US20160116231A1 - Stacking-type header, heat exchanger, and air-conditioning apparatus - Google Patents

Stacking-type header, heat exchanger, and air-conditioning apparatus Download PDF

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Publication number: US20160116231A1
Authority: US; United States
Prior art keywords: flow passage; flow; plate; refrigerant; shaped unit
Prior art date: 2013-05-15
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Abandoned

Application number

US14/786,595

Other languages

English (en)

Inventor

Shinya Higashiiue

Takashi Okazaki

Akira Ishibashi

Daisuke Ito

Takuya Matsuda

Shigeyoshi MATSUI

Atsushi Mochizuki

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Mitsubishi Electric Corp

Original Assignee

Mitsubishi Electric Corp

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

2013-05-15

Filing date

2013-05-15

Publication date

2016-04-28

2013-05-15 Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp

2015-10-23 Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OKAZAKI, TAKASHI, MATSUI, Shigeyoshi, HIGASHIIUE, SHINYA, ISHIBASHI, AKIRA, ITO, DAISUKE, MATSUDA, TAKUYA, MOCHIZUKI, ATSUSHI

2016-04-28 Publication of US20160116231A1 publication Critical patent/US20160116231A1/en

Status Abandoned legal-status Critical Current

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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
- 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, and an air-conditioning apparatus.
a stacking-type header including a first plate-shaped unit having a plurality of outlet flow passages formed therein, and a second plate-shaped unit stacked on the first plate-shaped unit and having a distribution flow passage formed therein, for distributing refrigerant, which passes through an inlet flow passage to flow into the second plate-shaped unit, to the plurality of outlet flow passages formed in the first plate-shaped unit to cause the refrigerant to flow out from the second plate-shaped unit.
the distribution flow passage includes a branching flow passage having a plurality of grooves extending perpendicular to a refrigerant inflow direction.
the refrigerant passing through the inlet flow passage passes through the plurality of grooves to be branched into a plurality of flows, to thereby pass through the plurality of outlet flow passages formed in the first plate-shaped unit to flow out from the first plate-shaped unit (for example, see Patent Literature 1).
the related-art stacking-type header has a problem in that the uniformity in distribution of the refrigerant is low.
the present invention has been made in view of the above-mentioned problems, and has an object to provide a stacking-type header improved in uniformity in distribution of refrigerant. Further, the present invention has an object to provide a heat exchanger improved in uniformity in distribution of refrigerant. Further, the present invention has an object to provide an air-conditioning apparatus improved in uniformity in distribution of refrigerant.
a stacking-type header including: a first plate-shaped unit having a plurality of first outlet flow passages formed therein; and a second plate-shaped unit stacked on the first plate-shaped unit, the second plate-shaped unit having a distribution flow passage formed therein, the distribution flow passage being configured to distribute refrigerant, which passes through a first inlet flow passage to flow into the second plate-shaped unit, to the plurality of first outlet flow passages to cause the refrigerant to flow out from the second plate-shaped unit, in which the distribution flow passage includes a branching flow passage including: an opening port configured to allow the refrigerant to flow thereinto; a first flow passage communicating between the opening port and an end portion positioned on an upper side relative to the opening port; and a second flow passage communicating between the opening port and an end portion positioned on a lower side relative to the opening port, and in which the branching flow passage is smaller in difference in flow resistance between the first flow passage and the second flow passage than a branching
the distribution flow passage includes the branching flow passage including: the opening port configured to allow the refrigerant to flow thereinto; the first flow passage communicating between the opening port and the end portion positioned on the upper side relative to the opening port; and the second flow passage communicating between the opening port and the end portion positioned on the lower side relative to the opening port, and the branching flow passage is smaller in difference in flow resistance between the first flow passage and the second flow passage than the branching flow passage in a state in which the flow-passage resistance in the first flow passage and the flow-passage resistance in the second flow passage are equal to each other, and in a state in which the first flow passage and the second flow passage are point symmetric with each other about the opening port.
the refrigerant passing through the first flow passage and the refrigerant passing through the second flow passage flow out at heights different from each other, with the result that the flow resistance of the first flow passage is larger than the flow resistance of the second flow passage so that a flow rate of the refrigerant that passes through the first flow passage to flow out is smaller than a flow rate of the refrigerant that passes through the second flow passage to flow out.
This phenomenon is suppressed in the stacking-type header according to the one embodiment of the present invention, and thus, the uniformity in distribution of the refrigerant is improved.
FIG. 1 is a view illustrating a configuration of a heat exchanger according to Embodiment 1.
FIG. 2 is a perspective view illustrating the heat exchanger according to Embodiment 1 under a state in which a stacking-type header is disassembled.
FIG. 3 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
FIG. 4 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
FIG. 5 are views each illustrating a modified example of a flow passage formed in a third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 6 is a perspective view illustrating the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 7 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
FIG. 8 is a view illustrating a comparative example of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 9 is a view illustrating Specific Example-1 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 10 is a graph showing effects of Specific Example-1 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 11 is a view illustrating Specific Example-2 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 12 is a view illustrating Specific Example-2 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 13 is a view illustrating Specific Example-3 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 14 is a view illustrating Specific Example-5 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 15 are views each illustrating a state of refrigerant of Specific Example-5 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 16 is a view illustrating Specific Example-6 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 17 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied.
FIG. 18 is a perspective view of Modified Example-1 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 19 is a perspective view of Modified Example-1 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 20 is a perspective view of Modified Example-2 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 21 is a perspective view of Modified Example-3 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 22 is a developed view of the stacking-type header of Modified Example-3 of the heat exchanger according to Embodiment 1.
FIG. 23 is a perspective view of Modified Example-4 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 24 are a main-part perspective view and a main-part sectional view of Modified Example-5 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 25 are a main-part perspective view and a main-part sectional view of Modified Example-6 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 26 are views each illustrating a specific example of the flow passage formed in the third plate-shaped member of Modified Example-6 of the heat exchanger according to Embodiment 1.
FIG. 27 is a perspective view of Modified Example-7 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 28 is a view illustrating a configuration of a heat exchanger according to Embodiment 2.
FIG. 29 is a perspective view illustrating the heat exchanger according to Embodiment 2 under a state in which a stacking-type header is disassembled.
FIG. 30 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 2.
FIG. 31 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 2 is applied.
FIG. 32 is a view illustrating a configuration of a heat exchanger according to Embodiment 3.
FIG. 33 is a perspective view illustrating the heat exchanger according to Embodiment 3 under a state in which a stacking-type header is disassembled.
FIG. 34 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 3.
FIG. 35 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 3 is applied.
the stacking-type header according to the present invention distributes refrigerant flowing into a heat exchanger, but the stacking-type header according to the present invention may distribute refrigerant flowing into other devices.
the configuration, operation, and other matters described below are merely examples, and the present invention is not limited to such configuration, operation, and other matters.
the same or similar components are denoted by the same reference symbols, or the reference symbols therefor are omitted. Further, the illustration of details in the structure is appropriately simplified or omitted. Further, overlapping description or similar description is appropriately simplified or omitted.
a resistance to act on refrigerant passing through a flow passage is generally defined as a “flow resistance”, and an element of the “flow resistance”, which is derived from characteristics of the flow passage (such as a shape and a surface property), is defined as a “flow-passage resistance”.
a heat exchanger according to Embodiment 1 is described.
FIG. 1 is a view illustrating the configuration of the heat exchanger according to Embodiment 1.
a heat exchanger 1 includes a stacking-type header 2 , a header 3 , a plurality of first heat transfer tubes 4 , a retaining member 5 , and a plurality of fins 6 .
the stacking-type header 2 includes a refrigerant inflow port 2 A and a plurality of refrigerant outflow ports 2 B.
the header 3 includes a plurality of refrigerant inflow ports 3 A and a refrigerant outflow port 3 B.
Refrigerant pipes are connected to the refrigerant inflow port 2 A of the stacking-type header 2 and the refrigerant outflow port 3 B of the header 3 .
the plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2 B of the stacking-type header 2 and the plurality of refrigerant inflow ports 3 A of the header 3 .
the first heat transfer tube 4 is a flat tube having a plurality of flow passages formed therein.
the first heat transfer tube 4 is made of, for example, aluminum. End portions of the plurality of first heat transfer tubes 4 on the stacking-type header 2 side are connected to the plurality of refrigerant outflow ports 2 B of the stacking-type header 2 under a state in which the end portions are retained by the plate-shaped retaining member 5 .
the retaining member 5 is made of, for example, aluminum.
the plurality of fins 6 are joined to the first heat transfer tubes 4 .
the fin 6 is made of, for example, aluminum. It is preferred that the first heat transfer tubes 4 and the fins 6 be joined by brazing. Note that, in FIG. 1 , there is illustrated a case where eight first heat transfer tubes 4 are provided, but the present invention is not limited to such a case.
the refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2 A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2 B to flow out toward the plurality of first heat transfer tubes 4 .
the refrigerant exchanges heat with air supplied by a fan, for example.
the refrigerant flowing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inflow ports 3 A to flow into the header 3 to be joined, and then passes through the refrigerant outflow port 3 B to flow out toward the refrigerant pipe.
the refrigerant can reversely flow.
FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
the stacking-type header 2 includes 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 on each other.
the first plate-shaped unit 11 is stacked on the refrigerant outflow side.
the first plate-shaped unit 11 includes a first plate-shaped member 21 .
the first plate-shaped unit 11 has a plurality of first outlet flow passages 11 A formed therein.
the plurality of first outlet flow passages 11 A correspond to the plurality of refrigerant outflow ports 2 B in FIG. 1 .
the first plate-shaped member 21 has a plurality of flow passages 21 A formed therein.
the plurality of flow passages 21 A are each a through hole having an inner peripheral surface shaped conforming to an outer peripheral surface of the first heat transfer tube 4 .
the plurality of flow passages 21 A function as the plurality of first outlet flow passages 11 A.
the first plate-shaped member 21 has a thickness of about 1 mm to 10 mm, and is made of aluminum, for example.
the end portions of the first heat transfer tubes 4 are projected from the surface of the retaining member 5 .
the first plate-shaped unit 11 When the first plate-shaped unit 11 is stacked on the retaining member 5 so that the inner peripheral surfaces of the first outlet flow passages 11 A are fitted to the outer peripheral surfaces of the respective end portions of the first heat transfer tubes 4 , the first heat transfer tubes 4 are connected to the first outlet flow passages 11 A.
the first outlet flow passages 11 A and the first heat transfer tubes 4 may be positioned through, for example, fitting between a convex portion formed in the retaining member 5 and a concave portion formed in the first plate-shaped unit 11 . In such a case, the end portions of the first heat transfer tubes 4 may not be projected from the surface of the retaining member 5 .
the retaining member 5 may be omitted so that the first heat transfer tubes 4 are directly connected to the first outlet flow passages 11 A. In such a case, the component cost and the like are reduced.
the second plate-shaped unit 12 is stacked on the refrigerant inflow side.
the second plate-shaped unit 12 includes a second plate-shaped member 22 and a plurality of third plate-shaped members 23 _ 1 to 23 _ 3 .
the second plate-shaped unit 12 has a distribution flow passage 12 A formed therein.
the distribution flow passage 12 A includes a first inlet flow passage 12 a and a plurality of branching flow passages 12 b .
the first inlet flow passage 12 a corresponds to the refrigerant inflow port 2 A in FIG. 1 .
the second plate-shaped member 22 has a flow passage 22 A formed therein.
the flow passage 22 A is a circular through hole.
the flow passage 22 A functions as the first inlet flow passage 12 a .
the second plate-shaped member 22 has a thickness of about 1 mm to 10 mm, and is made of aluminum, for example.
a fitting or other such component is provided on the surface of the second plate-shaped member 22 on the refrigerant inflow side, and the refrigerant pipe is connected to the first inlet flow passage 12 a through the fitting or other such component.
the inner peripheral surface of the first inlet flow passage 12 a may be shaped to be fitted to the outer peripheral surface of the refrigerant pipe so that the refrigerant pipe may be directly connected to the first inlet flow passage 12 a without using the fitting or other such component. In such a case, the component cost and the like are reduced.
the plurality of third plate-shaped members 23 _ 1 to 23 _ 3 respectively have a plurality of flow passages 23 A_ 1 to 23 A_ 3 formed therein.
the plurality of flow passages 23 A_ 1 to 23 A_ 3 are each a through groove.
the plurality of flow passages 23 A_ 1 to 23 A_ 3 are described in detail later.
each of the plurality of flow passages 23 A_ 1 to 23 A_ 3 functions as the branching flow passage 12 b .
the plurality of third plate-shaped members 23 _ 1 to 23 _ 3 each have a thickness of about 1 mm to 10 mm, and are made of aluminum, for example.
the plurality of third plate-shaped members 23 _ 1 to 23 _ 3 are collectively referred to as the third plate-shaped member 23 .
the plurality of flow passages 23 A_ 1 to 23 A_ 3 are collectively referred to as the flow passage 23 A.
the retaining member 5 , the first plate-shaped member 21 , the second plate-shaped member 22 , and the third plate-shaped member 23 are collectively referred to as the plate-shaped member.
the branching flow passage 12 b branches the refrigerant flowing therein into two flows to cause the refrigerant to flow out therefrom. Therefore, when the number of the first heat transfer tubes 4 to be connected is eight, at least three third plate-shaped members 23 are required. When the number of the first heat transfer tubes 4 to be connected is sixteen, at least four third plate-shaped members 23 are required.
the number of the first heat transfer tubes 4 to be connected is not limited to powers of 2. In such a case, the branching flow passage 12 b and a non-branching flow passage may be combined with each other. Note that, the number of the first heat transfer tubes 4 to be connected may be two.
FIG. 3 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
the flow passage 23 A formed in the third plate-shaped member 23 has a shape in which an end portion 23 a and an end portion 23 b are connected to each other through a straight-line part 23 c .
the straight-line part 23 c is substantially perpendicular to the gravity direction.
the branching flow passage 12 b is formed by closing, by a member stacked adjacent on the refrigerant inflow side, the flow passage 23 A in a region other than a partial region 23 f (hereinafter referred to as “opening port 23 f ”) between an end portion 23 d and an end portion 23 e of the straight-line part 23 c , and closing, by a member stacked adjacent on the refrigerant outflow side, a region other than the end portion 23 a and the end portion 23 b .
a region of the flow passage 23 A, which communicates between the end portion 23 b and the opening port 23 f is defined as a second flow passage 23 h.
the end portion 23 a is positioned on the upper side relative to the opening port 23 f
the end portion 23 l is positioned on the lower side relative to the opening port 23 f .
FIG. 4 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
the stacking-type header 2 is not limited to a stacking-type header in which the plurality of first outlet flow passages 11 A are arrayed along the gravity direction, and may be used in a case where the heat exchanger 1 is installed in an inclined manner, such as a heat exchanger for a wall-mounting type room air-conditioning apparatus indoor unit, an outdoor unit for an air-conditioning apparatus, or a chiller outdoor unit. Note that, in FIG. 4
the longitudinal direction of the cross section of the flow passage 21 A formed in the first plate-shaped member 21 in other words, the longitudinal direction of the cross section of the first outlet flow passage 11 A is perpendicular to the longitudinal direction of the first plate-shaped member 21 , but the longitudinal direction of the cross section of the first outlet flow passage 11 A may be perpendicular to the gravity direction.
the flow passage 23 A may be formed as a through groove shaped so that a connecting part 23 i for connecting the end portion 23 d of the straight-line part 23 c to the end portion 23 a and a connecting part 23 j for connecting the end portion 23 e of the straight-line part 23 c to the end portion 23 b are branched, and other flow passages may communicate with the branching flow passage 12 b .
the connecting parts 23 i and 23 j may be each a straight line or a curved line.
FIG. 5 are views each illustrating a modified example of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
the flow passage 23 A may not include the straight-line part 23 c .
a horizontal part between the end portion 23 a and the end portion 23 b of the flow passage 23 A, which is substantially perpendicular to the gravity direction, serves as the opening port 23 f .
the flow passage 23 A includes the straight-line part 23 c , when the refrigerant is branched at the opening port 23 f , the angles of the respective branching directions with respect to the gravity direction are uniform, which reduces the influence of the gravity.
the influence of the gravity is increased as compared to the case of including the straight-line part 23 c .
a difference between a flow resistance to act on the refrigerant passing through the first flow passage 23 g and a flow resistance to act on the refrigerant passing through the second flow passage 23 h are set smaller so that the uniformity in distribution of the refrigerant can be improved.
each of the end portion 23 a and the end portion 23 b may communicate with each of the connecting parts 23 i and 23 j through each of straight-line parts 23 k and 23 l parallel to the gravity direction.
each of the end portions 23 a and 23 b communicates with each of the connecting parts 23 i and 23 j through the straight-line parts 23 k and 23 l , drift caused when the refrigerant passes through the connecting parts 23 i and 23 j not parallel to the gravity direction is uniformized so that the uniformity in distribution of the refrigerant can be improved.
the refrigerant passing through the flow passage 22 A of the second plate-shaped member 22 flows into the opening port 23 f of the flow passage 23 A formed in the third plate-shaped member 23 _ 1 .
the refrigerant flowing into the opening port 23 f hits against the surface of the member stacked adjacent to the third plate-shaped member 23 _ 1 , and is branched into two flows respectively toward the end portion 23 d and the end portion 23 e of the straight-line part 23 c .
the branched refrigerant reaches each of the end portions 23 a and 23 b of the flow passage 23 A and flows into the opening port 23 f of the flow passage 23 A formed in the third plate-shaped member 23 _ 2 .
the refrigerant flowing into the opening port 23 f of the flow passage 23 A formed in the third plate-shaped member 23 _ 2 hits against the surface of the member stacked adjacent to the third plate-shaped member 23 _ 2 , and is branched into two flows respectively toward the end portion 23 d and the end portion 23 e of the straight-line part 23 c .
the branched refrigerant reaches each of the end portions 23 a and 23 b of the flow passage 23 A, and flows into the opening port 23 f of the flow passage 23 A formed in the third plate-shaped member 23 _ 3 .
the refrigerant flowing into the opening port 23 f of the flow passage 23 A formed in the third plate-shaped member 23 _ 3 hits against the surface of the member stacked adjacent to the third plate-shaped member 23 _ 3 , and is branched into two flows respectively toward the end portion 23 d and the end portion 23 e of the straight-line part 23 c .
the branched refrigerant reaches each of the end portions 23 a and 23 b of the flow passage 23 A, and passes through the flow passage 21 A of the first plate-shaped member 21 to flow into the first heat transfer tube 4 .
the respective plate-shaped members may be stacked by brazing.
a both-side clad member having a brazing material rolled on both surfaces thereof may be used for all of the plate-shaped members or alternate plate-shaped members to supply the brazing material for joining.
a one-side clad member having a brazing material rolled on one surface thereof may be used for all of the plate-shaped members to supply the brazing material for joining.
a brazing-material sheet may be stacked between the respective plate-shaped members to supply the brazing material.
a paste brazing material may be applied between the respective plate-shaped members to supply the brazing material.
a both-side clad member having a brazing material rolled on both surfaces thereof may be stacked between the respective plate-shaped members to supply the brazing material.
the plate-shaped members are stacked without a gap therebetween, which suppresses leakage of the refrigerant and further secures the pressure resistance.
the plate-shaped members are pressurized during brazing, the occurrence of brazing failure is further suppressed.
processing that promotes formation of a fillet, such as forming a rib at a position at which leakage of the refrigerant is liable to occur, is performed, the occurrence of brazing failure is further suppressed.
the members to be subjected to brazing including the first heat transfer tube 4 and the fin 6 , are made of the same material (for example, made of aluminum), the members may be collectively subjected to brazing, which improves the productivity. After the brazing in the stacking-type header 2 is performed, the brazing of the first heat transfer tube 4 and the fin 6 may be performed. Further, only the first plate-shaped unit 11 may be first joined to the retaining member 5 by brazing, and the second plate-shaped unit 12 may be joined by brazing thereafter.
FIG. 6 is a perspective view of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 7 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 1.
a plate-shaped member having a brazing material rolled on both surfaces thereof in other words, a both-side clad member may be stacked between the respective plate-shaped members to supply the brazing material.
a plurality of both-side clad members 24 _ 1 to 24 _ 5 are stacked between the respective plate-shaped members.
the plurality of both-side clad members 24 _ 1 to 24 _ 5 are collectively referred to as the both-side clad member 24 .
the both-side clad member 24 may be stacked between a part of the plate-shaped members, and a brazing material may be supplied between the remaining plate-shaped members by other methods.
the both-side clad member 24 has a flow passage 24 A, which passes through the both-side clad member 24 , formed in a region that is opposed to a refrigerant outflow region of the flow passage formed in the plate-shaped member stacked adjacent on the refrigerant inflow side.
the flow passage 24 A formed in the both-side clad member 24 stacked between the second plate-shaped member 22 and the third plate-shaped member 23 is a circular through hole.
the flow passage 24 A formed in the both-side clad member 24 _ 5 stacked between the first plate-shaped member 21 and the retaining member 5 is a through hole having an inner peripheral surface shaped conforming to the outer peripheral surface of the first heat transfer tube 4 .
the flow passage 24 A functions as a refrigerant partitioning flow passage for the first outlet flow passage 11 A and the distribution flow passage 12 A.
the end portions of the first heat transfer tubes 4 may be or not be projected from the surface of the both-side clad member 24 _ 5 .
the flow passage 24 A is formed by press working or other processing, the work is simplified, and the manufacturing cost and the like are reduced.
all of the members to be subjected to brazing including the both-side clad member 24 , are made of the same material (for example, made of aluminum), the members may be collectively subjected to brazing, which improves the productivity.
the branched flows of refrigerant flowing out from the branching flow passage 12 b can be reliably partitioned from each other. Further, by the amount of the thickness of each both-side clad member 24 , an entrance length for the refrigerant flowing into the branching flow passage 12 b or the first outlet flow passage 11 A can be secured, which improves the uniformity in distribution of the refrigerant. Further, the flows of the refrigerant can be reliably partitioned from each other, and hence the degree of freedom in design of the branching flow passage 12 b can be increased.
FIG. 8 is a view illustrating a comparative example of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1. Note that, in FIG. 8 , a part of the flow passage formed in a member stacked adjacent to the third plate-shaped member is indicated by the dotted lines. A state in which the both-side clad member 24 is stacked on the third plate-shaped member 23 is illustrated (state of FIG. 6 and FIG. 7 ), but the same holds true in a state in which the both-side clad member 24 is not stacked (state of FIG. 2 and FIG. 3 ).
a height difference between the end portion 23 a and a center 23 m of the opening port 23 f is defined as a flow-passage height h 1
a height difference between the end portion 23 b and the center 23 m of the opening port 23 f is defined as a flow-passage height h 2
a flow-passage length of the first flow passage 23 g is defined as a flow-passage length l 1
a flow-passage length of the second flow passage 23 h is defined as a flow-passage length l 2
a flow-passage width of the first flow passage 23 g is defined as a flow-passage width W 1
a flow-passage width of the second flow passage 23 h is defined as a flow-passage width W 2
a bending angle of the first flow passage 23 g is defined as a bending angle ⁇ 1
a bending angle of the second flow passage 23 h is defined as a bending angle ⁇
a thickness of the third plate-shaped member 23 that is, a flow-passage depth thereof is defined as ⁇ .
the center of the refrigerant outflow region of the first flow passage 23 g is defined as the end portion 23 a
the center of the refrigerant outflow region of the second flow passage 23 h is defined as the end portion 23 b.
a pressure of the refrigerant flowing into the opening port 23 f is defined as a pressure P 0
a pressure of the refrigerant flowing out from the end portion 23 a is defined as a pressure P 1
a pressure of the refrigerant flowing out from the end portion 23 b is defined as a pressure P 2
a pressure loss caused due to the flow-passage resistance in the first flow passage 23 g is defined as a pressure loss ⁇ Pf 1
a pressure loss caused due to the flow-passage resistance in the second flow passage 23 h is defined as a pressure loss ⁇ Pf 2 .
the pressure P 1 of the refrigerant flowing out from the end portion 23 a and the pressure P 2 of the refrigerant flowing out from the end portion 23 b are calculated by (Expression 1) and (Expression 2) below using a density ⁇ [kg/m 3 ] of the refrigerant.
the pressure P 1 of the refrigerant flowing out from the end portion 23 a and the pressure P 2 of the refrigerant flowing out from the end portion 23 b are not equal to each other because a flow resistance in the first flow passage 23 g , that is, a pressure loss ( ⁇ Pf 1 +p ⁇ g ⁇ h 1 ) generated in the refrigerant passing through the first flow passage 23 g and a flow resistance in the second flow passage 23 h , that is, a pressure loss ( ⁇ Pf 2 ⁇ g ⁇ h 2 ) generated in the refrigerant passing through the second flow passage 23 h are different from each other.
a flow rate of the refrigerant flowing out from the end portion 23 a and a flow rate of the refrigerant flowing out from the end portion 23 b are nonuniform.
the pressure loss ⁇ Pf 1 caused due to the flow-passage resistance in the first flow passage 23 g and the pressure loss ⁇ Pf 2 caused due to the flow-passage resistance in the second flow passage 23 h are respectively expressed by (Expression 3) and (Expression 4) below by using a friction coefficient ⁇ 1 [dimensionless] of the first flow passage 23 g , a friction coefficient ⁇ 2 [dimensionless] of the second flow passage 23 h , a hydraulic equivalent diameter dh 1 [m] of the first flow passage 23 g , a hydraulic equivalent diameter dh 2 [m] of the second flow passage 23 h , a flow velocity u 1 [m/s] of the refrigerant flowing through the first flow passage 23 g , a flow velocity u 2 [m/s] of the refrigerant flowing through the second flow passage 23 h , and a flow rate Gr [kg/s] of the refrigerant.
the pressure loss ⁇ Pf 1 caused due to the flow-passage resistance in the first flow passage 23 g and the pressure loss ⁇ Pf 2 caused due to the flow-passage resistance in the second flow passage 23 h have parameters such as the flow-passage lengths l 1 and l 2 , the flow-passage widths W 1 and W 2 , and the friction coefficients ⁇ 1 and ⁇ 2 , respectively.
the difference between the pressure loss ( ⁇ Pf 1 + ⁇ g ⁇ h 1 ) generated in the refrigerant passing through the first flow passage 23 g and the pressure loss ( ⁇ Pf 2 ⁇ g ⁇ h 2 ) generated in the refrigerant passing through the second flow passage 23 h can be set to 0 as necessary.
the flow passage 23 A of the third plate-shaped member 23 is improved so as to reduce the difference in flow resistance between the first flow passage 23 g and the second flow passage 23 h as compared to that in a state in which the flow-passage resistances in the first flow passage 23 g and the second flow passage 23 h are equal to each other, and in a state in which the first flow passage 23 g and the second flow passage 23 h are point symmetric with each other about the opening port 23 f .
the flow rate of the refrigerant flowing out from the end portion 23 a and the flow rate of the refrigerant flowing out from the end portion 23 b are equalized, which improves the uniformity in distribution of the refrigerant in the stacking-type header 2 .
the respective specific examples may be combined with each other.
FIG. 9 is a view illustrating Specific Example-1 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
the flow-passage width W 2 of the second flow passage 23 h is smaller than the flow-passage width W 1 of the first flow passage 23 g .
the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
FIG. 10 is a graph showing effects of Specific Example-1 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1. Note that, the flow rate of the refrigerant flowing through the first flow passage 23 g is defined as Wr 1 , and the flow rate of the refrigerant flowing through the second flow passage 23 h is defined as Wr 2 .
a ratio of the flow rate Wr 1 of the refrigerant flowing through the first flow passage 23 g to a sum of the flow rate Wr 1 of the refrigerant flowing through the first flow passage 23 g and the flow rate Wr 2 of the refrigerant flowing through the second flow passage 23 h can approach 0.5.
FIG. 11 is a view illustrating Specific Example-2 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
the flow-passage length l 2 of the second flow passage 23 h is larger than the flow-passage length l 1 of the first flow passage 23 g .
the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity. Effects of Specific Example-2 are the same as those obtained by changing the horizontal axis of FIG. 9 to l 2 /l 1 .
FIG. 12 is a view illustrating Specific Example-2 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 11 there is illustrated a case where the flow-passage length l 2 of the second flow passage 23 h is set larger than the flow-passage length l 1 of the first flow passage 23 g under a state in which the flow-passage height h 1 of the first flow passage 23 g and the flow-passage height h 2 of the second flow passage 23 h are set equal to each other.
the flow-passage height h 2 of the second flow passage 23 h may be set larger than the flow-passage height h 1 of the first flow passage 23 g in order that the flow-passage length l 2 of the second flow passage 23 h is larger than the flow-passage length l 1 of the first flow passage 23 g.
the flow-passage height h 2 of the second flow passage 23 h may be set larger than the flow-passage height h 1 of the first flow passage 23 g without changing a sum of the flow-passage height h 1 of the first flow passage 23 g and the flow-passage height h 2 of the second flow passage 23 h . Further, the flow-passage height h 2 of the second flow passage 23 h may be set larger than the flow-passage height h 1 of the first flow passage 23 g while changing the sum of the flow-passage height h 1 of the first flow passage 23 g and the flow-passage height h 2 of the second flow passage 23 h .
the flow-passage height h 2 of the second flow passage 23 h may be set larger than the flow-passage height h 1 of the first flow passage 23 g while increasing the sum of the flow-passage height h 1 of the first flow passage 23 g and the flow-passage height h 2 of the second flow passage 23 h.
FIG. 13 is a view illustrating Specific Example-3 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
the second flow passage 23 h has a projecting portion 23 n formed therein, which projects inward from the flow passage.
the projecting portion 23 n is an annular reducing portion, a semispherical projection, or the like.
the sectional area of the second flow passage 23 h is reduced so that the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
the projecting portion 23 n may be formed through insertion of a projecting portion formed on a member stacked adjacent to the third plate-shaped member into the flow passage 23 A. Note that, in the first flow passage 23 g , there may be formed a projecting portion having a projection amount smaller than that of the projecting portion 23 n formed in the second flow passage 23 h.
a surface roughness Ra 2 of the second flow passage 23 h is higher than a surface roughness Ra 1 of the first flow passage 23 g .
the friction coefficient ⁇ 2 of the second flow passage 23 h is increased so that the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
Effects of Specific Example-4 are the same as those obtained by changing the horizontal axis of FIG. 9 to Ra 2 /Ra 1 .
FIG. 14 is a view illustrating Specific Example-5 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
FIG. 15 are views each illustrating a state of the refrigerant of Specific Example-5 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1. Note that, FIG. 15( a ) illustrates a case where the bending angle ⁇ 2 of the second flow passage 23 h is smaller, and FIG. 15( b ) illustrates a case where the bending angle ⁇ 2 of the second flow passage 23 h is larger.
the bending angle ⁇ 2 of the second flow passage 23 h is larger than the bending angle ⁇ 1 of the first flow passage 23 g .
the flow of the refrigerant is disturbed to cause vortexes on an outer side of the bending portion and an inner side of the bending portion on the refrigerant outflow side.
the bending angle ⁇ 2 of the second flow passage 23 h is larger than the bending angle ⁇ 1 of the first flow passage 23 g , a region in which the flow of the refrigerant is disturbed is increased in the second flow passage 23 h so that the influence of the vortexes is increased.
the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
Effects of Specific Example-5 are the same as those obtained by changing the horizontal axis of FIG. 9 to ⁇ 2 / ⁇ 1 .
FIG. 16 is a view illustrating Specific Example-6 of the flow passage formed in the third plate-shaped member of the heat exchanger according to Embodiment 1.
the straight-line part 23 c is inclined by an inclination angle ⁇ 3 from a direction perpendicular to the gravity direction so that the second flow passage 23 h side is higher.
the refrigerant flowing through the first flow passage 23 g utilizes the gravity
the refrigerant flowing through the second flow passage 23 h resists the gravity.
the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
the flow passage 23 A may not include the straight-line part 23 c .
the first flow passage 23 g may communicate with the opening port 23 f from a lower side of the opening port 23 f
the second flow passage 23 h may communicate with the opening port 23 f from an upper side of the opening port 23 f.
the heat exchanger according to Embodiment 1 is used for an air-conditioning apparatus, but the present invention is not limited to such a case, and for example, the heat exchanger according to Embodiment 1 may be used for other refrigeration cycle apparatus including a refrigerant circuit. Further, there is described a case where the air-conditioning apparatus switches between a cooling operation and a heating operation, but the present invention is not limited to such a case, and the air-conditioning apparatus may perform only the cooling operation or the heating operation.
FIG. 17 is a view illustrating the configuration of the air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied. Note that, in FIG. 17 , the flow of the refrigerant during the cooling operation is indicated by the solid arrow, while the flow of the refrigerant during the heating operation is indicated by the dotted arrow.
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 refrigerant pipes to form a refrigerant circuit.
the controller 59 is connected to, 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 passage of the four-way valve 53 to switch between the cooling operation and the heating operation.
the heat source-side heat exchanger 54 acts as a condensor during the cooling operation, and acts as an evaporator during the heating operation.
the load-side heat exchanger 56 acts as the evaporator during the cooling operation, and acts as the condensor during the heating operation.
the refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 52 passes through the four-way valve 53 to flow into the heat source-side heat exchanger 54 , and is condensed through heat exchange with the outside air supplied by the heat source-side fan 57 , to thereby become the refrigerant in a high-pressure liquid state, which flows out from the heat source-side heat exchanger 54 .
the refrigerant in the high-pressure liquid state flowing out from the heat source-side heat exchanger 54 flows into the expansion device 55 to become the refrigerant in a low-pressure two-phase gas-liquid state.
the refrigerant in the low-pressure two-phase gas-liquid state flowing out from the expansion device 55 flows into the load-side heat exchanger 56 to be evaporated through heat exchange with indoor air supplied by the load-side fan 58 , to thereby become the refrigerant in a low-pressure gas state, which flows out from the load-side heat exchanger 56 .
the refrigerant in the low-pressure gas state flowing out from the load-side heat exchanger 56 passes through the four-way valve 53 to be sucked into the compressor 52 .
the refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 52 passes through the four-way valve 53 to flow into the load-side heat exchanger 56 , and is condensed through heat exchange with the indoor air supplied by the load-side fan 58 , to thereby become the refrigerant in a high-pressure liquid state, which flows out from the load-side heat exchanger 56 .
the refrigerant in the high-pressure liquid state flowing out from the load-side heat exchanger 56 flows into the expansion device 55 to become the refrigerant in a low-pressure two-phase gas-liquid state.
the refrigerant in the low-pressure two-phase gas-liquid state flowing out from the expansion device 55 flows into the heat source-side heat exchanger 54 to be evaporated through heat exchange with the outside air supplied by the heat source-side fan 57 , to thereby become the refrigerant in a low-pressure gas state, which flows out from the heat source-side heat exchanger 54 .
the refrigerant in the low-pressure gas state flowing out from the heat source-side heat exchanger 54 passes through the four-way valve 53 to be sucked into the compressor 52 .
the heat exchanger 1 is used for at least one of the heat source-side heat exchanger 54 or the load-side heat exchanger 56 .
the heat exchanger 1 acts as the evaporator
the heat exchanger 1 is connected so that the refrigerant flows in from the stacking-type header 2 and the refrigerant flows out from the header 3 .
the refrigerant in the two-phase gas-liquid state passes through the refrigerant pipe to flow into the stacking-type header 2
the refrigerant in the gas state passes through the first heat transfer tube 4 to flow into the header 3 .
the refrigerant in the gas state passes through the refrigerant pipe to flow into the header 3 , and the refrigerant in the liquid state passes through the first heat transfer tube 4 to flow into the stacking-type header 2 .
the flow passage 23 A of the third plate-shaped member 23 is smaller in difference in flow resistance between the first flow passage 23 g and the second flow passage 23 h than that in the state in which the flow-passage resistances in the first flow passage 23 g and the second flow passage 23 h are equal to each other, and in a state in which the first flow passage 23 g and the second flow passage 23 h are point symmetric with each other about the opening port 23 f . Therefore, the flow rate of the refrigerant flowing out from the end portion 23 a and the flow rate of the refrigerant flowing out from the end portion 23 b are equalized, which improves the uniformity in distribution of the refrigerant in the stacking-type header 2 .
the flow passage 23 A formed in the third plate-shaped member 23 is a through groove, and the branching flow passage 12 b is formed by stacking the third plate-shaped member 23 . Therefore, the processing and assembly are simplified, and the production efficiency, the manufacturing cost, and the like are reduced.
the refrigerant flowing therein when the refrigerant flowing therein is in a two-phase gas-liquid state, the refrigerant is easily affected by the gravity, and it is difficult to equalize the flow rate and the quality of the refrigerant flowing into each heat transfer tube.
the stacking-type header 2 regardless of the flow rate and the quality of the refrigerant in the two-phase gas-liquid state flowing therein, the refrigerant is less liable to be affected by the gravity, and the flow rate and the quality of the refrigerant flowing into each first heat transfer tube 4 can be equalized.
the stacking-type header when the heat transfer tube is changed from a circular tube to a flat tube for the purpose of reducing the refrigerant amount or achieving space saving in the heat exchanger, the stacking-type header is required to be upsized in the entire peripheral direction perpendicular to the refrigerant inflow direction.
the stacking-type header 2 is not required to be upsized in the entire peripheral direction perpendicular to the refrigerant inflow direction, and thus space saving is achieved in the heat exchanger 1 .
the sectional area of the flow passage in the heat transfer tube is reduced, and thus the pressure loss caused in the heat transfer tube is increased. Therefore, it is necessary to further reduce the angular interval between the plurality of grooves forming the branching flow passage to increase the number of paths (in other words, the number of heat transfer tubes), which causes upsize of the stacking-type header in the entire peripheral direction perpendicular to the refrigerant inflow direction.
the stacking-type header 2 even when the number of paths is required to be increased, the number of the third plate-shaped members 23 is only required to be increased, and hence the upsize of the stacking-type header 2 in the entire peripheral direction perpendicular to the refrigerant inflow direction is suppressed.
the stacking-type header 2 is not limited to the case where the first heat transfer tube 4 is a flat tube.
FIG. 18 is a perspective view of Modified Example-1 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled. Note that, in FIG. 18 and subsequent figures, a state in which the both-side clad member 24 is stacked is illustrated (state of FIG. 6 and FIG. 7 ), but it is needless to say that a state in which the both-side clad member 24 is not stacked (state of FIG. 2 and FIG. 3 ) may be employed.
the second plate-shaped member 22 may have the plurality of flow passages 22 A formed therein, in other words, the second plate-shaped unit 12 may have the plurality of first inlet flow passages 12 a formed therein, to thereby reduce the number of the third plate-shaped members 23 .
the component cost, the weight, and the like can be reduced.
FIG. 19 is a perspective view of Modified Example-1 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
the plurality of flow passages 22 A may not be formed in regions opposed to refrigerant inflow regions of the flow passages 23 A formed in the third plate-shaped member 23 .
the plurality of flow passages 22 A may be formed collectively at one position, and a flow passage 25 A of a different plate-shaped member 25 stacked between the second plate-shaped member 22 and the third plate-shaped member 23 _ 1 may guide each of the flows of the refrigerant passing through the plurality of flow passages 22 A to a region opposed to the refrigerant inflow region of the flow passage 23 A formed in the third plate-shaped member 23 .
FIG. 20 is a perspective view of Modified Example-2 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
any one of the third plate-shaped members 23 may be replaced by a different plate-shaped member 25 having a flow passage 25 B whose opening port 23 f is not positioned in the straight-line part 23 c .
the opening port 23 f is not positioned in the straight-line part 23 c but positioned in an intersecting part, and the refrigerant flows into the intersecting part to be branched into four flows.
the number of branches may be any number. As the number of branches is increased, the number of the third plate-shaped members 23 is reduced. With such a configuration, the uniformity in distribution of the refrigerant is reduced, but the component cost, the weight, and the like are reduced.
FIG. 21 is a perspective view of Modified Example-3 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 22 is a developed view of the stacking-type header of Modified Example-3 of the heat exchanger according to Embodiment 1. Note that, in FIG. 22 , the illustration of the both-side clad member 24 is omitted.
any one of the third plate-shaped members 23 may include the flow passage 23 A functioning as the branching flow passage 12 b for causing the refrigerant to flow out therefrom to the side on which the first plate-shaped unit 11 is present without turning back the refrigerant, and a flow passage 23 B functioning as a branching flow passage 12 b for causing the refrigerant to flow out therefrom by turning back the refrigerant to a side opposite to the side on which the first plate-shaped unit 11 is present.
the flow passage 23 B has a configuration similar to that of the flow passage 23 A.
the flow passage 23 B includes the straight-line part 23 c perpendicular to the gravity direction, and the refrigerant flows therein through the opening port 23 f formed between the end portion 23 d and the end portion 23 e of the straight-line part 23 c , passes through each of the end portion 23 d and the end portion 23 e , and flows out therefrom through each of the end portions 23 a and 23 b of the flow passage 23 B.
the number of the third plate-shaped members 23 is reduced, and the component cost, the weight, and the like are reduced. Further, the frequency of occurrence of brazing failure is reduced.
the third plate-shaped member 23 (for example, the third plate-shaped member 23 _ 1 ) stacked on the third plate-shaped member 23 having the flow passage 23 B formed therein on the side opposite to the side on which the first plate-shaped unit 11 is present may include a flow passage 23 C for returning the refrigerant flowing therein through the flow passage 23 B to the flow passage 23 A of the third plate-shaped member 23 having the flow passage 23 B formed therein without branching the refrigerant, or may include the flow passage 23 A for returning the refrigerant while branching the refrigerant.
FIG. 23 is a perspective view of Modified Example-4 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
a convex portion 26 may be formed on any one of the plate-shaped member and the both-side clad member 24 , in other words, a surface of any one of the members to be stacked.
the convex portion 26 may be a component such as a spacer.
the member stacked adjacent thereto has a concave portion 27 formed therein, into which the convex portion 26 is inserted.
the concave portion 27 may be or not be a through hole.
the convex portion 26 and the concave portion 27 may be fitted to each other.
a plurality of convex portions 26 and a plurality of concave portions 27 may be formed so that the members to be stacked are positioned through the fitting.
the concave portion 27 may not be formed, and the convex portion 26 may be fit into a part of the flow passage of the member stacked adjacent thereto.
the height, size, and the like of the convex portion 26 may be set to levels that do not inhibit the flow of the refrigerant.
FIG. 24 are a main-part perspective view and a main-part sectional view of Modified Example-5 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 24( a ) is a main-part perspective view under the state in which the stacking-type header is disassembled
FIG. 24( b ) is a sectional view of the first plate-shaped member 21 taken along the line A-A of FIG. 24( a ) .
any one of the plurality of flow passages 21 A formed in the first plate-shaped member 21 may be a tapered through hole having a circular shape at the surface of the first plate-shaped member 21 on the side on which the second plate-shaped unit 12 is present, and having a shape conforming to the outer peripheral surface of the first heat transfer tube 4 at the surface of the first plate-shaped member 21 on the side on which the retaining member 5 is present.
the through hole is shaped to gradually expand in a region from the surface on the side on which the second plate-shaped unit 12 is present to the surface on the side on which the retaining member 5 is present.
FIG. 25 are a main-part perspective view and a main-part sectional view of Modified Example-6 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
FIG. 25( a ) is a main-part perspective view under the state in which the stacking-type header is disassembled
FIG. 25( b ) is a sectional view of the third plate-shaped member 23 taken along the line B-B of FIG. 25( a ) .
any one of the flow passages 23 A formed in the third plate-shaped member 23 may be a bottomed groove.
a circular through hole 23 q is formed at each of an end portion 23 o and an end portion 23 p of a bottom surface of the groove of the flow passage 23 A.
the both-side clad member 24 is not required to be stacked between the plate-shaped members in order to interpose the flow passage 24 A functioning as the refrigerant partitioning flow passage between the branching flow passages 12 b , which improves the production efficiency. Note that, in FIG.
the refrigerant outflow side of the flow passage 23 A is the bottom surface, but the refrigerant inflow side of the flow passage 23 A may be the bottom surface.
a through hole may be formed in a region corresponding to the opening port 23 f.
FIG. 26 are views each illustrating a specific example of the flow passage formed in the third plate-shaped member of Modified Example-6 of the heat exchanger according to Embodiment 1. Note that, FIG. 26( b ) is a sectional view of the third plate-shaped member 23 taken along the line C-C of FIG. 26( a ) .
the flow-passage depth ⁇ 2 of the second flow passage 23 h is smaller than the flow-passage depth ⁇ 1 of the first flow passage 23 g .
the flow-passage resistance in the second flow passage 23 h is larger than the flow-passage resistance in the first flow passage 23 g , thereby suppressing the increase in flow rate of the refrigerant flowing into the second flow passage 23 h due to the influence of the gravity.
Effects of Modified Example-6 are the same as those obtained by changing the horizontal axis of FIG. 9 to ⁇ 1 / ⁇ 2 .
the flow passage 23 A may have a mode similar to those of Specific Example 1 to Specific Example 6. Further, setting the flow-passage depth ⁇ 2 of the second flow passage 23 h smaller than the flow-passage depth ⁇ 1 of the first flow passage 23 g and may be combined with the modes of Specific Example 1 to Specific Example 6.
Setting the flow-passage depth ⁇ 2 of the second flow passage 23 h smaller than the flow-passage depth ⁇ 1 of the first flow passage 23 g may be realized by forming only the first flow passage 23 g into a through groove. Further, the first flow passage 23 g and the second flow passage 23 h may be formed into through grooves, and a member for filling a part of the through groove in a depth direction may be fit only into the second flow passage 23 h . The member may be the convex portion formed on the member stacked adjacent to the third plate-shaped member.
FIG. 27 is a perspective view of Modified Example-7 of the heat exchanger according to Embodiment 1 under a state in which the stacking-type header is disassembled.
the flow passage 22 A functioning as the first inlet flow passage 12 a may be formed in a member to be stacked other than the second plate-shaped member 22 , in other words, a different plate-shaped member, the both-side clad member 24 , or other members.
the flow passage 22 A may be formed as, for example, a through hole passing through the different plate-shaped member from the side surface thereof to the surface on the side on which the second plate-shaped member 22 is present.
the present invention encompasses a configuration in which the first inlet flow passage 12 a is formed in the first plate-shaped unit 11
the “distribution flow passage” of the present invention encompasses distribution flow passages other than the distribution flow passage 12 A in which the first inlet flow passage 12 a is formed in the second plate-shaped unit 12 .
a heat exchanger according to Embodiment 2 is described.
Embodiment 1 Note that, overlapping description or similar description to that of Embodiment 1 is appropriately simplified or omitted.
FIG. 28 is a view illustrating the configuration of the heat exchanger according to Embodiment 2.
the heat exchanger 1 includes the stacking-type header 2 , the plurality of first heat transfer tubes 4 , the retaining member 5 , and the plurality of fins 6 .
the stacking-type header 2 includes the refrigerant inflow port 2 A, the plurality of refrigerant outflow ports 2 B, a plurality of refrigerant inflow ports 2 C, and a refrigerant outflow port 2 D.
the refrigerant pipes are connected to the refrigerant inflow port 2 A of the stacking-type header 2 and the refrigerant outflow port 2 D of the stacking-type header 2 .
the first heat transfer tube 4 is a flat tube subjected to hair-pin bending.
the plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2 B of the stacking-type header 2 and the plurality of refrigerant inflow ports 2 C of the stacking-type header 2 .
the refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2 A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2 B to flow out toward the plurality of first heat transfer tubes 4 .
the refrigerant exchanges heat with air supplied by a fan, for example.
the refrigerant passing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inflow ports 2 C to flow into the stacking-type header 2 to be joined, and then passes through the refrigerant outflow port 2 D to flow out toward the refrigerant pipe.
the refrigerant can reversely flow.
FIG. 29 is a perspective view of the heat exchanger according to Embodiment 2 under a state in which the stacking-type header is disassembled.
FIG. 30 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 2. Note that, in FIG. 30 , the illustration of the both-side clad member 24 is omitted.
the stacking-type header 2 includes the first plate-shaped unit 11 and the second plate-shaped unit 12 .
the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked on each other.
the first plate-shaped unit 11 has the plurality of first outlet flow passages 11 A and a plurality of second inlet flow passages 11 B formed therein.
the plurality of second inlet flow passages 11 B correspond to the plurality of refrigerant inflow ports 2 C in FIG. 28 .
the first plate-shaped member 21 has a plurality of flow passages 21 B formed therein.
the plurality of flow passages 21 B are each a through hole having an inner peripheral surface shaped conforming to an outer peripheral surface of the first heat transfer tube 4 .
the plurality of flow passages 21 B function as the plurality of second inlet flow passages 11 B.
the second plate-shaped unit 12 has the distribution flow passage 12 A and a joining flow passage 12 B formed therein.
the joining flow passage 12 B includes a mixing flow passage 12 c and a second outlet flow passage 12 d .
the second outlet flow passage 12 d corresponds to the refrigerant outflow port 2 D in FIG. 28 .
the second plate-shaped member 22 has a flow passage 22 B formed therein.
the flow passage 22 B is a circular through hole.
the flow passage 22 B functions as the second outlet flow passage 12 d .
a plurality of flow passages 22 B in other words, a plurality of second outlet flow passages 12 d may be formed.
the plurality of third plate-shaped members 23 _ 1 to 23 _ 3 respectively have a plurality of flow passages 23 D_ 1 to 23 D_ 3 formed therein.
the plurality of flow passages 23 D_ 1 to 23 D_ 3 are each a rectangular through hole passing through substantially the entire region in the height direction of the third plate-shaped member 23 .
each of the flow passages 23 D_ 1 to 23 D_ 3 functions as the mixing flow passage 12 c .
the plurality of flow passages 23 D_ 1 to 23 D_ 3 may not have a rectangular shape. In the following, in some cases, the plurality of flow passages 23 D_ 1 to 23 D_ 3 may be collectively referred to as the flow passage 23 D.
both-side clad member 24 having a brazing material rolled on both surfaces thereof between the respective plate-shaped members to supply the brazing material.
the flow passage 24 B formed in the both-side clad member 24 _ 5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having an inner peripheral surface shaped conforming to the outer peripheral surface of the first heat transfer tube 4 .
the flow passage 24 B formed in the both-side clad member 24 _ 4 stacked between the first plate-shaped member 21 and the third plate-shaped member 23 _ 3 is a circular through hole.
the flow passage 24 B formed in other both-side clad members 24 stacked between the third plate-shaped member 23 and the second plate-shaped member 22 is a rectangular through hole passing through substantially the entire region in the height direction of the both-side clad member 24 .
the flow passage 24 B functions as the refrigerant partitioning flow passage for the second inlet flow passage 11 B and the joining flow passage 12 B.
the flow passage 22 B functioning as the second outlet flow passage 12 d may be formed in a different plate-shaped member other than the second plate-shaped member 22 of the second plate-shaped unit 12 , the both-side clad member 24 , or other members.
a notch may be formed, which communicates between a part of the flow passage 23 D or the flow passage 24 B and, for example, a side surface of the different plate-shaped member or the both-side clad member 24 .
the mixing flow passage 12 c may be turned back so that the flow passage 22 B functioning as the second outlet flow passage 12 d is formed in the first plate-shaped member 21 .
the present invention encompasses a configuration in which the second outlet flow passage 12 d is formed in the first plate-shaped unit 11 , and the “joining flow passage” of the present invention encompasses joining flow passages other than the joining flow passage 12 B in which the second outlet flow passage 12 d is formed in the second plate-shaped unit 12 .
the mixed refrigerant passes through the flow passage 22 B of the second plate-shaped member 22 to flow out therefrom toward the refrigerant pipe.
FIG. 31 is a diagram illustrating a 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 the heat source-side heat exchanger 54 or the load-side heat exchanger 56 .
the heat exchanger 1 acts as the evaporator, the heat exchanger 1 is connected so that the refrigerant passes through the distribution flow passage 12 A of the stacking-type header 2 to flow into the first heat transfer tube 4 , and the refrigerant passes through the first heat transfer tube 4 to flow into the joining flow passage 12 B of the stacking-type header 2 .
the heat exchanger 1 acts as the evaporator
the refrigerant in a two-phase gas-liquid state passes through the refrigerant pipe to flow into the distribution flow passage 12 A of the stacking-type header 2
the refrigerant in a gas state passes through the first heat transfer tube 4 to flow into the joining flow passage 12 B of the stacking-type header 2
the heat exchanger 1 acts as the condensor
the refrigerant in a gas state passes through the refrigerant pipe to flow into the joining flow passage 12 B of the stacking-type header 2
the refrigerant in a liquid state passes through the first heat transfer tube 4 to flow into the distribution flow passage 12 A of the stacking-type header 2 .
the first plate-shaped unit 11 has the plurality of second inlet flow passages 11 B formed therein, and the second plate-shaped unit 12 has the joining flow passage 12 B formed therein. Therefore, the header 3 is unnecessary, and thus the component cost and the like of the heat exchanger 1 are reduced. Further, the header 3 is unnecessary, and accordingly, it is possible to extend the first heat transfer tube 4 to increase the number of the fins 6 and the like, in other words, increase the mounting volume of the heat exchanging unit of the heat exchanger 1 .
a heat exchanger according to Embodiment 3 is described.
FIG. 32 is a view illustrating the configuration of the heat exchanger according to Embodiment 3.
the heat exchanger 1 includes the stacking-type header 2 , the plurality of first heat transfer tubes 4 , a plurality of second heat transfer tubes 7 , the retaining member 5 , and the plurality of fins 6 .
the stacking-type header 2 includes a plurality of refrigerant turn-back ports 2 E.
the second heat transfer tube 7 is a flat tube subjected to hair-pin bending.
the plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2 B and the plurality of refrigerant turn-back ports 2 E of the stacking-type header 2
the plurality of second heat transfer tubes 7 are connected between the plurality of refrigerant turn-back ports 2 E and the plurality of refrigerant inflow ports 2 C of the stacking-type header 2 .
the refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2 A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2 B to flow out toward the plurality of first heat transfer tubes 4 .
the refrigerant exchanges heat with air supplied by a fan, for example.
the refrigerant passing through the plurality of first heat transfer tubes 4 flows into the plurality of refrigerant turn-back ports 2 E of the stacking-type header 2 to be turned back, and flows out therefrom toward the plurality of second heat transfer tubes 7 .
the refrigerant exchanges heat with air supplied by a fan, for example.
the flows of the refrigerant passing through the plurality of second heat transfer tubes 7 pass through the plurality of refrigerant inflow ports 2 C to flow into the stacking-type header 2 to be joined, and the joined refrigerant passes through the refrigerant outflow port 2 D to flow out therefrom toward the refrigerant pipe.
the refrigerant can reversely flow.
FIG. 33 is a perspective view of the heat exchanger according to Embodiment 3 under a state in which the stacking-type header is disassembled.
FIG. 34 is a developed view of the stacking-type header of the heat exchanger according to Embodiment 3. Note that, in FIG. 34 , the illustration of the both-side clad member 24 is omitted.
the stacking-type header 2 includes the first plate-shaped unit 11 and the second plate-shaped unit 12 .
the first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked on each other.
the first plate-shaped unit 11 has the plurality of first outlet flow passages 11 A, the plurality of second inlet flow passages 11 B, and a plurality of turn-back flow passages 11 C formed therein.
the plurality of turn-back flow passages 11 C correspond to the plurality of refrigerant turn-back ports 2 E in FIG. 32 .
the first plate-shaped member 21 has a plurality of flow passages 21 C formed therein.
the plurality of flow passages 21 C are each a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the end portion of the first heat transfer tube 4 on the refrigerant outflow side and the outer peripheral surface of the end portion of the second heat transfer tube 7 on the refrigerant inflow side.
the plurality of flow passages 21 C function as the plurality of turn-back flow passages 11 C.
the flow passage 24 C formed in the both-side clad member 24 _ 5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the end portion of the first heat transfer tube 4 on the refrigerant outflow side and the outer peripheral surface of the end portion of the second heat transfer tube 7 on the refrigerant inflow side.
the flow passage 24 C functions as the refrigerant partitioning flow passage for the turn-back flow passage 11 C.
the refrigerant flowing out from the flow passage 21 A of the first plate-shaped member 21 to pass through the first heat transfer tube 4 flows into the flow passage 21 C of the first plate-shaped member 21 to be turned back and flow into the second heat transfer tube 7 .
the refrigerant passing through the second heat transfer tube 7 flows into the flow passage 21 B of the first plate-shaped member 21 .
the refrigerant flowing into the flow passage 21 B of the first plate-shaped member 21 flows into the flow passage 23 D formed in the third plate-shaped member 23 to be mixed.
the mixed refrigerant passes through the flow passage 22 B of the second plate-shaped member 22 to flow out therefrom toward the refrigerant pipe.
FIG. 35 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 3 is applied.
the heat exchanger 1 is used for at least one of the heat source-side heat exchanger 54 or the load-side heat exchanger 56 .
the heat exchanger 1 acts as the evaporator, the heat exchanger 1 is connected so that the refrigerant passes through the distribution flow passage 12 A of the stacking-type header 2 to flow into the first heat transfer tube 4 , and the refrigerant passes through the second heat transfer tube 7 to flow into the joining flow passage 12 B of the stacking-type header 2 .
the heat exchanger 1 acts as the evaporator
the refrigerant in a two-phase gas-liquid state passes through the refrigerant pipe to flow into the distribution flow passage 12 A of the stacking-type header 2
the refrigerant in a gas state passes through the second heat transfer tube 7 to flow into the joining flow passage 12 B of the stacking-type header 2
the heat exchanger 1 acts as the condensor
the refrigerant in a gas state passes through the refrigerant pipe to flow into the joining flow passage 12 B of the stacking-type header 2
the refrigerant in a liquid state passes through the first heat transfer tube 4 to flow into the distribution flow passage 12 A of the stacking-type header 2 .
the heat exchanger 1 acts as the condensor
the heat exchanger 1 is arranged so that the first heat transfer tube 4 is positioned on the upstream side (windward side) of the air stream generated by the heat source-side fan 57 or the load-side fan 58 with respect to the second heat transfer tube 7 .
the refrigerant of the first heat transfer tube 4 is lower in temperature than the refrigerant of the second heat transfer tube 7 .
the air stream generated by the heat source-side fan 57 or the load-side fan 58 is lower in temperature on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1 .
the refrigerant can be subcooled (so-called subcooling) by the low-temperature air stream flowing on the upstream side of the heat exchanger 1 , which improves the condensor performance.
the heat source-side fan 57 and the load-side fan 58 may be arranged on the windward side or the leeward side.
the first plate-shaped unit 11 has the plurality of turn-back flow passages 11 C formed therein, and in addition to the plurality of first heat transfer tubes 4 , the plurality of second heat transfer tubes 7 are connected.
the housing that incorporates the heat exchanger 1 is upsized.
the heat exchange amount can be increased without changing the area in the state of the front view of the heat exchanger 1 , the interval between the fins 6 , or other matters.
the heat exchange amount is increased about 1.5 times or more.
the number of rows of the heat transfer tubes may be three or more. Still further, the area in the state of the front view of the heat exchanger 1 , the interval between the fins 6 , or other matters may be changed.
the header (stacking-type header 2 ) is arranged only on one side of the heat exchanger 1 .
the end portion may be misaligned in each row of the heat transfer tubes because the curvature radius of the bent part differs depending on each row of the heat transfer tubes.
the header (stacking-type header 2 ) is arranged only on one side of the heat exchanger 1 , even when the end portion is misaligned in each row of the heat transfer tubes, only the end portions on one side are required to be aligned, which improves the degree of freedom in design, the production efficiency, and other matters as compared to the case where the headers (stacking-type header 2 and header 3 ) are arranged on both sides of the heat exchanger 1 as in the heat exchanger according to Embodiment 1.
the heat exchanger 1 can be bent after the respective members of the heat exchanger 1 are joined to each other, which further improves the production efficiency.
the first heat transfer tube 4 is positioned on the windward side with respect to the second heat transfer tube 7 .
the headers stacking-type header 2 and header 3
the first heat transfer tube 4 and the second heat transfer tube 7 are flat tubes, unlike a circular tube, the degree of freedom in bending is low, and hence it is difficult to realize providing the temperature difference in the refrigerant for each row of the heat transfer tubes by deforming the flow passage of the refrigerant.

Landscapes

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

US14/786,595 2013-05-15 2013-05-15 Stacking-type header, heat exchanger, and air-conditioning apparatus Abandoned US20160116231A1 (en)

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
PCT/JP2013/063606 WO2014184914A1 (ja)	2013-05-15	2013-05-15	積層型ヘッダー、熱交換器、及び、空気調和装置

Related Parent Applications (1)

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PCT/JP2013/063606 A-371-Of-International WO2014184914A1 (ja)	2013-05-15	2013-05-15	積層型ヘッダー、熱交換器、及び、空気調和装置

Related Child Applications (1)

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US15/941,412 Division US10571205B2 (en)	2013-05-15	2018-03-30	Stacking-type header, heat exchanger, and air-conditioning apparatus

Publications (1)

Publication Number	Publication Date
US20160116231A1 true US20160116231A1 (en)	2016-04-28

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ID=51380231

Family Applications (2)

Application Number	Title	Priority Date	Filing Date
US14/786,595 Abandoned US20160116231A1 (en)	2013-05-15	2013-05-15	Stacking-type header, heat exchanger, and air-conditioning apparatus
US15/941,412 Active 2033-08-07 US10571205B2 (en)	2013-05-15	2018-03-30	Stacking-type header, heat exchanger, and air-conditioning apparatus

Family Applications After (1)

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US15/941,412 Active 2033-08-07 US10571205B2 (en)	2013-05-15	2018-03-30	Stacking-type header, heat exchanger, and air-conditioning apparatus

Country Status (5)

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US (2)	US20160116231A1 (ja)
EP (1)	EP3018441B1 (ja)
JP (1)	JP6177319B2 (ja)
CN (2)	CN105229405B (ja)
WO (1)	WO2014184914A1 (ja)

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CN110118505A (zh) *	2019-06-19	2019-08-13	浙江银轮机械股份有限公司	集流管组件及热交换器
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JP7631509B2 (ja) *	2021-04-27	2025-02-18	日本キヤリア株式会社	熱交換器および冷凍サイクル装置
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EP4163572A4 (en) *	2020-06-05	2023-07-05	Mitsubishi Electric Corporation	REFRIGERANT DISPENSER, HEAT EXCHANGER, AND AIR CONDITIONING DEVICE
US12209780B2 (en)	2020-10-21	2025-01-28	Mitsubishi Electric Corporation	Distributor, heat exchanger and air conditioner

Also Published As

Publication number	Publication date
CN105229405A (zh)	2016-01-06
JP6177319B2 (ja)	2017-08-09
EP3018441A1 (en)	2016-05-11
US10571205B2 (en)	2020-02-25
CN203798026U (zh)	2014-08-27
EP3018441B1 (en)	2019-07-24
WO2014184914A1 (ja)	2014-11-20
JPWO2014184914A1 (ja)	2017-02-23
EP3018441A4 (en)	2017-07-26
US20180224220A1 (en)	2018-08-09
CN105229405B (zh)	2017-05-17

Legal Events

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Title

Description

2015-10-23

AS

Assignment

Owner name: MITSUBISHI ELECTRIC CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HIGASHIIUE, SHINYA;OKAZAKI, TAKASHI;ISHIBASHI, AKIRA;AND OTHERS;SIGNING DATES FROM 20150907 TO 20150909;REEL/FRAME:036865/0090

2018-08-13

STCB

Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION

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