WO2019131569A1 - Header plateless type heat exchanger - Google Patents

Header plateless type heat exchanger Download PDF

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Publication number
WO2019131569A1
WO2019131569A1 PCT/JP2018/047418 JP2018047418W WO2019131569A1 WO 2019131569 A1 WO2019131569 A1 WO 2019131569A1 JP 2018047418 W JP2018047418 W JP 2018047418W WO 2019131569 A1 WO2019131569 A1 WO 2019131569A1
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Prior art keywords
heat exchanger
fluid
bulging portion
narrow
flat
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PCT/JP2018/047418
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French (fr)
Japanese (ja)
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中村　洋一
弘仁 杉本
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株式会社ティラド
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Priority to JP2019561680A priority Critical patent/JP7244439B2/en
Publication of WO2019131569A1 publication Critical patent/WO2019131569A1/en

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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention is an EGR cooler mainly for cooling exhaust gas with cooling water, and a heat exchanger most suitable for an exhaust heat recovery unit for recovering the heat of exhaust gas to cooling water, having a header plateless type core About.
  • the core of the header plateless type is obtained by bulging the open end of the flat tube in the thickness direction and laminating at the bulging portion makes the header plate unnecessary.
  • Patent Document 1 proposes a header plateless type heat exchanger.
  • This heat exchanger as shown in FIGS. 5 to 7, comprises a flat tube 11 forming its core, in which a pair of grooved plates are fitted together with their groove bottoms facing each other, A bulging portion 11a is formed at the edge on the open end side, and the flat tubes 11 are stacked in the bulging portion 11a, and the respective plates are integrally fixed by brazing. And, as shown in FIG. 6, the crossing angle ⁇ of each plate is formed at an acute angle.
  • the flat tubes become high temperature at the inlet of the exhaust gas, and the heat exchanger may be deteriorated due to repeated heat cycles.
  • the header plateless type heat exchanger has a simple structure, it has the disadvantage that the tip of each flat tube has a poor cooling performance compared to a heat exchanger with a header plate, and that portion has a high temperature It is because Therefore, it is an object of the present invention to provide a heat exchanger capable of reducing the temperature of the end of the flat tube as much as possible while having the advantage of the header plateless.
  • the present invention according to claim 1 is characterized in that the pair of side walls 1 and 2 are raised on both sides so that the whole is formed in a groove shape, and the open side edge of the groove bottom 3 orthogonal to the side wall is thickness direction
  • a flat tube 7 having a pair of plates 5 and 6 on the outer side of which a narrow bulging portion 4 is formed, the plates 5 and 6 being fitted in opposite directions to each other, And a plurality of flat tubes 7 stacked on one another at the bulging portion 4, and the plates 5 and 6 are brazed to one another.
  • a header plateless heat exchanger characterized by The present invention according to claim 2 is that the narrow width of the bulging portion 4 of each of the plates 5 and 6 is a flat triangular or flat surface which becomes wider at the both end portions as approaching the side walls 1 and 2. It is a header plateless type heat exchanger according to claim 1 having a brazed joint.
  • each plate 5 extends from the brazed joint to the outer surface side at the position of the longitudinal middle portion of the bulging portion 4 of the respective flat tubes 7 stacked.
  • the cross angle ⁇ of the second embodiment is formed at an obtuse angle, and the header plateless heat exchanger according to claim 1 or 2 is characterized.
  • the width of the bulging portion 4 of each of the plates 5 and 6 is wide at both end portions in the longitudinal direction of the bulging portion 4 and narrow at other intermediate portions. It is. Thereby, in the middle part of the bulging part 4 of each flat tube 7 where the temperature difference with the second fluid 20 becomes largest, the distance from the tip of each flat tube 7 to the second fluid 20 becomes short, and its tip portion Heat transfer between the second fluid 20 and the second fluid 20 is improved, and the temperature difference therebetween is suppressed.
  • the narrow width of the said bulging part 4 is formed widely in the said both ends, and the brazed area of the side walls 1 and 2 in the said both ends and the casing 13 fitted to them is ensured.
  • the reliability and strength of brazing are maintained. As a result, the deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved.
  • the invention according to claim 2 is that the bulging portion 4 is formed in a flat triangle or a curved shape which becomes wider as approaching the side walls 1 and 2. As a result, the concentration of thermal stress in the vicinity of the side wall is alleviated, so that a highly durable heat exchanger can be provided.
  • the crossing angle ⁇ of the brazing joint on the outer surface side of the bulging portion 4 of each flat tube 7 is formed to be an obtuse angle. Thereby, the circulation of the cooling water in the vicinity of the bulging portion 4 can be promoted, and the temperature rise of the tip portion of the flat tube 7 can be suppressed.
  • FIG. 1 is a plan view of an essential part of a heat exchanger core according to the present invention.
  • FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
  • FIG. 3 is a perspective view of the core.
  • FIG. 4 is an exploded perspective view of a heat exchanger having the same core.
  • FIG. 7 is a perspective view of the conventional core.
  • This heat exchanger is most suitable as an EGR cooler or an exhaust heat recovery device.
  • a large number of flat tubes 7 are stacked to form a core 18, and the outer periphery of the core 18 is fitted with a casing 13.
  • the first fluid (in this example, exhaust gas) 16 is caused to flow in the inner surface side of each flat tube 7, and the second fluid (in this example, cooling water) 20 is caused to flow in the outer surface side.
  • a pair of side walls 1 and 2 are raised on both sides, and a pair of plates 5 and 6 formed into a groove shape as a whole are opposed to each other in opposite directions.
  • a narrow bulging portion 4 having a narrow width is formed on the outer side in the thickness direction at the edges of both open sides (corresponding to both open end sides of the flat tube 7) of the plates 5 and 6. It is preferable to insert inner fins 19 into the inside of each flat tube 7 and to coat or apply a brazing material on at least one side of the parts to be joined together.
  • the core 18 laminated in the casing 13 is inserted.
  • the casing 13 is formed of a box-like casing main body 13a and an end cover 13b.
  • a pair of exhaust gas pipes 17 is disposed at both ends of the casing 13 so that the first fluid (exhaust gas) 16 flows inside the core 18, and the second fluid (cooling water 2.) Arrange a pipe 15 for cooling water so that 20 can flow. Then, the components are integrally brazed in a high temperature furnace to form a heat exchanger. Then, the first fluid (exhaust gas) 16 is supplied to the flat tube 7 in the direction of the arrow in FIG. Further, in FIG. 4, the second fluid (cooling water) 20 is supplied from one water pipe 15, led to the outer surface side of each flat tube 7, and discharged from the other water pipe 15.
  • the feature of the present invention is the shape of the bulging portion 4 shown in FIGS. 1 and 2.
  • the bulging portion 4 is formed by press forming in the thickness direction on the open side of each of the plates 5 and 6.
  • the bulging portion 4 is formed to be wide at both ends in FIG. 1 and narrow at the other portions. That is, the narrow portion 4a has a width L1 at the middle portion, and the wide portion 4b has a width L2 at both ends.
  • the width of the wide portion 4 b be a plane triangle which becomes wider toward both sides of the side walls 1 and 2 or a shape in which the plane is curved.
  • the narrow width of the said bulging part 4 is formed widely in the said both ends, and the brazed area of the side walls 1 and 2 in the said both ends and the casing 13 fitted to them is ensured. , The reliability and strength of brazing are maintained.
  • the width of the wide portion 4b is a flat triangle which becomes wider toward both sides of the side walls 1 and 2 or a curved surface, and the shape change is smooth, The concentration of thermal stress in the vicinity of the side wall is alleviated. As a result, the deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved. Further, as shown in FIG.
  • each extending from the brazing joint portion to the outer surface side at the position of the longitudinal direction Of the plates 5 and 6 preferably has an obtuse angle, and this shape promotes the flow of cooling water in the vicinity of the bulging portion 4 to suppress the temperature rise at the tip of the flat tube 7 be able to.
  • the maximum value of the tip temperature of the flat tube of the conventional core shown in FIGS. 5 to 7 was 358 ° C.
  • the maximum value of the tip temperature of the flat tube of the core of the invention is 275 ° C., and a significant temperature reduction effect is confirmed.
  • the present invention is suitable as an EGR cooler and can be used for other heat exchangers such as exhaust heat recovery equipment.

Abstract

In this header plateless type heat exchanger, a rise in temperature of a tube leading end section, into which high-temperature exhaust gas and the like flow, is suppressed and durability is improved. Regarding the width of each of swelling sections 4 of plates 5, 6 that constitute a flat tube 7, wide parts 4b are provided at both ends in the longitudinal direction of the swelling section 4, and a narrow part 4a is provided in the remaining intermediate portion.

Description

ヘッダープレートレス型熱交換器Header plateless heat exchanger
　本発明は、主として排気ガスを冷却水で冷却するＥＧＲクーラや、排気ガスの熱を冷却水に回収する排熱回収器に最適な熱交換器であって、ヘッダープレートレス型のコアを有するものに関する。
　ヘッダープレートレス型のコアとは、偏平チューブの開口端を厚み方向に膨出したものを使用し、その膨出部において積層することにより、ヘッダープレートを不要としたものである。 The present invention is an EGR cooler mainly for cooling exhaust gas with cooling water, and a heat exchanger most suitable for an exhaust heat recovery unit for recovering the heat of exhaust gas to cooling water, having a header plateless type core About.
The core of the header plateless type is obtained by bulging the open end of the flat tube in the thickness direction and laminating at the bulging portion makes the header plate unnecessary.
　下記特許文献１にヘッダープレートレス型熱交換器が提案されている。
　この熱交換器は、図５~図７に示す如く、そのコアを形成する偏平チューブ１１が、一対の溝型に形成されたプレートを互いに溝底を対向して嵌着したものからなり、その両端開放側の縁に膨出部１１ａが形成され、その膨出部１１ａにおいて各偏平チューブ１１を積層し、各プレート間を一体にろう付固定したものである。そして、図６に示されているように、各プレートの交角θは鋭角に形成されている。 Patent Document 1 below proposes a header plateless type heat exchanger.
This heat exchanger, as shown in FIGS. 5 to 7, comprises a flat tube 11 forming its core, in which a pair of grooved plates are fitted together with their groove bottoms facing each other, A bulging portion 11a is formed at the edge on the open end side, and the flat tubes 11 are stacked in the bulging portion 11a, and the respective plates are integrally fixed by brazing. And, as shown in FIG. 6, the crossing angle θ of each plate is formed at an acute angle.
特開２０１６−１８３８３３号公報JP, 2016-183833, A
　従来のヘッダープレートレス型熱交換器は、排気ガスの入口部において、各偏平チューブが高温となり、繰り返し生じるヒートサイクルにより熱交換器が劣化するおそれがある。
　これは、ヘッダープレートレス型熱交換器は構造が簡単になる利点を有するも、欠点として、ヘッダープレートのある熱交換器に比べて、各偏平チューブの先端部の冷却性が悪くその部分が高温となるからである。
　そこで、本発明はヘッダープレートレスの利点を有しつつ、可能な限り偏平チューブの先端部の温度を低下できる熱交換器を提供することを課題とする。 In the conventional header plateless type heat exchanger, the flat tubes become high temperature at the inlet of the exhaust gas, and the heat exchanger may be deteriorated due to repeated heat cycles.
Although this has the advantage that the header plateless type heat exchanger has a simple structure, it has the disadvantage that the tip of each flat tube has a poor cooling performance compared to a heat exchanger with a header plate, and that portion has a high temperature It is because
Therefore, it is an object of the present invention to provide a heat exchanger capable of reducing the temperature of the end of the flat tube as much as possible while having the advantage of the header plateless.
　請求項１に記載の本発明は、それぞれ両側に一対の側壁１，２が立上げられて全体が溝状に形成され且つ、その側壁に直交した溝底３の両開放側の縁に厚み方向外側に細幅の膨出部４が形成された一対のプレート５，６を有し、それらのプレート５，６が互いに逆向きに対向して嵌着されている偏平チューブ７と、
　複数の偏平チューブ７が膨出部４で互いに積層され、各プレート５，６が互いにろう付接合されている熱交換器コアと、を有し、
　各偏平チューブの前記膨出部４の先端から第一流体１６が内部に流入し、その外側に第二流体２０が流通する熱交換器であって、
　前記各プレート５，６の前記膨出部４の細幅が、前記膨出部４の長手方向の両端部で広い幅広部４ｂとなり、それ以外の中間部で狭い幅狭部４ａに形成されていることを特徴とするヘッダープレートレス型熱交換器である。
　請求項２に記載の本発明は、前記各プレート５，６の前記膨出部４の細幅が、前記両端部では前記側壁１，２に近づく程広くなる平面三角の、または平面が湾曲したろう付接合部を有することを特徴とする請求項１に記載のヘッダープレートレス型熱交換器である。
　請求項３に記載の本発明は、積層された各偏平チューブ７の前記膨出部４の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート５，６の交角θが、鈍角に形成されていることを特徴とする請求項１または請求項２に記載のヘッダープレートレス型熱交換器である。 The present invention according to claim 1 is characterized in that the pair of side walls 1 and 2 are raised on both sides so that the whole is formed in a groove shape, and the open side edge of the groove bottom 3 orthogonal to the side wall is thickness direction A flat tube 7 having a pair of plates 5 and 6 on the outer side of which a narrow bulging portion 4 is formed, the plates 5 and 6 being fitted in opposite directions to each other,
And a plurality of flat tubes 7 stacked on one another at the bulging portion 4, and the plates 5 and 6 are brazed to one another.
It is a heat exchanger in which the first fluid 16 flows into the inside from the tip end of the bulging portion 4 of each flat tube, and the second fluid 20 circulates outside thereof,
The narrow width of the bulging part 4 of each of the plates 5 and 6 is formed into a wide wide part 4 b at both end parts in the longitudinal direction of the bulging part 4 and is formed into a narrow narrow part 4 a at the other middle part A header plateless heat exchanger characterized by
The present invention according to claim 2 is that the narrow width of the bulging portion 4 of each of the plates 5 and 6 is a flat triangular or flat surface which becomes wider at the both end portions as approaching the side walls 1 and 2. It is a header plateless type heat exchanger according to claim 1 having a brazed joint.
In the present invention according to claim 3, each plate 5 extends from the brazed joint to the outer surface side at the position of the longitudinal middle portion of the bulging portion 4 of the respective flat tubes 7 stacked. The cross angle θ of the second embodiment is formed at an obtuse angle, and the header plateless heat exchanger according to claim 1 or 2 is characterized.
　請求項１に記載の発明は、各プレート５，６の前記膨出部４の細幅が、前記膨出部４の長手方向の両端部で広く、それ以外の中間部で狭く形成されたものである。
　それにより、第二流体２０との温度差が最も大きくなる各偏平チューブ７の膨出部４の中間部において、各偏平チューブ７の先端から第二流体２０までの距離が短くなり、その先端部と第二流体２０との伝熱が向上し、その間の温度差が抑制される。なお、前記両端部においては、前記膨出部４の細幅は広く形成されており、前記両端部における側壁１，２とそれらに被嵌されるケーシング１３とのろう付面積が確保されるので、ろう付の信頼性および強度は維持される。
　その結果、ヒートサイクルによる熱交換器の劣化が抑制され、熱交換器の耐久性が向上する。
　請求項２に記載の発明は、前記膨出部４の細幅を側壁１，２に近づく程広くなる平面三角または湾曲した形に形成したものである。それにより、側壁近傍の熱応力の集中が緩和されるので、耐久性の高い熱交換器を提供できる。
　請求項３に記載の発明は、各偏平チューブ７の膨出部４の外面側における、ろう付接合の交角θが、鈍角に形成されたものである。これにより、膨出部４の近傍の冷却水の流通を促進して、偏平チューブ７の先端部の温度上昇を抑えることができる。 According to the first aspect of the present invention, the width of the bulging portion 4 of each of the plates 5 and 6 is wide at both end portions in the longitudinal direction of the bulging portion 4 and narrow at other intermediate portions. It is.
Thereby, in the middle part of the bulging part 4 of each flat tube 7 where the temperature difference with the second fluid 20 becomes largest, the distance from the tip of each flat tube 7 to the second fluid 20 becomes short, and its tip portion Heat transfer between the second fluid 20 and the second fluid 20 is improved, and the temperature difference therebetween is suppressed. In addition, since the narrow width of the said bulging part 4 is formed widely in the said both ends, and the brazed area of the side walls 1 and 2 in the said both ends and the casing 13 fitted to them is ensured. , The reliability and strength of brazing are maintained.
As a result, the deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved.
The invention according to claim 2 is that the bulging portion 4 is formed in a flat triangle or a curved shape which becomes wider as approaching the side walls 1 and 2. As a result, the concentration of thermal stress in the vicinity of the side wall is alleviated, so that a highly durable heat exchanger can be provided.
In the invention according to claim 3, the crossing angle θ of the brazing joint on the outer surface side of the bulging portion 4 of each flat tube 7 is formed to be an obtuse angle. Thereby, the circulation of the cooling water in the vicinity of the bulging portion 4 can be promoted, and the temperature rise of the tip portion of the flat tube 7 can be suppressed.
　図１は本発明の熱交換器コアの要部平面図。
　図２は図１のＩＩ−ＩＩ矢視断面図。
　図３は同コアの斜視図。
　図４は同コアを有する熱交換器の分解斜視図。
　図５は従来型熱交換器コアの要部平面図。
　図６は図５のＶＩ−ＶＩ矢視断面図。
　図７は同従来型コアの斜視図。 FIG. 1 is a plan view of an essential part of a heat exchanger core according to the present invention.
FIG. 2 is a cross-sectional view taken along the line II-II in FIG.
FIG. 3 is a perspective view of the core.
FIG. 4 is an exploded perspective view of a heat exchanger having the same core.
FIG. 5 is a plan view of an essential part of a conventional heat exchanger core.
6 is a sectional view taken along the line VI-VI in FIG.
FIG. 7 is a perspective view of the conventional core.
　次に、図面に基づいて本発明の実施の形態につき説明する。
　この熱交換器は、ＥＧＲクーラや排熱回収器として最適なものである。これは、図４に示す如く、多数の偏平チューブ７を積層してコア１８を形成し、そのコア１８の外周をケーシング１３で被嵌する。そして、各偏平チューブ７の内面側に第一流体（この例では、排気ガス）１６を流通させ、その外面側に第二流体（この例では、冷却水）２０を流通させるものである。
　各偏平チューブ７は、図１~図３に示す如く、両側に一対の側壁１，２が立ち上げられ、全体が溝状に形成された一対のプレート５，６を互いに逆向きに対向して嵌着したものである。各プレート５，６の両開放側（偏平チューブ７の両開口端側に相当）の縁には、厚み方向外側に幅の狭い細幅の膨出部４が形成されている。
　各偏平チューブ７の内部にはインナーフィン１９を挿入し、また、互いに接合される部品の少なくとも一方側にはろう材を被覆または塗布しておくことが好ましい。
　一例として図４に示す如く、ケーシング１３内に積層されたコア１８が挿入される。この例では、ケーシング１３は箱状のケーシング本体１３ａと端蓋１３ｂにより形成されている。そして、コア１８の内部側に第一流体（排気ガス）１６が流通するようにケーシング１３の両端に一対の排気ガス用のパイプ１７を配し、コア１８の外面側に第二流体（冷却水）２０が流通するように冷却水用のパイプ１５を配する。そして、高温の炉内で各部品間を一体的にろう付して熱交換器を形成する。
　そして、その偏平チューブ７に図２において矢印方向に第一流体（排気ガス）１６が供給される。
　また、図４において、一方の水パイプ１５から第二流体（冷却水）２０が供給され、各偏平チューブ７の外面側にそれが導かれて、他方の水パイプ１５からそれが排出される。そして、その間に第一流体（排気ガス）１６と第二流体（冷却水）２０との間に熱交換が行われるものである。
（発明の特徴）
　ここにおいて、本発明の特徴とするところは、図１及び図２に示す膨出部４の形状である。この膨出部４は、各プレート５，６の開放側において、厚み方向にプレス成形により膨出させたものである。この膨出部４は、その幅が図１において両端部で広く、それ以外で狭く形成されている。
　即ち、中間部ではその幅狭部４ａが幅Ｌ１となり、両端部ではその幅広部４ｂが幅Ｌ２となる。ここに、Ｌ２＞Ｌ１である。図１に示すように、幅広部４ｂにおける幅は、その側壁１，２の両側に近づくほど広くなる平面三角、または平面が湾曲した形状とすることが好ましい。
（作用）
　このような特徴により、第二流体（冷却水）２０との温度差が最も大きくなる各偏平チューブ７の膨出部４の中間部において、各偏平チューブ７の先端から第二流体（冷却水）２０までの距離が短くなり、その先端部と第二流体（冷却水）２０との伝熱が向上し、その間の温度差が抑制される。なお、前記両端部においては、前記膨出部４の細幅は広く形成されており、前記両端部における側壁１，２とそれらに被嵌されるケーシング１３とのろう付け面積は確保されるので、ろう付けの信頼性および強度は維持される。
　さらに、この例では、幅広部４ｂにおける幅は、その側壁１，２の両側に近づくほど広くなる平面三角、または平面が湾曲した形状となっており、その形状変化がなだらかになっているので、側壁近傍の熱応力の集中が緩和される。
　その結果、ヒートサイクルによる熱交換器の劣化が抑制され、熱交換器の耐久性が向上する。
　また、図２に示されているように、積層された各偏平チューブ７の前記膨出部４の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート５，６の交角θを鈍角に形成することが好ましく、この形状にすることで、膨出部４の近傍の冷却水の流通を促進して、偏平チューブ７の先端部の温度上昇を抑えることができる。
　本発明の効果を確認するために一例について数値解析を実施したところ、図５~図７に示す従来型のコアの偏平チューブの先端部温度の最大値が３５８℃であったのに対し、本発明のコアの偏平チューブの先端部温度の最大値は２７５℃であり、大幅な温度低下効果が確認された。 Next, an embodiment of the present invention will be described based on the drawings.
This heat exchanger is most suitable as an EGR cooler or an exhaust heat recovery device. As shown in FIG. 4, a large number of flat tubes 7 are stacked to form a core 18, and the outer periphery of the core 18 is fitted with a casing 13. Then, the first fluid (in this example, exhaust gas) 16 is caused to flow in the inner surface side of each flat tube 7, and the second fluid (in this example, cooling water) 20 is caused to flow in the outer surface side.
As shown in FIGS. 1 to 3, in each flat tube 7, a pair of side walls 1 and 2 are raised on both sides, and a pair of plates 5 and 6 formed into a groove shape as a whole are opposed to each other in opposite directions. It is a fit. A narrow bulging portion 4 having a narrow width is formed on the outer side in the thickness direction at the edges of both open sides (corresponding to both open end sides of the flat tube 7) of the plates 5 and 6.
It is preferable to insert inner fins 19 into the inside of each flat tube 7 and to coat or apply a brazing material on at least one side of the parts to be joined together.
As shown in FIG. 4 as an example, the core 18 laminated in the casing 13 is inserted. In this example, the casing 13 is formed of a box-like casing main body 13a and an end cover 13b. Then, a pair of exhaust gas pipes 17 is disposed at both ends of the casing 13 so that the first fluid (exhaust gas) 16 flows inside the core 18, and the second fluid (cooling water 2.) Arrange a pipe 15 for cooling water so that 20 can flow. Then, the components are integrally brazed in a high temperature furnace to form a heat exchanger.
Then, the first fluid (exhaust gas) 16 is supplied to the flat tube 7 in the direction of the arrow in FIG.
Further, in FIG. 4, the second fluid (cooling water) 20 is supplied from one water pipe 15, led to the outer surface side of each flat tube 7, and discharged from the other water pipe 15. And heat exchange is performed between the 1st fluid (exhaust gas) 16 and the 2nd fluid (cooling water) 20 in the meantime.
(Features of the invention)
Here, the feature of the present invention is the shape of the bulging portion 4 shown in FIGS. 1 and 2. The bulging portion 4 is formed by press forming in the thickness direction on the open side of each of the plates 5 and 6. The bulging portion 4 is formed to be wide at both ends in FIG. 1 and narrow at the other portions.
That is, the narrow portion 4a has a width L1 at the middle portion, and the wide portion 4b has a width L2 at both ends. Here, L2> L1. As shown in FIG. 1, it is preferable that the width of the wide portion 4 b be a plane triangle which becomes wider toward both sides of the side walls 1 and 2 or a shape in which the plane is curved.
(Action)
By such a feature, in the middle portion of the bulging portion 4 of each flat tube 7 where the temperature difference with the second fluid (cooling water) 20 becomes largest, the second fluid (cooling water) from the tip of each flat tube 7 The distance to 20 is shortened, the heat transfer between the tip and the second fluid (cooling water) 20 is improved, and the temperature difference therebetween is suppressed. In addition, since the narrow width of the said bulging part 4 is formed widely in the said both ends, and the brazed area of the side walls 1 and 2 in the said both ends and the casing 13 fitted to them is ensured. , The reliability and strength of brazing are maintained.
Furthermore, in this example, the width of the wide portion 4b is a flat triangle which becomes wider toward both sides of the side walls 1 and 2 or a curved surface, and the shape change is smooth, The concentration of thermal stress in the vicinity of the side wall is alleviated.
As a result, the deterioration of the heat exchanger due to the heat cycle is suppressed, and the durability of the heat exchanger is improved.
Further, as shown in FIG. 2, at the position of the longitudinal middle portion of the bulging portion 4 of the stacked flat tubes 7, each extending from the brazing joint portion to the outer surface side at the position of the longitudinal direction Of the plates 5 and 6 preferably has an obtuse angle, and this shape promotes the flow of cooling water in the vicinity of the bulging portion 4 to suppress the temperature rise at the tip of the flat tube 7 be able to.
When numerical analysis was performed on an example to confirm the effect of the present invention, the maximum value of the tip temperature of the flat tube of the conventional core shown in FIGS. 5 to 7 was 358 ° C. The maximum value of the tip temperature of the flat tube of the core of the invention is 275 ° C., and a significant temperature reduction effect is confirmed.
　本発明は、ＥＧＲクーラとして最適であると共に、その他の熱交換器、例えば排熱回収器等に用いることができる。 The present invention is suitable as an EGR cooler and can be used for other heat exchangers such as exhaust heat recovery equipment.
　１，２　側壁
　３　溝底
　４　膨出部
　４ａ　幅狭部
　４ｂ　幅広部
　５，６　プレート
　７　偏平チューブ
　８　端部境界線
　９　ディンプル
　９ａ　ディンプル
　１０　偏平チューブ
　１１　偏平チューブ
　１１ａ　膨出部
　１２　コア
　１３　ケーシング
　１３ａ　ケーシング本体
　１３ｂ　端蓋
　１５　パイプ
　１６　第一流体（排気ガス）
　１７　パイプ
　１８　コア
　１９　インナーフィン
　２０　第二流体（冷却水）
　θ　交角
　Ｌ１　幅
　Ｌ２　幅 1, 2 side wall 3 groove bottom 4 bulging part 4a narrow part 4b wide part 5, 6 plate 7 flat tube 8 end boundary line 9 dimple 9a dimple 10 flat tube 11 flat tube 11a bulging part 12 core 13 casing 13a casing Body 13b End cover 15 Pipe 16 First fluid (exhaust gas)
17 pipe 18 core 19 inner fin 20 second fluid (cooling water)
θ Crossing angle L1 width L2 width

Claims (3)

  1. 　それぞれ両側に一対の側壁（１）（２）が立上げられて全体が溝状に形成され且つ、その側壁に直交した溝底（３）の両開放側の縁に厚み方向外側に細幅の膨出部（４）が形成された一対のプレート（５）（６）を有し、それらのプレート（５）（６）が互いに逆向きに対向して嵌着されている偏平チューブ（７）と、
    　複数の偏平チューブ（７）が膨出部（４）で互いに積層され、各プレート（５）（６）が互いにろう付接合されている熱交換器コアと、を有し、
    　各偏平チューブの前記膨出部（４）の先端から第一流体（１６）が内部に流入し、その外側に第二流体（２０）が流通する熱交換器であって、
    　前記各プレート（５）（６）の前記膨出部（４）の細幅が、前記膨出部（４）の長手方向の両端部で広い幅広部（４ｂ）となり、それ以外の中間部で狭い幅狭部（４ａ）に形成されていることを特徴とするヘッダープレートレス型熱交換器。     A pair of side walls (1) and (2) are raised on both sides, respectively, to form the whole in a groove shape, and narrow on the both open sides of the groove bottom (3) orthogonal to the side wall in the thickness direction Flat tube (7) having a pair of plates (5) and (6) formed with a bulging portion (4), and the plates (5) and (6) are fitted opposite to each other in opposite directions When,
    A plurality of flat tubes (7) stacked on each other at the bulge (4), and the plates (5) (6) are brazed to one another;
    A heat exchanger in which a first fluid (16) flows into the inside from the tip of the bulging portion (4) of each flat tube, and a second fluid (20) flows outside the first fluid (16),
    The narrow width of the bulging part (4) of each plate (5) (6) becomes the wide part (4b) which is wide at both ends in the longitudinal direction of the bulging part (4), and in the other middle part A header plateless heat exchanger characterized in that it is formed in a narrow narrow portion (4a).
  2. 　前記各プレート（５）（６）の前記膨出部（４）の細幅が、前記両端部では前記側壁（１）（２）に近づく程広くなる平面三角の、または平面が湾曲したろう付接合部を有することを特徴とする請求項１に記載のヘッダープレートレス型熱交換器。 The flat triangular or brazed flat surface becomes wider as the narrow width of the bulging portion (4) of each plate (5, 6) gets closer to the side wall (1) (2) at the both end portions The header plateless heat exchanger according to claim 1, characterized in that it has a joint.
  3. 　積層された各偏平チューブ（７）の前記膨出部（４）の長手方向の中間部の位置で、ろう付接合部からそれを横断して外面側に広がる各プレート（５）（６）の交角θが、鈍角に形成されていることを特徴とする請求項１または請求項２に記載のヘッダープレートレス型熱交換器。 At the position of the longitudinal middle of the bulging portion (4) of the stacked flat tubes (7), each plate (5) (6) extends transversely from the brazing joint to the outer surface side The header plateless heat exchanger according to claim 1 or 2, wherein the crossing angle θ is formed at an obtuse angle.
PCT/JP2018/047418 2017-12-27 2018-12-17 Header plateless type heat exchanger WO2019131569A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020250041A1 (en) * 2019-06-10 2020-12-17 株式会社ティラド Heat exchanger

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010037878A1 (en) * 2000-04-10 2001-11-08 Viktor Brost Header-less vehicle radiator
US20060219394A1 (en) * 2005-04-01 2006-10-05 Martin Michael A Stacked-tube heat exchanger
JP2015087090A (en) * 2013-11-01 2015-05-07 臼井国際産業株式会社 Multitubular heat exchanger
JP2015194324A (en) * 2014-03-27 2015-11-05 株式会社ティラド Header plate-less heat exchanger
WO2017073779A1 (en) * 2015-10-29 2017-05-04 株式会社ティラド Structure of heat exchanger core without header plate
JP2017187196A (en) * 2016-04-04 2017-10-12 株式会社デンソー Exhaust heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20010037878A1 (en) * 2000-04-10 2001-11-08 Viktor Brost Header-less vehicle radiator
US20060219394A1 (en) * 2005-04-01 2006-10-05 Martin Michael A Stacked-tube heat exchanger
JP2015087090A (en) * 2013-11-01 2015-05-07 臼井国際産業株式会社 Multitubular heat exchanger
JP2015194324A (en) * 2014-03-27 2015-11-05 株式会社ティラド Header plate-less heat exchanger
WO2017073779A1 (en) * 2015-10-29 2017-05-04 株式会社ティラド Structure of heat exchanger core without header plate
JP2017187196A (en) * 2016-04-04 2017-10-12 株式会社デンソー Exhaust heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020250041A1 (en) * 2019-06-10 2020-12-17 株式会社ティラド Heat exchanger

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