JPH02110294A - Heat exchanging core for heat exchanger - Google Patents
Heat exchanging core for heat exchangerInfo
- Publication number
- JPH02110294A JPH02110294A JP22360889A JP22360889A JPH02110294A JP H02110294 A JPH02110294 A JP H02110294A JP 22360889 A JP22360889 A JP 22360889A JP 22360889 A JP22360889 A JP 22360889A JP H02110294 A JPH02110294 A JP H02110294A
- Authority
- JP
- Japan
- Prior art keywords
- plates
- bottom wall
- flow passage
- plate
- acute angle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000001154 acute effect Effects 0.000 claims abstract description 13
- 230000000630 rising effect Effects 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 abstract description 4
- 239000012530 fluid Substances 0.000 description 27
- 238000002485 combustion reaction Methods 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
Classifications
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は内燃機関用オイルクーラなどの熱交換器の熱
交換コアに関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) This invention relates to a heat exchange core for a heat exchanger such as an oil cooler for an internal combustion engine.
（従来の技術）
従来皿形のプレートを重ねて各プレート間に層状の空室
を形成させ、これを第１、第２流路に区分し、例えば潤
滑油と冷却水のような第１１第のオイルクーラは上下１
対をなす上側板と下側板とを組み合わせ、さらにこれを
所要段数重ね合わせたうえ、その下面に下端板、上面に
オイル流出室となるリング状部材および冷却水の入口、
出口バイブを取付けたものである。この上側板・下側板
はそれぞれ底壁が段差をなして、段差部、凸部などが設
けられている。この上側板・下側板を組み合わせさらに
これを重ね合わせると、底壁に設けた段差のある凸部や
段差部の隙間が流体の流路となる。また底壁に設けた上
下方向の突出部分を互に突き合わせて当接させ、その立
上がり部分が２流体の境界をなし、突き合わせ面は上下
の同種流体の接触面となる。また、各空室の流体入口、
出口はほぼ中心に対し対称の位置に設けられている。(Prior Art) Conventionally, dish-shaped plates are stacked to form a layered cavity between each plate, and this is divided into a first and a second flow path. The oil cooler is upper and lower 1
A pair of upper and lower plates are combined, and the required number of stages are stacked on top of each other, and a lower end plate is provided on the lower surface, a ring-shaped member serving as an oil outflow chamber on the upper surface, and a cooling water inlet.
It is equipped with an exit vibrator. The bottom walls of the upper and lower plates each have a stepped bottom wall, and are provided with stepped portions, convex portions, and the like. When the upper and lower plates are combined and stacked on top of each other, the stepped convex portion provided on the bottom wall and the gap between the stepped portions become fluid flow paths. Further, the vertically protruding portions provided on the bottom wall are brought into contact with each other, and the rising portion forms a boundary between the two fluids, and the abutting surface becomes a contact surface between the upper and lower similar fluids. In addition, the fluid inlet of each chamber,
The outlets are located approximately symmetrically about the center.
（発明が解決しようとする課題）
上記のような熱交換器の上側板、下側板は通常金属板を
プレス成形することにより製作されるから上記のような
段差部や凸部などを正確に段差を付し、それぞれが平坦
で反りがないように成型するのは困難である。従って重
ね合わせたとき密着すべき部分に隙間を生じてろう着不
良による洩れを生じたり、流路形状が不正確になって所
期以上に流体の圧力損失が大きくなったりする。また底
壁を突出させて突き合わせ当接させた部分は同種流体間
の接触面となるから当接する面積だけ底壁の伝熱面積が
減殺される。(Problem to be Solved by the Invention) The upper and lower plates of the heat exchanger as described above are usually manufactured by press forming metal plates, so the steps and protrusions as described above can be precisely formed. It is difficult to mold each piece so that it is flat and does not warp. Therefore, when they are overlapped, a gap is created in the portions that should be in close contact, resulting in leakage due to poor soldering, or the shape of the flow path becomes inaccurate, resulting in greater fluid pressure loss than expected. Further, since the portion where the bottom wall protrudes and abuts against each other becomes a contact surface between fluids of the same type, the heat transfer area of the bottom wall is reduced by the area of contact.
さらに各空室内で中心に対しほぼ対称の位置に流入口と
流出口が設けられているから、空室内の流体は流入口で
中央口の左右に２分されほぼ半周を流れて流出する。従
って流れの径路が比較的短かい。これらの理由により熱
交換器の大きさの割には熱交換率が高（ない。Further, since the inlet and the outlet are provided at substantially symmetrical positions with respect to the center in each chamber, the fluid in the chamber is divided into two on the left and right sides of the center opening at the inlet, and flows out approximately half the circumference. Therefore, the flow path is relatively short. For these reasons, the heat exchange rate is high (not high) considering the size of the heat exchanger.
（課題を解決するための手段）
底壁の周縁と中央口の周縁とに立上りフランジを設け、
底壁上の鋭角に交わる２個の直径上にそれぞれ中心から
等距離の位置に開口を設け、方の鋭角内に半径方向に長
い凸条形突起を設け、他方の鋭角側の２個の開口に周縁
フランジを設けたプレートを１８０°ずつずらせながら
重ね合わせて各プレート間に１層おきの第１流路、第２
流路を形成させ、上記プレートの上下端面に上下端板を
固着し、そのいずれかに第１流入口、第１流出口、第２
流入口および第２流出口を穿設して、前記第１流路また
は第２流路に連通させた熱交換コアである。(Means for solving the problem) A rising flange is provided on the periphery of the bottom wall and the periphery of the central opening,
Openings are provided at positions equidistant from the center on two diameters that intersect at an acute angle on the bottom wall, a protrusion that is long in the radial direction is provided within one of the acute angles, and two openings on the other acute angle side are provided. Plates provided with peripheral flanges are stacked on top of each other while being shifted by 180 degrees, and a first flow path and a second flow path are formed every other layer between each plate.
A flow path is formed, upper and lower end plates are fixed to the upper and lower end surfaces of the plate, and a first inlet, a first outlet, and a second
It is a heat exchange core in which an inlet and a second outlet are bored to communicate with the first flow path or the second flow path.
（作用）
この熱交換コアはその上面または下面に前記第１、第２
流入口、第１第２流出口に連通ずる第１５第２流体の入
口室、出口室または入口バイブ、出口バイブが取付けら
れて熱交換器をなす。(Function) This heat exchange core has the first and second parts on its upper surface or lower surface.
An inlet, a fifteenth second fluid inlet chamber and an outlet chamber communicating with the first and second outlet or an inlet vibrator and an outlet vibrator are attached to form a heat exchanger.
熱交換コア内の各空室内では、凸条形突起の両側にある
開口の一方が入口、他方が出口となるから凸条形突起に
さえぎられて３６０°近い（はぼ３６０°−鋭角）迂回
流路を経て流れ、しかも第１、第２流体は互に逆向きの
迂回経路となる。In each chamber in the heat exchange core, one of the openings on both sides of the protrusion serves as an inlet, and the other serves as an outlet, so the detour is blocked by the protrusion and detours through nearly 360° (approximately 360° - an acute angle). The first and second fluids flow through the flow path, and the first and second fluids take detour paths in opposite directions.
また各プレートは開口部分を除き全底壁面が２流体間の
伝熱面積として利用される。さらにこのプレートは底壁
に段差を設けないから、反りのない正確な形状のものを
製作することができるので各フランジの接合部分の密着
が確実かつ均一となり、プレート間の流路形状も正確に
形成される。Further, the entire bottom wall surface of each plate except for the opening portion is used as a heat transfer area between two fluids. Furthermore, since this plate does not have a step on the bottom wall, it is possible to manufacture a plate with an accurate shape without warping, ensuring that the joints of each flange are in firm and uniform contact, and the shape of the flow path between the plates is also accurate. It is formed.
（実施例）
第１図、第２図はこの発明の実施例を示す断面図であり
、第３図、第４図にそのプレート５２を示す。第３図の
円形のプレート５２は底壁５の周縁に立上りフランジ４
ｂ、底壁５の中央に設けた中央口３の周縁に立上りフラ
ンジ４ａが設けてあ乙
る。′鋭角４Ｘ＋、、ＺＸｚで交わる二個の直径Ｘ＋
−ＹＸ２− Ｙ２上にそ、れぞれ開口５５ａ、 ５５ｂ
および５６ａ１５６ｂが穿設される。開口５５ａと５５
ｂは中心からの距離が等しく、開口５６ａと５６ｂも中
心からの距離が等しい。一方の鋭角４Ｙ＋、ＺＹｚ内に
半径力の周縁に開口フランジ６０が設けられる。このプ
レート５２を順次１８０°ずつ回転させて重ね、開口５
５ａ、５６ａの周縁の開口フランジ６０を隣接するプレ
ートの開口５５ｂ、５６ｂに接合させる。(Embodiment) FIGS. 1 and 2 are sectional views showing an embodiment of the present invention, and FIGS. 3 and 4 show a plate 52 thereof. The circular plate 52 in FIG.
b. A rising flange 4a is provided at the periphery of the central opening 3 provided at the center of the bottom wall 5. 'Two diameters X+ that intersect at an acute angle 4X+,, ZXz
-YX2- Openings 55a and 55b on Y2, respectively.
and 56a156b are drilled. Openings 55a and 55
b are the same distance from the center, and openings 56a and 56b are also the same distance from the center. An open flange 60 is provided at the periphery of the radial force within one acute angle 4Y+, ZYz. The plates 52 are sequentially rotated 180 degrees and stacked one on top of the other, and the opening 5
Opening flanges 60 at the peripheral edges of 5a, 56a are joined to openings 55b, 56b in adjacent plates.
このようにすれば積層された環状の空室が二つずつの開
口フランジ６０によって１層おきに連通し第１流入通路
１０、第１流出通路１１を有する第１流路（第１図）お
よび第２流入通路１２、第２流出通路１３を有する第２
流路（第２図）が形成される。このように重ね合わされ
たプレート５２の上端面に中央口９ｂ、第１流出路１１
に対向する第１流出口９ａを有する上端板９が固着され
、またこれらのプレート２の下端面に中央ロ１５ａ１第
１流入ロ１５ｂ１第２流入口１５Ｃ１第２流出口１５ｄ
を有する下端板１５が固着されて熱交換コア２５をなす
。第１図、第２図の例では下端板１５の周縁に一体的に
筒状垂下部１５ｅが設けられており、その内側に下蓋２
１が重ねられ、筒状垂下部１５ｅとの間に第２流体流入
室１７、第２流体流出室１８が形成される。入口バイブ
１９、出口バイブ２０が第２流体の流入室１７、流出室
１８にそれぞれ取付けられ、第２流入口１５ｃ、第２流
出口＋５ｄに連通ずる。下蓋２１の下面は第１流体入口
室１６を形成し第１流体人口１５ｂに連通ずる。In this way, the stacked annular cavities communicate with each other through two opening flanges 60, and a first flow path (FIG. 1) having a first inflow path 10 and a first outflow path 11; A second inlet passage having a second inflow passage 12 and a second outflow passage 13
A flow path (FIG. 2) is formed. A central opening 9b and a first outlet passage 11 are provided on the upper end surface of the plates 52 stacked in this manner.
An upper end plate 9 having a first outlet 9a facing the plate 2 is fixed to the lower end surface of these plates 2.
A lower end plate 15 having a shape is fixed to form a heat exchange core 25. In the example shown in FIGS. 1 and 2, a cylindrical hanging portion 15e is integrally provided on the periphery of the lower end plate 15, and a lower lid 2 is provided inside the cylindrical hanging portion 15e.
1 are stacked on top of each other, and a second fluid inflow chamber 17 and a second fluid outflow chamber 18 are formed between them and the cylindrical hanging portion 15e. An inlet vibe 19 and an outlet vibe 20 are attached to the second fluid inlet chamber 17 and outlet chamber 18, respectively, and communicate with the second inlet 15c and the second outlet +5d. The lower surface of the lower lid 21 forms a first fluid inlet chamber 16 and communicates with the first fluid port 15b.
上端板９の上面には開口１４ａを有するリング状の上部
室１４が取付けられその内部は第１流体出口室をなして
第１流出口９ａに連通ずる。このようにしてなる熱交換
器１は第１流体をオイル、第２流体を冷却水とした内燃
機関用のオイルクーラである。第１図、第２図に示す断
面図は、第３図における一方の鋭角＆ ＸＩ ｗ Ｚ
Ｘ２および他方の鋭角４Ｙｌ、ＺＹ２に沿った断面であ
る。各プレートの底壁５間において、流体は凸条形突起
５９にさえぎ６れて開口５５ｂから５６ｂまでまたは開
口５６ｂから５５ｂまでの間を、立上りフランジ４ａの
まわりにほぼ３６０°近い迂回経路をとって流れる。A ring-shaped upper chamber 14 having an opening 14a is attached to the upper surface of the upper end plate 9, and the inside thereof forms a first fluid outlet chamber and communicates with the first outlet 9a. The heat exchanger 1 constructed in this manner is an oil cooler for an internal combustion engine in which the first fluid is oil and the second fluid is cooling water. The cross-sectional views shown in FIGS. 1 and 2 are at one acute angle &XI w Z in FIG.
It is a cross section along X2 and the other acute angle 4Yl, ZY2. Between the bottom walls 5 of each plate, the fluid is blocked by the protrusion 59 and takes a nearly 360° detour around the rising flange 4a from the openings 55b to 56b or from the openings 56b to 55b. It flows.
そして第１流体の出入口と次層の第２流体の出入口とは
直径方向の反対側となり、第１流体と第２流体とはプレ
ート内の反対側でＵターンすることとなる。（流れの回
転方向は同方向、例えば共に時計廻りの場合もある。）
プレート５２には必要により小突起５８を設けて流体の
乱流発生、およびプレート間の補強に役立たせてもよい
。小突起は同一直径上では対応しない位置に設けられ、
相互の重ならないようにされる。The inlet/outlet of the first fluid and the inlet/outlet of the second fluid in the next layer are on opposite sides in the diametrical direction, and the first fluid and the second fluid make a U-turn on opposite sides within the plate. (The rotation direction of the flow may be the same, for example, both clockwise.)
If necessary, small protrusions 58 may be provided on the plates 52 to help generate fluid turbulence and reinforce the plates. Small protrusions are provided at positions that do not correspond on the same diameter,
They are prevented from overlapping each other.
（考案の効果）
この考案の熱交換コアは底壁に凹凸を設けない構造簡単
なプレートの１種類のみで構成することができ構造簡単
で部品点数が少なく、製作容易である。またプレートの
構造が簡単であるからプレス成形に際し正確で反りのな
いものが得られ、重ね合わせた際の立上りフランジおよ
び間口フランジの接合状態が均一に密着されたものとな
り、ろう付は不良による洩れ等が発生せず、機能の保証
が十分できるものである。またこのプレートは開口を除
き底壁全面が２流体間の伝熱面積として作用するから、
熱交換効率がよく、前記の構造簡単なことと相まって小
型、軽量化できる。(Effects of the invention) The heat exchange core of this invention can be composed of only one type of plate with a simple structure without any unevenness on the bottom wall, so the structure is simple, the number of parts is small, and it is easy to manufacture. In addition, since the structure of the plate is simple, it can be press-formed accurately and without warping, and when stacked, the upright flange and frontage flange are evenly bonded, and brazing is free from leakage due to defects. etc., and the functionality can be fully guaranteed. Also, since the entire bottom wall of this plate, excluding the opening, acts as a heat transfer area between the two fluids,
It has good heat exchange efficiency, and combined with the above-mentioned simple structure, it can be made smaller and lighter.
さらに、２流体は各プレート間においてほぼ３６０°近
い長い迂回経路をと５、かつ交互の層内を反対方向に流
れるから、この点からも熱交換効率は向上する。Furthermore, since the two fluids flow through long detours of approximately 360 degrees between each plate and in opposite directions in alternate layers, the heat exchange efficiency is improved from this point as well.
【図面の簡単な説明】
第１図、第２図はこの考案の実施例の断面を示し、それ
ぞれ第３図のＸＩ −Ｚ −Ｘ２およびＹ＋ −ＺＹ２
に沿った断面図である。第３図はこの考案におけるプレ
ートの図、第４図（イ）（ロ）（ハ）は第３図イーｆ線
、ローロ線、ハーバ線に沿ったプレートの断面図である
。
５・・・・・・底壁 ４ａ、４ｂ・・・・・・立上りフ
ランジ９・・・・・・上端板 ｌＯ・・・・・・第１流
入路＋１・・・・・・第１流出路 １２・・・・・・第
２流入路１３ ・’・・・・・第２流出路 １５・・・
・・・下端板５２・・・・・・プレート
５５ ａ 、 ５５ ｂ 、 ５６ ａ 、 ５６ ｂ
・＝ ・＝開口５９・・・・・・凸条形突起 ６０・
・・・・・開口フランジ第１図[BRIEF DESCRIPTION OF THE DRAWINGS] FIGS. 1 and 2 show cross sections of an embodiment of this invention, and XI-Z-X2 and Y+-ZY2 in FIG. 3, respectively.
FIG. FIG. 3 is a diagram of the plate in this invention, and FIGS. 4(a), 4(b), and 4(c) are sectional views of the plate along the E-f line, the Rolo line, and the Haber line in FIG. 5...Bottom wall 4a, 4b...Rising flange 9...Top end plate lO...First inflow path +1...First outflow Path 12...Second inflow path 13...Second outflow path 15...
...Lower end plate 52...Plates 55a, 55b, 56a, 56b
・= ・=Opening 59...Convex strip-shaped projection 60・
...Opening flange diagram 1
Claims (3)
に立上りフランジを設け、底壁上の鋭角に交わる２個の
直径上に中心から等距離の位置に開口をそれぞれ設け、
一方の鋭角内に半径方向に長い凸条形突起を設け、他方
の鋭角側の開口の周縁に開口フランジを設けてなるプレ
ートを、１８０°ずつ順次に円周方向にずらせて重ね合
わせて前記立上りフランジ同士を接合するとともに開口
フランジを他の開口周縁に接合して、１層おきに層状を
なす第１流路・第２流路を形成させ、前記プレートの上
端に上端板、下端に下端板を固着し、前記第１流路に連
通する第１流入口、第１流出口、第２流入口、および第
２流出口をそれぞれ上端板または下端板に穿設してなる
熱交換器の熱交換コア。(1) A rising flange is provided on the periphery of the bottom wall and the periphery of the central opening provided in the center of the bottom wall, and openings are provided at positions equidistant from the center on two diameters that intersect at an acute angle on the bottom wall. ,
Plates each having a radially long convex protrusion within one acute angle and an opening flange at the periphery of the opening on the other acute angle side are sequentially shifted by 180 degrees in the circumferential direction and stacked one on top of the other. The flanges are joined to each other and the opening flange is joined to the periphery of another opening to form a first flow path and a second flow path that are layered every other layer, and an upper end plate is attached to the upper end of the plate, and a lower end plate is attached to the lower end of the plate. and a first inlet, a first outlet, a second inlet, and a second outlet communicating with the first flow path are formed in the upper end plate or the lower end plate, respectively. replacement core.
しない位置に設けられた、特許請求の範囲第１項記載の
熱交換器の熱交換コア。(2) A heat exchange core of a heat exchanger according to claim 1, wherein a plurality of small protrusions are provided on the bottom wall of the plate at non-corresponding positions on the diameter.
る特許請求の範囲第１項記載の熱交換器の熱交換コア。(3) The heat exchange core of the heat exchanger according to claim 1, wherein all the openings formed in the bottom wall are equidistant from the center.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22360889A JPH02110294A (en) | 1989-08-30 | 1989-08-30 | Heat exchanging core for heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22360889A JPH02110294A (en) | 1989-08-30 | 1989-08-30 | Heat exchanging core for heat exchanger |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6461985A Division JPS61223213A (en) | 1985-02-28 | 1985-03-28 | Plate type oil cooler |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02110294A true JPH02110294A (en) | 1990-04-23 |
| JPH0416710B2 JPH0416710B2 (en) | 1992-03-24 |
Family
ID=16800860
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22360889A Granted JPH02110294A (en) | 1989-08-30 | 1989-08-30 | Heat exchanging core for heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02110294A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5513702A (en) * | 1992-12-21 | 1996-05-07 | Calsonic Corporation | Housingless type oil cooler and method for producing the same |
| US5797450A (en) * | 1996-05-02 | 1998-08-25 | Honda Giken Kogyo Kabushiki Kaisha | Oil cooler for automobiles |
| US20100251702A1 (en) * | 2007-11-07 | 2010-10-07 | The University Of Tokyo | Heat Recovery System |
-
1989
- 1989-08-30 JP JP22360889A patent/JPH02110294A/en active Granted
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5513702A (en) * | 1992-12-21 | 1996-05-07 | Calsonic Corporation | Housingless type oil cooler and method for producing the same |
| US5590709A (en) * | 1992-12-21 | 1997-01-07 | Calsonic Corporation | Housingless type oil cooler and method for producing the same |
| US5797450A (en) * | 1996-05-02 | 1998-08-25 | Honda Giken Kogyo Kabushiki Kaisha | Oil cooler for automobiles |
| US20100251702A1 (en) * | 2007-11-07 | 2010-10-07 | The University Of Tokyo | Heat Recovery System |
| US8266900B2 (en) * | 2007-11-07 | 2012-09-18 | The University Of Tokyo | Heat recovery system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0416710B2 (en) | 1992-03-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101156041B (en) | Plate-type heat exchanger | |
| JP6126358B2 (en) | Multi-plate oil cooler | |
| JP2007532852A (en) | Plate heat exchanger | |
| CN101983312A (en) | A plate heat exchanger | |
| JP2005530979A (en) | Stacked plate heat transfer body | |
| JPS62202997A (en) | Heat exchanger of compound type | |
| JP2003166792A (en) | Cylindrical heat exchanger | |
| JPH02110294A (en) | Heat exchanging core for heat exchanger | |
| JPH0330690B2 (en) | ||
| JP2009264727A (en) | Heat exchanger unit and heat exchanger using the same | |
| JP2010060168A (en) | Oil cooler | |
| JPH09184694A (en) | Core of laminated type heat exchanger | |
| JPH0719779A (en) | Manufacture of heat exchanger core | |
| JP2597170Y2 (en) | Dish-shaped plate for heat exchanger | |
| JP2509341Y2 (en) | Heat exchanger | |
| JP2001099582A (en) | Plate type heat exchanger and manufacturing method | |
| JPS5928219Y2 (en) | Oil cooler for internal combustion engine | |
| JPH08159685A (en) | Laminate type heat exchanger core | |
| JPH07190650A (en) | Heat exchanger | |
| JPH0461279B2 (en) | ||
| JP2006132806A (en) | Thermal storage device | |
| JPH0443742Y2 (en) | ||
| JP4471423B2 (en) | Plate heat exchanger | |
| JPH05264193A (en) | Plate type heat exchanger | |
| JPH0443745Y2 (en) |