EP2998681B1 - Gestapelter kopf, wärmetauscher und klimatisierungsvorrichtung - Google Patents

Gestapelter kopf, wärmetauscher und klimatisierungsvorrichtung Download PDF

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Publication number
EP2998681B1
EP2998681B1 EP13884840.3A EP13884840A EP2998681B1 EP 2998681 B1 EP2998681 B1 EP 2998681B1 EP 13884840 A EP13884840 A EP 13884840A EP 2998681 B1 EP2998681 B1 EP 2998681B1
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EP
European Patent Office
Prior art keywords
plate
refrigerant
projection
heat exchanger
shaped member
Prior art date
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Application number
EP13884840.3A
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English (en)
French (fr)
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EP2998681A4 (de
EP2998681A1 (de
Inventor
Daisuke Ito
Akira Ishibashi
Takashi Okazaki
Shigeyoshi MATSUI
Shinya Higashiiue
Takuya Matsuda
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2998681A1 publication Critical patent/EP2998681A1/de
Publication of EP2998681A4 publication Critical patent/EP2998681A4/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • 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
    • 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
    • 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
    • F28D1/053—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 straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a stacking-type header, a heat exchanger having the header, and an air-conditioning apparatus having the heat exchanger.
  • US 6892805 A discloses a header having the features in the preamble of claim 1.
  • a stacking-type header including a first plate-shaped unit provided with a plurality of outlet flow passages, and a second plate-shaped unit stacked on the first plate-shaped unit and provided with a distribution flow passage that causes refrigerant entering from an inlet flow passage to be distributed and flow out to the outlet flow passages provided in the first plate-shaped unit.
  • the distribution flow passage includes a branching flow passage with a plurality of grooves extending perpendicularly to the inflow direction of refrigerant. Refrigerant entering the branching flow passage from the inlet flow passage is divided into a plurality of branches while passing through the grooves, before flow outing through the outlet flow passages provided in the first plate-shaped unit (see, for example, Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2000-161818 (paragraphs [0012] to [0020], Figs. 1 and 2 )
  • stacking-type header in order to reduce the thickness of plate-shaped members that make up the second plate-shaped unit to achieve reductions in parts cost, weight, and the like, it is necessary to reduce the cross-sectional area of the grooves. In that case, however, pressure loss of refrigerant passing through the grooves increases. That is, stacking-type headers according to related art have a problem in that it is difficult to achieve reductions in parts cost, weight, and the like while minimizing an increase in the pressure loss of refrigerant.
  • the present invention has been made in view of the above-mentioned problem. Accordingly, it is an object of the present invention to provide a stacking-type header that makes it possible to achieve reductions in parts cost, weight, and the like while minimizing an increase in the pressure loss of refrigerant. It is another object of the present invention to provide a heat exchanger including the stacking-type header. It is still another object of the present invention to provide an air-conditioning apparatus including the heat exchanger.
  • a stacking-type header according to the present invention is set forth in claim 1.
  • the distribution flow passage includes at least one branching flow passage
  • the second plate-shaped unit has at least one first plate-shaped member having at least one first projection that is formed by press working, and the branching flow passage is formed as the inside of the first projection is closed in a region other than a region where refrigerant flows in and a region where refrigerant flows out. Therefore, even when the first plate-shaped member is reduced in thickness, a sufficient cross-sectional area of the branching flow passage can be secured, thereby making it possible to achieve reductions in parts cost, weight, and the like while minimizing an increase in the pressure loss of refrigerant.
  • the stacking-type header according to the present invention may distribute refrigerant entering another apparatus.
  • the configuration, operation, and the like described below are illustrative only, and not intended to limit the present invention to the specific configuration, operation, and the like described below.
  • the same reference signs are used to identify the same or similar elements, or reference signs are omitted for those elements. Further, illustration of detailed structures in the drawings will be simplified or omitted as appropriate. Further, description of overlapping or similar features will be simplified or omitted as appropriate.
  • Fig. 1 illustrates the configuration of the heat exchanger according to Embodiment 1.
  • a heat exchanger 1 has a stacking-type header 2, a header 3, a plurality of first heat transfer tubes 4, and a plurality of fins 5.
  • the stacking-type header 2 has a refrigerant inflow part 2A, and a plurality of refrigerant outflow parts 2B.
  • the header 3 has a plurality of refrigerant inflow parts 3A, and a refrigerant outflow part 3B.
  • a refrigerant pipe is connected to the refrigerant inflow part 2A of the stacking-type header 2 and the refrigerant outflow part 3B of the header 3.
  • the first heat transfer tubes 4 are connected between the refrigerant outflow parts 2B of the stacking-type header 2 and the refrigerant inflow parts 3A of the header 3.
  • the first heat transfer tube 4 is a flat tube provided with a plurality of passages.
  • the first heat transfer tube 4 is made of, for example, aluminum.
  • the end portions at the stacking-type header 2 side of the first heat transfer tubes 4 are connected to the respective refrigerant outflow parts 2B of the stacking-type header 2.
  • the end portions at the stacking-type header 2 side of the first heat transfer tubes 4 may be connected to the respective refrigerant outflow parts 2B of the stacking-type header 2 while being held by a plate-shaped holding member.
  • the fins 5 are joined to the first heat transfer tube 4.
  • the fin 5 is made of, for example, aluminum.
  • the first heat transfer tube 4 and the fin 5 may be joined together by brazing. While Fig. 1 depicts a case in which there are eight first heat transfer tubes 4, the present invention is not limited to this case. Further, the present invention is not limited to a case in which the first heat transfer tube 4 is a flat tube.
  • Refrigerant flowing through the refrigerant pipe flows in the stacking-type header 2 via the refrigerant inflow part 2A, and after being distributed in the stacking-type header 2, the distributed refrigerant flows out to the first heat transfer tubes 4 via the refrigerant outflow parts 2B.
  • the refrigerant exchanges heat with air or the like supplied by a fan, for example.
  • the refrigerant flowing through each of the first heat transfer tubes 4 flows in the header 3 via the refrigerant inflow parts 3A, and after merging in the header 3, the merged refrigerant flows out to the refrigerant pipe via the refrigerant outflow part 3B. Refrigerant flow can be reversed.
  • Fig. 2 is a perspective view, with the stacking-type header in an exploded state, of the heat exchanger according to Embodiment 1.
  • the stacking-type header 2 has a first plate-shaped unit 11, and a second plate-shaped unit 12.
  • the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked together.
  • the first plate-shaped unit 11 is stacked on the refrigerant outflow side toward which refrigerant flows out.
  • the first plate-shaped unit 11 has a first plate-shaped member 21, and a second plate-shaped member 22.
  • the first plate-shaped unit 11 is provided with a plurality of first outlet flow passages 11A.
  • the first outlet flow passages 11A correspond to the refrigerant outflow parts 2B in Fig. 1 .
  • the second plate-shaped unit 12 is stacked on the refrigerant inflow side from which refrigerant flows in.
  • the second plate-shaped unit 12 has a third plate-shaped member 23, and a plurality of fourth plate-shaped members 24_1 to 24_3.
  • the second plate-shaped unit 12 is provided with a distribution flow passage 12A.
  • the distribution flow passage 12A has a first inlet flow passage 12a, and a plurality of branching flow passages 12b.
  • the first inlet flow passage 12a corresponds to the refrigerant inflow part 2A in Fig. 1 .
  • the first plate-shaped member 21 has a first projection 21A and a second projection 21B.
  • the first projection 21A and the second projection 21B are formed by press working such as drawing or bending, and project toward the refrigerant inflow side.
  • the first projection 21A has a bottom. In a state in which the first plate-shaped member 21 is stacked, a part of an inner face 21a of the first projection 21A serves as a part of the first outlet passage 11A, and a part of an outer face 21b of the first projection 21A serves as a part of the branching flow passage 12b.
  • the second projection 21B has a bottom, and in a state in which the first plate-shaped member 21 is stacked, the second projection 21B serves as a joint reinforcement.
  • the first plate-shaped member 21 is made of, for example, aluminum.
  • the second plate-shaped member 22 has a first projection 22A and a second projection 22B.
  • the first projection 22A and the second projection 22B are formed by press working such as drawing or bending, and project toward the refrigerant inflow side.
  • the first projection 22A has a bottom being void.
  • an inner face 22a of the first projection 22A serves as a joint with the first heat transfer tube 4.
  • the second projection 22B has a bottom, and in a state in which the second plate-shaped member 22 is stacked, the second projection 22B serves as a joint reinforcement.
  • the second plate-shaped member 22 is made of, for example, aluminum.
  • the inner face 21a of the first projection 21A of the first plate-shaped member 21, and the inner face 22a of the first projection 22A of the second plate-shaped member 22 each have a shape that conforms to the outer peripheral surface of the first heat transfer tube 4.
  • the outer peripheral surface of the first heat transfer tube 4 is joined to the inner face 22a of the first projection 22A of the second plate-shaped member 22 by, for example, brazing or adhesion.
  • the bottom portion of the first projection 21A of the first plate-shaped member 21, and an end face of the first heat transfer tube 4 have a gap therebetween when in a joined state.
  • the third plate-shaped member 23 has a first projection 23A.
  • the first projection 23A is formed by press working such as drawing or bending, and projects toward the refrigerant inflow side.
  • the first projection 23A has a bottom being void.
  • an inner face 23a of the first projection 23A serves as the first inlet flow passage 12a.
  • the third plate-shaped member 23 is made of, for example, aluminum.
  • the inner face 23a of the first projection 23A of the third plate-shaped member 23 has a shape that conforms to the outer peripheral surface of the refrigerant pipe.
  • the outer peripheral surface of the refrigerant pipe is joined to the inner face 23a of the first projection 23A of the third plate-shaped member 23 by, for example, brazing or adhesion.
  • a metal sleeve or the like may be attached to the outer face of the first projection 23A of the third plate-shaped member 23, and the refrigerant pipe may be connected via the metal sleeve or the like.
  • the fourth plate-shaped members 24_1 to 24_3 have first projections 24A_1 to 24A_3 and second projections 24B_1 to 24B_3, respectively.
  • the first projections 24A_1 to 24A_3 and the second projections 24B_1 to 24B_3 are formed by press working such as drawing or bending, and project toward the refrigerant inflow side.
  • the first projection 24A_1 of the fourth plate-shaped member 24_1 has a bottom. In a state in which the fourth plate-shaped member 24_1 is stacked, an inner face 24a_1 of the first projection 24A_1 serves as a part of the branching flow passage 12b.
  • the first projections 24A_2 and 24A_3 of the fourth plate-shaped members 24_2 and 24_3 have a bottom.
  • inner faces 24a_2 and 24a_3 and outer faces 24b_2 and 24b_3 of the first projections 24A_2 and 24A_3 serve as a part of the branching flow passage 12b, respectively.
  • the second projections 24B_1 to 24B_3 have a bottom.
  • the fourth plate-shaped members 24_1 to 24_3 are stacked, the second projections 24B_1 to 24B_3 serve as a joint reinforcement.
  • the fourth plate-shaped members 24_1 to 24_3 are made of, for example, aluminum.
  • the fourth plate-shaped members 24_1 to 24_3 will be sometimes generically referred to as fourth plate-shaped member 24.
  • first projections 24A_1 to 24A_3 of the fourth plate-shaped member 24 will be sometimes generically referred to as first projection 24A.
  • the inner faces 24a_1 to 24a_3 of the first projection 24A of the fourth plate-shaped member 24 will be sometimes generically referred to as inner face 24a.
  • the outer faces 24b_1 to 24b_3 of the first projection 24A of the fourth plate-shaped member 24 will be sometimes generically referred to as outer face 24b.
  • the second projections 24B_1 to 24B_3 of the fourth plate-shaped member 24 will be sometimes generically referred to as second projection 24B.
  • first plate-shaped member 21, the second plate-shaped member 22, the third plate-shaped member 23, and the fourth plate-shaped member 24 will be sometimes generically referred to as plate-shaped member.
  • the fourth plate-shaped member 24 corresponds to "first plate-shaped member" according to the present invention.
  • Figs. 3 and 4 are each a cross-sectional view, with the stacking-type header in a stacked state, of the heat exchanger according to Embodiment 1.
  • Fig. 3 is a cross-sectional view taken along a line A-A in Fig. 2
  • Fig. 4 is a cross-sectional view taken along a line B-B in Fig. 2 .
  • the portion where refrigerant flows in is shaded.
  • the peripheral edge of the plate-shaped member is bent in the stacking direction, and the distal end of the peripheral edge is joined to the side face of the plate-shaped member that is adjacently stacked on the refrigerant inflow side.
  • the inner face 24a of the first projection 24A provided in the fourth plate-shaped member 24, and the outer face 24b or 21b of the first projection 24A or 21A provided in the fourth plate-shaped member 24 or the first plate-shaped member 21 adjacently stacked on the refrigerant outflow side, are joined while being in fitting engagement with each other, thus forming each of the branching flow passages 12b.
  • the inner face of the second projection 21B or 24B provided in the first plate-shaped member 21 or the fourth plate-shaped member 24, and the outer face of the second projection 22B, 21B, or 24B of the second plate-shaped member 22, the first plate-shaped member 21, or the fourth plate-shaped member 24 adjacently stacked on the refrigerant outflow side, are joined while being in fitting engagement with each other, thus forming a reinforcement.
  • the outer face of the second projection 24B_1 of the fourth plate-shaped member 24_1 is joined to the surface of the third plate-shaped member 23.
  • Figs. 5 and 6 are each a perspective view and a cross-sectional view of main portions, with the stacking-type header in an exploded state, of the heat exchanger according to Embodiment 1.
  • Figs. 5 and 6 are each a perspective view of the portion X in Fig. 2 and a cross-sectional view.
  • Fig. 5(b) is a cross-sectional view taken along a line C-C in Fig. 5(a)
  • Fig. 6(b) is a cross-sectional view taken along a line D-D in Fig. 6(a) .
  • the portion where refrigerant flows in is shaded.
  • branching flow passage 12b formed by the inner face 24a_3 of the first projection 24A_3 of the fourth plate-shaped member 24_3 and the outer face 21b of the first projection 21A of the first plate-shaped member 21, the same applies to the other branching flow passages 12b.
  • the inner face of a Z-shaped region (hereinafter, a Z-shaped region of the plate-shaped member located on the refrigerant inflow side will be generically referred to as inflow-side Z-shaped region 12b_1a) of the first projection 24A_3 of the fourth plate-shaped member 24_3 (hereinafter, the inner face of the inflow-side Z-shaped region 12b_1a will be generically referred to as inner face 12b_1b), and the outer face of a Z-shaped region (hereinafter, a Z-shaped region of the plate-shaped member located on the refrigerant outflow side will be generically referred to as outflow-side Z-shaped region 12b_2a) of the first projection 21A of the first plate-shaped member 21 (hereinafter, the outer face of the outflow-side Z-shaped region 12b_2a will be generically referred to as outer face 12b_2b), are joined while being in fitting engagement with each other, thus forming the branching
  • the inflow-side Z-shaped region 12b_1a has such a shape that connects two end portions 12b_1c and 12b_1d via a linear portion 12b_1e that is perpendicular to the direction of gravity.
  • the inflow-side Z-shaped region 12b_1a has a through-hole 12b_1f provided at the center.
  • Respective peripheral portions 12b_1h and 12b_1i of the two end portions 12b_1c and 12b_1d of the inflow-side Z-shaped region 12b_1a on the surface of the fourth plate-shaped member 24_3 project toward the refrigerant outflow side.
  • the outflow-side Z-shaped region 12b_2a has such a shape that connects two end portions 12b_2c and 12b_2d via a linear portion 12b_2e that is perpendicular to the direction of gravity.
  • the two end portions 12b_2c and 12b_2d of the outflow-side Z-shaped region 12b_2a are provided with through-holes 12b_2f and 12b_2g, respectively.
  • Respective peripheral portions 12b_2h and 12b_2i of the two end portions 12b_2c and 12b_2d of the outflow-side Z-shaped region 12b_2a on the first projection 21A of the first plate-shaped member 21 project toward the refrigerant outflow side.
  • peripheral portion 12b_1h or 12b_1i projecting toward the refrigerant outflow side, and the peripheral portion 12b_2h or 12b_2i recessed toward the refrigerant outflow side are joined while being in fitting engagement with each other. Consequently, the refrigerant entering through the through-hole 12b_1f and divided into two branches passes between the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a without leaking, and flows out from the through-hole 12b_2f or 12b_2g.
  • a protrusion 12b_2j is provided below the center of the outflow-side Z-shaped region 12b_2a in Figs. 5 and 6 .
  • the protrusion 12b_2j is joined while being in fitting engagement with a part of the inner face of the outflow-side Z-shaped region 12b_2a of another branching flow passage 12b adjacently located on the refrigerant outflow side, which communicates with a part located below the center of the inflow-side Z-shaped region 12b_1a in Figs. 5 and 6 .
  • the protrusion 12b_2j prevents refrigerant entering through the through-hole 12b_1f from leaking from the branching flow passage 12b by passing through the inner face of the outflow-side Z-shaped region 12b_2a of another branching flow passage 12b adjacently located on the refrigerant outflow side.
  • the inner face of the outflow-side Z-shaped region 12b_2a of another branching flow passage 12b adjacently located on the refrigerant outflow side may be closed by another method.
  • peripheral portions 12b_1h and 12b_1i that project toward the refrigerant outflow side may be recessed toward the refrigerant inflow side, and the peripheral portions 12b_2h and 12b_2i recessed toward the refrigerant outflow side may project toward the refrigerant inflow side.
  • the refrigerant entering through the through-hole 12b_1f and divided into two branches passes between the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a without leaking, and flows out from the through-holes 12b_2f or 12b_2g.
  • the branching flow passage 12b divides entering refrigerant into two branches that flow out the branching flow passage 12b. Accordingly, if there are eight first heat transfer tubes 4 to be connected, a minimum of three fourth plate-shaped members 24 are required. If there are sixteen first heat transfer tubes 4 to be connected, a minimum of four fourth plate-shaped members 24 are required.
  • the number of first heat transfer tubes 4 to be connected is not limited to a power of 2. In such a case, a combination of the branching flow passages 12b and non-branching flow passages may be used. The number of first heat transfer tubes 4 to be connected may be two.
  • the end portion 12b_1c of the inflow-side Z-shaped region 12b_1a and the end portion 12b_2c of the outflow-side Z-shaped region 12b_2a are located at different heights from the end portion 12b_1d of the inflow-side Z-shaped region 12b_1a and the end portion 12b_2d of the outflow-side Z-shaped region 12b_2a, respectively.
  • imbalance of the distances along the branching flow passage 12b from the through-hole 12b_1f to the through-hole 12b_2f and to the through-hole 12b_2g can be reduced without increasing geometric complflow outy.
  • the straight line connecting the through-hole 12b_2f and the through-hole 12b_2g extends in parallel to the longitudinal direction of the plate-shaped member. This makes it possible to reduce the size of the plate-shaped member in the transverse direction, thus reducing parts cost, weight, and the like. Further, the straight line connecting the through-hole 12b_2f and the through-hole 12b_2g extends in parallel to the arrangement direction of the first heat transfer tubes 4, which allows space saving for the heat exchanger 1.
  • the stacking-type header 2 is not limited to one in which the first outlet flow passages 11A are arranged along the direction of gravity.
  • the stacking-type header 2 may be also used for applications in which the heat exchanger 1 is disposed in a slanted orientation, as in the case of a heat exchanger in wall-mounted room air-conditioner's indoor units, outdoor units for air-conditioning apparatuses, and chiller outdoor units.
  • the inflow-side Z-shaped region 12b_1a and the outflow-side Z-shaped region 12b_2a may have such a shape that the linear portion 12b_1e and the linear portion 12b_2e are not perpendicular to the longitudinal direction of the plate-shaped member, respectively.
  • the branching flow passage 12b may have another shape. That is, the branching flow passage 12b may not be Z-shaped.
  • the inflow-side Z-shaped region 12b_1a and the outflow-side Z-shaped region 12b_2a may not have the linear portion 12b_1e and the linear portion 12b_2e, respectively. If the linear portion 12b_1e and the linear portion 12b_2e are present, this reduces the influence of gravity when refrigerant flows in from the through-hole 12b_1f and splits into two branches. That is, irrespective of the flow rate and quality of the refrigerant entering in a two-phase gas-liquid state, the influence of gravity is reduced.
  • the flow rate and quality of refrigerant entering each of the first heat transfer tubes 4 can be made uniform.
  • the inflow-side Z-shaped region 12b_1a and the outflow-side Z-shaped region 12b_2a may have a shape that branches out. If the inflow-side Z-shaped region 12b_1a and the outflow-side Z-shaped region 12b_2a do not branch out, the uniformity of refrigerant distribution can be improved.
  • the plate-shaped members may be stacked together by brazing. Stacking the plate-shaped members together by brazing allows the plate-shaped members to be stacked without any gap therebetween, thus minimizing leakage of refrigerant and also ensuring pressure tightness. If the plate-shaped members are brazed together while applying pressure, brazing failures are further reduced. If a process that promotes fillet formation, such as forming ribs, is applied to areas susceptible to refrigerant leakages, brazing failures are further reduced.
  • first heat transfer tube 4 and the fin 5 are made of the same material (for example, aluminum), these members can be brazed together at once, thus improving productivity.
  • Brazing of the first heat transfer tube 4 and the fin 5 may be performed after brazing of the stacking-type header 2. Further, first, only the first plate-shaped unit 11 may be joined to the first heat transfer tube 4 by brazing, and then the second plate-shaped unit 12 may be joined to the first heat transfer tube 4 by brazing.
  • Fig. 7 is a development diagram of the stacking-type header of the heat exchanger according to Embodiment 1.
  • the refrigerant that has passed through the first projection 23A of the third plate-shaped member 23 passes through the through-hole provided in the first projection 24A_1 of the fourth plate-shaped member 24_1, that is, the through-hole 12b_1f of the inflow-side Z-shaped region 12b_1a, and flows in the inside of the first projection 24A_1 of the fourth plate-shaped member 24_1.
  • the refrigerant hits the projection of a member stacked adjacent thereto, and splits into two branches.
  • the branched refrigerant passes between the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a, and then passes through the through-holes provided in the first projection 24A_2 of the fourth plate-shaped member 24_2, that is, the through-holes 12b_2f and 12b_2b of the outflow-side Z-shaped region 12b_2a.
  • the refrigerant hits the projection of a member stacked adjacent thereto, and splits into two branches.
  • the branched refrigerant passes between the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a, and then passes through the through-holes provided in the first projection 24A_3 of the fourth plate-shaped member 24_3, that is, the through-holes 12b_2f and 12b_2b of the outflow-side Z-shaped region 12b_2a.
  • the refrigerant hits the projection of a member stacked adjacent thereto, and splits into two branches.
  • the branched refrigerant passes between the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a, and then passes through the through-holes provided in the first projection 21A of the first plate-shaped member 21, that is, the through-holes 12b_2f and 12b_2b of the outflow-side Z-shaped region 12b_2a.
  • the refrigerant that has passed through the through-holes provided in the first projection 21A of the first plate-shaped member 21 passes through the first projection 22A of the second plate-shaped member 22, and flows in the first heat transfer tube 4.
  • the present invention is not limited to such a case.
  • the heat exchanger according to Embodiment 1 may be used in other refrigeration cycle devices having a refrigerant circuit.
  • the air-conditioning apparatus switches between cooling operation and heating operation
  • the present invention is not limited to such a case.
  • the air-conditioning apparatus may perform only cooling operation or heating operation.
  • Fig. 8 illustrates the configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied.
  • flow of refrigerant in cooling operation is indicated by solid arrows
  • flow of refrigerant in heating operation is indicated by dotted arrows.
  • an air-conditioning apparatus 51 includes a compressor 52, a four-way valve 53, a heat source-side heat exchanger 54, an expansion device 55, a load-side heat exchanger 56, a heat source-side fan 57, a load-side fan 58, and a controller 59.
  • the compressor 52, the four-way valve 53, the heat source-side heat exchanger 54, the expansion device 55, and the load-side heat exchanger 56 are connected by the refrigerant pipe to form a refrigerant circuit.
  • the controller 59 is connected with, for example, the compressor 52, the four-way valve 53, the expansion device 55, the heat source-side fan 57, the load-side fan 58, and various sensors.
  • the controller 59 switches the flow passages of the four-way valve 53 to switch between cooling operation and heating operation.
  • the heat source-side heat exchanger 54 acts as a condenser in cooling operation, and acts as an evaporator in heating operation.
  • the load-side heat exchanger 56 acts as an evaporator in cooling operation, and acts as a condenser in heating operation.
  • Refrigerant at high pressure and high temperature in a gaseous state discharged from the compressor 52 flows in the heat source-side heat exchanger 54 via the four-way valve 53, where the refrigerant exchanges heat with the outside air supplied by the heat source-side fan 57, causing the refrigerant to condense into refrigerant at high pressure in a liquid state, which then flows out the heat source-side heat exchanger 54.
  • the refrigerant at high pressure in a liquid state that has flow outed the heat source-side heat exchanger 54 flows in the expansion device 55, where the refrigerant turns into refrigerant at low pressure in a two-phase gas-liquid state.
  • the refrigerant at low pressure in a two-phase gas-liquid state flow outing the expansion device 55 flows in the load-side heat exchanger 56, where the refrigerant exchanges heat with the indoor air supplied by the load-side fan 58, causing the refrigerant to evaporate into refrigerant at low pressure in a gaseous state, which then flows out the load-side heat exchanger 56.
  • the refrigerant at low pressure in a gaseous state flow outing the load-side heat exchanger 56 is sucked by the compressor 52 via the four-way valve 53.
  • Refrigerant at high pressure and high temperature in a gaseous state discharged from the compressor 52 flows in the load-side heat exchanger 56 via the four-way valve 53, where the refrigerant exchanges heat with the indoor air supplied by the load-side fan 58 which causes the refrigerant to condense into refrigerant at high pressure in a liquid state, which then flows out the load-side heat exchanger 56.
  • the refrigerant at high pressure in a liquid state that has flow outed the load-side heat exchanger 56 flows in the expansion device 55, where the refrigerant turns into refrigerant at low pressure in a two-phase gas-liquid.
  • the refrigerant at low pressure in a two-phase gas-liquid flow outing the expansion device 55 flows in the heat source-side heat exchanger 54 where the refrigerant exchanges heat with the outside air supplied by the heat source-side fan 57, causing the refrigerant to condense into refrigerant at low pressure in a gaseous state, which then flows out the heat source-side heat exchanger 54.
  • the refrigerant at low pressure in a gaseous state flow outing the heat source-side heat exchanger 54 is sucked by the compressor 52 via the four-way valve 53.
  • the heat exchanger 1 is used in at least one of the heat source-side heat exchanger 54 and the load-side heat exchanger 56.
  • the heat exchanger 1 is connected in such a way that when the heat exchanger 1 acts as an evaporator, refrigerant flows in from the stacking-type header 2, and refrigerant flows out from the header 3. That is, when the heat exchanger 1 acts as an evaporator, refrigerant in a two-phase gas-liquid state flows in the stacking-type header 2 from the refrigerant pipe, and refrigerant in a gaseous state flows in the header 3 from the first heat transfer tube 4.
  • refrigerant in a gaseous state flows in the header 3 from the refrigerant pipe, and refrigerant in a liquid state flows in the stacking-type header 2 from the first heat transfer tube 4.
  • the branching flow passage 12b of the stacking-type header 2 is formed by the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a, that is, the inner face of the first projection of the plate-shaped member, and the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a, that is, the outer face of the first projection of another plate-shaped member.
  • the reduced thickness of the plate-shaped member enables a reduction in thermal capacity, which leads to shorter time required for heating and cooling performed during joining processes such as brazing, thus improving production efficiency.
  • the projection provided in the plate-shaped member can be formed by press working such as drawing or bending, machining cost is reduced.
  • the space between the plate-shaped members may be filled with a heat insulating material.
  • the peripheral edge of the plate-shaped member is bent in the stacking direction, and the distal end of the peripheral edge is joined to the side face of an adjacently stacked plate-shaped member. Accordingly, in comparison to when plate-shaped members that are not bent are stacked flat and joined together over a large area, the brazing filler metal is easily allowed to gather tightly at the distal end of the peripheral edge owing to surface tension. This reduces the frequency of joint failures due to uneven application of the brazing filler metal, and the amount of the brazing filler metal used. Further, for example, a process of finishing the joint surface into a flat surface, and a jig for applying uniform pressure over a large area during the brazing process become unnecessary, thus reducing manufacturing cost.
  • the brazing filler metal becomes concentrated in areas where the spacing is narrow, resulting in an uneven joint, a shrinkage cavity, or the like.
  • the members to be joined have a tight spacing and a small joint surface, which allows the brazing filler metal to gather tightly when joining these members together, thus reducing an uneven joint, a shrinkage cavity, or the like.
  • the joint area increases for improved joint strength.
  • the plate-shaped member is provided with the second projection, and the inner face of the second projection is joined to the outer face of the second projection provided in the adjacently stacked plate-shaped member. Consequently, these projections are joined to each other in a manner similar to line contact, which allows the brazing filler metal to easily gather tightly owing to surface tension. Therefore, the frequency of joint failures due to uneven application of the brazing filler metal is reduced, thus improving the reliability of reinforcement. Furthermore, the amount of the brazing filler metal used is reduced. Further, for example, a process of finishing the joint surface into a flat surface, and a jig for applying uniform pressure over a large area during brazing become unnecessary, thus reducing manufacturing cost.
  • the inner face 12b_1b of the inflow-side Z-shaped region 12b_1a that is, the inner face of the first projection of the plate-shaped member
  • the outer face 12b_2b of the outflow-side Z-shaped region 12b_2a that is, the outer face of the first projection of another plate-shaped member
  • Fig. 9 is a perspective view, with the stacking-type header in an exploded state, of Modification-1 of the heat exchanger according to Embodiment 1.
  • Fig. 10 is a cross-sectional view, with the stacking-type header in a stacked state, of Modification-1 of the heat exchanger according to Embodiment 1.
  • Fig. 11 is a development diagram of the stacking-type header in Modification-1 of the heat exchanger according to Embodiment 1.
  • Fig. 10 is a cross-sectional view taken along a line E-E in Fig. 9 . In Fig. 10 , the portion where refrigerant flows in is shaded.
  • Fig. 11 illustrates a state in which the first plate-shaped member 21, the second plate-shaped member 22, the third plate-shaped member 23, and the fourth plate-shaped member 24, and fifth plate-shaped members 25_1 to 25_5 are joined to each other.
  • the fifth plate-shaped members 25_1 to 25_5 may be joined to the first plate-shaped member 21, the second plate-shaped member 22, the third plate-shaped member 23, and the fourth plate-shaped member 24.
  • the plate-shaped member has the first projection 21A, 22A, 23A, or 24A, which is formed by press working such as drawing or bending and projects toward the refrigerant inflow side.
  • the first projection 21A, 22A, 23A, or 24A has a bottom being void, and in a state in which the plate-shaped member is stacked, its inner face 21a, 22a, 23a or 24a serves as a part of the branching flow passage 12b.
  • the fifth plate-shaped members 25_1 to 25_5 will be sometimes generically referred to as fifth plate-shaped member 25.
  • the fifth plate-shaped member 25 corresponds to "second plate-shaped member" according to the present invention.
  • the fifth plate-shaped members 25_1 to 25_5 are provided with through-holes 25A_1 to 25A_5, respectively.
  • the outer periphery at the distal end of each of the first projections 21A, 22A, 23A, and 24A is joined to the corresponding one of the through-holes 25A_1 to 25A_5 while being in fitting engagement with the corresponding through-hole.
  • the inside of the first projection 21A, 22A, 23A, or 24A is closed in a region other than the region where refrigerant flows in and the region where refrigerant flows out, by the surface of the fifth plate-shaped member 25 stacked on the refrigerant outflow side, and the surface of another plate-shaped member stacked on the refrigerant inflow side, thus forming the branching flow passage 12b.
  • Fig. 12 is a perspective view and a cross-sectional view of main portions, with the stacking-type header in an exploded state, of Modification-2 of the heat exchanger according to Embodiment 1.
  • Fig. 12(a) is a perspective view of main portions with the stacking-type header in an exploded state
  • Fig. 12(b) is a cross-sectional view of the first plate-shaped member 21 taken along a line F-F in Fig. 12(a) .
  • the portion where refrigerant flows in is shaded.
  • a region of the inner face 21a of the first projection 21A of the first plate-shaped member 21 other than the outflow-side Z-shaped region 12b_2a may have such a shape that gradually widens toward the refrigerant outflow side.
  • Fig. 13 is a perspective view, with the stacking-type header in an exploded state, of Modification-3 of the heat exchanger according to Embodiment 1.
  • the third plate-shaped member 23 may be provided with a plurality of first inlet flow passages 12a to reduce the number of fourth plate-shaped members 24. This configuration allows reductions in parts cost, weight, and the like.
  • Fig. 14 is a perspective view, with the stacking-type header in an exploded state, of Modification-4 of the heat exchanger according to Embodiment 1.
  • the first inlet flow passage 12a may be provided in a plate-shaped member other than the third plate-shaped member 23.
  • a through-hole may be provided in another plate-shaped member, and a projection for introducing refrigerant from the through-hole to the inner face 24a_1 of the first projection 24A_1 of the fourth plate-shaped member 24_1 may be provided in another plate-shaped member and a neighboring plate-shaped member.
  • the present invention encompasses configurations in which the first inlet flow passage 12a is provided in the first plate-shaped unit 11, and the "distribution flow passage” according to the present invention encompasses distribution flow passages other than the distribution flow passage 12A that has the first inlet flow passage 12a provided in the second plate-shaped unit 12.
  • Fig. 15 illustrates the configuration of a heat exchanger according to Embodiment 2.
  • a heat exchanger 1 has a stacking-type header 2, a plurality of first heat transfer tubes 4, and a plurality of fins 5.
  • the stacking-type header 2 has a refrigerant inflow part 2A, a plurality of refrigerant outflow parts 2B, a plurality of refrigerant inflow parts 2C, and a refrigerant outflow part 2D.
  • a refrigerant pipe is connected to the refrigerant inflow part 2A of the stacking-type header 2 and the refrigerant outflow part 2D of the stacking-type header 2.
  • the first heat transfer tube 4 is a flat tube with a hair pin bend. The first heat transfer tubes 4 are connected between the refrigerant outflow parts 2B of the stacking-type header 2 and the refrigerant inflow parts 2C of the stacking-type header 2.
  • Refrigerant flowing through the refrigerant pipe flows in the stacking-type header 2 via the refrigerant inflow part 2A, and after being distributed in the stacking-type header 2, the distributed refrigerant flows out to the first heat transfer tubes 4 via the refrigerant outflow parts 2B.
  • the refrigerant exchanges heat with air or the like supplied by a fan, for example.
  • the refrigerant that has passed through each of the first heat transfer tubes 4 flows in the stacking-type header 2 via the refrigerant inflow parts 2C, and after merging in the stacking-type header 2, the merged refrigerant flows out to the refrigerant pipe via the refrigerant outflow part 2D. Refrigerant flow can be reversed.
  • Fig. 16 is a perspective view, with the stacking-type header in an exploded state, of the heat exchanger according to Embodiment 2.
  • Fig. 17 is a development diagram of the stacking-type header of the heat exchanger according to Embodiment 2.
  • the stacking-type header 2 has a first plate-shaped unit 11, and a second plate-shaped unit 12.
  • the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked together.
  • the first plate-shaped unit 11 is provided with a plurality of first outlet flow passages 11A, and a plurality of second inlet flow passages 11B.
  • the first plate-shaped unit 11 has a first plate-shaped member 21, a sixth plate-shaped member 26, and a second plate-shaped member 22.
  • the second inlet flow passages 11B correspond to the refrigerant inflow parts 2C in Fig. 15 .
  • the first plate-shaped member 21, the second plate-shaped member 22, a third plate-shaped member 23, a fourth plate-shaped member 24, and the sixth plate-shaped member 26 will be sometimes generically referred to as plate-shaped member.
  • the second plate-shaped unit 12 is provided with a distribution flow passage 12A, and a joining flow passage 12B.
  • the joining flow passage 12B has a mixing passage 12c, and a second outlet flow passage 12d.
  • the second outlet flow passage 12d corresponds to the refrigerant outflow part 2D in Fig. 15 .
  • the second plate-shaped member 22 has a third projection 22C, which is formed by, for example, press working such as drawing or bending and projects toward the refrigerant outflow side.
  • the third projection 22C has a bottom being void only in a region connected to the refrigerant outflow-side end portion of the first heat transfer tube 4.
  • an outer face 22d of the third projection 22C serves as a part of the second inlet flow passage 11B.
  • the sixth plate-shaped member 26 has a first projection 26A, a second projection 26B, and a third projection 26C, which are formed by, for example, press working such as drawing or bending and project toward the refrigerant outflow side.
  • the third projection 26C has a bottom being void in a region that is not opposed to the refrigerant outflow-side end portion of the first heat transfer tube 4. In a state in which the sixth plate-shaped member 26 is stacked, an inner face 26c of the third projection 26C serves as a part of the second inlet flow passage 11B.
  • the first plate-shaped member 21 has, for example, a through portion 21C, which is formed by press working and does not project to neither the refrigerant outflow side nor the refrigerant inflow side. In a state in which the first plate-shaped member 21 is stacked, the through portion 21C serves as a part of the second inlet flow passage 11B.
  • the fourth plate-shaped member 24 has, for example, third projections 24C_1 to 24C_3, which are formed by press working such as drawing or bending and project toward the refrigerant inflow side.
  • the third projections 24C_1 to 24C_3 of the fourth plate-shaped member 24 will be sometimes generically referred to as third projection 24C.
  • the third projection 24C has a bottom being void, and in a state in which the fourth plate-shaped member 24 is stacked, inner faces 24c_1 to 24c_3 of the third projection 24C serve as a part of the mixing passage 12c.
  • the inner faces 24c_1 to 24c_3 of the third projection 24C of the fourth plate-shaped member 24 will be sometimes generically referred to as inner face 24c.
  • the third plate-shaped member 23 has, for example, a third projection 23C and a fourth projection 23D.
  • the third projection 23C is formed by press working such as drawing or bending, and projects toward the refrigerant inflow side.
  • the fourth projection 23D which is provided in the third projection 23C, projects toward the refrigerant outflow side.
  • the third projection 23C has a bottom.
  • an outer face 23d of the third projection 23C serves as a part of the mixing passage 12c.
  • the fourth projection 23D has a bottom being void.
  • an inner face 23e of the fourth projection 23D serves as the second outlet flow passage 12d.
  • the second outlet flow passage 12d may be provided in a plate-shaped member other than the third plate-shaped member 23.
  • a through-hole may be provided in another plate-shaped member, and a projection for introducing refrigerant to the through-hole may be provided in another plate-shaped member and a neighboring plate-shaped member.
  • the present invention encompasses configurations in which the second outlet flow passage 12d is provided in the first plate-shaped unit 11, and the "joining flow passage" according to the present invention encompasses joining flow passages other than the joining flow passage 12B that has the second outlet flow passage 12d provided in the second plate-shaped unit 12.
  • refrigerant passes through the third projection 22C of the second plate-shaped member 22, and flows in the inside of the third projection 26C of the sixth plate-shaped member 26.
  • the refrigerant After entering the inside of the third projection 26C of the sixth plate-shaped member 26, the refrigerant passes through the through portion 21C of the first plate-shaped member 21, and flows in the inside of the third projection 24C of the fourth plate-shaped member 24 where the refrigerant is mixed with another flow.
  • the mixed refrigerant passes through the fourth projection 23D of the third plate-shaped member 23, and flows out to the refrigerant pipe.
  • Fig. 18 illustrates the configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
  • the heat exchanger 1 is used for at least one of a heat source-side heat exchanger 54 and a load-side heat exchanger 56.
  • the heat exchanger 1 is connected in such a way that when the heat exchanger 1 acts as an evaporator, refrigerant flows in the first heat transfer tube 4 from the distribution flow passage 12A of the stacking-type header 2, and refrigerant flows in the joining flow passage 12B of the stacking-type header 2 from the first heat transfer tube 4.
  • refrigerant in a two-phase gas-liquid state flows in the distribution flow passage 12A of the stacking-type header 2 from the refrigerant pipe, and refrigerant in a gaseous state flows in the joining flow passage 12B of the stacking-type header 2 from the first heat transfer tube 4.
  • refrigerant in a gaseous state flows in the joining flow passage 12B of the stacking-type header 2 from the refrigerant pipe, and refrigerant in a liquid state flows in the distribution flow passage 12A of the stacking-type header 2 from the first heat transfer tube 4.
  • the first plate-shaped unit 11 is provided with the second inlet flow passages 11B, and the second plate-shaped unit 12 is provided with the joining flow passage 12B. Consequently, a header 3 becomes unnecessary, thus reducing, for example, parts cost of the heat exchanger 1. Since the header 3 is not required, it is possible to extend the first heat transfer tube 4 to increase the number of fins 5, that is, increase the mounting volume of the heat exchange unit of the heat exchanger 1.
  • Fig. 19 illustrates the configuration of the heat exchanger according to Embodiment 3.
  • a heat exchanger 1 has a stacking-type header 2, a plurality of first heat transfer tubes 4, a plurality of second heat transfer tubes 6, and a plurality of fins 5.
  • the stacking-type header 2 has a plurality of refrigerant turn-around parts 2E.
  • the second heat transfer tube 6 is a flat tube with a hair pin bend.
  • the first heat transfer tubes 4 are connected between a plurality of refrigerant outflow parts 2B and the refrigerant turn-around parts 2E of the stacking-type header 2, and the second heat transfer tubes 6 are connected between the refrigerant turn-around parts 2E and a plurality of refrigerant inflow parts 2C of the stacking-type header 2.
  • Refrigerant flowing through the refrigerant pipe flows in the stacking-type header 2 via a refrigerant inflow part 2A, and after being distributed in the stacking-type header 2, the distributed refrigerant flows out to the first heat transfer tubes 4 via the refrigerant outflow parts 2B.
  • the refrigerant exchanges heat with air or the like supplied by a fan, for example.
  • the refrigerant that has passed through the first heat transfer tubes 4 flows in the refrigerant turn-around parts 2E of the stacking-type header 2 where the refrigerant is turned around before flow outing to the second heat transfer tubes 6.
  • the refrigerant exchanges heat with air or the like supplied by a fan, for example.
  • each of the second heat transfer tubes 6 flows in the stacking-type header 2 via the refrigerant inflow parts 2C, and after merging in the stacking-type header 2, the merged refrigerant flows out to the refrigerant pipe via a refrigerant outflow part 2D. Refrigerant flow can be reversed.
  • Fig. 20 is a perspective view, with the stacking-type header in an exploded state, of the heat exchanger according to Embodiment 3.
  • Fig. 21 is a development diagram of the stacking-type header of the heat exchanger according to Embodiment 3.
  • the stacking-type header 2 has a first plate-shaped unit 11, and a second plate-shaped unit 12.
  • the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked together.
  • the first plate-shaped unit 11 is provided with a plurality of first outlet flow passages 11A, a plurality of second inlet flow passages 11B, and a plurality of turn-back flow passages 11C.
  • the turn-back flow passages 11C correspond to the refrigerant turn-around parts 2E in Fig. 19 .
  • a second plate-shaped member 22 has a third projection 22C and a fourth projection 22D.
  • the third projection 22C is formed by, for example, press working such as drawing or bending, and projects toward the side opposite to the side from which the refrigerant from the first heat transfer tube 4 flows in.
  • the fourth projection 22D is formed by, for example, press working such as drawing or bending, and projects toward the side to which the refrigerant from the second heat transfer tube 6 flows out.
  • the fourth projection 22D has a bottom being void only in regions that are connected to the refrigerant outflow-side end portion of the first heat transfer tube 4 and the refrigerant inflow-side end portion of the second heat transfer tube 6. In a state in which the second plate-shaped member 22 is stacked, an outer face 22f of the fourth projection 22D serves as a part of the turn-back flow passage 11C.
  • a sixth plate-shaped member 26 has a third projection 26C and a fourth projection 26D.
  • the third projection 26C is formed by, for example, press working such as drawing or bending, and projects toward the side opposite to the side from which refrigerant from the first heat transfer tube 4 flows in.
  • the fourth projection 26D is formed by, for example, press working such as drawing or bending, and projects toward the side to which refrigerant from the second heat transfer tube 6 flows out.
  • the fourth projection 26D has a bottom. In a state in which the sixth plate-shaped member 26 is stacked, an inner face 26e of the fourth projection 26D serves as a part of the turn-back flow passage 11C.
  • refrigerant passes through the fourth projection 22D of the second plate-shaped member 22, and flows in the inside of the fourth projection 26D of the sixth plate-shaped member 26.
  • the refrigerant passes through the fourth projection 22D of the second plate-shaped member 22 again, and flows in the second heat transfer tube 6.
  • the refrigerant that has passed through the second heat transfer tube 6 passes through the third projection 22C of the second plate-shaped member 22 and the third projection 26C of the sixth plate-shaped member 26, and flows in the inside of a third projection 24C of a fourth plate-shaped member 24 where the refrigerant is mixed with another flow.
  • the mixed refrigerant passes through the fourth projection 23D of the third plate-shaped member 23, and flows out to the refrigerant pipe.
  • Fig. 22 illustrates the configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
  • the heat exchanger 1 is used for at least one of a heat source-side heat exchanger 54 and a load-side heat exchanger 56.
  • the heat exchanger 1 is connected in such a way that when the heat exchanger 1 acts as an evaporator, refrigerant flows in the first heat transfer tube 4 from a distribution flow passage 12A of the stacking-type header 2, and refrigerant flows in a joining flow passage 12B of the stacking-type header 2 from the second heat transfer tube 6.
  • refrigerant in a two-phase gas-liquid state flows in the distribution flow passage 12A of the stacking-type header 2 from the refrigerant pipe, and refrigerant in a gaseous state flows in the joining flow passage 12B of the stacking-type header 2 from the second heat transfer tube 6.
  • refrigerant in a gaseous state flows in the joining flow passage 12B of the stacking-type header 2 from the refrigerant pipe, and refrigerant in a liquid state flows in the distribution flow passage 12A of the stacking-type header 2 from the first heat transfer tube 4.
  • the heat exchanger 1 is disposed so that when the heat exchanger 1 acts as a condenser, the first heat transfer tube 4 is located on the upstream side of airflow produced by the heat source-side fan 57 or the load-side fan 58 (upstream side of airflow), in comparison to the second heat transfer tube 6. That is, the flow of refrigerant from the second heat transfer tube 6 to the first heat transfer tube 4 and the airflow are opposed to each other.
  • the temperature of refrigerant in the first heat transfer tube 4 is lower than that of refrigerant in the second heat transfer tube 6.
  • the temperature of the airflow produced by the heat source-side fan 57 or the load-side fan 58 is lower on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1.
  • refrigerant can be subcooled (so-called subcooling) by the low-temperature airflow flowing on the upstream side of the heat exchanger 1, thereby improving condenser performance.
  • the heat source-side fan 57 and the load-side fan 58 may be provided on either of the upstream side of airflow and the downstream side of airflow.
  • the first plate-shaped unit 11 is provided with the turn-back flow passages 11C, and the second heat transfer tubes 6 are connected in addition to the first heat transfer tubes 4.
  • the amount of heat exchange can be increased by increasing the area of the heat exchanger 1 as seen in front view. However, in that case, the size of the housing that contains the heat exchanger 1 increases. Further, the amount of heat exchange can be increased by increasing the number of fins 5 by reducing the spacing of the fins 5. However, in that case, it is difficult to make the spacing of the fins 5 less than about 1 mm from the viewpoints of drainage performance, frosting performance, and dust-proofness. Consequently, a sufficient increase in the amount of heat exchange may not be attained in some cases.
  • increasing the number of rows of heat transfer tubes as in the case of the heat exchanger 1 makes it possible to increase the amount of heat exchange without changing the area of the heat exchanger 1 as seen in front view, the spacing of the fins 5, or the like.
  • Increasing the number of rows of heat transfer tubes to two increases the amount of heat exchange by more than about 1.5 times.
  • the number of rows of heat transfer tubes may be increased to three or more. Further, the area of the heat exchanger 1 as seen in front view, the spacing of the fins 5, or the like may be changed.
  • the header (the stacking-type header 2) is provided only on one side of the heat exchanger 1. If the heat exchanger 1 is disposed in such a way that, in order to increase the mounting volume of its heat exchange unit, for example, the heat exchanger 1 is bent along a plurality of side faces of the housing that contains the heat exchanger 1, each row of heat transfer tubes differs in the radius of curvature of its bent portion, which causes the end portions of individual rows of heat transfer tubes to become misaligned.
  • a header (the stacking-type header 2) is provided only on one side of the heat exchanger 1 as in the case of the stacking-type header 2, even if the end portions of individual rows of heat transfer tubes become out of alignment, only the end portions on one side needs to be aligned, thus enabling improvements in terms of the freedom of design, production efficiency, and the like in comparison to when headers (the stacking-type header 2 and the header 3) are provided on both sides of the heat exchanger 1 as in the case of the heat exchanger according to Embodiment 1. In particular, it also becomes possible to bend the heat exchanger 1 after joining each member of the heat exchanger 1, thus enabling a further improvement in production efficiency.
  • the first heat transfer tube 4 is located on the upstream side of airflow in comparison to the second heat transfer tube 6.
  • headers the stacking-type header 2 and a header 3 are provided on both sides of the heat exchanger 1 as in the case of the heat exchanger according to Embodiment 1, it is difficult to improve the condenser performance of the heat exchanger by providing a difference in the temperature of refrigerant between each row of heat transfer tubes.
  • each of the first heat transfer tube 4 and the second heat transfer tube 6 is a flat tube, unlike a circular tube, the limited freedom of bending means that it is difficult to provide a refrigerant temperature difference between each row of heat transfer tubes by deforming refrigerant passages.
  • the first heat transfer tube 4 and the second heat transfer tube 6 are connected to the stacking-type header 2 as in the case of the heat exchanger 1, a difference in refrigerant temperature is naturally created between each row of heat transfer tubes. Consequently, the refrigerant flow and the airflow can be opposed to each other easily without deforming refrigerant passages.

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

Claims (14)

  1. Stapel-Typ-Verteiler, umfassend:
    eine erste plattenförmige Einheit (11), die eine Vielzahl von darin ausgebildeten, ersten Auslassströmungskanälen (11A) aufweist; und
    eine zweite plattenförmige Einheit (12), die auf der ersten plattenförmigen Einheit (11) gestapelt ist und einen darin ausgebildeten, ersten Einlassströmungskanal (12a) und einen darin ausgebildeten, Verteilungsströmungskanal (12A) aufweist, wobei der Verteilungsströmungskanal (12A) konfiguriert ist, ein Kühlmittel zu verteilen, das durch den ersten Einlassströmungskanal (12a) hindurchtritt, um in die zweite plattenförmige Einheit (12) hinein, zu der Vielzahl von ersten Auslassströmungskanälen (11A) hin, zu strömen, um zu bewirken, dass das Kühlmittel aus der zweiten plattenförmigen Einheit (12) herausströmt,
    worin der Verteilungsströmungskanal (12A) mindestens einen Verzweigungsströmungskanal (12b) umfasst,
    worin die zweite plattenförmige Einheit (12) mindestens ein erstes plattenförmiges Element (24) aufweist, wobei der Stapel-Typ-Verteiler dadurch gekennzeichnet ist,
    dass das erste plattenförmige Element (24) mindestens einen durch Pressbearbeitung ausgebildeten, ersten Vorsprung (24A) aufweist, wobei der erste Vorsprung (24A) in eine Richtung vorsteht, in welche die zweite plattenförmige Einheit (12) auf der ersten plattenförmigen Einheit (11) gestapelt ist, und
    worin der Verzweigungsströmungskanal (12b) durch Schließen eines Bereichs in einem Inneren des ersten Vorsprungs (24A) ausgebildet ist, der sich von einem Bereich, in den das Kühlmittel hineinströmt und aus dem das Kühlmittel herausströmt, unterscheidet.
  2. Stapel-Typ-Verteiler nach Anspruch 1, worin:
    eine Umfangskante des ersten plattenförmigen Elements (24) gebogen ist; und
    ein distales Ende der Umfangskante mit einer Seitenfläche eines Elements zusammengefügt ist, das daran angrenzend befestigt ist.
  3. Stapel-Typ-Verteiler nach Anspruch 1 oder 2, worin:
    das erste plattenförmige Element (24) mindestens einen zweiten Vorsprung (24B) aufweist, der in einem Bereich vorgesehen ist, der sich von einem mit dem ersten Vorsprung (24A) bereitgestellten Bereich unterscheidet; und
    eine Innenfläche des zweiten Vorsprungs (24B) mit einer Außenfläche eines Vorsprungs zusammengefügt ist, der in einem Element vorgesehen ist, das an diesen angrenzend befestigt ist.
  4. Stapel-Typ-Verteiler nach einem der Ansprüche 1 bis 3, worin:
    der erste Vorsprung (24A) eine Unterseite aufweist; und
    das Innere des ersten Vorsprungs (24A) durch eine Außenfläche eines Vorsprungs geschlossen ist, der in einem Element vorgesehen ist, das an diesen angrenzend befestigt ist.
  5. Stapel-Typ-Verteiler nach einem der Ansprüche 1 bis 3, worin:
    die zweite plattenförmige Einheit (12) mindestens ein zweites plattenförmiges Element (25) aufweist, wobei das zweite plattenförmige Element (25) mindestens einen durchgehenden Abschnitt aufweist;
    eine Unterseite des ersten Vorsprungs (24A) hohl ist;
    das zweite plattenförmige Element (25) mit dem ersten plattenförmigen Element (24) derart zusammengefügt ist, dass der durchgehende Abschnitt mit einer Außenfläche eines distalen Endes des ersten Vorsprungs (24A) zusammengefügt ist; und
    das Innere des ersten Vorsprungs (24A) durch eine Oberfläche eines Elements, das an einer Seite des ersten plattenförmigen Elements (24), die sich von einer Seite, zu welcher der erste Vorsprung (24A) hin vorspringt, unterscheidet, befestigt ist, und eine Oberfläche eines Elements, das an einer Seite des zweiten plattenförmigen Elements (25), die einer Seite gegenüberliegt, an der das erste plattenförmige Element (24) vorhanden ist, befestigt ist, geschlossen ist.
  6. Stapel-Typ-Verteiler nach einem der Ansprüche 1 bis 5, worin:
    die erste plattenförmige Einheit (11) eine Vielzahl von zweiten Einlassströmungskanälen (11B) aufweist; und
    die zweite plattenförmige Einheit (12) einen Zusammenführungsströmungskanal (12B) aufweist, wobei der Zusammenführungsströmungskanal (12B) bewirkt, dass ein Kühlmittel aus jedem der zweiten Einlassströmungskanäle eintritt, um in einen zweiten Auslassströmungskanal (12d) zu münden und in diesen einzutreten.
  7. Stapel-Typ-Verteiler nach einem der Ansprüche 1 bis 6, worin die erste plattenförmige Einheit (11) eine Vielzahl von darin ausgebildeten Rückströmungskanälen (11C) aufweist, wobei die Vielzahl von Rückströmungskanälen (11C) konfiguriert ist, das in die erste plattenförmige Einheit (11) strömende Kühlmittel zurückströmen zu lassen, um zu bewirken, dass das Kühlmittel aus der ersten plattenförmigen Einheit (11) herausströmt.
  8. Wärmetauscher, umfassend:
    den Stapel-Typ-Verteiler nach einem der Ansprüche 1 bis 5; und
    eine Vielzahl von ersten Wärmetransportrohren (4), die jeweils mit der Vielzahl von ersten Auslassströmungskanälen (11A) verbunden sind.
  9. Wärmetauscher nach Anspruch 8,
    worin die erste plattenförmige Einheit (11) eine Vielzahl von darin ausgebildeten, zweiten Einlassströmungskanälen (11B) aufweist, in die das Kühlmittel, das durch die Vielzahl von ersten Wärmetransportrohren (4) hindurchtritt, hineinströmt, und
    worin die zweite plattenförmige Einheit (12) einen darin ausgebildeten Zusammenführungsströmungskanal (12B) aufweist, wobei der Zusammenführungsströmungskanal (12B) konfiguriert ist, Kühlmittelströme zusammenzuführen, die durch die Vielzahl von zweiten Einlassströmungskanälen (11B) hindurchtreten, um in die zweite plattenförmige Einheit (12) hineinzuströmen, um zu bewirken, dass das Kühlmittel in einen zweiten Auslassströmungskanal (12d) strömt.
  10. Wärmetauscher nach Anspruch 9, worin:
    die erste plattenförmige Einheit (11) eine Vielzahl von Rückströmungskanälen (11C) aufweist, die jeweils an einer Einlassseite derselben mit einem jeweiligen der ersten Wärmetransportrohre (4) verbunden sind, wobei die Rückströmungskanäle (11C) bewirken, dass das Kühlmittel, das von den ersten Wärmetransportrohren (4) eintritt, umgelenkt wird und aus den Rückströmungskanälen (11C) herausströmt; und
    der Wärmetauscher eine Vielzahl von zweiten Wärmetransportrohren (6) umfasst, wobei die zweiten Wärmetransportrohre (6) jeweils mit einer Auslassseite eines entsprechenden der Rückströmungskanäle (11C) und einem entsprechenden der zweiten Einlassströmungskanäle (11B) verbunden ist.
  11. Wärmetauscher nach einem der Ansprüche 8 bis 10, worin die Vielzahl von Wärmetransportrohren jeweils ein Flachrohr umfasst.
  12. Wärmetauscher nach Anspruch 11, worin jeder der ersten Auslassströmungskanäle (11A) eine Innenumfangsfläche aufweist, die sich in Richtung einer Außenumfangsfläche von jedem der ersten Wärmetransportrohre (4) allmählich ausdehnt.
  13. Klimatisierungsvorrichtung, umfassend den Wärmetauscher nach einem der Ansprüche 8 bis 12,
    worin der Verteilungsströmungskanal (12A) konfiguriert ist zu bewirken, dass das Kühlmittel aus dem Verteilungsströmungskanal (12A) heraus, zur Vielzahl von ersten Auslassströmungskanälen (11A) hin, strömt, wenn der Wärmetauscher als ein Verdampfer wirkt.
  14. Klimatisierungsvorrichtung, umfassend den Wärmetauscher nach Anspruch 10,
    worin der Verteilungsströmungskanal (12A) konfiguriert ist zu bewirken, dass das Kühlmittel aus dem Verteilungsströmungskanal (12A) heraus, zu der Vielzahl von ersten Auslassströmungskanälen (11A) hin, strömt, wenn der Wärmetauscher als ein Verdampfer wirkt, und
    worin die Vielzahl von ersten Wärmetransportrohren (4) auf einer windzugewandten Seite mit Bezug auf die Vielzahl von zweiten Wärmetransportrohren (6) positioniert ist, wenn der Wärmetauscher als ein Kondensator wirkt.
EP13884840.3A 2013-05-15 2013-05-15 Gestapelter kopf, wärmetauscher und klimatisierungsvorrichtung Active EP2998681B1 (de)

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JPWO2014184913A1 (ja) 2017-02-23
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HK1217116A1 (zh) 2016-12-23
CN203964700U (zh) 2014-11-26
EP2998681A1 (de) 2016-03-23

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