WO2015178005A1 - Échangeur de chaleur à empilement - Google Patents

Échangeur de chaleur à empilement 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
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English (en)
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 US15/309,219 priority Critical patent/US20170122669A1/en
Priority to CN201580026632.8A priority patent/CN106461298B/zh
Priority to DE112015002434.4T priority patent/DE112015002434T5/de
Publication of WO2015178005A1 publication Critical patent/WO2015178005A1/fr

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

Abstract

L'invention concerne un échangeur de chaleur à empilement comprenant une première unité d'échangeur de chaleur (12) qui échange de la chaleur entre de l'eau de refroidissement et un réfrigérant. La première unité d'échangeur de chaleur (12) comprend : une pluralité de premiers éléments en forme de plaque (11) qui sont empilés et assemblés; et une pluralité de premiers trajets d'écoulement de réfrigérant (121) et une pluralité de trajets d'écoulement d'eau de refroidissement (122) disposés entre la pluralité de premiers éléments en forme de plaque (11). La pluralité de premiers trajets d'écoulement de réfrigérant (121) et une pluralité de trajets d'écoulement d'eau de refroidissement (122) sont disposés dans le sens d'empilement de la pluralité de premiers éléments en forme de plaque (11). L'échangeur de chaleur à empilement comprend également une unité de séparation gaz-liquide (30) qui présente une première plaque supérieure (18) disposée sur le côté le plus extérieur dans le sens d'empilement de la pluralité de premiers éléments en forme de plaque (11), et une seconde plaque supérieure (19) reliée à la première plaque de supérieure (18), et un espace ménagé entre la première plaque supérieure (18) et la seconde plaque supérieure (19) qui sépare le gaz et le liquide du réfrigérant s'y écoulant et stocke le réfrigérant excédentaire dans un cycle de réfrigération. En conséquence, l'échangeur de chaleur à empilement comprend une unité de séparation gaz-liquide qui sépare le gaz et le liquide du réfrigérant présentant une plus grande compacité de corps et présente un espace mort de montage réduit.
PCT/JP2015/002482 2014-05-23 2015-05-18 Échangeur de chaleur à empilement WO2015178005A1 (fr)

Priority Applications (3)

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US15/309,219 US20170122669A1 (en) 2014-05-23 2015-05-18 Stacked heat exchanger
CN201580026632.8A CN106461298B (zh) 2014-05-23 2015-05-18 层叠型热交换器
DE112015002434.4T DE112015002434T5 (de) 2014-05-23 2015-05-18 Stapelwärmetauscher

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JP2014-107117 2014-05-23
JP2014107117 2014-05-23
JP2014-221497 2014-10-30
JP2014221497A JP6222042B2 (ja) 2014-05-23 2014-10-30 積層型熱交換器

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WO2015178005A1 true WO2015178005A1 (fr) 2015-11-26

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JP (1) JP6222042B2 (fr)
CN (1) CN106461298B (fr)
DE (1) DE112015002434T5 (fr)
WO (1) WO2015178005A1 (fr)

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CN105716440A (zh) * 2015-12-18 2016-06-29 广东工业大学 一种具有气液分离功能的板式冷凝器
CN105737647A (zh) * 2016-03-22 2016-07-06 江苏远卓设备制造有限公司 一种用于汽水分离的板式换热器
CN106052430A (zh) * 2016-07-11 2016-10-26 缪志先 一种带有气液分离装置的联体盒形层叠换热器
JP6177459B1 (ja) * 2016-02-12 2017-08-09 三菱電機株式会社 プレート式熱交換器および冷凍サイクル装置

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DE102014204935A1 (de) * 2014-03-17 2015-10-01 Mahle International Gmbh Heizkühlmodul
JP2017172948A (ja) * 2016-03-25 2017-09-28 パナソニックＩｐマネジメント株式会社 熱交換ユニットおよび車両用空調装置
CN106989543A (zh) * 2017-05-02 2017-07-28 安徽江淮松芝空调有限公司 一种换热器
US10935288B2 (en) * 2017-08-28 2021-03-02 Hanon Systems Condenser
FR3077379A1 (fr) * 2018-01-29 2019-08-02 Valeo Systemes Thermiques Dispositif de perturbation pour plaque d'un echangeur de chaleur
EP3572753B1 (fr) 2018-05-24 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
EP3572754B1 (fr) 2018-05-24 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
DE112019003749T5 (de) * 2018-07-24 2021-04-08 Hanon Systems Kondensator vom wassergekühlten typ
JP7188193B2 (ja) * 2019-03-07 2022-12-13 株式会社デンソー 熱交換器
EP3757503A1 (fr) * 2019-06-26 2020-12-30 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur doté d'un connecteur
JP7400234B2 (ja) * 2019-07-16 2023-12-19 株式会社デンソー 熱交換器
CN114270115B (zh) * 2019-08-08 2023-04-21 株式会社电装 热交换器
JP6783369B2 (ja) * 2019-11-07 2020-11-11 三菱重工サーマルシステムズ株式会社 熱交換システム
KR102347839B1 (ko) * 2020-09-29 2022-01-06 에스트라오토모티브시스템 주식회사 차량용 열 교환기

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JP6177459B1 (ja) * 2016-02-12 2017-08-09 三菱電機株式会社 プレート式熱交換器および冷凍サイクル装置
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JP2016001099A (ja) 2016-01-07
CN106461298A (zh) 2017-02-22
US20170122669A1 (en) 2017-05-04
CN106461298B (zh) 2018-11-16
JP6222042B2 (ja) 2017-11-01
DE112015002434T5 (de) 2017-03-02

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