JPH0547960Y2 - - Google Patents
Info
- Publication number
- JPH0547960Y2 JPH0547960Y2 JP1985057081U JP5708185U JPH0547960Y2 JP H0547960 Y2 JPH0547960 Y2 JP H0547960Y2 JP 1985057081 U JP1985057081 U JP 1985057081U JP 5708185 U JP5708185 U JP 5708185U JP H0547960 Y2 JPH0547960 Y2 JP H0547960Y2
- Authority
- JP
- Japan
- Prior art keywords
- temperature side
- flow path
- axis
- low
- temperature
- 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.)
- Expired - Lifetime
Links
- 239000012530 fluid Substances 0.000 claims description 24
- 230000035882 stress Effects 0.000 description 7
- 230000008646 thermal stress Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000001788 irregular Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
【考案の詳細な説明】
［産業上の利用分野］
本考案はプレートフイン型熱交換器に関するも
のである。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a plate-fin type heat exchanger.
［従来の技術］
例えば、伝熱面を矩形フインとしたプレートフ
イン型熱交換器には第４図に示す如く、流入側及
び流出側に設けられた斜交流部１とその間に設け
られた対向流部２をもち、幅方向に複数形成した
流路の長さをすべて同一にして熱交換効率を向上
させたものがある。斜交流部１では、高温側流体
３を流す高温側流路４と低温側流体５を流す低温
側流路６とが斜交しており、又前記対向流部２で
は、高温側流路４と低温側流路６とが平行になる
ように配されており、上記流路４，６が第５図に
示すように適数段積重ねられて伝熱部材７が構成
されている。この伝熱部材７は、幅方向に均一な
高い熱交換効率が達成できる優れた利点を有して
いる。[Prior Art] For example, a plate-fin type heat exchanger with a heat transfer surface having rectangular fins has a diagonal flow section 1 provided on an inflow side and an outflow side and an opposing section provided therebetween, as shown in Fig. 4. There is one that has a flow section 2 and has a plurality of flow channels formed in the width direction, all of which have the same length to improve heat exchange efficiency. In the oblique flow section 1, the high temperature side flow path 4 through which the high temperature side fluid 3 flows and the low temperature side flow path 6 through which the low temperature side fluid 5 flows obliquely, and in the counter flow section 2, the high temperature side flow path 4 flows in the high temperature side flow path 4. The heat transfer member 7 is arranged such that the flow paths 4 and 6 are parallel to each other, and the flow paths 4 and 6 are stacked in an appropriate number of stages as shown in FIG. This heat transfer member 7 has the excellent advantage of achieving uniform high heat exchange efficiency in the width direction.
［考案が解決しようとする課題］
しかし、上記従来の単一の伝熱部材７を有した
プレートフイン型熱交換器においては、第６図に
示す如く、高温側流体３及び低温側流体５は各々
流路４，６の入口においてはそれぞれ矢印で示す
ように均一な温度分布となつているが、出口にお
いて温度勾配αを生じる。[Problem to be solved by the invention] However, in the above conventional plate-fin heat exchanger having a single heat transfer member 7, as shown in FIG. 6, the high temperature side fluid 3 and the low temperature side fluid 5 are At the inlets of each of the channels 4 and 6, there is a uniform temperature distribution as shown by the arrows, but a temperature gradient α occurs at the outlet.
特に高温側流体３が流れ出る斜交流部１におけ
る側流路４の出口では温度勾配が大きく、そのた
め不定形な曲がり変化が生じ、よつて前記伝熱部
材７を包囲する図示しないヘツダを有した熱交換
器本体に応じて斜交流部１の点Ａ，Ｂ，Ｃの位置
には局部応力が発生する。 In particular, the temperature gradient is large at the outlet of the side flow path 4 in the oblique flow section 1 from which the high temperature side fluid 3 flows out, and as a result, an irregular bending change occurs. Local stress is generated at points A, B, and C of the oblique flow section 1 depending on the exchanger body.
即ち、点Ａの位置には高温側流体が流れて熱膨
張による熱変形を生じようとするが、点Ａは図示
しない常温の熱交換器本体に一体に固定されてい
るので、熱交換器本体に局所的な熱応力を生じる
ことになる。 In other words, the high-temperature fluid flows at the position of point A and tends to cause thermal deformation due to thermal expansion, but since point A is integrally fixed to the heat exchanger body (not shown) at room temperature, the heat exchanger body This results in localized thermal stress.
又点Ｂは最も温度の低い低温側流体５と高温側
流体３とが接する熱的負荷が最も厳しいところで
あり、更に点Ｂには前記第６図に示した温度の勾
配により、第７図にイ→で示すような不定形な曲が
り変形（以下変位と記す）を与える力が生じ図示
しない熱交換器本体のヘツダに応力が作用するこ
とになる。前記力イ→はロ→とハ→に分解することがで
きるが、前記プレートフイン型熱交換器を製作す
る際には前記ロ→及びハ→の両方の力を考慮して製作
しなくてはならず、製作が非常に大変である。 In addition, point B is the place where the thermal load is the severest where the low temperature side fluid 5 and the high temperature side fluid 3 are in contact with each other, and furthermore, due to the temperature gradient shown in FIG. A force that causes irregular bending deformation (hereinafter referred to as displacement) as shown by A→ is generated, and stress acts on the header (not shown) of the heat exchanger body. The force A→ can be decomposed into B→ and C→, but when manufacturing the plate fin type heat exchanger, it is necessary to consider both the forces B→ and C→. However, it is extremely difficult to produce.
従つて従来のプレートフイン型熱交換器では、
応力の集中があり、クラツクの発生、シール性の
低下等といつた問題を生じ、高温流体の熱交換に
は適用できない問題を有していた。 Therefore, in the conventional plate-fin heat exchanger,
There is a concentration of stress, which causes problems such as the occurrence of cracks and a decrease in sealing performance, which makes it impossible to apply it to heat exchange of high-temperature fluids.
本考案は、上記従来の問題点に着目してなした
もので、熱による変形を軸対称とすることにより
応力の集中を防止してプレートフイン型熱交換器
全体の強度の向上を図ることを目的としている。 The present invention was developed by focusing on the above-mentioned conventional problems, and aims to improve the overall strength of the plate-fin type heat exchanger by preventing stress concentration by making thermal deformation axially symmetrical. The purpose is
［課題を解決するための手段］
本考案は高温側流体と低温側流体が表裏におい
て対向して流れるよう幅方向に複数の流路を形成
した方形の対向流部と、該対向流部の流路方向両
端部に対称に形成され、前記対向流部の高温側流
路と低温側流路に各々連通し、且つ流れが交差す
るよう表裏に斜交高温側流路及び斜交低温側流路
を形成した斜交流部とを有し、前記高温側流体が
Ｓ字状に、又低温側流体が逆Ｓ字状に流れるよう
構成したプレート状の伝熱部材を、熱交換器本体
内に、該熱交換器本体の幅方向中心線を軸線とし
て軸対称に一体的に配設し、且つ前記熱交換器本
体の軸線上に、軸線側に向いた斜交高温側流路に
連通する高温出側ヘツダ及び軸線側に向いた斜交
低温側流路に連通する低温出側ヘツダを配設し、
且つ反軸線側に、反軸線側に向いた斜交低温側流
路に連通する低温入側ヘツダ及び反軸線側に向い
た斜交高温側流路に連通する高温入側ヘツダを配
設したことを特徴とするプレートフイン型熱交換
器にかかるものである。[Means for Solving the Problems] The present invention provides a rectangular counterflow section in which a plurality of channels are formed in the width direction so that high-temperature side fluid and low-temperature side fluid flow oppositely on the front and back sides, and a flow path in the counterflow section. An oblique high-temperature side flow path and an oblique low-temperature side flow path are formed symmetrically at both ends in the flow direction, communicate with the high temperature side flow path and the low temperature side flow path of the opposing flow section, and are arranged on the front and back so that the flows intersect. A plate-shaped heat transfer member is provided in the heat exchanger main body, and the plate-shaped heat transfer member is configured such that the high-temperature fluid flows in an S-shape and the low-temperature fluid flows in an inverted S-shape. A high-temperature outlet is integrally arranged axially symmetrically with the center line in the width direction of the heat exchanger body as an axis, and is connected to the diagonal high-temperature side flow path facing the axis on the axis of the heat exchanger body. A low-temperature outlet header is provided that communicates with the side header and the oblique low-temperature side flow path facing the axis,
In addition, a low-temperature inlet header communicating with the diagonal low-temperature side flow path facing the anti-axis side and a high-temperature input header communicating with the diagonal high-temperature side flow path facing the anti-axis side are arranged on the anti-axis side. This relates to a plate-fin type heat exchanger characterized by the following.
［作用］
熱交換器本体内に、該熱交換器本体の幅方向中
心線を軸線として伝熱部材を軸対称に一体に構成
しているので、高温出側ヘツダ及び低温出側ヘツ
ダに作用する伝熱部材の軸線方向の変位が相殺さ
れ、よつて局部的な熱応力の発生が防止されると
共に、高温入側ヘツダの断面積を十分に確保する
ために、高温入側ヘツダを反軸線側に分割して配
設してあるので、高温入側ヘツダへの熱応力の集
中が防止されてプレートフイン型熱交換器全体の
熱変形耐力は向上する。[Function] Since the heat transfer member is integrally constructed in the heat exchanger body in an axially symmetrical manner with the axis in the width direction of the heat exchanger body, it acts on the high-temperature outlet header and the low-temperature outlet header. The displacement of the heat transfer member in the axial direction is canceled out, thereby preventing the generation of local thermal stress, and in order to ensure a sufficient cross-sectional area of the high temperature input header, the high temperature input header is placed on the opposite axial side. Since the heat exchanger is divided into two parts, concentration of thermal stress on the high-temperature input header is prevented, and the thermal deformation resistance of the entire plate-fin type heat exchanger is improved.
［実施例］
以下、図面に基づいて本考案の実施例を説明す
る。[Example] Hereinafter, an example of the present invention will be described based on the drawings.
第１図〜第３図は本考案の一実施例である。 1 to 3 show an embodiment of the present invention.
熱交換器本体８に伝熱部材９が一体に配設され
ている。 A heat transfer member 9 is integrally provided with the heat exchanger body 8.
該伝熱部材９は方形を有し高温側流体３と低温
側流体５が表裏において対向して流れるよう幅方
向に複数の流路を形成した対向流部２と、該対向
流部２の流路方向両端部に対称に形成され、前記
対向流部２の高温側流路４と低温側流路６に各々
連通し、且つ流れが交差するよう表裏に斜交高温
側流路１０及び斜交低温側流路１１を形成した斜
交流部１とを有し、前記高温側流路４がＳ字状
に、又低温側流路６が逆Ｓ字状に流れるよう構成
されており、且つ前記伝熱部材９は、熱交換器本
体８の幅方向中心線を軸線１２として軸対称に一
体的に構成されている。 The heat transfer member 9 has a rectangular shape and includes a counterflow section 2 in which a plurality of channels are formed in the width direction so that the high temperature side fluid 3 and the low temperature side fluid 5 flow oppositely on the front and back sides, and a flow path in the counterflow section 2. They are formed symmetrically at both ends in the flow direction, communicate with the high temperature side flow path 4 and the low temperature side flow path 6 of the counter flow section 2, and have an oblique high temperature side flow path 10 and an oblique cross flow path on the front and back so that the flows intersect. The high temperature side flow path 4 is configured to flow in an S-shape, and the low temperature side flow path 6 is configured to flow in an inverted S-shape. The heat transfer member 9 is integrally constructed axially symmetrically with respect to the width direction center line of the heat exchanger main body 8 as an axis line 12 .
更に、前記熱交換器本体８の軸線１２上には、
軸線１２側に向いた斜交高温側流路１０に連通す
る高温出側ヘツダ１３及び軸線１２側に向いた斜
交低温側流路１１に連通する低温出側ヘツダ１４
が配設され、且つ反軸線１２側（軸線１２から熱
交換器本体８の幅方向に遠ざかる方向）には、反
軸線１２に向いた斜交低温側流路１１に連通する
低温入側ヘツダ１５及び反軸線１２側に向いた斜
交高温側流路１０に連通する高温入側ヘツダ１６
が配設されている。 Furthermore, on the axis 12 of the heat exchanger main body 8,
A high temperature outlet header 13 communicates with the oblique high temperature side flow path 10 facing the axis 12 side, and a low temperature outlet header 14 communicates with the oblique low temperature side flow path 11 facing the axis 12 side.
is disposed, and on the opposite axis 12 side (the direction away from the axis 12 in the width direction of the heat exchanger main body 8), there is a cold inlet header 15 that communicates with the oblique low temperature side flow path 11 facing the opposite axis 12. and a high-temperature inlet header 16 that communicates with the oblique high-temperature side flow path 10 facing the opposite axis 12 side.
is installed.
上述した如き構成によると、伝熱部材９、高温
側流体３の入出側ヘツダ１６，１３及び低温側流
体５の入出側ヘツダ１５，１４が熱交換器本体８
の幅方向中心線を中心とする軸線１２に対して軸
対称となるので、軸線１２方向の熱変形は相殺さ
れ、局部的な応力の集中が防止される。 According to the configuration described above, the heat transfer member 9, the inlet/outlet headers 16, 13 for the high temperature fluid 3, and the inlet/outlet headers 15, 14 for the low temperature fluid 5 are connected to the heat exchanger main body 8.
Since it is axially symmetrical with respect to the axis 12 centered on the center line in the width direction, thermal deformation in the direction of the axis 12 is canceled out, and local concentration of stress is prevented.
又、反軸線１２側に高温入側ヘツダ１６を分割
して配設することにより、十分な高温入側ヘツダ
１６の断面積が確保されて熱応力の集中が防止さ
れる。 Further, by dividing and arranging the high-temperature input header 16 on the side opposite to the axis 12, a sufficient cross-sectional area of the high-temperature input header 16 is ensured, and concentration of thermal stress is prevented.
第６図及び第７図に示した如き、従来熱応力の
集中のはげしかつた点Ａ、点Ｂについて述べる。 Points A and B, as shown in FIGS. 6 and 7, where thermal stress has conventionally been concentrated will be described.
第３図に示す如く、点Ａにおいて熱膨張が発生
しても、この熱膨張は背中合わせの伝熱部材９，
９の両方で同時に起こるため、点Ａにおける熱膨
張による変形は相殺されて点Ａに熱応力がかかる
ことはない。 As shown in FIG. 3, even if thermal expansion occurs at point A, this thermal expansion is caused by the back-to-back heat transfer members 9,
9 at the same time, the deformation due to thermal expansion at point A is canceled out and no thermal stress is applied to point A.
次いで、点B1及びB2に作用するイ→で示す如き
熱膨張による伝熱部材９を変形させようとする力
のうち、ロ→で示す軸線１２ａ方向に作用する力
は、高温出側ヘツダ１３を図中上方向へ全体的に
変位させる如く作用するだけで、点B1，B2にお
けるロ→方向の力による応力は相殺によつて低減さ
れる。 Next, among the forces acting on points B 1 and B 2 that try to deform the heat transfer member 9 due to thermal expansion, as shown by A→, the force acting in the direction of the axis 12a, shown by B→, is applied to the high temperature output header. 13 in the upward direction in the figure, the stress caused by the force in the direction B at points B 1 and B 2 is reduced by canceling it out.
尚、本考案のプレートフイン型熱交換器は、上
述の実施例にのみ限定されるものではなく、本考
案の要旨を逸脱しない範囲内において種々変更を
加え得ることは勿論である。 It should be noted that the plate-fin type heat exchanger of the present invention is not limited to the above-described embodiments, and it goes without saying that various changes can be made without departing from the gist of the present invention.
［考案の効果］
以上説明したように、本考案のプレートフイン
型熱交換器によれば、伝熱部材が中心線を中心と
した軸対称構造を有しているために、軸線方向の
熱変形による応力を相殺させて局部的な応力の発
生を防止すると共に、高温入側ヘツダを反軸線側
に分割して配設して、高温入側ヘツダの断面積を
十分に確保しているので、熱交換器の強度の大幅
な向上を図ることができ、よつてプレートフイン
型熱交換器をより高温熱エネルギーを有する高温
流体の熱交換に適用することが可能になる、など
の優れた効果を奏し得る。[Effects of the invention] As explained above, according to the plate-fin heat exchanger of the invention, since the heat transfer member has an axially symmetrical structure around the center line, thermal deformation in the axial direction is prevented. The high-temperature input header is divided and placed on the opposite axis to ensure a sufficient cross-sectional area of the high-temperature input header. The strength of the heat exchanger can be significantly improved, and the plate-fin type heat exchanger can be applied to heat exchange of high-temperature fluids that have higher-temperature thermal energy. It can be played.
第１図は本考案の一実施例の切断平面図、第２
図は第１図の−矢視図、第３図は応力の作用
状態を示す略図、第４図は従来のプレートフイン
型熱交換器の流路構造を示す斜視図、第５図は従
来のプレートフイン型熱交換器の伝熱部材の形状
を示す斜視図、第６図は従来の伝熱部材の温度分
布の状態を示す略図、第７図は従来の熱応力の作
用状態を示す略図である。
図中１は斜交流部、２は対向流部、３は高温側
流体、５は低温側流体、８は熱交換器本体、９は
伝熱部材、１０は斜交高温側流路、１１は斜交低
温側流路、１２は軸線、１３は高温出側ヘツダ、
１４は低温出側ヘツダ、１５は低温入側ヘツダ、
１６は高温入側ヘツダを示す。
Figure 1 is a cutaway plan view of one embodiment of the present invention;
The figures are a view from the - arrow in Fig. 1, Fig. 3 is a schematic diagram showing the state of stress action, Fig. 4 is a perspective view showing the flow passage structure of a conventional plate-fin type heat exchanger, and Fig. 5 is a conventional FIG. 6 is a perspective view showing the shape of a heat transfer member of a plate-fin type heat exchanger, FIG. 6 is a schematic diagram showing the state of temperature distribution of a conventional heat transfer member, and FIG. 7 is a schematic diagram showing the state of action of conventional thermal stress. be. In the figure, 1 is an oblique flow section, 2 is a counter flow section, 3 is a high temperature side fluid, 5 is a low temperature side fluid, 8 is a heat exchanger main body, 9 is a heat transfer member, 10 is an oblique high temperature side flow path, 11 is a An oblique low-temperature side flow path, 12 is an axis, 13 is a high-temperature outlet header,
14 is a low temperature output header, 15 is a low temperature input header,
16 indicates a high temperature entry header.
Claims (1)
て流れるよう幅方向に複数の流路を形成した方形
の対向流部と、該対向流部の流路方向両端部に対
称に形成され、前記対向流部の高温側流路と低温
側流路に各々連通し、且つ流れが交差するよう表
裏に斜交高温側流路及び斜交低温側流路を形成し
た斜交流部とを有し、前記高温側流体がＳ字状
に、又低温側流体が逆Ｓ字状に流れるよう構成し
たプレート状の伝熱部材を、熱交換器本体内に、
該熱交換器本体の幅方向中心線を軸線として軸対
称に一体的に配設し、且つ前記熱交換器本体の軸
線上に、軸線側に向いた斜交高温側流路に連通す
る高温出側ヘツダ及び軸線側に向いた斜交低温側
流路に連通する低温出側ヘツダを配設し、且つ反
軸線側に、反軸線側に向いた斜交低温側流路に連
通する低温入側ヘツダ及び反軸線側に向いた斜交
高温側流路に連通する高温入側ヘツダを配設した
ことを特徴とするプレートフイン型熱交換器。 A rectangular opposed flow section in which a plurality of channels are formed in the width direction so that the high temperature side fluid and the low temperature side fluid flow oppositely on the front and back sides; The diagonal flow section has an oblique flow section that communicates with the high temperature side flow path and the low temperature side flow path of the flow section, and has an oblique high temperature side flow path and an oblique low temperature side flow path formed on the front and back surfaces so that the flows intersect, A plate-shaped heat transfer member configured so that the high-temperature side fluid flows in an S-shape and the low-temperature side fluid flows in an inverted S-shape is installed inside the heat exchanger body.
A high-temperature outlet is integrally arranged axially symmetrically with the center line in the width direction of the heat exchanger body as an axis, and is connected to the diagonal high-temperature side flow path facing the axis on the axis of the heat exchanger body. A low-temperature outlet header that communicates with the side header and the oblique low-temperature side flow path facing the axis side is provided, and a low-temperature inlet header that communicates with the oblique low-temperature side flow path facing the opposite axis is disposed on the opposite axis side. A plate fin type heat exchanger characterized in that a high-temperature inlet header is provided that communicates with the header and an oblique high-temperature side flow path facing away from the axis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985057081U JPH0547960Y2 (en) | 1985-04-17 | 1985-04-17 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985057081U JPH0547960Y2 (en) | 1985-04-17 | 1985-04-17 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61175763U JPS61175763U (en) | 1986-11-01 |
| JPH0547960Y2 true JPH0547960Y2 (en) | 1993-12-17 |
Family
ID=30581276
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985057081U Expired - Lifetime JPH0547960Y2 (en) | 1985-04-17 | 1985-04-17 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0547960Y2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU2003902200A0 (en) | 2003-05-06 | 2003-05-22 | Meggitt (Uk) Ltd | Heat exchanger core |
| DE10352880A1 (en) * | 2003-11-10 | 2005-06-09 | Behr Gmbh & Co. Kg | Heat exchanger, in particular charge air / coolant radiator |
| DE10352881A1 (en) | 2003-11-10 | 2005-06-09 | Behr Gmbh & Co. Kg | Heat exchanger, in particular charge air / coolant radiator |
| JP4681528B2 (en) * | 2006-09-29 | 2011-05-11 | 三菱重工業株式会社 | Heat exchanger header structure |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5355545A (en) * | 1976-10-29 | 1978-05-20 | Alfa Laval Ab | Plate heat exchanger |
| JPS56993A (en) * | 1979-06-13 | 1981-01-08 | Hisaka Works Ltd | Plate-type heat exchanger |
| JPS5928225U (en) * | 1982-08-17 | 1984-02-22 | 未来工業株式会社 | Tension tool interposed between the box and concrete temporary frame |
-
1985
- 1985-04-17 JP JP1985057081U patent/JPH0547960Y2/ja not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5355545A (en) * | 1976-10-29 | 1978-05-20 | Alfa Laval Ab | Plate heat exchanger |
| JPS56993A (en) * | 1979-06-13 | 1981-01-08 | Hisaka Works Ltd | Plate-type heat exchanger |
| JPS5928225U (en) * | 1982-08-17 | 1984-02-22 | 未来工業株式会社 | Tension tool interposed between the box and concrete temporary frame |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61175763U (en) | 1986-11-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4081025A (en) | Multiple fluid stacked plate heat exchanger | |
| US5400854A (en) | Heat exchanger | |
| US4249597A (en) | Plate type heat exchanger | |
| JPH0547960Y2 (en) | ||
| JPS61180892A (en) | Plate type heat exchanger | |
| JP2761517B2 (en) | Plate heat exchanger | |
| JPH033824Y2 (en) | ||
| JPS63210595A (en) | Plate fin type heat exchanger | |
| KR960005790B1 (en) | Heat-exchangers | |
| JPS61114094A (en) | Heat exchanger | |
| JPH0722613Y2 (en) | Plate fin type heat exchanger | |
| JPH03177791A (en) | Lamination type heat exchanger | |
| JPS5938598A (en) | Plate type heat exchanger | |
| JP4230611B2 (en) | Plate heat exchanger | |
| JPS59183296A (en) | Heat exchanger of plate fin type | |
| JP2741950B2 (en) | Stacked heat exchanger | |
| JPH0624688Y2 (en) | Plate fin type heat exchanger | |
| JPH0722612Y2 (en) | Plate fin type heat exchanger | |
| JPH0624691Y2 (en) | Plate fin type heat exchanger | |
| JPH0645162Y2 (en) | Plate fin type heat exchanger | |
| JPS59163766U (en) | Heat exchanger | |
| JPH04371794A (en) | Lamination type heat exchanger | |
| JPH0645166Y2 (en) | Plate fin type heat exchanger | |
| JPH0129439Y2 (en) | ||
| JPH073164Y2 (en) | Plate fin type heat exchanger |