JP7359767B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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JP7359767B2
JP7359767B2 JP2020533511A JP2020533511A JP7359767B2 JP 7359767 B2 JP7359767 B2 JP 7359767B2 JP 2020533511 A JP2020533511 A JP 2020533511A JP 2020533511 A JP2020533511 A JP 2020533511A JP 7359767 B2 JP7359767 B2 JP 7359767B2
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heat exchanger
case
flat
short side
tube
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JPWO2020027008A1 (en
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喜彦 佐々木
聡 大友
朗 小室
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T Rad Co Ltd
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T Rad Co Ltd
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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
    • F28F9/02—Header boxes; End plates

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Description

本発明は、主として高温ガスを冷却水によって冷却する熱交換器であって、その高温ガスの入口近傍に生じる熱応力を減少させるものに関する。 The present invention mainly relates to a heat exchanger that cools high-temperature gas with cooling water, and that reduces thermal stress generated near the inlet of the high-temperature gas.

下記特許文献１に記載の熱交換器は、内部に高温ガスが流通する多数の管と、その管の端部が挿通される管底（ヘッダプレート）を有するハウジングを有し、熱膨張差に起因する熱応力を低減させるために、そのハウジングに膨張要素としてその周方向に複数の条溝を形成し、それを密封する密封手段を設けたものである。 The heat exchanger described in Patent Document 1 below has a housing having a large number of tubes through which high-temperature gas flows and a tube bottom (header plate) through which the ends of the tubes are inserted, and has a housing that has a tube bottom (header plate) through which the ends of the tubes are inserted. In order to reduce the resulting thermal stress, a plurality of grooves are formed in the circumferential direction of the housing as expansion elements, and a sealing means is provided to seal the grooves.

特許第４００６７３４号公報Patent No. 4006734

しかしながら、矩形断面を有するハウジングにおいては、矩形角部への条溝の形成は困難であり、また、条溝部の剛性は低下するので、周方向に渡って条溝を設けた場合、耐振強度が低下する欠点があった。
そこで、本発明は矩形断面を有するハウジングにおいても製作性および耐振強度を低下させることなく熱膨張差に起因する熱応力を低下させ、ヒートサイクルに対する耐久性を高めた熱交換器を提供することを課題とする。However, in a housing with a rectangular cross section, it is difficult to form grooves on the rectangular corners, and the rigidity of the grooves decreases. There was a drawback that it deteriorated.
Therefore, it is an object of the present invention to provide a heat exchanger that reduces the thermal stress caused by the difference in thermal expansion even in a housing having a rectangular cross section without reducing the manufacturability and vibration resistance, and improves the durability against heat cycles. Take it as a challenge.

請求項１に記載の本発明は、複数の偏平チューブ１が、その厚み方向に並列された熱交換器コア２と、
その熱交換器コア２の外周を被嵌し、横断面が長辺部３ａと短辺部３ｂとで矩形に形成されると共に、その短辺部３ｂが各偏平チューブ１の並列方向に位置するケース３と、
そのケース３の開口端部の短辺部３ｂに、その開口の縁に平行に曲折形成された熱膨張吸収用のビード４と、
ケース３の開口端に接合されるタンク５と、を具備する熱交換器である。
請求項２に記載の本発明の前記偏平チューブ１は、その長手方向の両端部が前記厚み方向に膨出された膨出部１ａを有し、その膨出部１ａで複数の偏平チューブ１が積層されて前記熱交換器コア２を構成した請求項１に記載の熱交換器である。
請求項３に記載の本発明は、ケース３の内面に環状のインナーフランジ６が接続され、そのインナーフランジ６とケース３との間に環状溝７が形成され、その環状溝７にシール材８を介して前記タンク５の開口縁が接合される請求項１または請求項２のいずれかに記載の熱交換器である。The present invention according to claim 1 includes a heat exchanger core 2 in which a plurality of flat tubes 1 are arranged in parallel in the thickness direction;
The outer periphery of the heat exchanger core 2 is fitted, and the cross section is formed into a rectangular shape with a long side 3a and a short side 3b, and the short side 3b is located in the parallel direction of each flat tube 1. Case 3 and
A bead 4 for absorbing thermal expansion is formed on the short side 3b of the opening end of the case 3, and is bent parallel to the edge of the opening.
This heat exchanger includes a tank 5 joined to an open end of a case 3.
The flat tube 1 of the present invention according to claim 2 has a bulged portion 1a bulged in the thickness direction at both ends in the longitudinal direction, and a plurality of flat tubes 1 are formed in the bulged portion 1a. 2. The heat exchanger according to claim 1, wherein the heat exchanger core 2 is formed by laminating layers.
In the present invention as set forth in claim 3, an annular inner flange 6 is connected to the inner surface of the case 3, an annular groove 7 is formed between the inner flange 6 and the case 3, and a sealing material 8 is provided in the annular groove 7. 3. The heat exchanger according to claim 1, wherein the opening edge of the tank 5 is joined via a .

請求項１に記載の発明は、ケース３の開口端部の短辺部３ｂに、熱膨張吸収用のビード４が形成され、各偏平チューブ１がケース３の短辺方向で、偏平チューブ１の厚み方向に並列されたものである。各偏平チューブ１は、その横断面の長手方向により大きく熱膨張するが、その膨張の大きい方向に配置されたビード４に、その熱膨張が効果的に吸収される。また、ケース３の角部にはビード４を設けていないので、ビードの成形は容易となる。
さらに、ビード４はケース３の周方向の全周に渡ってはいないので、ビード４の形成に伴うケース３の剛性の低下は少なく、耐振強度の低下は抑制される。
それにより製作性、耐振強度を低下させることなく、ヒートサイクルに対する耐久性の高い熱交換器を提供できる。
請求項２に記載の発明は、その熱交換器コア２を構成する偏平チューブ１の長手方向の両端部が厚み方向に膨出され、その膨出部１ａで複数の偏平チューブ１が厚み方向に且つ、ケース３の短辺部３ｂの方向に積層されたものである。
このような熱交換器においては、偏平チューブ１とケース３との間に熱膨張差の緩衝部となるヘッダプレートが存在しないが、本発明におけるビード４により、熱膨張差が効果的に吸収される。それにより、このようなヘッダプレートレス型熱交換器においても、ヒートサイクルに対する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、ケース３の内面のインナーフランジ６と、ケース３との間に環状溝７が形成され、それにシール材８を介してタンク５の開口縁が接合されたものである。
このようなインナーフランジ型熱交換器においては、フランジ部がケース外部に曲折形成されているアウターフランジ方式に比べて、フランジ部の剛性が高く、フランジ部の弾性変形によって吸収される熱膨張差は少ない。また、本発明におけるビード４により、熱膨張差が効果的に吸収される。それにより、このようなインナーフランジ型熱交換器においても、ヒートサイクルに対する耐久性の高い熱交換器を提供できる。In the invention according to claim 1, a bead 4 for absorbing thermal expansion is formed on the short side 3b of the open end of the case 3, and each flat tube 1 is formed in the short side direction of the case 3. They are arranged in parallel in the thickness direction. Each flat tube 1 thermally expands more greatly in the longitudinal direction of its cross section, but the thermal expansion is effectively absorbed by the beads 4 arranged in the direction of greater expansion. Further, since the bead 4 is not provided at the corner of the case 3, the bead can be easily formed.
Furthermore, since the bead 4 does not extend over the entire circumference of the case 3 in the circumferential direction, the decrease in rigidity of the case 3 due to the formation of the bead 4 is small, and a decrease in vibration resistance strength is suppressed.
Thereby, a heat exchanger with high durability against heat cycles can be provided without reducing manufacturability or vibration resistance.
In the invention according to claim 2, both longitudinal ends of the flat tubes 1 constituting the heat exchanger core 2 are bulged in the thickness direction, and the plurality of flat tubes 1 are bulged in the thickness direction at the bulged portions 1a. Moreover, they are stacked in the direction of the short side 3b of the case 3.
In such a heat exchanger, there is no header plate between the flat tube 1 and the case 3 that serves as a buffer for the difference in thermal expansion, but the bead 4 in the present invention effectively absorbs the difference in thermal expansion. Ru. Thereby, even in such a header plateless type heat exchanger, it is possible to provide a heat exchanger with high durability against heat cycles.
In the invention according to claim 3, an annular groove 7 is formed between an inner flange 6 on the inner surface of the case 3 and the case 3, and an opening edge of the tank 5 is joined to the annular groove 7 via a sealing material 8. be.
In such an inner flange type heat exchanger, compared to an outer flange type heat exchanger in which the flange part is bent outside the case, the flange part has higher rigidity, and the difference in thermal expansion absorbed by the elastic deformation of the flange part is smaller. few. Furthermore, the beads 4 in the present invention effectively absorb differences in thermal expansion. Thereby, even in such an inner flange type heat exchanger, it is possible to provide a heat exchanger with high durability against heat cycles.

図１は本発明の熱交換器の分解斜視図。
図２は同熱交換器の熱交換器コア２の要部縦断面斜視図。
図３は同熱交換器のビード４とタンク５との接合状態を示す縦断面図。
図４は同熱交換器のケース３の短辺部３ｂに設けたビード４の斜視図。
図５は同熱交換器の熱交換器コア２の斜視図。FIG. 1 is an exploded perspective view of the heat exchanger of the present invention.
FIG. 2 is a vertical cross-sectional perspective view of the main part of the heat exchanger core 2 of the heat exchanger.
FIG. 3 is a longitudinal cross-sectional view showing the state of connection between the bead 4 and the tank 5 of the heat exchanger.
FIG. 4 is a perspective view of the bead 4 provided on the short side 3b of the case 3 of the heat exchanger.
FIG. 5 is a perspective view of the heat exchanger core 2 of the heat exchanger.

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、主として高温ガスを冷却水によって冷却するチャージエアクーラに最適なものである。その熱交換器コア２は、図５に示す如く、多数の偏平チューブ１をその両端部で積層したものである（下側を省略）。
各偏平チューブ１は、両端に膨出部１ａが厚み方向に突出している。そして、その膨出部１ａにおいて、各偏平チューブ１どうしがろう付により接合される。偏平チューブ１の内部には、インナーフィン９を挿入することが好ましい。
そして、図１、図５に示す如く、偏平チューブ１内の第１流路１０に第１流体１３である高温ガスが導かれ、偏平チューブ１の外面側の第２流路１１に第２流体１４である冷却水（図１）が導かれる。偏平チューブ１の集合体からなる熱交換器コア２の端部には、図５において、その両端にインナーフランジ６が被嵌され（一方端のみ記載）、そして、その外側にケース３が被嵌される。
即ち、熱交換器コア２の外周は、インナーフランジ６を介して、図１に図示するケース３が被嵌される。この例では、ケース３は横断面が方形の長辺部３ａと短辺部３ｂとで形成され、その短辺部３ｂ方向に多数の偏平チューブ１が並列される。
また、短辺部３ｂには、一対のパイプ１２が取付けられ、その一方から第２流体（冷却水）１４が流入し、他方からそれが流出する。第２流体（冷却水）１４は、図５において各偏平チューブ１の外周に形成された第２流路１１に導かれる。
前述の如く、熱交換器コア２の端部にはインナーフランジ６が被嵌される。そのインナーフランジ６は図４、図５に示す如く、ケース３の内周に整合するスカート部とそれからＬ字状に立ち上げられたＬ字状部とを有し、そのＬ字状部とケース３との間に環状溝７が形成される。その環状溝７には、図３に示す如く、シール材８を介してタンク５の開口端が圧入され、爪部１６のカシメによってそれらの間が締結固定される。
ここにおいて本発明の特徴とするところは、ケース３の端部に設けたビード４の存在である。このビード４は、図１に示す如く、ケース３の開口端部の短辺部３ｂの高温ガスの流入口側の開口の縁に平行に曲折形成されている。
そして、図１において、タンク５から熱交換器コア２の偏平チューブ１に第１流体（高温ガス）１３が供給される。すると、偏平チューブ１はその開口の長手方向により長く膨張する。その膨張は、図４において、ケース３の短辺部３ｂを外側に押し広げると共に、上下方向にも引き延ばされる。そのような熱膨張は、ケース３の短辺部３ｂの端部に設けたビード４によって効果的に吸収される。
上記実施形態は、タンク５とケース３とが、インナーフランジ６に配置したシール材８を介して、爪部１６によりカシメ固定されている熱交換器である。
タンク５とケース３とは、インナーフランジ６及びシール材を介さずに、直接、ろう付又は溶接により接合することもできる。
この実施形態では、コア形状として、各偏平チューブ１は、その両端部が厚み方向に膨出された膨出部１ａを有し、膨出部１ａで複数の偏平チューブ１が積層されたヘッダプレートレス型のコアを用いたものである。各偏平チューブ１は、図１～図５に示す如く、その各開口端がチューブ長辺１ｂとチューブ短辺１ｃとで横断面方形に形成されている。
各偏平チューブ１は、次のような構造にすることができる。
そのチューブ短辺１ｃの端縁は、チューブ長辺１ｂの平坦部１ｅよりも突出する。
チューブ長辺１ｂの端は、チューブ短辺１ｃ側に角状に突出した角部１ｄが形成されている。チューブ長辺１ｂの膨出部１ａの中間部には、その角部１ｄより第１流体（高温ガス）１３の流通方向の下流側に配置された平坦部１ｅが形成されている。そして、角部１ｄと平坦部１ｅとの間は、湾曲部１ｆにより滑らかに湾曲して接続されている。
このような構造にするにより、ビード４の効果と相乗して、各偏平チューブ１のチューブ短辺１ｃに加わる熱応力の集中を回避することができる。
コア形状は、インナーフランジ６に多数の偏平チューブ挿通孔を並列して形成し、そこに偏平チューブを挿通した形状のコアであっても良い。Next, embodiments of the present invention will be described based on the drawings.
This heat exchanger is ideal for charge air coolers that primarily cool high-temperature gas with cooling water. As shown in FIG. 5, the heat exchanger core 2 is made by laminating a large number of flat tubes 1 at both ends thereof (the lower side is omitted).
Each flat tube 1 has bulges 1a at both ends protruding in the thickness direction. The flat tubes 1 are joined to each other by brazing at the bulging portion 1a. It is preferable that inner fins 9 be inserted into the flat tube 1 .
As shown in FIGS. 1 and 5, a high-temperature gas, which is the first fluid 13, is introduced into the first flow path 10 in the flat tube 1, and a second fluid is introduced into the second flow path 11 on the outer surface side of the flat tube 1. 14 (FIG. 1) is introduced. As shown in FIG. 5, inner flanges 6 are fitted on both ends of the heat exchanger core 2 consisting of an assembly of flat tubes 1 (only one end is shown), and a case 3 is fitted on the outside thereof. be done.
That is, the case 3 shown in FIG. 1 is fitted onto the outer periphery of the heat exchanger core 2 via the inner flange 6. In this example, the case 3 has a rectangular long side 3a and a short side 3b in cross section, and a large number of flat tubes 1 are arranged in parallel in the direction of the short side 3b.
Further, a pair of pipes 12 are attached to the short side portion 3b, and a second fluid (cooling water) 14 flows into one of the pipes and flows out from the other. The second fluid (cooling water) 14 is guided to the second flow path 11 formed around the outer periphery of each flat tube 1 in FIG.
As described above, the inner flange 6 is fitted onto the end of the heat exchanger core 2. As shown in FIGS. 4 and 5, the inner flange 6 has a skirt portion that matches the inner periphery of the case 3 and an L-shaped portion raised from the skirt portion, and the L-shaped portion and the case 3, an annular groove 7 is formed therebetween. As shown in FIG. 3, the open end of the tank 5 is press-fitted into the annular groove 7 via a sealing material 8, and the gap between them is fastened and fixed by caulking the claw portion 16.
Here, the feature of the present invention is the presence of a bead 4 provided at the end of the case 3. As shown in FIG. 1, the bead 4 is bent parallel to the edge of the opening on the short side 3b of the open end of the case 3 on the high temperature gas inlet side.
In FIG. 1, the first fluid (high temperature gas) 13 is supplied from the tank 5 to the flat tube 1 of the heat exchanger core 2. Then, the flat tube 1 expands longer in the longitudinal direction of its opening. As shown in FIG. 4, the expansion expands the short side portion 3b of the case 3 outward and also extends it in the vertical direction. Such thermal expansion is effectively absorbed by the bead 4 provided at the end of the short side 3b of the case 3.
The above-described embodiment is a heat exchanger in which the tank 5 and the case 3 are caulked and fixed by the claw portions 16 via the sealing material 8 disposed on the inner flange 6.
The tank 5 and the case 3 can also be directly joined by brazing or welding without using the inner flange 6 and the sealing material.
In this embodiment, as a core shape, each flat tube 1 has a bulging part 1a in which both ends thereof bulge in the thickness direction, and the bulging part 1a forms a header plate in which a plurality of flat tubes 1 are stacked. It uses a non-resistance type core. As shown in FIGS. 1 to 5, each flat tube 1 has its open end formed into a rectangular cross section with a tube long side 1b and a tube short side 1c.
Each flat tube 1 can have the following structure.
The edge of the tube short side 1c protrudes beyond the flat portion 1e of the tube long side 1b.
At the end of the long side 1b of the tube, a corner 1d is formed that protrudes in an angular shape toward the short side 1c of the tube. A flat portion 1e is formed at the intermediate portion of the bulging portion 1a on the long side 1b of the tube, and is located downstream of the corner portion 1d in the flow direction of the first fluid (high temperature gas) 13. The corner portion 1d and the flat portion 1e are smoothly curved and connected by a curved portion 1f.
With such a structure, in combination with the effect of the beads 4, it is possible to avoid concentration of thermal stress applied to the tube short side 1c of each flat tube 1.
The core may have a shape in which a large number of flat tube insertion holes are formed in parallel in the inner flange 6 and flat tubes are inserted through the holes.

１ 偏平チューブ
１ａ 膨出部
１ｂ チューブ長辺
１ｃ チューブ短辺
１ｄ 角部
１ｅ 平坦部
１ｆ 湾曲部
２ 熱交換器コア
３ ケース
３ａ 長辺部
３ｂ 短辺部
４ ビード
５ タンク
６ インナーフランジ
７ 環状溝
８ シール材
９ インナーフィン
１０ 第１流路
１１ 第２流路
１２ パイプ
１３ 第１流体（高温ガス）
１４ 第２流体（冷却水）
１５ 入口
１６ 爪部1 Flat tube 1a Swelling part 1b Tube long side 1c Tube short side 1d Corner part 1e Flat part 1f Curved part 2 Heat exchanger core 3 Case 3a Long side part 3b Short side part 4 Bead 5 Tank 6 Inner flange 7 Annular groove 8 Seal material 9 Inner fin 10 First flow path 11 Second flow path 12 Pipe 13 First fluid (high temperature gas)
14 Second fluid (cooling water)
15 Inlet 16 Claw portion

Claims (3)

複数の偏平チューブ（１）が、その厚み方向に並列された熱交換器コア（２）と、
その熱交換器コア（２）の外周を被嵌し、横断面が長辺部（３ａ）と短辺部（３ｂ）とで矩形に形成されると共に、その短辺部（３ｂ）が各偏平チューブ（１）の並列方向に位置するケース（３）と、
そのケース（３）の開口端部の短辺部（３ｂ）の角部を除く平坦部に、その開口の縁に平行に曲折形成された熱膨張吸収用のビード（４）と、
ケース（３）の開口端に接合されるタンク（５）と、を具備する熱交換器。 a heat exchanger core (2) in which a plurality of flat tubes (1) are arranged in parallel in the thickness direction;
The outer periphery of the heat exchanger core (2) is fitted, and the cross section is formed into a rectangle with a long side (3a) and a short side (3b), and the short side (3b) is attached to each flat side. a case (3) located in a parallel direction of the tube (1);
A bead (4) for absorbing thermal expansion is bent parallel to the edge of the opening on a flat part of the short side (3b) of the opening end of the case (3) excluding the corners ;
A heat exchanger comprising: a tank (5) joined to an open end of a case (3). 前記偏平チューブ（１）は、その長手方向の両端部が前記厚み方向に膨出された膨出部（１ａ）を有し、その膨出部（１ａ）で複数の偏平チューブ（１）が積層されて前記熱交換器コア（２）を構成した請求項１に記載の熱交換器。 The flat tube (1) has a bulging portion (1a) bulging in the thickness direction at both ends in the longitudinal direction, and a plurality of flat tubes (1) are laminated at the bulging portion (1a). 2. A heat exchanger according to claim 1, wherein said heat exchanger core (2) is formed by a combination of: ケース（３）の内面に環状のインナーフランジ（６）が接続され、そのインナーフランジ（６）とケース（３）との間に環状溝（７）が形成され、その環状溝（７）にシール材（８）を介して前記タンク（５）の開口縁が接合される請求項１または請求項２のいずれかに記載の熱交換器。 An annular inner flange (6) is connected to the inner surface of the case (3), an annular groove (7) is formed between the inner flange (6) and the case (3), and a seal is formed in the annular groove (7). The heat exchanger according to claim 1 or 2, wherein the opening edge of the tank (5) is joined via a material (8).
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Citations (5)

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WO2006035986A1 (en) 2004-09-28 2006-04-06 T.Rad Co., Ltd. Egr cooler
JP4173817B2 (en) 2002-02-01 2008-10-29 ベール ゲーエムベーハー ウント コー カーゲー Exhaust gas heat exchanger
JP2008275244A (en) 2007-04-27 2008-11-13 T Rad Co Ltd Manufacturing method of heat exchanger, and heat exchanger
JP2014055711A (en) 2012-09-12 2014-03-27 T Rad Co Ltd Tank coupling structure for header-plate-less heat exchanger
JP2015055458A (en) 2013-09-13 2015-03-23 株式会社ティラド Tank structure of header-plateless heat exchanger

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4173817B2 (en) 2002-02-01 2008-10-29 ベール ゲーエムベーハー ウント コー カーゲー Exhaust gas heat exchanger
WO2006035986A1 (en) 2004-09-28 2006-04-06 T.Rad Co., Ltd. Egr cooler
JP2008275244A (en) 2007-04-27 2008-11-13 T Rad Co Ltd Manufacturing method of heat exchanger, and heat exchanger
JP2014055711A (en) 2012-09-12 2014-03-27 T Rad Co Ltd Tank coupling structure for header-plate-less heat exchanger
JP2015055458A (en) 2013-09-13 2015-03-23 株式会社ティラド Tank structure of header-plateless heat exchanger

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