EP3088831B1 - Wärmetauscher und klimaanlage - Google Patents

Wärmetauscher und klimaanlage Download PDF

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Publication number
EP3088831B1
EP3088831B1 EP13900071.5A EP13900071A EP3088831B1 EP 3088831 B1 EP3088831 B1 EP 3088831B1 EP 13900071 A EP13900071 A EP 13900071A EP 3088831 B1 EP3088831 B1 EP 3088831B1
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EP
European Patent Office
Prior art keywords
tubes
openings
heat exchanger
flow passage
plate
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.)
Active
Application number
EP13900071.5A
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English (en)
French (fr)
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EP3088831A1 (de
EP3088831A4 (de
Inventor
Shigeyoshi MATSUI
Shinya Higashiiue
Takashi Okazaki
Akira Ishibashi
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3088831A1 publication Critical patent/EP3088831A1/de
Publication of EP3088831A4 publication Critical patent/EP3088831A4/de
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Publication of EP3088831B1 publication Critical patent/EP3088831B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to a stacking-type header, a heat exchanger, and an air-conditioning apparatus.
  • a heat exchanger including a return header including a tube bonding member with which flat tubes and a member are bonded to each other, a tube fixing member configured to position end portions of the flat tubes, a spacer portion, and a back plate, and having a refrigerant joining space formed in the return header so as to move refrigerant in a row direction (see, for example, Patent Literature 1).
  • a heat load (heat exchange amount) on an air upstream side is larger than that on an air downstream side (a downstream side of air). Therefore, it is desired that the distribution ratio be adjusted so as to increase the latent heat amount of the refrigerant flowing through the flow passages on the air upstream side.
  • the present invention has been made in view of the problems as described above, and therefore has an object to provide a stacking-type header, which is connected to a plurality of tubes so that a fluid flowing into the stacking-type header from one tube is caused to flow into an other tube, and is capable of reducing unevenness of the fluid flowing into the tube.
  • the present invention has an object to provide a stacking-type header capable of adjusting a distribution ratio of a fluid flowing into a tube from the stacking-type header.
  • the present invention has an object to provide a heat exchanger including the stacking-type header as described above.
  • the present invention has an object to provide an air-conditioning apparatus including the heat exchanger as described above.
  • the unevenness of the fluid flowing into the tube can be reduced in the stacking-type header connected to the plurality of tubes so that the fluid flowing into the stacking-type header from one tube is caused to flow into an other tube.
  • the distribution ratio of the fluid flowing into the tube from the stacking-type header can be adjusted relatively easily.
  • the stacking-type header according to the present invention distributes refrigerant flowing into a flat tube being a heat transfer tube of a heat exchanger, but the stacking-type header according to the present invention may distribute refrigerant flowing into other devices.
  • the configuration, operation, and other matters described below are merely examples, and the description is not intended to limit such configuration, operation, and other matters.
  • the same or similar components are denoted by the same reference symbols, or the reference symbols therefor are omitted. Further, the illustration of details in the structure is appropriately simplified or omitted. Further, overlapping description or similar description is appropriately simplified or omitted.
  • Fig. 1 is a side view for illustrating the schematic configuration of the heat exchanger 1 according to Embodiment 1.
  • Fig. 2 is a top view for illustrating the schematic configuration of the heat exchanger 1 according to Embodiment 1.
  • the heat exchanger 1 includes a stacking-type header 2, a plurality of first heat transfer tubes 4, a retaining member 5, a plurality of fins 6, and a plurality of second heat transfer tubes 7.
  • the stacking-type header 2 includes at least one first inlet flow passage 2A, a plurality of first outlet flow passages 2B, a plurality of second inlet flow passages 2C, a second outlet flow passage 2D, and turn-back flow passages 2E for turning back flows of refrigerant, which pass through the first heat transfer tubes 4, to the second heat transfer tubes 7.
  • Refrigerant tubes are connected to the first inlet flow passage 2A and the second outlet flow passage 2D of the stacking-type header 2, respectively.
  • the plurality of first heat transfer tubes 4 are connected between the plurality of first outlet flow passages 2B and the turn-back flow passages 2E of the stacking-type header 2, whereas the plurality of second heat transfer tubes 7 are connected between the turn-back flow passages 2E and the plurality of second inlet flow passages 2C of the stacking-type header 2.
  • the fin 6 has, for example, a plate-shaped shape.
  • the plurality of fins 6 are stacked at predetermined intervals so that a heat medium (for example, air) flows therebetween.
  • the fin 6 is made of a metal material such as aluminum or copper.
  • the fin 6 is made of, for example, aluminum.
  • Each of the first heat transfer tube 4 and the second heat transfer tube 7 is, for example, a flat tube subjected to hair-pin bending at an end portion side of the heat exchanger 1 that is opposite to the stacking-type header 2.
  • Each of the first heat transfer tube 4 and the second heat transfer tube 7 is made of a metal material such as aluminum or copper.
  • the first heat transfer tubes 4 and the second heat transfer tubes 7 are arranged in a plurality of stages in a stacking direction intersecting with an air flow direction.
  • the first heat transfer tubes 4 and the second heat transfer tubes 7 are arranged in rows in a row direction along the air flow direction.
  • the plurality of first heat transfer tubes 4 and the plurality of second heat transfer tubes 7 are arranged at intervals secured in a direction of the minor axis of the flat shape (stacking direction) while the major axis of the flat shape is oriented in the air flow direction (row direction).
  • the first heat transfer tubes 4 are, for example, arrayed in the stacking direction alternately with the second heat transfer tubes 7 in an adjacent row (staggered array).
  • two rows including the first heat transfer tubes 4 and the second heat transfer tubes 7 are arranged.
  • FIG. 1 there is illustrated a case where eight first heat transfer tubes 4 and eight second heat transfer tubes 7 are provided, but the present invention is not limited to such a case.
  • two first heat transfer tubes 4 and two second heat transfer tubes 7 may be provided.
  • Fig. 3 is a schematic configuration view for illustrating a cross section of each of the first heat transfer tube 4 and the second heat transfer tube 7 of the heat exchanger 1 according to Embodiment 1.
  • each of the first heat transfer tube 4 and the second heat transfer tube 7 at least one partition is provided to form a plurality of flow passages 30.
  • each of the first heat transfer tube 4 and the second heat transfer tube 7 corresponds to a "tube" of the present invention.
  • Embodiment 1 there is described a case where the flat tube is used, but the present invention is not limited thereto, and a tube having an arbitrary shape, such as a circular tube or a rectangular tube, may be used instead.
  • the refrigerant flowing through the refrigerant tube passes through the first inlet flow passage 2A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of first outlet flow passages 2B to flow out toward the plurality of first heat transfer tubes 4.
  • the refrigerant passing through the plurality of first heat transfer tubes 4 flows into the plurality of turn-back flow passages 2E of the stacking-type header 2 to be turned back, and flows out therefrom toward the plurality of second heat transfer tubes 7.
  • the flows of the refrigerant passing through the plurality of second heat transfer tubes 7 pass through the second inlet flow passages 2C to flow into the stacking-type header 2 again to be joined, and the joined refrigerant passes through the second outlet flow passage 2D to flow out therefrom toward the refrigerant pipe.
  • the refrigerant exchanges heat with, for example, air supplied by a fan.
  • the refrigerant may reversely flow.
  • Fig. 4 is a perspective view for illustrating the stacking-type header 2 of the heat exchanger 1 according to Embodiment 1 under a state in which the stacking-type header 2 is disassembled.
  • the stacking-type header 2 includes a first plate-shaped unit 11, a second plate-shaped unit 12, a third plate-shaped unit 13, a fourth plate-shaped unit 14, and a fifth plate-shaped unit 15.
  • the first plate-shaped unit 11 includes the retaining member 5, a cladding member 26_1, and a first plate-shaped member 21.
  • the second plate-shaped unit 12 includes a cladding member 26_2.
  • the third plate-shaped unit 13 includes a third plate-shaped member 23 and a cladding member 26_3.
  • the fourth plate-shaped unit 14 includes a plurality of fourth plate-shaped members 24_1 to 24_3 and a plurality of cladding members 26_4 and 26_5.
  • the fifth plate-shaped unit 15 includes a fifth plate-shaped member 25 and a cladding member 26_6.
  • a brazing material is applied to one or both surfaces of each of the cladding members 26_1 to 26_6.
  • the first plate-shaped member 21 is stacked on the retaining member 5 through intermediation of the cladding member 26_1.
  • the third plate-shaped member 23 is stacked on the first plate-shaped member 21 through intermediation of the cladding member 26_2.
  • the plurality of fourth plate-shaped members 24_1 to 24_3 are stacked on the third plate-shaped member 23 through intermediation of the cladding members 26_3 to 26_5, respectively.
  • the fifth plate-shaped member 25 is stacked on the fourth plate-shaped member 24_3 through intermediation of the cladding member 26_6.
  • each of the first plate-shaped member 21, the third plate-shaped member 23, the plurality of fourth plate-shaped members 24_1 to 24_3, and the fifth plate-shaped member 25 has a thickness of from about 1 mm to about 10 mm, and is made of aluminum.
  • the fourth plate-shaped members 24_1 to 24_3 are collectively referred to as the fourth plate-shaped member 24.
  • the cladding members 26_1 to 26_6 are collectively referred to as the cladding member 26.
  • the plurality of first outlet flow passages 2B of Fig. 1 are formed by flow passages 21B formed in the first plate-shaped member 21 and flow passages 26B formed in the cladding member 26_1.
  • Each of the flow passages 21B and the flow passages 26B is a through hole having an inner peripheral surface shaped conforming to an outer peripheral surface of the first heat transfer tube 4.
  • the end portions of the first heat transfer tubes 4 are joined to the retaining member 5 by brazing to be retained.
  • the cladding member 26_1 and the first plate-shaped member 21 are joined to each other, the end portions of the first heat transfer tubes 4 and the first outlet flow passages 2B are connected to each other.
  • first outlet flow passages 2B and the first heat transfer tubes 4 may be joined to each other without providing the retaining member 5. In such a case, the component cost and the like are reduced.
  • the plurality of turn-back flow passages 2E of Fig. 1 are formed by flow passages 21 E_1 and 21E_2 formed in the first plate-shaped member 21, flow passages 26E_1 and 26E_2 formed in the cladding member 26_2, flow passages 23E formed in the third plate-shaped member 23, and a side surface of the cladding member 26_3.
  • first heat transfer tubes 4 and the second heat transfer tubes 7 to be connected to the turn-back flow passages 2E are joined to the retaining member 5 by brazing to be retained.
  • first heat transfer tubes 4 and the second heat transfer tubes 7 are joined to the retaining member 5
  • the end portions of the first heat transfer tubes 4 and the second heat transfer tubes 7 are connected to the turn-back flow passages 2E.
  • Fig. 5 is a schematic sectional view for illustrating the stacking-type header 2 of the heat exchanger 1 according to Embodiment 1. Note that, in Fig. 5 , a cross section of a principal part of the stacking-type header 2 is illustrated in an enlarged manner.
  • the cladding member 26_2 is stacked on the first plate-shaped member 21, and the flow passages 26E_1 and 26E_2 of the cladding member 26_2 and the flow passages 21E_1 and 21 E_2 of the first plate-shaped member 21 are communicated with each other, respectively.
  • the end portions of the first heat transfer tube 4 and the second heat transfer tube 7 are arranged at a distance from the cladding member 26_2, and the flow passages 21E_1 and 21E_2 of the first plate-shaped member 21 define open spaces.
  • the flow passage 23E formed in the third plate-shaped member 23 is defined by a single opening having a size larger than the two flow passages 26E_1 and 26E_2 formed in the cladding member 26_2.
  • the cladding member 26_3 does not have an opening at a part facing the flow passage 23E.
  • the third plate-shaped member 23 and the cladding member 26_3 are stacked on the cladding member 26_2 to form a lateral bridging flow passage configured to communicate the two flow passages 26E_1 and 26E_2 formed in the cladding member 26_2.
  • the flow passage area (opening sectional area) of the flow passage 26E_1 formed in the cladding member 26_2 is set smaller than the flow passage area of the flow passage 21E_1 formed in the first plate-shaped member 21. Further, the flow passage area (opening sectional area) of the flow passage 26E_2 formed in the cladding member 26_2 is smaller than the flow passage area of the flow passage 21E_2 formed in the first plate-shaped member 21.
  • the flow passage area of the flow passage 26E_1 formed in the cladding member 26_2 is smaller than the flow passage area of the first heat transfer tube 4. Further, the flow passage area of the flow passage 26E_2 formed in the cladding member 26_2 is set smaller than the flow passage area of the second heat transfer tube 7.
  • a flow passage cross section V1 of the flow passage 26E_1 formed in the cladding member 26_2 is orthogonal to a center axis C1 of the first heat transfer tube 4. That is, the flow passage cross section V1 of the flow passage 26E_1 is set in parallel to a flow passage cross section of the first heat transfer tube 4.
  • a flow passage cross section V2 of the flow passage 26E_2 formed in the cladding member 26_2 is orthogonal to a center axis C2 of the second heat transfer tube 7. That is, the flow passage cross section V2 of the flow passage 26E_2 is set in parallel to a flow passage cross section of the second heat transfer tube 7.
  • Each of the flow passages 26E_1 and 26E_2 formed in the cladding member 26_2 has, for example, a circular shape.
  • each of the flow passages 26E_1 and 26E_2 is not limited to the circular shape, but may be any shape.
  • each of the flow passages 26E_1 and 26E_2 may have a flat shape in which the major axis direction thereof coincides with those of the first heat transfer tube 4 and the second heat transfer tube 7.
  • the width of each of the flow passages 26E_1 and 26E_2 in the major axis direction is smaller than the width of each of the first heat transfer tube 4 and the second heat transfer tube 7 in the major axis direction.
  • the shape of the flow passage 21E_1 formed in the first plate-shaped member 21 may be any shape as long as the shape encloses a contour of the first heat transfer tube 4 in sectional view.
  • the shape of the flow passage 21E_2 may be any shape as long as the shape encloses a contour of the second heat transfer tube 7 in sectional view.
  • each of the flow passages 21E_1 and 21E_2 is formed into a flat shape, and at least one of the width in the major axis direction or the width in the minor axis direction is set larger than those of the first heat transfer tube 4 and the second heat transfer tube 7.
  • first plate-shaped member 21, the cladding member 26_1, and the retaining member 5 correspond to a "first plate-shaped unit" of the present invention.
  • the cladding member 26_2 corresponds to a "second plate-shaped unit" of the present invention.
  • the third plate-shaped member 23 and the cladding member 26_3 correspond to a "third plate-shaped unit" of the present invention.
  • the flow passages 21 E_1 and 21 E_2 formed in the first plate-shaped member 21 correspond to a "first opening" of the present invention.
  • flow passages 26E_1 and 26E_2 formed in the cladding member 26_2 corresponds to a "second opening" of the present invention.
  • the flow passage 23E formed in the third plate-shaped member 23 corresponds to a "bridging flow passage" of the present invention.
  • a branching flow passage is formed by flow passages 24A formed in the fourth plate-shaped members 24.
  • the flow passage 24A is a linear through groove.
  • the branching flow passage has a structure to branch the refrigerant flowing thereinto from the first inlet flow passage 2A into two flows. The structure is multiply provided. Thereby, the refrigerant is distributed to the plurality of first outlet flow passages 2B.
  • a joining flow passage is formed by flow passages 24C formed in the fourth plate-shaped members 24.
  • the flow passage 24C is a rectangular through groove.
  • the joining flow passage is configured to join the flows of the refrigerant flowing thereinto from the second inlet flow passages 2C, to thereby cause the refrigerant to flow out toward the second outlet flow passage 2D.
  • the first inlet flow passage 2A of Fig. 1 is formed by a flow passage 25A formed in the fifth plate-shaped member 25 and a flow passage 25A formed in the cladding member 26_6.
  • the first inlet flow passage 2A is, for example, a circular through hole.
  • the second outlet flow passage 2D of Fig. 1 is formed by a flow passage 25D formed in the fifth plate-shaped member 25 and the flow passage 25D formed in the cladding member 26_6.
  • the second outlet flow passage 2D is, for example, a circular through hole.
  • the refrigerant flowing into the plurality of first heat transfer tubes 4 from the stacking-type header 2 flows through the first heat transfer tubes 4, and is then turned back at the end portion side of the heat exchanger 1 to flow into the stacking-type header 2 again from the turn-back flow passages 2E.
  • the refrigerant flowing into the turn-back flow passages 2E moves toward the second heat transfer tube 7 side of the turn-back flow passages 2E to flow out therefrom toward the plurality of second heat transfer tubes 7.
  • the refrigerant flowing into the plurality of second heat transfer tubes 7 from the stacking-type header 2 flows through the second heat transfer tubes 7, and is then turned back at the end portion side of the heat exchanger 1 to flow into the stacking-type header 2 again from the second inlet flow passages 2C. Then, the refrigerant passes through the second outlet flow passage 2D to flow out therefrom toward the refrigerant tube.
  • the refrigerant exchanges heat with, for example, air supplied by the fan.
  • the refrigerant may reversely flow.
  • Fig. 6 is a schematic sectional view for illustrating the flow of the refrigerant in the stacking-type header 2 of the heat exchanger 1 according to Embodiment 1. Note that, in Fig. 6 , the cross section of the principal part of the stacking-type header 2 is illustrated in an enlarged manner.
  • Fig. 7 is a sectional view taken along the line I-I of Fig. 6 .
  • Fig. 8 is a sectional view taken along the line II-II of Fig. 6 .
  • Fig. 9 is a sectional view taken along the line III-III of Fig. 6 .
  • the refrigerant flowing through the first heat transfer tube 4 flows into the flow passage 21E_1 of the first plate-shaped member 21 from the end portion of the first heat transfer tube 4.
  • the refrigerant flowing through the open space of the flow passage 21 E_1 is contracted by the flow passage 26E_1 of the cladding member 26_2 to flow out therefrom toward the flow passage 23E formed in the third plate-shaped member 23.
  • the refrigerant flowing through the flow passage 23E moves toward the second heat transfer tube 7 side, and is contracted by the flow passage 26E_2 of the cladding member 26_2 to flow into the flow passage 21E_2 of the first plate-shaped member 21.
  • the refrigerant flow direction is not limited to that described above, but the refrigerant may be caused to flow in a reverse direction.
  • Fig. 22 is a view for illustrating a turn-back flow passage of a related-art stacking-type header.
  • the flow passages 21E_1 and 21 E_2 of the first plate-shaped member 21 and the flow passages 26E_1 and 26E_2 of the cladding member 26_2 are not formed in a turn-back flow passage 2E illustrated in Fig. 22 .
  • the flow passages 21E_1 and 21E_2 of the first plate-shaped member 21 and the flow passages 26E_1 and 26E_2 of the cladding member 26_2 are formed, and the flow passage area (opening sectional area) of each of the flow passages 26E_1 and 26E_2 is smaller than the flow passage area of each of the flow passages 21E_1 and 21E_2.
  • the flow passage cross section V1 of the flow passage 26E_1 formed in the cladding member 26_2 is orthogonal to the center axis C1 of the first heat transfer tube 4.
  • the flow passage cross section V2 of the flow passage 26E_2 formed in the cladding member 26_2 is orthogonal to the center axis C2 of the second heat transfer tubes 7.
  • the refrigerant flow direction is changed by 90 degrees, thereby increasing the effect of suppressing the unevenness of the liquid-phase refrigerant that may be caused by the inertia force.
  • Embodiment 2 a stacking-type header 2 of a heat exchanger 1 according to Embodiment 2 is described focusing on differences from Embodiment 1.
  • Fig. 10 is a schematic sectional view for illustrating the stacking-type header 2 of the heat exchanger 1 according to Embodiment 2. Note that, in Fig. 10 , a cross section of a main part of the stacking-type header 2 is illustrated in an enlarged manner.
  • a center axis of the flow passage 21 E_1 of the first plate-shaped member 21 and a center axis of the flow passage 26E_1 of the cladding member 26_2 are offset from each other.
  • a center axis of the flow passage 21E_2 of the first plate-shaped member 21 and a center axis of the flow passage 26E_2 of the cladding member 26_2 are offset from each other.
  • the center axis of the flow passage 26E_1 corresponding to the first heat transfer tube 4 is offset from the center axis of the flow passage 21 E_1 toward the second heat transfer tube 7 side
  • the center axis of the flow passage 26E_2 corresponding to the second heat transfer tube 7 is offset from the center axis of the flow passage 21 E_2 toward the first heat transfer tube 4 side.
  • An offset amount Z of the center axes satisfies a relationship of 0 ⁇ Z ⁇ W3/2, where W3 represents an outer diameter of each of the first heat transfer tube 4 and the second heat transfer tube 7 in the major axis direction.
  • center axes are offset so that a distance between the center axis of the flow passage 26E_2 corresponding to the first heat transfer tube 4 and the center axis of the first heat transfer tube 4 is shorter than a distance between the center axis of the second heat transfer tube 7 and the center axis of the flow passage 26E_1 corresponding to the first heat transfer tube 4.
  • center axes are offset so that a distance between the center axis of the flow passage 26E_2 corresponding to the second heat transfer tube 7 and the center axis of the second heat transfer tube 7 is shorter than a distance between the center axis of the first heat transfer tube 4 and the center axis of the flow passage 26E_1 corresponding to the second heat transfer tube 7.
  • Fig. 11 is a schematic sectional view for illustrating the flow of the refrigerant in the stacking-type header 2 of the heat exchanger 1 according to Embodiment 2. Note that, in Fig. 11 , the cross section of the main part of the stacking-type header 2 is illustrated in an enlarged manner.
  • Fig. 12 is a sectional view taken along the line I-I of Fig. 11 .
  • Fig. 13 is a sectional view taken along the line II-II of Fig. 11 .
  • Fig. 14 is a sectional view taken along the line III-III of Fig. 11 .
  • the refrigerant flowing through the first heat transfer tube 4 flows into the flow passage 21E_1 of the first plate-shaped member 21 from the end portion of the first heat transfer tube 4.
  • the refrigerant flowing through the open space of the flow passage 21 E_1 is contracted by the flow passage 26E_1 offset toward the second heat transfer tube 7 side to flow out therefrom toward the flow passage 23E formed in the third plate-shaped member 23.
  • the refrigerant in the two-phase gas-liquid state passing through the flow passage 23E is affected by the inertia force so that refrigerant having high density flows on the outer side and refrigerant having low density flows on the inner side.
  • the refrigerant flowing through the flow passage 23E moves toward the second heat transfer tube 7 side, and is contracted by the flow passage 26E_2 of the cladding member 26_2 to flow into the flow passage 21 E_2 from the flow passage 26E_2 offset toward the first heat transfer tube 4 side.
  • the liquid refrigerant flowing out from the flow passage 26E_2 of the cladding member 26_2 toward the flow passage 21 E_2 of the first plate-shaped member 21 flows more through the first heat transfer tube 4 side of the open space of the flow passage 21 E_2 to which the end portion of the second heat transfer tube 7 is connected. Therefore, the liquid refrigerant flowing into the plurality of flow passages 30 inside the second heat transfer tube 7 from the flow passage 21 E_2 of the first plate-shaped member 21 flows more into the flow passages on the first heat transfer tube 4 side.
  • the ratio between the gas-phase refrigerant and the liquid-phase refrigerant flowing into the plurality of flow passages 30 inside the second heat transfer tube 7 can be appropriately adjusted through adjustment of the offset amount Z.
  • the refrigerant flow direction is not limited to that described above, but the refrigerant may be caused to flow in a reverse direction.
  • the ratio between the gas-phase refrigerant and the liquid-phase refrigerant flowing into the plurality of flow passages 30 inside the first heat transfer tube 4 can be appropriately adjusted through the adjustment of the offset amount Z.
  • the heat exchanger 1 according to Embodiment 2 is used for an air-conditioning apparatus, but the present invention is not limited to such a case, and for example, the heat exchanger 1 according to Embodiment 2 may be used for other refrigeration cycle apparatus including a refrigerant circuit. Further, there is described a case where the air-conditioning apparatus switches between a cooling operation and a heating operation, but the present invention is not limited to such a case, and the air-conditioning apparatus may perform only the cooling operation or the heating operation.
  • Fig. 15 is a diagram for illustrating the configuration of the air-conditioning apparatus to which the heat exchanger 1 according to Embodiment 2 is applied. Note that, in Fig. 15 , the flow of the refrigerant during the cooling operation is indicated by the solid arrow, while the flow of the refrigerant during the heating operation is indicated by the dotted arrow.
  • the air-conditioning apparatus includes a compressor 71, a four-way valve 72, an outdoor heat exchanger (heat source-side heat exchanger) 73, an expansion device 74, an indoor heat exchanger (load-side heat exchanger) 75, an outdoor fan (heat source-side fan) 76, and an indoor fan (load-side fan) 77.
  • the compressor 71, the four-way valve 72, the outdoor heat exchanger 73, the expansion device 74, and the indoor heat exchanger 75 are connected by refrigerant tubes to form a refrigerant circuit.
  • the flow passage of the four-way valve 72 is switched to switch between the cooling operation and the heating operation.
  • the refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 71 passes through the four-way valve 72 to flow into the outdoor heat exchanger 73, and is condensed through heat exchange with air supplied by the outdoor fan 76.
  • the condensed refrigerant is brought into a high-pressure liquid state to flow out from the outdoor heat exchanger 73.
  • the refrigerant is then brought into a low-pressure two-phase gas-liquid state by the expansion device 74.
  • the refrigerant in the low-pressure two-phase gas-liquid state flows into the indoor heat exchanger 75, and is evaporated through heat exchange with air supplied by the indoor fan 77, to thereby cool the inside of a room.
  • the evaporated refrigerant is brought into a low-pressure gas state to flow out from the indoor heat exchanger 75.
  • the refrigerant then passes through the four-way valve 72 to be sucked into the compressor 71.
  • the refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 71 passes through the four-way valve 72 to flow into the indoor heat exchanger 75, and is condensed through heat exchange with air supplied by the indoor fan 77, to thereby heat the inside of the room.
  • the condensed refrigerant is brought into a high-pressure liquid state to flow out from the indoor heat exchanger 75.
  • the refrigerant then turns into refrigerant in a low-pressure two-phase gas-liquid state by the expansion device 74.
  • the refrigerant in the low-pressure two-phase gas-liquid state flows into the outdoor heat exchanger 73, and is evaporated through heat exchange with air supplied by the outdoor fan 76.
  • the evaporated refrigerant is brought into a low-pressure gas state to flow out from the outdoor heat exchanger 73.
  • the refrigerant then passes through the four-way valve 72 to be sucked into the compressor 71.
  • the heat exchanger 1 is used for at least one of the outdoor heat exchanger 73 or the indoor heat exchanger 75.
  • the heat exchanger 1 serves as the evaporator
  • the heat exchanger 1 is connected so that the refrigerant flows in from the first inlet flow passage 2A of the stacking-type header 2 and the refrigerant flows out from the second outlet flow passage 2D.
  • the heat exchanger 1 serves as the evaporator
  • the refrigerant in the two-phase gas-liquid state passes through the refrigerant tube to flow into the stacking-type header 2.
  • the heat exchanger 1 serves as the condenser
  • the refrigerant reversely flows through the stacking-type header 2.
  • the refrigerant passes through the first heat transfer tube 4 arranged in a row on an air upstream side, and then passes through the turn-back flow passage 2E of the stacking-type header 2 to flow into the second heat transfer tube 7 arranged in a row on an air downstream side.
  • the refrigerant passes through the second heat transfer tube 7 arranged in the row on the air downstream side, and then passes through the turn-back flow passage 2E of the stacking-type header 2 to flow into the first heat transfer tube 4 arranged in the row on the air upstream side.
  • Fig. 16 and Fig. 17 are diagrams for illustrating a liquid amount distribution of the refrigerant flowing into the second heat transfer tube 7 when the heat exchanger 1 according to Embodiment 2 of the present invention serves as the evaporator.
  • Fig. 18 is a graph for showing temperature changes of air and the refrigerant when the heat exchanger 1 according to Embodiment 2 serves as the evaporator.
  • the refrigerant flows in a direction along that of the air flow generated through the drive of the outdoor fan 76. Specifically, the refrigerant flows into the flow passage 26E_1 from the first heat transfer tube 4, and then flows into the flow passage 26E_2 from the flow passage 23E in the two-phase gas-liquid state.
  • the refrigerant in the two-phase gas-liquid state passing through the flow passage 23E is affected by the inertia force so that refrigerant having high density flows on the outer side and refrigerant having low density flows on the inner side.
  • the offset amount Z of the flow passage 26E_2 is Z>0, and hence the liquid refrigerant flowing into the flow passage 26E_2 flows more into the point S side of the second heat transfer tube 7.
  • a temperature difference between the air and the refrigerant passing through the heat exchanger 1 is more significant on the air upstream side.
  • the heat load heat exchange amount
  • the refrigerant is distributed to the flow passages 30 of the second heat transfer tube 7 so that the liquid refrigerant flows more into the point S side of the second heat transfer tube 7, that is, into the flow passages on the air upstream side.
  • the evaporation of the liquid refrigerant is promoted to enhance the heat exchange efficiency.
  • Fig. 19 is a view for illustrating a gas amount distribution of the refrigerant flowing into the first heat transfer tube 4 when the heat exchanger 1 according to Embodiment 2 serves as the condenser.
  • Fig. 20 is a graph for showing the gas amount distribution of the refrigerant flowing into the first heat transfer tube 4 when the heat exchanger 1 according to Embodiment 2 serves as the condenser.
  • Fig. 21 is a graph for showing temperature changes of the air and the refrigerant when the heat exchanger 1 according to Embodiment 2 serves as the condenser.
  • the refrigerant flows in a reverse direction to that of the air flow generated through the drive of the outdoor fan 76. Specifically, the refrigerant flows into the flow passage 26E_2 from the second heat transfer tube 7, and then flows into the flow passage 26E_1 from the flow passage 23E in the two-phase gas-liquid state.
  • the refrigerant in the two-phase gas-liquid state passing through the flow passage 23E is affected by the inertia force so that refrigerant having high density flows on the outer side and refrigerant having low density flows on the inner side.
  • the offset amount Z of the flow passage 26E_1 is Z>0, and hence the gas refrigerant flowing into the flow passage 26E_1 flows more into the point L side of the first heat transfer tube 4.
  • the heat exchanger 1 serves as the condenser
  • the temperature difference between the air and the refrigerant passing through the heat exchanger 1 is more significant on the windward side.
  • the heat load heat exchange amount
  • the refrigerant is distributed to the plurality of flow passages 30 of the first heat transfer tube 4 so that the gas refrigerant flows more into the point L side of the first heat transfer tube 4, that is, into the flow passages on the windward side.
  • the condensation of the gas refrigerant is promoted to enhance the heat exchange efficiency.
  • each of the flow passages 26E_1 and 26E_2 is offset in view of the relationship between the flow direction of the refrigerant in the two-phase gas-liquid state and the air flow direction, but the present invention is not limited thereto.
  • the distribution ratio of the fluid flowing into each of the first heat transfer tube 4 and the second heat transfer tube 7 from the stacking-type header 2 can be appropriately adjusted by arbitrarily setting the offset amount and the offset direction.
  • the distribution ratio of the refrigerant can be adjusted relatively easily, and hence the stacking-type header 2 can be used under a variety of situations, environments, or other conditions.
  • the turn-back flow passage 2E is formed by the flow passages 21E_1 and 21 E_2 formed in the first plate-shaped member 21, the first outlet flow passages 2B formed in the cladding member 26_2, and the flow passage 23E formed in the third plate-shaped member 23.

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

Claims (12)

  1. Wärmetauscher (1) umfassend eine Sammelkammer (2) vom Stapeltyp, die einen ersten Einlass-Strömungsdurchlass (2A), eine Vielzahl von ersten Auslass-Strömungsdurchlässen (2B), die mit einer Vielzahl von ersten Rohren (4) verbunden sind, eine Vielzahl von zweiten Einlass-Strömungsdurchlässen (2C), die mit einer Vielzahl von zweiten Rohren (7) verbunden sind, und einen zweiten Auslass-Strömungsdurchlass (2D) umfasst, wobei die Sammelkammer (2) vom Stapeltyp Folgendes bereitstellt:
    dass der erste Einlass-Strömungsdurchlass (2A) einem Fluid ermöglicht, in die Sammelkammer (2) vom Stapeltyp zu strömen, aufgeteilt zu werden, und dann durch die Vielzahl von ersten Auslass-Strömungsdurchlässen (2B) in Richtung der Vielzahl von ersten Rohren (4) zu strömen, und
    dass die Vielzahl von zweiten Einlass-Strömungsdurchlässen (2C) dem Fluid ermöglichen, aus der Vielzahl von zweiten Rohren (7) in die Sammelkammer (2) vom Stapeltyp zu strömen, zusammengeführt zu werden, durch den zweiten Auslass-Strömungsdurchlass (2D) hindurchzutreten und von dort auszuströmen,
    wobei die Sammelkammer (2) vom Stapeltyp ferner Folgendes umfasst:
    eine erste plattenförmige Einheit (21, 26_1, 5) mit einer Vielzahl von ersten Öffnungen (21E_1, 21E_2), mit denen die Vielzahl von ersten Rohren (4) bzw. die Vielzahl von zweiten Rohren (7) verbunden sind;
    eine zweite plattenförmige Einheit (26_2) mit einer Vielzahl von zweiten Öffnungen (26E_1, 26E_2), die auf der ersten plattenförmigen Einheit (21, 26_1, 5) stapelförmig angeordnet ist, um den zweiten Öffnungen (26E_1, 26E_2) zu ermöglichen, mit den ersten Öffnungen (21E_1, 21E_2) in Verbindung zu stehen;
    eine dritte plattenförmige Einheit (23, 26_3), die auf der zweiten plattenförmigen Einheit stapelförmig angeordnet ist, wobei die dritte plattenförmige Einheit Folgendes umfasst:
    ein drittes plattenförmiges Element (23) mit dritten Öffnungen, deren Größe größer ist als die Größe der entsprechenden zweiten Öffnungen (26E_1, 26E_2),
    ein Mantelelement (26_3), das keine Öffnungen an einem Teil aufweist, der den dritten Öffnungen zugewandt ist, und auf dem dritten plattenförmigen Element stapelförmig angeordnet ist, und
    Überbrückungsströmungsdurchlässe (23E), die jeweils durch eine entsprechende dritte Öffnung und das Mantelelement (26_3) gebildet sind und jeweils ausgelegt sind, um zu ermöglichen, dass eine zweite Öffnung (26E_1) der Vielzahl von zweiten Öffnungen (26E_1, 26E_2), die der Vielzahl von ersten Rohren (4) entsprechen, mit einer zweiten Öffnung (26E_2) der Vielzahl von zweiten Öffnungen (26E_1, 26E_2), die der Vielzahl von zweiten Rohren (7) entsprechen, in Verbindung stehen;
    wobei ein Querschnittsbereich von jeder der zweiten Öffnungen (26E_1, 26E_2) kleiner ist als ein Querschnittsbereich von jeder der ersten Öffnungen (21E_1, 21E_2),
    dadurch gekennzeichnet, dass die Sammelkammer vom Stapeltyp ferner eine Vielzahl von Umkehr-Strömungsdurchlässen (2E) zur Umkehr von Strömungen des Fluids, das durch die Vielzahl von ersten Rohren (4) und die Vielzahl von zweiten Rohren (7) strömt, umfasst, wobei
    jeder Umkehr-Strömungsdurchlass (2E) aus ersten Öffnungen (21E_1, 21E_2) aus der Vielzahl von ersten Öffnungen, aus zweiten Öffnungen (26E_1, 26E_2) aus der Vielzahl von zweiten Öffnungen, und aus einem Überbrückungsströmungsdurchlass der Überbrückungsströmungsdurchlässe (23E) gebildet ist, und wobei
    die Vielzahl von Umkehr-Strömungsdurchlässen (2E) derart angeordnet ist, dass Fluid, das durch die Vielzahl von ersten Rohren (4) strömt, in die Vielzahl von Umkehr-Strömungsdurchlässen (2E) der Sammelkammer vom Stapeltyp strömt, um umgekehrt zu werden, wodurch das Fluid von dort in Richtung der Vielzahl der zweiten Rohre (7) strömt.
  2. Wärmetauscher (1) nach Anspruch 1, wobei eine Mittelachse von jeder der ersten Öffnungen (21E_1, 21E_2) und eine Mittelachse einer entsprechenden der zweiten Öffnungen (26E_1, 26E_2), zueinander versetzt angeordnet sind.
  3. Wärmetauscher (1) nach Anspruch 2, wobei eine Mittelachse der zweiten Öffnungen (26E_1), die der Vielzahl von ersten Rohren (4) entsprechen, zu einer Mittelachse der ersten Öffnungen, die der Vielzahl von ersten Rohren (4) entsprechen, in Richtung der Vielzahl von zweiten Rohren (7) versetzt angeordnet ist.
  4. Wärmetauscher (1) nach einem der Ansprüche 1 bis 3, wobei die erste plattenförmige Einheit (21, 26_1, 5), die zweite plattenförmige Einheit (26_2) und die dritte plattenförmige Einheit (23, 26_3) Folgendes umfassen:
    Mantelelemente mit einem darauf aufgebrachten Lötmaterial; und
    unbedeckte Elemente, auf die kein Lötmaterial aufgebracht wurde, und
    wobei die Mantelelemente und die unbedeckten Elemente abwechselnd gestapelt sind.
  5. Wärmetauscher (1) nach einem der Ansprüche 1 bis 4, wobei die Vielzahl von ersten Rohren (4) und die Vielzahl von zweiten Rohren (7) jeweils eine Vielzahl von darin ausgebildeten Strömungsdurchlässen (30) aufweisen.
  6. Wärmetauscher (1) nach einem der Ansprüche 1 bis 5, wobei der Querschnittsbereich von jeder der zweiten Öffnungen (26E_1, 26E_2) kleiner ist als ein Querschnittsbereich, der einem aus der Vielzahl von ersten Rohren (4) und der Vielzahl von zweiten Rohren (7) entspricht.
  7. Wärmetauscher (1) nach einem der Ansprüche 1 bis 6, wobei der Querschnittsbereich von jeder der zweiten Öffnungen (26E_1, 26E_2) orthogonal auf eine Mittelachse eines Strömungsdurchlasses des entsprechenden einen aus der Vielzahl von ersten und zweiten Rohren steht.
  8. Wärmetauscher (1) nach einem der Ansprüche 1 bis 7, wobei jede der zweiten Öffnungen (26E_1, 26E_2) kreisförmig ist.
  9. Wärmetauscher (1) nach einem der Ansprüche 1 bis 7, wobei
    jedes aus der Vielzahl von ersten Rohren (4) und der Vielzahl von zweiten Rohren (7) ein flaches Rohr umfasst,
    jede der zweiten Öffnungen (26E_1, 26E_2) eine flache Form aufweist, in der eine Richtung einer Hauptachse von jeder der zweiten Öffnungen (26E_1, 26E_2) mit einer Richtung einer Hauptachse des flachen Rohres übereinstimmt, und
    eine Breite von jeder der zweiten Öffnungen (26E_1, 26E_2) in der Richtung ihrer Hauptachse kleiner ist als eine Breite des flachen Rohrs in der Richtung von dessen Hauptachse.
  10. Wärmetauscher (1) nach einem der Ansprüche 1 bis 9, wobei
    jedes aus der Vielzahl von ersten Rohren (4) und der Vielzahl von zweiten Rohren (7) ein flaches Rohr umfasst, und
    zumindest eines aus einer Breite von jeder der ersten Öffnungen (26E_1, 26E_2) in einer Richtung ihrer Hauptachse und einer Breite von jeder der ersten Öffnungen (26E_1, 26E_2) in einer Richtung ihrer Nebenachse größer ist als eine entsprechende aus einer Breite des flachen Rohrs in einer Richtung von dessen Hauptachse und einer Breite des flachen Rohrs in einer Richtung von dessen Nebenachse.
  11. Klimagerät, das einen Wärmetauscher (1) nach einem der Ansprüche 1 bis 10 umfasst.
  12. Klimagerät nach Anspruch 11, wobei
    die Vielzahl von ersten Rohren (4) und die Vielzahl von zweiten Rohren (7) des Wärmetauschers (1) in einer Vielzahl von Reihen in Luftdurchtrittsrichtung angeordnet sind, und
    wenn der Wärmetauscher (1) als Verdampfer fungiert, Kühlmittel durch die Rohre auf einer luftstromaufwärtigen Seite in die Sammelkammer (2) vom Stapeltyp strömt und dann in die Rohre einer luftstromabwärtigen Seite von der Sammelkammer (2) vom Stapeltyp strömt.
EP13900071.5A 2013-12-27 2013-12-27 Wärmetauscher und klimaanlage Active EP3088831B1 (de)

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JP6388067B2 (ja) * 2016-09-29 2018-09-12 ダイキン工業株式会社 熱交換器および空気調和装置
WO2018179311A1 (ja) * 2017-03-31 2018-10-04 三菱電機株式会社 熱交換器およびそれを備えた冷凍サイクル装置
JP6819811B1 (ja) * 2019-06-28 2021-01-27 ダイキン工業株式会社 熱交換器およびヒートポンプ装置
WO2021025156A1 (ja) * 2019-08-07 2021-02-11 ダイキン工業株式会社 熱交換器およびヒートポンプ装置
EP4235058A4 (de) * 2020-10-20 2024-01-10 Mitsubishi Electric Corporation Wärmetauscher und kältekreislaufvorrichtung
AU2020476620B2 (en) * 2020-11-12 2024-07-04 Mitsubishi Electric Corporation Indoor heat exchanger and indoor unit of air-conditioning apparatus
WO2024023958A1 (ja) * 2022-07-27 2024-02-01 三菱電機株式会社 熱交換器及び冷凍サイクル装置

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JPS602087U (ja) * 1983-06-18 1985-01-09 日本軽金属株式会社 管継手
JPH09189498A (ja) * 1996-01-09 1997-07-22 Nippon Light Metal Co Ltd 熱媒体分流促進機構付ヘッダ及びその成形方法
US20020023734A1 (en) * 2000-08-09 2002-02-28 Wagner William W. Charge air cooler and method of assembling the same
JP3960233B2 (ja) * 2002-04-03 2007-08-15 株式会社デンソー 熱交換器
JP4281634B2 (ja) * 2004-06-28 2009-06-17 株式会社デンソー 冷媒蒸発器
KR20070091218A (ko) * 2005-02-02 2007-09-07 캐리어 코포레이션 헤더 내에 천공 플레이트를 갖는 열교환기
JP4852304B2 (ja) * 2005-12-14 2012-01-11 昭和電工株式会社 熱交換器
US8726976B2 (en) * 2008-02-22 2014-05-20 Liebert Corporation Laminated sheet manifold for microchannel heat exchanger
FR2947332B1 (fr) * 2009-06-25 2011-07-22 Valeo Systemes Thermiques Boite collectrice pour echangeur de chaleur ayant une aptitude au brasage amelioree
JP5545160B2 (ja) * 2010-10-07 2014-07-09 三菱電機株式会社 熱交換器
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