JP2019132443A - Connection structure of tank for heat exchanger - Google Patents

Connection structure of tank for heat exchanger Download PDF

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JP2019132443A
JP2019132443A JP2018012413A JP2018012413A JP2019132443A JP 2019132443 A JP2019132443 A JP 2019132443A JP 2018012413 A JP2018012413 A JP 2018012413A JP 2018012413 A JP2018012413 A JP 2018012413A JP 2019132443 A JP2019132443 A JP 2019132443A
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slit
tank
claw portion
connection structure
curved surface
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JP7010715B2 (en
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聡 大友
Satoshi Otomo
聡 大友
喜彦 佐々木
Yoshihiko Sasaki
喜彦 佐々木
洋輝 遠山
Hiroki Toyama
洋輝 遠山
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T Rad Co Ltd
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T Rad Co Ltd
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Abstract

To improve supporting force of a claw portion and to prevent cracking at a bottom of the claw portion in a connection structure of a tank for a heat exchanger in which the claw portion is bent into an arc-shape.SOLUTION: An end portion adjacent to a slit 8, of a claw portion 6 is composed of a curved face 9 curved to be vertically disposed on an end face of a flange portion, and a locking edge 6a at a slit 8 side, of the curved face 9 is locked on the end face of the flange portion. The curved face 9 is expanded into a fan shape from the slit 8 side to an outer side, and a length C at an end edge side, of the curved face 9 is longer than a length D of the locking edge 6a at the slit 8 side.SELECTED DRAWING: Figure 5

Description

本発明は、タンク本体とその開口端を、シールパッキンを介して被嵌するプレートとの接合構造に関する。   The present invention relates to a joint structure between a tank body and a plate that fits an opening end of the tank body through a seal packing.

下記特許文献１に記載の締付け結合装置は、タンク本体とその開口端を被嵌するヘッダプレート（特許文献１の第２の部材（管板）に相当）とを具備し、タンク本体はその開口端の外周がフランジ状に突設される。そしてヘッダプレートの環状溝に、そのフランジ部がパッキンを介して嵌入される。
そのヘッダプレートは、環状溝の外周にその端縁から所定距離離れた位置にフランジ部に平行な多数のスリットが間欠的に形成され、そのスリットに隣接する端部がフランジ部に平行に塑性変形されて、平面視Ｕ字状の係止爪が形成される。そして、その係止爪のスリット側の端縁がフランジ部の平面に係止されるものである。 The tightening and coupling device described in Patent Document 1 below includes a tank body and a header plate (corresponding to the second member (tube plate) of Patent Document 1) that fits the opening end of the tank body. The outer periphery of the end protrudes in a flange shape. And the flange part is inserted in the annular groove of a header plate via packing.
The header plate is intermittently formed with a large number of slits parallel to the flange at a predetermined distance from the edge on the outer periphery of the annular groove, and the end adjacent to the slit is plastically deformed parallel to the flange. Thus, a locking claw having a U-shape in plan view is formed. And the edge by the side of the slit of the latching claw is latched by the plane of a flange part.

そのカシメ構造は、図１１に示す通りである。即ち、スリット８に隣接する端部を平面視で弧状に塑性変形し、その端縁をフランジ部に乗り上げて係止したものである。   The caulking structure is as shown in FIG. That is, the end portion adjacent to the slit 8 is plastically deformed in an arc shape in plan view, and the end edge rides on the flange portion and is locked.

特公昭５８−４２０６号公報Japanese Patent Publication No.58-4206 米国特許第４８８１５９５号明細書US Pat. No. 4,881,595

特許文献１に記載の発明は、その係止爪をフランジ部に乗り上げて係止するため、タンクの内圧および振動に対して、その根元部に応力集中が発生し易く、疲労亀裂を生じるおそれがある。
そこで、本発明はタンクに内圧および振動が作用しても、係止爪に亀裂が生じ難く、よって耐圧性および耐振性が高く信頼性の高い接続構造を提供することを課題とする。 Since the invention described in Patent Document 1 rides and locks the locking claw on the flange portion, stress concentration tends to occur at the base portion with respect to the internal pressure and vibration of the tank, and there is a risk of causing fatigue cracks. is there.
Therefore, an object of the present invention is to provide a highly reliable connection structure with high pressure resistance and vibration resistance even when internal pressure and vibration are applied to the tank, so that the claw is not easily cracked.

請求項１に記載の本発明は、一端が開口１とされ、その開口１の端部外周にフランジ部２が突設されているタンク本体３と、
そのタンク本体３のフランジ部２がシールパッキン４を介して被嵌されていると共に、前記フランジ部２の前記シールパッキン４と反対側の端面５を、爪部６でカシメ締結するプレート７と、を有する熱交換器用タンクの接続構造において、
前記プレート７の前記フランジ部２側の端部に、前記タンク本体３の前記端面５に平行なスリット８が形成されており、
前記爪部６は、スリット８に隣接する端部が、前記フランジ部２の前記端面５に立設するように湾曲する湾曲面９で形成されていると共に、その湾曲面９のスリット８側の係止縁６ａが前記フランジ部２の前記端面５に係止されており、
前記湾曲面９はスリット８側から外側に扇状に拡開されて、その湾曲面９の端縁側の長さＣとスリット８側の係止縁６ａの長さＤの関係が、Ｃ＞Ｄとなることを特徴とする熱交換器用タンクの接続構造である。 The present invention according to claim 1 includes a tank body 3 in which one end is an opening 1 and a flange portion 2 projects from an outer periphery of the end of the opening 1;
The flange portion 2 of the tank body 3 is fitted through a seal packing 4, and the end surface 5 opposite to the seal packing 4 of the flange portion 2 is caulked and fastened with a claw portion 6, In the connection structure of the tank for heat exchanger having
A slit 8 parallel to the end surface 5 of the tank body 3 is formed at an end of the plate 7 on the flange portion 2 side,
The claw portion 6 is formed with a curved surface 9 that is curved so that an end portion adjacent to the slit 8 stands on the end surface 5 of the flange portion 2, and the slit surface 8 on the curved surface 9 side. A locking edge 6a is locked to the end surface 5 of the flange portion 2,
The curved surface 9 is fanned outward from the slit 8 side, and the relationship between the length C of the edge side of the curved surface 9 and the length D of the locking edge 6a on the slit 8 side is C> D. It is the connection structure of the tank for heat exchangers characterized by becoming.

請求項２に記載の本発明は、前記爪部６の前記湾曲面９は、前記スリット８の長手方向の中心部において、前記フランジ部２の前記端面５に対して、その反対側が僅かにタンク本体３の外面側に傾斜していることを請求項１に記載の熱交換器用タンクの接続構造である。   According to the second aspect of the present invention, the curved surface 9 of the claw portion 6 is slightly tanked on the opposite side of the end surface 5 of the flange portion 2 at the center portion in the longitudinal direction of the slit 8. 2. The heat exchanger tank connection structure according to claim 1, wherein the heat exchanger tank is inclined toward the outer surface side of the main body 3.

本発明は、プレート７の爪部６がフランジ部２の端面５に立設して湾曲し、その湾曲面９が扇状に拡開されるように、その湾曲面９の端縁側の長さＣがスリット８側の係止縁６ａの長さＤより長く形成されているものである。そのため、爪部６に加わる荷重は、爪部６のスリット８側から放射方向外側に分散して支持される。それにより、爪部の変形および亀裂を防止し、タンクとプレートとの接続部の信頼性を向上できる。   In the present invention, the length C on the edge side of the curved surface 9 is such that the claw portion 6 of the plate 7 is erected and curved on the end surface 5 of the flange portion 2 and the curved surface 9 is expanded in a fan shape. Is longer than the length D of the locking edge 6a on the slit 8 side. Therefore, the load applied to the claw portion 6 is dispersed and supported from the slit 8 side of the claw portion 6 to the radially outer side. Thereby, deformation | transformation and a crack of a nail | claw part can be prevented and the reliability of the connection part of a tank and a plate can be improved.

請求項２に記載の発明は、前記爪部６の前記湾曲面９が端面５に対して、僅かにタンク本体３の外面側に傾斜しているものである。そのため、爪部６に荷重が加わった場合でも、爪部６はより開きにくくなっている。それにより、さらに、タンクとプレートとの接続部の信頼性を向上できる。   The invention according to claim 2 is such that the curved surface 9 of the claw portion 6 is slightly inclined with respect to the end surface 5 toward the outer surface of the tank body 3. Therefore, even when a load is applied to the claw portion 6, the claw portion 6 is more difficult to open. Thereby, the reliability of the connection part of a tank and a plate can be improved further.

本発明の熱交換器用タンクの接続構造の要部斜視図。The principal part perspective view of the connection structure of the tank for heat exchangers of this invention. 同熱交換器のタンクに用いられるタンク本体３であって、（Ａ）はタンク本体３の要部斜視図、（Ｂ）はその要部横断面図。It is the tank main body 3 used for the tank of the heat exchanger, Comprising: (A) is a principal part perspective view of the tank main body 3, (B) is the principal part cross-sectional view. 同構造のカシメ加工を示す説明図であって、（Ａ）はそのカシメ前の要部横断面図、（Ｂ）はカシメ後の要部横断面図。It is explanatory drawing which shows the crimping process of the structure, Comprising: (A) is the principal part cross-sectional view before the crimping, (B) is the principal part cross-sectional view after crimping. 同構造のカシメの説明図であって、（Ａ）はそのカシメ前の状態を示す水平方向の縦断面図、（Ｂ）はカシメ後の状態を示す水平方向の縦断面図。It is explanatory drawing of the crimping of the structure, Comprising: (A) is a horizontal longitudinal cross-sectional view which shows the state before the crimping, (B) is a horizontal longitudinal cross-sectional view which shows the state after crimping. （Ａ）は同カシメ後の正面図、（Ｂ）は（Ａ）の要部拡大図。(A) is a front view after caulking, and (B) is an enlarged view of the main part of (A). 同接続構造及び、従来構造における爪部６の引張試験結果を示し、横軸に爪部６の変位、縦軸に荷重を記載したものである。そして○印は本発明品の結果であり、■印は従来品の結果である。The tensile test result of the nail | claw part 6 in the same connection structure and a conventional structure is shown, The displacement of the nail | claw part 6 is written on the horizontal axis, and the load is written on the vertical axis. The ◯ marks indicate the results of the present invention product, and the ■ marks indicate the results of the conventional product. 本発明品と従来品との疲労試験結果を示すものである。そして横軸に１×１０５から１×１０６までの耐久回数を示し、縦軸にその荷重を示す。The fatigue test result with this invention product and a conventional product is shown. The horizontal axis indicates the number of durability times from 1 × 10 5 to 1 × 10 6 , and the vertical axis indicates the load. 本発明のタンクの支柱部１１の他の実施例を示す要部横断面図。The principal part cross-sectional view which shows the other Example of the support | pillar part 11 of the tank of this invention. 本発明の爪部６の他の実施例を示す要部横断面図。The principal part cross-sectional view which shows the other Example of the nail | claw part 6 of this invention. 同接続構造を有する熱交換器の斜視図。The perspective view of the heat exchanger which has the connection structure. 従来型接続構造の要部正面図。The principal part front view of the conventional connection structure.

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。   Next, embodiments of the present invention will be described with reference to the drawings.

図１は本発明の熱交換器用タンクの接続構造の要部斜視図であり、図２はそのタンク本体３の要部斜視図である。そして、図３はタンク本体３とプレート７との接続状態を示す要部縦断面図である。
本発明の熱交換器用タンクの接続構造は、図１に示す如く、プレート７とタンク本体３とを接続するものである。そのタンク本体３は、図２に示す如く、その開口１の外周にフランジ部２が環状に突設形成されている。また、フランジ部２に対して垂直な支柱部１１がタンク本体３の周方向に定間隔に突設されている。
支柱部１１は、図２（Ｂ）に示す如く、フランジ部２の外周から距離ｔ分だけオフセットされて突設されていることが好ましい。 FIG. 1 is a main part perspective view of a connection structure for a heat exchanger tank according to the present invention, and FIG. 2 is a main part perspective view of the tank main body 3. FIG. 3 is a longitudinal sectional view of a main part showing a connection state between the tank body 3 and the plate 7.
The connection structure for a heat exchanger tank according to the present invention connects the plate 7 and the tank body 3 as shown in FIG. As shown in FIG. 2, the tank body 3 has a flange portion 2 formed in a projecting manner on the outer periphery of the opening 1. In addition, struts 11 that are perpendicular to the flange 2 are projected at regular intervals in the circumferential direction of the tank body 3.
As shown in FIG. 2 (B), the support column 11 is preferably provided so as to be offset from the outer periphery of the flange unit 2 by a distance t.

プレート７は、この実施例では筒状のケーシングからなる。そして、ケーシングの開口縁に近接して多数のスリット８が定間隔に配置され、そのスリット８はプレート７の端縁に平行に形成されている。このスリット８に隣接する端縁により爪部６が形成される。このプレート７は、図３に示す如く、その端部の内周に内ブラケット１４がろう付固定されている。その内ブラケット１４は環状に形成されており、その横断面が鈎形に曲折されている。そして、内ブラケット１４とプレート７の内面との間に環状溝が形成されており、そこにシールパッキン４が装着されている。   The plate 7 consists of a cylindrical casing in this embodiment. A large number of slits 8 are arranged at regular intervals in the vicinity of the opening edge of the casing, and the slits 8 are formed in parallel to the edge of the plate 7. A claw portion 6 is formed by an edge adjacent to the slit 8. As shown in FIG. 3, an inner bracket 14 is brazed and fixed to the inner periphery of the end of the plate 7. The inner bracket 14 is formed in an annular shape, and its cross section is bent into a bowl shape. An annular groove is formed between the inner bracket 14 and the inner surface of the plate 7, and the seal packing 4 is attached thereto.

また、内ブラケット１４の内側には、ヘッダプレートを必要としないコア１３が配置されている。このコア１３は、両開口の端部が厚み方向に拡開されている膨出部１６を有する偏平チューブ１５の積層体からなる。各偏平チューブ１５の膨出部１６の外面と内ブラケット１４とプレート７の接触部が一体にろう付け固定されている。
図３（Ａ）に示す如く、プレート７と内ブラケット１４の間に形成された環状溝にシールパッキン４を介して、タンク本体３のフランジ部２が内ブラケット１４に配置されている。タンク本体３のフランジ部２は、プレート７のスリット８に隣接する端部の湾曲面９からなる爪部６により係止されている。 A core 13 that does not require a header plate is disposed inside the inner bracket 14. This core 13 consists of a laminated body of the flat tube 15 which has the bulging part 16 by which the edge part of both opening was expanded in the thickness direction. The outer surface of the bulging portion 16 of each flat tube 15 and the contact portion between the inner bracket 14 and the plate 7 are integrally brazed and fixed.
As shown in FIG. 3A, the flange portion 2 of the tank body 3 is disposed on the inner bracket 14 via a seal packing 4 in an annular groove formed between the plate 7 and the inner bracket 14. The flange portion 2 of the tank body 3 is locked by a claw portion 6 formed of a curved surface 9 at an end portion adjacent to the slit 8 of the plate 7.

図４（Ａ）（Ｂ）は、その爪部６のカシメ工程を順に示す、説明図であり、カシメ治具１７を矢印方向に移動することにより、プレート７のスリット８に隣接する縁部を湾曲に塑性変形して、その端部をタンク本体３の外面に接触させる。そして、図３（Ｂ）に
示す如く、その爪部６の係止縁６ａが、フランジ部２の端面５に係止されている。
前記塑性変形に際して、プレート７は図４（Ｂ）に示す如く、スリット８に隣接する縁部の中間位置が周方向に離間する一対の支柱部１１との間に位置している。
その塑性変形後の爪部６は、図５（Ａ）の正面図に示す如く、その係止縁６ａを基準として、その変形部が扇形に拡開された湾曲面９を有する形状である。即ち、図５（Ｂ）に示す如く、爪部６の湾曲面９は、湾曲面９のスリット８側の係止縁６ａの長さＤと湾曲面９の先端縁の長さＣとの関係が、Ｃ＞Ｄとなっており、湾曲面９の両端の開き角度θは、鋭角となる。 4 (A) and 4 (B) are explanatory views showing the caulking process of the claw portion 6 in order. The edge adjacent to the slit 8 of the plate 7 is moved by moving the caulking jig 17 in the direction of the arrow. It is plastically deformed into a curve, and its end is brought into contact with the outer surface of the tank body 3. As shown in FIG. 3B, the locking edge 6 a of the claw portion 6 is locked to the end surface 5 of the flange portion 2.
During the plastic deformation, as shown in FIG. 4B, the plate 7 is positioned between a pair of support columns 11 in which an intermediate position of an edge adjacent to the slit 8 is separated in the circumferential direction.
As shown in the front view of FIG. 5A, the claw portion 6 after the plastic deformation has a shape having a curved surface 9 in which the deformed portion is expanded in a fan shape with the locking edge 6a as a reference. That is, as shown in FIG. 5B, the curved surface 9 of the claw portion 6 has a relationship between the length D of the locking edge 6 a on the slit 8 side of the curved surface 9 and the length C of the leading edge of the curved surface 9. However, C> D, and the opening angle θ at both ends of the curved surface 9 is an acute angle.

図１および図３（Ｂ）に示す如く、各スリット８間をつなぐ各架橋部１９を根元にして、各架橋部１９からプレート７の先端縁にかけて、タンク本体３の支柱部１１側に倒れ込むように、僅かに傾斜（図３（Ｂ）の傾斜角度αを参照）していることが好ましい。これにより、容易にＣ（湾曲面９の先端縁の長さ）＞Ｄ（湾曲面９のスリット８側の係止縁６ａの長さ）、とすることができる。
各架橋部１９からプレート７の先端縁にかけての傾斜を形成する場合、支柱部１１をランジ部２の外周から距離ｔ分だけオフセットさせて突設したオフセット型の形状とする手段を用いることができる（図２（Ｂ））。この手段により、カシメの際、各架橋部１９からプレート７の先端縁にかけて容易に傾斜させることができる。また、支柱部１１の形状をオフセット型とする代わりに、図８に示す如く、フランジ部２の端面５から離れるにしたがって先細りする傾斜面としても、同様の効果が得られる。 As shown in FIG. 1 and FIG. 3 (B), the bridges 19 connecting the slits 8 are rooted, and the bridges 19 fall from the bridges 19 to the leading edge of the plate 7 toward the support column 11 of the tank body 3. In addition, it is preferable that it is slightly inclined (see the inclination angle α in FIG. 3B). Thereby, it is possible to easily satisfy C (length of the leading edge of the curved surface 9)> D (length of the locking edge 6a on the slit 8 side of the curved surface 9).
In the case of forming an inclination from each bridging portion 19 to the leading edge of the plate 7, it is possible to use an offset-type shape in which the column portion 11 is protruded by being offset from the outer periphery of the lung portion 2 by a distance t. (FIG. 2 (B)). By this means, the caulking can be easily inclined from each bridging portion 19 to the tip edge of the plate 7. Moreover, the same effect is acquired also as an inclined surface which tapers as it leaves | separates from the end surface 5 of the flange part 2, as shown in FIG.

この実施例によれば、タンク本体３の内圧および振動による爪部６への荷重は、爪部６の係止縁６ａに加わり、その爪部６は僅かに傾斜し且つ、拡開されているため、爪部６の全体に分散して支持される。
図６は、この実施例の爪部６の引張試験結果の一例を示し、その爪部６に、それをタンク３の外面から引離す加重を加えたときの加重と、その変位との関係を示す。また、図７は、その疲労試験結果の一例を、耐久回数と加重との関係で表したものである。
図７のグラフの横軸の目盛１．Ｅ＋０５、１．Ｅ＋０６は、それぞれ１×１０５、１×１０６を意味する。
これらのデータから、この実施例による爪部６の支持強度は、図１１の従来型の爪部の支持強度よりも高いことが確認できる。 According to this embodiment, the load on the claw portion 6 due to the internal pressure and vibration of the tank body 3 is applied to the locking edge 6a of the claw portion 6, and the claw portion 6 is slightly inclined and expanded. Therefore, the nail part 6 is supported dispersedly.
FIG. 6 shows an example of the tensile test result of the claw portion 6 of this embodiment, and the relationship between the load when the load that separates the claw portion 6 from the outer surface of the tank 3 and the displacement is shown. Show. FIG. 7 shows an example of the fatigue test result in terms of the relationship between the number of durability times and the weight.
Scale on the horizontal axis of the graph of FIG. E + 05, 1. E + 06 means 1 × 10 5 and 1 × 10 6 , respectively.
From these data, it can be confirmed that the support strength of the claw portion 6 according to this embodiment is higher than the support strength of the conventional claw portion of FIG.

図９は、図３（Ｂ）の爪部６の他の例である。
その違いは、図３（Ｂ）の爪部６の湾曲面９が、スリット８の長手方向の中心部において、タンク本体３の側壁に接しているのに対し、この例では、爪部６の湾曲面９が、フランジ部２の端面５に対して、湾曲面９の先端縁のみがタンク本体３の側壁に接しており、そのスリット８側の係止縁６ａが傾斜してフランジ部２の端面５に接している。
そのため、タンク本体３の内圧および振動により、爪部６に荷重が加わった場合でも、爪部６はより開きにくくなっている。それにより、さらに、タンクとプレートとの接続部の信頼性が向上する。 FIG. 9 shows another example of the claw portion 6 shown in FIG.
The difference is that the curved surface 9 of the claw portion 6 in FIG. 3B is in contact with the side wall of the tank body 3 at the center in the longitudinal direction of the slit 8, whereas in this example, the claw portion 6 The curved surface 9 is in contact with the side wall of the tank body 3 with respect to the end surface 5 of the flange portion 2, and the locking edge 6 a on the slit 8 side is inclined to incline the flange portion 2. It is in contact with the end face 5.
Therefore, even when a load is applied to the claw portion 6 due to the internal pressure and vibration of the tank body 3, the claw portion 6 is more difficult to open. Thereby, the reliability of the connection part of a tank and a plate improves further.

本願における各発明の熱交換器用タンクの接続構造は、一例として図１０に示すようなチャージエアクーラの他、ラジエータ、ＥＧＲクーラ、排熱回収器などの熱交換器に利用することができる。   The connection structure of the heat exchanger tank of each invention in the present application can be used for a heat exchanger such as a radiator, an EGR cooler, an exhaust heat recovery unit, in addition to a charge air cooler as shown in FIG. 10 as an example.

１ 開口
２ フランジ部
３ タンク本体
４ シールパッキン
５ 端面
６ 爪部
６ａ 係止縁
７ プレート
８ スリット
９ 湾曲面 DESCRIPTION OF SYMBOLS 1 Opening 2 Flange part 3 Tank main body 4 Seal packing 5 End surface 6 Claw part 6a Locking edge 7 Plate 8 Slit 9 Curved surface

１１ 支柱部
１３ コア
１４ 内ブラケット
１５ 偏平チューブ
１６ 膨出部
１７ カシメ治具
１８ カシメ曲線
１９ 架橋部
Ｃ 長さ
Ｄ 長さ
ｔ 距離
θ 開き角度
α 傾斜角度 DESCRIPTION OF SYMBOLS 11 Support | pillar part 13 Core 14 Inner bracket 15 Flat tube 16 A bulging part 17 A crimping jig | tool 18 A crimping curve 19 Bridging part C Length D Length t Distance (theta) Opening angle (alpha) Inclination angle

Claims (2)

一端が開口（１）とされ、その開口（１）の端部外周にフランジ部（２）が突設されているタンク本体（３）と、
そのタンク本体（３）のフランジ部（２）がシールパッキン（４）を介して被嵌されていると共に、前記フランジ部（２）の前記シールパッキン（４）と反対側の端面（５）を、爪部（６）でカシメ締結するプレート（７）と、を有する熱交換器用タンクの接続構造において、
前記プレート（７）の前記フランジ部（２）側の端部に、前記タンク本体（３）の前記端面（５）に平行なスリット（８）が形成されており、
前記爪部（６）は、スリット（８）に隣接する端部が、前記フランジ部（２）の前記端面（５）に立設するように湾曲する湾曲面（９）で形成されていると共に、その湾曲面（９）のスリット（８）側の係止縁（６ａ）が前記フランジ部（２）の前記端面（５）に係止されており、
前記湾曲面（９）はスリット（８）側から外側に扇状に拡開されて、その湾曲面（９）の端縁側の長さ（Ｃ）とスリット（８）側の係止縁（６ａ）の長さ（Ｄ）の関係が、Ｃ＞Ｄとなることを特徴とする熱交換器用タンクの接続構造。 One end of the tank body (3) has an opening (1), and a flange (2) projects from the outer periphery of the opening (1).
The flange portion (2) of the tank body (3) is fitted through the seal packing (4), and the end surface (5) opposite to the seal packing (4) of the flange portion (2) is provided. In the connection structure of the tank for the heat exchanger having the plate (7) to be swaged with the claw portion (6),
A slit (8) parallel to the end surface (5) of the tank body (3) is formed at the end of the plate (7) on the flange (2) side,
The claw portion (6) is formed with a curved surface (9) that is curved so that an end portion adjacent to the slit (8) is erected on the end surface (5) of the flange portion (2). The locking edge (6a) on the slit (8) side of the curved surface (9) is locked to the end surface (5) of the flange portion (2),
The curved surface (9) is fanned outward from the slit (8) side, and the length (C) of the curved surface (9) on the edge side and the locking edge (6a) on the slit (8) side are expanded. The connection structure of the tank for heat exchangers, wherein the relationship of the length (D) is C> D. 前記爪部（６）の前記湾曲面（９）は、前記スリット（８）の長手方向の中心部において、前記フランジ部（２）の前記端面（５）に対して、その反対側が僅かにタンク本体（３）の外面側に傾斜していることを請求項１に記載の熱交換器用タンクの接続構造。   The curved surface (9) of the claw portion (6) is slightly tanked on the opposite side to the end surface (5) of the flange portion (2) at the center in the longitudinal direction of the slit (8). The connection structure for a tank for a heat exchanger according to claim 1, wherein the connection structure is inclined toward the outer surface of the main body (3).
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59199131A (en) * 1983-04-26 1984-11-12 Toyo Radiator Kk Production of tank for heat exchanger
US20160370131A1 (en) * 2015-06-18 2016-12-22 Borgwarner Emissions Systems Spain, S.L.U. 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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59199131A (en) * 1983-04-26 1984-11-12 Toyo Radiator Kk Production of tank for heat exchanger
US20160370131A1 (en) * 2015-06-18 2016-12-22 Borgwarner Emissions Systems Spain, S.L.U. 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

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