WO2021130917A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2021130917A1
WO2021130917A1 PCT/JP2019/050891 JP2019050891W WO2021130917A1 WO 2021130917 A1 WO2021130917 A1 WO 2021130917A1 JP 2019050891 W JP2019050891 W JP 2019050891W WO 2021130917 A1 WO2021130917 A1 WO 2021130917A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
joint
transfer tube
peripheral surface
tube
Prior art date
Application number
PCT/JP2019/050891
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
宏治 幸本
加藤　央平
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 JP2021566649A priority Critical patent/JP7258185B2/ja
Priority to PCT/JP2019/050891 priority patent/WO2021130917A1/ja
Publication of WO2021130917A1 publication Critical patent/WO2021130917A1/ja

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K1/00—Soldering, e.g. brazing, or unsoldering
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
    • B23K1/00—Soldering, e.g. brazing, or unsoldering
    • B23K1/14—Soldering, e.g. brazing, or unsoldering specially adapted for soldering seams
    • B23K1/18—Soldering, e.g. brazing, or unsoldering specially adapted for soldering seams circumferential seams, e.g. of shells
    • 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
    • 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
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the present disclosure relates to a heat exchanger provided with a joint for connecting a flat heat transfer tube and a circular tube.
  • a flat heat transfer tube is known as a heat transfer tube for heat exchangers used in air conditioners and the like.
  • the flat heat transfer tube is internally divided into a plurality of flow paths by a partition wall.
  • a circular refrigerant pipe is generally connected to the flat heat transfer pipe.
  • the circular tube connects, for example, flat heat transfer tubes to each other.
  • the circular pipe connects a flat heat transfer pipe and a refrigerant pipe other than the heat transfer pipe. This is because the circular pipe is easier to bend than the flat heat transfer pipe, so that the degree of freedom of the connection path of the refrigerant pipe can be improved.
  • the flat heat transfer tube and the circular tube are connected by a joint.
  • the joint includes a first insertion port into which a flat heat transfer tube is inserted. Then, the joint and the flat heat transfer tube inserted into the first insertion port are brazed and joined. Further, the joint is provided with a second insertion port into which a circular pipe is inserted. Then, the joint and the circular pipe inserted into the second insertion port are brazed and joined.
  • the lateral direction and the side end portion of the relief portion are defined as follows.
  • the direction in which the side is the short side is hereinafter referred to as the short direction.
  • the position on the most flank side is the flank side end of the joint between the joint and the heat transfer tube. It will be referred to.
  • a heat exchanger equipped with a conventional joint in which a relief portion is formed is used, and when a refrigerant flows in the joint, the pressure of the refrigerant acts on the joint in a direction in which the joint is expanded in the lateral direction.
  • the pressure of this refrigerant causes stress concentration at the relief portion side end of the joint between the joint and the heat transfer tube.
  • the stress acting on the relief portion side end portion is applied to the portion of the partition wall of the flat heat transfer tube facing the relief portion side end portion. Therefore, the compressive strength of the heat exchanger provided with the conventional joint in which the relief portion is formed depends on the thickness of the portion of the partition wall of the heat transfer tube facing the relief portion side end.
  • the thickness of the partition wall in the flat heat transfer tube in recent years, from the viewpoint of cost reduction and reduction of material usage, it may be required to reduce the thickness of the partition wall in the flat heat transfer tube.
  • a heat exchanger provided with a conventional joint in which a relief portion is formed when trying to reduce the thickness of the partition wall of the heat transfer tube while suppressing a decrease in compressive strength, the side end of the relief portion in the partition wall It is necessary to reduce the thickness of other parts of the partition wall while maintaining the thickness of the part facing the portion.
  • the flat heat transfer tube is formed by a processing method such as extrusion processing in which the thickness of a part of the partition wall cannot be changed.
  • a heat exchanger provided with a conventional joint in which a relief portion is formed has a problem that it is not possible to reduce the thickness of the partition wall of the heat transfer tube while suppressing a decrease in compressive strength.
  • the present disclosure has been made against the background of the above-mentioned problems, and it is possible to suppress the brazing material from flowing into the flow path of the heat transfer tube, and it is possible to reduce the load supported by the partition wall of the heat transfer tube as compared with the conventional case.
  • the purpose is to provide a switch.
  • the heat exchanger has a flat shape, and has a heat transfer tube whose inside is divided into a plurality of flow paths by a partition wall, a circular tube through which a refrigerant flows, and a heat transfer tube and a brazing joint with the circular tube.
  • the heat transfer tube is provided with a joint for connecting the heat transfer tube and the circular tube, and the joint includes a first insertion port into which the heat transfer tube is inserted and brazed to the outer peripheral surface of the heat transfer tube.
  • a circular tube is inserted, and the outer peripheral surface of the circular tube is provided with a second insertion port that is brazed and joined, and the inner peripheral surface of the joint is at a position facing the end of the heat transfer tube.
  • a relief portion that is recessed toward the outer peripheral surface of the joint is formed, and the joint has ribs that protrude toward the outer peripheral surface of the heat transfer tube and are brazed and joined to the outer peripheral surface of the heat transfer tube. I have.
  • the heat exchanger joint according to the present disclosure is formed with a relief portion recessed toward the outer peripheral surface of the joint at a position facing the end of the heat transfer tube. Therefore, the heat exchanger according to the present disclosure can prevent the brazing material from flowing into the flow path of the heat transfer tube. Further, the joint of the heat exchanger according to the present disclosure is provided with a rib that protrudes toward the outer peripheral surface of the heat transfer tube and is brazed to the outer peripheral surface of the heat transfer tube at the relief portion. Therefore, the heat exchanger according to the present disclosure can reduce the load supported by the partition wall of the heat transfer tube as compared with the conventional heat exchanger in which the brazing material is prevented from flowing into the flow path of the heat transfer tube. it can.
  • FIG. 1 is a perspective view showing a heat exchanger according to the embodiment.
  • FIG. 2 is an enlarged view of part A of FIG.
  • FIG. 3 is a perspective view showing the vicinity of the end portion of the heat transfer tube of the heat exchanger according to the embodiment.
  • the heat exchanger 1 includes a plurality of fins 2 and a plurality of heat transfer tubes 10.
  • the plurality of fins 2 have, for example, a substantially rectangular plate shape, and are arranged at predetermined intervals. In the present embodiment, the plurality of fins 2 are arranged at predetermined intervals in the lateral direction.
  • a plurality of heat transfer tubes 10 penetrate through these plurality of fins 2.
  • the plurality of heat transfer tubes 10 and the plurality of fins 2 are joined by brazing.
  • the plurality of heat transfer tubes 10 have a flat shape. Further, the inside of the plurality of heat transfer tubes 10 is divided into a plurality of flow paths 12 by the partition wall 11. Refrigerant flows through each flow path 12.
  • the area where the fins 2 are arranged is the heat exchanger 3. Specifically, the air flowing between the fins 2 exchanges heat with the refrigerant flowing through the flow path 12 of the heat transfer tube 10 via the wall portion of the heat transfer tube 10 and the fins 2.
  • the heat exchanger 1 includes a plurality of circular tubes 4 in order to allow the refrigerant to flow through each heat transfer tube 10.
  • the circular tube 4 has a substantially cylindrical shape.
  • the circular pipe 4 is a refrigerant pipe through which the refrigerant flowing into the heat transfer pipe 10 or the refrigerant flowing out of the heat transfer pipe 10 flows.
  • the circular tube 4 connects, for example, the heat transfer tubes 10 to each other. Further, for example, the circular pipe 4 connects the heat transfer pipe 10 and the refrigerant pipe other than the heat transfer pipe 10. Since the circular tube 4 is easier to bend than the flat heat transfer tube 10, the degree of freedom of the connection path of the refrigerant pipe can be improved.
  • the heat transfer tube 10 and the circular tube 4 are connected by a joint 20.
  • the heat exchanger 1 includes a plurality of joints 20.
  • the joint 20 includes a first insertion port 21 into which the heat transfer tube 10 is inserted. Then, the joint 20 and the heat transfer tube 10 inserted into the first insertion port 21 are brazed and joined. More specifically, the inner peripheral surface of the first insertion port 21 of the joint 20 and the outer peripheral surface of the heat transfer tube 10 are brazed and joined.
  • the joint 20 includes a second insertion port 22 into which the circular pipe 4 is inserted. Then, the joint 20 and the circular pipe 4 inserted into the second insertion port 22 are brazed and joined.
  • the inner peripheral surface of the second insertion port 22 of the joint 20 and the outer peripheral surface of the circular pipe 4 are brazed and joined. That is, the joint 20 is brazed to the heat transfer tube 10 and the circular tube 4, and connects the heat transfer tube 10 and the circular tube 4.
  • the distribution direction X, the longitudinal direction Y, and the lateral direction Z are defined as follows.
  • the direction in which the flow path 12 of the heat transfer tube 10 extends is defined as the distribution direction X.
  • the longitudinal direction is defined as the longitudinal direction Y in the cross section of the heat transfer tube 10 cut by the virtual plane perpendicular to the flow path 12.
  • the direction in which the heat transfer tube 10 is cut in a virtual plane perpendicular to the flow path 12 in the lateral direction is defined as the lateral direction Z.
  • the heat transfer tube 10 of the heat exchanger 1 according to the present embodiment is bent in a substantially L-shape in a plan view.
  • the portion of the heat transfer tube 10 inserted into the first insertion port 21 is cut by a virtual plane perpendicular to the flow path 12, and the longitudinal direction Y and the lateral direction Z are determined.
  • the joint 20 according to the present embodiment is divided into a first member 30 and a second member 40 in the lateral direction Z.
  • the first member 30 and the second member 40 are arranged in the lateral direction Z. Therefore, in the present embodiment, the lateral direction Z may be referred to as the dividing direction.
  • FIG. 4 is an exploded perspective view showing the periphery of the joint of the heat exchanger according to the embodiment.
  • FIG. 5 is a plan view of the periphery of the joint of the heat exchanger according to the embodiment.
  • 6 and 7 are cross-sectional views of the periphery of the heat exchanger joint according to the embodiment, and are perspective views of the periphery of the joint. Note that FIGS. 6 and 7 are cross-sectional views obtained by cutting the periphery of the joint 20 in a virtual plane parallel to the distribution direction X and the lateral direction Z.
  • the joint 20 according to the present embodiment includes ribs 26.
  • FIG. 6 is a cross-sectional view in which the periphery of the joint 20 is cut in a virtual plane that does not pass through the rib 26.
  • FIG. 7 is a cross-sectional view obtained by cutting the periphery of the joint 20 in a virtual plane passing through the rib 26.
  • the joint 20 includes a first member 30 and a second member 40 arranged in the lateral direction Z, which is the dividing direction.
  • the first member 30 and the second member 40 are formed by, for example, pressing.
  • the first member 30 and the second member 40 have the same shape. That is, in the present embodiment, the same member can be used as the first member 30 and the second member 40.
  • the first member 30 includes a recess 31 that forms a part of the first insertion port 21.
  • the second member 40 includes a recess 41 that constitutes the remaining portion of the first insertion port 21.
  • the inner peripheral surface of the first insertion port 21 has a shape along the outer peripheral surface of the flat heat transfer tube 10. Therefore, the inner peripheral surface of the recess 31 of the first member 30 has a shape along the outer peripheral surface of the flat heat transfer tube 10.
  • the inner peripheral surface of the recess 41 of the second member 40 also has a shape along the outer peripheral surface of the flat heat transfer tube 10.
  • the inner peripheral surface of the recess 31 of the first member 30 is a surface of the recess 31 that faces the outer peripheral surface of the heat transfer tube 10.
  • the inner peripheral surface of the recess 41 of the second member 40 is a surface of the recess 41 that faces the outer peripheral surface of the heat transfer tube 10.
  • the first member 30 is provided with a recess 32 that forms a part of the second insertion port 22.
  • the second member 40 includes a recess 42 that constitutes the remaining portion of the second insertion port 22.
  • the inner peripheral surface of the second insertion port 22 has a shape along the outer peripheral surface of the circular tube 4. Therefore, the inner peripheral surface of the recess 32 of the first member 30 has a shape along the outer peripheral surface of the circular tube 4. Further, the inner peripheral surface of the recess 42 of the second member 40 also has a shape along the outer peripheral surface of the circular tube 4.
  • the inner peripheral surface of the recess 32 of the first member 30 is a surface of the recess 32 that faces the outer peripheral surface of the circular tube 4.
  • the inner peripheral surface of the recess 42 of the second member 40 is a surface of the recess 42 facing the outer peripheral surface of the circular pipe 4.
  • the heat transfer tube 10 and the circular tube 4 are sandwiched between the first member 30 and the second member 40, and the first member 30, the second member 40, the heat transfer tube 10 and the circular tube are sandwiched between the first member 30 and the second member 40. 4 is brazed and joined.
  • the heat transfer tube 10 is inserted into the first insertion port 21.
  • the portions of the inner peripheral surface of the first insertion port 21 and the outer peripheral surface of the heat transfer tube 10 that are in contact with each other via the brazing material are joined. Will be done.
  • the portion where the inner peripheral surface of the first insertion port 21 and the outer peripheral surface of the heat transfer tube 10 are brazed and joined is referred to as a joint portion 23.
  • the end portion of the heat transfer tube 10 on the end portion 13 side is referred to as a relief portion side end portion 24.
  • the end portion 13 of the heat transfer tube 10 is an end portion of the end portion of the heat transfer tube 10 on the side inserted into the joint 20.
  • the circular pipe 4 is inserted into the second insertion port 22.
  • the portions of the inner peripheral surface of the second insertion port 22 and the outer peripheral surface of the circular pipe 4 that are in contact with each other via the brazing material are joined. Will be done.
  • the periphery of the end portion of the first member 30 facing the longitudinal direction Y and the vicinity of the end portion of the second member 40 facing the longitudinal direction Y are opposed to each other.
  • the area around the end is in contact with the brazing material. Then, the portion of the first member 30 and the second member 40 is brazed and joined.
  • the heat exchanger 1 When the heat exchanger 1 is used after the heat transfer tube 10, the circular tube 4 and the joint 20 are brazed and joined, the refrigerant flowing out from one of the heat transfer tube 10 and the circular tube 4 is connected to the first member 30 in the joint 20. It flows into the space between the second member 40 and the second member 40. Then, the refrigerant that has flowed into the space between the first member 30 and the second member 40 in the joint 20 flows into the other of the heat transfer tube 10 and the circular tube 4.
  • the first member 30 and the second member 40 are temporarily fixed so that the first member 30 and the second member 40 do not separate from each other. It is necessary to do it.
  • the first member 30 and the second member 40 are temporarily fixed as follows. At least one convex portion 34 protruding toward the second member 40 is formed on the surface of the first member 30 on the side facing the second member 40. Further, on the surface of the second member 40 on the side facing the first member 30, a concave portion 43 into which the convex portion 34 is fitted is formed at a position facing the convex portion 34.
  • At least one convex portion 44 protruding toward the first member 30 is formed on the surface of the second member 40 on the side facing the first member 30. Further, on the surface of the first member 30 on the side facing the second member 40, a concave portion 33 into which the convex portion 44 is fitted is formed at a position facing the convex portion 44.
  • a relief portion 25 recessed toward the outer peripheral surface of the joint 20 is formed at a position facing the end portion 13 of the heat transfer tube 10.
  • the joint 20 according to the present embodiment includes the first member 30 and the second member 40. Therefore, in the joint 20 according to the present embodiment, relief portions 25 are formed on both the first member 30 and the second member 40.
  • the relief portion 25 By forming the relief portion 25, the end portion 13 of the heat transfer tube 10 and the inner peripheral surface of the joint 20 do not come into contact with each other. In other words, by forming the relief portion 25, the relief portion side end portion 24 of the joint portion 23 and the end portion 13 of the heat transfer tube 10 are separated from each other. Therefore, by forming the relief portion 25, it is possible to prevent the brazing material from flowing into the flow path 12 of the heat transfer tube 10.
  • the thickness of the partition wall in the flat heat transfer tube in recent years, from the viewpoint of cost reduction and reduction of material usage, it may be required to reduce the thickness of the partition wall in the flat heat transfer tube.
  • a heat exchanger provided with a conventional joint in which a relief portion is formed when trying to reduce the thickness of the partition wall of the heat transfer tube while suppressing a decrease in compressive strength, the side end of the relief portion in the partition wall It is necessary to reduce the thickness of other parts of the partition wall while maintaining the thickness of the part facing the portion.
  • the flat heat transfer tube is formed by a processing method such as extrusion processing in which the thickness of a part of the partition wall cannot be changed. For this reason, the heat exchanger provided with the conventional joint in which the relief portion is formed has not been able to reduce the thickness of the partition wall of the heat transfer tube while suppressing the reduction in the compressive strength.
  • the joint 20 is provided with the rib 26 in order to reduce the load supported by the partition wall 11 of the heat transfer tube 10 as compared with the conventional case.
  • the joint 20 includes a rib 26 at the relief portion 25 that projects toward the outer peripheral surface of the heat transfer tube 10.
  • the rib 26 extends in the distribution direction X, for example. Further, the rib 26 is brazed and joined to the outer peripheral surface of the heat transfer tube 10. The reason why the load supported by the partition wall 11 of the heat transfer tube 10 can be reduced as compared with the conventional case by providing the rib 26 will be described later.
  • the joint 20 includes a plurality of ribs 26.
  • the plurality of ribs 26 are arranged at intervals in the longitudinal direction Y. That is, the plurality of ribs 26 are arranged at intervals in the direction perpendicular to the flow path 12 of the heat transfer tube 10.
  • the joint end 27 among the portions of the rib 26 that are brazed to the outer peripheral surface of the heat transfer tube 10, the position closest to the end 13 side of the heat transfer tube 10 is defined as the joint end 27.
  • the joint end portion 27 is defined in this way, in the present embodiment, the joint end portion 27 and the end portion 13 of the heat transfer tube 10 are separated from each other.
  • the joint in which the rib 26 is removed from the joint 20 according to the present embodiment will be referred to as the joint 120 according to the comparative example. That is, the joint 120 according to the comparative example has a configuration that does not include the rib 26. Further, the heat exchanger provided with the joint 120 according to the comparative example is referred to as the heat exchanger according to the comparative example.
  • the same configurations as the configurations of the heat exchanger 1 and the joint 20 according to the present embodiment include the heat exchanger 1 and the heat exchanger 1 according to the present embodiment.
  • the same reference numerals as those of the joint 20 are assigned. Further, in the following, first, the principle that stress concentration occurs at the relief portion side end portion 24 of the joint 120 according to the comparative example will be described. After that, the reason why the load supported by the partition wall 11 of the heat transfer tube 10 can be reduced as compared with the conventional case by providing the rib 26 will be described.
  • FIG. 8 is a cross-sectional view showing the periphery of the joint of the heat exchanger according to the comparative example.
  • FIG. 8 is a cross-sectional view in which the periphery of the joint 120 according to the comparative example is cut in a virtual plane parallel to the distribution direction X and the lateral direction Z.
  • FIG. 9 is a diagram for explaining the state of the load acting on the portion where the inner peripheral surface of the first insertion port and the outer peripheral surface of the heat transfer tube are brazed and joined in the joint according to the comparative example. .. That is, FIG. 9 is a diagram for explaining the state of the load acting on the joint portion 23 of the joint 120 according to the comparative example.
  • the refrigerant in the joint 120 according to the comparative example is separated from the first member 30 and the second member 40.
  • Pressure 50 acts.
  • the load 51 acts on the joint portion 23 where the inner peripheral surface of the joint 120 and the outer peripheral surface of the heat transfer tube 10 according to the comparative example are brazed and joined.
  • the moment 52 shown in FIG. 8 also acts on the joint portion 23.
  • a load 51 acts on the joint portion 23 as shown in FIG. Specifically, on the end 13 side of the heat transfer tube 10 in the joint portion 23, the load 51 acts in the direction of peeling off the inner peripheral surface of the first insertion port 21 and the outer peripheral surface of the heat transfer tube 10.
  • a load 51 which is a tensile load, acts on the end 13 side of the heat transfer tube 10 at the joint 23.
  • the load 51 is the largest at the relief portion side end portion 24, which is the end portion 13 side of the heat transfer tube 10 most in the joint portion 23. That is, stress concentration occurs at the relief portion side end portion 24 of the joint portion 23.
  • the moment 52 acts on the joint portion 23, the load 51 becomes smaller as the distance from the relief portion side end portion 24 increases, and the direction of the load 51 eventually reverses. That is, the load 51 becomes the compressive load.
  • the compressive strength of the heat exchanger according to the comparative example depends on the thickness of the portion of the partition wall 11 of the heat transfer tube 10 facing the relief portion side end portion 24. That is, in the heat exchanger according to the comparative example, the thickness of the portion of the partition wall 11 of the heat transfer tube 10 facing the relief portion side end portion 24 is set to a thickness that satisfies the withstand voltage strength of the heat exchanger according to the comparative example. There is a need.
  • the flat heat transfer tube 10 is formed by a processing method such as extrusion processing in which the thickness of a part of the partition wall 11 cannot be changed. Therefore, in the heat exchanger according to the comparative example, the partition wall 11 of the heat transfer tube 10 becomes thick.
  • the load 51 acting on the position closest to the end 13 side of the heat transfer tube 10 at the position where the inner peripheral surface of the joint 120 and the outer peripheral surface of the heat transfer tube 10 according to the comparative example are brazed and joined is a moment.
  • the load 51 acting on the position closest to the end 13 side of the heat transfer tube 10 is increased at the portion where the surfaces are brazed and joined.
  • the joint 120 according to the comparative example and the joint 20 according to the present embodiment are observed.
  • the position where the inner peripheral surface of the joint 120 and the outer peripheral surface of the heat transfer tube 10 are brazed and joined to the end 13 side of the heat transfer tube 10 is the relief portion side end. It becomes a part 24.
  • the position where the inner peripheral surface of the joint 20 and the outer peripheral surface of the heat transfer tube 10 are brazed and joined is the position closest to the end 13 side of the heat transfer tube 10. It becomes the joint end portion 27.
  • the distance from the brazed joint between the second insertion port 22 and the circular pipe 4 to the joint end 27 is the escape portion side end from the brazed joint between the second insertion port 22 and the circular pipe 4. It is short compared to the distance to 24. Therefore, the joint 20 according to the present embodiment has a smaller moment 52 than the joint 120 according to the comparative example. Therefore, the load 51 acting on the joint end portion 27 in the joint 20 according to the present embodiment is smaller than the load 51 acting on the relief portion side end portion 24 in the joint 120 according to the comparative example.
  • the joint 20 according to the present embodiment can suppress the load supported by the partition wall 11 of the heat transfer tube 10 as compared with the joint 120 according to the comparative example.
  • the joint 20 according to the present embodiment suppresses the load supported by the partition wall 11 of the heat transfer tube 10 as compared with the conventional heat exchanger in which the brazing material is suppressed from flowing into the flow path of the heat transfer tube. it can. Therefore, in the heat exchanger 1 according to the present embodiment, the partition wall 11 of the heat transfer tube 10 can be made thinner than the heat exchanger according to the comparative example.
  • the partition wall 11 of the heat transfer tube 10 is made thinner than that of the conventional heat exchanger in which the brazing material is prevented from flowing into the flow path of the heat transfer tube. Can be done.
  • the joint 20 according to the present embodiment includes a plurality of ribs 26. By providing the plurality of ribs 26, the number of the joint end portions 27 of the ribs 26 is larger than that in the case where one rib 26 is provided, so that the load supported by the partition wall 11 of the heat transfer tube 10 can be further suppressed.
  • the partition wall 11 of the heat transfer tube 10 can be made thinner.
  • the joint end portion 27 and the end portion 13 of the heat transfer tube 10 are separated from each other. Therefore, in the joint 20 according to the present embodiment, the brazing material flows into the flow path 12 of the heat transfer tube 10 as compared with the conventional heat exchanger in which the brazing material is prevented from flowing into the flow path of the heat transfer tube. It can be suppressed more. The reason for this will be described with reference to FIGS. 10 and 11.
  • FIG. 10 is a plan view showing a heat transfer tube of the heat exchanger according to the comparative example.
  • FIG. 10 shows a cross section of the joint portion 23 of the joint 120 according to the comparative example, which is arranged above the heat transfer tube 10.
  • FIG. 11 is a plan view showing a heat transfer tube of the heat exchanger according to the embodiment. It should be noted that FIG. 11 shows a cross-sectional view of a portion of the joint portion 23 of the joint 20 and the rib 26 of the joint 20 according to the present embodiment, which is joined to the heat transfer tube 10 and is arranged above the heat transfer tube 10. Shown. Further, the black-painted arrow at the tip shown in FIGS. 10 and 11 indicates the flow direction of the brazing material.
  • the end 13 of the heat transfer tube 10 is connected to the brazed portion between the joint 120 and the heat transfer tube 10.
  • the brazing material that protrudes to the side protrudes from the relief portion side end portion 24 of the joint portion 23 to the end portion 13 side of the heat transfer tube 10.
  • the relief portion side end portion 24 has a linear shape substantially parallel to the end portion 13 of the heat transfer tube 10. Therefore, as shown by the black-painted arrow at the tip in FIG. 10, in the joint 120 according to the comparative example, the brazing material protruding from the relief portion side end portion 24 of the joint portion 23 flows in the distribution direction X. That is, in the joint 120 according to the comparative example, the brazing material protruding from the relief portion side end portion 24 of the joint portion 23 flows toward the end portion 13 of the heat transfer tube 10.
  • the heat transfer tube 10 is connected from the brazed portion between the joint 20 and the heat transfer tube 10.
  • the brazing material that protrudes to the end portion 13 side of the heat transfer tube 10 protrudes from the relief portion side end portion 24 of the joint portion 23 to the end portion 13 side of the heat transfer tube 10.
  • the heat transfer tube 10 is connected from the brazed portion between the joint 20 and the heat transfer tube 10.
  • the brazing material that protrudes toward the end 13 side of the rib 26 also protrudes toward the end 13 side of the heat transfer tube 10 from the boundary of the portion of the rib 26 that is joined to the heat transfer tube 10.
  • the brazing portion protruding from the brazed portion between the joint 20 and the heat transfer tube 10 toward the end 13 side of the heat transfer tube 10 A part of the material flows in the longitudinal direction Y from the end side of the rib 26 facing the longitudinal direction Y. Due to this flow of brazing material, the amount of brazing material flowing in the distribution direction X is reduced in the joint 20 according to the present embodiment. Therefore, the joint 20 according to the present embodiment can further suppress the brazing material from flowing into the flow path 12 of the heat transfer tube 10 as compared with the joint 120 according to the comparative example not provided with the rib 26.
  • the brazing material flows into the flow path 12 of the heat transfer tube 10 as compared with the conventional heat exchanger in which the brazing material is prevented from flowing into the flow path of the heat transfer tube. It can be suppressed more.
  • the joint 20 is divided into a first member 30 and a second member 40.
  • the joint 20 may be an integrally formed product.
  • the heat exchanger 1 includes a heat transfer tube 10, a circular tube 4 through which the refrigerant flows, and a joint 20.
  • the heat transfer tube 10 has a flat shape, and the inside is divided into a plurality of flow paths 12 by a partition wall 11.
  • the joint 20 is brazed to the heat transfer tube 10 and the circular tube 4, and connects the heat transfer tube 10 and the circular tube 4.
  • the joint 20 has a first insertion port 21 into which the heat transfer tube 10 is inserted and brazed to the outer peripheral surface of the heat transfer tube 10, and a circular tube 4 is inserted and brazed to the outer peripheral surface of the circular tube 4. It is provided with a second insertion port 22 that is brazed and joined.
  • a relief portion 25 recessed toward the outer peripheral surface of the joint 20 is formed at a position facing the end portion 13 of the heat transfer tube 10. Further, the joint 20 is provided with a rib 26 that protrudes toward the outer peripheral surface of the heat transfer tube 10 and is brazed to the outer peripheral surface of the heat transfer tube 10 at the relief portion 25.
  • the joint 20 of the heat exchanger 1 according to the present embodiment is formed with a relief portion 25 recessed toward the outer peripheral surface of the joint 20 at a position facing the end portion 13 of the heat transfer tube 10. Therefore, the heat exchanger 1 according to the present embodiment can prevent the brazing material from flowing into the flow path 12 of the heat transfer tube 10. Further, the joint 20 of the heat exchanger 1 according to the present embodiment includes a rib 26 in the relief portion 25, which protrudes toward the outer peripheral surface of the heat transfer tube 10 and is brazed to the outer peripheral surface of the heat transfer tube 10. ing. Therefore, the heat exchanger 1 according to the present embodiment has a load supported by the partition wall 11 of the heat transfer tube 10 as compared with the conventional heat exchanger in which the brazing material is prevented from flowing into the flow path of the heat transfer tube. Can be reduced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2019/050891 2019-12-25 2019-12-25 熱交換器 WO2021130917A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2021566649A JP7258185B2 (ja) 2019-12-25 2019-12-25 熱交換器
PCT/JP2019/050891 WO2021130917A1 (ja) 2019-12-25 2019-12-25 熱交換器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/050891 WO2021130917A1 (ja) 2019-12-25 2019-12-25 熱交換器

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WO2021130917A1 true WO2021130917A1 (ja) 2021-07-01

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JP (1) JP7258185B2 (enrdf_load_stackoverflow)
WO (1) WO2021130917A1 (enrdf_load_stackoverflow)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS501957U (enrdf_load_stackoverflow) * 1973-05-04 1975-01-10
JPS58132392U (ja) * 1982-03-02 1983-09-06 東京ラヂエ−タ−製造株式会社 熱交換器のジヨイント装置
JPH08327287A (ja) * 1995-06-05 1996-12-13 Zexel Corp 熱交換器のヘッダ構造
JP2006308144A (ja) * 2005-04-26 2006-11-09 Calsonic Kansei Corp 熱交換器のヘッダタンクとチューブとの接合構造
JP2016038141A (ja) * 2014-08-07 2016-03-22 三菱電機株式会社 熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS501957U (enrdf_load_stackoverflow) * 1973-05-04 1975-01-10
JPS58132392U (ja) * 1982-03-02 1983-09-06 東京ラヂエ−タ−製造株式会社 熱交換器のジヨイント装置
JPH08327287A (ja) * 1995-06-05 1996-12-13 Zexel Corp 熱交換器のヘッダ構造
JP2006308144A (ja) * 2005-04-26 2006-11-09 Calsonic Kansei Corp 熱交換器のヘッダタンクとチューブとの接合構造
JP2016038141A (ja) * 2014-08-07 2016-03-22 三菱電機株式会社 熱交換器

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JP7258185B2 (ja) 2023-04-14
JPWO2021130917A1 (enrdf_load_stackoverflow) 2021-07-01

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