WO2015063875A1 - Collecteur stratifié, échangeur de chaleur, et appareil de climatisation - Google Patents

Collecteur stratifié, échangeur de chaleur, et appareil de climatisation Download PDF

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Publication number
WO2015063875A1
WO2015063875A1 PCT/JP2013/079346 JP2013079346W WO2015063875A1 WO 2015063875 A1 WO2015063875 A1 WO 2015063875A1 JP 2013079346 W JP2013079346 W JP 2013079346W WO 2015063875 A1 WO2015063875 A1 WO 2015063875A1
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WO
WIPO (PCT)
Prior art keywords
plate
opening
flat tube
pipe
heat exchanger
Prior art date
Application number
PCT/JP2013/079346
Other languages
English (en)
Japanese (ja)
Inventor
拓未 西山
岡崎　多佳志
石橋　晃
真哉 東井上
繁佳 松井
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 PCT/JP2013/079346 priority Critical patent/WO2015063875A1/fr
Priority to EP13896215.4A priority patent/EP3064880B1/fr
Priority to JP2015544683A priority patent/JP6116702B2/ja
Publication of WO2015063875A1 publication Critical patent/WO2015063875A1/fr

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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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/30—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being attachable to the element
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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.
  • the liquid refrigerant that has flowed out from the end of the flat tube to the spacer portion has a larger space in the spacer portion, so that the flow state becomes close to a laminar flow. For this reason, the refrigerant
  • the present invention has been made in order to solve the above-described problems, and is a fluid that flows into a pipe in a stacked header that is connected to a plurality of pipes and allows a fluid that flows from one pipe to flow into another pipe. It is an object of the present invention to provide a stacked header that can reduce the bias of. Moreover, an object of this invention is to obtain the heat exchanger provided with such a laminated header. Moreover, 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 plurality of first plates having a second opening, the second openings being stacked on the first plate so as to communicate with the first openings, and a flow path being formed;
  • a flow path area of the flow path is changed continuously or stepwise in the stacking direction of the plurality of second plate-like bodies.
  • the present invention is connected to a plurality of pipes, and in a stacked header that allows a fluid flowing from one pipe to flow into another pipe, can reduce the bias of the fluid flowing into the pipe.
  • the laminated header according to the present invention will be described with reference to the drawings.
  • the multilayer header according to the present invention may be applied to other devices.
  • the configuration, operation, and the like described below are merely examples, and are not limited to such configuration, operation, and the like.
  • 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 Embodiment 1 of the present invention.
  • FIG. 2 is a top view showing a schematic configuration of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • the heat exchanger 1 includes a laminated header 10, a plurality of flat tubes 20, and a plurality of fins 3.
  • a fluid for example, a refrigerant
  • the fins 3 have, for example, a plate shape and are stacked at a predetermined interval, and a heat medium (for example, air) circulates between the fins 3.
  • the fin 3 is comprised by metal materials, such as aluminum and copper, for example.
  • the flat tube 20 has a flat cross section.
  • the flat tube 20 is made of, for example, a metal material such as aluminum or copper.
  • the flat tube 20 is arranged such that the direction of the long axis of the flat shape faces the air flow direction and is spaced in the direction of the short axis of the flat shape.
  • the flat tubes 20 are arranged in a plurality of stages in the step direction intersecting the air flow direction.
  • the flat tubes 20 are arranged in a plurality of rows in the row direction along the air flow direction.
  • the flat tube 20 is 2 rows.
  • the side where the refrigerant flows into the laminated header 10 is referred to as a flat tube 20a
  • the side where the refrigerant flows out of the laminated header 10 is referred to as a flat tube 20b.
  • the content common to all the flat tubes 20 is described when the suffix is not attached
  • FIG. 3 is a schematic configuration diagram showing a cross section of the flat tube 20 of the heat exchanger 1 according to Embodiment 1 of the present invention.
  • at least one partition is provided inside the flat tube 20 and a plurality of flow paths are formed.
  • the length in the short axis direction of the flat tube 20 is referred to as a tube height H21
  • the length in the long axis direction is referred to as a tube width L22
  • the distance between the outer periphery of the flat tube 20 and the inner periphery of the flow path is The length is referred to as tube thickness t23.
  • the flat tube 20 corresponds to the “pipe” 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.
  • FIG. 4 is a schematic perspective view showing a state in which the laminated header 10 of the heat exchanger 1 according to Embodiment 1 of the present invention is disassembled.
  • the portion A in FIG. 1 is shown in an enlarged manner.
  • the multilayer header 10 includes a plurality of bare materials 11 and a plurality of clad materials 12.
  • the clad material 12 is a plate-like member to which a brazing material is applied.
  • the bare material 11 is a plate-like member to which no brazing material is applied.
  • the laminated header 10 is configured by alternately laminating bare materials 11 and clad materials 12.
  • the laminated header 10 includes the bare material 11 and the clad material 12 in which the first opening 30 is formed, and the bare material 11 and the clad material 12 in which the second opening 40 that communicates with the first opening 30 is formed. And the bare material 11 and the clad material 12 in which the third openings 50 communicating with the plurality of second openings 40 are formed, and the bare material 11 in which no openings are formed are stacked, and the flow of the fluid flows A road is formed.
  • the bare header 11 and the clad 12 may be laminated in any number to form the laminated header 10.
  • the bare material 11 and the clad material 12 are given suffixes a to f as they are laminated from the insertion side of the flat tube 20.
  • the first opening 30, the second opening 40, and the third opening 50 are given the same suffix as the corresponding bare material 11 or the cladding material 12. If no suffix is added, the contents common to all are described.
  • FIG. 5 is a schematic perspective view showing a laminated state of the laminated header 10 according to Embodiment 1 of the present invention.
  • FIG. 6 is a schematic cross-sectional view of the multilayer header 10 according to Embodiment 1 of the present invention.
  • the BB cross section of FIG. 1 is shown enlarged.
  • Each layer of the bare material 11 and the clad material 12 of the multilayer header 10 includes a first opening 30 to which the flat tube 20 is connected, a contracted flow channel 41 formed by the second opening 40, and a third opening. 50 constitutes the column passing flow path 51 formed by 50.
  • the contracted flow path 41 is given the same suffix as the corresponding flat tube 20. If no suffix is added, the contents common to all are described.
  • a first opening 30a is formed in the bare material 11a and the clad material 12a.
  • the first opening 30a has a flat shape corresponding to the shape of the flat tube 20, and the major axis direction is in the column direction.
  • the first opening 30 a is formed larger than the outer periphery of the flat tube 20. That is, the hole height H31 that is the length of the short axis of the first opening 30 is not less than the tube height H21 of the flat tube 20, and the hole width L32 that is the length of the long axis of the first opening 30 is
  • the flat tube 20 has a tube width L22 or more. The end of the flat tube 20 is inserted into the first opening 30a.
  • Second openings 40b to 40d are formed in the bare materials 11b to 11d and the clad materials 12b to 12d.
  • the second openings 40b to 40d have a flat shape corresponding to the shape of the flat tube 20, and the major axis direction faces the column direction.
  • the bare materials 11b to 11d and the clad materials 12b to 12d are laminated so that the second openings 40b to 40d communicate with the first opening 30a, and the contracted flow path 41 is formed.
  • the second opening 40 b of the bare material 11 b adjacent to the clad material 12 a is formed smaller than the outer periphery of the flat tube 20. That is, the hole height H41, which is the length of the short axis of the second opening 40b of the bare material 11b, is less than the pipe height H21 of the flat tube 20, and is the length of the long axis of the second opening 40b.
  • the hole width L42 is less than the tube width L22 of the flat tube 20.
  • a part of the end surface of the flat tube 20 inserted into the first opening 30 is in contact with the side surface of the bare material 11b.
  • regulates the insertion position of the flat tube 20 by receiving the flat tube 20 end part with the bare material 11b is provided.
  • the second opening 40b is preferably larger than the inner circumference of the flat tube 20. That is, the relationship of tube height H21> hole height H41 ⁇ (tube height H21-2 ⁇ tube thickness t23) and tube width L22> hole width L42 ⁇ (tube width L22-2 ⁇ tube thickness t23). It is. Thereby, the flow path in the flat tube 20 is not blocked by the bare material 11b, and the flow path resistance can be reduced.
  • the flat tube 20 is inserted into the first opening 30 and the brazing material of the clad material 12a is heated and melted while a part of the end surface of the flat tube 20 is in contact with the bare material 11b.
  • the brazing material By the brazing material, the side surface of the flat tube 20 and the inner peripheral surface of the first opening 30a are connected. Moreover, it connects with the bare material 11b in which the brazing material is not apply
  • the second opening 40c of the bare material 11c and the clad material 12c is formed smaller than the second opening 40b of the bare material 11b and the clad material 12b. Further, the second opening 40d of the bare material 11d and the cladding material 12d is formed smaller than the second opening 40c of the bare material 11c and the cladding material 12c. As described above, the sizes of the second openings 40b to 40d are formed so as to be closer to the bare material 11a and the clad material 12a. That is, the flow path area (opening cross-sectional area) of the contracted flow path 41 has a structure that increases stepwise in the stacking direction of the bare material 11 and the clad material 12.
  • the bare material 11d and the clad material 12d arranged farthest from the bare material 11a are the size of the second opening 40d. Is the smallest. That is, the flow path area (opening cross-sectional area) of the contracted flow path 41 is the smallest at a position farthest from the bare material 11a. Note that only one of the second openings 40d of the bare material 11d or the clad material 12d may be formed to be the smallest.
  • the contracted flow path 41 is formed by the second openings 40b to 40d of the bare materials 11b to 11d and the clad materials 12b to 12d has been described.
  • the number of stacked layers is arbitrarily set. can do. It is desirable that the length of the contracted flow channel 41 in the stacking direction is longer than the thickness of the two bare materials 11 combined.
  • the length by which the edge part of the flat tube 20 is inserted can be varied by laminating
  • the flat tube 20 is inserted into at least one clad material 12a.
  • a third opening 50e is formed in the bare material 11e and the clad material 12e.
  • the third opening 50e is formed by one opening having a size including the two second openings 40d formed in the bare material 11d and the clad material 12d.
  • the bare material 11f is not provided with an opening in a portion facing the third opening 50e.
  • the present invention is not limited to this.
  • a groove-like flow path may be formed on one plate-like member and laminated on the clad material 12d.
  • the reduced flow path 41a corresponding to the flat tube 20a and the reduced flow corresponding to the flat pipe 20b are used. You may connect the flow path 41b.
  • the number of stacked bare members 11e and clad members 12e forming the line passing channel 51 is not limited to one, and may be arbitrarily changed.
  • the column passage 51 may be formed by alternately laminating the bare material 11e and the clad material 12e each having the third opening 50 formed thereon.
  • the pressure loss can be reduced by laminating a plurality of the bare materials 11e and the clad materials 12e to increase the channel area of the column passing channel 51.
  • the bare material 11a and the clad material 12a correspond to the “first plate-like body” in the present invention.
  • the bare materials 11b to 11d and the clad materials 12b to 12d correspond to the “second plate-like body” in the present invention.
  • the bare materials 11e and 11f and the clad materials 12e to 12f correspond to the “third plate-like body” in the present invention.
  • FIG. 7 is a schematic cross-sectional view illustrating the flow of the refrigerant in the multilayer header 10 according to Embodiment 1 of the present invention.
  • the arrow shown by FIG. 7 has shown the direction through which a refrigerant
  • a case where the refrigerant flows into the laminated header 10 from the flat tube 20a and flows out from the laminated header 10 into the flat tube 20a will be described as an example.
  • the refrigerant that has flowed into the laminated header 10 from the end of the flat tube 20 a is contracted by the contracted flow channel 41 a and flows through the row passing channel 51.
  • the flow path of the refrigerant from the end of the flat tube 20a toward the connecting flow path 51 is gradually reduced in flow area (open sectional area).
  • the bias of the refrigerant is suppressed.
  • the flow state of the refrigerant can be made to be more sprayed by contracting with the contracted flow channel 41.
  • the refrigerant that has flowed through the line passing flow path 51 flows into the contracted flow path 41b corresponding to the flat tube 20b.
  • the refrigerant that has flowed into the contracted flow path 41b flows into the flat tube 20b.
  • the flow path area (opening cross-sectional area) of the refrigerant flow path from the contracted flow path 41b to the flat tube 20b gradually increases, the refrigerant is evenly distributed to each flow path of the flat tube 20b.
  • coolant is not limited to the said description, You may flow in the reverse direction.
  • the flow direction of the heat medium (for example, air) that exchanges heat with the refrigerant in the flat tube 20 may be either parallel to or opposed to the flow direction of the column passage 51.
  • the bare material 11 having the second opening 40 and the clad material 12 are laminated to form a contracted flow channel 41, and the flow path area of the contracted flow channel 41 is as follows. It changes stepwise in the stacking direction. For this reason, the bias of the refrigerant flowing into the contracted flow channel 41 from the flat tube 20 and flowing out of the contracted flow channel 41 can be suppressed. Moreover, the bias of the refrigerant flowing into the flat tube 20 from the contracted flow channel 41 can be suppressed.
  • the size of the second opening 40 is larger as it is closer to the flat tube 20. For this reason, it can be set as the structure where the flow path area of the contraction flow path 41 which goes to the connecting flow path 51 from the edge part of the flat tube 20 becomes small, and the deviation of the refrigerant
  • the bare material 11 and the clad material 12 in which the second opening 40 is formed have the second opening 40 having the largest size. It is formed small. For this reason, the flow state of the refrigerant flowing into the contracted flow channel 41 from the flat tube 20 and flowing out from the contracted flow channel 41 can be made more sprayed.
  • the bare material 11 a into which the end of the flat tube 20 is inserted and the first opening 30 a of the clad material 12 a are formed larger than the outer periphery of the flat tube 20. That is, the hole height H31 of the first opening 30a is not less than the tube height H21, and the hole width L32 of the first opening 30a is not less than the tube width L22. For this reason, the surface (insertion white) which adhere
  • the second opening 40 b of the bare material 11 b adjacent to the clad material 12 a is formed smaller than the outer periphery of the flat tube 20. That is, the hole height H41 of the second opening 40b is less than the tube height H21, and the hole width L42 of the second opening 40b is less than the tube width L22. For this reason, a part of end surface of the flat tube 20 inserted in the 1st opening part 30 is contacted with the side surface of the bare material 11b, and the insertion position of the flat tube 20 can be prescribed
  • a heat exchanger can be manufactured without making the insertion wall longer than necessary, and in the heat exchanger of the same size, the ratio of the heat exchange part is increased. Can do.
  • the size of the heat exchanger 1 can be reduced when an equivalent heat exchanging capability is obtained by shortening the insertion length of the flat tube 20.
  • the bonding area between the flat tube 20 and the laminated header 10 is increased, and the bonding strength can be improved.
  • the second opening 40b is larger than the inner circumference of the flat tube 20. That is, tube height H21> hole height H41 of second opening 40b ⁇ (tube height H21-2 ⁇ tube thickness t23) and tube width L22> hole width L42 of second opening 40b ⁇ (tube The relationship of width L22-2 ⁇ tube thickness t23). For this reason, the flow path in the flat tube 20 is not blocked by the bare material 11b, and the flow path resistance can be reduced.
  • the shape of the contracted flow path into a stepped shape, it can be manufactured relatively easily as compared with chamfering or curved surface shape processing.
  • the manufacturing cost can be reduced by facilitating the manufacturing.
  • By adopting a simple step-like shape it is possible to facilitate the production of the mold even in the production of the mold by cutting or casting. Further, the manufacturing cost can be reduced by facilitating the manufacture.
  • Embodiment 2 the laminated header 10 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. 9 is a schematic cross-sectional view of the multilayer header 10 according to Embodiment 2 of the present invention.
  • the laminated header 10 according to the second embodiment has a structure in which the flow passage area (opening cross-sectional area) of the contracted flow passage 41 continuously changes in the lamination direction of the bare material 11 and the clad material 12. .
  • the wall surface shape 13 of the cross section in the stacking direction of the bare materials 11b to 11d and the cladding materials 12b to 12d is formed in a straight line (chamfered shape).
  • the flow path area of the contracted flow path 41 changes continuously so that it may become large as the flat tube 20 is approached.
  • the wall shape of the contracted flow channel 41 is not limited to a linear shape as long as it has a continuously changing shape. Further, only a part of the bare materials 11b to 11d and the clad materials 12b to 12d may be continuously changed. For example, as shown in FIG. 10, among the bare materials 11b to 11d and the cladding materials 12b to 12d, the wall surface shape 14 of the cross section in the stacking direction of the bare materials 11c to 11d and the cladding materials 12c to 12d is curved (rounded shape). ). For example, as shown in FIG. 11, the wall surface shape 15 in all of the bare materials 11b to 11d and the clad materials 12b to 12d may be formed in a curved shape (rounded shape).
  • the bare material 11 having the second opening 40 and the clad material 12 are laminated to form the contracted flow channel 41, and the channel area of the contracted flow channel 41 is , Changes continuously in the stacking direction. For this reason, the bias of the refrigerant flowing into the contracted flow channel 41 from the flat tube 20 and flowing out of the contracted flow channel 41 can be suppressed. Moreover, the bias of the refrigerant flowing into the flat tube 20 from the contracted flow channel 41 can be suppressed.
  • the separation of the refrigerant flow and the generation of vortices in the contracted flow path 41 can be reduced.
  • the pressure loss in a flow path can be reduced by reducing the separation of flow and the generation of vortices.
  • the refrigerant can be evenly distributed to each flow path provided in the flat tube 20.
  • the level difference of the contracted flow channel 41 the retention of liquid refrigerant or oil can be suppressed.
  • Embodiment 3 the laminated header 10 according to the third embodiment will be described focusing on differences from the first embodiment.
  • symbol is attached
  • FIG. 1 the same code
  • symbol is attached
  • FIG. 12 is a schematic cross-sectional view of the multilayer header 10 according to Embodiment 3 of the present invention.
  • the principal part of the laminated header 10 is expanded and shown.
  • the laminated header 10 according to the third embodiment is melted between the side surface of the flat tube 20 and the inner peripheral surface of the first opening 30a of the bare material 11a and the cladding material 12a.
  • a clearance 60 for collecting brazing material is provided. That is, the relationship between the tube height H21 of the flat tube 20, the hole height H31 of the first opening 30a, and the height of the clearance 60 (distance in the short axis direction of the flat tube 20) is the height of the clearance 60.
  • the relationship between the tube width L22 of the flat tube 20, the hole width L32 of the first opening 30a, and the width of the clearance 60 is the width of the clearance 60 ⁇ (hole width) L32 ⁇ tube width L22) / 2.
  • the height of the clearance 60 and the length of the width may be different.
  • the clearance 60 corresponds to a “gap” in the present invention.
  • the height and width of the clearance 60 (the distance between the side surface of the flat tube 20 and the inner peripheral surface of the first opening 30a) are too large, the molten brazing material will become the inner periphery of the flat tube 20 and the first opening 30.
  • the flat tube 20 and the laminated header 10 cannot be bonded to each other without sufficiently reaching the surface. For this reason, for example, the length of the clearance 60 ⁇ 0.10 mm is desirable.
  • FIG. 13 is a schematic cross-sectional view for explaining the action during brazing of the multilayer header 10 according to the third embodiment of the present invention.
  • the flat tube 20 is inserted into the first opening 30 and the brazing material of the clad material 12a is heated while a part of the end surface of the flat tube 20 is in contact with the bare material 11b.
  • the material melts.
  • the molten brazing material 61 permeates between the side surface of the flat tube 20 and the inner peripheral surface of the first opening 30a by gravity or surface tension.
  • the molten brazing material 61 flows to the side surface of the flat tube 20 (in the direction of the arrow in FIG. 13) along the clearance 60 that is an open end. Thereby, the bare material 11a, the clad material 12a, and the side surface of the flat tube 20 are adhere
  • the laminated header 10 has a clearance 60 in which molten brazing material accumulates between the side surface of the flat tube 20 and the inner peripheral surface of the first opening 30 of the bare material 11a and the cladding material 12a. Provided. For this reason, it is possible to prevent the brazing material melted from the clad material 12a from flowing into the end portion of the flat tube 20 during brazing. Further, by adopting a structure in which the brazing material does not easily enter the end portion of the flat tube 20, the flow path in the flat tube 20 is not blocked, and the refrigerant can be evenly distributed.
  • the clearance 60 it is possible to absorb a deviation caused by a dimensional error when the plurality of flat tubes 20 are simultaneously inserted into the laminated header 10. Therefore, the flat tube 20 can be easily inserted into the laminated header 10. Further, since the flat tube 20 can be easily inserted into the laminated header 10, the manufacturing cost can be reduced.
  • the length of the clearance 60 is set to 0.10 mm or less, it is possible to reduce unbonding between the bare material 11a and the side surface of the flat tube 20. Moreover, joint strength can be improved by reducing the non-adhesion of the bare material 11a and the flat tube 20 side surface. Further, the reliability can be improved by improving the bonding strength.
  • Embodiment 4 FIG.
  • the laminated header 10 according to the fourth embodiment will be described focusing on differences from the first embodiment.
  • symbol is attached
  • FIG. 1
  • FIG. 14 is a schematic cross-sectional view of the multilayer header 10 according to the fourth embodiment of the present invention.
  • FIG. 15 is an enlarged view showing a portion C of FIG.
  • the laminated header 10 according to the third embodiment is such that the bare material 11 b that contacts a part of the end face of the flat tube 20 is a part that contacts a part of the end face of the flat tube 20. Is formed to be smaller than the non-contact portion.
  • the bare material 11b is formed so that the size of the opening is different between the side where the end of the flat tube 20 is inserted and the side where the end of the flat tube 20 contacts (the back side). Yes.
  • a portion where a part of the end face of the flat tube 20 contacts is referred to as a protrusion-shaped portion 110.
  • the second opening 40b of the bare material 11b has a hole height H31 of the first opening 30a ⁇ a hole height H41 of the second opening 40b ⁇ the tube height on the side where the end of the flat tube 20 is inserted. H21, and the hole width L32 of the first opening 30a ⁇ the hole width L42 of the second opening 40b ⁇ the tube width L22. Further, the back side where the end of the flat tube 20 contacts is the tube height H21 ⁇ the hole height H41 ⁇ (tube height H21-2 ⁇ tube thickness t23) of the second opening 40b and the tube width L22 ⁇ The hole width L42 of the second opening 40b ⁇ (tube width L22-2 ⁇ tube thickness t23).
  • FIG. 16 is a schematic cross-sectional view showing a state in which the flat tube 20 is inserted in the laminated header 10 according to the fourth embodiment of the present invention.
  • FIG. 17 is an enlarged view showing a D portion of FIG.
  • FIG. 18 is a schematic cross-sectional view for explaining the action during brazing of the multilayer header 10 according to the fourth embodiment of the present invention.
  • FIG. 19 is an enlarged view showing a portion E of FIG.
  • the molten brazing material 61 is separated between the side surface of the flat tube 20 and the inner peripheral surface of the first opening portion 30 a by gravity or surface tension. It penetrates into the insertion side of the flat tube 20 of the material 11b. At this time, the molten brazing material 61 flows to the side surface of the flat tube 20 that is the open end (in the direction of the arrows in FIGS. 18 and 19). Thereby, the bare material 11a, the clad material 12a, the side surface of the flat tube 20, and the insertion side of the flat tube 20 of the bare material 11b are bonded.
  • the bare material 11a is formed such that the thickness of the portion where a part of the end face of the flat tube 20 contacts is smaller than the portion where it does not contact. That is, the protrusion-shaped part 110 is provided on the back side of the bare material 11b. For this reason, it is possible to define the insertion white at the end of the flat tube 20.
  • the brazing material 61 can be prevented from entering the flat tube 20.
  • edge part of the flat tube 20 is fixed in the bare material 11b, more insertion scissors can be obtained. Moreover, many adhesion areas at the time of brazing can be obtained by obtaining more than insertion scissors. Moreover, adhesive strength can be improved by obtaining many adhesion areas. Moreover, reliability can be improved by improving contact strength.
  • the distance between the end portion of the flat tube 20 and the clad material 12a is increased, it is possible to prevent the brazing material 61 from flowing into the flat tube 20 even if it flows to the flat tube 20 side.
  • the brazing material 61 does not easily enter the end of the flat tube 20, the flow path at both ends of the flat tube 20 is not blocked, so that the refrigerant can be evenly distributed.
  • Embodiment 5 FIG. In the fifth embodiment, a configuration of an air conditioner to which the stacked header 10 and a heat exchanger including the stacked header 10 are applied will be described.
  • FIG. 20 and 21 are diagrams showing a schematic configuration of an air-conditioning apparatus 91 according to Embodiment 5 of the present invention.
  • FIG. 20 has shown the case where the air conditioning apparatus 91 performs heating operation.
  • FIG. 21 shows a case where the air conditioner 91 performs a cooling operation.
  • the air conditioner 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger 94, a throttle device 95, an indoor heat exchanger 96, and an outdoor fan 97. And an indoor fan 98 and a control device 99.
  • the compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion device 95, and the indoor heat exchanger 96 are connected by a refrigerant pipe to form a refrigerant circulation circuit.
  • the four-way valve 93 may be another flow path switching device.
  • the outdoor heat exchanger 94 is the heat exchanger 1.
  • air generated by driving the outdoor fan 97 is ventilated.
  • the outdoor fan 97 may be provided on the leeward side of the heat exchanger 1 or may be provided on the leeward side of the heat exchanger 1.
  • a compressor 92, a four-way valve 93, a throttle device 95, an outdoor fan 97, an indoor fan 98, various sensors, and the like are connected to the control device 99.
  • the control device 99 By switching the flow path of the four-way valve 93 by the control device 99, the heating operation and the cooling operation are switched.
  • the flow of the refrigerant during the heating operation will be described with reference to FIG.
  • the high-pressure and high-temperature gaseous refrigerant discharged from the compressor 92 flows into the indoor heat exchanger 96 through the four-way valve 93 and is condensed by heat exchange with the air supplied by the indoor fan 98. Heat up.
  • the condensed refrigerant becomes a high-pressure supercooled liquid state (or low-dryness gas-liquid two-phase refrigerant), flows out of the indoor heat exchanger 96, and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 95. .
  • the low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 94, exchanges heat with the air supplied by the outdoor fan 97, and evaporates.
  • the evaporated refrigerant enters a low-pressure superheated gas state, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93. That is, during the heating operation, the outdoor heat exchanger 94 acts as an evaporator.
  • the refrigerant passes through the flat tubes 20a arranged in the windward row, passes through the laminated header 10, and flows into the flat tubes 20b arranged in the leeward row.
  • the refrigerant flow during the cooling operation will be described with reference to FIG.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 92 flows into the outdoor heat exchanger 94 through the four-way valve 93, exchanges heat with the air supplied by the outdoor fan 97, and condenses.
  • the condensed refrigerant becomes a high-pressure supercooled liquid state (or a low-dryness gas-liquid two-phase refrigerant), flows out of the outdoor heat exchanger 94, and enters a low-pressure gas-liquid two-phase state by the expansion device 95.
  • the low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 96 and evaporates by heat exchange with the air supplied by the indoor fan 98, thereby cooling the room.
  • the evaporated refrigerant becomes a low-pressure superheated gas state, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 through the four-way valve 93. That is, during the cooling operation, the outdoor heat exchanger 94 functions as a condenser.
  • the refrigerant passes through the flat tubes 20b arranged in the leeward row, flows into the flat tubes 20b arranged in the upwind row through the stacked header 10.
  • FIG. 22 is a schematic cross-sectional view of the multilayer header 10 according to Embodiment 5 of the present invention.
  • the main part of the multilayer header 10 is shown enlarged.
  • the multilayer header 10 according to the fifth embodiment includes the bare material 11 a and the bare material 11 d serving as the outlet of the contracted flow channel 41, the central axis of the first opening 30 a of the bare material 11 a and the cladding material 12 a, and The central axis of the second opening 40d of the clad material 12d is eccentric from each other.
  • the central axis of the second opening 40d of the contracted flow channel 41 corresponding to one of the flat tubes 20 is the center of the first opening 30a of the contracted flow channel 41. It is eccentric to the other flat tube 20 side rather than the shaft.
  • the amount of eccentricity Z is 0 ⁇ Z ⁇ W3 / 2, where W3 is the outer diameter in the major axis direction of the flat tube 20a and the flat tube 20b.
  • the distance between the central axis of the second opening 40d corresponding to the flat tube 20a and the central axis of the flat tube 20a is such that the central axis of the flat tube 20b and the second opening 40d corresponding to the flat tube 20a.
  • the distance between the central axis of the second opening 40d corresponding to the flat tube 20b and the central axis of the flat tube 20b is such that the central axis of the flat tube 20a and the second opening 40d corresponding to the flat tube 20b. It is decentered so as to be shorter than the distance between the center axis.
  • FIG.23 and FIG.24 is a figure explaining the liquid quantity distribution of the refrigerant
  • coolant which flows in into the flat tube 20b in case the heat exchanger 1 which concerns on Embodiment 5 of this invention acts as an evaporator.
  • the refrigerant is in parallel with the air flow generated by driving the outdoor fan 97. That is, it flows from the flat tube 20a to the contracted flow channel 41a, and flows from the row passing channel 51 to the contracted flow channel 41b in a gas-liquid two-phase state.
  • the heat exchanger 1 since the eccentric amount Z is Z> 0 in the contracted flow channel 41b, a large amount of liquid refrigerant that has flowed into the contracted flow channel 41b flows into the S point side of the flat tube 20b. Will be.
  • the heat exchanger 1 acts as an evaporator, since the heat load (heat exchange amount) on the windward side of the air flow generated by driving the outdoor fan 97 is large, the S point side of the flat tube 20b, that is, the flow path on the windward side.
  • the liquid refrigerant is distributed to the flow path holes of the flat tube 20 so that a large amount of the liquid refrigerant flows in the liquid, so that the evaporation of the liquid refrigerant is promoted and the heat exchange efficiency is improved.
  • FIG.25 and FIG.26 is a figure explaining the liquid quantity distribution of the refrigerant
  • coolant which flows in into the flat tube 20a in case the heat exchanger 1 which concerns on Embodiment 5 of this invention acts as a condenser.
  • the refrigerant becomes a counterflow with the air flow generated by driving the outdoor fan 97. That is, it flows from the flat tube 20b to the contracted flow channel 41b, and flows from the row passing channel 51 into the contracted flow channel 41a in a gas-liquid two-phase state.
  • the heat exchanger 1 since the eccentric amount Z is Z> 0 in the contracted flow channel 41a, a large amount of gas refrigerant flowing into the contracted flow channel 41a flows into the S point side of the flat tube 20a. Will be.
  • the heat exchanger 1 acts as a condenser, since the heat load (heat exchange amount) on the windward side of the air flow generated by the driving of the outdoor fan 97 is large, the L point side of the flat tube 20a, that is, the flow path on the windward side.

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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

La présente invention concerne un collecteur stratifié pourvu : d'un premier corps similaire à un panneau qui présente une première ouverture (30) à laquelle est raccordé un tube plat (20) ; et d'une pluralité de seconds corps similaires à des panneaux, chacun d'eux présentant une seconde ouverture (40), et à l'intérieur de chacun desquels un conduit d'écoulement est formé en étant stratifié au premier corps similaire à un panneau de telle sorte que la seconde ouverture (40) communique avec la première ouverture (30). Une zone de conduit d'écoulement du conduit d'écoulement change en continu ou par étapes dans le sens de stratification des seconds corps similaires à des panneaux.
PCT/JP2013/079346 2013-10-30 2013-10-30 Collecteur stratifié, échangeur de chaleur, et appareil de climatisation WO2015063875A1 (fr)

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PCT/JP2013/079346 WO2015063875A1 (fr) 2013-10-30 2013-10-30 Collecteur stratifié, échangeur de chaleur, et appareil de climatisation
EP13896215.4A EP3064880B1 (fr) 2013-10-30 2013-10-30 Collecteur stratifié, échangeur de chaleur, et appareil de climatisation
JP2015544683A JP6116702B2 (ja) 2013-10-30 2013-10-30 積層型ヘッダー、熱交換器、熱交換器の製造方法、及び、空気調和装置

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JPWO2015111216A1 (ja) * 2014-01-27 2017-03-23 三菱電機株式会社 積層型ヘッダー、熱交換器、及び、空気調和装置
EP3239642A1 (fr) * 2016-01-15 2017-11-01 Hamilton Sundstrand Corporation Échangeurs thermiques
WO2018062519A1 (fr) * 2016-09-29 2018-04-05 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
JP2018189337A (ja) * 2017-05-10 2018-11-29 株式会社デンソー 冷媒蒸発器およびその製造方法
WO2020174557A1 (fr) * 2019-02-26 2020-09-03 三菱電機株式会社 Collecteur en couches, échangeur de chaleur et procédé de fabrication d'échangeur de chaleur
JP2021025765A (ja) * 2019-08-07 2021-02-22 ダイキン工業株式会社 熱交換器およびヒートポンプ装置
WO2022259288A1 (fr) * 2021-06-07 2022-12-15 三菱電機株式会社 Échangeur de chaleur et unité extérieure
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
JP7485993B1 (ja) 2023-01-06 2024-05-17 ダイキン工業株式会社 熱交換器

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JP7253894B2 (ja) * 2018-10-30 2023-04-07 三星電子株式会社 洗濯機
JP7275699B2 (ja) * 2019-03-19 2023-05-18 株式会社富士通ゼネラル 積層体及び積層体の製造方法

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JPWO2015111216A1 (ja) * 2014-01-27 2017-03-23 三菱電機株式会社 積層型ヘッダー、熱交換器、及び、空気調和装置
EP3239642A1 (fr) * 2016-01-15 2017-11-01 Hamilton Sundstrand Corporation Échangeurs thermiques
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JP2018059704A (ja) * 2016-09-29 2018-04-12 ダイキン工業株式会社 熱交換器および空気調和装置
WO2018062519A1 (fr) * 2016-09-29 2018-04-05 ダイキン工業株式会社 Échangeur de chaleur et climatiseur
JP2018189337A (ja) * 2017-05-10 2018-11-29 株式会社デンソー 冷媒蒸発器およびその製造方法
WO2020174557A1 (fr) * 2019-02-26 2020-09-03 三菱電機株式会社 Collecteur en couches, échangeur de chaleur et procédé de fabrication d'échangeur de chaleur
JPWO2020174557A1 (ja) * 2019-02-26 2021-09-30 三菱電機株式会社 積層型ヘッダ、熱交換器、及び熱交換器の製造方法
JP7038892B2 (ja) 2019-02-26 2022-03-18 三菱電機株式会社 積層型ヘッダ、熱交換器、及び熱交換器の製造方法
JP2021025765A (ja) * 2019-08-07 2021-02-22 ダイキン工業株式会社 熱交換器およびヒートポンプ装置
US11555655B2 (en) 2019-08-07 2023-01-17 Daikin Industries, Ltd. Heat exchanger and heat pump device
WO2022259288A1 (fr) * 2021-06-07 2022-12-15 三菱電機株式会社 Échangeur de chaleur et unité extérieure
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
JP7485993B1 (ja) 2023-01-06 2024-05-17 ダイキン工業株式会社 熱交換器

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EP3064880A4 (fr) 2017-10-18

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