WO2017115436A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
WO2017115436A1
WO2017115436A1 PCT/JP2015/086562 JP2015086562W WO2017115436A1 WO 2017115436 A1 WO2017115436 A1 WO 2017115436A1 JP 2015086562 W JP2015086562 W JP 2015086562W WO 2017115436 A1 WO2017115436 A1 WO 2017115436A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat
heat exchange
wavy
lines
Prior art date
Application number
PCT/JP2015/086562
Other languages
French (fr)
Japanese (ja)
Inventor
潤 柳本
直毅 鹿園
パスカル ツァイゼ
庸人 和氣
Original Assignee
国立大学法人東京大学
有限会社和氣製作所
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 国立大学法人東京大学, 有限会社和氣製作所 filed Critical 国立大学法人東京大学
Priority to JP2017558830A priority Critical patent/JPWO2017115436A1/en
Priority to PCT/JP2015/086562 priority patent/WO2017115436A1/en
Priority to CN201580085593.9A priority patent/CN108700384A/en
Priority to US16/066,887 priority patent/US20180372425A1/en
Priority to EP15912102.9A priority patent/EP3399268A4/en
Publication of WO2017115436A1 publication Critical patent/WO2017115436A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • 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
    • F28F3/04—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
    • F28F3/042—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 in the form of local deformations of the element
    • F28F3/046—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 in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being 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
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element

Definitions

  • the present invention relates to a heat exchanger, and more particularly to a heat exchanger that performs heat exchange by flowing a fluid over the surface of a heat transfer member.
  • an angle formed with respect to the main flow of air on a flat surface of a flat tubular heat exchange tube is a predetermined angle within a range of 10 degrees to 60 degrees.
  • corrugation which has a peak part and a trough part so that it may fold back symmetrically by the folding line of the predetermined space
  • the wavy unevenness of this heat exchanger has a shape in which peaks (convex parts) and troughs (concave parts) of the wavy unevenness are connected in a V shape (or W shape).
  • the heat exchanger of the present invention increases the yield of the heat transfer member when the amplitude of the wavy unevenness of the heat transfer member is the same, and increases the wavy amplitude of the heat transfer member when the yield of the heat transfer member is the same.
  • the main purpose is to make it larger.
  • the heat exchanger of the present invention employs the following means in order to achieve the main object described above.
  • the heat exchanger of the present invention is A heat exchanger that exchanges heat by flowing a fluid over the surface of a heat transfer member,
  • the fluid side surface has wavy irregularities with a smooth curve, and the top line where the top of the wave continues and the bottom line where the bottom of the wave continues connect the V-shape in the horizontal direction.
  • the bent portion is formed so as to be curved, and the main flow of the fluid is formed in a V-shaped vertical direction. It is characterized by that.
  • the surface of the heat transfer member on the fluid side has wavy irregularities with a smooth curve, and the top line where the top of the wave continues and the bottom line where the bottom of the wave continues are V-shaped.
  • the bent part is curved, that is, two V-shaped lines are connected in a horizontal direction to form a W-shaped line.
  • corrugation is formed so that the main flow of the fluid may become a V-shaped perpendicular direction (up-down direction).
  • the top line and the bottom line may be formed so as to alternately connect straight portions and arc portions.
  • the minimum radius of the bent portion can be increased as compared with the case where the top line and the bottom line are formed by a sine curve.
  • the yield of the heat transfer member can be further increased when the amplitude of the wavy unevenness of the heat transfer member is the same, and the heat transfer When the yield of the members is the same, the amplitude of the wavy unevenness of the heat transfer member can be increased.
  • the circular arc part may be formed so that the radius is 1/5 or more of the length of the linear part.
  • the wavy unevenness may be formed such that the cross section is alternately continuous with straight lines and arcs. In this way, the amplitude of the wavy unevenness can be increased compared with the case where the cross section of the wavy unevenness is formed by a sine curve, and the heat transfer efficiency of the heat exchanger can be further improved.
  • FIG. 2 is a sectional view showing an AA section in FIG. 1. It is explanatory drawing which shows the outline of a structure of the heat exchanger 920 of a comparative example.
  • FIG. 1 is an explanatory view showing an outline of the configuration of a heat exchanger 20 as one embodiment of the present invention
  • FIG. 2 shows the appearance of a plurality of heat exchange tubes 30 used in the heat exchanger 20 of the embodiment from the side.
  • FIG. FIG. 3 is a cross-sectional view showing the AA cross section in FIG.
  • FIG. 4 is an explanatory diagram showing an outline of the configuration of the heat exchanger 920 of the comparative example.
  • the heat exchanger 20 according to the embodiment includes a plurality of heat exchange tubes 30 arranged in parallel so that the longitudinal direction is the vertical direction, and a shell that houses the plurality of heat exchange tubes 30. 50.
  • Each heat exchange tube 30 is formed by pressing so as to be a flat hollow tube having a substantially rectangular shape as a whole using a plate material made of a metal material (for example, stainless steel or aluminum), and the longitudinal direction is the vertical direction. The contact points are joined by brazing.
  • the inlet 31 formed in the vicinity of the lower end in the vertical direction of each heat exchange tube 30 is joined to the inlet 31 of the adjacent heat exchange tube 30 by stacking the heat exchange tubes 30.
  • a communication pipe 31 a communicating with 31 is formed.
  • the outlet 32 formed in the vicinity of the upper upper end of each heat exchanging tube 30 is similar to the inflow port 31 by stacking the respective heat exchanging tubes 30 to allow the flow of the adjacent heat exchanging tubes 30 to flow.
  • a connecting pipe 32 a that is joined to the outlet 32 and communicates with each outlet 32 is formed. Therefore, the first heat exchange medium such as water or oil flows in from the inlet 31 of each heat exchange tube 30, flows vertically upward, and flows out from the outlet 32 of each heat exchange tube 30.
  • the first heat exchange medium such as water or oil flows in from the inlet 31 of each heat exchange tube 30, flows vertically upward, and flows out from the outlet 32 of each heat exchange tube 30.
  • the shell 50 is a substantially rectangular parallelepiped shape that houses a plurality of heat exchange tubes 30 connected by connecting pipes 31 a and 32 a by a plate material made of a metal material (for example, stainless steel or aluminum). It is formed as a case.
  • An inflow port 51 is formed above the shell 50, and an outflow port 52 is formed below the shell 50. Therefore, the second heat exchange medium such as air or exhaust gas flows from the inlet 51 formed above the shell 50, passes between the plurality of heat exchange tubes 30, and flows below the shell 50. It flows out from the outlet 52.
  • a plurality of wavy irregularities 34 and 36 are formed on both flat surfaces 33 and 35 of each heat exchange tube 30 by smooth curved surfaces.
  • FIG. 1 the wavy unevenness 34 of the flat surface 33 on one side of both flat surfaces 33, 35 of the heat exchange tube 30 is shown, and the flat surface 35 on the other side (the flat surface on the back side in FIG. 1).
  • the wavy irregularities 36 are parenthesized.
  • the wavy irregularities 34 and 36 have V-shaped (or W) alternating top lines 34a and 36a in which the tops of the waves indicated by a plurality of solid lines continue and bottom lines 34b and 36b in which the bottoms indicated by a plurality of broken lines continue.
  • the top of the wave means the position of 90 degrees when the convex part and the concave part of the wave are indicated by a sine wave, that is, the position of the maximum value (the top of the convex part).
  • It means a position of 270 degrees when the wave convex part and the concave part are indicated by a sine wave, that is, the position of the minimum value (the bottom of the concave part).
  • the main flow of the second heat exchange medium is at its angle (angle in the range of 30 to 60 degrees) in the V-shaped (or W-shaped) shaded portions of the top lines 34a and 36a and the bottom lines 34b and 36b. It will cross at.
  • the top lines 34a, 36a and the bottom lines 34b, 36b are formed on both flat surfaces 33, 35 of each heat exchange tube 30 so as to form a shape in which V-shaped (or W-shaped) are connected in the horizontal direction.
  • the secondary flow means a flow that flows along the surfaces of the wave-like irregularities 34 and 36 effective for heat exchange, and is different from a vortex flow or a stirring flow.
  • the top lines 34a and 36a and the bottom lines 34b and 36b are formed so that straight portions 34c and 36c formed by straight lines and arc portions 34d and 36d formed by circular arcs are alternately continued.
  • the radius of the arc portions 34d and 36d is set to 1/5 or more of the length of the straight portions 34c and 36c. In this way, the V-shaped (or W-shaped) bent portion is formed into an arc (curve) as shown in the heat exchanger 920 of the comparative example of FIG.
  • the heat exchanging tube 30 of the embodiment has a higher yield in the press working when the amplitudes of the wavy irregularities 34 and 36 are the same as the heat exchanging tube 930 of the heat exchanger 920 of the comparative example.
  • the amplitude of the wavy irregularities 34 and 36 can be increased when the yield during pressing is the same.
  • the wavy irregularities 34 and 36 of the embodiment are formed so that straight lines and arcs are alternately continued, and the top and bottom of the arc are the top lines 34a and 36a and the bottom. Lines 34b and 36b are formed.
  • the wavy irregularities 34 and 36 are formed so that the cross-sections are alternately continuous with straight lines and arcs, as compared with the case where the cross-sections are formed into sinusoidal curves. This is because the minimum radius can be increased and thereby the amplitude can be increased.
  • the wavy unevenness 34 of the flat surface 33 on one side and the wavy unevenness 36 of the flat surface 35 on the other side are parallel to each other, that is, the flat surface 33 of the one side.
  • the top line 34a of the wavy uneven surface 34 and the bottom line 36b of the wavy uneven surface 36 of the flat surface 35 on the other side are aligned, and the wavy surface of the bottom line 34b of the wavy uneven surface 34 of the flat surface 33 on the one side and the flat surface 35 on the other side. It arrange
  • the top lines 34a and 36a and the bottom lines 34b and 36b are alternately V-shaped on the both flat surfaces 33 and 35 of the heat exchange tube 30 as wavy irregularities 34 and 36.
  • the top line 934a, 936a and the bottom line 934b, 936b are bent by forming the V-shaped (or W-shaped) bent portion so as to form a shape in which the W-shaped shape is connected in the horizontal direction.
  • the amplitude of the wavy unevenness 34 and 36 is increased.
  • the yield during press working can be increased, and when the yield during press working is the same, the amplitudes of the wavy irregularities 34 and 36 can be increased.
  • the top lines 34a and 36a and the bottom lines 34b and 36b are formed so that the straight portions 34c and 36c and the arc portions 34d and 36d are alternately continued, the top and bottom lines are formed as sinusoidal curves.
  • the minimum radius of the bent portion can be increased, and the stress concentration generated in the bent portion during press working can be reduced.
  • the yield at the time of pressing can be further increased, and when the yield at the time of the pressing is the same, the amplitude of the wavy irregularities 34 and 36 is further increased. can do.
  • top lines 34a, 36a and the bottom lines 34b, 36b are formed on both flat surfaces 33, 35 of the heat exchanging tube 30 so as to form a V-shaped (or W-shaped) line in the horizontal direction.
  • a secondary flow effective for heat exchange can be generated on the surfaces of the irregularities 34 and 36, and a heat exchanger with high heat exchange efficiency can be obtained.
  • the wavy irregularities 34 and 36 are formed so that the cross sections thereof are alternately continuous with straight lines and arcs, the minimum radii of the top and bottom of the wave are compared with the case where the cross sections are formed to be sinusoidal. Can be increased, whereby the amplitude can be increased. Thereby, it can be set as a heat exchanger with still higher heat exchange efficiency.
  • the wavy irregularities 34 and 36 are formed so that the top lines 34a and 36a and the bottom lines 34b and 36b are alternately continuous with the straight portions 34c and 36c and the arc portions 34d and 36d. Since the top line and the bottom line may be formed so that the bent part of the V-shaped (or W-shaped) is curved, the top line and the bottom line are formed so that the S-shaped curved part and the arc part are alternately continued. Alternatively, the top line and the bottom line may be formed so that the sine curve is continuous.
  • the first heat exchange medium and the second heat exchange medium are counterflowed, but the first heat exchange medium and the second heat exchange medium are orthogonally flowed.
  • one or both of the first heat exchange medium and the second heat exchange medium may be bypassed.
  • the present invention has been described as an example in which the present invention is applied to the heat exchange tube of the finless heat exchanger 20, but may be applied to a fin such as a corrugated fin heat exchanger.
  • a fin such as a corrugated fin heat exchanger.
  • the top line and the bottom line are alternately V-shaped (or W-shaped) and V-shaped (or W-shaped). Further, it may be formed so that the main flow of the fluid flowing through the fins is in a V-shaped vertical direction so that the bent portion of the fin is curved.
  • the present invention can be used in the heat exchanger manufacturing industry.

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

Abstract

This heat exchanger is equipped with heat exchanger tubes 30 each with both flat surfaces 33 and 35 thereof formed with wavelike recessed and protruding portions 34 , 36. The wavelike recessed and protruding portions 34 , 36 are formed with top lines 34a , 36a and bottom lines 34b , 36b alternating with each other. The top lines 34a , 36a and the bottom lines 34b , 36b each have a shape such that V shapes are horizontally connected, each of the V shapes having a curved bending portion. Thus, it is possible to reduce stress concentration on the bending portions during press processing compared to heat exchanger tubes that have the V shapes of top lines and bottom lines horizontally connected to have acute-angled bending portions. As a result, when the amplitudes of the wavelike recessed and protruding portions 34 , 36 are made equal, the yields during press processing can be enhanced, and when the yields during press processing are made equal, the amplitudes of the wavelike recessed and protruding portions 34 , 36 can be increased .

Description

熱交換器Heat exchanger
　本発明は、熱交換器に関し、詳しくは、伝熱部材の表面に流体を流すことにより熱交換を行なう熱交換器に関する。 The present invention relates to a heat exchanger, and more particularly to a heat exchanger that performs heat exchange by flowing a fluid over the surface of a heat transfer member.
　従来、この種の熱交換器としては、偏平な管状の熱交換用チューブの偏平面に空気の主要な流れに対してなす角が１０度から６０度の範囲のうちの所定角となるように、かつ、空気の主要な流れに沿った所定間隔の折り返し線で対称に折り返すよう山部と谷部とを有する波状の凹凸を有するものが提案されている（例えば、特許文献１参照）。この熱交換器の波状の凹凸は、波状の凹凸の山部（凸部）や谷部（凹部）はＶ字（或いはＷ字）を連ねた形状となっており、このように波状の凹凸を形成することにより、空気の主要な流れに対して波状の凹凸の表面に沿って流れる二次流れを生じさせ、熱交換器の熱交換効率を向上させている。 Conventionally, in this type of heat exchanger, an angle formed with respect to the main flow of air on a flat surface of a flat tubular heat exchange tube is a predetermined angle within a range of 10 degrees to 60 degrees. And what has the wavy unevenness | corrugation which has a peak part and a trough part so that it may fold back symmetrically by the folding line of the predetermined space | interval along the main flow of air is proposed (for example, refer patent document 1). The wavy unevenness of this heat exchanger has a shape in which peaks (convex parts) and troughs (concave parts) of the wavy unevenness are connected in a V shape (or W shape). By forming, the secondary flow which flows along the surface of a wavy unevenness | corrugation with respect to the main flow of air is produced, and the heat exchange efficiency of a heat exchanger is improved.
特開２００８－２３２５９２号公報JP 2008-232592 A
　上述の熱交換器では、熱交換効率を向上させるために波状の凹凸の振幅（頂部と底部の高低差）を大きくすることが望まれるが、波状の凹凸の振幅を大きくすると、熱交換用チューブをプレス加工により形成する場合には、波状の凹凸の山部（凸部）や谷部（凹部）を連ねたＶ字（或いはＷ字）の屈曲部に応力集中による破損が生じ、熱交換用チューブの歩留まりが低くなってしまう。 In the above heat exchanger, it is desirable to increase the amplitude of the wavy unevenness (the difference in height between the top and the bottom) in order to improve the heat exchange efficiency, but if the amplitude of the wavy unevenness is increased, the heat exchange tube Is formed by press working, damage due to stress concentration occurs at the V-shaped (or W-shaped) bent portion connecting the ridges (convex portions) and valleys (concave portions) of wavy irregularities, and is used for heat exchange. Tube yield will be low.
　本発明の熱交換器は、伝熱部材の波状の凹凸の振幅を同一としたときには伝熱部材の歩留まりをより高くし、伝熱部材の歩留まりを同一としたときには伝熱部材の波状の振幅をより大きくすることを主目的とする。 The heat exchanger of the present invention increases the yield of the heat transfer member when the amplitude of the wavy unevenness of the heat transfer member is the same, and increases the wavy amplitude of the heat transfer member when the yield of the heat transfer member is the same. The main purpose is to make it larger.
　本発明の熱交換器は、上述の主目的を達成するために以下の手段を採った。 The heat exchanger of the present invention employs the following means in order to achieve the main object described above.
　本発明の熱交換器は、
　伝熱部材の表面に流体を流すことにより熱交換を行なう熱交換器であって、
　前記伝熱部材には、前記流体側の表面に、滑らかな曲線による波状の凹凸が、波の頂部が連続する頂部線と波の底部が連続する底部線とがＶ字を水平方向に連ねて屈曲部が曲線となるように形成されていると共に前記流体の主要な流れがＶ字の垂直方向となるように形成されている、
　ことを特徴とする。 The heat exchanger of the present invention is
A heat exchanger that exchanges heat by flowing a fluid over the surface of a heat transfer member,
In the heat transfer member, the fluid side surface has wavy irregularities with a smooth curve, and the top line where the top of the wave continues and the bottom line where the bottom of the wave continues connect the V-shape in the horizontal direction. The bent portion is formed so as to be curved, and the main flow of the fluid is formed in a V-shaped vertical direction.
It is characterized by that.
　この本発明の熱交換器では、伝熱部材の流体側の表面には、滑らかな曲線による波状の凹凸が、波の頂部が連続する頂部線と波の底部が連続する底部線とがＶ字を水平方向に連ねて屈曲部が曲線となるように、即ち、Ｖ字を水平方向に２つ連ねてＷ字となるように更に連続して連ねるように形成されている。そして、この波状の凹凸は、流体の主要な流れがＶ字の垂直方向（上下方向）となるように形成されている。頂部線と底部線とのＶ字の屈曲部（Ｗ字の屈曲部）を曲線となるようにすることにより、屈曲部の応力集中を小さくすることができる。この結果、伝熱部材の波状の凹凸の振幅を同一としたときには伝熱部材の歩留まりをより高くすることができ、伝熱部材の歩留まりを同一としたときには伝熱部材の波状の凹凸の振幅をより大きくすることができる。もとより、本発明の熱交換器では、伝熱部材の流体側の表面には、滑らかな曲線による波状の凹凸がＶ字を連ねた形状として形成されているから、流体の主要な流れに対して伝熱部材の波状の凹凸の表面に沿って滑らかに流れる二次流れを生じさせ、熱交換器の伝熱効率を向上させることができる。 In the heat exchanger of the present invention, the surface of the heat transfer member on the fluid side has wavy irregularities with a smooth curve, and the top line where the top of the wave continues and the bottom line where the bottom of the wave continues are V-shaped. Are bent in a horizontal direction so that the bent part is curved, that is, two V-shaped lines are connected in a horizontal direction to form a W-shaped line. And this wavy unevenness | corrugation is formed so that the main flow of the fluid may become a V-shaped perpendicular direction (up-down direction). By making the V-shaped bent portion (W-shaped bent portion) of the top line and the bottom line into a curved line, the stress concentration of the bent portion can be reduced. As a result, when the amplitude of the wavy unevenness of the heat transfer member is the same, the yield of the heat transfer member can be further increased, and when the yield of the heat transfer member is the same, the amplitude of the wavy unevenness of the heat transfer member is increased. Can be larger. Of course, in the heat exchanger according to the present invention, the surface of the heat transfer member on the fluid side is formed with wave-like irregularities by a smooth curve in a shape of V-shaped, so that the main flow of fluid The secondary flow which flows smoothly along the surface of the wavy unevenness | corrugation of a heat-transfer member can be produced, and the heat-transfer efficiency of a heat exchanger can be improved.
　こうした本発明の熱交換器において、前記頂部線および前記底部線は、直線部と円弧部とを交互に接続するように形成されているものとすることもできる。こうすれば、頂部線と底部線とを正弦曲線により形成する場合に比して、屈曲部の最小半径を大きくすることができる。この結果、頂部線と底部線とを正弦曲線により形成する場合に比して、伝熱部材の波状の凹凸の振幅を同一としたときには伝熱部材の歩留まりをより高くすることができ、伝熱部材の歩留まりを同一としたときには伝熱部材の波状の凹凸の振幅をより大きくすることができる。この場合、前記円弧部は、半径が前記直線部の長さの１／５以上となるよう形成されているものとすることもできる。 In such a heat exchanger according to the present invention, the top line and the bottom line may be formed so as to alternately connect straight portions and arc portions. In this case, the minimum radius of the bent portion can be increased as compared with the case where the top line and the bottom line are formed by a sine curve. As a result, compared to the case where the top line and the bottom line are formed by a sine curve, the yield of the heat transfer member can be further increased when the amplitude of the wavy unevenness of the heat transfer member is the same, and the heat transfer When the yield of the members is the same, the amplitude of the wavy unevenness of the heat transfer member can be increased. In this case, the circular arc part may be formed so that the radius is 1/5 or more of the length of the linear part.
　また、本発明の熱交換器において、前記波状の凹凸は、断面が直線と円弧とを交互に連続するように形成されているものとすることもできる。こうすれば、波状の凹凸の断面を正弦曲線により形成する場合に比して、波状の凹凸の振幅を大きくすることができ、熱交換器の伝熱効率を更に向上させることができる。 Further, in the heat exchanger of the present invention, the wavy unevenness may be formed such that the cross section is alternately continuous with straight lines and arcs. In this way, the amplitude of the wavy unevenness can be increased compared with the case where the cross section of the wavy unevenness is formed by a sine curve, and the heat transfer efficiency of the heat exchanger can be further improved.
　本発明の熱交換器において、前記伝熱部材は扁平な中空管として形成された熱交換用チューブであり、前記波状の凹凸は前記熱交換用チューブの扁平面に形成されているものとすることもできる。即ち、フィンレスの熱交換器に適用してもよいのである。また、本発明の熱交換器において、前記伝熱部材は、熱交換用チューブに連結されたフィンであるものとすることもできる。即ち、コルゲートフィン型の熱交換器などに適用してもよいのである。 In the heat exchanger of the present invention, the heat transfer member is a heat exchange tube formed as a flat hollow tube, and the wavy unevenness is formed on a flat surface of the heat exchange tube. You can also. That is, it may be applied to a finless heat exchanger. In the heat exchanger according to the present invention, the heat transfer member may be a fin connected to a heat exchange tube. That is, the present invention may be applied to a corrugated fin type heat exchanger.
本発明の一実施例としての熱交換器２０の構成の概略を示す説明図である。It is explanatory drawing which shows the outline of a structure of the heat exchanger 20 as one Example of this invention. 実施例の熱交換器２０に用いる複数の熱交換用チューブ３０の外観を側面から示す側面図である。It is a side view which shows the external appearance of the several tube 30 for heat exchange used for the heat exchanger 20 of an Example from the side. 図１中のＡ－Ａ断面を示す断面図である。FIG. 2 is a sectional view showing an AA section in FIG. 1. 比較例の熱交換器９２０の構成の概略を示す説明図である。It is explanatory drawing which shows the outline of a structure of the heat exchanger 920 of a comparative example.
　次に、本発明を実施するための形態を実施例を用いて説明する。 Next, modes for carrying out the present invention will be described using examples.
　図１は本発明の一実施例としての熱交換器２０の構成の概略を示す説明図であり、図２は実施例の熱交換器２０に用いる複数の熱交換用チューブ３０の外観を側面から示す側面図である。図３は、図１中のＡ－Ａ断面を示す断面図である。図４は、比較例の熱交換器９２０の構成の概略を示す説明図である。実施例の熱交換器２０は、図１に示すように、長手方向が鉛直方向となるように並列に配置した複数の熱交換用チューブ３０と、この複数の熱交換用チューブ３０を収納するシェル５０と、を備える。 FIG. 1 is an explanatory view showing an outline of the configuration of a heat exchanger 20 as one embodiment of the present invention, and FIG. 2 shows the appearance of a plurality of heat exchange tubes 30 used in the heat exchanger 20 of the embodiment from the side. FIG. FIG. 3 is a cross-sectional view showing the AA cross section in FIG. FIG. 4 is an explanatory diagram showing an outline of the configuration of the heat exchanger 920 of the comparative example. As shown in FIG. 1, the heat exchanger 20 according to the embodiment includes a plurality of heat exchange tubes 30 arranged in parallel so that the longitudinal direction is the vertical direction, and a shell that houses the plurality of heat exchange tubes 30. 50.
　各熱交換用チューブ３０は、金属材料（例えば、ステンレスやアルミニウムなど）による板材を用いて全体として略矩形形状の扁平な中空管となるようプレス加工により形成され、長手方向が鉛直方向となるように積層され、接触点がロウ付けにより接合されて構成されている。各熱交換用チューブ３０の鉛直下方の下端近傍に形成された流入口３１は、各熱交換用チューブ３０を積層することにより隣接する熱交換用チューブ３０の流入口３１と接合され、各流入口３１を連通する連絡管３１ａを形成する。また、各熱交換用チューブ３０の鉛直上方の上端近傍に形成された流出口３２も、流入口３１と同様に、各熱交換用チューブ３０を積層することにより隣接する熱交換用チューブ３０の流出口３２と接合され、各流出口３２を連通する連絡管３２ａを形成する。したがって、水やオイルなどの第１熱交換媒体は、各熱交換用チューブ３０の流入口３１から流入して鉛直上方に流れ、各熱交換用チューブ３０の流出口３２から流出する。 Each heat exchange tube 30 is formed by pressing so as to be a flat hollow tube having a substantially rectangular shape as a whole using a plate material made of a metal material (for example, stainless steel or aluminum), and the longitudinal direction is the vertical direction. The contact points are joined by brazing. The inlet 31 formed in the vicinity of the lower end in the vertical direction of each heat exchange tube 30 is joined to the inlet 31 of the adjacent heat exchange tube 30 by stacking the heat exchange tubes 30. A communication pipe 31 a communicating with 31 is formed. Further, the outlet 32 formed in the vicinity of the upper upper end of each heat exchanging tube 30 is similar to the inflow port 31 by stacking the respective heat exchanging tubes 30 to allow the flow of the adjacent heat exchanging tubes 30 to flow. A connecting pipe 32 a that is joined to the outlet 32 and communicates with each outlet 32 is formed. Therefore, the first heat exchange medium such as water or oil flows in from the inlet 31 of each heat exchange tube 30, flows vertically upward, and flows out from the outlet 32 of each heat exchange tube 30.
　シェル５０は、各熱交換用チューブ３０と同様に、金属材料（例えば、ステンレスやアルミニウムなど）による板材により、連絡管３１ａ，３２ａにより連結された複数の熱交換用チューブ３０を収納する略直方体形状のケースとして形成されている。シェル５０の上方には流入口５１が形成されており、シェル５０の下方には流出口５２が形成されている。したがって、空気や排ガスなどの第２熱交換媒体は、シェル５０の上方に形成された流入口５１から流入し、複数の熱交換用チューブ３０の間を通り、シェル５０の下方に形成された流出口５２から流出する。 Similarly to each heat exchange tube 30, the shell 50 is a substantially rectangular parallelepiped shape that houses a plurality of heat exchange tubes 30 connected by connecting pipes 31 a and 32 a by a plate material made of a metal material (for example, stainless steel or aluminum). It is formed as a case. An inflow port 51 is formed above the shell 50, and an outflow port 52 is formed below the shell 50. Therefore, the second heat exchange medium such as air or exhaust gas flows from the inlet 51 formed above the shell 50, passes between the plurality of heat exchange tubes 30, and flows below the shell 50. It flows out from the outlet 52.
　各熱交換用チューブ３０の両扁平面３３，３５には、滑らかな曲面により複数の波状凹凸３４，３６が形成されている。図１では、熱交換用チューブ３０の両扁平面３３，３５のうちの一方側の扁平面３３の波状凹凸３４を示しており、他方側の扁平面３５（図１中裏面側の扁平面）の波状凹凸３６については括弧書きとした。波状凹凸３４，３６は、複数の実線で示す波の頂部が連続する頂部線３４ａ，３６ａと、複数の破線で示す底部が連続する底部線３４ｂ，３６ｂと、が交互に共にＶ字（或いはＷ字）を水平方向に連ねた形状となるように且つＶ字（或いはＷ字）の屈曲部が曲線となるように形成されている。ここで、波の頂部は、波の凸部と凹部とが正弦波で示されたときの９０度の位置、即ち最大値の位置（凸部の頂）を意味しており、波の底部は、波の凸部と凹部とが正弦波で示されたときの２７０度の位置、即ち最小値の位置（凹部の底）を意味している。上述したように、複数の熱交換用チューブ３０の間を通る第２熱交換媒体は、シェル５０の上方に形成された流入口５１から流入し、シェル５０の下方に形成された流出口５２から流出するから、第２熱交換媒体の主流の流れは頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂのＶ字（或いはＷ字）の斜線部ではその角度（３０度～６０度の範囲の角度）で交差することになる。このように、各熱交換用チューブ３０の両扁平面３３，３５に頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂがＶ字（或いはＷ字）を水平方向に連ねた形状となるように形成するのは、第２熱交換媒体を流したときに、第２熱交換媒体の主要な流れの他に熱交換に有効な二次流れを生じさせるためである。ここで、二次流れは、熱交換に有効な波状凹凸３４，３６の表面に沿って流れる流れを意味しており、渦流や攪拌流とは異なる。 A plurality of wavy irregularities 34 and 36 are formed on both flat surfaces 33 and 35 of each heat exchange tube 30 by smooth curved surfaces. In FIG. 1, the wavy unevenness 34 of the flat surface 33 on one side of both flat surfaces 33, 35 of the heat exchange tube 30 is shown, and the flat surface 35 on the other side (the flat surface on the back side in FIG. 1). The wavy irregularities 36 are parenthesized. The wavy irregularities 34 and 36 have V-shaped (or W) alternating top lines 34a and 36a in which the tops of the waves indicated by a plurality of solid lines continue and bottom lines 34b and 36b in which the bottoms indicated by a plurality of broken lines continue. Are bent in a horizontal direction, and the bent portion of the V-shape (or W-shape) is curved. Here, the top of the wave means the position of 90 degrees when the convex part and the concave part of the wave are indicated by a sine wave, that is, the position of the maximum value (the top of the convex part). , It means a position of 270 degrees when the wave convex part and the concave part are indicated by a sine wave, that is, the position of the minimum value (the bottom of the concave part). As described above, the second heat exchange medium passing between the plurality of heat exchange tubes 30 flows from the inlet 51 formed above the shell 50 and from the outlet 52 formed below the shell 50. Therefore, the main flow of the second heat exchange medium is at its angle (angle in the range of 30 to 60 degrees) in the V-shaped (or W-shaped) shaded portions of the top lines 34a and 36a and the bottom lines 34b and 36b. It will cross at. In this way, the top lines 34a, 36a and the bottom lines 34b, 36b are formed on both flat surfaces 33, 35 of each heat exchange tube 30 so as to form a shape in which V-shaped (or W-shaped) are connected in the horizontal direction. This is because when the second heat exchange medium is flowed, a secondary flow effective for heat exchange is generated in addition to the main flow of the second heat exchange medium. Here, the secondary flow means a flow that flows along the surfaces of the wave- like irregularities 34 and 36 effective for heat exchange, and is different from a vortex flow or a stirring flow.
　実施例では、頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂは、直線により形成された直線部３４ｃ，３６ｃと円弧により形成された円弧部３４ｄ、３６ｄとが交互に連続するように形成されている。実施例では、円弧部３４ｄ、３６ｄの半径としては直線部３４ｃ，３６ｃの長さの１／５以上とした。このように、Ｖ字（或いはＷ字）の屈曲部を円弧（曲線）となるように形成するのは、図４の比較例の熱交換器９２０に示すように、熱交換用チューブ９３０の両扁平面９３３，９３５に波状凹凸９３４，９３６を頂部線９３４ａ，９３６ａおよび底部線９３４ｂ，９３６ｂが屈曲部が鋭角のＶ字（或いはＷ字）を水平方向に連ねた形状となるように形成した場合に比して、プレス加工の際に屈曲部に生じる応力集中を小さくするためである。プレス加工の際に屈曲部に生じる応力集中は、屈曲部の最小半径が小さくなるほど大きくなり、波状凹凸３４，３６の振幅が大きくなるほど大きくなる。また、応力集中が大きいほど、クラックが生じやすくなる。この結果、実施例の熱交換用チューブ３０は、比較例の熱交換器９２０の熱交換用チューブ９３０に比して、波状凹凸３４，３６の振幅を同一としたときにはプレス加工の際の歩留まりを高くすることができ、プレス加工の際の歩留まりを同一としたときには波状凹凸３４，３６の振幅を大きくすることができる。 In the embodiment, the top lines 34a and 36a and the bottom lines 34b and 36b are formed so that straight portions 34c and 36c formed by straight lines and arc portions 34d and 36d formed by circular arcs are alternately continued. . In the embodiment, the radius of the arc portions 34d and 36d is set to 1/5 or more of the length of the straight portions 34c and 36c. In this way, the V-shaped (or W-shaped) bent portion is formed into an arc (curve) as shown in the heat exchanger 920 of the comparative example of FIG. When wavy irregularities 934 and 936 are formed on the flat surfaces 933 and 935 so that the top lines 934a and 936a and the bottom lines 934b and 936b have V-shaped (or W-shaped) whose bent portions are connected in the horizontal direction. This is because the stress concentration generated in the bent portion during press working is reduced as compared with the above. The stress concentration generated in the bent portion during the press working increases as the minimum radius of the bent portion decreases, and increases as the amplitude of the wavy irregularities 34 and 36 increases. Moreover, the greater the stress concentration, the easier it is for cracks to occur. As a result, the heat exchanging tube 30 of the embodiment has a higher yield in the press working when the amplitudes of the wavy irregularities 34 and 36 are the same as the heat exchanging tube 930 of the heat exchanger 920 of the comparative example. The amplitude of the wavy irregularities 34 and 36 can be increased when the yield during pressing is the same.
　実施例の波状凹凸３４，３６は、その断面は、図３に示すように、直線と円弧とが交互に連続するように形成されており、円弧の頂部および底部が頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂを形成する。このように、波状凹凸３４，３６を断面が直線と円弧とが交互に連続するように形成するのは、断面が正弦曲線となるように形成する場合に比して、波の頂部や底部の最小半径を大きくすることができ、これにより振幅を大きくすることができるからである。 As shown in FIG. 3, the wavy irregularities 34 and 36 of the embodiment are formed so that straight lines and arcs are alternately continued, and the top and bottom of the arc are the top lines 34a and 36a and the bottom. Lines 34b and 36b are formed. In this way, the wavy irregularities 34 and 36 are formed so that the cross-sections are alternately continuous with straight lines and arcs, as compared with the case where the cross-sections are formed into sinusoidal curves. This is because the minimum radius can be increased and thereby the amplitude can be increased.
　なお、実施例の熱交換用チューブ３０では、一方側の扁平面３３の波状凹凸３４と他方側の扁平面３５の波状凹凸３６とが平行になるように、即ち、一方側の扁平面３３の波状凹凸３４の頂部線３４ａと他方側の扁平面３５の波状凹凸３６の底部線３６ｂとが整合すると共に一方側の扁平面３３の波状凹凸３４の底部線３４ｂと他方側の扁平面３５の波状凹凸３６の頂部線３６ａとが整合するように配置した。 In the heat exchanging tube 30 of the embodiment, the wavy unevenness 34 of the flat surface 33 on one side and the wavy unevenness 36 of the flat surface 35 on the other side are parallel to each other, that is, the flat surface 33 of the one side. The top line 34a of the wavy uneven surface 34 and the bottom line 36b of the wavy uneven surface 36 of the flat surface 35 on the other side are aligned, and the wavy surface of the bottom line 34b of the wavy uneven surface 34 of the flat surface 33 on the one side and the flat surface 35 on the other side. It arrange | positions so that the top line 36a of the unevenness | corrugation 36 may align.
　以上説明した実施例の熱交換器２０では、熱交換用チューブ３０の両扁平面３３，３５に波状凹凸３４，３６として、頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂが交互に共にＶ字（或いはＷ字）を水平方向に連ねた形状となるように且つＶ字（或いはＷ字）の屈曲部が曲線となるように形成することにより、頂部線９３４ａ，９３６ａおよび底部線９３４ｂ，９３６ｂが屈曲部が鋭角のＶ字（或いはＷ字）を水平方向に連ねた形状となるように形成した比較例の熱交換器９２０の熱交換用チューブ９３０に比して、波状凹凸３４，３６の振幅を同一としたときにはプレス加工の際の歩留まりを高くすることができ、プレス加工の際の歩留まりを同一としたときには波状凹凸３４，３６の振幅を大きくすることができる。しかも、頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂを直線部３４ｃ，３６ｃと円弧部３４ｄ、３６ｄとが交互に連続するように形成したから、頂部線および底部線を正弦曲線として形成するものに比して、屈曲部の最小半径を大きくすることができ、プレス加工の際に屈曲部に生じる応力集中を小さくすることができる。これにより、波状凹凸３４，３６の振幅を同一としたときにはプレス加工の際の歩留まりを更に高くすることができ、プレス加工の際の歩留まりを同一としたときには波状凹凸３４，３６の振幅を更に大きくすることができる。 In the heat exchanger 20 of the embodiment described above, the top lines 34a and 36a and the bottom lines 34b and 36b are alternately V-shaped on the both flat surfaces 33 and 35 of the heat exchange tube 30 as wavy irregularities 34 and 36. Alternatively, the top line 934a, 936a and the bottom line 934b, 936b are bent by forming the V-shaped (or W-shaped) bent portion so as to form a shape in which the W-shaped shape is connected in the horizontal direction. Compared with the heat exchange tube 930 of the heat exchanger 920 of the comparative example in which the portion is formed so as to form a shape in which the V-shaped (or W-shaped) portion having an acute angle is connected in the horizontal direction, the amplitude of the wavy unevenness 34 and 36 is increased. When they are the same, the yield during press working can be increased, and when the yield during press working is the same, the amplitudes of the wavy irregularities 34 and 36 can be increased. Moreover, since the top lines 34a and 36a and the bottom lines 34b and 36b are formed so that the straight portions 34c and 36c and the arc portions 34d and 36d are alternately continued, the top and bottom lines are formed as sinusoidal curves. In comparison, the minimum radius of the bent portion can be increased, and the stress concentration generated in the bent portion during press working can be reduced. As a result, when the amplitudes of the wavy irregularities 34 and 36 are the same, the yield at the time of pressing can be further increased, and when the yield at the time of the pressing is the same, the amplitude of the wavy irregularities 34 and 36 is further increased. can do.
　もとより、熱交換用チューブ３０の両扁平面３３，３５に頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂがＶ字（或いはＷ字）を水平方向に連ねた形状となるように形成するから、波状凹凸３４，３６の表面に第２熱交換媒体の主要な流れの他に熱交換に有効な二次流れを生じさせることができ、高い熱交換効率の熱交換器とすることができる。さらに、波状凹凸３４，３６をその断面が直線と円弧とが交互に連続するように形成するから、断面が正弦曲線となるように形成する場合に比して、波の頂部や底部の最小半径を大きくすることができ、これにより振幅を大きくすることができる。これにより、更に熱交換効率の高い熱交換器とすることができる。 Of course, since the top lines 34a, 36a and the bottom lines 34b, 36b are formed on both flat surfaces 33, 35 of the heat exchanging tube 30 so as to form a V-shaped (or W-shaped) line in the horizontal direction. In addition to the main flow of the second heat exchange medium, a secondary flow effective for heat exchange can be generated on the surfaces of the irregularities 34 and 36, and a heat exchanger with high heat exchange efficiency can be obtained. Further, since the wavy irregularities 34 and 36 are formed so that the cross sections thereof are alternately continuous with straight lines and arcs, the minimum radii of the top and bottom of the wave are compared with the case where the cross sections are formed to be sinusoidal. Can be increased, whereby the amplitude can be increased. Thereby, it can be set as a heat exchanger with still higher heat exchange efficiency.
　実施例の熱交換器２０では、波状凹凸３４，３６を頂部線３４ａ，３６ａおよび底部線３４ｂ，３６ｂを直線部３４ｃ，３６ｃと円弧部３４ｄ、３６ｄとが交互に連続するように形成したが、頂部線および底部線がＶ字（或いはＷ字）の屈曲部が曲線となるように形成すればよいから、頂部線および底部線をＳ字曲線部と円弧部とが交互に連続するように形成したり、頂部線および底部線を正弦曲線が連続するように形成したりしても構わない。 In the heat exchanger 20 of the example, the wavy irregularities 34 and 36 are formed so that the top lines 34a and 36a and the bottom lines 34b and 36b are alternately continuous with the straight portions 34c and 36c and the arc portions 34d and 36d. Since the top line and the bottom line may be formed so that the bent part of the V-shaped (or W-shaped) is curved, the top line and the bottom line are formed so that the S-shaped curved part and the arc part are alternately continued. Alternatively, the top line and the bottom line may be formed so that the sine curve is continuous.
　実施例の熱交換器２０では、波状凹凸３４，３６をその断面が直線と円弧とが交互に連続するように形成したが、その断面がＳ字曲線部と円弧部とが交互に連続するように形成したり、その断面が正弦曲線が連続するように形成したりしてもよい。 In the heat exchanger 20 of the embodiment, the wavy irregularities 34 and 36 are formed so that the cross sections thereof are alternately continuous with straight lines and arcs, but the cross sections thereof are alternately continuous with the S-curve portions and the arc portions. The cross section may be formed so that the sinusoidal curve is continuous.
　実施例の熱交換器２０では、第１熱交換媒体と第２熱交換媒体とを対向流とするものとしたが、第１熱交換媒体と第２熱交換媒体とを直交流とするものとしてもよいし、第１熱交換媒体や第２熱交換媒体の一方または双方が迂流するようにしても構わない。 In the heat exchanger 20 of the embodiment, the first heat exchange medium and the second heat exchange medium are counterflowed, but the first heat exchange medium and the second heat exchange medium are orthogonally flowed. Alternatively, one or both of the first heat exchange medium and the second heat exchange medium may be bypassed.
　実施例では、本発明をフィンレスの熱交換器２０の熱交換用チューブに適用した一例として説明したが、コルゲートフィン型熱交換器などのフィンに適用してもよい。この場合、フィンに、滑らかな曲線による波状の凹凸として、頂部線および底部線が交互に共にＶ字（或いはＷ字）を水平方向に連ねた形状となるように且つＶ字（或いはＷ字）の屈曲部が曲線となるように、更に、フィンに流れる流体の主要な流れがＶ字の垂直方向となるように形成すればよい。 In the embodiment, the present invention has been described as an example in which the present invention is applied to the heat exchange tube of the finless heat exchanger 20, but may be applied to a fin such as a corrugated fin heat exchanger. In this case, as a wave-like unevenness with a smooth curve on the fin, the top line and the bottom line are alternately V-shaped (or W-shaped) and V-shaped (or W-shaped). Further, it may be formed so that the main flow of the fluid flowing through the fins is in a V-shaped vertical direction so that the bent portion of the fin is curved.
　以上、本発明を実施するための形態について実施例を用いて説明したが、本発明はこうした実施例に何等限定されるものではなく、本発明の要旨を逸脱しない範囲内において、種々なる形態で実施し得ることは勿論である。 As mentioned above, although the form for implementing this invention was demonstrated using the Example, this invention is not limited at all to such an Example, In the range which does not deviate from the summary of this invention, it is with various forms. Of course, it can be implemented.
　本発明は、熱交換器の製造産業などに利用可能である。 The present invention can be used in the heat exchanger manufacturing industry.

Claims (6)

  1. 　伝熱部材の表面に流体を流すことにより熱交換を行なう熱交換器であって、
    　前記伝熱部材には、前記流体側の表面に、滑らかな曲線による波状の凹凸が、波の頂部が連続する頂部線と波の底部が連続する底部線とがＶ字を水平方向に連ねて屈曲部が曲線となるように形成されていると共に前記流体の主要な流れがＶ字の垂直方向となるように形成されている、
    　ことを特徴とする熱交換器。     A heat exchanger that exchanges heat by flowing a fluid over the surface of a heat transfer member,
    In the heat transfer member, the fluid side surface has wavy irregularities with a smooth curve, and the top line where the top of the wave continues and the bottom line where the bottom of the wave continues connect the V-shape in the horizontal direction. The bent portion is formed so as to be curved, and the main flow of the fluid is formed in a V-shaped vertical direction.
    A heat exchanger characterized by that.
  2. 　請求項１記載の熱交換器であって、
    　前記頂部線および前記底部線は、直線部と円弧部とを交互に接続するように形成されている、
    　熱交換器。     The heat exchanger according to claim 1,
    The top line and the bottom line are formed so as to alternately connect straight portions and arc portions,
    Heat exchanger.
  3. 　請求項２記載の熱交換器であって、
    　前記円弧部は、半径が前記直線部の長さの１／５以上となるよう形成されている、
    　熱交換器。     The heat exchanger according to claim 2,
    The arc portion is formed so that the radius is 1/5 or more of the length of the linear portion.
    Heat exchanger.
  4. 　請求項１ないし３のうちのいずれか１つの請求項に記載の熱交換器であって、
    　前記波状の凹凸は、断面が直線と円弧とを交互に連続するように形成されている、
    　熱交換器。     The heat exchanger according to any one of claims 1 to 3,
    The wavy irregularities are formed so that the cross section is alternately continuous with straight lines and arcs,
    Heat exchanger.
  5. 　請求項１ないし４のうちのいずれか１つの請求項に記載の熱交換器であって、
    　前記伝熱部材は、扁平な中空管として形成された熱交換用チューブであり、
    　前記波状の凹凸は、前記熱交換用チューブの扁平面に形成されている、
    　熱交換器。     A heat exchanger according to any one of claims 1 to 4, wherein
    The heat transfer member is a heat exchange tube formed as a flat hollow tube,
    The wavy unevenness is formed on the flat surface of the heat exchange tube,
    Heat exchanger.
  6. 　請求項１ないし４のうちのいずれか１つの請求項に記載の熱交換器であって、
    　前記伝熱部材は、熱交換用チューブに連結されたフィンである、
    　熱交換器。     A heat exchanger according to any one of claims 1 to 4, wherein
    The heat transfer member is a fin connected to a heat exchange tube.
    Heat exchanger.
PCT/JP2015/086562 2015-12-28 2015-12-28 Heat exchanger WO2017115436A1 (en)

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