WO2015097876A1 - Collecteur empilé, échangeur de chaleur et climatiseur - Google Patents

Collecteur empilé, échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2015097876A1
WO2015097876A1 PCT/JP2013/085150 JP2013085150W WO2015097876A1 WO 2015097876 A1 WO2015097876 A1 WO 2015097876A1 JP 2013085150 W JP2013085150 W JP 2013085150W WO 2015097876 A1 WO2015097876 A1 WO 2015097876A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
flow path
refrigerant
plate
opening
Prior art date
Application number
PCT/JP2013/085150
Other languages
English (en)
Japanese (ja)
Inventor
繁佳 松井
真哉 東井上
岡崎　多佳志
石橋　晃
厚志 望月
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP13900071.5A priority Critical patent/EP3088831B1/fr
Priority to JP2015554455A priority patent/JP6080982B2/ja
Priority to PCT/JP2013/085150 priority patent/WO2015097876A1/fr
Publication of WO2015097876A1 publication Critical patent/WO2015097876A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to a laminated header, a heat exchanger, and an air conditioner.
  • a conventional heat exchanger includes a tube bonding member that bonds a flat tube and a member, a tube fixing member that aligns the end of the flat tube, a spacer portion, and a back plate.
  • coolant merge space to move is formed is known (for example, refer patent document 1).
  • the ratio (distribution ratio) of the gas-phase refrigerant and the liquid-phase refrigerant flowing into the plurality of flow paths inside the pipe can be adjusted as appropriate. It is rare. For example, in a heat exchanger that exchanges heat between the air passing through the heat exchanger and the refrigerant in the pipe, the heat load (heat exchange amount) on the windward side is larger than that on the leeward side. It is desired to adjust the distribution rate so that the amount of latent heat of the flowing refrigerant increases.
  • the present invention has been made against the background of the above problems.
  • a laminated header that is connected to a plurality of pipes and flows a fluid flowing from one pipe into another pipe, the fluid flowing into the pipe is obtained.
  • An object is to obtain a laminated header capable of reducing the bias.
  • an object of this invention is to obtain the heat exchanger provided with such a laminated header.
  • an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.
  • a multilayer header according to the present invention is a multilayer header that is connected to a plurality of pipes and allows a fluid flowing from one pipe to flow into another pipe, and includes a first opening to which the pipe is connected.
  • a second plate having a first plate-like body and a second opening, wherein the second opening is stacked on the first plate-like body so as to communicate with the first opening.
  • a straddle channel is formed to communicate the channel and the channel corresponding to the other pipe, and the channel area of the channel in the second opening is greater than the channel area of the first opening. Is also small.
  • a heat exchanger includes the laminated header and a plurality of pipes connected to the laminated header, and the plurality of pipes are provided with a plurality of flow paths therein. .
  • the air conditioner according to the present invention includes the above heat exchanger.
  • the present invention can reduce unevenness of fluid flowing into a pipe in a stacked header that is connected to a plurality of pipes and allows a fluid flowing from one pipe to flow into another pipe. Further, according to the present invention, the distribution ratio of the fluid flowing into the pipe from the laminated header can be adjusted relatively easily.
  • FIG. 1 is a side view showing a schematic configuration of a heat exchanger 1 according to Embodiment 1.
  • FIG. 1 is a top view showing a schematic configuration of a heat exchanger 1 according to Embodiment 1.
  • FIG. 3 is a schematic configuration diagram illustrating a cross section of a first heat transfer tube 4 and a second heat transfer tube 7 of the heat exchanger 1 according to Embodiment 1.
  • FIG. It is a perspective view in the state which decomposed
  • FIG. 3 is a schematic cross-sectional view of a stacked header 2 of the heat exchanger 1 according to Embodiment 1.
  • FIG. 3 is a schematic cross-sectional view for explaining a refrigerant flow in the stacked header 2 of the heat exchanger 1 according to Embodiment 1. It is II sectional drawing of FIG. It is II-II sectional drawing of FIG.
  • FIG. 7 is a cross-sectional view taken along the line III-III in FIG. 6.
  • 4 is a schematic cross-sectional view of a stacked header 2 of a heat exchanger 1 according to Embodiment 2.
  • FIG. It is a schematic sectional drawing explaining the flow of the refrigerant
  • FIG. It is II sectional drawing of FIG. FIG. 12 is a sectional view taken along the line II-II in FIG. 11.
  • FIG. 13 is a sectional view taken along the line III-III in FIG. 11. It is a figure which shows the structure of the air conditioning apparatus to which the heat exchanger 1 which concerns on Embodiment 2 is applied. It is a figure explaining the liquid quantity distribution of the refrigerant
  • the laminated header according to the present invention will be described with reference to the drawings.
  • the laminated header according to the present invention distributes the refrigerant flowing into the flat tube which is the heat transfer tube of the heat exchanger.
  • the laminated header according to the present invention is The refrigerant flowing into other devices may be distributed.
  • the configuration, operation, and the like described below are merely examples, and the configuration, operation, and the like are not limited thereto.
  • symbol is attached
  • symbol is abbreviate
  • the illustration of the fine structure is simplified or omitted as appropriate.
  • overlapping or similar descriptions are appropriately simplified or omitted.
  • FIG. 1 is a side view showing a schematic configuration of a heat exchanger 1 according to the first embodiment.
  • FIG. 2 is a top view showing a schematic configuration of the heat exchanger 1 according to the first embodiment.
  • the heat exchanger 1 includes a stacked header 2, a plurality of first heat transfer tubes 4, a holding member 5, a plurality of fins 6, and a plurality of second heat transfer tubes 7. And have.
  • the laminated header 2 includes at least one first inlet channel 2A, a plurality of first outlet channels 2B, a plurality of second inlet channels 2C, a second outlet channel 2D, and a first heat transfer tube 4. And a folded flow path 2E for folding the refrigerant that has passed through the second heat transfer tube 7.
  • a refrigerant pipe is connected to the first inlet channel 2A and the second outlet channel 2D of the stacked header 2.
  • a plurality of first heat transfer tubes 4 are connected between the plurality of first outlet channels 2B and the folded channel 2E of the laminated header 2, and between the folded channel 2E and the plurality of second inlet channels 2C.
  • a plurality of second heat transfer tubes 7 are connected.
  • the fins 6 have, for example, a plate shape, and are laminated at a predetermined interval, and a heat medium (for example, air) circulates between the fins 6.
  • the fin 6 is comprised with metal materials, such as aluminum and copper, for example.
  • the fin 6 is made of, for example, aluminum.
  • the first heat transfer tube 4 and the second heat transfer tube 7 are flat tubes that are subjected to, for example, hairpin bending on the end side opposite to the stacked header 2 of the heat exchanger 1.
  • the 1st heat exchanger tube 4 and the 2nd heat exchanger tube 7 are constituted by metal materials, such as aluminum and copper, for example.
  • the ends of the first heat transfer tube 4 and the second heat transfer tube 7 on the laminated header 2 side are held by a plate-like holding member 5 and connected to the plurality of first outlet channels 2B of the laminated header 2.
  • the first heat transfer tube 4 and the second heat transfer tube 7 are arranged in a plurality of stages in the step direction intersecting the air flow direction.
  • the first heat transfer tubes 4 and the second heat transfer tubes 7 are arranged in a row in a row direction along the air flow direction.
  • a plurality of the first heat transfer tubes 4 and the second heat transfer tubes 7 are arranged with the direction of the long axis of the flat shape facing the air flow direction (column direction) and the direction of the short axis of the flat shape (step direction) spaced apart.
  • the 1st heat exchanger tube 4 is alternately arranged with the 2nd heat exchanger tube 7 of the row
  • FIG. 3 is a schematic configuration diagram illustrating a cross section of the first heat transfer tube 4 and the second heat transfer tube 7 of the heat exchanger 1 according to the first embodiment.
  • at least one partition is provided inside the first heat transfer tube 4 and the second heat transfer tube 7, and a plurality of flow paths 30 are formed.
  • the first heat transfer tube 4 and the second heat transfer tube 7 correspond to “piping” in the present invention.
  • this invention is not limited to this, Piping of arbitrary shapes, such as a circular tube and a square tube, can be used.
  • the refrigerant that has passed through the plurality of first heat transfer tubes 4 flows again into the stacked header 2 from the second inlet flow path 2C, joins, and flows out to the refrigerant piping via the second outlet flow path 2D.
  • the refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 4 and the plurality of second heat transfer tubes 7.
  • the refrigerant can flow backward.
  • FIG. 4 is a perspective view of the heat exchanger 1 according to Embodiment 1 with the stacked header 2 disassembled.
  • the laminated header 2 includes a first plate 11, a second plate 12, a third plate 13, a fourth plate 14, and a fifth plate. And a body 15.
  • the first plate-like body 11 includes a holding member 5, a clad material 26_1, and a first plate-like member 21.
  • the second plate-like body 12 has a clad material 26_2.
  • the third plate-like body 13 includes a third plate-like member 23 and a clad material 26_3.
  • the fourth plate-like body 14 includes a plurality of fourth plate-like members 24_1 to 24_3 and a plurality of clad materials 26_4 to 26_5.
  • the fifth plate-like body 15 includes a fifth plate-like member 25 and a clad material 26_6.
  • a brazing material is applied to both surfaces or one surface of the cladding materials 26_1 to 26_6.
  • the first plate-like member 21 is stacked on the holding member 5 via the clad material 26_1.
  • the third plate-like member 23 is laminated on the first plate-like member 21 via the clad material 26_2.
  • the plurality of fourth plate-like members 24_1 to 24_3 are stacked on the third plate-like member 23 via the clad materials 26_3 to 26_4.
  • the fifth plate-like member 25 is laminated on the fourth plate-like member 24_3 via the clad material 26_6.
  • the first plate member 21, the third plate member 23, the plurality of fourth plate members 24_1 to 24_3, and the fifth plate member 25 are, for example, about 1 to 10 mm in thickness and are made of aluminum. is there.
  • the fourth plate members 24_1 to 24_3 may be collectively referred to as the fourth plate member 24 in some cases.
  • the cladding materials 26_1 to 26_6 may be collectively referred to as the cladding material 26 in some cases.
  • a plurality of first outlet channels 2B in FIG. 1 are formed by the channel 21B formed in the first plate member 21 and the channel 26B formed in the cladding material 26_1.
  • the flow path 21 ⁇ / b> B and the flow path 26 ⁇ / b> B are through holes having an inner peripheral surface along the outer peripheral surface of the first heat transfer tube 4.
  • the end of the first heat transfer tube 4 is joined and held to the holding member 5 by brazing.
  • the edge part of the 1st heat exchanger tube 4 and the 1st exit flow path 2B will be connected.
  • the holding member 5 is not provided, and the first outlet channel 2B and the first heat transfer tube 4 may be joined. In such a case, parts costs and the like are reduced.
  • a plurality of folded flow paths 2E in FIG. 1 are formed by the side surfaces. End portions of the first heat transfer tube 4 and the second heat transfer tube 7 connected to the folded flow path 2E are joined and held to the holding member 5 by brazing. When the first heat transfer tube 4 and the second heat transfer tube 7 and the holding member 5 are joined, the ends of the first heat transfer tube 4 and the second heat transfer tube 7 and the folded flow path 2E are connected.
  • FIG. 5 is a schematic cross-sectional view of the stacked header 2 of the heat exchanger 1 according to the first embodiment.
  • the cross section of the main part of the multilayer header 2 is shown enlarged.
  • the clad material 26_2 is laminated on the first plate-like member 21, and the flow paths 26E_1 and 26E_2 of the clad material 26_2 and the flow paths 21E_1 and 21E_2 of the first plate-like member 21 communicate with each other.
  • the end portions of the first heat transfer tube 4 and the second heat transfer tube 7 are spaced from the clad material 26_2, and the flow paths 21E_1 and 21E_2 of the first plate member 21 are open spaces.
  • the flow path 23E formed in the third plate member 23 is formed by one opening having a size including the two flow paths 26E_1 and 26E_2 formed in the clad material 26_2.
  • the cladding material 26_3 is not provided with an opening in a portion facing the flow path 23E.
  • the third plate-like member 23 and the clad material 26_3 are laminated on the clad material 26_2, thereby forming a row flow path that communicates between the two flow paths 26E_1 and 26E_2 formed in the clad material 26_2. Yes.
  • the channel area (opening cross-sectional area) of the channel 26E_1 formed in the clad material 26_2 is smaller than the channel area of the channel 21E_1 formed in the first plate member 21. Further, the channel area (open sectional area) of the channel 26E_2 formed in the clad material 26_2 is smaller than the channel area of the channel 21E_2 formed in the first plate member 21. Further, the flow path area of the flow path 26E_1 formed in the clad material 26_2 is smaller than the flow path area of the first heat transfer tube 4. Further, the flow path area of the flow path 26E_2 formed in the clad material 26_2 is formed to be smaller than the flow path area of the second heat transfer tube 7.
  • a flow path cross section V1 of the flow path 26E_1 formed in the cladding material 26_2 is orthogonal to the central axis C1 of the first heat transfer tube 4. That is, the channel cross section V1 of the channel 26E_1 is formed to be parallel to the channel cross section of the first heat transfer tube 4. Further, the flow path cross section V2 of the flow path 26E_2 formed in the clad material 26_2 is orthogonal to the central axis C2 of the first heat transfer tube 4. That is, the channel cross section V2 of the channel 26E_2 is formed to be parallel to the channel cross section of the second heat transfer tube 7.
  • the flow paths 26E_1 and 26E_2 formed in the clad material 26_2 have, for example, a circular shape.
  • the shape of the flow paths 26E_1 and 26E_2 is not limited to a circular shape, and may be an arbitrary shape. For example, you may have the flat shape whose major axis direction is the same as the 1st heat exchanger tube 4 and the 2nd heat exchanger tube 7.
  • the width in the major axis direction of the flow paths 26E_1 and 26E_2 is made shorter than the width in the major axis direction of the first heat transfer tube 4 and the second heat transfer tube 7.
  • the shape of the flow path 21 ⁇ / b> E_ 1 formed in the first plate-like member 21 may be any shape as long as it includes the outer shape of the first heat transfer tube 4 in a cross-sectional view.
  • the shape of the flow path 21E_2 may be any shape as long as it includes the outer shape of the second heat transfer tube 7 in a cross-sectional view.
  • the flow paths 21 ⁇ / b> E_ ⁇ b> 1 and 21 ⁇ / b> E_ ⁇ b> 2 have a flat shape, and at least one of the width in the long axis direction and the width in the short axis direction is formed larger than the first heat transfer tube 4 and the second heat transfer tube 7.
  • the first plate member 21, the clad material 26_1, and the holding member 5 correspond to the “first plate body” in the present invention.
  • the clad material 26_2 corresponds to the “second plate-like body” in the present invention.
  • the third plate-like member 23 and the clad material 26_3 correspond to the “third plate-like body” in the present invention.
  • the flow paths 21E_1 and 21E_2 formed in the first plate member 21 correspond to the “first opening” in the present invention.
  • the flow paths 26E_1 and 26E_2 formed in the clad material 26_2 correspond to the “second opening” in the present invention.
  • the flow path 23E formed in the third plate-like member 23 corresponds to the “strand flow path” in the present invention.
  • a branch channel is formed by the channel 24 A formed in the fourth plate-like member 24.
  • the flow path 24A is a linear through groove.
  • the branch channel distributes the refrigerant flowing from the first inlet channel 2A to the plurality of first outlet channels 2B by repeating two branches a plurality of times.
  • a merging channel is formed by the channel 24 ⁇ / b> B formed in the fourth plate-like member 24.
  • the flow path 24B is a linear through groove.
  • the merging channel merges the refrigerant that has flowed in from the second inlet channel 2C and flows it out to the second outlet channel 2D.
  • the first inlet channel 2A in FIG. 1 is formed by the channel 25A formed in the fifth plate member 25 and the channel 25A formed in the clad material 26_6.
  • the first inlet channel 2A is, for example, a circular through hole.
  • the second outlet flow channel 2D in FIG. 1 is formed by the flow channel 25D formed in the fifth plate member 25 and the 25D formed in the clad material 26_6.
  • the second outlet channel 2D is, for example, a circular through hole.
  • the refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of first heat transfer tubes 4 and the second heat transfer tubes 7.
  • the refrigerant can flow backward.
  • FIG. 6 is a schematic cross-sectional view illustrating the refrigerant flow in the stacked header 2 of the heat exchanger 1 according to the first embodiment.
  • the cross section of the principal part of the laminated header 2 is expanded and shown.
  • 7 is a cross-sectional view taken along the line II of FIG. 8 is a cross-sectional view taken along the line II-II in FIG. 9 is a cross-sectional view taken along the line III-III in FIG.
  • the arrows shown in FIGS. 7 to 9 indicate the direction in which the refrigerant flows.
  • a case where the refrigerant flows from the first heat transfer tube 4 to the laminated header 2 and the refrigerant flows from the laminated header 2 to the second heat transfer tube 7 will be described as an example.
  • the refrigerant flowing through the first heat transfer tube 4 flows from the end of the first heat transfer tube 4 into the flow path 21E_1 of the first plate-like member 21.
  • the refrigerant flowing through the open space of the flow path 21E_1 is contracted by the flow path 26E_1 of the clad material 26_2, and flows out to the flow path 23E formed in the third plate-like member 23.
  • the refrigerant flowing through the flow path 23E moves to the second heat transfer tube 7 side, is contracted by the flow path 26E_2 of the clad material 26_2, and flows into the flow path 21E_2 of the first plate member 21.
  • the refrigerant that has flowed out from the flow path 26E_2 of the clad material 26_2 to the flow path 21E_2 of the first plate-like member 21 spreads and flows through the open space of the flow path 21E_2.
  • the refrigerant is evenly distributed to 30.
  • coolant is not limited to the said description, You may flow in the reverse direction.
  • FIG. 22 is a diagram showing a folded channel in a conventional laminated header.
  • the flow paths 21E_1 and 21E_2 of the first plate-like member 21 and the flow paths 26E_1 and 26E_2 of the clad material 26_2 are not provided.
  • the liquid is biased to the wall surface in the flow direction due to the inertial force, and a plurality of flows formed in the first heat transfer tube 4 and the second heat transfer tube 7 are formed.
  • the refrigerant flowing into the passage 30 is biased in the flow direction, and the refrigerant cannot be evenly distributed.
  • the stacked header 2 of the heat exchanger 1 includes the flow paths 21E_1 and 21E_2 of the first plate member 21 and the flow paths 26E_1 and 26E_2 of the clad material 26_2, and the flow paths 26E_1 and 26E_1,
  • the channel area (opening cross-sectional area) of 26E_2 is smaller than the channel areas of the channels 21E_1 and 21E_2. For this reason, the bias
  • the bias of the liquid phase refrigerant in the flow paths 21E_1 and 21E_2 of the first plate-like member 21 can be suppressed, and the first heat transfer tube 4. It is possible to suppress an uneven distribution rate of the plurality of flow paths 30 formed in the second heat transfer tube 7.
  • the channel cross section V1 of the channel 26E_1 formed in the clad material 26_2 is orthogonal to the central axis C1 of the first heat transfer tube 4.
  • the flow path cross section V2 of the flow path 26E_2 formed in the clad material 26_2 is orthogonal to the central axis C2 of the first heat transfer tube 4.
  • Embodiment 2 the stacked header 2 of the heat exchanger 1 according to the second embodiment will be described focusing on differences from the first embodiment.
  • symbol is attached
  • FIG. 1 the same code
  • symbol is attached
  • FIG. 10 is a schematic cross-sectional view of the stacked header 2 of the heat exchanger 1 according to the second embodiment.
  • the cross section of the principal part of the laminated header 2 is expanded and shown.
  • the central axis of the flow path 21E_1 of the first plate member 21 and the central axis of the flow path 26E_1 of the clad material 26_2 are eccentric to each other. Yes.
  • the central axis of the flow path 21E_2 of the first plate-like member 21 and the central axis of the flow path 26E_2 of the clad material 26_2 are decentered from each other. That is, the central axis of the flow path 26E_1 corresponding to the first heat transfer tube 4 is eccentric to the second heat transfer pipe 7 side with respect to the central axis of the flow path 21E_1, and the center of the flow path 26E_2 corresponding to the second heat transfer pipe 7 The axis is eccentric to the first heat transfer tube 4 side with respect to the central axis of the flow path 21E_2.
  • the amount of eccentricity Z is 0 ⁇ Z ⁇ W3 / 2, where W3 is the outer diameter of the first heat transfer tube 4 and the second heat transfer tube 7 in the major axis direction.
  • the distance between the central axis of the flow path 26 ⁇ / b> E_ 1 corresponding to the first heat transfer tube 4 and the central axis of the first heat transfer tube 4 corresponds to the central axis of the second heat transfer tube 7 and the first heat transfer tube 4. Is eccentric so as to be shorter than the distance from the central axis of the flow path 26E_1. Further, the distance between the center axis of the flow path 26 ⁇ / b> E_ 2 corresponding to the second heat transfer tube 7 and the center axis of the second heat transfer tube 7 corresponds to the center axis of the first heat transfer tube 4 and the second heat transfer tube 7. Is eccentric so as to be shorter than the distance from the central axis of the flow path 26E_1.
  • FIG. 11 is a schematic cross-sectional view illustrating the flow of refrigerant in the stacked header 2 of the heat exchanger 1 according to the second embodiment.
  • the cross section of the principal part of the laminated header 2 is expanded and shown.
  • 12 is a cross-sectional view taken along the line II of FIG. 13 is a cross-sectional view taken along the line II-II in FIG. 14 is a cross-sectional view taken along the line III-III in FIG. Note that the arrows shown in FIGS. 11 to 14 indicate the direction in which the refrigerant flows.
  • the case where the gas-liquid two-phase refrigerant flows from the first heat transfer tube 4 to the laminated header 2 and the gas-liquid two-phase refrigerant flows from the laminated header 2 to the second heat transfer tube 7 is taken as an example. explain.
  • the refrigerant flowing through the first heat transfer tube 4 flows from the end of the first heat transfer tube 4 into the flow path 21E_1 of the first plate-like member 21.
  • the refrigerant flowing through the open space of the flow path 21E_1 is contracted by the flow path 26E_1 eccentric to the second heat transfer tube 7 side, and flows out to the flow path 23E formed in the third plate member 23.
  • the refrigerant in the gas-liquid two-phase state passing through the flow path 23E is affected by the inertial force, so that the refrigerant having a high density flows outside and the refrigerant having a low density flows inside.
  • the refrigerant flowing through the flow path 23E moves to the second heat transfer tube 7 side, is contracted by the flow path 26E_2 of the clad material 26_2, and flows into the flow path 21E_2 eccentric to the first heat transfer tube 4 side.
  • the liquid refrigerant that has flowed out from the flow path 26E_2 of the clad material 26_2 to the flow path 21E_2 of the first plate-like member 21 is the first in the open space of the flow path 21E_2 to which the end of the second heat transfer tube 7 is connected. 1 Circulates a lot on the heat transfer tube 4 side.
  • the distribution direction of the refrigerant is not limited to the above description, and may flow in the reverse direction.
  • the ratio (distribution ratio) of the gas-phase refrigerant and the liquid-phase refrigerant flowing into the plurality of flow paths 30 inside the first heat transfer tube 4 is adjusted by adjusting the eccentric amount Z. It is possible to adjust as appropriate.
  • FIG. 15 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger 1 according to Embodiment 2 is applied.
  • the air conditioner includes a compressor 71, a four-way valve 72, an outdoor heat exchanger (heat source side heat exchanger) 73, a throttling device 74, and an indoor heat exchanger (load side heat).
  • an outdoor fan (heat source side fan) 76 and an indoor fan (load side fan) 77 is an outdoor fan (heat source side fan) 76 and an indoor fan (load side fan) 77.
  • the compressor 71, the four-way valve 72, the outdoor heat exchanger 73, the expansion device 74, and the indoor heat exchanger 75 are connected by a refrigerant pipe to form a refrigerant circulation circuit. By switching the flow path of the four-way valve 72, the cooling operation and the heating operation are switched.
  • the flow of the refrigerant during the cooling operation will be described.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 71 flows into the outdoor heat exchanger 73 through the four-way valve 72, exchanges heat with the air supplied by the outdoor fan 76, and condenses.
  • the condensed refrigerant enters a high-pressure liquid state, flows out of the outdoor heat exchanger 73, and enters a low-pressure gas-liquid two-phase state by the expansion device 74.
  • the low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 75 and evaporates by heat exchange with the air supplied by the indoor fan 77, thereby cooling the room.
  • the evaporated refrigerant enters a low-pressure gas state, flows out of the indoor heat exchanger 75, and is sucked into the compressor 71 through the four-way valve 72.
  • the flow of the refrigerant during the heating operation will be described.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 71 flows into the indoor heat exchanger 75 via the four-way valve 72 and condenses by heat exchange with the air supplied by the indoor fan 77, Heat up.
  • the condensed refrigerant enters a high-pressure liquid state, flows out of the indoor heat exchanger 75, and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 74.
  • the low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 73, exchanges heat with the air supplied by the outdoor fan 76, and evaporates.
  • the evaporated refrigerant enters a low-pressure gas state, flows out of the outdoor heat exchanger 73, and is sucked into the compressor 71 through the four-way valve 72.
  • the heat exchanger 1 is used for at least one of the outdoor heat exchanger 73 and the indoor heat exchanger 75.
  • the heat exchanger 1 acts as an evaporator
  • the heat exchanger 1 is connected so that the refrigerant flows in from the first inlet channel 2A of the stacked header 2 and flows out from the second outlet channel 2D. That is, when the heat exchanger 1 acts as an evaporator, the gas-liquid two-phase refrigerant flows into the laminated header 2 from the refrigerant pipe. Further, when the heat exchanger 1 acts as a condenser, the refrigerant flows back through the stacked header 2.
  • the refrigerant passes through the first heat transfer tubes 4 arranged in the windward row, passes through the folded flow path 2E of the laminated header 2, and is on the leeward side. It flows into the 2nd heat exchanger tube 7 arranged in this row.
  • the heat exchanger 1 acts as a condenser
  • the refrigerant passes through the second heat transfer tubes 7 arranged in the leeward row, passes through the folded flow path 2E of the laminated header 2, and then goes upwind. It flows into the 2nd heat exchanger tube 7 arranged in this row.
  • FIGS. 16 and 17 are diagrams for explaining the liquid amount distribution of the refrigerant flowing into the second heat transfer tube 7 when the heat exchanger 1 according to Embodiment 2 of the present invention functions as an evaporator.
  • FIG. 18 is a diagram showing temperature changes of air and refrigerant when the heat exchanger 1 according to Embodiment 2 acts as an evaporator.
  • the refrigerant when the heat exchanger 1 acts as an evaporator, the refrigerant is in parallel with the air flow generated by driving the outdoor fan 76. That is, it flows from the first heat transfer tube 4 to the flow path 26E_1 and flows from the flow path 23E to the flow path 26E_2 in a gas-liquid two-phase state.
  • FIG. 19 is a diagram for explaining the liquid amount distribution of the refrigerant flowing into the first heat transfer tube 4 when the heat exchanger 1 according to Embodiment 2 acts as a condenser.
  • FIG. 20 is a diagram for explaining the liquid amount distribution of the refrigerant flowing into the first heat transfer tube 4 when the heat exchanger 1 according to Embodiment 2 acts as a condenser.
  • FIG. 21 is a diagram showing temperature changes of air and refrigerant when the heat exchanger 1 according to Embodiment 2 acts as a condenser.
  • the refrigerant becomes a counterflow with the air flow generated by driving the outdoor fan 76. That is, it flows from the second heat transfer tube 7 to the flow path 26E_2 and flows from the flow path 23E to the flow path 26E_1 in a gas-liquid two-phase state.
  • the heat exchanger 1 since the eccentric amount Z is Z> 0 in the flow path 26E_1, a large amount of gas refrigerant flowing into the flow path 26E_1 flows into the S point side of the first heat transfer tube 4. It becomes. Moreover, as shown in FIG. 21, when the heat exchanger 1 acts as a condenser, the temperature difference between the air passing through the heat exchanger 1 and the refrigerant increases toward the windward side. In other words, since the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 76 is large, a large amount of gas refrigerant flows through the two points on the first heat transfer tube 4, that is, the flow path on the windward side. Moreover, by being distributed to the plurality of flow paths 30 of the first heat transfer tube 4, the condensation of the gas refrigerant is promoted, and the heat exchange efficiency is improved.
  • the case where the flow paths 26E_1 and 26E_2 are decentered is described based on the relationship between the flow direction of the refrigerant in the gas-liquid two-phase state and the direction of the air flow.
  • the present invention is not limited to this.
  • the distribution ratio of the fluid flowing from the laminated header 2 into the first heat transfer tube 4 and the second heat transfer tube 7 can be adjusted as appropriate.
  • the stacked header 2 can be used in various situations and environments.
  • the folded flow path 2E is formed in the flow paths 21E_1 and 21E_2 formed in the first plate member 21, the first outlet flow path 2B formed in the clad material 26_2, and the third plate member 23. Since it is formed by the flow path 23E, the adjustment of the amount of eccentricity and the direction of eccentricity described above can be realized without complicating the structure, and parts costs, manufacturing processes, and the like are reduced.

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

Abstract

L'invention concerne un collecteur empilé qui comprend un premier élément de plaque (21) ayant un trajet d'écoulement (21E_1, 21E_2), un matériau de gainage (26_2), dans lequel est formé un trajet d'écoulement (26E_1, 26E_2), et un troisième élément de plaque (23). Un trajet d'écoulement (23E), au moyen duquel un trajet d'écoulement correspondant à l'un de deux d'une pluralité de tuyaux communique avec un trajet d'écoulement correspondant à l'autre des deux tuyaux, est formé dans le troisième élément de plaque (23). L'aire de trajet d'écoulement du trajet d'écoulement (26E_1, 26E_2) dans le matériau de gainage (26_2) est inférieure à l'aire de trajet d'écoulement du trajet d'écoulement (21E_1, 21E_2).
PCT/JP2013/085150 2013-12-27 2013-12-27 Collecteur empilé, échangeur de chaleur et climatiseur WO2015097876A1 (fr)

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EP13900071.5A EP3088831B1 (fr) 2013-12-27 2013-12-27 Échangeur de chaleur et climatiseur
JP2015554455A JP6080982B2 (ja) 2013-12-27 2013-12-27 積層型ヘッダー、熱交換器、及び、空気調和装置
PCT/JP2013/085150 WO2015097876A1 (fr) 2013-12-27 2013-12-27 Collecteur empilé, échangeur de chaleur et climatiseur

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WO2018062519A1 (fr) * 2016-09-29 2018-04-05 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
WO2018179311A1 (fr) * 2017-03-31 2018-10-04 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération doté de ce dernier
CN114174753A (zh) * 2019-08-07 2022-03-11 大金工业株式会社 热交换器和热泵装置
WO2022085067A1 (fr) * 2020-10-20 2022-04-28 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
JPWO2022102040A1 (fr) * 2020-11-12 2022-05-19
WO2024023958A1 (fr) * 2022-07-27 2024-02-01 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

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WO2020262699A1 (fr) * 2019-06-28 2020-12-30 ダイキン工業株式会社 Échangeur de chaleur et appareil de pompe à chaleur

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WO2018062519A1 (fr) * 2016-09-29 2018-04-05 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
CN110476036B (zh) * 2017-03-31 2021-05-18 三菱电机株式会社 热交换器及具备该热交换器的制冷循环装置
CN110476036A (zh) * 2017-03-31 2019-11-19 三菱电机株式会社 热交换器及具备该热交换器的制冷循环装置
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WO2018179311A1 (fr) * 2017-03-31 2018-10-04 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération doté de ce dernier
CN114174753A (zh) * 2019-08-07 2022-03-11 大金工业株式会社 热交换器和热泵装置
CN114174753B (zh) * 2019-08-07 2023-01-13 大金工业株式会社 热交换器和热泵装置
WO2022085067A1 (fr) * 2020-10-20 2022-04-28 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
JPWO2022102040A1 (fr) * 2020-11-12 2022-05-19
WO2022102040A1 (fr) * 2020-11-12 2022-05-19 三菱電機株式会社 Échangeur de chaleur intérieur et unité intérieure de climatiseur
JP7471446B2 (ja) 2020-11-12 2024-04-19 三菱電機株式会社 室内熱交換器、及び空気調和機の室内機
WO2024023958A1 (fr) * 2022-07-27 2024-02-01 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

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EP3088831A4 (fr) 2017-09-13
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JPWO2015097876A1 (ja) 2017-03-23
EP3088831A1 (fr) 2016-11-02

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