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WO2018047299A1 - Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2018047299A1
WO2018047299A1 PCT/JP2016/076641 JP2016076641W WO2018047299A1 WO 2018047299 A1 WO2018047299 A1 WO 2018047299A1 JP 2016076641 W JP2016076641 W JP 2016076641W WO 2018047299 A1 WO2018047299 A1 WO 2018047299A1
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WO
WIPO (PCT)
Prior art keywords
plate
flow path
heat transfer
heat
heat exchanger
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2016/076641
Other languages
English (en)
Japanese (ja)
Inventor
悟 梁池
加藤　央平
進一 内野
美藤　尚文
博和 南迫
正純 知崎
浩平 葛西
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP16915717.9A priority Critical patent/EP3511666B1/fr
Priority to PCT/JP2016/076641 priority patent/WO2018047299A1/fr
Priority to JP2018537951A priority patent/JPWO2018047299A1/ja
Publication of WO2018047299A1 publication Critical patent/WO2018047299A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F28D9/0093—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
    • 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
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations

Definitions

  • the present invention relates to a plate heat exchanger and a refrigeration cycle apparatus, and more particularly to a plate heat exchanger having a plurality of heat exchange areas and a refrigeration cycle apparatus including the plate heat exchanger.
  • a plate type heat exchanger having a plurality of heat exchange areas is known.
  • Such a plate heat exchanger is described in, for example, Japanese Patent Application Laid-Open No. 2005-106385 (Patent Document 1).
  • the plate heat exchanger described in this publication has two heat exchange areas (condensing unit and subcooling unit) that are divided based on the state of the refrigerant.
  • the flow path is provided.
  • the refrigerant flow path is provided with a liquid receiver disposed outside the heat exchanger between the condensing unit and the supercooling unit.
  • the fluid to be heated is heat-exchanged with the refrigerant that has been condensed in the condensing unit and then liquefied in the liquid receiver, and then the superheated refrigerant and heat before being supplied to the liquid receiver in the condensing unit. Exchanged.
  • the plate heat exchanger has a boundary plate (partition plate) that separates the condensing part and the supercooling part.
  • the flow path of the fluid to be heated positioned closest to the supercooling section in the condensing section is provided so as to be adjacent to the refrigerant flow path positioned closest to the condensing section in the supercooling section via the boundary plate.
  • the pressure difference can fluctuate repeatedly depending on the operating conditions of the refrigeration cycle apparatus. This is because the pressure of the refrigerant can fluctuate depending on the operating conditions and the load, while the heated fluid has a smaller pressure fluctuation depending on the operating conditions than the refrigerant.
  • the partition plate which repeatedly received the pressure difference variation has a problem that it repeatedly undergoes minute deformation and is damaged by fatigue.
  • the plate heat exchanger has a problem that the partition plate has a high risk of breakage and is not sufficiently reliable.
  • the main object of the present invention is to provide a plate heat exchanger and a refrigeration cycle apparatus in which breakage of the partition plate is suppressed and sufficiently high reliability is provided.
  • the plate heat exchanger includes a first heat exchange unit and a second heat exchange unit including a plurality of heat transfer plates stacked in a first direction, and a first heat exchange unit and a second heat exchanger in the first direction. It is arranged between the heat exchange unit, the first side in the first direction faces the heat transfer plate of the first heat exchange unit, and the second side faces the heat transfer plate of the second heat exchange unit. And a partition plate.
  • the first heat exchange unit includes a first flow path in which the first fluid flows in a second direction intersecting the first direction and a second flow path in which the second fluid flows in a third direction intersecting the first direction. Including.
  • a first flow path or a second flow path is provided between adjacent heat transfer plates in the first direction among the plurality of heat transfer plates.
  • the first flow path and the second flow path are alternately provided in the first direction.
  • the second heat exchange unit includes a third flow path in which the first fluid flows in a fourth direction intersecting the first direction and a fourth flow path in which the third fluid flows in a fifth direction intersecting the first direction.
  • a third flow path or a fourth flow path is provided between the heat transfer plates adjacent in the first direction among the plurality of heat transfer plates.
  • the third flow path and the fourth flow path are alternately provided in the first direction.
  • the partition plate is provided with a circulation port for allowing the first fluid to flow from the first flow path to the third flow path.
  • the distance from at least a part of the first flow path to the partition plate is shorter than the distance from the second flow path to the partition plate.
  • the distance from at least a part of the third flow path to the partition plate is shorter than the distance from the fourth flow path to the partition plate.
  • FIG. 1 is a perspective view which shows the plate type heat exchanger which concerns on Embodiment 1 from one entrance / exit plate side
  • (b) is the plate type heat exchanger which concerns on Embodiment 1 from the other entrance / exit plate side.
  • FIG. 3 is a diagram illustrating an example of a flow path of each fluid in the plate heat exchanger according to Embodiment 1.
  • FIG. 2 is an exploded view showing an example of the configuration of a plate heat exchanger according to Embodiment 1.
  • FIG. 4 is a plan view showing an example of a first heat transfer plate of the plate heat exchanger according to Embodiment 1.
  • FIG. 4 is a plan view showing an example of a partition plate of the plate heat exchanger according to Embodiment 1.
  • FIG. It is a side view of the partition plate shown in FIG. It is a fragmentary sectional view along the longitudinal direction of a partition plate which shows an example of the partition plate of the plate-type heat exchanger which concerns on Embodiment 1, and a heat-transfer plate arrange
  • 3 is a plan view showing an example of a first entrance / exit plate of the plate heat exchanger according to Embodiment 1.
  • FIG. It is a side view of the 1st entrance / exit plate shown in FIG. 4 is a plan view showing an example of a second entrance / exit plate of the plate heat exchanger according to Embodiment 1.
  • FIG. 1st entrance / exit plate It is a side view of the 1st entrance / exit plate shown in FIG. It is the schematic which shows an example of the refrigerating-cycle apparatus provided with the plate type heat exchanger which concerns on Embodiment 1.
  • FIG. It is an exploded view which shows an example of a structure of the plate type heat exchanger which concerns on Embodiment 2.
  • FIG. It is sectional drawing which shows an example of the 2nd flow path formed near the 1st entrance / exit plate of the plate type heat exchanger which concerns on Embodiment 2.
  • FIG. 6 is a cross-sectional view showing an example of a first entrance / exit plate of a plate heat exchanger according to Embodiment 3.
  • FIG. 6 is sectional drawing which shows an example of the 2nd entrance / exit plate of the plate type heat exchanger which concerns on Embodiment 3.
  • FIG. It is sectional drawing which shows the other example of the partition plate of the plate type heat exchanger which concerns on Embodiment 3.
  • FIG. 6 is a cross-sectional view showing an example of a first entrance / exit plate of a plate heat exchanger according to Embodiment 3.
  • FIG. It is sectional drawing which shows an example of the 2nd entrance / exit plate of the plate type heat exchanger which concerns on Embodiment 3.
  • FIG. is sectional drawing which shows the other example of the partition plate of the plate type heat exchanger which concerns on Embodiment 3.
  • FIG. ⁇ Plate type heat exchanger> As shown in FIGS. 1 to 3, a plate heat exchanger 100 according to Embodiment 1 will be described.
  • the plate heat exchanger 100 includes a first heat exchange unit 10 and a second heat exchange unit 20 including a plurality of heat transfer plates 1 stacked in the first direction, and a partition plate 2.
  • the first heat exchange unit 10 is provided so that the first fluid and the second fluid can exchange heat via the heat transfer plate 1.
  • the first flow path 5 flows in the second direction where the first fluid intersects the first direction, and the second fluid flows in the first direction.
  • the second flow paths 6 that flow in the third direction intersecting with are alternately provided.
  • the first flow path 5 and the second flow path 6 are arranged so as to be adjacent to each other with one heat transfer plate 1 interposed therebetween.
  • a plurality of first flow paths 5 and second flow paths 6 may be provided.
  • the first fluid flows through the distribution holes 61 extending in the first direction through the passage holes 11 and 13 of the heat transfer plate 1 to be described later. Distributed to path 5. Further, the first fluid distributed to each first flow path 5 flows into and merges with a distribution path 62 extending along the first direction through the passage holes 12 and 15 of the heat transfer plate 1 described later.
  • the second fluid flows through the distribution paths 63 extending along the first direction through the passage holes 11 and 13 of the heat transfer plate 1 to be described later. Distributed to path 6; Further, the second fluid distributed to each second flow path 6 flows into and merges with a distribution path 64 extending along the first direction through the passage holes 12 and 15 of the heat transfer plate 1 described later.
  • the second heat exchange unit 20 is provided so that the first fluid and the third fluid can exchange heat via the heat transfer plate 1.
  • the third flow path 7 flows in the fourth direction in which the first fluid intersects the first direction, and the third fluid flows in the first direction.
  • the fourth flow paths 8 that flow in the fifth direction intersecting with are alternately provided.
  • the third flow path 7 and the fourth flow path 8 are arranged adjacent to each other with one heat transfer plate 1 interposed therebetween.
  • a plurality of third flow paths 7 and fourth flow paths 8 may be provided.
  • the first fluid passes through the distribution holes 65 extending in the first direction through the passage holes 12 and 15 of the heat transfer plate 1 to be described later. Distributed to the road 7; Further, the first fluid distributed to each second flow path 7 flows into and merges with a distribution path 66 extending along the first direction through the passage holes 11 and 13 of the heat transfer plate 1 described later.
  • the third fluid passes through a distribution path 67 extending in the first direction through the passage holes 11, 12, 13, 15 of the heat transfer plate 1 described later. Each of the fourth flow paths 8 is distributed. Further, the third fluid distributed to each of the fourth flow paths 8 flows into and merges with a distribution path 68 extending along the first direction through the passage holes 11 and 13 of the heat transfer plate 1 described later.
  • the partition plate 2 is disposed between the first heat exchange unit 10 and the second heat exchange unit 20 in the first direction.
  • the partition plate 2 has a first side in the first direction (hereinafter referred to as the front side) facing the heat transfer plate 1 of the first heat exchange unit 10 and a second side (hereinafter referred to as the rear side). 2 faces the heat transfer plate 1 of the heat exchange unit 20.
  • the partition plate 2 has a circulation port 21 (see FIG. 3) through which the first fluid flows from the first flow path 5 in the first heat exchange unit 10 to the third flow path 7 in the second heat exchange unit 20. Is provided.
  • the first flow path 5 has a first portion 5A located closer to the partition plate 2 than the second flow path 6.
  • the first flow path 5 has a first portion 5A located closer to the partition plate 2 than the second portion 6A located closest to the partition plate 2 in the second flow path 6.
  • the first portion 5A that is closest to the partition plate 2 in the first flow path 5 is the second portion that is closest to the partition plate 2 in the second flow path 6. It is closer to the partition plate 2 than 6A.
  • the third flow path 7 has a third portion 7A located closer to the partition plate 2 than the fourth flow path 8.
  • the third flow path 7 has a third portion 7A located closer to the partition plate 2 than the fourth portion 8A located closest to the partition plate 2 in the fourth flow path 8.
  • the third portion 7A that is closest to the partition plate 2 in the third flow path 7 is closer to the partition plate 2 than the fourth portion 8A that is closest to the partition plate 2 in the fourth flow path 8. close.
  • the first portion 5A located closest to the partition plate 2 in the first flow path 5 is a third portion located closest to the partition plate 2 in the third flow path 7 via the flow port 21 of the partition plate 2. 7A is connected.
  • the first fluid flowing in the first flow path 5 and the first flow in the third flow path 7 are provided in the partition plate 2 that partitions the first heat exchange unit 10 and the second heat exchange unit 20.
  • a pressure difference with the fluid is applied.
  • the first fluid flowing through the third flow path 7 is the first fluid that has flowed through the first flow path 5 and reaches the third flow path 7 through the flow port 21 of the partition plate 2. Therefore, the pressure difference between the first fluid flowing in the first flow path 5 and the first fluid flowing in the third flow path 7 is the pressure difference between the first fluid and the second fluid, and the first fluid and the third fluid.
  • the pressure difference and the pressure difference between the second fluid and the third fluid are small. Therefore, the plate heat exchanger 100 has sufficiently high reliability because the partition plate 2 is prevented from being damaged.
  • the first direction is, for example, a direction along the horizontal direction.
  • the second direction, the third direction, the fourth direction, and the fifth direction are, for example, directions along the vertical direction.
  • the plate heat exchanger 100 includes a plurality of heat transfer plates 1, a partition plate 2, a first entrance / exit plate 3, and a second entrance / exit plate 4.
  • the 1st entrance / exit plate 3 is arrange
  • the 2nd entrance / exit plate 4 is arrange
  • the planar shape of the heat transfer plate 1, the partition plate 2, the first entrance / exit plate 3, and the second entrance / exit plate 4 is, for example, a substantially rectangular shape.
  • passage holes 11, 12, 13 for circulating any one of the first fluid to the third fluid are provided in the outer peripheral portion (four corners) of each heat transfer plate 1. , 15 are provided.
  • the passage holes 11, 12, 13, 15 penetrate the heat transfer plate 1 in the thickness direction (the first direction).
  • the passage hole 11 and the passage hole 12, and the passage hole 13 and the passage hole 15 are provided so as to face each other with an interval in the longitudinal direction of the heat transfer plate 1.
  • the passage hole 11 and the passage hole 15, and the passage hole 12 and the passage hole 13 are provided so as to face each other with an interval in the short direction of the heat transfer plate 1.
  • the passage holes 13 and 15 are provided on the top surfaces of the convex portions 14 and 16 protruding in the thickness direction from the surface on which the passage holes 11 and 12 are provided.
  • the top surfaces of the convex portions 14 and 16 are in contact with the other heat transfer plate 1, the partition plate 2, or the first entrance / exit plate 3 adjacent on the front side in the first direction.
  • the heat transfer plate 1 is provided with a heat transfer surface 17 having, for example, a wavy cross-sectional shape inside the passage holes 11, 12, 13, and 15.
  • the top portion 18 and the bottom portion 19 of the wave-like structure of the heat transfer surface 17 form, for example, a herringbone pattern when the heat transfer surface 17 is viewed in plan.
  • the first heat exchange unit 10 includes heat transfer plates 1 a, 1 b, 1 c, and 1 d in the order closer to the partition plate 2.
  • the second heat exchange unit 20 includes heat transfer plates 1e, 1f, 1g, and 1h in the order closer to the partition plate 2.
  • Each of the heat transfer plates 1a, 1b, 1c, 1d, 1e, 1f, 1g, and 1h has the same configuration.
  • each of the plurality of heat transfer plates 1 is stacked, for example, alternately upside down.
  • the passage hole 11 of a certain heat transfer plate 1c is provided, for example, so as to overlap with the passage holes 13 of the heat transfer plates 1b and 1d adjacent to the heat transfer plate 1c in the first direction.
  • the passage hole 12 of a certain heat transfer plate 1c is provided, for example, so as to overlap with the passage holes 15 of the heat transfer plates 1b and 1d adjacent to the heat transfer plate 1c in the first direction.
  • each of the plurality of heat transfer plates 1 is laminated, for example, alternately upside down.
  • the passage hole 12 of the heat transfer plate 1a is provided so as to overlap the passage hole 15 of the heat transfer plate 1e and the flow port 21 of the partition plate 2 in the first direction.
  • the heat transfer plates 1a, 1b, 1c and 1d have a first flow path between the heat transfer plate 1a and the heat transfer plate 1b and between the heat transfer plate 1c and the heat transfer plate 1d.
  • 5 and the second flow path 6 is provided between the heat transfer plate 1b and the heat transfer plate 1c.
  • the heat transfer plates 1e, 1f, 1g, and 1h are the third flow path 7 between the heat transfer plate 1e and the heat transfer plate 1f, and between the heat transfer plate 1g and the heat transfer plate 1h, and heat transfer The fourth flow path 8 is provided between the plate 1f and the heat transfer plate 1g and between the heat transfer plate 1h and the heat transfer plate 1i.
  • one distribution port 21 for distributing the first fluid is provided on the outer peripheral portion of the partition plate 2.
  • the partition plate 2 is provided with a flat portion 24 that overlaps the heat transfer surface 17 of the heat transfer plate 1 adjacent in the first direction.
  • the circulation port 21 is provided so as to overlap with the passage holes 12 of the heat transfer plates 1 a and 1 e adjacent to the partition plate 2.
  • the first flow path 5 of the first heat exchange unit 10 and the third flow path 7 of the second heat exchange unit 20 are connected via a circulation port 21.
  • the partition plate 2 is provided with a circulation port 21 on the top surface of the convex portion 22 projecting in the thickness direction (the first direction) rather than the flat portion 24.
  • the partition plate 2 is provided with a convex portion 23 protruding in the thickness direction in the same manner as the convex portion 22 on the outer peripheral portion located on the opposite side of the convex portion 22 in the longitudinal direction.
  • the convex portion 23 is disposed above the convex portion 22.
  • the top surface of the convex portion 22 is in contact with a portion where the passage hole 12 of the adjacent heat transfer plate 1a is provided on the front side in the first direction.
  • the top surface of the convex portion 23 is in contact with a portion where the passage hole 11 of the adjacent heat transfer plate 1a is provided on the front side in the first direction.
  • the partition plate 2 is fixed to the heat transfer plate 1a and the heat transfer plate 1e.
  • the bottom portion 19 of the heat transfer plate 1a is fixed to a surface located on the front side of the flat portion 24 of the partition plate 2, and is brazed, for example.
  • the top portion 18 of the heat transfer plate 1e is fixed to a surface of the partition plate 2 located on the rear side of the flat portion 24, and is brazed, for example.
  • the space provided between the top portion 18 of the heat transfer plate 1a and the flat portion 24 of the partition plate 2 is closed and does not constitute the first flow path 5 and the second flow path 6.
  • the space provided between the bottom portion 19 of the heat transfer plate 1e and the flat portion 24 of the partition plate 2 is closed and does not constitute the third flow path 7 and the fourth flow path 8.
  • the flow path provided closest to the partition plate 2 includes the heat transfer plate 1 a facing the partition plate 2, It is provided between the heat transfer plate 1a and the heat transfer plate 1b adjacent in the first direction. Between the heat-transfer plate 1a and the heat-transfer plate 1b, it is provided so that it may become the 1st part 5A located closest to the partition plate 2 in the 1st flow path 5. Between the heat transfer plate 1b and the heat transfer plate 1c, the second flow path 6 is provided so as to be the second portion 6A located closest to the partition plate 2.
  • the flow path provided closest to the partition plate 2 includes the heat transfer plate 1 e facing the partition plate 2, It is provided between the heat transfer plate 1e and the heat transfer plate 1f adjacent in the first direction. Between the heat transfer plate 1e and the heat transfer plate 1f, the third flow path 7 is provided so as to be the third portion 7A located closest to the partition plate 2. Between the heat transfer plate 1f and the heat transfer plate 1g, the fourth flow path 8 is provided so as to be the fourth portion 8A located closest to the partition plate 2.
  • the first inlet 31, the second inlet 32, and the second outlet for circulating the first fluid or the second fluid are disposed in the outer peripheral portion of the first inlet / outlet plate 3.
  • 33 is provided.
  • the first inlet 31, the second inlet 32, and the second outlet 33 penetrate the first inlet / outlet plate 3 in the thickness direction (the first direction).
  • the first inflow port 31 and the second outflow port 33 are provided to face each other with an interval in the short direction of the heat transfer plate 1.
  • the 2nd inflow port 32 and the 2nd outflow port 33 are provided so that it may oppose at intervals in the longitudinal direction of the heat exchanger plate 1.
  • the first inlet 31 and the second outlet 33 are preferably disposed above the second inlet 32.
  • the first inflow port 31 is preferably provided above the circulation port 21 of the partition plate 2.
  • the first inlet / outlet plate 3 includes a first inlet 31, a second inlet 32, an outer periphery provided with the second outlet 33, and the first inlet 31,
  • the center part located inside the 2nd inflow port 32 and the 2nd outflow port 33 is provided flat in side view.
  • the first entrance / exit plate 3 is provided with a flat portion 34 that overlaps the heat transfer surface 17 of the heat transfer plate 1 adjacent in the first direction.
  • a first outlet 41, a third inlet 42, and a third outlet for allowing the first fluid or the third fluid to flow through the outer peripheral portion of the second inlet / outlet plate 4. 43 is provided.
  • the first outlet 41, the third inlet 42, and the third outlet 43 penetrate the second inlet / outlet plate 4 in the thickness direction (the first direction).
  • the 1st outflow port 41 and the 3rd outflow port 43 are provided so that it may oppose with a space
  • the 3rd inflow port 42 and the 3rd outflow port 43 are provided so that it may oppose at intervals in the longitudinal direction of the heat exchanger plate 1.
  • the first outlet 41 and the third outlet 43 are disposed above the third inlet 42.
  • the first outlet 41 is preferably provided above the circulation port 21 of the partition plate 2.
  • the second inlet / outlet plate 4 includes an outer peripheral portion provided with the first outlet 41, the third inlet 42, and the third outlet 43, the first outlet 41, and the first outlet 41.
  • a central portion located inside the three inlets 42 and the third outlets 43 is provided flat in a side view.
  • the second entrance / exit plate 4 is provided with a flat portion 44 that overlaps the heat transfer surface 17 of the heat transfer plate 1 adjacent in the first direction.
  • the first inlet / outlet plate 3 has a first inlet 31 through which the first fluid flows into the first flow path 5 and a second fluid flows into the second flow path 6. It is preferable that a second inflow port 32 to be discharged and a second outflow port 33 for the second fluid to flow out from the second flow path 6 are provided.
  • the second inlet 32 is preferably provided below the second outlet 33.
  • the second direction is preferably a direction from the top to the bottom, and the third direction is preferably a direction from the bottom to the top.
  • the first fluid flowing through the first flow path 5 is condensed by exchanging heat with the second fluid flowing through the second flow path 6 (details will be described later).
  • the first fluid that has been sufficiently heat-exchanged with the second fluid has a higher density than the first fluid that has not been sufficiently heat-exchanged with the second fluid. Therefore, when the first fluid flows through the first flow path 5 from below to above, the flow of the first fluid sufficiently exchanged with the second fluid so as to oppose the flow of the first fluid ( Downflow) occurs in the first flow path 5.
  • the flow of the first fluid in the first flow path 5 is inhibited by the downward flow, and the heat exchange efficiency of the plate heat exchanger is reduced.
  • the first fluid is condensed when it flows through the first flow path 5 from the upper side to the lower side.
  • the flow is not disturbed by the downflow.
  • the plate heat exchanger 100 the decrease in heat exchange efficiency is suppressed.
  • the second inlet / outlet plate 4 has a first outlet 41 through which the first fluid flows out from the third flow path 7 and the third fluid flows into the fourth flow path 8.
  • the third inflow port 42 to be discharged and the third outflow port 43 for the third fluid to flow out from the fourth flow path 8 are provided.
  • the third inlet 42 is preferably provided below the third outlet 43.
  • the fifth direction is preferably a direction from the bottom to the top.
  • the third fluid flowing into the fourth flow path 8 is in a gas-liquid two-phase state (details will be described later).
  • the third fluid flows through the fourth channel 8 from above to below, the third fluid is a plurality of heat transfer configured as the fourth channel 8 above the heat transfer surface 17 of the heat transfer plate 1. Distributed between the surfaces 17.
  • the liquid refrigerant of the third fluid has a higher density than the gas-phase refrigerant and tends to flow downward, so the third fluid is evenly distributed between the plurality of heat transfer surfaces 17 constituting the fourth flow path 8. Difficult to distribute.
  • the plate heat exchanger 100 can be applied to a refrigeration cycle apparatus 200 as shown in FIG.
  • the refrigeration cycle apparatus 200 includes a plate heat exchanger 100 configured as a condenser, a compressor 51, an expansion valve 52, an evaporator 53, an injection expansion valve 54, a pump 55, and a fan 56. Prepare.
  • the refrigeration cycle apparatus 200 includes a compressor 51, a first flow path 5, a third flow path 7, and a fourth flow path 8 of the plate heat exchanger 100, an expansion valve 52, and an evaporator 53 connected in order. Provide a circuit. Further, the refrigeration cycle apparatus 200 is branched from the refrigerant circuit downstream of the third flow path 7, and the injection expansion valve 54, the fourth flow path 8, and the intermediate pressure part of the compressor 51 are connected in order. Is provided. Furthermore, the refrigeration cycle apparatus 200 includes a heat medium circuit in which the pump 55 and the second flow path 6 are sequentially connected. That is, in the refrigeration cycle apparatus 200, the first fluid and the third fluid are refrigerants, and the second fluid is a heat medium such as water or brine. The first fluid is a high-pressure gas refrigerant, and the third fluid is a low-pressure gas-liquid two-phase refrigerant.
  • the first inlet 31 of the first inlet / outlet plate 3 is provided as an inlet for the first fluid.
  • the second inlet 32 of the first inlet / outlet plate 3 is provided as an inlet for the second fluid.
  • the second outlet 33 of the first inlet / outlet plate 3 is provided as an outlet for the second fluid.
  • the first outlet 41 of the second inlet / outlet plate 4 is provided as an outlet for the first fluid.
  • the third inlet 42 of the second inlet / outlet plate 4 is provided as an inlet for the third fluid.
  • the third outlet 43 of the second inlet / outlet plate 4 is provided as an outlet for the third fluid.
  • the first fluid flows into the first heat exchange unit 10 from the first inlet 31 of the first inlet / outlet plate 3, and flows between the heat transfer plates 1a and 1b and between the heat transfer plates 1c and 1d from above to below.
  • the second fluid flows into the first heat exchange unit 10 from the second inlet 32 of the first inlet / outlet plate 3 and flows between the heat transfer plates 1b and 1c from below to above.
  • a 1st fluid and a 2nd fluid are heat-exchanged via the heat exchanger plates 1b and 1c.
  • the second fluid that has exchanged heat with the first fluid flows out of the first heat exchange unit 10 through the second outlet 33 of the first inlet / outlet plate 3.
  • the first fluid exchanged with the second fluid flows into the second heat exchange unit 20 through the flow port 21 of the partition plate 2.
  • the first fluid that has flowed into the second heat exchange unit 20 flows from the lower side to the upper side between the heat transfer plates 1e and 1f and between the heat transfer plates 1g and 1h.
  • the third fluid flows into the second heat exchange unit 20 from the third inlet 42 of the second inlet / outlet plate 4 and circulates between the heat transfer plates 1f and 1g and between the heat transfer plates 1h and 1i from below to above. .
  • the 1st fluid and the 3rd fluid are heat-exchanged via heat transfer plates 1f, 1g, 1g, and 1i.
  • the refrigerant as the first fluid discharged from the compressor 51 flows through the first flow path 5 in the first heat exchange unit 10 of the plate heat exchanger 100, thereby causing the second flow.
  • Heat exchange with the heat medium as the second fluid flowing through the path 6 condenses.
  • the condensed refrigerant is supercooled by exchanging heat with the refrigerant as the third fluid flowing through the fourth flow path 8 by flowing through the third flow path 7 in the second heat exchange unit 20.
  • a part of the supercooled refrigerant is decompressed by the expansion valve 52.
  • the decompressed refrigerant evaporates by exchanging heat with the gas supplied by the fan 56 in the evaporator 53.
  • the evaporated refrigerant is sucked into the compressor 51.
  • the remainder other than the part of the refrigerant that has been supercooled through the third flow path 7 flows into the injection circuit.
  • the refrigerant flowing into the injection circuit is decompressed by the injection expansion valve 54.
  • the decompressed refrigerant flows through the fourth flow path 8 in the second heat exchange unit 20, and is heated by exchanging heat with the refrigerant flowing through the third flow path 7.
  • the refrigeration cycle apparatus 200 includes an injection circuit, an increase in the temperature of the refrigerant discharged from the compressor 51 can be suppressed.
  • the refrigeration cycle apparatus 200 includes a refrigerant circuit for exchanging heat between the first fluid and the second fluid and exchanging heat between the first fluid and the third fluid.
  • the refrigerant circuit is plate-type heat exchange.
  • the thickness of the partition plate 2 in the first direction may be smaller than the thickness of the heat transfer plate 1 in the first direction.
  • a pressure difference between the first fluid flowing through the first flow path 5 and the second fluid flowing through the second flow path 6 is applied to the heat transfer plate 1.
  • a pressure difference between the first fluid flowing through the first flow path 5 and the first fluid flowing through the third flow path 7 is applied to the partition plate 2. Therefore, the pressure difference applied to the partition plate 2 is smaller than the pressure difference applied to the heat transfer plate 1.
  • the vessel 100 can be highly reliable.
  • the first flow path 5 is formed only between the heat transfer plates 1a, 1b. In this case, the entire first flow path 5 is located closer to the partition plate 2 than the second flow path 6 formed between the heat transfer plates 1b and 1c.
  • the plate heat exchanger 101 according to the second embodiment basically has the same configuration as the plate heat exchanger 100 according to the first embodiment, but at least a part of the second flow path 6 is the first. It is located closer to the first entrance / exit plate 3 than the flow path 5, and at least a part of the fourth flow path 8 is located closer to the second entrance / exit plate 4 than the third flow path 7.
  • the second flow path 6 has a sixth portion 6B located closer to the first entrance / exit plate 3 than the fifth portion 5B located closest to the first entrance / exit plate 3 in the first flow path 5. is doing.
  • the fourth flow path 8 has an eighth portion 8B located closer to the second entrance / exit plate 4 than the seventh portion 7B located closest to the second entrance / exit plate 4 in the third flow path 7. .
  • the first entrance / exit plate 3 is fixed to the heat transfer plate 1j.
  • the top portion 18 of the heat transfer plate 1j is fixed to a surface of the first entrance / exit plate 3 located on the rear side of the flat portion 34, and is brazed, for example.
  • the space provided between the flat portion 34 of the first entrance / exit plate 3 and the bottom portion 19 of the heat transfer plate 1j is closed and does not constitute the first flow path 5 and the second flow path 6.
  • the second entrance / exit plate 4 is fixed to the heat transfer plate 1i.
  • the bottom portion 19 of the heat transfer plate 1i is fixed to a surface of the second entrance / exit plate 4 that is located on the front side of the flat portion 44, and is brazed, for example.
  • a space provided between the flat portion 44 of the second entrance / exit plate 4 and the top portion 18 of the heat transfer plate 1 i is closed and does not constitute the third flow path 7 and the fourth flow path 8.
  • the flow path provided closest to the first inlet / outlet plate 3 is between the heat transfer plate 1j and the heat transfer plate 1d. Is provided. Between the heat transfer plate 1j and the heat transfer plate 1d, the second flow path 6 is provided so as to be the sixth portion 6B located closest to the first entrance / exit plate 3. Between the heat transfer plate 1d and the heat transfer plate 1c, the first flow path 5 is provided so as to be the fifth portion 5B located closest to the first entrance / exit plate 3.
  • the flow path provided closest to the second entrance / exit plate 4 is between the heat transfer plate 1 h and the heat transfer plate 1 i. Is provided.
  • the fourth flow path 8 is provided so as to be the eighth portion 8B located closest to the second entrance / exit plate 4.
  • the third flow path 7 is provided so as to be the seventh portion 7B located closest to the second entrance / exit plate 4.
  • the plate heat exchanger 101 according to the second embodiment having such a configuration has basically the same configuration as the plate heat exchanger 100 according to the first embodiment, Similar effects can be achieved.
  • the plate heat exchanger 101 includes a first entrance / exit plate 3 disposed so as to sandwich the partition plate 2 and the first heat exchange unit 10 in the first direction, and the partition plate 2 and the second heat in the first direction. And a second entrance / exit plate 4 disposed so as to sandwich the exchange unit 20.
  • the second flow path 6 has a sixth portion 6B located closer to the first entrance / exit plate 3 than the fifth part 5B located closest to the first entrance / exit plate 3 in the first flow path 5.
  • the fourth flow path 8 has an eighth portion 8B located closer to the second entrance / exit plate 4 than the seventh portion 7B located closest to the second entrance / exit plate 4 in the third flow path 7. .
  • the pressure of the second fluid flowing through the second flow path 6 and the pressure of the gas surrounding the outside of the plate heat exchanger 101 are applied to the first inlet / outlet plate 3 of the plate heat exchanger 101.
  • the difference is applied.
  • the pressure of the second fluid flowing through the second flow path 6 is the pressure of the first fluid flowing through the first flow path 5.
  • the difference between the pressure of the first fluid flowing through the first flow path 5 and the pressure of the gas surrounding the plate heat exchanger 101 is the first.
  • the pressure difference applied to the first entrance / exit plate 3 can be reduced.
  • the plate heat exchanger 101 has high reliability because the risk of the first entrance / exit plate 3 being damaged is reduced.
  • the second inlet / outlet plate 4 of the plate heat exchanger 101 has a pressure of the third fluid flowing through the fourth flow path 8 and a pressure of the gas surrounding the outside of the plate heat exchanger 101 (for example, atmospheric pressure). The difference is applied.
  • the pressure of the third fluid flowing through the fourth flow path 8 is the pressure of the first fluid flowing through the third flow path 7. Lower than. Therefore, according to the plate type heat exchanger 101, the difference between the pressure of the first fluid flowing through the third flow path 7 and the pressure of the gas surrounding the outside of the plate type heat exchanger 101 (for example, atmospheric pressure) is the second.
  • the pressure difference applied to the second entrance / exit plate 4 can be reduced.
  • the plate heat exchanger 101 is highly reliable because the risk of the second entrance / exit plate 4 being damaged is reduced.
  • the plate heat exchanger 101 includes a pressure difference applied to the partition plate 2, a pressure difference applied to the first inlet / outlet plate 3, and a pressure difference applied to the second inlet / outlet plate 4. Is set to be the minimum.
  • the pressure difference applied to the partition plate 2 includes the pressure difference between the first fluid and the second fluid, the pressure difference between the first fluid and the third fluid, and the first The pressure difference between the first fluid is smaller than the pressure difference between the second fluid and the third fluid.
  • the pressure difference applied to the first inlet / outlet plate 3 is smaller than the pressure difference between the first fluid and the gas surrounding the plate heat exchanger 101, and the second fluid This is the pressure difference with the gas surrounding the outside of the plate heat exchanger 101.
  • the pressure difference applied to the second inlet / outlet plate 4 is smaller than the pressure difference between the first fluid and the gas surrounding the plate heat exchanger 101, and the third fluid This is the pressure difference with the gas surrounding the outside of the plate heat exchanger 101. Therefore, according to the plate-type heat exchanger 101, as described above, the partition plate 2, the first entrance / exit plate 3, and the second entrance / exit plate 4 are prevented from being damaged and have sufficiently high reliability. Yes.
  • the plate heat exchanger according to the third embodiment basically has the same configuration as the plate heat exchanger 100 according to the first embodiment, but includes a partition plate 2, a first inlet / outlet plate 3, and a second inlet / outlet.
  • the difference is that at least one of the plates 4 in the first direction is specified to be thicker than the heat transfer plate 1.
  • each of the partition plate 2, the first entrance / exit plate 3, and the second entrance / exit plate 4 is thicker in the first direction than the heat transfer plate 1.
  • the thickness of the heat transfer plate 1 is the thickness T1 of the heat transfer surface 17 of the heat transfer plate 1 (see FIG. 18).
  • the heat transfer plate 1 is formed, for example, by pressing a plate-like member, and the thickness of the heat transfer surface 17 is equal to the thickness of the convex portions 14 and 16.
  • the thickness of the partition plate 2 is the thickness T2 of the flat portion 24 of the partition plate 2 (see FIG. 17).
  • the partition plate 2 is formed, for example, by press-molding a plate-like member, and the thickness of the flat portion 24 is equal to the thickness of the convex portions 22 and 23.
  • the thickness of the first entrance / exit plate 3 is the thickness T3 (see FIG. 19) of the flat portion 34 of the first entrance / exit plate 3.
  • the thickness of the second entrance / exit plate 4 is the thickness T4 of the flat portion 44 of the second entrance / exit plate 4 (see FIG. 20).
  • the 1st entrance / exit plate 3 and the 2nd entrance / exit plate 4 are formed when a plate-shaped member is press-molded, for example.
  • the thickness T1 of the heat transfer plate 1 is provided so as not to hinder heat exchange between the first fluid and the second fluid and to withstand the pressure difference between the first fluid and the second fluid.
  • the thickness T2 of the partition plate 2 in the first direction is thicker than the thickness T1 of the heat transfer plate 1 in the first direction.
  • the partition plate 2 can be applied to the difference between the pressure of the first fluid flowing through the first flow path 5 and the pressure of the first fluid flowing through the third flow path 7 that can be applied to the partition plate 2. , Has a sufficiently high strength. Therefore, the plate-type heat exchanger according to Embodiment 3 has high reliability because the breakage of the partition plate 2 is suppressed.
  • the thickness T3 of the first entrance / exit plate 3 in the first direction and the thickness T4 of the second entrance / exit plate 4 in the first direction are the first direction of the heat transfer plate 1. It is thicker than the thickness T1.
  • the first inlet / outlet plate 3 has a pressure difference that can be applied to the first inlet / outlet plate 3, that is, the first fluid flowing through the first flow path 5 and the gas surrounding the outside of the plate heat exchanger. It has a sufficiently high strength against the pressure difference or the pressure difference between the second fluid flowing through the second flow path 6 and the gas surrounding the outside of the plate heat exchanger.
  • the second inlet / outlet plate 4 has a pressure difference that can be applied to the second inlet / outlet plate 4, that is, a pressure difference between the first fluid flowing through the third flow path 7 and the gas surrounding the plate heat exchanger or the fourth flow. It has a sufficiently high strength against the pressure difference between the third fluid flowing through the passage 8 and the gas surrounding the outside of the plate heat exchanger. Therefore, the plate-type heat exchanger according to Embodiment 3 has high reliability because damage to the first entrance / exit plate 3 and the second entrance / exit plate 4 is suppressed.
  • the partition plate 2 may be composed of one member. As shown in FIG. 21, the partition plate 2 may be composed of a plurality of members. The partition plate 2 may be configured by bonding the first member 25 and the second member 26 together.
  • the material constituting the second member 26 has higher strength than, for example, the material constituting the heat transfer plate 1.
  • the material constituting the heat transfer plate 1 is stainless steel, copper (Cu), aluminum (Al), or the like
  • the material constituting the second member 26 is, for example, titanium (Ti), stainless steel, duralumin, or the like. Alloy.
  • the thickness T2 of the partition plate 2 in the first direction corresponds to the sum of the thickness T5 of the first member 25 in the first direction and the thickness T6 of the second member 26 in the first direction.
  • the thickness T6 of the second member 26 in the first direction may be thinner than the thickness T1 of the heat transfer plate 1.
  • the partition plate 2 is configured to prevent the difference between the pressure of the first fluid flowing through the first flow path 5 and the pressure of the first fluid flowing through the third flow path 7 that can be applied to the partition plate 2. , Has a sufficiently high strength.
  • the first entrance / exit plate 3 and the second entrance / exit plate 4 may be composed of one member. Moreover, as FIG. 22 and FIG. 23 show, the 1st entrance / exit plate 3 and the 2nd entrance / exit plate 4 may be comprised by the some member.
  • the first entrance / exit plate 3 may be configured by bonding the third member 35 and the fourth member 36 together.
  • the second entrance / exit plate 4 may be configured by bonding the fifth member 45 and the sixth member 46 together.
  • the material constituting the fourth member 36 and the sixth member 46 has higher strength than the material constituting the heat transfer plate 1, for example.
  • the material which comprises the heat-transfer plate 1 should just be arbitrary materials which have high heat conductivity, it is stainless steel, copper (Cu), aluminum (Al) etc., for example.
  • the material constituting the fourth member 36 and the sixth member 46 is, for example, titanium (Ti), or an alloy such as stainless steel or duralumin.
  • the thickness T3 of the first entrance / exit plate 3 in the first direction corresponds to the sum of the thickness T7 of the third member 35 in the first direction and the thickness T8 of the fourth member 36 in the first direction.
  • the thickness T4 of the second entrance / exit plate 4 in the first direction corresponds to the sum of the thickness T9 of the fifth member 45 in the first direction and the thickness T10 of the sixth member 46 in the first direction.
  • the thicknesses T8 and T10 in the first direction of the fourth member 36 and the sixth member 46 may be thinner than the thickness T1 of the heat transfer plate 1.
  • the first entrance / exit plate 3 has a sufficiently high strength against the pressure difference that can be applied to the first entrance / exit plate 3.
  • the second entrance / exit plate 4 has a sufficiently high strength against a pressure difference that can be applied to the second entrance / exit plate 4.
  • any one of the partition plate 2, the first inlet / outlet plate 3, and the second inlet / outlet plate 4 in the first direction is thicker than the heat transfer plate 1. It may be.
  • the plate heat exchanger having such a configuration has high reliability because the damage to the plate provided with the thickness in the first direction larger than that of the heat transfer plate 1 is suppressed. .
  • the plate heat exchanger according to the fourth embodiment basically has the same configuration as the plate heat exchanger 100 according to the first embodiment, but includes a partition plate 2, a first inlet / outlet plate 3, and a second inlet / outlet.
  • the difference is that at least one of the plates 4 is specified to include a material having higher strength than the material constituting the heat transfer plate 1.
  • each of the partition plate 2, the first entrance / exit plate 3, and the second entrance / exit plate 4 includes a material having a higher strength than the material constituting the heat transfer plate 1.
  • the material which comprises the heat-transfer plate 1 should just be arbitrary materials which have high heat conductivity, it is stainless steel, copper (Cu), aluminum (Al) etc., for example.
  • the material which comprises the partition plate 2 should just be arbitrary materials which are higher intensity
  • the material constituting the first entrance / exit plate 3 and the second entrance / exit plate 4 may be any material having higher strength than the material constituting the heat transfer plate 1. For example, titanium (Ti), stainless steel, or duralumin Alloy.
  • the partition plate 2 can be applied to the difference between the pressure of the first fluid flowing through the first flow path 5 and the pressure of the first fluid flowing through the third flow path 7 that can be applied to the partition plate 2.
  • the first entrance / exit plate 3 has a sufficiently high strength against a pressure difference that can be applied to the first entrance / exit plate 3.
  • the second entrance / exit plate 4 has a sufficiently high strength against a pressure difference that can be applied to the second entrance / exit plate 4. Therefore, the plate-type heat exchanger according to Embodiment 4 has high reliability because breakage of the partition plate 2, the first entrance / exit plate 3, and the second entrance / exit plate 4 is suppressed.
  • the heat-transfer plate 1a and the heat-transfer plate 1e are adhering to the partition plate 2, it is not restricted to this.
  • the partition plate 2 may be provided so as to form a flow path of the first fluid between the heat transfer plates 1 adjacent in the first direction. If it says from a different viewpoint, the partition plate which concerns on this Embodiment may be comprised as the composite_body
  • the present invention is particularly advantageously applied to a plate heat exchanger capable of performing heat exchange between three fluids.

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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

La présente invention est pourvue : d'une première unité d'échange de chaleur (10) et d'une seconde unité d'échange de chaleur (20), dont chacune inclut une pluralité de plaques de transfert de chaleur (1) stratifiées dans la première direction ; et d'une plaque de séparation (2) qui est disposée entre la première unité d'échange de chaleur (10) et la seconde unité d'échange de chaleur (20) dans la première direction. Dans la première unité d'échange de chaleur (10), des premiers canaux d'écoulement (5), dans lesquels s'écoule un premier fluide, et des deuxièmes canaux d'écoulement (6), dans lesquels s'écoule un deuxième fluide, sont disposés en alternance dans la première direction. Dans la seconde unité d'échange de chaleur (20), des troisièmes canaux d'écoulement (7), dans lesquels le premier fluide s'écoule, et des quatrièmes canaux d'écoulement (8), dans lesquels un troisième fluide s'écoule, sont disposés en alternance dans la première direction. Au moins une partie des premiers canaux d'écoulement (5) est positionnée plus près de la plaque de séparation (2) que les deuxièmes canaux d'écoulement (6). Au moins une partie des troisièmes canaux d'écoulement (7) est positionnée plus près de la plaque de séparation (2) que les quatrièmes canaux d'écoulement (8).
PCT/JP2016/076641 2016-09-09 2016-09-09 Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération Ceased WO2018047299A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP16915717.9A EP3511666B1 (fr) 2016-09-09 2016-09-09 Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération
PCT/JP2016/076641 WO2018047299A1 (fr) 2016-09-09 2016-09-09 Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération
JP2018537951A JPWO2018047299A1 (ja) 2016-09-09 2016-09-09 プレート式熱交換器および冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/076641 WO2018047299A1 (fr) 2016-09-09 2016-09-09 Échangeur de chaleur de type à plaque et dispositif à cycle de réfrigération

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KR102908779B1 (ko) * 2023-05-12 2026-01-07 주식회사 코렌스 판형 열교환기

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FI129787B (fi) * 2021-03-19 2022-08-31 Hoegforsgst Oy Levylämmönsiirrin ja menetelmä kaukolämmön siirtämiseksi käyttöveteen

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JPH063081A (ja) * 1992-06-17 1994-01-11 Mitsubishi Electric Corp プレート型熱交換器
JP2000018735A (ja) * 1998-06-23 2000-01-18 Kobe Steel Ltd 冷凍装置
JP2000171177A (ja) * 1998-12-08 2000-06-23 Osaka Gas Co Ltd 三流体用プレート式熱交換器、及び、その製造方法
WO2004042312A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Module d'echange a plaque empilees, notamment pour un vehicule automobile
JP2005106385A (ja) * 2003-09-30 2005-04-21 Hisaka Works Ltd プレート式熱交換器
EP2952832A1 (fr) * 2014-06-06 2015-12-09 Vaillant GmbH Système de pompe à chaleur avec économiseur intégré
WO2016117069A1 (fr) * 2015-01-22 2016-07-28 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif extérieur de type à pompe à chaleur

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FR2843449B1 (fr) * 2002-08-09 2005-05-06 Valeo Thermique Moteur Sa Echangeur de chaleur pour le circuit d'air d'admission d'un moteur thermique
DE102012010681B4 (de) * 2012-05-30 2024-03-07 Audi Ag Anordnung zur Temperierung des Schmiermittels einer Brennkraftmaschine

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Publication number Priority date Publication date Assignee Title
JPH063081A (ja) * 1992-06-17 1994-01-11 Mitsubishi Electric Corp プレート型熱交換器
JP2000018735A (ja) * 1998-06-23 2000-01-18 Kobe Steel Ltd 冷凍装置
JP2000171177A (ja) * 1998-12-08 2000-06-23 Osaka Gas Co Ltd 三流体用プレート式熱交換器、及び、その製造方法
WO2004042312A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Module d'echange a plaque empilees, notamment pour un vehicule automobile
JP2005106385A (ja) * 2003-09-30 2005-04-21 Hisaka Works Ltd プレート式熱交換器
EP2952832A1 (fr) * 2014-06-06 2015-12-09 Vaillant GmbH Système de pompe à chaleur avec économiseur intégré
WO2016117069A1 (fr) * 2015-01-22 2016-07-28 三菱電機株式会社 Échangeur de chaleur à plaques et dispositif extérieur de type à pompe à chaleur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102908779B1 (ko) * 2023-05-12 2026-01-07 주식회사 코렌스 판형 열교환기

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EP3511666A4 (fr) 2019-09-25
EP3511666A1 (fr) 2019-07-17
EP3511666B1 (fr) 2020-10-21

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