JPS58148393A - Heat exchanger - Google Patents

Abstract

PURPOSE:To prevent stress corrosion cracking of core plates effectively, by using an I-ring as an elastic seal member, and sealing the interface between the core plates and a tank in a reliable manner without rendering the peak value of pressure at the contact surface too high. CONSTITUTION:A radiator of this invention comprises a metal core section 1 including corrugated fins 7 of copper and brass tubes 8. In assembling the radiator, a coupling portion 10 formed at the marginal portion of a tank 2 is fitted into a groove 20. Here, the inner and the outer side wall surfaces 13, 14 of the coupling portion 10 are respectively held in engagement with the inner and the outer side walls 17, 18 of the groove 20, and an elastic seal member 30 is interposed between the inner work surface 11 of the coupling portion 10 and the inner surface of the bottom wall 19 of the groove 20. The elastic seal member 30 is shaped in the form of a packing (I-ring) having a recess 30a curved smoothly in the side faces A of its rectangular cross section, and the interface is sealed by compressing the I-ring 30 to a prescribed compression ratio (8-40%).

Description

【発明の詳細な説明】 をかしめ作業によって取付は九熱交換器の改良に関し、
例えば自動車用フジエータに用いて好適なものである。[Detailed Description of the Invention] Regarding the improvement of a heat exchanger, which can be installed by caulking work,
For example, it is suitable for use in automobile fugiators.

コア部端面にコアプレートを設け，このコアプレートの
外周縁を溝形に成形し，この溝内に、合成＊ｍ製タンク
の端縁に設は友，ほぼ四角形断面の取付部を嵌合させ，
コアプレートのｍｅ部の外面に係合したかしめグレート
をこの取付部にかしめることによってタンクを本体ＫＷ
！封装着する形式の熱交換器は公知である。満に嵌合し
たタンク端縁取付部の底面と溝底面との聞に＃′ｉ弾性
シーｙ材が設置しであるが、この弾性シール材の直下の
溝底壁を構成しているコアプレート部分に、水質の纏い
冷却水を用い九ときなどに．ｍれが生じ。A core plate is provided on the end face of the core part, the outer periphery of this core plate is formed into a groove shape, and a mounting part with a substantially square cross section is fitted into the groove, which is attached to the edge of the synthetic*m tank. ，
By caulking the caulking grating that is engaged with the outer surface of the me part of the core plate to this attachment part, the tank can be attached to the main body KW.
! Heat exchangers of the sealed type are known. A #'i elastic seal material is installed between the bottom surface of the fully fitted tank edge attachment part and the groove bottom surface, and the core plate that constitutes the groove bottom wall directly below this elastic seal material. Use high-quality cooling water to cool the parts. A mishap occurred.

熱交換器の寿命が短かくなることがあった。これが応力
腐食割れであることを本発明者らはつきとめ丸。応力腐
食割れというのは、腐食という化学的な働きと応力とい
う物理的な働きの相乗作用によって生じる割れのことで
ある。The life of the heat exchanger could be shortened. The inventors discovered that this was stress corrosion cracking. Stress corrosion cracking is cracking that occurs due to the synergistic effect of the chemical action of corrosion and the physical action of stress.

本発明の目的はこのような応力腐食割れを防いで前記形
式の熱交ＪＩｌ＃１の寿命を延ばすことＫある。An object of the present invention is to prevent such stress corrosion cracking and extend the life of the heat exchanger JIl #1 of the type described above.

以下、添付図面な参隔しながらより詳しく説明する。A more detailed explanation will be given below with reference to the accompanying drawings.

第１図は本発明に係る熱交換器、たとえば自動車用フジ
エータを示しており、フジエータは鋼製のコルゲートフ
ィン７と黄銅製のチューブ虐を含む金属製のコア！Ｉｌ
とその上、下端に書画装着し九合成１１＃製のタンクｇ
、３とを包含する。上方のタンク８には冷却水補給口４
と冷却水直入バイブ６とが設けてあり、下方タンク８に
は冷却水流出パイプ６が設けであるが、基本的に上、下
のタンクは同じ構造であるから、以下、上方のタンク１
についてのみ説明する。上下を逆にして考えれば、以下
の説明は下方タンク８にも適用できることは了解された
い。FIG. 1 shows a heat exchanger according to the present invention, for example a fugiator for an automobile, and the fugiator has a metal core including corrugated fins 7 made of steel and tubes made of brass! Il
And on top of that, there is a tank g made of 9 synthetic 11 # with calligraphy attached to the bottom end.
, 3. There is a cooling water supply port 4 in the upper tank 8.
The lower tank 8 is provided with a cooling water outflow pipe 6, but since the upper and lower tanks basically have the same structure, the upper tank 1 will be described below.
I will only explain about. It should be understood that the following explanation can also be applied to the lower tank 8 if considered upside down.

第８図はタンク８をコア部ＩＫＶＩ封装着する従来方法
を示しており、タンク８は一端闘故となっており、これ
をフルゲートフィンテの付い友チューブ８から成るコア
部ｌの端部にかぶせることによってタンク１が完全とな
る。タンクＯ開披端縁の金屑に沿ってほぼ四角形断面の
取付１１ｘｏが設けである。この取付部ｌＯは互に平行
で平ら表表面を持つ内、外の作用面１１．１１とこれら
内外作用面に対して直角の内、外のＳｔｍ面１８．１４
とを有する。Figure 8 shows the conventional method of sealing the tank 8 to the core part IKVI. Tank 1 is completed by covering it. A mounting 11xo having a substantially square cross section is provided along the metal scrap on the open edge of the tank O. This mounting part lO has inner and outer working surfaces 11.11 that are parallel to each other and have flat surfaces, and inner and outer Stm surfaces 18.14 that are perpendicular to these inner and outer working surfaces.
and has.

コア部ｌ、具体的ＫＦｉチューブ７の端ｉ１にはその上
端付近で周方向に黄＃＃のコアデレー）１６が過当な手
段、たとえば半田付、ろう付は等で１着しである。コア
プレー）ＩＩＩの外周１ｉ＊Ｆｉ内、外の１１１１Ｉ１
１７，１ｇおよび戚纏１９を有するｍｓｇ。At the core portion l, specifically at the end i1 of the KFi tube 7, a yellow core (##) 16 is attached in the circumferential direction near its upper end by an appropriate means such as soldering, brazing, etc. Core play) III outer circumference 1i*Fi inside and outside 1111I1
17.1g and msg with 19.

となるように成形しである。It is molded to look like this.

組立時、＃１部ｇｏにタンク８の端縁取付部１０が嵌め
込まれ、このとき、取付ｓ１０の内、外の一壁面１８．
１４はそれぞれ溝部ｇｏの内、外の１＋１１１１１１７
．１８と保合し、取付部ｌＯの内方作用面１１と＃錫酸
１＄１１９の内面との関にはゴム製０リングからなる弾
性シール材ｇ１が設置される。During assembly, the edge attachment part 10 of the tank 8 is fitted into the #1 part go, and at this time, one of the inner and outer wall surfaces 18. of the attachment s10 is fitted.
14 is 1+1111117 inside and outside of the groove go, respectively.
．． 18, and an elastic sealing material g1 made of a rubber O-ring is installed between the inner working surface 11 of the attachment part 10 and the inner surface of the #stannic acid 1$119.

次に、ｊｊ［縁につめｌ５ｓｓを有するほぼＬ字形（図
では違り字形になっているが１反対軸ではＬ字形である
）の断面を持つ鉄Ｉｔｉ製のかしめプレート８３をコア
プレー）１６の溝部２０に係合させ、つめ部１龜をタン
ク１の端縁取付部１０の外方作用面１１１に向ってかし
める。その結果、タンク端縁取付部１０はその内方作用
面１１で弾性シール材２１を変形すると共にコアグレー
）１１１の調部ｇＯＫ竪固に９１封装着されるととＫな
る。Next, jj [a core play of a caulking plate 83 made of iron Iti having an approximately L-shaped cross section (in the figure, it is a different shape, but it is L-shaped on the opposite axis) with a tab l5ss on the edge) It is engaged with the groove part 20 and the pawl part 1 is caulked toward the outward working surface 111 of the edge attachment part 10 of the tank 1. As a result, the tank edge attachment portion 10 deforms the elastic sealing material 21 on its inner working surface 11, and the adjustment portion of the core gray) 111 is vertically and firmly sealed.

しかしながら、以上の構成においては２本発明者等の研
究によればタンクｇの内部ムに存在する冷却水が、コア
グレート溝部８０の内面、タンク取付け１ｌＮｏの内面
および弾性シー〜＃８１の表面でＳＳ、された徽小空閾
８４に浸透することによ少、コアプレート１９にすきま
腐食１ｉｎｉが生じることが確かめられた。However, in the above configuration, according to research by the present inventors, the cooling water existing in the internal chamber of the tank g is distributed on the inner surface of the core grate groove 80, the inner surface of the tank attachment 1lNo., and the surface of the elastic seam #81. It was confirmed that crevice corrosion 1 ini occurred in the core plate 19 due to penetration into the SS and small space threshold 84.

すなわち、すきま部２４に溜った熱交換流体は弾性Ｖ−
ル材ｉｌｌの下面とコアグレー）１９の内面とで形成さ
れたすきｔ＠５ｉ６ｃ、毛細管現象および弾性ンーｐｖ
ｓｓｌが圧縮固定されることによって生ずる接面圧力の
バランスによって浸透する。That is, the heat exchange fluid accumulated in the gap 24 has an elasticity V-
The gap t@5i6c formed between the lower surface of the core material ill and the inner surface of the core gray) 19, capillarity and elasticity pv
Penetration occurs due to the balance of contact pressure created by compressing and fixing SSL.

そして、すきま部ｓｈＫ浸入した熱交換流体は。And the heat exchange fluid that entered the gap shK.

その中の腐食性成分が拡散しにくい上に、ＩＲ鋼製のコ
アプレート表面の不ａｍ皮膜（酸化皮膜）はその不＃態
を保持しようとしてすきま部ｓ６の液体中の酸素を消費
し、そのためすきま部ｊ５内の液体と微小空間ｓ４内の
液体との間に酸素の濃度差が生じ、酸素濃淡電池が形成
される。特に、自動車用フジエータとして用いる場合に
は、熱交換流体となるエンジン冷却水中に、アミン・ア
ンモニア等の腐食成分が含まれている為、電池の作用に
よりすきま部ｌｂ内の液体のＰＭが低下し、との結果生
じる腐食Ｓ境は非常にきびしいものとなる。In addition, the corrosive components therein are difficult to diffuse, and the atomized film (oxide film) on the surface of the IR steel core plate consumes oxygen in the liquid in the gap s6 in an attempt to maintain its amorphous state. A difference in oxygen concentration occurs between the liquid in the gap j5 and the liquid in the micro space s4, and an oxygen concentration battery is formed. In particular, when used as an automobile fugiator, the engine cooling water that serves as the heat exchange fluid contains corrosive components such as amines and ammonia, so the PM of the liquid in the gap lb decreases due to the action of the battery. , the resulting corrosion S boundary is very severe.

それに加えて、前述したゴム製ローリングからなる弾性
Ｓ／−ｕ材ｆｉｌを逸富＠〜４０ｊ１１４１度圧−固定
しているのて、第８図に示す様に、窒−リンダを一定圧
Ｊ１＊まで圧縮することによって生ずる綾触＃Ｊ（コア
プレー）１９）への接触面押圧力ＰＩが部分的に加わる
仁とになる。従って、この圧力ＰＩＫＴｏ交換器内の系
統圧ｒ２が加って生ずる接面圧力ＰｍＯは一−リング直
下のコアデレー）１９の内部に特に大きな背型を加えて
いる。以上の条件下で、コアプレート溝部ｓＯの底１１
１１９では。In addition, since the elastic S/-u material fil made of the rubber rolling mentioned above is fixed at a pressure of 1141 degrees, the nitrogen cylinder is kept at a constant pressure of J1* as shown in FIG. The contact surface pressing force PI on the twill contact #J (core play) 19), which is generated by compressing the core to 19), is partially applied. Therefore, the contact pressure PmO generated by adding the system pressure r2 in the pressure PIKTo exchanger applies a particularly large back shape to the inside of the core 19 directly below the first ring. Under the above conditions, the bottom 11 of the core plate groove sO
At 119.

きびしい腐食環境と過大な応力とがあいまって、応力腐
食割れが容易に生ずることは明らかである。It is clear that the combination of a harsh corrosive environment and excessive stress easily causes stress corrosion cracking.

本発明者等はこの事実に初めて気付き種々の実験の結果
１本発明に到達した。その際、アミン・アンモニア等の
成分を多く含むエンジン冷却水を熱交換鑞体として用い
九場合に１割れ寿命の縮化が着しくなることも併せて！
認した。The present inventors noticed this fact for the first time, and as a result of various experiments, they arrived at the present invention. At that time, if engine cooling water containing a large amount of components such as amines and ammonia is used as a heat exchange solder, the service life will be shortened by one crack!
Approved.

そこで本発明においては、弾性シー３部材ｇｌを、第４
図に示すように、四角形状の断面の側面イに内方に向っ
て、なめらかな曲率で゛へこんだ凹１１ａｏａを有する
パツキンａＯ（以下、Ｉ型リングという）とし、このｌ
型リング８Ｇを第６図に示す如く、前述のローリングの
場合と同様に一定（８〜４０％）の圧縮率に圧縮しＶ−
ルを行々う。Therefore, in the present invention, the elastic seam 3 member gl is
As shown in the figure, the packing ring aO (hereinafter referred to as I-type ring) has a recess 11aoa inwardly recessed with a smooth curvature on the side surface A of a square cross section.
As shown in FIG. 6, the mold ring 8G is compressed to a constant compression ratio (8 to 40%) in the same way as in the case of rolling described above, and V-
Let's go to Ru.

前述のＩｎリング８０を圧縮することによって生ずる１
ａＬｊｌｉ圧力Ｐａｌの大きさは四部ａｏａの形状。1 produced by compressing the aforementioned In ring 80.
The size of aLjli pressure Pal has the shape of a four-part aoa.

すなわち凹部の深さく第４図中Ｗ３）と−率ＩＫよって
自在に―節可能である。そして、こＯ綾向圧力ｒｍｘの
ピーク値を従来の蒙−リングによる接面圧力ＰｍＯより
小さくするととによって、コアプレー）１ｇ１に生ずる
内部の応力を低減する。That is, it can be freely articulated depending on the depth of the recess (W3) in FIG. 4 and the ratio IK. By making the peak value of the axial pressure rmx smaller than the contact pressure PmO by the conventional ring, the internal stress generated in the core play 1g1 is reduced.

また、圧縮時の■型すンダＯコアプレート１９との接触
長さＩを従来の豐−リングのそれよりも長くすることが
可能であり、そのことによって、徽小空関８４内の冷却
液がすきｔ＠２５に浸透する深さが接面圧力Ｐ　ｍ　Ｉ
の分布上、ピーク接面圧力Ｓｔで達しない様にすること
が可能となる。この二つの働きの相乗効果により、応力
腐食割れ寿命を大幅に向上することができる。In addition, it is possible to make the contact length I with the ■-type Sunda O core plate 19 during compression longer than that of the conventional toe ring. The depth of penetration into the gap t@25 is the contact pressure P m I
Due to the distribution of , it is possible to prevent the peak contact pressure St from reaching the peak contact pressure St. The synergistic effect of these two functions can significantly improve stress corrosion cracking life.

尤も、単に応力腐食割れ寿命を伸ばすだけ０回的であれ
ば、接面圧力Ｐｍを下げればよいのであるが、Ｊｌ！面
圧力！−をあまシ下けては当然ながらシー〜が不充分と
なり洩れが発生することになる。Of course, if all you want to do is extend the life of stress corrosion cracking, all you need to do is lower the contact pressure Pm, but Jl! Surface pressure! If - is lowered, of course, the value of - will be insufficient and leakage will occur.

従って、良好なシールを保ちながら応力腐食割れ寿命を
伸ばすには、第６図に示すように必費充分１に接面圧力
Ｐｄを維持しつつ、かつピーク接面圧力はめ１０高くし
すぎなりようＫするのが望しい。Therefore, in order to extend the stress corrosion cracking life while maintaining a good seal, it is necessary to maintain the contact pressure Pd at a sufficient level of 1 and increase the peak contact pressure 10 too high, as shown in Figure 6. It is desirable to do K.

そＯ為にも、本発明の■型リングのように接触長さＩを
長くして、ピーク接面圧力があまり突出し表いようにす
ると都合がよい。崗、第６図αは弾性シーに部材１１と
してＯリングを用いた場合のピーク接面圧力ＰＩＩＩＯ
を示し、図中βはＩ型リング３０を用いた場合のピーク
接面圧力Ｐａ１ｔ示す・ また、熱交換器の冷却波系統圧ＰＩによってタンク８は
第７図に示す一点鎖纏の如く変形するのであるが、その
時、タンク８の取付は部１０の中心０と１弾性シール材
２１の圧縮によって生ずる反力Ｎｏ葡菖方向との間にズ
レが生じれば、反力ｌによってモーメン）Ｍが矢印の如
く回転変位とな）、その結果コアプＶ−Ｆｉｌｌ＠１＠
を変形させ。For this reason, it is advantageous to make the contact length I longer, as in the case of the ■-shaped ring of the present invention, so that the peak contact pressure does not protrude too much. Figure 6 α shows the peak contact pressure PIIIO when an O-ring is used as the member 11 in the elastic seam.
In the figure, β indicates the peak contact pressure Pa1t when the I-type ring 30 is used. Also, the tank 8 is deformed like a chain chain as shown in Figure 7 due to the cooling wave system pressure PI of the heat exchanger. However, at that time, when mounting the tank 8, if there is a deviation between the center 0 of the part 10 and the direction of the reaction force No. 1 caused by the compression of the elastic sealing material 21, the moment) M will be (rotational displacement as shown by the arrow), resulting in corep V-Fill@1@
Transform it.

コアプレー）１９の内面に応力を生ぜしめる。core play) creates stress on the inner surface of 19.

しかしながら、その場合であっても１弾性シール材ｇｌ
としてＩＪシリング０を用いれば、前述／Ｑｌ の如く反力Ｉが殉−リングに比べ小さくなり、しかも、
ζ−りングに比ベコアブレート一部内での組付けによる
パフツキの範囲も小さく、そのため取付部１Ｇ中心Ｏと
反力ｙｏ＊＊ａとのズレ本手さくなるので、モーメント
ＭＫよる応力腐食割れも生じに〈〈なっている。However, even in that case, 1 elastic sealing material
If IJ Schilling 0 is used as
Compared to the ζ-ring, the range of puffiness caused by assembly within a part of the core blast is small, and as a result, the deviation between the center O of the mounting part 1G and the reaction force yo**a becomes smaller, and stress corrosion cracking due to the moment MK also occurs. It has become.

そして、本例では、第８図に示すように、コアプレート
側壁１Ｂの高さｈを鍍めデレー）１８０寸法■より小さ
くしている為、具体的には（Ｍ−ｋ）≧０．６−に設定
しである為、鍍めプレート２８のツメｓｓの折り曲げ加
工時にコアプレー）＠ｌｌｌ１ｇＫは直接圧力荷置が加
わらずコアプレート１９への応力は低くできる。この効
果と合せてｌ型リング８Ｇを用いるととによってさらに
応力腐食割れ寿命が向上する。In this example, as shown in FIG. 8, the height h of the core plate side wall 1B is smaller than the plating diameter) 180 dimension (2), so specifically (M-k)≧0.6 Since it is set to -, the stress on the core plate 19 can be lowered because no direct pressure is applied to the core play) @llll1gK during the bending process of the claw ss of the plating plate 28. In addition to this effect, the use of the l-shaped ring 8G further improves the stress corrosion cracking life.

なお５本発明のｌ型リング８Ｇの爽施−として第４図の
記号で説明するとＷ１＝ｓ、ｍ■、Ｗｚ　＝ｇＯｓｍ、
　Ｙ＝３．５６．Ｘ＝ｆＬ１．ａ程度の形状の物が熱交
換−用として良い。そして、このｔ＃状の■型りング８
０Ｖｒ用いれば応力腐食割れ寿命（１０） が１弾性シール材ｇｌとして従来の０リングを用いたー
に比べ、１．５倍以上の向上することをｍ認している。5. When explaining the replacement of the l-shaped ring 8G of the present invention using the symbols shown in FIG. 4, W1 = s, m, Wz = gOsm,
Y=3.56. X=fL1. A material with a shape of about a is suitable for heat exchange. And this t# shaped ■ type ring 8
It has been confirmed that if 0Vr is used, the stress corrosion cracking life (10) will be improved by more than 1.5 times compared to using a conventional O-ring as one elastic seal material.

そして、Ｉ型リング８０は前述したように１ｇ１面の凹
部３０畠深さＷｌを種々変廻することＫより、接面圧力
Ｐｍを任意に設定できるのであるが、この凹部深さＷｌ
があまり洩〈ては、Ｉ型すングＳＯ［型に要する圧力が
過大となってしまい実用的でなく、を九、深さＷ３をあ
まり深くしては残部の輻Ｗｚが狭くなりすぎ■型リング
に耐久性がなくなるととＫなる。そこで本発明者等の寮
験によれば、この深さＷｌをＩ型リング８０の断面の＠
Ｗ　ｌに対して ｏ、ｏｓＷ１≦Ｗ１≦０．１ｗ。As mentioned above, in the I-type ring 80, the contact surface pressure Pm can be arbitrarily set by varying the depth Wl of the recess 30 on the 1 g 1 side.
If there is too much leakage, the pressure required for the I-type SO [mold will be excessive and it will be impractical.9) If the depth W3 is made too deep, the remaining radius Wz will be too narrow. If the ring loses its durability, it becomes K. According to the dormitory experience of the present inventors, this depth Wl is defined as @ of the cross section of the I-shaped ring 80.
o for W l, osW1≦W1≦0.1w.

の範囲内にしておけばよいことが砿かめられた。It was concluded that it would be best to keep it within the range of .

０ 崗１弾性シール部材２１としてｌｆｆ１ｌ！Ｊング（を
用いれば、接面圧力ｒＩＱは第す図のようＫなるが、こ
の接面圧力Ｐｍの圧力分布を更Ｋｇ整すべく第９．１０
．１１図に示すように、タンク取付部ｌＯの作用面１１
もしくはコアプレート１６の■型Ｖ（１１） ング対向部に凸部もしくは凹部４０，４１．４１を形成
してもよい。第９図及び第１１図図示の例では中央部の
接面圧力Ｐｍが増し、第１Ｏ図図示の例では周辺部の接
面圧力？鳳が増すことになる。0 lff1l as the elastic sealing member 21! If J () is used, the contact pressure rIQ will be K as shown in Figure 9.10 to further adjust the pressure distribution of this contact pressure Pm.
．． As shown in Fig. 11, the working surface 11 of the tank attachment part
Alternatively, convex portions or concave portions 40, 41, 41 may be formed in the portion of the core plate 16 facing the ■-shaped V (11) ring. In the examples shown in FIGS. 9 and 11, the contact pressure Pm at the center increases, and in the example shown in FIG. 1O, the contact pressure Pm at the peripheral area increases. Otori will increase.

また、上述の例では鍍めプレートｓｓＫよってコアプレ
ート１６を樹脂タンクｆｉ［錠め固定したが、敏めプレ
ートを有しなく、コアプレートにて一体錠めをする構造
の熱交換−においても１本発明の■型リング８０は同様
の効果を有する。Further, in the above example, the core plate 16 is locked and fixed to the resin tank fi by the plating plate ssK, but it is also possible to use a heat exchanger having a structure in which the core plate does not have a sharpening plate and is integrally locked with the core plate. The ■-shaped ring 80 of the present invention has similar effects.

以上説明したように本発明熱交換器では１弾性シール部
材として■型りングを用いたため、接面圧力のピーク値
を過大とすることなく、コアプレート　タンク間を！寮
にシールすることができ、その結果コアプレートの応力
腐食−れも極めて良好に阻止で睡るという優れた効果を
有する。As explained above, in the heat exchanger of the present invention, the molded ring is used as the first elastic sealing member, so the peak value of the contact surface pressure is not excessive, and the gap between the core plate and the tank is maintained. It has the excellent effect of being able to be sealed to the dormitory, and as a result, stress corrosion of the core plate is extremely well inhibited.

【図面の簡単な説明】[Brief explanation of drawings]

第１図は本発明熱交換器の一例を示す正面図、第２図は
従来の熱交換−を示す断面図、第Ｓ図は第８図図示熱交
換−の接面圧力分布を示す説明図。 第４図は本発明に保る弾性シール部材の一例をボ（ｌｊ
ｌ） す断面図、第す図は第１図のＸ−Ｘ矢視断面図、Ｉ！６
図は接面圧力と応力腐食割れ寿命及びシール洩れとの関
係を示す説明図、第７図はＩ！１図図示熱交換謔の使用
状態を説明する断面図、第８図コアプレートの高さｈを
示す断面図、第９図〜第１１図は夫々本発明熱交換器の
他の例の要部を示す断面図である。 ３・・・タンク、８・・・チューブ、１６・・・コアグ
レート、８０・・・Ｉ型リング（弾性シール部材）。 代理入升珊士　岡　部　　　隆 Ｃｌ８） 第１図　　　　　第２図 ＼ 第３図　　　　第４図 丁 第５図　　　　　　竿６図 第７図　　　　　第８図 ］！：Ｉ　　　　　　　　　　　　　　　　　　　　１
）　ＪＵ！！　１０図 第１１図Fig. 1 is a front view showing an example of the heat exchanger of the present invention, Fig. 2 is a sectional view showing a conventional heat exchanger, and Fig. S is an explanatory diagram showing the contact surface pressure distribution of the heat exchanger shown in Fig. 8. . FIG. 4 shows an example of the elastic seal member according to the present invention.
l) A cross-sectional view; 6
The figure is an explanatory diagram showing the relationship between contact pressure, stress corrosion cracking life and seal leakage, and Figure 7 is I! Figure 1 is a cross-sectional view illustrating the state of use of the illustrated heat exchanger, Figure 8 is a cross-sectional view showing the height h of the core plate, and Figures 9 to 11 are main parts of other examples of the heat exchanger of the present invention. FIG. 3...tank, 8...tube, 16...core grate, 80...I-type ring (elastic sealing member). Substitute Masu Sanshi Takashi Okabe Cl8) Fig. 1 Fig. 2 ＼ Fig. 3 Fig. 4 Fig. 5 Fig. 6 Fig. 7 Fig. 8]! :I 1
) JU! ! Figure 10 Figure 11

Claims (1)

【特許請求の範囲】 （１）熱交換流体を流す金属製のチューブと、このチュ
ーブの端部に固定された金属製のコアプレートと、この
コアプレートに欽め結合された樹脂製のタンクと、この
タンクと前記コアプレートとの間に介在され８〜４０≦
圧縮変形してタンクとコアプレートとの間のシールを保
つ弾性シール部材とを備え、かつ、前記弾性シール部材
をその断面形状が軸面になめらかな凹部を有する四角形
状のものとし良熱交換器。 （幻前記チューブ内にはアミン・アンモニアを含む熱交
換流体が流れる特＃！Ｆ＃求の範囲第１項記載の熱交換
−０ （８）前記コアプレートが黄銅製である特許請求の範囲
第１項もしくは第Ｓ項記載の熱交換器。 （４）前記弾性シール部材の凹部の深さＷｓが弾性シー
Ａ／ｓ材の断面幅Ｗｌに対して ｏ、ｏ　　ｂ　Ｗ、≦Ｗ、≦ｏ４Ｗ。 の範囲内である特＃！ＦｔＩ４求の範囲第１項ないし第
８項いずれか記載の熱交換器。[Claims] (1) A metal tube through which a heat exchange fluid flows, a metal core plate fixed to the end of the tube, and a resin tank coupled to the core plate. , interposed between this tank and the core plate, and 8 to 40≦
An elastic seal member that maintains a seal between a tank and a core plate by being compressed and deformed, and the elastic seal member has a square cross-sectional shape with a smooth concave portion on an axial surface. . (Heat exchange-0 according to claim 1, in which a heat exchange fluid containing amine and ammonia flows in the tube. (8) Claim 1, in which the core plate is made of brass. The heat exchanger according to item 1 or item S. (4) The depth Ws of the recessed portion of the elastic seal member is o, o b W, ≦W, ≦o4W with respect to the cross-sectional width Wl of the elastic seam A/s material. The heat exchanger according to any one of items 1 to 8, wherein the desired range is within the range of .