located in the 1st ceiling board 18 side rather than the approximate center part of a plate lamination direction. Has a first closing portion (not shown) for closing a protruding portion (not shown) constituting the first tank space 15 for cooling water. Thereby, the 1st tank space 15 for cooling water is divided into two spaces in the board lamination direction.
　また、第１熱交換部１２を構成する多数枚の第１板状部材１１のうち、板積層方向の略中央部と最端板状部材１７との間に位置する板状部材１１は、冷却水用第２タンク空間１６を構成する突出部（図示せず）を閉塞する第２閉塞部（図示せず）を有している。これにより、冷却水用第２タンク空間１６は板積層方向に２つの空間に仕切られている。 Of the many first plate-like members 11 constituting the first heat exchange unit 12, the plate-like member 11 located between the substantially central portion in the plate stacking direction and the outermost plate-like member 17 is cooled. A second closing part (not shown) for closing a protruding part (not shown) constituting the second tank space 16 for water is provided. Thereby, the cooling water second tank space 16 is partitioned into two spaces in the plate stacking direction.
　続いて、本実施形態における熱交換器１０の冷却水の流れについて説明する。 Then, the flow of the cooling water of the heat exchanger 10 in this embodiment is demonstrated.
　図１１の一点鎖線矢印に示すように、第２熱交換部６２の冷却水入口７０３から冷却水用第３タンク空間６５０へ流入した冷却水は、冷却水流路６２３を流れて、冷却水用第４タンク空間６６０へ流入する。冷却水用第４タンク空間６６０へ流入した冷却水は、第２内部冷却水通路８０を流れて、第１熱交換部１２の冷却水用第２タンク空間１６へ流入する。 As indicated by a one-dot chain line arrow in FIG. 11, the cooling water that has flowed into the cooling water third tank space 650 from the cooling water inlet 703 of the second heat exchanging unit 62 flows through the cooling water flow path 623, It flows into the 4-tank space 660. The cooling water flowing into the fourth cooling water tank space 660 flows through the second internal cooling water passage 80 and flows into the second cooling water tank space 16 of the first heat exchange unit 12.
　一方、熱交換器１０の冷却水入口１０４から第１内部冷却水通路４０を介して冷却水用第１タンク空間１５に流入した冷却水は、板積層方向他端側（図１１の例では下方側）の第１冷却水流路１２２を流れて、冷却水用第２タンク空間１６へ流入する。このように、本実施形態の熱交換器１０は、冷却水用第２タンク空間１６において、熱交換器１０の冷却水入口１０４から流入した冷却水と、第２熱交換部６２を通過した後の冷却水とが合流するように構成されている。 On the other hand, the cooling water flowing into the cooling water first tank space 15 from the cooling water inlet 104 of the heat exchanger 10 via the first internal cooling water passage 40 is the other side in the plate stacking direction (in the example of FIG. Side) first cooling water flow path 122 and flows into the cooling water second tank space 16. Thus, after the heat exchanger 10 of this embodiment passes the 2nd heat exchange part 62 with the cooling water which flowed in from the cooling water inlet 104 of the heat exchanger 10 in the 2nd tank space 16 for cooling water. The cooling water is configured to merge.
　冷却水用第２タンク空間１６へ流入した冷却水は、板積層方向中央側の第１冷却水流路１２２を冷却水用第２タンク空間１６から冷却水用第１タンク空間１５へ向かって流れた後、板積層方向一端側（図１１の例では上方側）の第１冷却水流路１２２を冷却水用第１タンク空間１５から冷却水用第２タンク空間１６へ向かって流れて、冷却水出口１０２から外部へ流出する。すなわち、第１熱交換部１２は、冷却水の流れが２回Ｕターンするように構成されている。 The cooling water flowing into the second cooling water tank space 16 flows from the second cooling water tank space 16 toward the first cooling water tank space 15 through the first cooling water flow path 122 at the center side in the plate stacking direction. Thereafter, the coolant flows through the first cooling water flow path 122 on one end side in the plate stacking direction (upper side in the example of FIG. 11) from the first cooling water tank space 15 toward the second cooling water tank space 16, and the cooling water outlet. It flows out from 102. That is, the first heat exchange unit 12 is configured such that the flow of the cooling water makes a U-turn twice.
　以上説明したように、本実施形態の熱交換器１０では、第１熱交換部１２に、熱交換器１０の冷却水入口１０４から流入した冷却水と、第２熱交換部６２を通過した後の冷却水との双方を流入させている。すなわち、第１熱交換部１２に対して、冷却水を並列に流入させることができる。このため、第１熱交換部１２において冷却水の圧力損失を低減でき、第１熱交換部１２の熱交換効率を向上させることができる。
（第５実施形態）
　次に、本開示の第５実施形態について図１２に基づいて説明する。本第５実施形態は、上記第４実施形態と比較して、冷却水入口１０４および第１内部冷却水パイプ４１を廃止して、第１熱交換部１２において第２熱交換部６２を通過した後の冷却水と冷媒とを熱交換させる点が異なるものである。 As described above, in the heat exchanger 10 of the present embodiment, the cooling water that has flowed into the first heat exchange unit 12 from the cooling water inlet 104 of the heat exchanger 10 and the second heat exchange unit 62 are passed through. Both cooling water and water are introduced. That is, the cooling water can be allowed to flow in parallel to the first heat exchange unit 12. For this reason, it is possible to reduce the pressure loss of the cooling water in the first heat exchange unit 12 and to improve the heat exchange efficiency of the first heat exchange unit 12.
(Fifth embodiment)
Next, a fifth embodiment of the present disclosure will be described based on FIG. Compared with the fourth embodiment, the fifth embodiment abolishes the cooling water inlet 104 and the first internal cooling water pipe 41 and passes through the second heat exchange unit 62 in the first heat exchange unit 12. The point which heat-exchanges a later cooling water and a refrigerant | coolant differs.
　図１２に示すように、第１熱交換部１２の冷却水用第２タンク空間１６は、第２熱交換部６２を通過した後の冷却水のみが流入するようになっている。また、本実施形態では、第１熱交換部１２を構成する多数枚の第１板状部材１１のうち中央板状部材１１Ａは、冷却水用第２タンク空間１６を構成する突出部（図示せず）を閉塞する閉塞部（図示せず）を有している。これにより、冷却水用第２タンク空間１６は板積層方向に２つの空間に仕切られている。 As shown in FIG. 12, only the cooling water after passing through the second heat exchange section 62 flows into the second tank space 16 for cooling water of the first heat exchange section 12. In the present embodiment, the central plate-like member 11A among the multiple first plate-like members 11 constituting the first heat exchanging portion 12 is a protruding portion (not shown) constituting the second tank space 16 for cooling water. A closing portion (not shown) that closes the opening). Thereby, the cooling water second tank space 16 is partitioned into two spaces in the plate stacking direction.
　したがって、冷却水用第２タンク空間１６へ流入した冷却水は、板積層方向他案側（図１２の例では下方側）の第１冷却水流路１２２を冷却水用第２タンク空間１６から冷却水用第１タンク空間１５へ向かって流れた後、板積層方向一端側（図１１の例では上方側）の第１冷却水流路１２２を冷却水用第１タンク空間１５から冷却水用第２タンク空間１６へ向かって流れて、冷却水出口１０２から外部へ流出する。すなわち、第１熱交換部１２は、冷却水の流れが１回Ｕターンするように構成されている。 Therefore, the cooling water that has flowed into the second cooling water tank space 16 cools the first cooling water flow path 122 on the other side in the plate stacking direction (downward in the example of FIG. 12) from the second cooling water tank space 16. After flowing toward the first water tank space 15, the first cooling water flow path 122 on one end side in the plate stacking direction (the upper side in the example of FIG. 11) passes through the first cooling water flow path 122 from the first cooling water tank space 15. It flows toward the tank space 16 and flows out from the cooling water outlet 102 to the outside. That is, the first heat exchange unit 12 is configured such that the flow of the cooling water makes a U-turn once.
　以上説明したように、本実施形態の熱交換器１０では、第１熱交換部１２に、第２熱交換部６２を通過した後の冷却水を流入させている。すなわち、第２熱交換部６２に、熱交換器１０に流入させる冷却水の全量を流通させている。このため、気液分離部３０によって気液分離された液相冷媒の過冷却を優先的に行うことができる。 As described above, in the heat exchanger 10 of the present embodiment, the cooling water after passing through the second heat exchange unit 62 is caused to flow into the first heat exchange unit 12. That is, the entire amount of cooling water that flows into the heat exchanger 10 is circulated through the second heat exchange unit 62. For this reason, the supercooling of the liquid-phase refrigerant separated by the gas-liquid separation unit 30 can be performed preferentially.
　このとき、第１熱交換部１２では、第２熱交換部６２を通過した後の冷却水により冷媒を冷却することになる。しかしながら、液相冷媒の過冷却に必要な冷却能力は小さいので、第１熱交換部１２の冷媒凝縮機能が損なわれることを抑制できる。
（第６実施形態）
　次に、本開示の第６実施形態について図１３～図１８に基づいて説明する。本第５実施形態は、上記第５実施形態と比較して、熱交換器１０を、凝縮モードと蒸発モードとを切り替え可能なヒートポンプサイクルの室外器として用いた点が異なるものである。 At this time, in the 1st heat exchange part 12, a refrigerant | coolant is cooled with the cooling water after passing the 2nd heat exchange part 62. FIG. However, since the cooling capacity required for the supercooling of the liquid-phase refrigerant is small, it is possible to suppress the refrigerant condensing function of the first heat exchange unit 12 from being impaired.
(Sixth embodiment)
Next, a sixth embodiment of the present disclosure will be described with reference to FIGS. The fifth embodiment is different from the fifth embodiment in that the heat exchanger 10 is used as an outdoor unit of a heat pump cycle capable of switching between a condensation mode and an evaporation mode.
　凝縮モードは、熱交換器１０を、冷凍サイクルの高圧側冷媒と冷却水とを熱交換して高圧側冷媒を凝縮させる凝縮器として機能させるモードである。蒸発モードは、熱交換器１０を、冷凍サイクルの低圧側冷媒と冷却水とを熱交換して低圧側冷媒を蒸発させる蒸発器として機能させるモードである。なお、図１３～図１８において、実線矢印が凝縮モード時の冷媒流れを示しており、二点鎖線矢印が蒸発モード時の冷媒流れを示しており、一点鎖線矢印が冷却水流れを示している。 The condensation mode is a mode for causing the heat exchanger 10 to function as a condenser for condensing the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant and the cooling water of the refrigeration cycle. The evaporation mode is a mode in which the heat exchanger 10 functions as an evaporator that exchanges heat between the low-pressure side refrigerant and the cooling water of the refrigeration cycle to evaporate the low-pressure side refrigerant. In FIGS. 13 to 18, the solid arrow indicates the refrigerant flow in the condensation mode, the two-dot chain arrow indicates the refrigerant flow in the evaporation mode, and the one-dot chain arrow indicates the cooling water flow. .
　図１３および図１７に示すように、本実施形態の第２ジョイント２３は、凝縮モード時に第２熱交換部６２から冷媒を外部へ流出させる第１冷媒出口１０３を形成している。図１４および図１７に示すように、第２ジョイント２３は、第３最端板状部材６８における重力方向上方側に配置されている。なお、図１６に示すように、本実施形態では、第３冷却水パイプ７３も、第３最端板状部材６８における重力方向上方側に配置されている。 As shown in FIGS. 13 and 17, the second joint 23 of the present embodiment forms a first refrigerant outlet 103 through which the refrigerant flows out from the second heat exchanging unit 62 during the condensation mode. As shown in FIGS. 14 and 17, the second joint 23 is disposed on the uppermost side in the gravity direction of the third endmost plate-like member 68. As shown in FIG. 16, in the present embodiment, the third cooling water pipe 73 is also arranged on the upper side in the gravity direction of the third outermost plate member 68.
　図１４および図１５に示すように、第２天井板１９の長手方向における冷媒流入部１８１に近い側の端部に、第５ジョイント７５が取り付けられている。第５ジョイント７５は、冷媒配管を接合するための部材であり、蒸発モード時に気液分離部３０から冷媒を外部へ流出させる第２冷媒出口７０５を形成している。本実施形態では、冷媒流入部１８１および第５ジョイント７５は、第２天井板１９における重力方向上方側に配置されている。 As shown in FIGS. 14 and 15, a fifth joint 75 is attached to the end of the second ceiling plate 19 on the side close to the refrigerant inflow portion 181 in the longitudinal direction. The fifth joint 75 is a member for joining the refrigerant pipes, and forms a second refrigerant outlet 705 that allows the refrigerant to flow out from the gas-liquid separator 30 in the evaporation mode. In the present embodiment, the refrigerant inflow portion 181 and the fifth joint 75 are disposed on the upper side in the gravity direction of the second ceiling plate 19.
　続いて、本実施形態における熱交換器１０の冷媒の流れについて説明する。 Subsequently, the flow of the refrigerant in the heat exchanger 10 in the present embodiment will be described.
　凝縮モードにおいては、図１３の実線矢印に示すように、冷媒流入部１８１から気液分離部３０へ流入した冷媒は、気液分離部３０にて気液分離される。気液分離部３０にて気液分離された液相冷媒は、液相冷媒流入孔６７１から液相冷媒用第１タンク空間６３へ流入する。液相冷媒用第１タンク空間６３へ流入した冷媒は、第２冷媒流路６２１を液相冷媒用第１タンク空間６３から液相冷媒用第２タンク空間６４へ向かって流れて、冷媒出口１０３から外部へ流出する。 In the condensation mode, as indicated by the solid line arrows in FIG. 13, the refrigerant that has flowed from the refrigerant inflow portion 181 into the gas-liquid separation portion 30 is separated into gas and liquid by the gas-liquid separation portion 30. The liquid-phase refrigerant that has been gas-liquid separated by the gas-liquid separation unit 30 flows into the liquid-phase refrigerant first tank space 63 from the liquid-phase refrigerant inflow hole 671. The refrigerant that has flowed into the first liquid phase refrigerant tank space 63 flows from the first liquid phase refrigerant tank space 63 toward the second liquid phase refrigerant tank space 64 through the second refrigerant flow path 621, and the refrigerant outlet 103. Out to the outside.
　一方、蒸発モードにおいては、図１８の二点鎖線矢印に示すように、冷媒流入部１８１から気液分離部３０へ流入した冷媒は、第２冷媒出口７０５から外部へ流出する。 On the other hand, in the evaporation mode, as indicated by the two-dot chain line arrow in FIG. 18, the refrigerant that has flowed from the refrigerant inflow portion 181 to the gas-liquid separation portion 30 flows out from the second refrigerant outlet 705 to the outside.
　したがって、気液分離部３０は内部に、凝縮モード時に第１熱交換部１２から流入した冷媒を第２熱交換部６２へ流出させる冷媒通路と、蒸発モード時に第１熱交換部１２から流入した冷媒を外部へ流出させる冷媒通路と、を有する。 Therefore, the gas-liquid separation unit 30 has a refrigerant passage that allows the refrigerant flowing from the first heat exchange unit 12 to flow out to the second heat exchange unit 62 in the condensation mode, and the first heat exchange unit 12 to flow in the evaporation mode. And a refrigerant passage through which the refrigerant flows out.
　なお、熱交換器１０内の冷媒流路の切り替えは、熱交換器１０の外部（より詳細には、冷媒出口側）に設けたバルブ等により行うことができる。このように、熱交換器１０内の冷媒流路を切り替えることで、蒸発モードと凝縮モードとを切り替えることができる。 Note that switching of the refrigerant flow path in the heat exchanger 10 can be performed by a valve or the like provided outside the heat exchanger 10 (more specifically, on the refrigerant outlet side). Thus, by switching the refrigerant flow path in the heat exchanger 10, the evaporation mode and the condensation mode can be switched.
　以上説明したように、本実施形態の熱交換器１０は、当該熱交換器１０の内部に、凝縮モードの冷媒流れと蒸発モードの冷媒流れとを形成可能になっている。このため、本実施形態の熱交換器１０を、ヒートポンプサイクルの室外器として好適に用いることができる。この場合、室外器の水冷化を図ることができ、これより冷却水の蓄熱効果から冷媒挙動が安定しＣＯＰ制御を容易に行うことができる。
（第７実施形態）
　次に、本開示の第７実施形態について図１９～図２１に基づいて説明する。本第７実施形態は、上記第４実施形態と比較して、気液分離部３０の構成が異なるものである。 As described above, the heat exchanger 10 of the present embodiment is capable of forming the refrigerant flow in the condensation mode and the refrigerant flow in the evaporation mode inside the heat exchanger 10. For this reason, the heat exchanger 10 of this embodiment can be used suitably as an outdoor unit of a heat pump cycle. In this case, water cooling of the outdoor unit can be achieved, and from this, the refrigerant behavior is stabilized by the heat storage effect of the cooling water, and COP control can be easily performed.
(Seventh embodiment)
Next, a seventh embodiment of the present disclosure will be described with reference to FIGS. The seventh embodiment is different from the fourth embodiment in the configuration of the gas-liquid separation unit 30.
　図１９および図２０に示すように、本実施形態の気液分離部３０は、複数の第３板状部材９１を互いに積層されて接合されることによって一体的に形成されている。第３板状部材９１の積層方向は、第１板状部材１１の積層方向（板積層方向）と平行になっている。第３板状部材９１は、第１板状部材１１に対して、配置方向の長さおよび幅方向の長さが等しくなっている。 As shown in FIG. 19 and FIG. 20, the gas-liquid separator 30 of this embodiment is integrally formed by stacking and joining a plurality of third plate-like members 91 to each other. The lamination direction of the third plate member 91 is parallel to the lamination direction (plate lamination direction) of the first plate member 11. The third plate-like member 91 is equal in length to the first plate-like member 11 in the arrangement direction and in the width direction.
　多数の第３板状部材９１は、張出部９１１の突出先端が互いに同じ側を向くように配置されている。なお、本実施形態では、第１板状部材１１は、張出部１１１の突出先端が気液分離部３０と反対側（図１９の例では上方側）を向くように配置されている。一方、第２板状部材６１および第３板状部材９１は、それぞれ、張出部６１１、９１１の突出先端が第１熱交換部１２と反対側（図１９の例では下方側）を向くように配置されている。 The multiple third plate-like members 91 are arranged so that the protruding tips of the overhang portions 911 face the same side. In the present embodiment, the first plate-like member 11 is arranged so that the protruding tip of the overhanging portion 111 faces the side opposite to the gas-liquid separation portion 30 (the upper side in the example of FIG. 19). On the other hand, the second plate-like member 61 and the third plate-like member 91 are such that the protruding tips of the overhang portions 611 and 911 face the opposite side to the first heat exchange portion 12 (the lower side in the example of FIG. 19), respectively. Is arranged.
　図２１に示すように、複数の第３板状部材９１同士の間には、第１熱交換部１２の第１冷媒流路１２１から流入した冷媒が流れる複数の気液分離通路９２が形成されている。第３板状部材９１には第１貫通穴９１２が設けられており、これにより隣り合う気液分離通路９２同士が互いに連通している。なお、気液分離通路９２には、インナーフィンは配置されていない。 As shown in FIG. 21, a plurality of gas-liquid separation passages 92 through which the refrigerant flowing from the first refrigerant channel 121 of the first heat exchange unit 12 flows are formed between the plurality of third plate-like members 91. ing. The 3rd plate-shaped member 91 is provided with the 1st through-hole 912, and the gas-liquid separation channel | path 92 adjacent to each other by this communicates with each other. Note that no inner fin is disposed in the gas-liquid separation passage 92.
　ここで、気液分離部３０を構成する多数枚の第３板状部材９１のうち、最も板積層方向一端側に位置する第３板状部材９１を第３天井板９３(第３端板）といい、最も板積層方向他端側に位置する第３板状部材９１を第４天井板９４（第４端板）という。 Here, among the multiple third plate-like members 91 constituting the gas-liquid separation unit 30, the third plate-like member 91 located closest to one end side in the plate stacking direction is the third ceiling plate 93 (third end plate). The third plate-like member 91 located closest to the other end side in the plate stacking direction is referred to as a fourth ceiling plate 94 (fourth end plate).
　第３天井板９３は、第１天井板１８の板積層方向他端側の面に接合されている。第４天井板９４の張出部９１１における板積層方向他端側の面には、第２天井板１９が接合されている。また、第３天井板９３は、他の第３板状部材９１と比較して、板厚が厚くなっている。 The third ceiling plate 93 is joined to the surface of the first ceiling plate 18 on the other end side in the plate stacking direction. The second ceiling plate 19 is joined to the surface on the other end side in the plate stacking direction of the overhanging portion 911 of the fourth ceiling plate 94. The third ceiling plate 93 is thicker than the other third plate member 91.
　第３板状部材９１には、第１内部冷却水パイプ４１が貫通する第２貫通穴９１３と、第２内部冷却水パイプ８１が貫通する第３貫通穴（図示せず）が設けられている。なお、本実施形態では、第１内部冷却水パイプ４１は、第２冷却水パイプ２４と一体に形成されている。 The third plate-like member 91 is provided with a second through hole 913 through which the first internal cooling water pipe 41 passes and a third through hole (not shown) through which the second internal cooling water pipe 81 passes. . In the present embodiment, the first internal cooling water pipe 41 is formed integrally with the second cooling water pipe 24.
　図２０および図２１に示すように、第２天井板１９における第２熱交換部６２が接合されている部位以外の部位には、乾燥剤９５を気液分離部３０内に挿入するための挿入口９６が設けられている。挿入口９６は、栓部９７によって閉塞されている。 As shown in FIG. 20 and FIG. 21, the insertion for inserting the desiccant 95 into the gas-liquid separation unit 30 is performed on the second ceiling plate 19 other than the part where the second heat exchange unit 62 is joined. A mouth 96 is provided. The insertion port 96 is closed by a plug portion 97.
　乾燥剤９５は、袋体の内部に吸水用の粒状ゼオライトが収納されたものであり、冷媒中の水分を吸収するようになっている。これは、冷媒中の水分により冷凍サイクルを構成する各機能部品が腐食したり、膨張弁の細孔で凍結して冷媒流れが滞ったりするのを防止するためのものである。 The desiccant 95 is one in which granular zeolite for water absorption is stored inside the bag body, and absorbs moisture in the refrigerant. This is to prevent each functional component constituting the refrigeration cycle from being corroded by moisture in the refrigerant, or freezing in the pores of the expansion valve to stagnate the refrigerant flow.
　乾燥剤９５は、気液分離部３０内部、すなわち気液分離通路９２における挿入口９６に対応する部位に配置されている。本実施形態では、乾燥剤９５は、第１貫通穴９１２の近傍に配置されている。 The desiccant 95 is disposed inside the gas-liquid separator 30, that is, at a portion corresponding to the insertion port 96 in the gas-liquid separation passage 92. In the present embodiment, the desiccant 95 is disposed in the vicinity of the first through hole 912.
　図示は省略しているが、本実施形態の第３天井板９３には、凹部が設けられている。凹部は、第３天井板９３の一部を板積層方向他側に向かって凹ませることにより形成されている。第３天井板９３に凹部を設けることで、第１天井板１８と第３天井板９３との間、すなわち第１熱交換部１２と気液分離部３０との間に、隙間を形成することができる。 Although not shown, the third ceiling plate 93 of the present embodiment is provided with a recess. The recess is formed by denting a part of the third ceiling plate 93 toward the other side in the plate stacking direction. By providing a recess in the third ceiling plate 93, a gap is formed between the first ceiling plate 18 and the third ceiling plate 93, that is, between the first heat exchange unit 12 and the gas-liquid separation unit 30. Can do.
　以上説明したように、本実施形態では、気液分離部３０内の気液分離空間を多数枚の第３板状部材９１により構成している。これにより、気液分離部３０内で冷媒液面が分割されるので、冷媒液面の泡立ちを抑制することができる。 As described above, in this embodiment, the gas-liquid separation space in the gas-liquid separation unit 30 is configured by a large number of third plate members 91. Thereby, since a refrigerant | coolant liquid level is divided | segmented within the gas-liquid separation part 30, foaming of a refrigerant | coolant liquid level can be suppressed.
　ところで、第２板状部材６１における冷媒流れ方向の長さを、第１板状部材１１における前記冷媒の流れ方向の長さと同等とした場合、気液分離部３０内に乾燥剤９５を設置するためには、専用部品を追加する必要がある。このため、製造コストが増大するという問題がある。 By the way, when the length of the refrigerant flow direction in the second plate member 61 is equal to the length of the refrigerant flow direction in the first plate member 11, the desiccant 95 is installed in the gas-liquid separator 30. In order to do this, it is necessary to add dedicated parts. For this reason, there exists a problem that manufacturing cost increases.
　これに対し、本実施形態では、第２板状部材６１における冷媒流れ方向の長さを、第１板状部材１１における前記冷媒の流れ方向の長さよりも短くしている。さらに、第２天井板１９における第２熱交換部６２が接合されている部位以外の部位には、乾燥剤９５を気液分離部３０内に挿入するための挿入口９６を設けている。これによれば、乾燥剤９５を設置するための専用部品を追加することなく、気液分離部３０内に乾燥剤９５を挿入することができる。 In contrast, in the present embodiment, the length of the second plate member 61 in the refrigerant flow direction is shorter than the length of the first plate member 11 in the refrigerant flow direction. Further, an insertion port 96 for inserting the desiccant 95 into the gas-liquid separation unit 30 is provided at a portion of the second ceiling plate 19 other than the portion where the second heat exchange unit 62 is joined. According to this, it is possible to insert the desiccant 95 into the gas-liquid separator 30 without adding a dedicated part for installing the desiccant 95.
　また、本実施形態では、第１冷媒流路１２１にオフセットフィン５０を配置しているので、気液分離部３０に冷媒が二相（気相と液相）に分離して流入することを抑制できる。なお、第３板状部材９１は気液分離部３０内の液相冷媒により冷却されているので、気液分離部３０に流入する際に気泡（気相冷媒）がわずかに混入した場合でも、気泡は第３板状部材９１と熱交換することで冷却されて凝縮する。 Moreover, in this embodiment, since the offset fin 50 is arrange | positioned in the 1st refrigerant | coolant flow path 121, it suppresses that a refrigerant | coolant isolate | separates into the gas-liquid separation part 30, and flows in into two phases (a gaseous phase and a liquid phase). it can. In addition, since the third plate-like member 91 is cooled by the liquid phase refrigerant in the gas-liquid separation unit 30, even when bubbles (gas phase refrigerant) are slightly mixed when flowing into the gas-liquid separation unit 30, The bubbles are cooled and condensed by exchanging heat with the third plate-like member 91.
　したがって、本実施形態では、気液分離部３０の気液分離性を向上させることが可能となる。 Therefore, in this embodiment, the gas-liquid separation property of the gas-liquid separation unit 30 can be improved.
　また、本実施形態では、第３天井板９３に凹部を設けて、第１熱交換部１２と気液分離部３０との間に隙間を形成している。これにより、高温冷媒の有する熱により気液分離部３０内の液相冷媒が加熱されることを抑制できる。 In the present embodiment, a recess is provided in the third ceiling plate 93 so that a gap is formed between the first heat exchange unit 12 and the gas-liquid separation unit 30. Thereby, it can suppress that the liquid phase refrigerant | coolant in the gas-liquid separation part 30 is heated with the heat which a high temperature refrigerant | coolant has.
　ところで、本実施形態では、図示しないラジエータにおいて冷却された冷却水を、冷却水入口１０４から第１内部冷却水通路４０を介して第１熱交換部１２に流入させるとともに、冷却水入口７０３から第２熱交換部６２に流入させている。このため、２つの冷却水入口１０４、７０３から流入する冷却水量を制御することで、第１熱交換部１２への通水流量および第２熱交換部６２への通水流量の流量分配制御を行うことができる。 By the way, in the present embodiment, cooling water cooled by a radiator (not shown) is caused to flow from the cooling water inlet 104 into the first heat exchange section 12 via the first internal cooling water passage 40 and from the cooling water inlet 703 to the first. 2 The heat exchange section 62 is made to flow. Therefore, by controlling the amount of cooling water flowing in from the two cooling water inlets 104 and 703, flow distribution control of the water flow rate to the first heat exchange unit 12 and the water flow rate to the second heat exchange unit 62 is performed. It can be carried out.
　すなわち、第１熱交換部１２への通水流量を増加させることで、冷媒の凝縮性能を向上させ、凝縮能力を増大させることができる。一方、第２熱交換部６２への通水流量を増加させることで、冷媒の過冷却性能を向上させ、冷媒の過冷却度を高めることができる。 That is, by increasing the water flow rate to the first heat exchange unit 12, the condensation performance of the refrigerant can be improved and the condensation capacity can be increased. On the other hand, by increasing the water flow rate to the second heat exchange unit 62, it is possible to improve the supercooling performance of the refrigerant and increase the degree of supercooling of the refrigerant.
　なお、第２熱交換部６２にて加熱された冷却水を冷却するための専用ラジエータを設け、この専用ラジエータにより冷却された冷却水を第２熱交換部６２に流入させてもよい。これによれば、冷媒の過冷却度をより高めることができる。 In addition, a dedicated radiator for cooling the cooling water heated in the second heat exchange unit 62 may be provided, and the cooling water cooled by the dedicated radiator may flow into the second heat exchange unit 62. According to this, the degree of supercooling of the refrigerant can be further increased.
　空冷式、すなわち冷媒と空気との間で熱交換を行うことにより冷媒を冷却する熱交換器であって、凝縮部と過冷却部が同一放熱面上に配置されているものでは、熱交換器に対する空気の流入量を制御できない場合がある。このため、冷媒の過冷却度を高めるためには、凝縮部と過冷却部の放熱面積割合を変更するしか方法がないので、過冷却部の面積を増大させて、凝縮部の面積を縮小させる必要がある。しかしながら、凝縮部の面積が縮小すると、冷媒圧力が上昇するため、実質的に冷媒の過冷却度を制御することが困難であった。 A heat exchanger that cools the refrigerant by air exchange, that is, heat exchange between the refrigerant and air, in which the condensing unit and the supercooling unit are arranged on the same heat radiation surface, the heat exchanger In some cases, it is not possible to control the amount of air inflow. For this reason, in order to increase the degree of supercooling of the refrigerant, there is only a method of changing the heat radiation area ratio of the condensing part and the supercooling part. There is a need. However, when the area of the condensing part is reduced, the refrigerant pressure increases, so it is difficult to substantially control the degree of supercooling of the refrigerant.
　これに対し、本実施形態では、上述したように、第１熱交換部１２への通水流量および第２熱交換部６２への通水流量の流量分配制御を行うことで、冷媒の過冷却度の制御を行うことが可能となる。 On the other hand, in the present embodiment, as described above, the refrigerant is supercooled by performing flow rate distribution control of the water flow rate to the first heat exchange unit 12 and the water flow rate to the second heat exchange unit 62. It is possible to control the degree.
　本開示は上述の実施形態に限定されることなく、本開示の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。 The present disclosure is not limited to the above-described embodiment, and various modifications can be made as follows without departing from the spirit of the present disclosure.
　上記第６実施形態では、熱交換器１０内の冷媒流路の切り替えを、熱交換器１０の外部に設けたバルブ等により行う例について説明したが、冷媒流路の切替方法はこれに限定されない。例えば、熱交換器１０の気液分離部３０の内部に、第１熱交換部１２から流出した冷媒を外部へ流出させる冷媒流れと、第１熱交換部１２から流出した冷媒を第２熱交換部６２へ流入させる冷媒流れとを切り替え可能なバルブ等を設けてもよい。 In the sixth embodiment, the example in which switching of the refrigerant flow path in the heat exchanger 10 is performed by a valve or the like provided outside the heat exchanger 10 has been described, but the method of switching the refrigerant flow path is not limited to this. . For example, the refrigerant flow that causes the refrigerant that has flowed out from the first heat exchange unit 12 to flow to the outside in the gas-liquid separation unit 30 of the heat exchanger 10, and the refrigerant that has flowed out from the first heat exchange unit 12 to the second heat exchange You may provide the valve | bulb etc. which can switch the refrigerant | coolant flow made to flow in into the part 62. FIG.
　上記各実施形態に開示された手段は、実施可能な範囲で適宜組み合わせてもよい。 The means disclosed in each of the above embodiments may be appropriately combined within a practicable range.

Claims (8)

  1. 　冷凍サイクルの冷媒と第１熱媒体とを熱交換させる第１熱交換部（１２）を備える積層型熱交換器であって、
    　前記第１熱交換部（１２）は、
    　　互いに積層されて接合された複数の第１板状部材（１１）と、
    　　前記複数の第１板状部材（１１）の間に設けられて、前記複数の第１板状部材（１１）の積層方向に並んでおり、前記冷媒が流れる複数の第１冷媒流路（１２１）と、
    　　前記複数の第１板状部材（１１）の間に設けられて、前記複数の第１板状部材（１１）の積層方向に並んでおり、前記第１熱媒体が流れる複数の第１熱媒体流路（１２２）と、を含み、
    　前記複数の第１板状部材（１１）のうちの１つで前記積層方向の最外側に配置される第１端板（１８）に接合された第２端板（１９）と、
    　前記第１端板（１８）と前記２端板（１９）との間に設けられた空間を有し、内部に流入した前記冷媒の気液を分離するとともに前記冷凍サイクル内の余剰冷媒を蓄える気液分離部（３０）と、をさらに備えている積層型熱交換器。     A stacked heat exchanger comprising a first heat exchange section (12) for exchanging heat between a refrigerant of a refrigeration cycle and a first heat medium,
    The first heat exchange unit (12)
    A plurality of first plate-like members (11) laminated and joined to each other;
    A plurality of first refrigerant flow paths (121) provided between the plurality of first plate members (11), arranged in the stacking direction of the plurality of first plate members (11), and through which the refrigerant flows. )When,
    A plurality of first heat media which are provided between the plurality of first plate members (11) and are arranged in the stacking direction of the plurality of first plate members (11) and through which the first heat medium flows. A flow path (122),
    A second end plate (19) joined to a first end plate (18) disposed on the outermost side in the stacking direction in one of the plurality of first plate-like members (11);
    It has a space provided between the first end plate (18) and the second end plate (19), separates the gas-liquid of the refrigerant flowing into the inside, and stores excess refrigerant in the refrigeration cycle. And a gas-liquid separator (30).
  2. 　前記第１端板（１８）の重力方向下方部は、前記気液分離部（３０）に前記冷媒を流入させる冷媒流入部（１８１）を有し、
    　前記第２端板（１９）の重力方向下方部は、前記気液分離部（３０）から液相の前記冷媒を流出させる冷媒流出部（１９１）を有している請求項１に記載の積層型熱交換器。     The gravity direction lower part of the first end plate (18) has a refrigerant inflow part (181) for allowing the refrigerant to flow into the gas-liquid separation part (30),
    The lamination according to claim 1, wherein a lower part in the gravity direction of the second end plate (19) has a refrigerant outflow part (191) for allowing the liquid-phase refrigerant to flow out from the gas-liquid separation part (30). Mold heat exchanger.
  3. 　さらに、前記冷媒と第２熱媒体とを熱交換させる第２熱交換部（６２）を備え、
    　前記第２熱交換部（６２）は、
    　　互いに積層されて接合された複数の第２板状部材（６１）と、
    　　前記複数の第２板状部材（６１）の間に設けられた、前記冷媒が流れる複数の第２冷媒流路（６２１）と、
    　　前記複数の第２板状部材（６１）の間に設けられた、前記第２熱媒体が流れる複数の第２熱媒体流路（６２２、６２３）と、を含み、
    　前記複数の第２板状部材（６１）における前記冷媒の流れ方向の長さは、前記複数の第１板状部材（１１）における前記冷媒の流れ方向の長さよりも短くなっており、
    　前記第２熱交換部（６２）は、前記第２端板（１９）に接合されており、
    　前記第２冷媒流路（６２１）は、前記気液分離部（３０）と連通している請求項１または２に記載の積層型熱交換器。     And a second heat exchange part (62) for exchanging heat between the refrigerant and the second heat medium,
    The second heat exchange part (62)
    A plurality of second plate-like members (61) laminated and joined to each other;
    A plurality of second refrigerant flow paths (621) through which the refrigerant flows, provided between the plurality of second plate-like members (61);
    A plurality of second heat medium passages (622, 623) provided between the plurality of second plate-like members (61), through which the second heat medium flows,
    The length in the flow direction of the refrigerant in the plurality of second plate members (61) is shorter than the length in the flow direction of the refrigerant in the plurality of first plate members (11),
    The second heat exchange part (62) is joined to the second end plate (19),
    The stacked heat exchanger according to claim 1 or 2, wherein the second refrigerant channel (621) communicates with the gas-liquid separator (30).
  4. 　前記第１熱媒体および前記第２熱媒体は、冷却水であり、
    　前記気液分離部（３０）の内部に設けられて、前記冷却水が流通するとともに、前記第１熱媒体流路（１２２）と前記第２熱媒体流路（６２３）とを連通させる内部冷却水通路（８０）をさらに備える請求項３に記載の積層型熱交換器。     The first heat medium and the second heat medium are cooling water,
    Internal cooling provided inside the gas-liquid separator (30) to allow the cooling water to flow and to communicate the first heat medium flow path (122) and the second heat medium flow path (623). The stacked heat exchanger according to claim 3, further comprising a water passage (80).
  5. 　前記第２熱媒体は、前記第１熱交換部（１２）に流入する前記冷媒よりも圧力が低い低圧冷媒である請求項３に記載の積層型熱交換器。 The stacked heat exchanger according to claim 3, wherein the second heat medium is a low-pressure refrigerant whose pressure is lower than that of the refrigerant flowing into the first heat exchange section (12).
  6. 　前記気液分離部（３０）は内部に、前記第１熱交換部（１２）から流入した前記冷媒を外部へ流出させる冷媒通路と、前記第１熱交換部（１２）から流入した冷媒を前記第２熱交換部（６２）へ流出させる冷媒通路と、を有する請求項３に記載の積層型熱交換器。 The gas-liquid separation unit (30) includes a refrigerant passage through which the refrigerant flowing in from the first heat exchange unit (12) flows out to the outside, and a refrigerant flowing in from the first heat exchange unit (12). The laminated heat exchanger according to claim 3, further comprising a refrigerant passage that flows out to the second heat exchange section (62).
  7. 　前記気液分離部（３０）は、
    　　前記第１端板（１８）と前記第２端板（１９）との間の前記空間に配置されて、互いに積層されて接合された複数の第３板状部材（９１）と、
    　前記複数の第３板状部材（９１）間に設けられて、前記冷媒の気液を分離するとともに前記冷凍サイクル内の余剰冷媒を蓄える複数の気液分離通路（９２）と、を有し、
    　隣り合う前記気液分離通路（９２）同士は、互いに連通している請求項１ないし６のいずれか１つに記載の積層型熱交換器。     The gas-liquid separator (30)
    A plurality of third plate-like members (91) disposed in the space between the first end plate (18) and the second end plate (19) and laminated and joined to each other;
    A plurality of gas-liquid separation passages (92) provided between the plurality of third plate-like members (91) for separating the gas-liquid of the refrigerant and storing surplus refrigerant in the refrigeration cycle,
    The stacked heat exchanger according to any one of claims 1 to 6, wherein the adjacent gas-liquid separation passages (92) communicate with each other.
  8. 　さらに、前記冷媒と第２熱媒体とを熱交換させる第２熱交換部（６２）を備え、
    　前記第２熱交換部（６２）は、
    　　互いに積層されて接合され複数の第２板状部材（６１）と、
    　　前記複数の第２板状部材（６１）の間に設けられた、前記冷媒が流れる複数の第２冷媒流路（６２１）と、
    　　前記複数の第２板状部材（６１）の間に設けられた、前記第２熱媒体が流れる複数の第２熱媒体流路（６２２、６２３）と、を含み、
    　前記複数の第２板状部材（６１）における前記冷媒の流れ方向の長さは、前記複数の第１板状部材（１１）における前記冷媒の流れ方向の長さよりも短くなっており、
    　前記第２熱交換部（６２）は、前記第２端板（１９）に接合されており、
    　前記第２冷媒流路（６２１）は、前記気液分離部（３０）と連通しており、
    　前記第２端板（１９）は、前記第２熱交換部（６２）が接合されている部位以外の部位に、乾燥剤（９５）を前記気液分離部（３０）内に挿入するための挿入口（９６）を有する請求項１ないし２または４ないし７のいずれか１つに記載の積層型熱交換器。     And a second heat exchange part (62) for exchanging heat between the refrigerant and the second heat medium,
    The second heat exchange part (62)
    A plurality of second plate-like members (61) laminated and joined to each other;
    A plurality of second refrigerant flow paths (621) through which the refrigerant flows, provided between the plurality of second plate-like members (61);
    A plurality of second heat medium passages (622, 623) provided between the plurality of second plate-like members (61), through which the second heat medium flows,
    The length in the flow direction of the refrigerant in the plurality of second plate members (61) is shorter than the length in the flow direction of the refrigerant in the plurality of first plate members (11),
    The second heat exchange part (62) is joined to the second end plate (19),
    The second refrigerant channel (621) communicates with the gas-liquid separator (30),
    The second end plate (19) is for inserting a desiccant (95) into the gas-liquid separator (30) in a portion other than the portion where the second heat exchanging portion (62) is joined. The stacked heat exchanger according to any one of claims 1 to 2 or 4 to 7, further comprising an insertion port (96).
PCT/JP2015/002482 2014-05-23 2015-05-18 Stacked heat exchanger WO2015178005A1 (en)

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CN201580026632.8A CN106461298B (en) 2014-05-23 2015-05-18 Laminated type heat exchanger
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105716440A (en) * 2015-12-18 2016-06-29 广东工业大学 Plate type condenser with gas-liquid separation function
CN105737647A (en) * 2016-03-22 2016-07-06 江苏远卓设备制造有限公司 Plate heat exchanger for steam-water separation
CN106052430A (en) * 2016-07-11 2016-10-26 缪志先 Conjoined box-shaped laminating heat exchanger with gas-liquid separation devices
JP6177459B1 (en) * 2016-02-12 2017-08-09 三菱電機株式会社 Plate heat exchanger and refrigeration cycle equipment

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014204935A1 (en) * 2014-03-17 2015-10-01 Mahle International Gmbh Heizkühlmodul
JP2017172948A (en) * 2016-03-25 2017-09-28 パナソニックＩｐマネジメント株式会社 Heat exchanging unit and vehicle air conditioning device
CN106989543A (en) * 2017-05-02 2017-07-28 安徽江淮松芝空调有限公司 A kind of heat exchanger
US10935288B2 (en) * 2017-08-28 2021-03-02 Hanon Systems Condenser
FR3077379A1 (en) * 2018-01-29 2019-08-02 Valeo Systemes Thermiques PERTURBATION DEVICE FOR PLATE OF A HEAT EXCHANGER
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US11813924B2 (en) * 2018-07-24 2023-11-14 Hanon Systems Water-cooling type condenser
JP7188193B2 (en) * 2019-03-07 2022-12-13 株式会社デンソー Heat exchanger
EP3757503A1 (en) * 2019-06-26 2020-12-30 Valeo Autosystemy SP. Z.O.O. Heat exchanger with a connector
JP7400234B2 (en) * 2019-07-16 2023-12-19 株式会社デンソー Heat exchanger
CN114270115B (en) * 2019-08-08 2023-04-21 株式会社电装 Heat exchanger
JP6783369B2 (en) * 2019-11-07 2020-11-11 三菱重工サーマルシステムズ株式会社 Heat exchange system
KR102347839B1 (en) * 2020-09-29 2022-01-06 에스트라오토모티브시스템 주식회사 Heat exchanger for vehicles

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58179471U (en) * 1982-05-26 1983-12-01 カルソニックカンセイ株式会社 Mounting structure of liquid tank in irregularly shaped tubular capacitor
JPH0628561U (en) * 1992-09-10 1994-04-15 昭和アルミニウム株式会社 Heat exchanger
JPH08219588A (en) * 1994-02-16 1996-08-30 Nippondenso Co Ltd Liquid receiver integration type refrigerant condenser
JP2000205700A (en) * 1999-01-14 2000-07-28 Denso Corp Liquid receiver integrated type refrigerant condenser
WO2009065812A1 (en) * 2007-11-20 2009-05-28 Valeo Systemes Thermiques Condenser for air-conditioning circuit with built-in cylinder
US20120222846A1 (en) * 2011-02-17 2012-09-06 Delphi Technologies, Inc. Unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2412573A (en) * 1942-04-15 1946-12-17 Westinghouse Electric Corp Heat exchange apparatus
US5546761A (en) * 1994-02-16 1996-08-20 Nippondenso Co., Ltd. Receiver-integrated refrigerant condenser
JP2005321151A (en) * 2004-05-10 2005-11-17 Sanden Corp Heat exchanger
US8434324B2 (en) * 2010-04-05 2013-05-07 Denso Corporation Evaporator unit
JP5421933B2 (en) * 2011-01-12 2014-02-19 サンデン株式会社 Heat exchanger
JP5951381B2 (en) * 2012-07-17 2016-07-13 カルソニックカンセイ株式会社 Evaporator structure
KR101461871B1 (en) * 2012-10-19 2014-11-13 현대자동차 주식회사 Condenser for vehicle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58179471U (en) * 1982-05-26 1983-12-01 カルソニックカンセイ株式会社 Mounting structure of liquid tank in irregularly shaped tubular capacitor
JPH0628561U (en) * 1992-09-10 1994-04-15 昭和アルミニウム株式会社 Heat exchanger
JPH08219588A (en) * 1994-02-16 1996-08-30 Nippondenso Co Ltd Liquid receiver integration type refrigerant condenser
JP2000205700A (en) * 1999-01-14 2000-07-28 Denso Corp Liquid receiver integrated type refrigerant condenser
WO2009065812A1 (en) * 2007-11-20 2009-05-28 Valeo Systemes Thermiques Condenser for air-conditioning circuit with built-in cylinder
US20120222846A1 (en) * 2011-02-17 2012-09-06 Delphi Technologies, Inc. Unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105716440A (en) * 2015-12-18 2016-06-29 广东工业大学 Plate type condenser with gas-liquid separation function
JP6177459B1 (en) * 2016-02-12 2017-08-09 三菱電機株式会社 Plate heat exchanger and refrigeration cycle equipment
CN105737647A (en) * 2016-03-22 2016-07-06 江苏远卓设备制造有限公司 Plate heat exchanger for steam-water separation
CN106052430A (en) * 2016-07-11 2016-10-26 缪志先 Conjoined box-shaped laminating heat exchanger with gas-liquid separation devices

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CN106461298A (en) 2017-02-22
US20170122669A1 (en) 2017-05-04
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DE112015002434T5 (en) 2017-03-02
JP2016001099A (en) 2016-01-07

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