WO2016166963A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2016166963A1
WO2016166963A1 PCT/JP2016/001972 JP2016001972W WO2016166963A1 WO 2016166963 A1 WO2016166963 A1 WO 2016166963A1 JP 2016001972 W JP2016001972 W JP 2016001972W WO 2016166963 A1 WO2016166963 A1 WO 2016166963A1
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WO
WIPO (PCT)
Prior art keywords
sub
flow
guide wall
region
convex
Prior art date
Application number
PCT/JP2016/001972
Other languages
English (en)
Japanese (ja)
Inventor
勇輔 高木
安浩 水野
Original Assignee
株式会社デンソー
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
Priority claimed from JP2016051273A external-priority patent/JP6327271B2/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112016001793.6T priority Critical patent/DE112016001793T5/de
Priority to US15/566,589 priority patent/US10107553B2/en
Priority to CN201680021947.8A priority patent/CN107532865B/zh
Publication of WO2016166963A1 publication Critical patent/WO2016166963A1/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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
    • H01L23/00—Details of semiconductor or other solid state devices
    • H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
    • H01L23/46—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids
    • H01L23/473—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids by flowing liquids

Definitions

  • the present disclosure relates to a heat exchanger having wave fins.
  • a heat exchanger configured by arranging a flow channel so as to sandwich the heating element from both sides.
  • a heat exchanger has a configuration in which heating elements and channel tubes are alternately stacked, and the plurality of stacked channel tubes are communicated by a communication member, and a cooling medium is connected to each channel tube. It is configured to be distributed.
  • a partition member is provided in the flow path pipe, and the heat medium flow path is formed in two stages in the thickness direction of the flow path pipe in one flow path pipe.
  • inner fins are arranged in each of the heat medium flow paths formed in two stages.
  • wave fins are used as parts that increase the heat transfer area.
  • This disclosure aims to improve the thermal performance of the heat exchanger.
  • the heat exchanger according to the first aspect of the present disclosure is formed in a flat shape having a predetermined thickness, and is disposed inside the flow path tube, the flow path pipe through which the heat medium that exchanges heat with the heat exchange object is circulated. And an inner fin that increases the heat transfer area between the heat exchange object and the heat medium.
  • the inner fin includes a wave fin that divides a main flow path through which the heat medium flows into a plurality of sub flow paths, and a guide wall connected to the wave fin.
  • the longitudinal direction of the channel tube is defined as the x direction
  • the thickness direction of the channel tube is defined as the z direction
  • the direction perpendicular to both the x direction and the z direction is defined as the y direction.
  • the wave fin includes a first convex portion that is convex toward the first side in the y direction and a second convex portion that is convex toward the second side in the y direction.
  • the first convex portions and the second convex portions are alternately arranged via the intermediate portion so that the cross-sectional shape perpendicular to the z direction has a wave shape.
  • the wave fin is formed with an opening that connects two sub-channels that are adjacent to each other across the wave fin among the plurality of sub-channels.
  • the guide wall is connected to a portion of the end portion around the opening of the wave fin that is located on the downstream side of the flow of the heat medium in the sub flow channel, and protrudes from the wave fin to the sub flow channel.
  • the front end of the guide wall faces the upstream side of the flow of the heat medium in the sub flow path.
  • a guide wall is connected to the part located in the upstream of the flow of the heat carrier in a subflow path among the edge parts around the opening part of a wavefin, and protrudes from a wave fin to a subflow path.
  • the front end of the guide wall faces the downstream side of the flow of the heat medium in the sub-flow channel.
  • a heat exchanger has a flat shape having a predetermined thickness, and is disposed inside a flow path tube through which a heat medium that exchanges heat with a heat exchange object flows. And an inner fin that increases the heat transfer area between the heat exchange object and the heat medium.
  • the inner fin includes a wave fin that divides a main flow path through which the heat medium flows into a plurality of sub flow paths, and a guide wall connected to the wave fin.
  • the longitudinal direction of the channel tube is defined as the x direction
  • the thickness direction of the channel tube is defined as the z direction
  • the direction perpendicular to both the x direction and the z direction is defined as the y direction.
  • the wave fins include a plurality of first protrusions protruding toward the first side of the flow path tube in the y direction, and a plurality of second protrusions protruding toward the second side of the flow path tube in the y direction. And having.
  • the first protrusions and the second protrusions are alternately arranged so that the cross-sectional shape perpendicular to the z direction has a wave shape.
  • the wave fin has an opening that connects two sub-channels that are adjacent to each other across the wave fin among the plurality of sub-channels.
  • the guide wall protrudes from the end of the wave fin that divides the downstream side or the upstream side of the opening in the flow direction of the heat medium in the secondary channel into the secondary channel.
  • the guide wall is connected to a portion of the end portion around the opening of the wave fin that is located on the downstream side of the flow of the heat medium, and protrudes from the wave fin to the narrow channel, so that the heat medium flowing through the narrow channel is A part flows into the adjacent narrow channel through the opening, and the occurrence of peeling in the vicinity of the wave fin in the narrow channel is suppressed. Therefore, the thermal performance of the heat exchanger can be improved.
  • FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
  • FIG. 3 is a sectional view taken along the line III-III in FIG. 2.
  • FIG. 4 is an arrow view of the flow channel tube in the IV direction of FIG. 2. It is a figure which shows a mode that the inner fin was mounted in the one surface side of the intermediate
  • FIG. 7 is a sectional view taken along line VII-VII in FIG. 3. It is the elements on larger scale of FIG. It is IX-IX sectional drawing of FIG.
  • FIG. 7 is a sectional view taken along line VII-VII in FIG. 3. It is sectional drawing of the wave fin in the heat exchanger which is not provided with an opening part, Comprising: It is a figure corresponded in FIG. It is IX-IX sectional drawing of FIG. It is sectional drawing of the narrow flow path in 2nd Embodiment, Comprising: It is a figure corresponded in FIG.
  • FIG. 1 It is a perspective view of the area
  • FIG. 8 is a cross-sectional view illustrating an arrangement of communication paths in a modified example of the embodiment of the present disclosure, corresponding to FIG. 7.
  • FIG. 8 is a cross-sectional view illustrating an arrangement of communication paths in a modified example of the embodiment of the present disclosure, corresponding to FIG. 7.
  • FIG. 8 is a cross-sectional view illustrating an arrangement of communication paths in a modified example of the embodiment of the present disclosure, corresponding to FIG. 7.
  • FIG. 8 is a cross-sectional view illustrating an arrangement of communication paths in a modified example of the embodiment of the present disclosure, corresponding to FIG. 7. It is sectional drawing of the wave fin in the modification of embodiment of this indication, Comprising: It is a figure corresponded in FIG.
  • FIG. 29 is a cross-sectional view of a narrow channel according to a modification of the embodiment of the present disclosure, corresponding to FIG. 28. It is the elements on larger scale of FIG.
  • FIGS. 1 A first embodiment of the present disclosure will be described with reference to FIGS.
  • the example which comprises the cooler which cools the several electronic component 2 as a heat exchange target object with the laminated heat exchanger 1 of this embodiment is demonstrated.
  • the laminated heat exchanger 1 of this embodiment may be used for other purposes. Moreover, you may use the laminated heat exchanger 1 of this embodiment for a heating.
  • the electronic component 2 is, for example, a power card applied to an inverter circuit that outputs a three-phase AC voltage to a traveling motor.
  • the stacked heat exchanger 1 corresponds to a heat exchanger.
  • the laminated heat exchanger 1 includes a flow path pipe 3 and an inner fin 34 disposed inside the flow path pipe 3. As shown in FIG. 1, the stacked heat exchanger 1 has a plurality of flow channel tubes 3 stacked in a state where electronic components 2 are disposed in a gap formed between adjacent flow channel tubes 3. Configured.
  • the flow path tube 3 is a channel through which a heat medium that exchanges heat with the electronic component 2 circulates.
  • a heat medium for example, water mixed with an ethylene glycol antifreeze, natural refrigerant such as water or ammonia, or the like can be used.
  • a direction perpendicular to the direction in which the flow channel tubes 3 are laminated (lamination direction) and perpendicular to the longitudinal direction of the flow channel tubes 3 is defined as a short direction (second direction) of the flow channel tubes 3.
  • the channel tube 3 has a pair of peripheral edges in the short direction extending in parallel along the longitudinal direction (first direction), and the shape of the peripheral edge in the longitudinal direction is a semicircle. It has a shape.
  • the stacking direction of the channel pipes 3 is defined as the thickness direction (third direction) of the channel pipes 3.
  • the channel tube 3 is formed in a flat shape in which a channel cross section perpendicular to the longitudinal direction has a predetermined thickness.
  • the longitudinal direction of the channel tube 3 corresponds to the x direction.
  • the short direction of the channel tube 3 corresponds to the y direction.
  • the thickness direction of the channel tube 3 corresponds to the z direction.
  • FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1, but the illustration of the electronic component 2 is omitted in order to clarify the shape of the flow path tube 3.
  • FIG. 2 the inner fins 34 arranged inside the flow channel pipe 3 are indicated by dotted lines. 2, 3, 5, and 6, an opening 36 and a guide wall 37 described later are not shown.
  • the flow path pipe 3 is configured by laminating metal plates having high thermal conductivity such as aluminum and copper, and joining these plates. As shown in FIG. 3, the flow channel pipe 3 includes outer shell plates 31 and 32 and an intermediate plate 33.
  • the outer shell plates 31 and 32 are plate members constituting the outer shell of the flow channel tube 3, and heat exchange between the electronic component 2 and the heat medium is performed through the outer shell plates 31 and 32.
  • the intermediate plate 33 is formed of a rectangular plate member, and is disposed between the outer shell plates 31 and 32 so as to face the outer shell plates 31 and 32, respectively. At both ends of the intermediate plate 33 in the longitudinal direction of the flow channel tube 3, circular openings are formed corresponding to the openings of the projecting tube part 35.
  • a medium flow path 30 through which a heat medium flows is formed between the outer shell plates 31 and 32 and the intermediate plate 33.
  • Inner fins 34 are arranged between the outer shell plate 31 and the intermediate plate 33 and between the outer shell plate 32 and the intermediate plate 33.
  • the medium flow path 30 that is the main flow path is divided into a plurality of narrow flow paths (sub flow paths).
  • the inner fin 34 is a component that increases the heat transfer area between the heat medium and the electronic component 2.
  • the inner fin 34 is formed, for example, by pressing a metal plate-like plate having high thermal conductivity such as aluminum.
  • the flow path pipe 3 includes inner fins 34 disposed between the outer shell plate 31 and the intermediate plate 33 and between the outer shell plate 32 and the intermediate plate 33, and the outer periphery of the outer shell plates 31, 32 and the intermediate plate 33. It is comprised by joining the inside of a part with a brazing material.
  • the inner fin 34 is joined to the outer shell plates 31 and 32 by a brazing material.
  • the electronic component 2 when the electronic component 2 is disposed in a gap formed between two adjacent flow channel tubes 3 to configure the stacked heat exchanger 1, the force applied from the outside in the stacking direction is used. It is possible to suppress the deformation of the flow path pipe 3.
  • the peripheral edge of the intermediate plate 33 may be held between the outer shell plates 31 and 32.
  • the stacked heat exchanger 1 includes a protruding tube portion 35.
  • the projecting pipe portion 35 is a pipe that connects adjacent flow path pipes 3.
  • the projecting pipe part 35 opens in the stacking direction of the flow path pipes 3 and protrudes in the stacking direction of the flow path pipes 3. It is said that.
  • the channel pipes 3 other than the channel pipe 3 located on the outermost side in the stacking direction are provided with protruding pipe portions 35 on both sides in the stacking direction.
  • the flow channel tube 3 located on the outermost side in the stacking direction is provided with a protruding tube portion 35 only on one surface facing the adjacent flow channel tubes 3.
  • the plurality of flow path pipes 3 are connected by fitting the protruding pipe parts 35 to each other and joining the side walls of the protruding pipe parts 35 to each other. Thereby, the medium flow path 30 of the adjacent flow path pipe
  • tube 3 is connecting.
  • the supply header part 11 is a pipe that supplies a heat medium to the medium flow path 30 of the flow path pipe 3
  • the discharge header part 12 is a pipe that discharges the heat medium from the medium flow path 30 of the flow path pipe 3.
  • a medium introduction part 4 and a medium outlet part 5 are connected to one of the plurality of flow path pipes 3 arranged on the outermost side in the stacking direction.
  • the medium introducing unit 4 is a pipe for introducing a heat medium into the stacked heat exchanger 1
  • the medium deriving unit 5 is a pipe for deriving the heat medium from the stacked heat exchanger 1.
  • the medium introduction part 4 and the medium lead-out part 5 are joined to the flow channel pipe 3 by a joining technique such as brazing.
  • the stacked heat exchanger 1 includes a medium introducing unit 4 and a medium deriving unit 5.
  • the heat medium is supplied to the stacked heat exchanger 1 through the medium introducing unit 4 and discharged from the stacked heat exchanger 1 through the medium outlet unit 5 by a pump. Further, the heat medium flowing through the stacked heat exchanger 1 has a constant flow rate by a pump.
  • the configuration of the inner fin 34 will be described with reference to FIGS.
  • the inner fin 34 has a plurality of first fins 340 and a plurality of second fins 341. As shown in FIG. 5, among the inner fins 34, the region where the plurality of first fins 340 are formed is the region 34b, the end of the heat medium flow upstream from the region 34b is the end 34a, and the end of the downstream side is the end 34a. Let it be the end 34c.
  • the first fin 340 divides the medium flow path 30, which is the main flow path through which the heat medium flows, into a plurality of narrow flow paths.
  • the region 34 b in which the plurality of first fins 340 are formed has a corrugated cross-sectional shape perpendicular to the longitudinal direction of the flow channel tube 3. The vicinity of the top of the waveform is in contact with the outer shell plates 31 and 32 and the intermediate plate 33.
  • the longitudinal direction may be the same as the flow direction of the heat medium.
  • first fin 340 a portion that is convex in one direction in the thickness direction of the flow path tube 3 and that contacts the outer shell plate 31 or 32 is defined as a top portion 340a.
  • the portion that is convex in the other direction of the thickness direction of the flow channel tube 3 and that contacts the intermediate plate 33 is defined as a bottom portion 340b.
  • a portion of the first fin 340 that connects the top portion 340a and the bottom portion 340b is referred to as a wall surface portion 340c.
  • the regions 34b where the first fins 340 are formed have a cross-sectional shape perpendicular to the longitudinal direction of the flow channel tube 3 because the top portions 340a and the bottom portions 340b are alternately arranged via the wall surface portions 340c. It is made into a shape.
  • the first fin 340 has a configuration in which a bottom portion 340b, a wall surface portion 340c, a top portion 340a, a wall surface portion 340c, and a bottom portion 340b are arranged in this order.
  • the region 34 b in which the plurality of first fins 340 are formed in the inner fin 34 is perpendicular to the longitudinal direction of the flow channel tube 3.
  • a simple cross-sectional shape is a wave shape.
  • the wall surface portion 340c has a plurality of convex portions 340d, concave portions 340e, and intermediate portions 340f.
  • the wall surface portion 340c has a convex shape 340d and a concave portion 340e alternately arranged via an intermediate portion 340f that connects the convex portion 340d and the concave portion 340e, so that the cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 is waved. It is made into a shape.
  • the convex portion 340d has a cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 that is curved toward the first side (one side) in the short direction of the flow channel tube 3, and the concave portion 340e is The cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 is a curved shape that is convex toward the second side (the other side) in the short direction of the flow channel tube 3.
  • the convex portion 340d and the concave portion 340e correspond to a first convex portion and a second convex portion, respectively.
  • the intermediate portion 340f has a straight cross-sectional shape perpendicular to the thickness direction of the flow path tube 3.
  • the wall surface portion 340c By forming the wall surface portion 340c with the convex portion 340d, the recess portion 340e, and the intermediate portion 340f, the wall surface portion 340c has a triangular wave shape in the longitudinal direction of the flow channel tube 3 when viewed from the thickness direction of the flow channel tube 3. It has a bent shape.
  • the wall surface portion 340c corresponds to a wave fin.
  • the second fin 341 forms a narrow channel together with the first fin 340, and is formed at the end 34a and the end 34c so as to be parallel to the longitudinal direction of the channel tube 3.
  • the second fin 341 has a linear shape when viewed from the thickness direction of the flow path tube 3.
  • the end 34 a and the end 34 c of the inner fin 34 where the second fin 341 is formed have a corrugated cross-sectional shape perpendicular to the longitudinal direction of the flow channel tube 3.
  • one continuous fin is constituted by the second fin 341 formed at the end 34a, the first fin 340, and the second fin 341 formed at the end 34c.
  • the wall surface portion 340c is formed with a plurality of openings 36 for connecting two adjacent narrow channels with the wall surface portion 340c interposed therebetween.
  • the opening 36 is formed in a portion extending from the convex portion 340d to the intermediate portion 340f and a portion extending from the concave portion 340e to the intermediate portion 340f.
  • a guide wall 37 is connected to the wall surface part 340 c, and the inner fin 34 also has a guide wall 37.
  • the guide wall 37 is for improving heat transfer by the leading edge effect and for suppressing the occurrence of peeling by guiding the heat medium to the adjacent narrow channel.
  • the guide wall 37 is connected to the downstream side of the flow of the heat medium in one of the two narrow channels of the two narrow channels connected by the opening 36 in the end portion around the opening 36 of the wall surface portion 340c.
  • the guide wall 37 protrudes from the wall surface part 340c to one narrow flow path, and the tip thereof faces the upstream side of the flow of the heat medium.
  • the inner fin 34 has a plurality of guide walls 37, and the guide walls 37 are arranged corresponding to the plurality of openings 36.
  • the convex portion 340d and the guide wall 37, and the concave portion 340e and the guide wall 37 are smoothly connected.
  • the end portion of the guide wall 37 other than the end portion facing the flow of the heat medium is connected to the top portion 340a, the bottom portion 340b, or the wall surface portion 340c.
  • openings 36 and guide walls 37 can be formed by press working that simultaneously cuts a plate-like plate that is the material of the inner fin 34 and bends the cut portion.
  • the part that is upstream of the medium flow channel 30 after processing becomes a part of the first fin 340 and the part that is downstream is from the first fin 340.
  • the guide wall 37 is raised (separated).
  • a portion surrounded by the boundary between the guide wall 37 and the first fin 340 and the portion remaining on the first fin 340 side in the side surface of the cut portion is an opening 36.
  • the opening 36 and the guide wall 37 may be formed by making a cut in a plate-like plate as a material for the inner fin 34 and pressing the cut plate.
  • the heat medium flows in a direction facing the tip of the guide wall 37.
  • the guide wall 37 has a convex portion of the concave portion 340 e in the region R ⁇ b> 1 where the heat medium flows from the convex portion 340 d toward the concave portion 340 e when the thermal medium flows in a direction facing the tip of the guide wall 37. It protrudes from the wall surface part 340c to the side.
  • the guide wall 37 is a second side in the short direction of the flow channel tube 3.
  • the guide wall 37 protrudes from the wall surface part 340c on the convex side of the convex part 340d in the region R2 where the heat medium flows from the concave part 340e toward the convex part 340d.
  • the guide wall 37 may protrude from the wall surface part 340c to the second side in the short direction of the flow channel pipe 3 in the region R2 in which the heat medium flows from the concave part 340e toward the convex part 340d. Note that the heat medium flows from the left side to the right side in FIG.
  • the flow remaining in the same narrow channel without being guided to the adjacent narrow channel by the guide wall 37 is the main flow, and the flow guided to the adjacent narrow channel by the guide wall 37 is the split flow. Then, the cross-sectional area of the main flow channel is larger than the cross-sectional area of the diverted flow channel.
  • the straight line L1 in FIG. 7 indicates a plane perpendicular to the flow direction of the heat medium in the main flow, passing through the tip of the guide wall 37 facing the flow of the heat medium.
  • the straight line L2 indicates a plane that passes through the tip of the guide wall 37 that faces the flow of the heat medium and is perpendicular to the flow direction of the heat medium in the divided flow.
  • the cross-sectional area of the main flow path is surrounded by the top portion 340a or the bottom portion 340b, the wall surface portion 340c, the guide wall 37, and the outer shell plates 31, 32 or the intermediate plate 33 in the plane indicated by the straight line L1.
  • the flow path cross-sectional area of the divided flow is defined as an area of a portion surrounded by the wall surface portion 340c, the guide wall 37, and the top portion 340a or the bottom portion 340b in the plane indicated by the straight line L2.
  • the guide wall 37 protrudes into area
  • region R4 of one narrow channel among two narrow channels adjacent on both sides of the wall surface part 340c the guide wall 37 protrudes into area
  • the region R3 is a region having a narrower width than a predetermined width formed in the narrow channel when the width of the narrow channel in the short direction of the channel tube 3 changes in the thickness direction of the channel tube 3. is there.
  • the region R4 is a region having a width wider than a predetermined width formed in the narrow channel when the width of the narrow channel in the short direction of the channel tube 3 changes in the thickness direction of the channel tube 3.
  • the inner fin 34 is manufactured by pressing a metal plate-like plate. Therefore, among the narrow channels surrounded by the top portion 340a, the wall surface portion 340c, and the intermediate plate 33, the width w1 in the short direction of the channel tube 3 in the region on the top portion 340a side is larger than the width w2 in the region on the intermediate plate 33 side. small. Of the narrow channels surrounded by the bottom portion 340b, the wall surface portion 340c, and the outer shell plate 31 or the outer shell plate 32, the width w3 in the short direction of the flow channel 3 in the region on the bottom portion 340b side is the outer shell. It is smaller than the width w4 of the region on the plate 31 or outer shell plate 32 side.
  • the distance from the top 340a and the distance from the bottom 340b are equal to each other in the thickness direction of the channel tube 3, and are located on both sides of a plane perpendicular to the thickness direction of the channel tube 3.
  • the regions are referred to as regions R3 and R4, respectively.
  • the width (corresponding to the above-mentioned predetermined width) of the portion where the distance from the top portion 340a and the distance from the bottom portion 340b are equal to each other in the thickness direction of the flow path tube 3 is defined as w5.
  • the width of the region R3 is smaller than the width w5, and the width of the region R4 is larger than the width w5.
  • the region R3 is a region sandwiched between this flat surface and the top portion 340a or the bottom portion 340b in the narrow channel.
  • the region R4 is a region sandwiched between the flat surface and the outer shell plates 31, 32 or the intermediate plate 33 in the narrow channel.
  • a straight line L3 in FIG. 9 indicates the boundary between the region R3 and the region R4. Regions R3 and R4 correspond to a first region and a second region, respectively.
  • the heat medium flows into the flow path pipe 3 directly from the medium introduction section 4 or through the supply header section 11 and directly into the flow path pipe 3 or through the discharge header section 12 to the medium outlet section 5.
  • the electronic component 2 is cooled by heat exchange between the electronic component 2 and the heat medium.
  • the heat medium meanders and flows through a plurality of wave-shaped narrow channels.
  • 10 and 11 are cross-sectional views of a heat exchanger that does not include the opening 36.
  • the front end of the guide wall 37 faces the upstream side of the flow of the heat medium.
  • the heat medium when the heat medium meanders and flows as shown by the arrow A1 in FIG. 11, the heat medium may be peeled off. As shown by a region R5 in FIG. 11, when the heat medium passes through the curve formed by the two convex portions 340d or the two concave portions 340e, the separation occurs in the vicinity of the wall surface portion 340c that is the inner side of the curve. There is a fear.
  • the peeled portion has a slow flow and contributes less to heat transfer promotion than the fast flowing portion. Further, the pressure loss in the flow channel pipe 3 may increase due to the occurrence of peeling. Therefore, there is a possibility that the performance of the heat exchanger is deteriorated due to the occurrence of peeling.
  • the opening 36 is formed, and the guide wall 37 is connected to a portion located on the downstream side of the flow of the heat medium in the end portion around the opening 36 of the wall surface portion 340c. Further, the guide wall 37 protrudes from one of the two narrow channels adjacent to the wall surface 340c from the wall surface 340c. Therefore, a part of the meandering flow indicated by the arrow A2 in FIG. 12 is a part of the wall surface part 340c, which is a part where peeling occurs when the opening part 36 is not formed through the opening part 36 as indicated by the arrow A3. It flows into the vicinity and the occurrence of peeling at this portion is suppressed.
  • a region R6 in FIG. 12 is a portion where peeling occurs in the present embodiment, and is smaller than the region R5 where peeling occurs when the opening 36 is not formed.
  • the occurrence of peeling is suppressed, the area of the portion contributing to heat transfer among the portions where the inner fin 34 and the heat medium are in contact is increased, and the increase in pressure loss is suppressed. Is done. Thereby, the thermal performance of a heat exchanger improves.
  • the cross-sectional area of the main stream is larger than the cross-sectional area of the shunt flow as described above, the flow rate of the main stream that continues to flow through the same narrow channel without passing through the opening 36 passes through the opening 36.
  • the main flow meandering flow is maintained because the flow rate is larger than the flow rate of the divided flow flowing into the adjacent narrow channel.
  • the inner fin 34 can be further enhanced in heat transfer by forming the opening 36 and the guide wall 37. And the heat performance (heat exchange amount) of the heat exchanger can be improved.
  • the flow speed is slower in the region having a short width in the short direction compared to the region having a narrow width in the short direction, and the peeling portion is not shown in the region R7 in FIG. large.
  • the temperature of the heat medium is higher in a region where the width in the short direction is wide than in a region where the width in the short direction is narrow.
  • the velocity distribution and temperature of the heat medium can be obtained by flowing a heat medium that passes through a narrow area in the short direction into a wide area in the short direction of adjacent narrow channels. It can effectively improve the distribution and improve the heat performance of the heat exchanger.
  • the guide wall 37 projects into one narrow channel region R3 of two adjacent narrow channels, and the heat medium is supplied to the other narrow channel region as indicated by an arrow A4 in FIG. Guide to R4. Therefore, the velocity distribution and temperature distribution of the heat medium are improved, and the occurrence of peeling is suppressed.
  • a region R8 in FIG. 14 is a portion where peeling occurs in the present embodiment, and is smaller than the region R7 where peeling occurs when the opening 36 is not formed. Thereby, the thermal performance of the heat exchanger can be further improved.
  • the guide wall 37 is arranged as described above to efficiently suppress the occurrence of peeling, thereby largely suppressing the increase in pressure loss, thereby suppressing the occurrence of peeling.
  • An increase in pressure loss in the entire exchanger can be suppressed, and the thermal performance of the heat exchanger can be further improved.
  • the guide wall 37 protrudes into the region R3 where the width in the short direction is narrow and the flow velocity of the heat medium is large.
  • the guide wall 37 may be formed in a portion where the flow rate of the heat medium is maximum in each narrow channel. Therefore, since a heat medium collides with the front-end
  • peeling is particularly likely to occur in the portion included in the region R4 inside the convex portion 340d and the concave portion 340e. Therefore, you may arrange
  • the opening 36 is formed in the convex portion 340d and the concave portion 340e.
  • the guide wall 37 corresponding to the opening 36 formed in the convex portion 340d is connected to the convex portion 340d and protrudes from the wall surface portion 340c to the convex side of the convex portion 340d.
  • the guide wall 37 corresponding to the opening portion 36 formed in the convex portion 340d may protrude from the wall surface portion 340c to the first side in the short direction.
  • the guide wall 37 corresponding to the opening 36 formed in the recess 340e is connected to the recess 340e and protrudes from the wall surface 340c on the convex side of the recess 340e.
  • the guide wall 37 corresponding to the opening 36 formed in the recess 340e may protrude from the wall surface part 340c to the second side in the short side direction.
  • the guide wall 37 is arranged such that the distance d1 is larger than the distance d2 in at least a part of the cross section perpendicular to the thickness direction of the flow path tube 3.
  • the wall surface portion 340c includes one convex portion 340d, one intermediate portion 340f directly connected to one convex portion 340d, one concave portion 340e directly connected to one intermediate portion 340f, and the concave portion It has a portion (first continuous portion) composed of one guide wall 37 directly connected to 340e.
  • the distance d1 is between the portion located on the outermost side on the first side and the portion located on the outermost side on the second side, on the first side surface in the short direction of the flow path pipe 3 of the first continuous portion. This is the distance in the short direction of the flow path tube 3.
  • the distance in the short direction of the flow path tube 3 is also d1.
  • the wall surface portion 340c is composed of one convex portion 340d, one intermediate portion 340f directly connected to one convex portion 340d, and one concave portion 340e directly connected to one intermediate portion 340f. It has a part (second continuous part).
  • the distance d2 is between the portion located on the outermost side on the first side and the portion located on the outermost side on the second side on the surface on the first side in the short direction of the flow path pipe 3 of the second continuous portion. This is the distance in the short direction of the flow path tube 3.
  • the distance in the short direction of the flow path tube 3 is also d2.
  • the wall surface portion 340c includes one of the convex portions 340d, one of the intermediate portions 340f directly connected to the single convex portion 340d, and one of the concave portions 340e directly connected to the single intermediate portion 340f. And a portion (third continuous portion) constituted by the guide wall 37 directly connected to the convex portion 340d.
  • d3 d1
  • d3 d2
  • a region R9 in FIG. 17 is a portion where peeling occurs in the present embodiment, and is smaller than the region R5 where peeling occurs when the opening 36 is not formed.
  • the effect of the wave fin of improving the thermal performance of a heat exchanger by lengthening the flow path of the heat medium in the flow path pipe 3 and increasing the local flow velocity can be further enhanced. it can.
  • the fins are cut and raised to promote turbulence.
  • the cut-and-raised part is formed to escape the meandering refrigerant flow, and the meandering flow that is characteristic of the wave fins is disrupted. Cannot be obtained.
  • the guide wall 37 corresponding to the opening 36 formed in the convex portion 340d protrudes from the wall surface portion 340c on the convex side of the convex portion 340d.
  • a guide wall 37 corresponding to the opening 36 formed in the recess 340e protrudes from the wall surface part 340c on the convex side of the recess 340e.
  • the guide wall 37 corresponding to the opening 36 formed in the convex portion 340d may protrude from the wall surface portion 340c to the first side in the short direction, and the guide wall 37 corresponding to the opening 36 formed in the concave portion 340e is You may protrude from the wall surface part 340c to the 2nd side of a short direction.
  • the guide wall 37 has distances d1 and d3 larger than the distance d2 in at least a part of a cross section perpendicular to the thickness direction of the inner fin 34 in the portion constituted by the wall surface portion 340c and the guide wall 37. It is arranged to be.
  • the depth of the meandering flow of the heat medium is larger than when the guide wall 37 is not formed. That is, when the dimensions of the inner fin 34 and the flow rate of the heat medium passing through the inner fin 34 are constant, in this embodiment, the meandering flow is deepened, the flow path is substantially lengthened, and the local flow velocity is increased.
  • the thermal performance of the heat exchanger can be further improved.
  • the depth of the meandering flow of the heat medium may be the amount of movement of the meandering flow of the heat medium in the short direction. That is, the deep meandering flow may mean that the amount of movement of the meandering flow in the short direction is large.
  • the depth of the meandering flow of the heat medium may be the amplitude of the meandering flow of the heat medium in the short direction. That is, the deep meandering flow may mean that the amplitude of the meandering flow in the short direction is large.
  • the heat medium flows in the opposite direction to the first embodiment.
  • the guide wall 37 is a flow of the heat medium in one of the two narrow channels connected by the opening 36 in the end portion around the opening 36 of the wall surface portion 340c. Connected upstream.
  • the guide wall 37 protrudes from the wall surface part 340c to one narrow flow path, and the tip thereof faces the downstream side of the flow of the heat medium.
  • the heat medium flows from the region R4 to the region R3 through the opening 36, and the velocity distribution and the temperature distribution of the heat medium are similar to those in the first embodiment. Improved. Accordingly, as shown in FIGS. 18 and 19, the regions R10 and R11 where peeling occurs in this embodiment are smaller than the regions R5 and R7 where peeling occurs when the opening 36 is not formed. Thus, also in this embodiment, generation
  • the main flow indicated by the arrow A7 in FIG. 18 is pulled to the outside of the curve by the diversion indicated by the arrow A8, and the meandering flow becomes deeper than that in the first embodiment. Therefore, the thermal performance of the heat exchanger can be further improved by increasing the local flow rate.
  • the deep meandering flow may mean that the amount of movement of the meandering flow in the short direction is large.
  • the heat medium flows in a direction opposite to that of the second embodiment, and the tip of the guide wall 37 faces the downstream side of the flow of the heat medium.
  • the main flow indicated by the arrow A10 in FIG. 20 is pulled to the outside of the curve by the branch flow indicated by the arrow A11, and the meandering flow becomes deeper than that in the second embodiment.
  • produces in this embodiment becomes smaller than area
  • the local flow velocity increases due to the deep meandering flow. Therefore, the thermal performance of the heat exchanger can be further improved.
  • the deep meandering flow may mean that the amount of movement of the meandering flow in the short direction is large.
  • the openings 36 are formed in all the wall surfaces 340c.
  • the openings 36 may be formed only in some of the wall surfaces 340c.
  • the wall surface portion 340 c in which the opening portion 36 is formed and the wall surface portion 340 c in which the opening portion 36 is not formed may be alternately arranged.
  • the opening 36 is formed in the region R1 and the region R2, but the opening 36 may be formed only in the region R1 or only in the region R2. Further, whether the opening 36 is formed in the region R1 and the region R2, only the region R1, or only the region R2 may be changed in each of the plurality of wall surfaces 340c. For example, as shown in FIG. 23, the wall surface portion 340c in which the opening 36 is formed only in the region R1 and the wall surface portion 340c formed only in the region R2 may be alternately arranged.
  • the opening 36 is formed in the convex portion 340d and the concave portion 340e.
  • the opening 36 may be formed only in the convex portion 340d or only in the concave portion 340e.
  • the wall surface portion 340c in which the opening 36 is formed only in the convex portion 340d and the wall surface portion 340c formed only in the concave portion 340e may be alternately arranged.
  • the flow path pipe 3 includes the outer shell plates 31 and 32 and the intermediate plate 33, but the flow path pipe 3 may not include the intermediate plate 33. . Further, only one inner fin 34 may be disposed in the flow path pipe 3.
  • the guide wall 37 protrudes into the region R3 and guides the heat medium to the region R4 of the adjacent narrow channel.
  • a part of the guide wall 37 protrudes into the region R4 and transfers the heat medium.
  • the area is made larger than the area of the portion (second part) connecting the region R4 of one narrow channel and the region R3 of the other narrow channel. That is, the channel cross-sectional area in the branch flow region R3 is larger than the channel cross-sectional area in the region R4, and the geometric center P1 of the flow channel cross-section in the branch flow exists in the region R3.
  • the shapes of the opening 36 and the guide wall 37 may be different from those of the first to fourth embodiments.
  • the electronic component 2 By arranging the electronic component 2 in a gap formed between two adjacent flow channel tubes 3 to constitute the stacked heat exchanger 1, a force is applied to the flow channel tube 3 from the outside in the stacking direction. .
  • the guide wall 37 is bent as shown in FIG. 25, stress concentrates on the bent portion 37a, so that the inner fin 34 and the flow channel tube 3 are easily deformed. Therefore, the opening 36 and the guide wall 37 may be shaped so that stress is not easily concentrated on the guide wall 37, and the buckling strength of the guide wall 37 may be increased.
  • the cross-sectional shape of the opening 36 is triangular as in the first to fourth embodiments, or the cross-sectional shape of the opening 36 is trapezoidal as shown in FIG.
  • the cross-sectional shape perpendicular to the longitudinal direction may be a straight line connecting the top portion 340a and the bottom portion 340b.
  • the shape of the convex portion 340d and the concave portion 340e may be other shapes.
  • the shape of the portion located on both sides of the opening 36 in the convex portion 340d is linear, and flat with the intermediate portion 340f.
  • a smooth surface may be formed.
  • the heat medium may smoothly flow from the narrow channel to the adjacent narrow channel. Therefore, as in the second and fourth embodiments, the portion of the channel tube 3 in the portion from the end opposite to the guide wall 37 to the intermediate portion 340f among the ends around the opening 36 of the convex portion 340d.
  • the cross-sectional shape perpendicular to the thickness direction may be rounded so as to be convex toward the convex side of the convex portion 340d. Thereby, as shown by arrow A12 in FIG. 28, the heat medium smoothly flows into the adjacent narrow channel.
  • the cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 in the portion extending from the end on the opposite side of the guide wall 37 to the intermediate portion 340f among the ends around the opening 36 of the recess 340e is formed in the recess 340e. It is good also as a rounded shape so that it may become convex toward the convex side.
  • the cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 in the portion extending from the end opposite to the guide wall 37 to the intermediate portion 340f among the ends around the opening 36 of the convex portion 340d is It is good also as a rounded shape so that it may become convex toward the 1st side.
  • the cross-sectional shape perpendicular to the thickness direction of the flow channel tube 3 in the portion from the end opposite to the guide wall 37 to the intermediate portion 340f among the ends around the opening 36 of the recess 340e is a short direction. It is good also as a rounded shape so that it may become convex toward the 2nd side.
  • the width of the opening 36 may be large.
  • the width w7 of the opening 36 is the width of the opening 36 in FIG. 27 due to the rounded shape of the convex part 340d and the part extending from the concave part 340e to the intermediate part 340f. It is made larger than w6, and the above effect can be enhanced.
  • the inner fin 34 is formed with the opening 36 in the first embodiment and the wall surface 340c to which the guide wall 37 is connected, and the opening 36 in the second embodiment is formed and the guide wall 37 is connected.
  • You may have the wall surface part 340c.
  • the opening part 36 in 1st Embodiment may be formed in the one wall part 340c, the guide wall 37 may be connected, the opening part 36 in 2nd Embodiment may be formed, and the guide wall 37 may be connected. .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Condensed Matter Physics & Semiconductors (AREA)
  • Geometry (AREA)
  • General Physics & Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Power Engineering (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

La présente invention concerne un échangeur de chaleur équipé: d'un tube de canalisation (3) conformé en une forme plate ayant une épaisseur prédéterminée, un fluide caloporteur pour un échange thermique avec un objet avec lequel un échange de chaleur est effectué en étant circulé à travers l'intérieur du tube de canalisation (3); et des ailettes internes (34) disposées dans le tube de canalisation. Les ailettes intérieures ont des ailettes ondulées (340c) pour diviser un canal principal en une pluralité de canaux secondaires, et des parois de guidage (37) raccordées aux ailettes ondulées. La direction longitudinale du tube de canalisation est définie comme la direction x, la direction de l'épaisseur du canal tube est définie comme la direction z, et la direction perpendiculaire à la direction x et la direction z est définie comme la direction y. Les ailettes ondulées comprennent des premières parties convexes (340d) formées de manière à présenter un bombement vers l'extérieur vers un premier côté dans la direction y, et secondes parties convexes (340e) formée de manière à présenter un renflement vers l'extérieur vers un second côté dans la direction y. Des parties d'ouverture (36) reliant deux canaux secondaires adjacents sont formés dans les ailettes ondulées. Les parois de guidage font saillie depuis des ailettes ondulées vers des canaux secondaires. Cet échangeur de chaleur permet de favoriser le transfert de chaleur et d'améliorer la performance thermique de l'échangeur de chaleur.
PCT/JP2016/001972 2015-04-17 2016-04-11 Échangeur de chaleur WO2016166963A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112016001793.6T DE112016001793T5 (de) 2015-04-17 2016-04-11 Wärmetauscher
US15/566,589 US10107553B2 (en) 2015-04-17 2016-04-11 Heat exchanger
CN201680021947.8A CN107532865B (zh) 2015-04-17 2016-04-11 热交换器

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2015085241 2015-04-17
JP2015-085241 2015-04-17
JP2016-051273 2016-03-15
JP2016051273A JP6327271B2 (ja) 2015-04-17 2016-03-15 熱交換器

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WO2016166963A1 true WO2016166963A1 (fr) 2016-10-20

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018074121A (ja) * 2016-11-04 2018-05-10 株式会社デンソー 積層型熱交換器
JP2018109476A (ja) * 2017-01-05 2018-07-12 株式会社ユタカ技研 熱交換器
JP2020092263A (ja) * 2018-11-22 2020-06-11 株式会社Ｓｏｋｅｎ 電子部品冷却装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63189784A (ja) * 1987-01-14 1988-08-05 マーストン・パルマー・リミテッド 熱交換器
JPH0732377U (ja) * 1993-10-29 1995-06-16 株式会社土屋製作所 熱交換器の伝熱フィン
JP2002350083A (ja) * 2001-05-22 2002-12-04 Calsonic Kansei Corp 熱交換器用インナーフィン
JP2009204182A (ja) * 2008-02-26 2009-09-10 Denso Corp 熱交換器
JP2012017943A (ja) * 2010-07-09 2012-01-26 Denso Corp オイルクーラ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63189784A (ja) * 1987-01-14 1988-08-05 マーストン・パルマー・リミテッド 熱交換器
JPH0732377U (ja) * 1993-10-29 1995-06-16 株式会社土屋製作所 熱交換器の伝熱フィン
JP2002350083A (ja) * 2001-05-22 2002-12-04 Calsonic Kansei Corp 熱交換器用インナーフィン
JP2009204182A (ja) * 2008-02-26 2009-09-10 Denso Corp 熱交換器
JP2012017943A (ja) * 2010-07-09 2012-01-26 Denso Corp オイルクーラ

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018074121A (ja) * 2016-11-04 2018-05-10 株式会社デンソー 積層型熱交換器
JP2018109476A (ja) * 2017-01-05 2018-07-12 株式会社ユタカ技研 熱交換器
JP2020092263A (ja) * 2018-11-22 2020-06-11 株式会社Ｓｏｋｅｎ 電子部品冷却装置
JP7336368B2 (ja) 2018-11-22 2023-08-31 株式会社Soken 電子部品冷却装置

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