JPS58130997A - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JPS58130997A JPS58130997A JP1368582A JP1368582A JPS58130997A JP S58130997 A JPS58130997 A JP S58130997A JP 1368582 A JP1368582 A JP 1368582A JP 1368582 A JP1368582 A JP 1368582A JP S58130997 A JPS58130997 A JP S58130997A
- Authority
- JP
- Japan
- Prior art keywords
- tubes
- row
- core
- heat exchanger
- tube
- 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.)
- Pending
Links
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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- 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
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
Landscapes
- 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)
Abstract
Description
【発明の詳細な説明】
本発明は、自動車用ラジェータ等に用いられる熱交換器
に関し、特にコルゲートフィン型熱交換器の改良に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat exchanger used in an automobile radiator or the like, and particularly relates to an improvement of a corrugated fin type heat exchanger.
従来、コルゲートフィン型熱交換器、例えば自動車用ラ
ジェータは、第１図に示すようにエンジンで加熱された
被冷却水を冷却するコア１と、このコア１の上下端に各
別に設けられ、エンジンのウォータジャケットに接続さ
れる上部タンク２及び下部タンク３とから構成され、そ
して上記コア１は第２図（α）またはＣｂ）に示すよう
に冷却用空気の流れＸの方向に２列または３列等、多数
列に配置された多数の扁平チューブ４を有し、この各列
の扁平チューブ４の扁平長手方向は空気流れＸめ方向に
一致し、かつ空気流れＸ方向の各列の扁平チューブ４は
一線に配列されているとともに゛、相隣接する扁平チュ
ーブ４．４間には２列または３列等、多数列に配置され
たチューブ間にまたがってチュ−プと熱的に結合するコ
ルゲートフィン５が介在され、さらにコルゲートフィン
５にはその熱伝達率を向上するためルーバ６を形成した
構造になっている。Conventionally, a corrugated fin type heat exchanger, such as an automobile radiator, has a core 1 that cools water heated by the engine, and a core 1 that is separately provided at the upper and lower ends of the core 1, as shown in FIG. The core 1 consists of an upper tank 2 and a lower tank 3 connected to a water jacket, and the core 1 is arranged in two or three rows in the direction of the cooling air flow It has a large number of flat tubes 4 arranged in many rows such as rows, the flat longitudinal direction of the flat tubes 4 in each row coincides with the air flow X direction, and the flat tubes in each row in the air flow X direction. 4 are arranged in a line, and between the adjacent flat tubes 4.4 there is a corrugate that spans between the tubes arranged in multiple rows, such as 2 or 3 rows, and is thermally coupled to the tubes. Fins 5 are interposed, and louvers 6 are formed on the corrugated fins 5 to improve the heat transfer coefficient.
このように各チューブ間にフィンを設けるのは、コアに
おける空気側の放熱面積を拡大してラジェータ、即ち熱
交換器の放熱性能を向上させるため、及び熱交換器の小
形化、軽量化を図るためであるが、従来このような目的
を達成される一手段としてのコルゲートフィン５は、上
記第２図（α）、（ｂ）からも自明な如くコアのチュー
ブ列が２列、３列等、多数列になってくると、これに合
わせてフィン幅ｄも変わってくる。例えばチューブ列が
１列のコアにおけるフィン幅ｄを１６鱈とすると、２列
、３列になるに従ってこれらに使用されるフィンも１６
■の列数の倍数値の幅のものが必要になってくる。The purpose of providing fins between each tube in this way is to expand the heat radiation area on the air side of the core to improve the heat radiation performance of the radiator, that is, the heat exchanger, and to make the heat exchanger smaller and lighter. However, as is obvious from FIGS. 2(a) and (b), the conventional corrugated fin 5 as a means for achieving this purpose has two or three rows of tubes in the core. , as the number of rows increases, the fin width d changes accordingly. For example, if the fin width d in the core of one tube row is 16 mm, then the fins used for the second and third rows will also be 16 mm.
■You will need something with a width that is a multiple of the number of columns.
このことは、チューブ列数に合った幅寸法のコルゲート
フィンをそれぞれ用意しなければならないとともに、こ
れらを加工するコルゲートギヤ及びその装置も各々別々
に設備しなければならない。このため、コルゲートフィ
ンの生産設備が複雑化し、その設備費も増大すると共に
、幅寸法の異なるコルゲートフィンを熱交換器機種数に
応じて用意しなければならない関係上、生産コストが上
昇し、特に３列ないしそれ以上の多数列コルゲートフィ
ンにルーバ加工を施すコルゲートギヤ及びその装置にな
ると、コルゲートギヤ及びその装置が高価になり、さら
に生産コストが上昇する欠点があった。This means that corrugate fins with widths that match the number of tube rows must be prepared, and corrugate gears and equipment for processing these fins must also be separately installed. For this reason, the production equipment for corrugated fins becomes complicated, and the equipment costs increase.In addition, corrugated fins with different width dimensions must be prepared according to the number of heat exchanger models, which increases production costs. When it comes to corrugate gears and equipment for applying louver processing to three or more rows of corrugated fins, the corrugate gears and equipment become expensive, and the production cost increases.
本発明は上記従来の問題を解決したもので、熱交換器コ
アを構成するチューブ列数に関係なくコルゲートフィン
の幅寸法を統一化し、これによりフィン生産設備の小規
模化及びフィン生産コストの低減を図り、併せてコアの
放熱性能を向上できる熱交換器を提供することを目的と
する。The present invention solves the above-mentioned conventional problems by unifying the width dimensions of corrugated fins regardless of the number of tube rows constituting the heat exchanger core, thereby reducing the size of fin production equipment and fin production costs. The present invention aims to provide a heat exchanger that can improve the heat dissipation performance of the core.
この目的を達成するために本発明の熱交換器は、そのコ
アにおいて、これに送風される空気流れの方向に複数段
に配列された各列のチューブ群を、列単位で空気流れと
直角な方向にチューブピッチの数分の１互いにずらして
空気流れ方向の前後に相隣接する列間のチューブが互い
のチューブ間に位置されるよう構成し、かつ各列のチュ
ーブ間にはこれと熱的に結合される１列用のコルゲート
フィンを各別に介在したものである。To achieve this objective, the heat exchanger of the present invention has tube groups arranged in multiple stages in the direction of the air flow blown to the heat exchanger in each row at right angles to the air flow. The tubes in the rows adjacent to each other in the front and rear directions in the air flow direction are shifted from each other by a fraction of the tube pitch in the air flow direction, and the tubes in each row are arranged so that the tubes are located between the tubes in each row. Each row of corrugated fins is connected to a single row of corrugated fins.
以下、本発明の実施例を図面について説明する。Embodiments of the present invention will be described below with reference to the drawings.
第３図及び第４図は本発明にかかるコルゲートフィン型
熱交換器の一例を示し、具体的には自動車用ラジェータ
の部分構造図を示している。3 and 4 show an example of a corrugated fin type heat exchanger according to the present invention, and specifically show a partial structural diagram of a radiator for an automobile.
この第３図及び第４図において、放熱部を構成するコア
１０は、これに送風される空気流れＸの方向に２段に配
列された２列のチューブ群１１．１２を有し、この各チ
ューブ群１１．１２は空気流れＸと直角な方向（コア幅
方向）に所定のピッチで配列された多数の扁平チューブ
゛１１α、１２αから構成されているとともに、このよ
うにした各列のチューブ群１１．１２は列単位で空気流
れＸと直角な方向に所望間隔、例えばチューブピッチＰ
ｔの１／２分互いにずらして配置され、これにより、空
気流れＸの方向の前段に位置する列チューブ群１１の扁
平チューブ１１α及び、後段に位置する列チューブ群１
２の扁平チューブ１２αが相前後するチューブ列の互い
のチューブ間に位置する配列構成にする。In FIGS. 3 and 4, the core 10 constituting the heat dissipation section has two rows of tube groups 11 and 12 arranged in two stages in the direction of the air flow X blown thereto. The tube groups 11 and 12 are composed of a large number of flat tubes 11α and 12α arranged at a predetermined pitch in the direction perpendicular to the air flow X (core width direction), and each row of tube groups arranged in this way 11.12 is the desired interval in the direction perpendicular to the air flow X in row units, for example, the tube pitch P
The flat tubes 11α of the row tube group 11 located at the front stage in the direction of the air flow X and the row tube group 1 located at the rear stage are arranged to be shifted from each other by 1/2 of t.
The arrangement is such that the two flat tubes 12α are located between tubes in successive tube rows.
また、このように配列された各チューブ群１１．１２の
各扁平チューブ１１αと１１α及び１２αと１２α間に
は１列用の幅寸法ｄに相当する同一形状のコルゲートフ
ィン１３がそれぞれ介在され、チューブと熱的に結合さ
れているとともに、この各フィン１３には、その熱伝達
率を増大させるルーバ１４が形成されている。Further, corrugate fins 13 of the same shape corresponding to the width dimension d for one row are interposed between the flat tubes 11α and 11α and between the flat tubes 12α and 12α of each tube group 11.12 arranged in this way, respectively. Each fin 13 is formed with a louver 14 that increases its heat transfer coefficient.
また、上記配列の扁平チューブ１１α、１２αの端部は
同一の座板１５に貫通接合され、この座板１５には樹脂
製あるいは金属製のタンク１６が一体に取り付けられて
いる。なお、第３図では上部タンク１６を組付けた状態
を示した力よ、図示しない下部タンクにおいても第１図
と同様な形で取り付けられている。Further, the ends of the flat tubes 11α and 12α in the above arrangement are penetrated and joined to the same seat plate 15, and a tank 16 made of resin or metal is integrally attached to this seat plate 15. It should be noted that the force shown in FIG. 3 with the upper tank 16 assembled is also attached to the lower tank (not shown) in the same manner as in FIG. 1.
上記のように構成されたラジェータにおいては、空気流
れＸの前後段に位置するチューブ群１１．１２の各扁平
チュー ブ１１α、１２αが、従来のように空気流れＸ
の方向の一線に並ばずに１／２ Ｐｔずれ、しかもチュ
ーブ１１αと１１ｂ、１２αと１２ｂ間に形成される冷
却空気通路がたがいちがいになってストレートな通路と
なっていないため、コアＩＯＫ対し送風される空気がＸ
方向からコアｌｏ内に導入されると、該空気はチューブ
ｌｌａ、１２αによって複雑に分散されると同時に、各
通路内のコルゲートフィン１３及びそのルーバ１４によ
ってさらに複雑に変化する乱流に変換されることになる
。In the radiator configured as described above, each of the flat tubes 11α and 12α of the tube groups 11.12 located at the front and rear stages of the air flow
The cooling air passages formed between the tubes 11α and 11b and between the tubes 12α and 12b are not lined up in a straight line and are shifted by 1/2 Pt, and the cooling air passages formed between the tubes 11α and 11b and between the tubes 12α and 12b are different and do not form straight passages. The air that is exposed is X
When introduced from the direction into the core lo, the air is dispersed in a complicated manner by the tubes lla and 12α, and at the same time is converted into a turbulent flow that changes in a more complicated manner by the corrugated fins 13 and their louvers 14 in each passage. It turns out.
このため、空気側におけるチューブｌｌａ、１２ｂ及び
フィン１３の空気の境界層が薄くなってチューブ及びフ
ィンの熱伝達率を大きくする。Therefore, the boundary layer of air between the tubes lla, 12b and the fins 13 on the air side becomes thinner, increasing the heat transfer coefficient between the tubes and the fins.
このことはコアの空気側の放熱面積及びコアを通過する
風量が一定であったとしてもラジェー換言すれば、同一
放熱性能の場合、ラジェータを従来のものより小形、軽
量化できることを意味する。This means that even if the heat radiation area on the air side of the core and the amount of air passing through the core are constant, the radiator, in other words, can be made smaller and lighter than conventional radiators with the same heat radiation performance.
第５図は３列のチューブ群１７α、１７ｂ。FIG. 5 shows three rows of tube groups 17α and 17b.
１７６を備えた熱交換器コアに本発明方式を適用した場
合の他の例を示すもので、各列のチューブ群１７ ａ、
１７ ｂ、 １７ ｃは同一の扁平チューブ１８
及びコルゲートフィン１３よりなり、そして空気流れＸ
方向の前後において互いに隣接する列間のチューブ１８
はコアの幅方向（矢印Ｙの方向）に１／２Ｐｔずらした
配列となっている。この実施例においても上記実施例と
同様な効果が得られる。This shows another example in which the method of the present invention is applied to a heat exchanger core equipped with tube groups 17a, 176 in each row.
17 b and 17 c are the same flat tube 18
and corrugated fins 13, and air flow X
Tubes 18 between adjacent rows in the front and back directions
are arranged in a manner shifted by 1/2Pt in the width direction of the core (direction of arrow Y). In this embodiment as well, the same effects as in the above embodiment can be obtained.
また、第６図１は３列のチューブ群１７α、１７ｂ、１
７ｃを備えた熱交換器コアの変形例を示すもので、この
実施例においては各列のチューブ群１７・α、１７６．
１７ｃのコア幅方向へのずれ間隔をチューブピッチＰｔ
の１／３とした場合である。この場合の実施例において
も上記と同様な作用効果が得られる。In addition, FIG. 6 1 shows three rows of tube groups 17α, 17b, 1
7c is shown, and in this embodiment, each row of tube groups 17.α, 176.
17c in the core width direction is the tube pitch Pt
This is the case when it is set to 1/3 of that. In this embodiment as well, the same effects as described above can be obtained.
なお、上記各実施例では各列のチューブ群の各扁平チュ
ーブ間に介在されるコルゲートフィン１３のフィンピッ
チは同一であるとして説明したが、これに限定されるも
のではなく、例えば空気流れＸ方向に配列される各段の
列チューブ群に設けられるコルゲートフィン１３のフィ
ンピッチを変えても良く、この場合は同一列数のチュー
ブを有する熱交換器であってもその放熱性能を変えるこ
とができる効果がある。In each of the above embodiments, the fin pitch of the corrugated fins 13 interposed between the flat tubes in each row of tube groups is the same, but the fin pitch is not limited to this, and for example, the fin pitch is the same in the X direction of the air flow. The fin pitch of the corrugated fins 13 provided in each row of tube groups arranged in the tube group may be changed, and in this case, even if the heat exchanger has the same number of rows of tubes, its heat dissipation performance can be changed. effective.
以上のように本発明によれば、熱交換器を構成するコア
において、これに送風される空気流れ方向に複数段に配
列された各列のチューブ群を、列単位で空気流れと直角
な方向にチューブピッチの数分の１互いにずらして空気
流れ方向 、の前後に相隣接する列間のチューブが互
いのチューブ間に位置するよう構成し、かつ各列のチュ
ーブ間にはこれと熱的に結合される１列用のコルゲート
フィンを各別に介在したものであるから、熱交換器を構
成するコアチューブ列を複数段にしても、これに使用さ
れるコルゲートフィンを標準化、即ち１列用の同一フィ
ン幅寸法のものとすることができ、このため、コルゲー
トフィンを加工するコルゲートギヤ及びその装置等の生
産設備が小規模のもので済み、しかも単一フィンを加工
するのみで良いため、フィンの生産性が向上しコストの
低減が可能になる。As described above, according to the present invention, in the core constituting the heat exchanger, tube groups in each row arranged in multiple stages in the direction of air flow blown to the core are arranged in a direction perpendicular to the air flow. The tubes in adjacent rows are arranged so that they are shifted from each other by a fraction of the tube pitch in the air flow direction, and the tubes in adjacent rows are positioned between each other, and there is a thermal space between the tubes in each row. Since the corrugated fins for each row are connected separately, even if the core tube rows constituting the heat exchanger are arranged in multiple stages, the corrugated fins used for this are standardized; The fins can have the same width dimension, so the production equipment such as the corrugated gear and its equipment for processing corrugated fins can be small-scale.Furthermore, since it is only necessary to process a single fin, This will improve productivity and reduce costs.
また、各列のチューブ群は空気流れ方向と直角な方向に
チューブピッチの数分の１互いにずらすことで各列のチ
ューブ間に形成される冷却空気通路を空気流れ方向にた
がいちがいにしたので、コアを通過する冷却空気の乱流
が増大され、フィンの熱伝達率が向上して熱交換器の放
熱量を増大できる効果がある。In addition, the tube groups in each row are shifted from each other by a fraction of the tube pitch in a direction perpendicular to the air flow direction, so that the cooling air passages formed between the tubes in each row are made to differ in the air flow direction. This has the effect of increasing the turbulence of cooling air passing through the core, improving the heat transfer coefficient of the fins, and increasing the heat radiation amount of the heat exchanger.
第１図は従来における熱交換器を示す概略正面図、第２
図（α）、（ｉは第１図におけるコア部分のチューブと
コルゲートフィンとの関係を示す平面図、第３図は本発
明にかかる熱交換器の一例を示す一部の斜視図、第４図
は第３図におけるコア部分のチューブとコルゲートフィ
ンとの関係を示す平面図、第５図及び第６図は本発明方
式を３列のコアチューブに適用した場合の例を示す説明
用平面図である。
１０・・・コア、１１．１２・・・チューブ群、１１α
、１２α・・・扁平チューブ、１３・・・コルゲートフ
ィン、１４・・・ルーバ、１５・・・座板、１６・・・
タンク。
特 許 出 願 人 日本ラヂヱーター株式会社第１
図
第４図
第５図
第６図
ＩＸFigure 1 is a schematic front view showing a conventional heat exchanger, Figure 2 is a schematic front view showing a conventional heat exchanger;
(α), (i is a plan view showing the relationship between the tube of the core part and the corrugated fin in FIG. 1, FIG. 3 is a partial perspective view showing an example of the heat exchanger according to the present invention, and FIG. The figure is a plan view showing the relationship between the tube of the core part and the corrugated fin in Fig. 3, and Figs. 5 and 6 are explanatory plan views showing an example of applying the method of the present invention to three rows of core tubes. 10...Core, 11.12...Tube group, 11α
, 12α... flat tube, 13... corrugated fin, 14... louver, 15... seat plate, 16...
tank. Patent applicant: Japan Radiator Co., Ltd. No. 1
Figure 4 Figure 5 Figure 6 IX
Claims (2)
、このコアの両端に一体に設けたタンクとを有する熱交
換器において、上記コアはこれに送風される空気流れ方
向に複数段に配列されたチューブ群を有し、この各別の
チューブ群を列単位で空気流れと直角な方向妃チューブ
ピッチの数分の１互いにずらし、これにより空気流れ方
向の前後に相隣接する列間のチューブが互いのチューブ
間に位置されるよう構成し、かつ上記各列のチューブ間
にはこれと熱的に結合する１列用のコルゲートフィンを
各別に介在したことを特徴とする熱交換器。(1) In a heat exchanger having a core having tubes and corrugated fins, and a tank integrally provided at both ends of the core, the core is a group of tubes arranged in multiple stages in the direction of air flow blown to the core. The different tube groups are shifted from each other by a fraction of the tube pitch in the direction perpendicular to the air flow direction, so that the tubes between adjacent rows in the front and back of the air flow direction are aligned with each other. A heat exchanger characterized in that a corrugated fin for one row is interposed between each row of tubes and is thermally connected to the tubes in each row.
コルゲートフィンのフィンピッチが異なっていることを
特徴とする特許請求の範囲第１項記載の熱交換器。(2) The heat exchanger according to claim 1, wherein the fin pitches of the corrugated fins interposed between the tubes in each row of tube groups are different.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1368582A JPS58130997A (en) | 1982-01-29 | 1982-01-29 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1368582A JPS58130997A (en) | 1982-01-29 | 1982-01-29 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58130997A true JPS58130997A (en) | 1983-08-04 |
Family
ID=11840036
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1368582A Pending JPS58130997A (en) | 1982-01-29 | 1982-01-29 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58130997A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5456311A (en) * | 1992-04-16 | 1995-10-10 | Langerer & Reich Gmbh & Co. | Heat exchanger |
| US6286590B1 (en) * | 1996-04-09 | 2001-09-11 | Lg Electronics Inc. | Heat exchanger with flat tubes of two columns |
| EP1195567A1 (en) * | 1997-03-17 | 2002-04-10 | Denso Corporation | Heat exchanger having several heat exchanging portions |
| JP2002115934A (en) * | 2000-10-06 | 2002-04-19 | Denso Corp | Vaporizer and freezer |
| FR2826108A1 (en) * | 2001-06-19 | 2002-12-20 | Valeo Climatisation | Automobile heat exchanger comprises two manifolds each provided with two rows of holes, tube bundle, received in holes, has inserts alternately located with tubes in separate rows |
| JP2006327325A (en) * | 2005-05-24 | 2006-12-07 | Honda Motor Co Ltd | Cooling device for fuel cell electric vehicle |
-
1982
- 1982-01-29 JP JP1368582A patent/JPS58130997A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5456311A (en) * | 1992-04-16 | 1995-10-10 | Langerer & Reich Gmbh & Co. | Heat exchanger |
| US6286590B1 (en) * | 1996-04-09 | 2001-09-11 | Lg Electronics Inc. | Heat exchanger with flat tubes of two columns |
| EP1195567A1 (en) * | 1997-03-17 | 2002-04-10 | Denso Corporation | Heat exchanger having several heat exchanging portions |
| JP2002115934A (en) * | 2000-10-06 | 2002-04-19 | Denso Corp | Vaporizer and freezer |
| FR2826108A1 (en) * | 2001-06-19 | 2002-12-20 | Valeo Climatisation | Automobile heat exchanger comprises two manifolds each provided with two rows of holes, tube bundle, received in holes, has inserts alternately located with tubes in separate rows |
| JP2006327325A (en) * | 2005-05-24 | 2006-12-07 | Honda Motor Co Ltd | Cooling device for fuel cell electric vehicle |
| JP4644034B2 (en) * | 2005-05-24 | 2011-03-02 | 本田技研工業株式会社 | Cooling device for fuel cell vehicle |
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