EP3064819B1 - Raccord de tuyaux, échangeur de chaleur et climatiseur - Google Patents

Raccord de tuyaux, échangeur de chaleur et climatiseur Download PDF

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Publication number
EP3064819B1
EP3064819B1 EP13896742.7A EP13896742A EP3064819B1 EP 3064819 B1 EP3064819 B1 EP 3064819B1 EP 13896742 A EP13896742 A EP 13896742A EP 3064819 B1 EP3064819 B1 EP 3064819B1
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EP
European Patent Office
Prior art keywords
tube
end portion
heat exchanger
fitting
windward
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
EP13896742.7A
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German (de)
English (en)
Other versions
EP3064819A1 (fr
EP3064819A4 (fr
Inventor
Shinya Higashiiue
Shigeyoshi MATSUI
Akira Ishibashi
Takashi Okazaki
Daisuke Ito
Yuki UGAJIN
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP3064819A1 publication Critical patent/EP3064819A1/fr
Publication of EP3064819A4 publication Critical patent/EP3064819A4/fr
Application granted granted Critical
Publication of EP3064819B1 publication Critical patent/EP3064819B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28F1/32—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 the means having portions engaging further tubular 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
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/089—Coatings, claddings or bonding layers made from metals or metal alloys
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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 tube fitting, a heat exchanger, and an air-conditioning apparatus.
  • Tube fittings thus far developed include a type having a through portion formed therethrough, to a first end portion of which a flat tube is connected and to a second end portion of which a tube different in cross-sectional shape from the flat tube, for example a round tube, is connected.
  • the flat tube includes a plurality of flow paths aligned in the direction of the major axis (see, for example, Patent Literature 1).
  • JP2012107841A which discloses a heat exchanger according to the preamble of claim 1, provides a fin tube type heat exchanger capable of suppressing an unbalance state of the dryness of refrigerants in a plurality of refrigerant routes, and to provide an air conditioner using the heat exchanger.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2013-142454 (Paragraph [0009], Fig. 1, Fig. 2 )
  • a fluid flowing through the tube different in cross-sectional shape from the flat tube may be subjected to inertial force acting in a direction parallel to the major axis of the flat tube, in which case the balance among the flows of fluid flowing into each of the flow paths formed in the flat tube may fluctuate.
  • the fluid flowing through the tube different in cross-sectional shape from the flat tube is refrigerant in a two-phase gas-liquid, the fluctuation of the balance becomes more prominent.
  • the central axis of the first end portion to which the flat tube is connected and the central axis of the second end portion, to which the tube different in cross-sectional shape from the flat tube is connected coincide with each other, and therefore there is no way to cope with the fluctuation of the balance among the flows of fluid flowing into each of the flow paths formed in the flat tube.
  • the balance among the flows of fluid flowing into the plurality of flow paths in the flat tube is unable to be optimized.
  • the present invention has been accomplished in view of the foregoing problem, and provides a heat exchanger according to claim 1.
  • the tube fitting according to the present invention even when a fluid flowing through the tube different in cross-sectional shape from the flat tube is subjected to inertial force acting in a direction parallel to the major axis of the flat tube, the balance among the flows of fluid flowing into each of the flow paths formed in the flat tube can be optimized, since the central axis of the first end portion of the through portion and the central axis of the second end portion of the through portion are deviated from each other.
  • the heat exchanger including the tube fitting according to the present invention is employed in an air-conditioning apparatus in the following description, the heat exchanger may be incorporated in another refrigeration cycle apparatus having a refrigerant circuit.
  • the heat exchanger according to the present invention is exemplified by an outdoor heat exchanger of the air-conditioning apparatus in the description given hereunder, the heat exchanger may be an indoor heat exchanger of the air-conditioning apparatus.
  • the air-conditioning apparatus cited hereunder is configured to be switched between a heating operation and a cooling operation, the air-conditioning apparatus may be configured to perform only either of the heating operation and the cooling operation.
  • Fig. 1 is a perspective view of the heat exchanger according to Embodiment 1.
  • the heat exchanger 1 includes a heat exchange unit 2 and a branch/junction section 3.
  • the heat exchange unit 2 includes a windward heat exchange unit 21 located windward in the flow direction of air passing through the heat exchange unit 2 (blank arrow in Fig. 1 ), and a leeward heat exchange unit 31 located leeward in the air flow direction.
  • the windward heat exchange unit 21 includes a plurality of windward heat transfer tubes 22, and a plurality of windward fins 23 respectively joined to the windward heat transfer tubes 22, for example by brazing.
  • the leeward heat exchange unit 31 includes a plurality of leeward heat transfer tubes 32, and a plurality of leeward fins 33 respectively joined to the leeward heat transfer tubes 32, for example by brazing.
  • the heat exchange unit 2 may be constituted of two rows, namely a row of the windward heat exchange unit 21 and a row of the leeward heat exchange unit 31, or three or more rows.
  • the windward heat transfer tubes 22 and the leeward heat transfer tubes 32 are flat tubes, each including a plurality of flow paths aligned in the direction of the major axis.
  • Each of the plurality of windward heat transfer tubes 22 and the plurality of leeward heat transfer tubes 32 is bent in a hair-pin shape between a first end portion and a second end portion, so as to form a turnback section 22a, 32a.
  • the windward heat transfer tubes 22 and the leeward heat transfer tubes 32 are arranged in a plurality of columns stacked in a direction intersecting the flow of air passing through the heat exchange unit 2 (blank arrow in Fig. 1 ).
  • the first end portion and the second end portion of each of the windward heat transfer tubes 22 and the leeward heat transfer tubes 32 are aligned so as to oppose the branch/junction section 3.
  • the branch/junction section 3 includes a stacked header 51 and a cylindrical header 61.
  • the stacked header 51 and the cylindrical header 61 are aligned in the flow direction of air passing through the heat exchange unit 2 (blank arrow in Fig. 1 ).
  • a non-illustrated refrigerant tube is connected to the stacked header 51, via a joint tube 52.
  • a non-illustrated refrigerant tube is also connected to the cylindrical header 61, via a joint tube 62.
  • the joint tube 52 and the joint tube 62 are, for example, round tubes.
  • the stacked header 51 includes therein a branch/junction flow path 51a, and is connected to the windward heat exchange unit 21.
  • the branch/junction flow path 51a serves as branch flow path for distributing the refrigerant received through the non-illustrated refrigerant tube to the plurality of windward heat transfer tubes 22 in the windward heat exchange unit 21.
  • the branch/junction flow path 51a serves as junction flow path for merging the refrigerant received from each of the windward heat transfer tubes 22 in the windward heat exchange unit 21 and passing the merged flow to the non-illustrated refrigerant tube.
  • the stacked header 51 corresponds to the "header located on a windward side" in the present invention.
  • the cylindrical header 61 includes therein a branch/junction flow path 61a, and is connected to the leeward heat exchange unit 31.
  • the branch/junction flow path 61a serves as branch flow path for distributing the refrigerant received through the non-illustrated refrigerant tube to the plurality of leeward heat transfer tubes 32 in the leeward heat exchange unit 31.
  • the branch/junction flow path 61a serves as junction flow path for merging the refrigerant received from each of the leeward heat transfer tubes 32 in the leeward heat exchange unit 31 and passing the merged flow to the non-illustrated refrigerant tube.
  • the cylindrical header 61 corresponds to the "header located on a leeward side" in the present invention.
  • Fig. 2 is an exploded perspective view of the stacked header of the heat exchanger according to Embodiment 1. Arrows in Fig. 2 indicate the flow of the refrigerant realized when the branch/junction flow path 51a of the stacked header 51 serves as branch flow path.
  • the stacked header 51 includes a first plate member 53 including a flow path segment 53a, a plurality of second plate members 54_1 to 54_3 respectively including flow path segments 54a_1 to 54a_3, and a third plate member 55 including a plurality of flow path segments 55a, the first, second, and third plate members being stacked via clad members 56_1 to 56_4 each including one or more flow path segments 56a, sequentially interposed between the plate members.
  • a braze material is applied to one or both surfaces of the clad members 56_1 to 56_4.
  • the first plate member 53, the plurality of second plate members 54_1 to 54_3, the third plate member 55, and the plurality of clad members 56_1 to 56_4 may be collectively referred to as "plate member".
  • the flow path segments 53a, 55a, 56a are circular through holes.
  • Each of the flow path segments 54a_1 to 54a_3 is a linear through slot in which a first end portion and a second end portion are located at different heights in the gravity direction (for example, Z-shape or S-shape).
  • the non-illustrated refrigerant tube is connected to the flow path segment 53a, via the joint tube 52.
  • the windward heat transfer tubes 22 are respectively connected to the flow path segments 55a, via a joint tube 57.
  • the joint tube 57 is, for example, a round tube or an elliptical tube.
  • the flow path segment 56a of the clad member 56_1 is formed so as to oppose the flow path segment 53a.
  • the flow path segments 56a of the clad member 56_4 are formed so as to oppose the respective flow path segments 55a.
  • the first end portion and the second end portion of the flow path segments 54a_1 to 54a_3 are located so as to oppose the flow path segment 56a of one of the clad members 56_2 to 56_4 stacked on the side of the windward heat exchange unit 21.
  • a section of each of the flow path segments 54a_1 to 54a_3 between the first end portion and the second end portion is located so as to oppose the flow path segment 56a of one of the clad member 56_1 to 56_3 stacked on the opposite side of the windward heat exchange unit 21.
  • the branch/junction flow path 51a serves as branch flow path when the refrigerant flows in the direction of the arrows in Fig. 2 , and serves as junction flow path when the refrigerant flows in the direction opposite to the arrows.
  • the refrigerant which has entered the flow path segment 53a through the joint tube 52 flows into the section between the first end portion and the second end portion of the flow path segment 54a_1 through the flow path segment 56a, thereby colliding with the surface of the clad member 56_2 and being branched in two directions.
  • the refrigerant thus branched flows out through the first end portion and the second end portion of the flow path segment 54a_1 and flows into the section between the first end portion and the second end portion of the flow path segment 54a_2 through the flow path segments 56a, thereby colliding with the surface of the clad member 56_3 and being branched in two directions.
  • the refrigerant thus branched flows out through the first end portion and the second end portion of the flow path segment 54a_2 and flows into the section between the first end portion and the second end portion of the flow path segment 54a_3 through the flow path segments 56a, thereby colliding with the surface of the clad member 56_4 and being branched in two directions.
  • the refrigerant branched as above flows out through the first end portion and the second end portion of the flow path segment 54a_3, and flows into each of the joint tubes 57 through the corresponding flow path segment 56a and the flow path segment 55a.
  • the refrigerant which has entered the flow path segment 55a through the joint tube 57 passes through the flow path segment 56a and flows into the first end portion and the second end portion of the flow path segment 54a_3, and then into the flow path segment 56a communicating with the section between the first end portion and the second end portion of the flow path segment 54a_3, thus to be merged together.
  • the refrigerant thus merged flows into the first end portion and the second end portion of the flow path segment 54a_2, and then into the flow path segment 56a communicating with the section between the first end portion and the second end portion of the flow path segment 54a_2, thus to be merged together.
  • the refrigerant thus merged flows into the first end portion and the second end portion of the flow path segment 54a_1, and then into the flow path segment 56a communicating with the section between the first end portion and the second end portion of the flow path segment 54a_1, thus to be merged together.
  • the refrigerant merged as above flows into the joint tube 52 through the flow path segment 53a.
  • first plate member 53, the second plate members 54_1 to 54_3, and the third plate member 55 may be directly stacked on each other without the clad members 56_1 to 56_4 being interposed.
  • the flow path segments 56a serve as a refrigerant isolation flow path, and assures the isolation of the refrigerant flows passing through the flow path segments 53a, 54a_1 to 54a_3, and 55a.
  • each of the first plate member 53, the second plate member 54_1 to 54_3, and the third plate member 55 may be coupled with the corresponding clad member 56_1 to 56_4, and such plate members may be directly stacked on each other.
  • Fig. 3 is a perspective view of the cylindrical header of the heat exchanger according to Embodiment 1. Arrows in Fig. 3 indicate the flow of the refrigerant realized when the branch/junction flow path 61a of the cylindrical header 61 serves as junction flow path.
  • the cylindrical header 61 includes a cylindrical portion 63 having the both end portions closed, and aligned such that the axial direction is parallel to the gravity direction.
  • the axial direction of the cylindrical portion 63 is parallel to the gravity direction.
  • Arranging the cylindrical header 61 so as to make the axial direction of the cylindrical portion 63 parallel to the longitudinal direction of the stacked header 51 allows reduction of the footprint of the branch/junction section 3.
  • the cylindrical portion 63 may be an oval tube having an elliptical cross-section.
  • the non-illustrated refrigerant tube is connected to the sidewall of the cylindrical portion 63, via the joint tube 62.
  • a plurality of joint tubes 64 respectively connected to the leeward heat transfer tubes 32, are connected.
  • the joint tube 64 is, for example, a round tube or an elliptical tube.
  • the cylindrical portion 63 includes therein the branch/junction flow path 61a.
  • the branch/junction flow path 61a serves as junction flow path when the refrigerant flows in the direction of the arrows in Fig. 3 , and serves as branch flow path when the refrigerant flows in the direction opposite to the arrows.
  • the branch/junction flow path 61a serves as junction flow path
  • the refrigerant which has entered the plurality of joint tubes 64 flows through inside the cylindrical portion 63 and then flows into the joint tube 62, thus to be merged.
  • the branch/junction flow path 61a serves as branch flow path
  • the refrigerant flowing in through the joint tube 62 passes through inside the cylindrical portion 63 and then flows into each of the joint tubes 64, thus to be branched.
  • a circumferential position of the cylindrical portion 63 where the joint tube 62 is connected and circumferential positions where the joint tubes 64 are connected are not opposed across the center of the cylindrical portion 63.
  • Such a configuration facilitates the refrigerant to evenly flow into the plurality of joint tubes 64, when the branch/junction flow path 61a serves as branch flow path.
  • Fig. 4 and Fig. 5 are schematic drawings illustrating the connection between the heat exchange unit and the branch/junction section of the heat exchanger according to Embodiment 1.
  • Fig. 5 is a cross-sectional view taken along a line A-A in Fig. 4 .
  • a windward concentric tube fitting 41A is joined to the first end portion 22b of the windward heat transfer tube 22.
  • a windward eccentric tube fitting 41B is joined to the second end portion 22c of the windward heat transfer tube 22.
  • a leeward concentric tube fitting 42A is joined to the second end portion 32c of the leeward heat transfer tube 32.
  • a leeward eccentric tube fitting 42B is joined to the first end portion 32b of the leeward heat transfer tube 32.
  • the joint tube 57 of the stacked header 51 is connected to the windward concentric tube fitting 41A.
  • the joint tube 64 of the cylindrical header 61 is connected to the leeward concentric tube fitting 42A.
  • the windward eccentric tube fitting 41B and the leeward eccentric tube fitting 42B are connected to each other via a row joint tube 43.
  • the row joint tube 43 is, for example, a round tube or an elliptical tube, bent in an arcuate shape.
  • Fig. 6 is a schematic drawing illustrating the connection between the heat exchange unit and the branch/junction section of the heat exchanger according to a variation of Embodiment 1.
  • Fig. 6 is a cross-sectional view from a position corresponding to the line A-A in Fig. 4 .
  • the windward heat transfer tubes 22 and the leeward heat transfer tubes 32 may be arranged such that, when viewed from a lateral position of the heat exchanger 1, the first end portion 22b and the second end portion 22c of the windward heat transfer tube 22 and the first end portion 32b and the second end portion 32c of the leeward heat transfer tube 32 are formed in a staggered manner as shown in Fig. 5 , or form a checker pattern as shown in Fig. 6 .
  • Fig. 7 and Fig. 8 are schematic drawings illustrating the connection between the heat exchange unit and the branch/junction section of the heat exchanger according to another variation of Embodiment 1.
  • Fig. 7 and Fig. 8 are cross-sectional views from a position corresponding to the line A-A in Fig. 4 .
  • the second end portion 22c of the windward heat transfer tube 22 and the first end portion 22b of the windward heat transfer tube 22 of the adjacent column may be connected to each other via a windward column joint tube 44 and the windward concentric tube fitting 41A, and the second end portion 32c of the leeward heat transfer tube 32 and the first end portion 32b of the leeward heat transfer tube 32 of the adjacent column may be connected via a leeward column joint tube 45 and the leeward concentric tube fitting 42A.
  • the windward column joint tube 44 and the leeward column joint tube 45 are, for example, round tubes or elliptical tubes bent in an arcuate shape.
  • the first end portion of the windward heat transfer tube 22 and the first end portion of the adjacent windward heat transfer tube 22 may be connected via the windward column joint tube 44 and the windward concentric tube fitting 41A, and the first end portion of the leeward heat transfer tube 32 and the first end portion of the adjacent leeward heat transfer tube 32 may be connected via the leeward column joint tube 45 and the leeward concentric tube fitting 42A, so as to allow the refrigerant to turn the flow direction.
  • Fig. 9 is a schematic drawing showing the configuration of the windward concentric tube fitting and the leeward concentric tube fitting of the heat exchanger according to Embodiment 1.
  • Fig. 9 includes a front cross-sectional view of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A, a side cross-sectional view thereof, and an upper plan view and a bottom view thereof.
  • the tubes respectively connected to a first end portion 72 and a second end portion 73 of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A are indicated by broken lines.
  • round tubes are employed as joint tube 57 of the stacked header 51 and joint tube 64 of the cylindrical header 61.
  • the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A each include a through portion 71.
  • the first end portion 72 of the through portion 71 has a cross-sectional shape that matches the cross-sectional shape of the windward heat transfer tube 22 or the leeward heat transfer tube 32.
  • the second end portion 73 of the through portion 71 has a cross-sectional shape that matches the cross-sectional shape of the joint tube 57 of the stacked header 51 or the joint tube 64 of the cylindrical header 61.
  • the central axis of the first end portion 72 and the central axis of the second end portion 73 coincide with each other.
  • the inner diameter D1 of the second end portion 73 is smaller than or equal to the inner diameter W1 of the first end portion 72 taken along the major axis.
  • the inner diameter D2 of the second end portion 73 is larger than or equal to the inner diameter W2 of the first end portion 72 taken along the minor axis. Accordingly, the inner diameter D (D1, D2) of the cross-section of the second end portion 73 with respect to the entire circumference thereof may be expressed as W2 ⁇ D ⁇ W1.
  • the flow path cross-sectional area (d1 2 ⁇ ⁇ /4) of the joint tube 57 of the stacked header 51 and the joint tube 64 of the cylindrical header 61 is larger than the flow path cross-sectional area (w1 ⁇ w2 ⁇ number of flow paths) of the windward heat transfer tube 22 and the leeward heat transfer tube 32.
  • D1 may be either larger or smaller than D2.
  • the foregoing configuration not only enables reduction in size of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A by making D1 smaller, but also suppresses pressure loss of the refrigerant flowing through the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A by increasing D2 so as to allow a tube having a larger flow path cross-sectional area to be connected.
  • the configuration that can be expressed as W2 ⁇ D ⁇ W1 contributes to improving the degree of freedom in bending work of the joint tube 57 of the stacked header 51 and the joint tube 64 of the cylindrical header 61.
  • Fig. 10 is a schematic drawing showing a configuration of the windward concentric tube fitting and the leeward concentric tube fitting of the heat exchanger according to a comparative example.
  • Fig. 10 is a front cross-sectional view of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A.
  • the tubes respectively connected to the first end portion 72 and the second end portion 73 of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A are indicated by broken lines.
  • the through portion 71 includes a shape transition section 74 located between the first end portion 72 and the second end portion 73.
  • the shape transition section 74 Through the shape transition section 74, the cross-sectional shape of the inner circumferential surface of the first end portion 72 is gradually translated into the cross-sectional shape of the inner circumferential surface of the second end portion 73.
  • the shape transition section 74 is not provided in the through portion 71, in other words when the first end portion 72 and the second end portion 73 directly communicate with each other as shown in Fig. 10 , a vortex flow is generated at corner portions of the first end portion 72, which incurs pressure loss of the refrigerant flowing through the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A.
  • forming the shape transition section 74 in the region between the first end portion 72 and the second end portion 73 of the through portion 71 suppresses such a phenomenon.
  • the joint tube 57 of the stacked header 51 and the joint tube 64 of the cylindrical header 61 are inserted to the boundary between the second end portion 73 and the shape transition section 74, when joined to the tube fitting 41A, 42A.
  • the region in the inner circumferential surface of the second end portion 73 where the outer circumferential surface of the joint tube 57 of the stacked header 51 or the joint tube 64 of the cylindrical header 61 is joined is closely adjacent to the shape transition section 74.
  • the refrigerant flowing in through the joint tube 57 of the stacked header 51 or the joint tube 64 of the cylindrical header 61 can flow into the windward heat transfer tube 22 or the leeward heat transfer tube 32 without passing over a stepped portion, thereby being more effectively exempted from suffering pressure loss.
  • the second end portion 73 can be formed in a reduced axial length, which leads to reduction in size of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A.
  • Fig. 11 is a schematic drawing showing the configuration of the windward eccentric tube fitting and the leeward eccentric tube fitting of the heat exchanger according to Embodiment 1.
  • Fig. 11 includes a front cross-sectional view of the windward eccentric tube fitting 41B and the leeward eccentric tube fitting 42B, and associated components.
  • the windward eccentric tube fitting 41B and the leeward eccentric tube fitting 42B basically have the same configuration as that of the windward concentric tube fitting 41A and the leeward concentric tube fitting 42A, however are different therefrom in that the central axis of the first end portion 72 and the central axis of the second end portion 73 are deviated from each other, as shown in Fig. 11 .
  • the eccentricity Z may be expressed as 0 ⁇ Z ⁇ W3/2, where W3 represents the outer diameter taken along the major axis of the windward heat transfer tube 22 and the leeward heat exchanger 32
  • the central axes are deviated such that the distance between the central axis of the second end portion 73 of the through portion 71 of the windward eccentric tube fitting 41B and the central axis of the leeward heat transfer tube 32 becomes shorter than the distance between the central axis of the first end portion 72 of the through portion 71 of the windward eccentric tube fitting 41B and the central axis of the leeward heat transfer tube 32.
  • the central axes are deviated such that the distance between the central axis of the second end portion 73 of the through portion 71 of the leeward eccentric tube fitting 42B and the central axis of the windward heat transfer tube 22 becomes shorter than the distance between the central axis of the first end portion 72 of the through portion 71 of the leeward eccentric tube fitting 42B and the central axis of the windward heat transfer tube 22.
  • Fig. 12 and Fig. 13 are block diagrams showing the configuration of the air-conditioning apparatus including the heat exchanger according to Embodiment 1.
  • Fig. 12 represents the case where the air-conditioning apparatus 91 performs a heating operation.
  • Fig. 13 represents the case where the air-conditioning apparatus 91 performs a cooling operation.
  • the air-conditioning apparatus 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger (heat source-side heat exchanger) 94, an expansion device 95, an indoor heat exchanger (load-side heat exchanger) 96, an outdoor fan (heat source-side fan) 97, an indoor fan (load-side fan) 98, and a controller 99.
  • the compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion device 95, and the indoor heat exchanger 96 are connected via a refrigerant pipe, so as to form a refrigerant circuit.
  • the four-way valve 93 may be another type of flow switching device.
  • the outdoor heat exchanger 94 corresponds to the heat exchanger 1.
  • the stacked header 51 is located on the windward side and the cylindrical header 61 is located on the leeward side, in the airflow generated when the outdoor fan 97 is driven.
  • the outdoor fan 97 may be provided either windward or leeward of the heat exchanger 1.
  • the controller 99 for example the compressor 92, the four-way valve 93, the expansion device 95, the outdoor fan 97, the indoor fan 98, and various sensors are connected.
  • the controller 99 switches the flow path in the four-way valve 93, thereby switching between the heating operation and the cooling operation.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 92 flows into the indoor heat exchanger 96 through the four-way valve 93, and is condensed through heat exchange with air supplied by the indoor fan 98, thereby heating the indoor air.
  • the condensed refrigerant turns into high-pressure subcooled liquid refrigerant and flows out of the indoor heat exchanger 96, and then turns into low-pressure two-phase gas-liquid refrigerant in the expansion device 95.
  • the low-pressure two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 94, and is evaporated through heat exchange with air supplied by the outdoor fan 97.
  • the evaporated refrigerant turns into low-pressure superheated gas refrigerant and flows out of the outdoor heat exchanger 94, and is then sucked into the compressor 92 through the four-way valve 93.
  • the outdoor heat exchanger 94 acts as evaporator in the heating operation.
  • the refrigerant flows into the branch/junction flow path 51a of the stacked header 51 thus to be branched, and flows into the windward heat transfer tube 22 of the windward heat exchange unit 21, through the windward concentric tube fitting 41A.
  • the refrigerant which has entered the windward heat transfer tube 22 sequentially passes through the windward eccentric tube fitting 41B, the row joint tube 43, and the leeward eccentric tube fitting 42B, and flows into the leeward heat transfer tube 32 of the leeward heat exchange unit 31.
  • the refrigerant which has entered the leeward heat transfer tube 32 passes through the leeward concentric tube fitting 42A and flows into the branch/junction flow path 61a of the cylindrical header 61, thus to be merged.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 92 flows into the outdoor heat exchanger 94 through the four-way valve 93, and is condensed through heat exchange with air supplied by the outdoor fan 97.
  • the condensed refrigerant turns into high-pressure subcooled liquid refrigerant or low-quality refrigerant, and flows out of the outdoor heat exchanger 94 and then turns into low-pressure two-phase gas-liquid refrigerant in the expansion device 95.
  • the low-pressure two-phase gas-liquid refrigerant flows into the indoor heat exchanger 96, and is evaporated through heat exchange with air supplied by the indoor fan 98, thereby cooling the indoor air.
  • the evaporated refrigerant turns into low-pressure superheated gas refrigerant and flows out of the indoor heat exchanger 96, and is then sucked into the compressor 92 through the four-way valve 93.
  • the outdoor heat exchanger 94 acts as condenser in the cooling operation.
  • the refrigerant flows into the branch/junction flow path 61a of the cylindrical header 61 thus to be branched, and flows into the leeward heat transfer tube 32 of the leeward heat exchange unit 31, through the leeward concentric tube fitting 42A.
  • the refrigerant which has entered the leeward heat transfer tube 32 sequentially passes through the leeward eccentric tube fitting 42B, the row joint tube 43, and the windward eccentric tube fitting 41B, and flows into the windward heat transfer tube 22 of the windward heat exchange unit 21.
  • the refrigerant which has entered the windward heat transfer tube 22 passes through the windward concentric tube fitting 41A and flows into the branch/junction flow path 51a of the stacked header 51, thus to be merged.
  • the central axis of the first end portion 72 and the central axis of the second end portion 73 are deviated from each other, in the windward eccentric tube fitting 41B and the leeward eccentric tube fitting 42B. Therefore, the balance among the flows of flows of the fluid flowing into the windward heat transfer tube 22 and the leeward heat transfer tube 32 can be optimized.
  • Fig. 14 and Fig. 15 are a schematic drawing and a graph respectively, illustrating liquid distribution of the refrigerant flowing into the leeward heat transfer tube, realized when the heat exchanger according to Embodiment 1 acts as evaporator.
  • the flow direction of the refrigerant is indicated by solid arrows.
  • the refrigerant flows parallel to the airflow generated by driving the outdoor fan 97 as shown in Fig. 14 and Fig. 15 , in other words flows from the windward heat transfer tube 22 to the leeward heat transfer tube 32, and then flows into the leeward eccentric tube fitting 42B through the row joint tube 43 in the two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant flowing through the row joint tube 43 is subjected to centrifugal force, so that a high-density portion of the refrigerant flows along the outer side and a low-density portion of the refrigerant flows along the inner side.
  • the eccentricity Z between the central axis of the first end portion 72 and the central axis of the second end portion 73 is larger than 0 in the leeward eccentric tube fitting 42B, and therefore a major portion of the liquid refrigerant flowing into the leeward eccentric tube fitting 42B flows toward the point S in the leeward heat transfer tube 32.
  • the thermal load (heat exchange amount) of the airflow generated by driving the outdoor fan 97 is larger on the windward side, and therefore distributing the liquid refrigerant to the flow path openings of the flat tube such that a major portion thereof flows toward the point S of the leeward heat transfer tube 32, in other words into the flow path on the windward side, allows the liquid refrigerant to be more efficiently evaporated, thereby improving the heat exchange efficiency.
  • the row joint tube 43 can be formed with a smaller curvature radius so as to increase the capacity of the heat exchange unit 2, and therefore the heat exchange efficiency can be further improved. The improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance. Further, the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.
  • Fig. 16 and Fig. 17 are a schematic drawing and a graph respectively, illustrating gas distribution of the refrigerant flowing into the windward heat transfer tube, realized when the heat exchanger according to Embodiment 1 acts as condenser.
  • the flow direction of the refrigerant is indicated by solid arrows.
  • the refrigerant flows against the airflow generated by driving the outdoor fan 97 as shown in Fig. 16 and Fig. 17 , in other words the refrigerant flows from the leeward heat transfer tube 32 to the windward heat transfer tube 22, and then flows into the windward eccentric tube fitting 41B through the row joint tube 43 in the two-phase gas-liquid state.
  • the two-phase gas-liquid refrigerant flowing through the row joint tube 43 is subjected to centrifugal force, so that a high-density portion of the refrigerant flows along the outer side and a low-density portion of the refrigerant flows along the inner side.
  • the eccentricity Z between the central axis of the first end portion 72 and the central axis of the second end portion 73 is larger than 0 in the windward eccentric tube fitting 41B, and therefore a major portion of the gas refrigerant flowing into the windward eccentric tube fitting 41B flows toward the point L in the windward heat transfer tube 22, since a major portion of liquid refrigerant flows toward the point S.
  • the thermal load (heat exchange amount) of the airflow generated by driving the outdoor fan 97 is larger on the windward side, and therefore distributing the gas refrigerant to the flow path openings of the flat tube such that a major portion thereof flows toward the point L of the windward heat transfer tube 22, in other words into the flow path on the windward side, allows the gas refrigerant to be more efficiently condensed, thereby improving the heat exchange efficiency.
  • the row joint tube 43 can be formed with a smaller curvature radius and the capacity of the heat exchange unit 2 can be increased, and therefore the heat exchange efficiency can be further improved. The improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance. Further, the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.
  • the inner diameter D (D1, D2) of the cross-section of the second end portion 73 with respect to the entire circumference thereof is set to W2 ⁇ D ⁇ W1, where W1 represents the inner diameter of the first end portion 72 taken along the major axis and W2 represents the inner diameter thereof taken along the minor axis, reduction in size and reduction in pressure loss can both be realized. Accordingly, the spacing between the heat exchange unit 2 and the branch/junction section 3 can be narrowed so as to increase the capacity of the heat exchange unit 2, and therefore the heat exchange efficiency can be improved. The improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance. Further, the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.
  • the shape transition section 74 is provided in the region between the first end portion 72 and the second end portion 73 of the through portion 71, and the region in the inner circumferential surface of the second end portion 73 where the outer circumferential surface of the joint tube 57 of the stacked header 51, the joint tube 64 of the cylindrical header 61, or the row joint tube 43 is joined is closely adjacent to the shape transition section 74, and therefore reduction in size and reduction in pressure loss can both be realized.
  • the spacing between the heat exchange unit 2 and the branch/junction section 3 can be narrowed so as to increase the capacity of the heat exchange unit 2, and therefore the heat exchange efficiency can be improved.
  • the improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance.
  • the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.
  • Fig. 18 is a perspective view of the heat exchanger according to Embodiment 2.
  • the heat exchange unit 2 only includes the windward heat exchange unit 21.
  • the windward heat transfer tubes 22 are arranged in a plurality of columns in a direction intersecting the flow direction of air passing through the heat exchange unit 2 (blank arrow in Fig. 18 ).
  • Each of the windward heat transfer tubes 22 is bent in a hair-pin shape between the first end portion and the second end portion, so as to form a turnback section 22a.
  • the first end portion and the second end portion of each of the windward heat transfer tubes 22 are aligned so as to oppose the stacked header 51.
  • the stacked header 51 includes therein a branch/junction flow path 51a, and is connected to the windward heat exchange unit 21.
  • the branch/junction flow path 51a serves as branch flow path for distributing the refrigerant received through a non-illustrated refrigerant tube to the plurality of windward heat transfer tubes 22 in the windward heat exchange unit 21.
  • the branch/junction flow path 51a serves as junction flow path for merging the refrigerant received from each of the windward heat transfer tubes 22 in the windward heat exchange unit 21 and passing the merged flow to the non-illustrated refrigerant tube.
  • the cylindrical header 61 includes therein a branch/junction flow path 61a, and is connected to the windward heat exchange unit 21.
  • the branch/junction flow path 61a serves as branch flow path for distributing the refrigerant received through a non-illustrated refrigerant tube to the plurality of windward heat transfer tubes 22 in the windward heat exchange unit 21.
  • the branch/junction flow path 61a serves as junction flow path for merging the refrigerant received from each of the windward heat transfer tubes 22 in the windward heat exchange unit 21 and passing the merged flow to the non-illustrated refrigerant tube.
  • Fig. 19 and Fig. 20 are schematic drawings illustrating the connection between the heat exchange unit and the branch/junction section of the heat exchanger according to Embodiment 2.
  • Fig. 20 is a cross-sectional view taken along a line B-B in Fig. 19 .
  • each of the windward concentric tube fittings 41A is joined to the first end portion 22b or the second end portion 22c of the windward heat transfer tube 22.
  • the joint tube 57 of the stacked header 51 is connected to the windward concentric tube fitting 41A joined to the first end portion 22b of the windward heat transfer tube 22.
  • the joint tube 64 of the cylindrical header 61 is connected to the windward concentric tube fitting 41A joined to the second end portion 22c of the windward heat transfer tube 22.
  • Fig. 21 is a schematic drawing illustrating the connection between the heat exchange unit and the branch/junction section of the heat exchanger according to a variation of Embodiment 2.
  • Fig. 21 is a cross-sectional view from a position corresponding to the line B-B in Fig. 19 .
  • the second end portion 22c of the windward heat transfer tube 22 and the first end portion 22b of the windward heat transfer tube 22 of the adjacent column may be connected to each other via the windward column joint tube 44 and the windward concentric tube fitting 41A.
  • Fig. 22 is a block diagram showing the configuration of the air-conditioning apparatus including the heat exchanger according to Embodiment 2.
  • Fig. 22 represents the case where the air-conditioning apparatus 91 performs a heating operation.
  • the refrigerant flows into the branch/junction flow path 51a of the stacked header 51 thus to be branched, and flows into the windward heat transfer tube 22 of the windward heat exchange unit 21, through the windward concentric tube fitting 41A.
  • the refrigerant which has entered the windward heat transfer tube 22 passes through the windward concentric tube fitting 41A and flows into the branch/junction flow path 61a of the cylindrical header 61, thus to be merged.
  • Fig. 23 is a block diagram showing the configuration of the air-conditioning apparatus including the heat exchanger according to Embodiment 2.
  • Fig. 23 represents the case where the air-conditioning apparatus 91 performs a cooling operation.
  • the refrigerant flows into the branch/junction flow path 61a of the cylindrical header 61 thus to be branched, and flows into the windward heat transfer tube 22 of the windward heat exchange unit 21, through the windward concentric tube fitting 41A.
  • the refrigerant which has entered the windward heat transfer tube 22 passes through the windward concentric tube fitting 41A and flows into the branch/junction flow path 51a of the stacked header 51, thus to be merged.
  • the inner diameter D (D1, D2) of the cross-section of the second end portion 73 with respect to the entire circumference thereof is set to W2 ⁇ D ⁇ W1, where W1 represents the inner diameter of the first end portion 72 taken along the major axis and W2 represents the inner diameter thereof taken along the minor axis, and therefore reduction in size and reduction in pressure loss can both be realized. Accordingly, the spacing between the heat exchange unit 2 and the branch/junction section 3 can be narrowed so as to increase the capacity of the heat exchange unit 2, and consequently the heat exchange efficiency can be improved. The improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance. Further, the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.
  • the shape transition section 74 is provided in the region between the first end portion 72 and the second end portion 73 of the through portion 71, and the region in the inner circumferential surface of the second end portion 73 where the outer circumferential surface of the joint tube 57 of the stacked header 51 or the joint tube 64 of the cylindrical header 61 is joined is closely adjacent to the shape transition section 74, and therefore reduction in size and reduction in pressure loss can both be realized. Accordingly, the spacing between the heat exchange unit 2 and the branch/junction section 3 can be narrowed so as to increase the capacity of the heat exchange unit 2, and therefore the heat exchange efficiency can be improved. The improvement in heat exchange efficiency leads to improved operation efficiency of the refrigeration cycle, thereby upgrading the energy saving performance. Further, the footprint of the heat exchanger 1 can be reduced without compromising the performance level of the refrigeration cycle.

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  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
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Claims (7)

  1. Echangeur de chaleur (1) comprenant :
    un premier raccord de tube (41B) comprenant une partie débouchante (71), à une première partie d'extrémité (72) de laquelle est raccordé un premier tube plat (22) et à une seconde partie d'extrémité (73) de laquelle un tube de joint de rangée (43), différent du point de la vue de la forme transversale du premier tube plat (22), est raccordé ;
    un second raccord de tube (42B) comprenant une partie débouchante (71), à une première partie d'extrémité (72) de laquelle un second tube plat (32) est raccordé et à une seconde partie d'extrémité (73) de laquelle le tube de joint de rangée (43), différent du point de la vue de la forme transversale du second tube plat (32), est raccordé ; et
    une unité d'échange de chaleur (21, 31) comprenant le premier tube plat (22), dont au moins une partie d'extrémité (22c) est raccordée à la première partie d'extrémité (72) du premier raccord de tube (41B), et le second tube plat (32) positionné du côté du vent ou du côté sous le vent du premier tube plat (22),
    dans lequel un axe central de la première partie d'extrémité (72) et un axe central de la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22) sont déviés l'un de l'autre,
    un axe central de la première partie d'extrémité (72) et un axe central de la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32) sont déviés l'un de l'autre,
    la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22) et la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32) sont raccordées entre elles via le tube de joint de rangée (43), caractérisé par :
    une distance entre l'axe central de la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22) et un axe central du second tube plat (32) est plus courte qu'une distance entre l'axe central de la première partie d'extrémité (72) du premier raccord de tube (41B) raccordée au premier tube plat (22) et l'axe central du second tube plat (32), et
    une distance entre l'axe central de la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32) et l'axe central du premier tube plat (22) est plus courte qu'une distance entre l'axe central de la première partie d'extrémité (72) du second raccord de tube (42B) raccordée au second tube plat (32) et l'axe central du premier tube plat (22).
  2. Echangeur de chaleur (1) selon la revendication 1,
    dans lequel un diamètre interne D de la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22) dans une section transversale perpendiculaire à l'axe central par rapport à toute la circonférence est inférieur ou égal à un diamètre interne W1 de la première partie d'extrémité (72) du premier raccord de tube (41B) raccordée au premier tube plat (22) dans l'axe majeur, et égal ou supérieur à un diamètre interne W2 de la première partie d'extrémité (72) dans l'axe mineur, et
    un diamètre interne D de la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32) dans une section transversale perpendiculaire à l'axe central par rapport à toute la circonférence est inférieur ou égal à un diamètre interne W1 de la première partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32) dans l'axe majeur, et égal ou supérieur à un diamètre interne W2 de la première partie d'extrémité (72) dans l'axe mineur.
  3. Echangeur de chaleur (1) selon la revendication 1 ou 2,
    dans lequel une surface circonférentielle externe du tube de joint de rangée (43) est assemblée à une surface circonférentielle interne de la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22),
    la partie débouchante (71) du premier raccord de tube (41B) comprend une section de transition de forme (74) formée dans une région entre la première partie d'extrémité (72) du premier raccord de tube (41B) et la seconde partie d'extrémité (73) du premier raccord de tube (41B), la section de transition de forme (74) étant configurée pour faire effectuer progressivement une translation à une forme transversale de la surface circonférentielle interne de la première partie d'extrémité (72) du premier raccord de tube (41B) en une forme transversale de la surface circonférentielle interne de la seconde partie d'extrémité (73) du premier raccord de tube (41B), et
    une région dans la surface circonférentielle interne de la seconde partie d'extrémité (73) du premier raccord de tube (41B) raccordée au premier tube plat (22), où la surface circonférentielle externe du tube de joint de rangée (43) est assemblée, est adjacente à la section de transition de forme (74) du premier raccord de tube (41B),
    une surface circonférentielle externe du tube de joint de rangée (43) est assemblée à une surface circonférentielle interne de la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32),
    la partie débouchante (71) du second raccord de tube (42B) comprend une section de transition de forme (74) formée dans une région entre la première partie d'extrémité (72) du second raccord de tube (42B) et la seconde partie d'extrémité (73) du second raccord de tube (42B), la section de transition de forme (74) du second raccord de tube (42B) étant configurée afin de faire effectuer progressivement une translation à une forme transversale de la surface circonférentielle interne de la première partie d'extrémité (72) du second raccord de tube (42B) en une forme transversale de la surface circonférentielle interne de la seconde partie d'extrémité (73) du second raccord de tube (42B), et
    une région dans la surface circonférentielle interne de la seconde partie d'extrémité (73) du second raccord de tube (42B) raccordée au second tube plat (32), où la surface circonférentielle externe du tube de joint de rangée (43) est assemblée, est adjacente à la section de transition de forme (74) du second raccord de tube (42B).
  4. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 3,
    dans lequel l'unité d'échange de chaleur (21, 31) sert d'évaporateur et le second tube plat (32) est positionné du côté du vent du premier tube plat (22).
  5. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 3,
    dans lequel l'unité d'échange de chaleur (21, 31) sert de condenseur et le second tube plat (32) est positionné du côté sous le vent du premier tube plat (22).
  6. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 5,
    dans lequel une surface transversale de trajectoire d'écoulement du tube de joint de rangée (43) est supérieure à une zone transversale de trajectoire d'écoulement du premier tube plat (22) ou du second tube plat (32).
  7. Appareil de climatisation (91) comprenant un échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 6.
EP13896742.7A 2013-10-29 2013-10-29 Raccord de tuyaux, échangeur de chaleur et climatiseur Active EP3064819B1 (fr)

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PCT/JP2013/079248 WO2015063858A1 (fr) 2013-10-29 2013-10-29 Raccord de tuyaux, échangeur de chaleur et climatiseur

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EP3064819A4 EP3064819A4 (fr) 2017-05-31
EP3064819B1 true EP3064819B1 (fr) 2019-07-24

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WO (1) WO2015063858A1 (fr)

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US10054376B2 (en) * 2013-10-29 2018-08-21 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
WO2017094114A1 (fr) * 2015-12-01 2017-06-08 三菱電機株式会社 Dispositif à cycle de réfrigération
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JP6207624B2 (ja) 2017-10-04
CN105683639B (zh) 2018-01-19
WO2015063858A1 (fr) 2015-05-07
CN105683639A (zh) 2016-06-15
EP3064819A1 (fr) 2016-09-07
US20160245560A1 (en) 2016-08-25
EP3064819A4 (fr) 2017-05-31
JPWO2015063858A1 (ja) 2017-03-09

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