JP2010038477A - Porous tube for heat exchange - Google Patents

Porous tube for heat exchange Download PDF

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JP2010038477A
JP2010038477A JP2008203698A JP2008203698A JP2010038477A JP 2010038477 A JP2010038477 A JP 2010038477A JP 2008203698 A JP2008203698 A JP 2008203698A JP 2008203698 A JP2008203698 A JP 2008203698A JP 2010038477 A JP2010038477 A JP 2010038477A
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tube
walls
hole tube
heat exchange
flat
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Toshikatsu Tawara
利克 田原
Kenji Makino
健司 槇野
Shigeki Kimura
茂樹 木村
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Tokyo Radiator Mfg Co Ltd
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Tokyo Radiator Mfg Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure capable of being manufactured by conventional extrusion molding, and preventing fracture of right and left sidewalls of a porous tube by heat strain, with respect to the porous tube for heat exchange used in an intercooler for a vehicle. <P>SOLUTION: In the porous tube for heat exchange composed of a flat tube having tabular upper and lower walls, and the right and left sidewalls of a roughly semicircular section, and a plurality of vertical partitioning walls disposed between the upper and lower walls of the flat tube, and further having a plurality of passages, a pair of ribs respectively projecting inward from the center of the height of each inner face of the right and left sidewalls, having the taper shape having an intersecting angle of an upper face and a lower face of 10-30 degrees, having round tips, and having the sectional shape in which a thickness of a base section is less than the thickest section of the flat tube, are extended along the passages. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、車両等に搭載されるインタークーラに用いられ、内部に排気ガスを流通させて冷却する熱交換用多穴チューブに関する。   The present invention relates to a multi-hole tube for heat exchange that is used in an intercooler mounted on a vehicle or the like and cools by circulating exhaust gas therein.

従来の車両等のインタークーラに用いられる熱交換用チューブには、押出し成形されたアルミ製の多穴チューブが多く用いられている。   An extruded aluminum multi-hole tube is often used as a heat exchange tube used in a conventional intercooler such as a vehicle.

そして、インタークーラ用のアルミ製の多穴チューブ１０は、一般的に０．４ｍｍ〜０．６ｍｍの板厚の中空の扁平管の中に、０．３ｍｍ〜０．６ｍｍの仕切壁３を幅方向に等間隔で複数設置している。それぞれの仕切壁３は扁平管の上下壁１、１間に垂直に立てられ、管内を複数の通路に仕切っている（図５、図６）。   The multi-hole tube 10 made of aluminum for the intercooler generally has a partition wall 3 having a width of 0.3 mm to 0.6 mm in a hollow flat tube having a thickness of 0.4 mm to 0.6 mm. Several are installed at equal intervals in the direction. Each partition wall 3 stands vertically between the upper and lower walls 1 and 1 of the flat tube and partitions the inside of the tube into a plurality of passages (FIGS. 5 and 6).

図７に示すように、複数の多穴チューブ１０とフィン２０（図７では図示せず。図８に図示）とを交互に積層し、多穴チューブ１０を入口側および出口側の端部で、複数の孔を有するエンドプレート３０、３０にそれぞれ貫装して束ねる。その後、図８に示すように、エンドプレート３０、３０を入口方向および出口方向からヘッダー４０、４０で挟持して接合し、インタークーラを形成する。
排気ガスは、入口側のヘッダー４０から分岐してそれぞれの多穴チューブ１０の仕切られた通路を流通し、出口側のヘッダー４０で再び合流する。一方、空気等の冷却流体はフィン２０に沿って多穴チューブ１０同士の間を排気ガスと交差方向に流れ、排気ガスを冷却する。 As shown in FIG. 7, a plurality of multi-hole tubes 10 and fins 20 (not shown in FIG. 7, not shown in FIG. 8) are alternately laminated, and the multi-hole tubes 10 are formed at the end portions on the inlet side and the outlet side. The end plates 30 and 30 having a plurality of holes are respectively penetrated and bundled. After that, as shown in FIG. 8, the end plates 30 and 30 are sandwiched and joined by headers 40 and 40 from the inlet direction and the outlet direction to form an intercooler.
The exhaust gas branches off from the header 40 on the inlet side, flows through the partitioned passages of the multi-hole tubes 10, and merges again at the header 40 on the outlet side. On the other hand, a cooling fluid such as air flows between the multi-hole tubes 10 along the fins 20 in the direction intersecting with the exhaust gas, thereby cooling the exhaust gas.

近年、エンジンの高性能化に伴い排気ガスが高温なものとなっているため、これを冷却するインタークーラの熱交換性能を向上する必要がある。このため、インタークーラの大型化や、インタークーラに使用される熱交換用チューブに様々な工夫がなされている。
例えば、図５、６に示すように、多穴チューブ１０の上下壁１の内面及び仕切壁３に数箇所の突条４を突出させるなど、表面積を大きく取って、空気等の冷却流体と高温の排気ガスとの熱交換効率を上げる工夫がなされている。特許文献１には、通路の断面の直径や上下壁の突条の本数を最適化したものが記載されている。 In recent years, as the performance of engines has increased, the exhaust gas has become hot. Therefore, it is necessary to improve the heat exchange performance of an intercooler that cools the exhaust gas. For this reason, various devices have been made to increase the size of the intercooler and heat exchange tubes used in the intercooler.
For example, as shown in FIGS. 5 and 6, the surface of the multi-hole tube 10 has a large surface area, such as by projecting several protrusions 4 on the inner surfaces of the upper and lower walls 1 and the partition wall 3, and a cooling fluid such as air and a high temperature. Has been devised to increase the efficiency of heat exchange with the exhaust gas. Patent Document 1 describes an optimization of the diameter of the cross section of the passage and the number of protrusions on the upper and lower walls.

特許文献２には、上下壁のそれぞれに複数の突条を設ける場合に、上下壁の突条のピッチを半分ずつずらすことで、突条を設けた箇所でも上下壁の必要な距離を確保し、管内で詰まりが発生するのを防止するものが記載されている。   In Patent Document 2, when a plurality of ridges are provided on each of the upper and lower walls, the necessary distance between the upper and lower walls is ensured even at the location where the ridges are provided by shifting the pitch of the ridges on the upper and lower walls by half. In this document, what prevents clogging in a pipe is described.

このように従来のインタークーラ用の多穴チューブでは、高温の排気ガスが効率良くインタークーラ内に流れるように、入口側ヘッダーの内部形状、多穴チューブ内の突条や仕切壁の形状および設置方法を工夫し、熱交換性能を向上させていた。
しかし、排気ガスの高温化に伴い、この排気ガスが流れ込む多穴チューブの入口・出口の付近が熱歪みにより破損する問題が発生していた。 As described above, in the conventional multi-hole tube for intercooler, the internal shape of the header on the inlet side, the shape of the ridges and partition walls in the multi-hole tube, and the installation so that the high-temperature exhaust gas can efficiently flow into the intercooler. The method was devised to improve the heat exchange performance.
However, with the high temperature of the exhaust gas, there has been a problem that the vicinity of the inlet / outlet of the multi-hole tube into which the exhaust gas flows is damaged due to thermal distortion.

高温の排気ガスが流入すると、熱によって多穴チューブ１０が膨張して、入口方向および出口方向に伸びる（図９（ｂ））。一方、エンドプレート３０はヘッダー４０によって両側から位置を固定されているため、伸長する多穴チューブ１０との接合部７が伸びの方向に引っ張られて長さＥのたわみが発生する。
多穴チューブ１０にもエンドプレート３０から伸長を抑制する力が加わるため、エンドプレート３０との接合部７付近には強い熱歪みが発生し、多穴チューブ１０を圧縮する方向の歪みを生じる。インタークーラにガスが流れていないときにはこの力は発生しないため（図９（ａ））、繰り返しの使用により、エンドプレート３０との接合部７付近の多穴チューブ１０の側壁２に亀裂８が生じ、破損することがあった（図９（ｃ））。 When hot exhaust gas flows in, the multi-hole tube 10 expands due to heat and extends in the inlet direction and the outlet direction (FIG. 9B). On the other hand, since the position of the end plate 30 is fixed from both sides by the header 40, the joint portion 7 with the expanding multi-hole tube 10 is pulled in the extending direction, and the deflection of the length E occurs.
Since the force which suppresses expansion | extension from the end plate 30 is added also to the multi-hole tube 10, a strong thermal strain generate | occur | produces in the junction part 7 vicinity with the end plate 30, and the distortion of the direction which compresses the multi-hole tube 10 arises. Since no force is generated when no gas flows through the intercooler (FIG. 9A), cracks 8 are generated in the side wall 2 of the multi-hole tube 10 near the joint 7 with the end plate 30 by repeated use. In some cases, it was damaged (FIG. 9C).

特許文献３には、熱歪みによる破損を防止するために、一枚の板状素材を屈曲させて成形する熱交換用チューブにおいて、屈曲によって一方の側壁を形成する際に、内側に突出するように折り込まれた折込部を設けたものが記載されている。   In Patent Document 3, in order to prevent breakage due to thermal strain, in a heat exchange tube formed by bending a single plate-shaped material, when one side wall is formed by bending, it protrudes inward. The thing which provided the folding part folded in is described.

特開２００２−３１８０８６号公報JP 2002-318086 A 特開２００６−１６２０８５号公報JP 2006-162085 A 特開２００７−１５５３００号公報JP 2007-155300 A

一方で押出し成形式の多穴チューブでは、左右側壁の曲面部を肉厚にして補強する方法が一般的であり、１．５ｍｍ程度の厚さまでは押出し成形で製造することが可能であった。しかし、１．５ｍｍ以上の板厚に形成することは押出し成形以外の方法によらねばならず、材料費が増加することもあり、コスト高となっていた。   On the other hand, in the extrusion-type multi-hole tube, a method of reinforcing the curved portions of the left and right side walls by increasing the thickness is generally used, and a thickness of about 1.5 mm can be manufactured by extrusion molding. However, the formation of a plate thickness of 1.5 mm or more has to be performed by a method other than extrusion molding, and the material cost may increase, resulting in high costs.

本発明は上記問題点を解決するためになされたものであり、車両用インタークーラに用いられる熱交換用多穴チューブにおいて、熱歪みによる多穴チューブ左右側壁の破損を防止することができ、かつ、従来の押出し成形による製造が可能な構造を提供することを課題とする。   The present invention was made to solve the above problems, and in the multi-hole tube for heat exchange used in the vehicle intercooler, the damage to the left and right side walls of the multi-hole tube due to thermal strain can be prevented, and Another object of the present invention is to provide a structure that can be manufactured by conventional extrusion molding.

本発明において、上記課題が解決される手段は以下の通りである。
第１の発明は、平板状の上下壁及び断面略半円状の左右側壁を有する扁平管と、この扁平管の上下壁の間に介在する複数の垂直な仕切壁とからなり複数の通路を有する熱交換用多穴チューブにおいて、上記左右側壁の各内面高さ中央から内方へそれぞれ突出し、上面と下面との交角が１０〜３０度の先細り形状で先端が丸く、基部の厚さが扁平管の最厚部以下である断面形状を有する一対のリブを通路に沿って延設したことを特徴とする。 In the present invention, means for solving the above problems are as follows.
A first invention comprises a flat tube having flat upper and lower walls and left and right side walls having a substantially semicircular cross section, and a plurality of vertical partition walls interposed between the upper and lower walls of the flat tube. In the multi-hole tube for heat exchange, each of the left and right side walls protrudes inward from the center of the inner surface of each of the left and right side walls, the angle of intersection between the upper surface and the lower surface is 10 to 30 degrees, the tip is round, and the base is flat. A pair of ribs having a cross-sectional shape that is equal to or less than the thickest part of the tube is extended along the passage.

第２の発明は、平板状の上下壁及び断面略半円状の左右側壁を有する扁平管と、この扁平管の上下壁の間に介在する複数の垂直な仕切壁とからなり複数の通路を有する熱交換用多穴チューブにおいて、上記仕切壁と略同等の板厚を有する水平な補強板を、上記左右側壁の各内面高さ中央と両端に配置した仕切壁との間にそれぞれ介設したことを特徴とする。   A second invention comprises a flat tube having flat upper and lower walls and left and right side walls having a substantially semicircular cross section, and a plurality of vertical partition walls interposed between the upper and lower walls of the flat tube. In the multi-hole tube for heat exchange having, horizontal reinforcing plates having substantially the same thickness as the partition walls are respectively interposed between the center of each inner surface height of the left and right side walls and the partition walls disposed at both ends. It is characterized by that.

第１の発明によれば、上記左右側壁の各内面高さ中央から内方へそれぞれ突出し、上面と下面との交角が１０〜３０度の先細り形状で先端が丸く、基部の厚さが扁平管の最厚部以下である断面形状を有する一対のリブを通路に沿って延設したことにより、多穴チューブの左右側壁が補強されるため、高温の排気ガスの流通によって熱歪みが生じて多穴チューブが破損するのを防止することができる。また、側壁全体の板厚を上げる対策に比べて管内断面積の減少が少なく済むため、多穴チューブ内を流れるガスの抵抗の増加と、材料費の増加を抑えることができる。さらに、従来の押出し成形によって容易に製造することができる。   According to the first invention, each of the left and right side walls protrudes inward from the center of the inner surface of each of the left and right side walls. Since the left and right side walls of the multi-hole tube are reinforced by extending a pair of ribs having a cross-sectional shape that is equal to or less than the thickest portion of the multi-hole tube, thermal distortion occurs due to the circulation of high-temperature exhaust gas. It is possible to prevent the hole tube from being damaged. In addition, since the reduction in the cross-sectional area in the tube is less than the measure for increasing the plate thickness of the entire side wall, it is possible to suppress an increase in resistance of the gas flowing in the multi-hole tube and an increase in material cost. Furthermore, it can be easily manufactured by conventional extrusion molding.

第２の発明によれば、上記仕切壁と略同等の板厚を有する水平な補強板を、上記左右側壁の各内面高さ中央と両端に配置した仕切壁との間にそれぞれ介設したことにより、多穴チューブの左右側壁を補強するとともに、左右側壁から両端の仕切壁までの範囲全体の剛性をも上げることが可能となり、熱歪みによる多穴チューブの破損を防止することができる。また、側壁全体の板厚を上げる対策に比べて管内断面積の減少が少なく済むため、多穴チューブ内を流れるガスの抵抗の増加と、材料費の増加を抑えることができる。さらに、従来の押出し成形によって容易に製造することができる。   According to 2nd invention, the horizontal reinforcement board which has a board thickness substantially equivalent to the said partition wall was each interposed between the partition walls arrange | positioned in the center of each inner surface height of the said right and left side walls, and both ends, respectively. Thus, it is possible to reinforce the left and right side walls of the multi-hole tube and to increase the rigidity of the entire range from the left and right side walls to the partition walls at both ends, and to prevent damage to the multi-hole tube due to thermal strain. In addition, since the reduction in the cross-sectional area in the tube is less than the measure for increasing the plate thickness of the entire side wall, it is possible to suppress an increase in resistance of the gas flowing in the multi-hole tube and an increase in material cost. Furthermore, it can be easily manufactured by conventional extrusion molding.

以下、本発明の実施形態に係る熱交換用多穴チューブについて、図面に基づいて説明する。
図１は第１実施形態に係るアルミ製の多穴チューブの断面図であり、図２は図１において破線で囲まれたＡ部の拡大図である。 Hereinafter, a multi-hole tube for heat exchange according to an embodiment of the present invention will be described based on the drawings.
FIG. 1 is a cross-sectional view of an aluminum multi-hole tube according to the first embodiment, and FIG. 2 is an enlarged view of a portion A surrounded by a broken line in FIG.

図１に示すように、多穴チューブは、平板状の上下壁１、１と、断面略半円状の左右の側壁２、２とからなる扁平管であり、内部を上下壁１、１の間に垂直に立てられた複数の仕切壁３で仕切られている。このため多穴チューブは、互いに仕切られて並行する複数の排気ガスの通路を有している。   As shown in FIG. 1, the multi-hole tube is a flat tube composed of flat upper and lower walls 1 and 1 and left and right side walls 2 and 2 having a substantially semicircular cross section. It is partitioned by a plurality of partition walls 3 standing vertically therebetween. For this reason, the multi-hole tube has a plurality of exhaust gas passages that are partitioned from each other in parallel.

高温の排気ガスの流通に伴う熱歪みに対する剛性を上げるため、側壁２は上下壁１および仕切壁３に比して肉厚に形成されている。ただし、側壁２の板厚は押出し成形の可能な厚さに止めるのが望ましい。
また、管内の表面積を増やして熱交換効率を向上させるため、通路に沿って延びる多数の突条４が、上下壁１、１の内面から内方に向かって突出している。 The side wall 2 is formed thicker than the upper and lower walls 1 and the partition wall 3 in order to increase the rigidity against thermal distortion accompanying the circulation of high-temperature exhaust gas. However, it is desirable that the thickness of the side wall 2 be limited to a thickness that allows extrusion.
Moreover, in order to increase the surface area in a pipe | tube and to improve heat exchange efficiency, many protrusions 4 extended along a channel | path protrude inward from the inner surface of the upper-and-lower walls 1 and 1. FIG.

図２に示すように、この多穴チューブの側壁２の内面高さ中央に位置する曲面部の頂点（多穴チューブの最側端）には、多穴チューブの幅方向内方に向けて突設したリブ５が、通路に沿って延びている。このリブ５は、上面と下面との交角Ｂを１０〜３０度とし、リブ５で最も厚い根元の厚さは、側壁２の厚さを超えないものとする。また、リブ５の先端を細く鋭く形成すると、多穴チューブ生産時の押出し成形の型の消耗が激しくなるため、先端は所定の太さで緩やかに丸みを帯びさせて形成する。   As shown in FIG. 2, the apex of the curved surface portion (the outermost end of the multi-hole tube) located at the center of the inner surface height of the side wall 2 of the multi-hole tube protrudes inward in the width direction of the multi-hole tube. The provided rib 5 extends along the passage. The rib 5 has an intersection angle B between the upper surface and the lower surface of 10 to 30 degrees, and the thickness of the thickest root of the rib 5 does not exceed the thickness of the side wall 2. Further, if the tip of the rib 5 is formed to be thin and sharp, the consumption of the extrusion mold during the production of the multi-hole tube becomes severe. Therefore, the tip is formed to be gently rounded with a predetermined thickness.

このように構成したことにより、第１実施形態の多穴チューブは押出し成形にて製造することができる。
また、左右側壁２、２の各内面高さ中央から内方へそれぞれ突出し、上面と下面との交角が１０〜３０度の先細り形状で先端が丸く、基部の厚さが扁平管の最厚部以下である断面形状を有する一対のリブ５、５を通路に沿って延設したことにより、多穴チューブの側壁２が補強されるため、高温の排気ガスの流通によって熱歪みが生じて多穴チューブが破損するのを防止することができる。また、側壁２全体の板厚を上げる対策に比べて管内断面積の減少が少なく済むため、多穴チューブ内を流れるガスの抵抗の増加と、材料費の増加を抑えることができる。
リブ５には、多穴チューブの内面の表面積を増やして熱交換を促進する効果もある。 By comprising in this way, the multi-hole tube of 1st Embodiment can be manufactured by extrusion molding.
Also, each of the left and right side walls 2 and 2 protrudes inward from the center of the inner surface of each of the inner walls, the angle between the upper surface and the lower surface is 10 to 30 degrees, the tip is round, and the thickness of the base is the thickest part of the flat tube Since the side walls 2 of the multi-hole tube are reinforced by extending a pair of ribs 5 and 5 having a cross-sectional shape as follows along the passage, thermal distortion occurs due to the circulation of high-temperature exhaust gas, and the multi-hole It is possible to prevent the tube from being damaged. In addition, since the reduction in the cross-sectional area in the tube can be reduced as compared with the measure for increasing the thickness of the entire side wall 2, it is possible to suppress an increase in resistance of gas flowing in the multi-hole tube and an increase in material cost.
The rib 5 also has an effect of promoting heat exchange by increasing the surface area of the inner surface of the multi-hole tube.

押出し成形にて製造する場合には、リブ５は多穴チューブの通路の全長にわたり成形されることになるが、熱歪みによる破損を防止する観点からは、リブ５は最低限、歪みの発生する多穴チューブの出入口からエンドプレート３０との接合部付近まで成形されていればよい。   In the case of manufacturing by extrusion molding, the rib 5 is molded over the entire length of the passage of the multi-hole tube, but from the viewpoint of preventing breakage due to thermal strain, the rib 5 generates distortion at a minimum. What is necessary is just to shape | mold from the entrance / exit of a multi-hole tube to the junction part vicinity with the end plate 30. FIG.

＜第２実施形態＞
第２実施形態として、側壁２からリブ５を突設する代わりに、左右側壁２、２とその内側に隣接する仕切壁３との間に、水平な補強板６を介設してもよい。
図３は第２実施形態に係るアルミ製の多穴チューブの断面図であり、図４は図３において破線で囲まれたＣ部の拡大図である。 <Second Embodiment>
As a second embodiment, instead of projecting the ribs 5 from the side walls 2, a horizontal reinforcing plate 6 may be interposed between the left and right side walls 2, 2 and the partition wall 3 adjacent to the inside.
FIG. 3 is a cross-sectional view of an aluminum multi-hole tube according to the second embodiment, and FIG. 4 is an enlarged view of a portion C surrounded by a broken line in FIG.

第２実施形態の多穴チューブも、上下壁１、１と左右側壁２、２と仕切壁３とを有する点は第１実施形態と同様である。しかし、左右側壁２、２の内面高さ中央からは、リブ５を設ける代わりに、内側に隣接する両端の仕切壁３、３との間に水平な補強板６、６をそれぞれ張り渡している。   The multi-hole tube of the second embodiment is the same as the first embodiment in that it has upper and lower walls 1, 1, left and right side walls 2, 2 and a partition wall 3. However, from the center of the inner surface height of the left and right side walls 2 and 2, horizontal reinforcing plates 6 and 6 are respectively stretched between the partition walls 3 and 3 at both ends adjacent to the inside instead of providing the rib 5. .

この補強板６の厚さは側壁２の厚さを超えないものとし、厚さが一定になるように設定する。仕切壁３と略同等の厚さに設定するのが好ましい。この補強板６により、多穴チューブ内の両側端の通路は上下に二分割される。
このように構成したことにより、第２実施形態の多穴チューブは押出し成形にて製造することができる。 The thickness of the reinforcing plate 6 does not exceed the thickness of the side wall 2 and is set so that the thickness is constant. It is preferable to set the thickness substantially equal to that of the partition wall 3. By this reinforcing plate 6, the passages at both ends in the multi-hole tube are vertically divided into two.
By comprising in this way, the multi-hole tube of 2nd Embodiment can be manufactured by extrusion molding.

また、仕切壁３と略同等の板厚を有する水平な補強板６を、上記左右側壁２、２の各内面高さ中央と両端に配置した仕切壁３、３との間にそれぞれ介設したことにより、多穴チューブの側壁２を補強するとともに、左右側壁２、２から両端の仕切壁３、３までの範囲全体の剛性をも上げることが可能となり、熱歪みによる多穴チューブの破損を防止することができる。また、側壁２全体の板厚を上げる対策に比べて管内断面積の減少が少なく済むため、多穴チューブ内を流れるガスの抵抗の増加と、材料費の増加を抑えることができる。   Further, horizontal reinforcing plates 6 having substantially the same thickness as the partition walls 3 are respectively interposed between the center of the inner surface height of the left and right side walls 2 and 2 and the partition walls 3 and 3 disposed at both ends. As a result, the side wall 2 of the multi-hole tube can be reinforced, and the rigidity of the entire range from the left and right side walls 2, 2 to the partition walls 3, 3 at both ends can be increased. Can be prevented. In addition, since the reduction in the cross-sectional area in the tube can be reduced as compared with the measure for increasing the thickness of the entire side wall 2, it is possible to suppress an increase in resistance of gas flowing in the multi-hole tube and an increase in material cost.

本発明の第１実施形態に係る多穴チューブの断面図である。It is sectional drawing of the multi-hole tube which concerns on 1st Embodiment of this invention. 図１のＡ部の拡大図である。It is an enlarged view of the A section of FIG. 本発明の第２実施形態に係る多穴チューブの断面図である。It is sectional drawing of the multi-hole tube which concerns on 2nd Embodiment of this invention. 図３のＣ部の拡大図である。It is an enlarged view of the C section of FIG. 従来の多穴チューブを示す断面図である。It is sectional drawing which shows the conventional multi-hole tube. 図５のＤ部の拡大図である。It is an enlarged view of the D section of FIG. 多穴チューブとエンドプレートとの取付構造を示す斜視図である。It is a perspective view which shows the attachment structure of a multi-hole tube and an end plate. 多穴チューブを用いたインタークーラを示す斜視図である。It is a perspective view which shows the intercooler using a multi-hole tube. 従来のインタークーラにおける多穴チューブの熱歪みを説明する図であり、（ａ）はインタークーラ不使用時の断面図、（ｂ）はインタークーラ使用時の断面図、（ｃ）は、（ｂ）の接合部付近の拡大図である。It is a figure explaining the thermal distortion of the multi-hole tube in the conventional intercooler, (a) is sectional drawing at the time of non-use of an intercooler, (b) is sectional drawing at the time of using an intercooler, (c) is (b) FIG.

符号の説明Explanation of symbols

１ 上下壁
２ 側壁
３ 仕切壁
４ 突条
５ リブ
６ 補強板
７ 接合部
８ 亀裂
１０ 多穴チューブ
２０ フィン
３０ エンドプレート
４０ ヘッダー DESCRIPTION OF SYMBOLS 1 Upper and lower walls 2 Side wall 3 Partition wall 4 Projection 5 Rib 6 Reinforcement plate 7 Joint part 8 Crack 10 Multi-hole tube 20 Fin 30 End plate 40 Header

Claims (2)

平板状の上下壁及び断面略半円状の左右側壁を有する扁平管と、
この扁平管の上下壁の間に介在する複数の垂直な仕切壁とからなり複数の通路を有する熱交換用多穴チューブにおいて、
上記左右側壁の各内面高さ中央から内方へそれぞれ突出し、上面と下面との交角が１０〜３０度の先細り形状で先端が丸く、基部の厚さが扁平管の最厚部以下である断面形状を有する一対のリブを通路に沿って延設したことを特徴とする熱交換用多穴チューブ。 Flat tubes having flat upper and lower walls and left and right side walls having a substantially semicircular cross section;
In the multi-hole tube for heat exchange consisting of a plurality of vertical partition walls interposed between the upper and lower walls of this flat tube and having a plurality of passages,
A cross section that protrudes inward from the center of the inner surface height of each of the left and right side walls, has a tapered shape with an angle of intersection of the upper surface and the lower surface of 10 to 30 degrees, has a rounded tip, and the thickness of the base portion is equal to or less than the thickest portion of the flat tube A multi-hole tube for heat exchange, wherein a pair of ribs having a shape are extended along a passage. 平板状の上下壁及び断面略半円状の左右側壁を有する扁平管と、
この扁平管の上下壁の間に介在する複数の垂直な仕切壁とからなり複数の通路を有する熱交換用多穴チューブにおいて、
上記仕切壁と略同等の板厚を有する水平な補強板を、上記左右側壁の各内面高さ中央と両端に配置した仕切壁との間にそれぞれ介設したことを特徴とする熱交換用多穴チューブ。 Flat tubes having flat upper and lower walls and left and right side walls having a substantially semicircular cross section;
In the multi-hole tube for heat exchange consisting of a plurality of vertical partition walls interposed between the upper and lower walls of this flat tube and having a plurality of passages,
A large number of heat exchangers, characterized in that horizontal reinforcing plates having substantially the same thickness as the partition walls are interposed between the center of the inner surface height of the left and right side walls and the partition walls disposed at both ends, respectively. Hole tube.
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JP2012154495A (en) * 2011-01-21 2012-08-16 Daikin Industries Ltd Heat exchanger, and air conditioner
CN102748978A (en) * 2012-07-05 2012-10-24 无锡金洋铝业有限公司 Asymmetrical flat tube for heat exchanger passage
JP2014020590A (en) * 2012-07-12 2014-02-03 Isuzu Motors Ltd Vehicular intercooler
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US20170211892A1 (en) * 2016-01-25 2017-07-27 Hanon Systems Tube for heat exchanger
KR20170088605A (en) * 2016-01-25 2017-08-02 한온시스템 주식회사 Exchanger
KR20170088746A (en) * 2016-01-25 2017-08-02 한온시스템 주식회사 A tube of heat exchanger

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JPS59205591A (en) * 1983-05-09 1984-11-21 Nippon Denso Co Ltd Heat exchanger
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Publication number Priority date Publication date Assignee Title
JP2012154495A (en) * 2011-01-21 2012-08-16 Daikin Industries Ltd Heat exchanger, and air conditioner
CN102748978A (en) * 2012-07-05 2012-10-24 无锡金洋铝业有限公司 Asymmetrical flat tube for heat exchanger passage
JP2014020590A (en) * 2012-07-12 2014-02-03 Isuzu Motors Ltd Vehicular intercooler
DE102014213088A1 (en) * 2014-07-04 2016-01-07 Mahle International Gmbh flat tube
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KR20170088605A (en) * 2016-01-25 2017-08-02 한온시스템 주식회사 Exchanger
KR20170088746A (en) * 2016-01-25 2017-08-02 한온시스템 주식회사 A tube of heat exchanger
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KR101982748B1 (en) * 2016-01-25 2019-05-28 한온시스템 주식회사 A tube of heat exchanger

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