WO2015063858A1 - 管継手、熱交換器、及び、空気調和装置 - Google Patents

管継手、熱交換器、及び、空気調和装置 Download PDF

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Publication number
WO2015063858A1
WO2015063858A1 PCT/JP2013/079248 JP2013079248W WO2015063858A1 WO 2015063858 A1 WO2015063858 A1 WO 2015063858A1 JP 2013079248 W JP2013079248 W JP 2013079248W WO 2015063858 A1 WO2015063858 A1 WO 2015063858A1
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WO
WIPO (PCT)
Prior art keywords
pipe
pipe joint
heat exchanger
flat tube
peripheral surface
Prior art date
Application number
PCT/JP2013/079248
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
真哉 東井上
繁佳 松井
石橋　晃
岡崎　多佳志
伊東　大輔
裕樹 宇賀神
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CN201380080615.3A priority Critical patent/CN105683639B/zh
Priority to JP2015544658A priority patent/JP6207624B2/ja
Priority to PCT/JP2013/079248 priority patent/WO2015063858A1/ja
Priority to US15/026,644 priority patent/US20160245560A1/en
Priority to EP13896742.7A priority patent/EP3064819B1/en
Publication of WO2015063858A1 publication Critical patent/WO2015063858A1/ja

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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 pipe joint, a heat exchanger, and an air conditioner.
  • a penetration part is formed, a flat tube is connected to one end of the penetration part, and a pipe having a cross-sectional shape different from that of the flat pipe, for example, a circular pipe, is connected to the other end of the penetration part. Some are connected.
  • a plurality of flow paths are formed in the flat tube in the long axis direction (see, for example, Patent Document 1).
  • JP 2013-142454 A (paragraph [0009], FIGS. 1 and 2)
  • a pipe joint for example, if an inertial force of a component parallel to the long axis direction of a flat tube is acting on a fluid passing through a pipe having a cross-sectional shape different from that of the flat tube, the inertial force causes the flat tube to The balance of the fluid flowing into each formed flow path changes.
  • the fluid passing through a tube having a cross-sectional shape different from that of a flat tube is a gas-liquid two-phase refrigerant
  • the phenomenon becomes significant.
  • the central axis of one end to which the flat tube is connected and the central axis of the other end to which the tube having a different cross-sectional shape from the flat tube is connected are coaxial.
  • the change of the balance of the fluid flowing into each flow path formed in the flat tube cannot be dealt with. In other words, such a pipe joint has a problem that the balance of the fluid flowing into the plurality of flow paths of the flat tube cannot be optimized.
  • the present invention has been made against the background of the above problems, and an object thereof is to obtain a pipe joint capable of optimizing the balance of fluid flowing into a plurality of flow paths of a flat tube. Moreover, an object of this invention is to obtain the heat exchanger provided with such a pipe joint. Moreover, an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.
  • a penetrating portion is formed, a flat tube is connected to one end of the penetrating portion, and another pipe having a cross-sectional shape different from that of the flat tube is connected to the other end of the penetrating portion.
  • the central axis of the one end and the central axis of the other end are eccentric from each other.
  • FIG. 1 is a perspective view of a heat exchanger according to Embodiment 1.
  • FIG. It is a perspective view in the state which the laminated header of the heat exchanger which concerns on Embodiment 1 decomposed
  • FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1.
  • FIG. 1 It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1.
  • FIG. 2 It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure which shows the structure of the windward concentric pipe joint of the heat exchanger which concerns on Embodiment 1, and a leeward concentric pipe joint. It is a figure which shows the structure of the windward concentric pipe joint and leeward concentric pipe joint of the heat exchanger which concerns on a comparative example. It is a figure which shows the structure of the windward eccentric pipe joint and leeward eccentric pipe joint of the heat exchanger which concerns on Embodiment 1.
  • FIG. It is a figure explaining the connection of the heat exchange part and split mixing flow part of the modification of the heat exchanger which concerns on Embodiment 2.
  • FIG. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 2 is applied. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger which concerns on Embodiment 2 is applied.
  • the pipe joint which concerns on this invention is a member which comprises a heat exchanger below is demonstrated, the pipe joint which concerns on this invention may be a member which comprises another apparatus.
  • the heat exchanger provided with the pipe joint according to the present invention is applied to an air conditioner is described.
  • the present invention is not limited to such a case, and includes, for example, a refrigerant circulation circuit. You may apply to another refrigeration cycle apparatus.
  • the heat exchanger provided with the pipe joint according to the present invention is an outdoor heat exchanger of an air conditioner is described, it is not limited to such a case, and the indoor heat exchange of the air conditioner It may be a vessel.
  • an air conditioning apparatus switches between heating operation and cooling operation is demonstrated, it is not limited to such a case, You may perform only heating operation or cooling operation.
  • Embodiment 1 FIG. The heat exchanger according to Embodiment 1 will be described. ⁇ Configuration of heat exchanger> Below, the structure of the heat exchanger which concerns on Embodiment 1 is demonstrated. (Schematic configuration of heat exchanger) Below, schematic structure of the heat exchanger which concerns on Embodiment 1 is demonstrated. 1 is a perspective view of a heat exchanger according to Embodiment 1. FIG. As shown in FIG. 1, the heat exchanger 1 includes a heat exchanging unit 2 and a split blending unit 3.
  • the heat exchange unit 2 includes an upwind heat exchange unit 21 disposed on the leeward side and a leeward side disposed on the leeward side in the direction of passage of air passing through the heat exchange unit 2 (the white arrow in the figure). And a heat exchanging unit 31.
  • the windward heat exchange unit 21 includes a plurality of windward heat transfer tubes 22 and a plurality of windward fins 23 joined to the plurality of windward heat transfer tubes 22 by, for example, brazing.
  • the leeward side heat exchange unit 31 includes a plurality of leeward side heat transfer tubes 32 and a plurality of leeward side fins 33 joined to the plurality of leeward side heat transfer tubes 32 by brazing or the like, for example.
  • the heat exchanging unit 2 may be configured by two rows of the windward side heat exchanging unit 21 and the leeward side heat exchanging unit 31, or may be configured by three or more rows.
  • the windward side heat transfer tube 22 and the leeward side heat transfer tube 32 are flat tubes, and a plurality of flow paths are formed in the major axis direction. Each of the plurality of windward side heat transfer tubes 22 and the plurality of leeward side heat transfer tubes 32 is bent in a hairpin shape between one end and the other end to form folded portions 22a and 32a.
  • the windward side heat transfer tubes 22 and the leeward side heat transfer tubes 32 are arranged in a plurality of stages in a direction intersecting with the passage direction of air passing through the heat exchanging unit 2 (the white arrow in the figure). One end and the other end of each of the plurality of windward side heat transfer tubes 22 and the plurality of leeward side heat transfer tubes 32 are arranged in parallel so as to face the mixing / mixing flow portion 3.
  • the distribution flow unit 3 includes a laminated header 51 and a cylindrical header 61.
  • the laminated header 51 and the cylindrical header 61 are arranged side by side so as to follow the passage direction of air passing through the heat exchanging unit 2 (the white arrow in the figure).
  • a refrigerant pipe (not shown) is connected to the laminated header 51 via a connecting pipe 52.
  • Refrigerant piping (not shown) is connected to the tubular header 61 via a connecting pipe 62.
  • the connection pipe 52 and the connection pipe 62 are, for example, circular pipes.
  • the laminated header 51 is connected to the windward heat exchanging unit 21, and a split flow channel 51 a is formed therein.
  • the split-mixing flow channel 51a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21. It becomes an outflow distribution channel.
  • the split flow channel 51a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.
  • the stacked header 51 corresponds to the “header disposed on the windward side” of the present invention.
  • the cylindrical header 61 is connected to the leeward side heat exchanging portion 31 and a split flow channel 61a is formed therein.
  • the split flow channel 61a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of leeward heat transfer tubes 32 of the leeward heat exchange unit 31. It becomes an outflow distribution channel.
  • the split-mixing flow channel 61a joins refrigerant flowing in from the plurality of leeward heat transfer tubes 32 of the leeward heat exchange unit 31 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.
  • the cylindrical header 61 corresponds to the “header arranged on the leeward side” of the present invention.
  • FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
  • coolant in case the distribution flow path 51a of the laminated header 51 functions as a distribution flow path is shown by the arrow.
  • the third plate-like member 55 formed with is laminated via a plurality of clad members 56_1 to 56_4 in which the partial flow passages 56a are formed, whereby the laminated header 51 is configured.
  • a brazing material is applied to both surfaces or one surface of the cladding materials 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 are collectively referred to as “plate members”. May be described.
  • the partial flow paths 53a, 55a, and 56a are circular through holes.
  • Each of the partial flow paths 54a_1 to 54a_3 is a linear (for example, Z-shaped, S-shaped, etc.) through groove in which the height in the gravity direction of one end and the other end is different from each other.
  • a refrigerant pipe (not shown) is connected to the partial flow path 53a through the connection pipe 52.
  • the windward heat transfer tube 22 is connected to each of the partial flow paths 55a via the connection pipe 57.
  • the connection pipe 57 is, for example, a circular pipe or an elliptical pipe.
  • the partial flow path 56a of the cladding material 56_1 is formed at a position facing the partial flow path 53a.
  • the partial flow path 56a of the cladding material 56_4 is formed at a position facing the partial flow path 55a.
  • One end and the other end of the partial flow paths 54a_1 to 54a_3 are opposed to the partial flow paths 56a of the clad members 56_2 to 56_4 laminated adjacent to the side close to the windward heat exchange section 21.
  • a portion between one end portion and the other end portion of the partial flow paths 54a_1 to 54a_3 is a partial flow path 56a of the clad material 56_1 to 56_3 laminated adjacent to the side far from the windward heat exchange section 21. Opposite.
  • the split flow channel 51a functions as a distribution channel when the refrigerant flows in the direction of the arrow in the figure, and functions as a merging channel when the refrigerant flows in the direction opposite to the arrow in the figure.
  • the refrigerant that has flowed into the partial flow channel 53a via the connection pipe 52 passes through the partial flow channel 56a and is at one end of the partial flow channel 54a_1. Between the first end and the other end, hits the surface of the clad material 56_2, and is branched in two directions.
  • the branched refrigerant flows out from one end and the other end of the partial flow channel 54a_1, and passes between the one end and the other end of the partial flow channel 54a_2 via the partial flow channel 56a.
  • the branched refrigerant flows out from one end and the other end of the partial flow path 54a_2, and passes between the one end and the other end of the partial flow path 54a_3 through the partial flow path 56a. , And hits the surface of the clad material 56_4 to be branched in two directions.
  • the branched refrigerant flows out from one end and the other end of the partial flow path 54a_3, and flows into the connection pipe 57 through the partial flow path 56a and the partial flow path 55a.
  • the refrigerant that has flowed into the partial channel 55a via the connection pipe 57 passes through the partial channel 56a and is at one end of the partial channel 54a_3. And flows into the other end, and flows into the partial flow path 56a communicating between one end and the other end of the partial flow path 54a_3, thereby being merged.
  • the merged refrigerant flows into one end and the other end of the partial flow path 54a_2, and flows into the partial flow path 56a that communicates between one end and the other end of the partial flow path 54a_2. To be merged.
  • the merged refrigerant flows into one end and the other end of the partial flow path 54a_1, and flows into the partial flow path 56a that communicates between one end and the other end of the partial flow path 54a_1. To be merged.
  • the merged refrigerant flows into the connecting pipe 52 through the partial flow path 53a.
  • first plate-like member 53, the second plate-like members 54_1 to 54_3, and the third plate-like member 55 may be directly laminated without using the clad members 56_1 to 56_4.
  • the partial flow path 56a functions as a refrigerant isolation flow path, so that the refrigerant passing through the partial flow paths 53a, 54a_1 to 54a_3, 55a can be isolated from each other. Ensured.
  • Each of the first plate-like member 53, the second plate-like members 54_1 to 54_3, and the third plate-like member 55, and the clad members 56_1 to 56_4 laminated adjacent to each other are integrated into a plate shape.
  • the members may be directly laminated.
  • FIG. 3 is a perspective view of a cylindrical header of the heat exchanger according to the first embodiment.
  • merging flow path is shown by the arrow.
  • the cylindrical header 61 includes a cylindrical portion 63 in which one end and the other end are closed so that the axial direction is parallel to the direction of gravity. is there.
  • the axial direction of the cylindrical portion 63 may not be parallel to the direction of gravity. Since the cylindrical header 61 is disposed so that the axial direction of the cylindrical portion 63 and the longitudinal direction of the laminated header 51 are parallel to each other, the split flow portion 3 is saved.
  • the cylindrical portion 63 may be, for example, a cylindrical portion having an elliptical cross section.
  • a refrigerant pipe (not shown) is connected to the side wall of the cylindrical portion 63 via a connecting pipe 62.
  • the leeward heat transfer tube 32 is connected to the side wall of the cylindrical portion 63 via a plurality of connection tubes 64.
  • the connection pipe 64 is, for example, a circular pipe or an elliptical pipe.
  • the inner side of the cylindrical portion 63 is a split blending flow path 61a.
  • the split flow channel 61a functions as a merge channel when the refrigerant flows in the direction of the arrow in the figure, and functions as a distribution channel when the refrigerant flows in the direction opposite to the arrow in the figure.
  • the split flow channel 61a functions as a merge channel
  • the refrigerant that has flowed into the plurality of connection pipes 64 merges by passing through the inside of the cylindrical portion 63 and flowing into the connection pipe 62.
  • the mixing / mixing flow path 61a functions as a distribution flow path
  • the refrigerant flowing into the connection pipe 62 is distributed by passing through the inside of the cylindrical portion 63 and flowing into the plurality of connection pipes 64.
  • connection pipe 62 and the plurality of connection pipes 64 are arranged so that the direction in which the connection pipe 62 is connected and the direction in which the plurality of connection pipes 64 are connected are not aligned. It is good to be connected. By being configured in this way, it is possible to improve the uniformity of the refrigerant flowing into the plurality of connection pipes 64 when the mixing / mixing flow path 61a functions as a distribution flow path.
  • FIG. 5 is a cross-sectional view taken along line AA in FIG.
  • the windward concentric pipe joint 41 ⁇ / b> A is joined to one end 22 b of the windward heat transfer pipe 22.
  • the upwind eccentric pipe joint 41 ⁇ / b> B is joined to the other end 22 c of the upwind heat transfer tube 22.
  • the leeward concentric pipe joint 42 ⁇ / b> A is joined to the other end 32 c of the leeward heat transfer pipe 32.
  • the leeward eccentric pipe joint 42 ⁇ / b> B is joined to one end 32 b of the leeward heat transfer tube 32.
  • the connecting pipe 57 of the laminated header 51 is connected to the windward concentric pipe joint 41A.
  • a connecting pipe 64 of the tubular header 61 is connected to the leeward side concentric pipe joint 42A.
  • the upwind eccentric pipe joint 41B and the downwind eccentric pipe joint 42B are connected by a crossover pipe 43.
  • the cross-over tube 43 is, for example, a circular tube or an elliptic tube bent in an arc shape.
  • FIG. 6 is a diagram for explaining the connection of the heat exchange unit and the mixing and mixing unit in the modification of the heat exchanger according to the first embodiment. 6 is a cross-sectional view taken along the line AA in FIG. As shown in FIG. 5, the windward side heat transfer tube 22 and the leeward side heat transfer tube 32 include one end 22 b and the other end 22 c of the windward side heat transfer tube 22 and one of the leeward side heat transfer tubes 32.
  • the end portion 32b and the other end portion 32c may be arranged in a zigzag shape when the heat exchanger 1 is viewed from the side, and as shown in FIG. You may arrange
  • 7 and 8 are diagrams for explaining the connection of the heat exchange unit and the mixing and mixing unit in the modification of the heat exchanger according to the first embodiment.
  • 7 and 8 are cross-sectional views taken along the line AA in FIG.
  • the other end 22c of the windward heat transfer tube 22, and one end 22b of the windward heat transfer tube 22 adjacent to the windward heat transfer tube 22 Are connected using the windward side transition pipe 44 and the windward concentric pipe joint 41 ⁇ / b> A, and the other end 32 c of the leeward side heat transfer pipe 32 and the leeward side heat transfer pipe 32 on the next stage of the leeward side heat transfer pipe 32.
  • the windward side transition pipe 44 and the leeward side transition pipe 45 are, for example, a circular pipe or an elliptical pipe bent in an arc shape.
  • the windward heat transfer tube 22 and the leeward heat transfer tube 32 are not bent into a hairpin shape between one end and the other end, and the folded portions 22a and 32a are not formed.
  • One end portion of the heat pipe 22 and one end portion of the windward heat transfer pipe 22 adjacent to the heat pipe 22 are connected using the windward transition pipe 44 and the windward concentric pipe joint 41A, and the windward side
  • One end portion of the side heat transfer tube 32 and one end portion of the leeward side heat transfer tube 32 adjacent to the side heat transfer tube 32 are connected using the leeward side crossover tube 45 and the leeward side concentric pipe joint 42A.
  • the refrigerant may be folded back.
  • FIG. 9 is a diagram illustrating the structures of the windward concentric pipe joint and the leeward concentric pipe joint of the heat exchanger according to Embodiment 1.
  • sectional drawing in the state which looked at the windward concentric pipe joint 41A and the leeward side concentric pipe coupling 42A the sectional view in the state seen from the side, those top views, and those A bottom view is shown.
  • FIG. 9 sectional drawing in the state which looked at the windward concentric pipe joint 41A and the leeward side concentric pipe coupling 42A, the sectional view in the state seen from the side, those top views, and those A bottom view is shown.
  • FIG. 9 shows a case where the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 are circular pipes.
  • a penetration portion 71 is formed in the windward concentric pipe joint 41 ⁇ / b> A and the leeward concentric pipe joint 42 ⁇ / b> A.
  • the cross-sectional shape of one end 72 of the penetrating portion 71 is a shape that follows the cross-sectional shape of the windward side heat transfer tube 22 or the leeward side heat transfer tube 32.
  • the cross-sectional shape of the other end 73 of the penetrating portion 71 is a shape that follows the cross-sectional shape of the connection pipe 57 of the laminated header 51 or the connection pipe 64 of the cylindrical header 61.
  • the central axis of one end 72 and the central axis of the other end 73 are coaxial.
  • the inner diameter D (D1, D2) in the entire circumferential direction of the cross-sectional shape of the other end portion 73 is W2 ⁇ D ⁇ W1.
  • the flow path cross-sectional area (d1 2 ⁇ ⁇ / 4) of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is the flow path cross-sectional area of the windward side heat transfer pipe 22 and the leeward side heat transfer pipe 32. Larger than (w1 ⁇ w2 ⁇ number of flow paths).
  • D1 can be shortened to downsize the windward concentric pipe joint 41A and the leeward side concentric pipe joint 42A, and D2 can be lengthened to join a pipe having a large channel cross-sectional area.
  • it is compatible to reduce the pressure loss generated in the refrigerant passing through the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A.
  • W2 ⁇ D ⁇ W1 since W2 ⁇ D ⁇ W1, the degree of freedom of bending of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is improved.
  • FIG. 10 is a diagram illustrating the structures of the windward concentric pipe joint and the leeward concentric pipe joint of the heat exchanger according to the comparative example.
  • FIG. 10 shows a cross-sectional view of the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A as viewed from the front.
  • the pipes connected to one end 72 and the other end 73 of the upwind concentric pipe joint 41A and the downwind concentric pipe joint 42A are shown by dotted lines.
  • the cross-sectional shape of the inner peripheral surface of the one end 72 is changed to the cross-sectional shape of the inner peripheral surface of the other end 73.
  • a shape converting portion 74 that is continuously changed is formed. As shown in FIG. 10, when the shape converting portion 74 is not formed in the penetrating portion 71, that is, when one end 72 and the other end 73 are in direct communication, one end A vortex is produced at the corner of 72, and pressure loss occurs in the refrigerant passing through the windward concentric pipe joint 41A and the leeward concentric pipe joint 42A. Such a phenomenon is suppressed by forming the shape conversion part 74 in the area
  • connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 are joined in a state where they are inserted up to the boundary between the other end 73 and the shape conversion part 74. That is, the region where the outer peripheral surface of the connection pipe 57 of the multilayer header 51 and the outer peripheral surface of the connection pipe 64 of the cylindrical header 61 is joined to the inner peripheral surface of the other end 73 is adjacent to the shape conversion unit 74. Therefore, the refrigerant flowing in from the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 flows into the windward side heat transfer pipe 22 and the leeward side heat transfer pipe 32 without passing through the steps, resulting in pressure loss. Occurrence is further suppressed. In addition, the axial dimension of the other end 73 can be reduced, and the downwind concentric pipe joint 41A and the downwind concentric pipe joint 42A are reduced in size.
  • FIG. 11 is a diagram illustrating the structure of the upwind eccentric pipe joint and the downwind eccentric pipe joint of the heat exchanger according to the first embodiment.
  • the cross section of the windward eccentric pipe joint 41B and the leeward eccentric pipe joint 42B in the state seen from the front and its peripheral members are illustrated.
  • the windward eccentric pipe joint 41B and the leeward eccentric pipe joint 42B have the same configuration as the windward concentric pipe joint 41A and the leeward side concentric pipe joint 42A, but as shown in FIG. The difference is that the central axis and the central axis of the other end 73 are eccentric from each other.
  • the amount of eccentricity Z is 0 ⁇ Z ⁇ W3 / 2, where W3 is the outer diameter in the major axis direction of the windward side heat transfer tube 22 and the leeward side heat transfer tube 32.
  • the distance between the central axis of the other end 73 of the penetration part 71 of the upwind eccentric pipe joint 41B and the central axis of the leeward side heat transfer pipe 32 is one of the penetration parts 71 of the upwind eccentric pipe joint 41B. It is eccentric so as to be shorter than the distance between the central axis of the end portion 72 and the central axis of the leeward heat transfer tube 32. In addition, the distance between the central axis of the other end 73 of the penetrating portion 71 of the leeward side eccentric pipe joint 42B and the central axis of the upwind heat transfer pipe 22 is such that the distance between the penetrating part 71 of the leeward side eccentric pipe joint 42B. It is eccentric so as to be shorter than the distance between the central axis of one end 72 and the central axis of the windward heat transfer tube 22.
  • FIG. 12 has shown the case where the air conditioning apparatus 91 performs heating operation.
  • FIG. 13 shows a case where the air conditioner 91 performs a cooling operation.
  • the air conditioner 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger (heat source side heat exchanger) 94, an expansion device 95, and an indoor heat exchanger.
  • 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 by a refrigerant pipe to form a refrigerant circulation circuit.
  • the four-way valve 93 may be another flow path switching device.
  • the outdoor heat exchanger 94 is the heat exchanger 1.
  • the heat exchanger 1 is provided such that the laminated header 51 is disposed on the windward side of the air flow generated by driving the outdoor fan 97 and the cylindrical header 61 is disposed on the leeward side.
  • the outdoor fan 97 may be provided on the leeward side of the heat exchanger 1 or may be provided on the leeward side of the heat exchanger 1.
  • a compressor 92, a four-way valve 93, a throttle device 95, an outdoor fan 97, an indoor fan 98, various sensors, and the like are connected to the control device 99.
  • the control device 99 By switching the flow path of the four-way valve 93 by the control device 99, the heating operation and the cooling operation are switched.
  • the condensed refrigerant enters a high-pressure supercooled liquid state, flows out of the indoor heat exchanger 96, and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 95.
  • the low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 94, exchanges heat with the air supplied by the outdoor fan 97, and evaporates.
  • the evaporated refrigerant enters a low-pressure superheated gas state, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93. That is, during the heating operation, the outdoor heat exchanger 94 acts as an evaporator.
  • the refrigerant flows into the split flow channel 51 a of the laminated header 51 and is distributed, passes through the windward concentric pipe joint 41 ⁇ / b> A, and reaches the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into.
  • the refrigerant flowing into the windward side heat transfer tube 22 sequentially passes through the windward side eccentric pipe joint 41B, the crossover pipe 43, and the leeward side eccentric pipe joint 42B, and flows into the leeward side heat transfer pipe 32 of the leeward side heat exchange section 31.
  • the refrigerant that has flowed into the leeward heat transfer pipe 32 passes through the leeward side concentric pipe joint 42 ⁇ / b> A, flows into the mixed flow passage 61 a of the tubular header 61, and is 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, exchanges heat with the air supplied by the outdoor fan 97, and condenses.
  • the condensed refrigerant enters a high-pressure supercooled liquid state or a low dryness state, flows out of the outdoor heat exchanger 94, and enters a low-pressure gas-liquid two-phase state by the expansion device 95.
  • the low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 96 and evaporates by heat exchange with the air supplied by the indoor fan 98, thereby cooling the room.
  • the evaporated refrigerant becomes a low-pressure superheated gas state, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 through the four-way valve 93. That is, during the cooling operation, the outdoor heat exchanger 94 functions as a condenser.
  • the refrigerant flows into the split flow passage 61 a of the cylindrical header 61 and is distributed, passes through the leeward concentric pipe joint 42 ⁇ / b> A, and passes through the leeward heat transfer tube 32 of the leeward heat exchanger 31. Flow into.
  • the refrigerant that has flowed into the leeward heat transfer pipe 32 sequentially passes through the leeward eccentric pipe joint 42B, the crossover pipe 43, and the windward eccentric pipe joint 41B, and then flows into the windward heat transfer pipe 22 of the windward heat exchange section 21. To do.
  • the refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 ⁇ / b> A, flows into the mixed flow passage 51 a of the laminated header 51, and is merged.
  • FIG.14 and FIG.15 is a figure explaining the liquid quantity distribution of the refrigerant
  • the flow direction of the refrigerant is indicated by black arrows. That is, when the heat exchanging unit 2 acts as an evaporator, as shown in FIGS. 14 and 15, the refrigerant is in a parallel flow with the air flow generated by driving the outdoor fan 97, that is, the wind It flows from the upper heat transfer tube 22 to the leeward heat transfer tube 32, and flows from the crossover tube 43 into the leeward eccentric tube joint 42B in a gas-liquid two-phase state.
  • the eccentric amount Z between the central axis of one end 72 and the central axis of the other end 73 is Z> 0.
  • a large amount of the liquid refrigerant that has flowed into the eccentric pipe joint 42 ⁇ / b> B flows into the S point side of the leeward heat transfer pipe 32.
  • the heat exchanger 1 acts as an evaporator, since the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 97 is large, the S point side of the leeward heat transfer tube 32, that is, on the windward side.
  • FIG.16 and FIG.17 is a figure explaining the gas quantity distribution of the refrigerant
  • the flow direction of the refrigerant is indicated by black arrows.
  • the heat exchanging unit 2 acts as a condenser, as shown in FIGS. 16 and 17, the refrigerant is in a relationship opposite to the air flow generated by driving the outdoor fan 97, that is, downwind. It flows from the side heat transfer pipe 32 to the windward side heat transfer pipe 22, and flows from the row connecting pipe 43 into the windward side eccentric pipe joint 41B in a gas-liquid two-phase state.
  • the eccentric amount Z between the central axis of one end 72 and the central axis of the other end 73 is Z> 0.
  • the gas refrigerant that has flowed into the eccentric pipe joint 41 ⁇ / b> B flows into the L point side of the windward heat transfer tube 22 as much liquid refrigerant flows into the S point side.
  • the heat exchanger 1 acts as a condenser
  • the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 97 is large, the L point side of the windward heat transfer tube 22, that is, the windward side
  • condensation of the gas refrigerant is promoted and heat exchange efficiency is improved.
  • the radius of curvature of the crossover tube 43 can be reduced, and the volume of the heat exchanging unit 2 can be increased, so that the heat exchange efficiency is further improved.
  • the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved.
  • the inner diameter in the major axis direction of one end 72 is set to W1. If the inner diameter in the minor axis direction is W2, the inner diameter D (D1, D2) in the entire circumferential direction of the cross-sectional shape of the other end 73 is W2 ⁇ D ⁇ W1, so that the size can be reduced and the pressure It is compatible with reducing the loss. Therefore, the space
  • one end 72 and the other end of the penetrating part 71 are provided in the heat exchanger 1, in the windward concentric pipe joint 41A, the leeward concentric pipe joint 42A, the windward eccentric pipe joint 41B, and the leeward eccentric pipe joint 42B.
  • a shape conversion portion 74 is formed in a region between the portions 73, and the connection pipe 57 of the laminated header 51, the connection pipe 64 of the cylindrical header 61, and the crossover pipe on the inner peripheral surface of the other end 73 Since the area
  • interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.
  • FIG. 18 is a perspective view of the heat exchanger according to the second embodiment. As shown in FIG. 18, the heat exchanging unit 2 includes only the windward heat exchanging unit 21.
  • the windward side heat transfer tubes 22 are arranged in a plurality of stages in a direction intersecting with the passage direction of air passing through the heat exchanging unit 2 (indicated by white arrows in the figure). Each of the plurality of windward side heat transfer tubes 22 is bent in a hairpin shape between one end and the other end to form a folded portion 22a. One end and the other end of each of the plurality of windward side heat transfer tubes 22 are juxtaposed so as to face the laminated header 51.
  • the laminated header 51 is connected to the windward heat exchanging unit 21, and a split flow channel 51 a is formed therein.
  • the split-mixing flow channel 51a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21. It becomes an outflow distribution channel.
  • the split flow channel 51a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.
  • the cylindrical header 61 is connected to the windward heat exchange unit 21, and a split flow channel 61a is formed therein.
  • the split flow channel 61a distributes the refrigerant flowing from the refrigerant pipe (not shown) to the plurality of windward heat transfer tubes 22 of the windward heat exchange unit 21. It becomes an outflow distribution channel.
  • the split-mixing flow channel 61a joins refrigerant flowing in from the plurality of windward side heat transfer tubes 22 of the windward side heat exchange unit 21 to a refrigerant pipe (not shown). It becomes the merging channel that flows out.
  • FIG.19 and FIG.20 is a figure explaining the connection of the heat exchange part and splitting flow part of the heat exchanger which concerns on Embodiment 2.
  • FIG. 20 is a cross-sectional view taken along line BB in FIG.
  • the windward concentric pipe joint 41A is joined to one end 22b and the other end 22c of the windward heat transfer tube 22, respectively.
  • the connection pipe 57 of the laminated header 51 is connected to the upwind concentric pipe joint 41 ⁇ / b> A joined to one end 22 b of the upwind heat transfer pipe 22.
  • the connecting pipe 64 of the tubular header 61 is connected to the upwind concentric pipe joint 41A joined to the other end 22c of the upwind heat transfer pipe 22.
  • FIG. 21 is a diagram for explaining the connection of the heat exchange unit and the mixing and mixing unit in a modification of the heat exchanger according to the second embodiment.
  • FIG. 21 is a cross-sectional view taken along the line BB in FIG.
  • the other end portion 22 c of the windward side heat transfer tube 22 and one end portion 22 b of the windward side heat transfer tube 22 adjacent to the windward side heat transfer tube 22 are connected to the windward side step. You may connect using the pipe
  • FIG. 22 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
  • FIG. 22 has shown the case where the air conditioning apparatus 91 performs heating operation.
  • the refrigerant flow during the heating operation will be described with reference to FIG.
  • the refrigerant flows into the split flow channel 51 a of the laminated header 51 and is distributed, passes through the windward concentric pipe joint 41 ⁇ / b> A, and reaches the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into.
  • the refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 ⁇ / b> A, flows into the split flow passage 61 a of the tubular header 61, and is merged.
  • FIG. 23 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
  • FIG. 23 shows a case where the air conditioner 91 performs a cooling operation.
  • the flow of the refrigerant during the cooling operation will be described with reference to FIG.
  • the refrigerant flows into the split flow passage 61 a of the cylindrical header 61 and is distributed, passes through the windward concentric pipe joint 41 ⁇ / b> A, and passes through the windward heat transfer tube 22 of the windward heat exchange unit 21. Flow into.
  • the refrigerant that has flowed into the windward heat transfer pipe 22 passes through the windward concentric pipe joint 41 ⁇ / b> A, flows into the mixed flow passage 51 a of the laminated header 51, and is merged.
  • interval of the heat exchange part 2 and the split mixing flow part 3 can be narrowed, the volume of the heat exchange part 2 can be expanded, and heat exchange efficiency is improved. And with the improvement in heat exchange efficiency, the operating efficiency of the refrigeration cycle is improved and the energy saving performance is improved. Moreover, it is also possible to save the space of the heat exchanger 1 while maintaining the performance of the refrigeration cycle.
  • the region where the shape conversion part 74 is formed and the outer peripheral surface of the connection pipe 57 of the laminated header 51 and the connection pipe 64 of the cylindrical header 61 is joined to the inner peripheral surface of the other end 73 is the shape conversion. Since it is adjacent to the portion 74, it is possible to achieve both a reduction in size and a reduction in pressure loss. Therefore, the space
  • Embodiment 1 and Embodiment 2 were demonstrated, this invention is not limited to description of each embodiment. For example, it is possible to combine all or some of the embodiments.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2013/079248 2013-10-29 2013-10-29 管継手、熱交換器、及び、空気調和装置 WO2015063858A1 (ja)

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CN201380080615.3A CN105683639B (zh) 2013-10-29 2013-10-29 管接头、换热器和空调装置
JP2015544658A JP6207624B2 (ja) 2013-10-29 2013-10-29 熱交換器、及び、空気調和装置
PCT/JP2013/079248 WO2015063858A1 (ja) 2013-10-29 2013-10-29 管継手、熱交換器、及び、空気調和装置
US15/026,644 US20160245560A1 (en) 2013-10-29 2013-10-29 Tube fitting, heat exchanger, and air-conditioning apparatus
EP13896742.7A EP3064819B1 (en) 2013-10-29 2013-10-29 Pipe joint, heat exchanger, and air conditioner

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JP2019143844A (ja) * 2018-02-19 2019-08-29 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 室外機、及び、空気調和装置
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EP3064819B1 (en) 2019-07-24
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CN105683639A (zh) 2016-06-15
US20160245560A1 (en) 2016-08-25

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