JP2005291546A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP2005291546A
JP2005291546A JP2004103676A JP2004103676A JP2005291546A JP 2005291546 A JP2005291546 A JP 2005291546A JP 2004103676 A JP2004103676 A JP 2004103676A JP 2004103676 A JP2004103676 A JP 2004103676A JP 2005291546 A JP2005291546 A JP 2005291546A
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plate
heat exchanger
exchanger according
plates
fluid
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Kenji Miyamoto
健二 宮本
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/048—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prevent damage by repetitive deformation and fatigue by fluid pressure, in a heat exchanger for laminating plates forming fluid passages on a surface. <P>SOLUTION: This heat exchanger having a multilayer structure is constituted by arranging clearance between a wall surface top part 12c between adjacent grooves of the plates and the other plate opposed to the top part, by defining the fluid passages 14 and 15 between the adjacent plates by laminating a plurality of plates 12 forming a plurality of grooves 12a on the surface. Here, a wall surface of the plates positioned on the outermost side of one end or both ends of the multilayer structure, is formed into a structure of allowing its top part to abut on opposed end part members. Thus, even when a fluid passage forming plate is extremely thin, the plate can be restrained from being deformed in the laminating direction by the fluid pressure. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は熱交換器に関し、詳しくは表面に流体通路となる多数の溝を形成したプレートを積層してなる熱交換器の構造的改良に関する。   The present invention relates to a heat exchanger, and more particularly to a structural improvement of a heat exchanger formed by laminating a plate having a plurality of grooves formed as fluid passages on the surface.

多数のフィンまたは波型断面を有するプレートを積層した構造を有する熱交換器が知られている（特許文献１参照）。このような積層構造の熱交換器において、内部を流れる流体との熱の授受によりプレートに発生する熱応力を緩和するために、前記フィンや波型プレートの他のプレートと対向する部分を相互に接続せずに隙間を設けたものが提案されている。
特開平２００２−２０３５８６号公報 A heat exchanger having a structure in which a large number of fins or plates having corrugated cross sections are stacked is known (see Patent Document 1). In such a heat exchanger having a laminated structure, in order to relieve the thermal stress generated in the plate due to the transfer of heat with the fluid flowing inside, the portions facing the fins and the other plates of the corrugated plate are mutually connected. The thing which provided the clearance gap without connecting is proposed.
Japanese Patent Laid-Open No. 2002-203586

しかしながら、このように隙間を設けると熱交換器を構成する積層体の内部の剛性が低下してしまい、流体からの内圧による変形が生じやすくなる。内圧による変形が繰り返されると金属疲労により構造的信頼性が損なわれかねない。   However, when such a gap is provided, the internal rigidity of the laminate constituting the heat exchanger is lowered, and deformation due to internal pressure from the fluid is likely to occur. When deformation due to internal pressure is repeated, structural reliability may be impaired by metal fatigue.

また、マイクロチャンネルによる高い熱交換性能を利用した蒸発器では、液体の蒸発部を形成する流体の流路は通常の熱交換器に比べて極めて狭く、加えて小型化を図るために板の厚みは通常の熱交換器よりも薄くなっている。板の両面の流体通路には高温流体と低温流体が流れ、板のフィンのない部位は熱交換性能を優先するためにさらに薄くなっているので、前記のような隙間を有する積層構造の熱交換器を適用すると、前記内部圧力による変形に加え、熱膨張による変形も繰り返されることから、信頼性の確保がより難しくなる。   In addition, in the evaporator using the high heat exchange performance by the microchannel, the flow path of the fluid forming the liquid evaporation section is extremely narrow compared to the normal heat exchanger, and in addition, the thickness of the plate is reduced for miniaturization. Is thinner than a normal heat exchanger. High temperature fluid and low temperature fluid flow through the fluid passages on both sides of the plate, and the plateless fins are made thinner to prioritize heat exchange performance. When a vessel is applied, since deformation due to thermal expansion is repeated in addition to deformation due to the internal pressure, it becomes more difficult to ensure reliability.

本発明は、表面に複数の溝を形成したプレートを複数個積層して隣接するプレート間に流体通路を画成し、前記プレートの隣接する溝間の壁面の頂部と該頂部と対向する他のプレートとの間に間隙を設けた積層構造の熱交換器を基本構成として、前記積層構造の一方端または両端の最外側に位置するプレートの壁面は、その頂部を対向する端部部材に当接させた構造とする。   According to the present invention, a plurality of plates having a plurality of grooves formed on the surface are stacked to define a fluid passage between adjacent plates, and the top of the wall surface between the adjacent grooves of the plate and the other facing the top Based on a laminated heat exchanger with a gap between the plates, the wall surface of the plate located on the outermost side of one or both ends of the laminated structure is in contact with the opposite end member. The structure is the same.

最外側のプレートの壁面頂部を端部部材と当接させた前記構成により、熱交換器を形成する積層体の積層方向の剛性を高めることができ、これにより流体通路を形成するプレートが極めて薄い場合においても流体圧力によりプレートが積層方向に膨張ないし変形するのを抑制して、変形の繰り返しによる信頼性の低下を防ぐことができる。   With the above-described configuration in which the top of the wall surface of the outermost plate is in contact with the end member, the rigidity in the stacking direction of the stacked body forming the heat exchanger can be increased, whereby the plate forming the fluid passage is extremely thin Even in the case, it is possible to prevent the plate from expanding or deforming in the stacking direction due to the fluid pressure, and to prevent a decrease in reliability due to repeated deformation.

以下、本発明の実施形態を図面に基づいて説明する。図１において、１１は熱交換器の本体またはコアを構成する積層体を示している。積層体１１は、複数個（図では６枚）のプレート１２とその両側に設けられたエンドプレート（端部部材）１３からなっている。プレート１２は、図２−１〜図２−３に示したように板状部材の両面に流体通路を構成する多数の溝１２ａがエッチング加工等により形成されている。両面の溝１２ａは、面方向から見たときに互いに直交するように異なる向きに形成されている。このプレート１２を、その溝１２ａが隣接する他のプレート１２の溝１２ａと向きが一致するように積層してゆくことで、各プレート１２間に向きが異なる２系統の流体通路１４と１５が交互に画成されるようにしている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. In FIG. 1, reference numeral 11 denotes a laminated body constituting the main body or core of the heat exchanger. The laminated body 11 includes a plurality (six in the figure) of plates 12 and end plates (end members) 13 provided on both sides thereof. In the plate 12, as shown in FIGS. 2-1 to 2-3, a large number of grooves 12a constituting fluid passages are formed on both surfaces of the plate-like member by etching or the like. The grooves 12a on both surfaces are formed in different directions so as to be orthogonal to each other when viewed from the surface direction. By laminating this plate 12 so that the direction of the groove 12a coincides with the direction of the groove 12a of the other adjacent plate 12, two fluid passages 14 and 15 having different orientations alternate between the plates 12. To be defined.

隣接するプレート１２間では溝１２ａ同士が対向することにより略円形断面の流体通路１４または１５が並行に多数形成されるが、隣り合う溝１２ａと溝１２ａとの間の壁面１２ｂは、その頂部１２ｃの高さが、隣接する他のプレート１２の壁面頂部１２ｃとの間に所定の間隙が生じるように設定されている。前述したとおり、この間隙により熱応力を吸収する作用を得ている。   A large number of fluid passages 14 or 15 having a substantially circular cross section are formed in parallel between the adjacent plates 12 because the grooves 12a face each other. The wall surface 12b between the adjacent grooves 12a and 12a has a top portion 12c. Is set so that a predetermined gap is formed between the top surface 12c of the wall surface of another adjacent plate 12. As described above, an effect of absorbing thermal stress is obtained by this gap.

ただし、積層体１１の端部に位置するプレート１１については、その外側を向いた壁面１２の頂部１２ｃがエンドプレート１３の表面に当接するように形成されている。エンドプレート１３はプレート１２に比較して高い剛性を有する厚板で形成されている。このように、最外側のプレート１２の壁面頂部１２ｃを高い曲げ剛性を有するエンドプレート１３と当接させた構成により、プレート１２が極めて薄い場合においても流体圧力により積層体１１が積層方向に膨張変形するのを抑制することができる。特に、低温流体と高温流体の圧力差があって、積層体の最も外側の通路１５を流れる流体の圧力が比較的低い場合においても、内側層のプレート１２の変形を効果的に抑制することができる。   However, the plate 11 positioned at the end of the laminated body 11 is formed such that the top portion 12c of the wall surface 12 facing the outside contacts the surface of the end plate 13. The end plate 13 is formed of a thick plate having higher rigidity than the plate 12. As described above, the structure in which the wall surface top portion 12c of the outermost plate 12 is in contact with the end plate 13 having high bending rigidity allows the laminate 11 to be expanded and deformed in the stacking direction by fluid pressure even when the plate 12 is extremely thin. Can be suppressed. In particular, even when there is a pressure difference between the low temperature fluid and the high temperature fluid and the pressure of the fluid flowing through the outermost passage 15 of the laminate is relatively low, the deformation of the inner layer plate 12 can be effectively suppressed. it can.

図３〜図６に前記エンドプレート１３に関する他の実施形態を示す。図１と異なる部分について説明すると、図３に示したものではエンドプレート１３を隣接するプレート１２の個々の壁面頂部１２ｃとロウ付け等により接合した一体化した構成となっている。これにより、エンドプレート１３とこれに隣接するプレート１２とが一体となって高剛性を発揮するので、エンドプレート１３を図１のものに比較して薄く、軽量にすることができる。図４に示したものでは、エンドプレート１３を、２枚の薄板１３ａの間に多孔質構造からなる中間層１３ｂを挟持した構成としている。中間層１３ｂとしては、例えば発泡金属板やハニカム構造体を適用することができる。この構成によれば、軽量・高剛性化を図れると共に、多孔質構造の中間層１３ｂが断熱作用を有することから熱交換器としての効率も向上する。図５に示したものでは、エンドプレート１３の内側面に、プレート１２の溝１２ａと対向するように多数の溝１３ｃを形成して、積層体１１の最外側部の流体通路１５’の断面積を、内側層のものと同等に確保できるようにしている。ただし内側層の流体通路１５とは異なり、溝１３ｃ間の壁面頂部は対向する溝１２ａ間の壁面頂部と接合させて所要の剛性を確保するようにしている。図６−１と図６−２は、エンドプレート１３のプレート１２とは反対側の表面に、エッチング加工により縦横にリブ１３ｄを形成したものである。このようにエンドプレート１３の外側面にリブ構造を設けることにより、エンドプレート１３自体の剛性を向上させつつ軽量化を図ることができる。   3 to 6 show other embodiments relating to the end plate 13. A different part from FIG. 1 will be described. In the structure shown in FIG. 3, the end plate 13 is integrated with individual wall tops 12c of the adjacent plates 12 by brazing or the like. Thereby, since the end plate 13 and the plate 12 adjacent to the end plate 13 are integrated to exhibit high rigidity, the end plate 13 can be made thinner and lighter than that of FIG. In the structure shown in FIG. 4, the end plate 13 has a structure in which an intermediate layer 13b having a porous structure is sandwiched between two thin plates 13a. As the intermediate layer 13b, for example, a metal foam plate or a honeycomb structure can be applied. According to this configuration, light weight and high rigidity can be achieved, and the efficiency as a heat exchanger is improved because the porous intermediate layer 13b has a heat insulating action. In the example shown in FIG. 5, a large number of grooves 13 c are formed on the inner surface of the end plate 13 so as to face the grooves 12 a of the plate 12, and the cross-sectional area of the fluid passage 15 ′ at the outermost portion of the laminate 11 is formed. Can be secured equivalent to that of the inner layer. However, unlike the fluid passage 15 in the inner layer, the top of the wall surface between the grooves 13c is joined to the top of the wall surface between the opposing grooves 12a to ensure the required rigidity. 6A and 6B, ribs 13d are formed vertically and horizontally on the surface of the end plate 13 opposite to the plate 12 by etching. By providing the rib structure on the outer surface of the end plate 13 in this way, it is possible to reduce the weight while improving the rigidity of the end plate 13 itself.

図７以下に、プレート１２の通路構造に関する他の実施形態を示す。図１と異なる部分について説明すると、図７に示したものでは、積層体１１の最外側に位置するプレート１２は、その溝１２ａ内に流体の流れ方向に沿ってフィン状の薄いリブ１２ｄが形成されている。これにより当該プレート１２の剛性を高め、かつ伝熱面積を大きく確保して、放熱により損失を生じやすい外側プレート部分での熱交換効率を向上させている。図８〜図９は、積層体１１の最外側に位置するプレート１２に形成した複数の溝１２ａのうち、低温流体の出口領域付近のものにのみ前記同様のリブ１２ｄを形成したものである。図８は前記積層体１１の構成を、図９−１と図９−２は前記積層体１１を熱交換器ハウジング２０に収装した蒸発器の構成を、それぞれ示している。低温流体として水を流体通路１５に、高温流体として燃焼ガスを流体通路１４にそれぞれ供給する場合、水が燃焼ガスから受熱して蒸気化する出口付近での剛性を前記リブ１２ｄにより確保するものである。詳細には、低温流体である水については、図９−１に示したように、複数の通路１５の途中に仕切部２１を設けて、ハウジング２０の一端部に設けられた入口部２０ａからの水の流れを入口側通路群１５Ａを介して反対側のチャンバ部２０ｂに導き、該チャンバ部２０ｂから出口側通路群１５Ｂへと流れを反転させ、その間に蒸気化した水を出口部２０ｃから取り出すようになっている。一方、高温流体である燃焼ガスは図９−２に示したように、前記低温流体通路１５と交差する高温流体通路１４に一方向流として供給するようになっている。この構成によれば、熱的な影響により剛性確保上不利になる低温流体出口領域のみをリブ１２ｄにより効果的に補強することができる。図１０は前記低温流体出口領域の剛性を重点的に確保するための他の実施形態であり、これは図示したようにエンドプレート１３の前記低温流体出口領域に相当する表面において、他の部分よりもリブ間隔が密となるようにリブ１３ｄを形成したものである。図中の符号１５Ａ、１５Ｂはそれぞれ図９−１に示した低温流体の入口側通路群、出口側通路群の位置を表している。   FIG. 7 and subsequent figures show other embodiments relating to the passage structure of the plate 12. The portion different from FIG. 1 will be described. In the structure shown in FIG. 7, the plate 12 located on the outermost side of the laminated body 11 has fin-shaped thin ribs 12d formed in the grooves 12a along the fluid flow direction. Has been. As a result, the rigidity of the plate 12 is increased, a large heat transfer area is secured, and the heat exchange efficiency at the outer plate portion where loss is easily caused by heat radiation is improved. FIGS. 8 to 9 show the same rib 12d formed only in the vicinity of the low temperature fluid outlet region among the plurality of grooves 12a formed in the plate 12 positioned on the outermost side of the laminated body 11. FIGS. 8 shows the configuration of the laminate 11, and FIGS. 9-1 and 9-2 show the configuration of an evaporator in which the laminate 11 is housed in the heat exchanger housing 20, respectively. When water is supplied to the fluid passage 15 as a low-temperature fluid and combustion gas is supplied to the fluid passage 14 as a high-temperature fluid, the rib 12d ensures rigidity near the outlet where water receives heat from the combustion gas and vaporizes. is there. Specifically, as shown in FIG. 9A, the water that is a low-temperature fluid is provided with a partition portion 21 in the middle of the plurality of passages 15, and from an inlet portion 20 a provided at one end portion of the housing 20. The flow of water is guided to the opposite chamber portion 20b through the inlet side passage group 15A, the flow is reversed from the chamber portion 20b to the outlet side passage group 15B, and the vaporized water is taken out from the outlet portion 20c. It is like that. On the other hand, the combustion gas, which is a high-temperature fluid, is supplied as a one-way flow to the high-temperature fluid passage 14 intersecting with the low-temperature fluid passage 15 as shown in FIG. According to this configuration, it is possible to effectively reinforce only the low-temperature fluid outlet region, which is disadvantageous in securing rigidity due to thermal influence, by the ribs 12d. FIG. 10 shows another embodiment for preferentially securing the rigidity of the cryogenic fluid outlet region. This is because the surface of the end plate 13 corresponding to the cryogenic fluid outlet region as shown in FIG. Also, ribs 13d are formed so that the rib interval is close. Reference numerals 15A and 15B in the figure respectively represent the positions of the cryogenic fluid inlet side passage group and the outlet side passage group shown in FIG.

なお、前記実施形態の構成において、２系統の流体通路１４と１５の何れを低温流体通路または高温流体通路としてもよいが、剛性および強度に対する熱的な影響を排除する観点からは、積層体１１の最外側に位置することになる流体通路１５を低温流体通路として適用することが望ましい。   In the configuration of the embodiment, any of the two fluid passages 14 and 15 may be a low temperature fluid passage or a high temperature fluid passage. However, from the viewpoint of eliminating the thermal influence on rigidity and strength, the laminate 11 It is desirable to apply the fluid passage 15 which will be located on the outermost side of the gas passage as a cryogenic fluid passage.

また、前記各実施形態では、プレート１２の両面に溝１２ａを形成しているが、これに限られず一方の面にのみ溝１２ａを形成したものを積層して熱交換器を構成してもよい。ただし、エッチング加工により溝１２ａを形成する場合は、加工上その深さに制約を有するので、実施形態として示したように両面に形成する構成としたほうが、流体通路面積ないし伝熱面積と剛性を確保する上で有利であり、また熱交換器としての部品点数を節約することができる。   Moreover, in each said embodiment, although the groove | channel 12a is formed in both surfaces of the plate 12, it is not restricted to this, You may comprise a heat exchanger by laminating | stacking what formed the groove | channel 12a only in one surface. . However, when the groove 12a is formed by etching, the depth of the process is limited. Therefore, the structure formed on both sides as shown in the embodiment has a fluid passage area or heat transfer area and rigidity. It is advantageous in securing the number of parts, and the number of parts as a heat exchanger can be saved.

本発明に係る熱交換器（積層体）の第１の実施形態の縦断面図。The longitudinal cross-sectional view of 1st Embodiment of the heat exchanger (laminated body) which concerns on this invention. 前記実施形態のプレートの平面図。The top view of the plate of the said embodiment. 図２−１のＡ−Ａ断面図。AA sectional drawing of FIGS. 2-1. 図２−１のＢ−Ｂ断面図。BB sectional drawing of FIGS. 2-1. 本発明に係る熱交換器（積層体）の第２の実施形態の縦断面図。The longitudinal cross-sectional view of 2nd Embodiment of the heat exchanger (laminated body) which concerns on this invention. 本発明に係る熱交換器（積層体）の第３の実施形態の縦断面図。The longitudinal cross-sectional view of 3rd Embodiment of the heat exchanger (laminated body) which concerns on this invention. 本発明に係る熱交換器（積層体）の第４の実施形態の縦断面図。The longitudinal cross-sectional view of 4th Embodiment of the heat exchanger (laminated body) which concerns on this invention. エンドプレートに関する他の実施形態の平面図。The top view of other embodiment regarding an end plate. エンドプレートに関する他の実施形態の正面図。The front view of other embodiment regarding an end plate. 本発明に係る熱交換器（積層体）の第５の実施形態の縦断面図。The longitudinal cross-sectional view of 5th Embodiment of the heat exchanger (laminated body) which concerns on this invention. 本発明に係る熱交換器（積層体）の第６の実施形態の縦断面図。The longitudinal cross-sectional view of 6th Embodiment of the heat exchanger (laminated body) which concerns on this invention. 前記第６の実施形態の熱交換器としての構成例を示す第１の縦断面図。The 1st longitudinal cross-sectional view which shows the structural example as a heat exchanger of the said 6th Embodiment. 前記第６の実施形態の熱交換器としての構成例を示す第２の縦断面図。The 2nd longitudinal cross-sectional view which shows the structural example as a heat exchanger of the said 6th Embodiment. 図８の熱交換器（積層体）に適用するエンドプレートの平面図。The top view of the end plate applied to the heat exchanger (laminated body) of FIG.

符号の説明Explanation of symbols

１１ 熱交換器（積層体）
１２ プレート
１２ａ 溝
１２ｂ 壁面
１２ｃ 頂部
１２ｄ 溝内のリブ
１３ エンドプレート（端部部材）
１３ｂ 多孔質構造
１３ｃ 溝
１３ｄ リブ
１４ 流体通路
１５ 流体通路
２０ 熱交換器のハウジング 11 Heat exchanger (laminate)
12 Plate 12a Groove 12b Wall 12c Top 12d Rib in Groove 13 End Plate (End Member)
13b Porous structure 13c Groove 13d Rib 14 Fluid passage 15 Fluid passage 20 Heat exchanger housing

Claims (11)

表面に複数の溝を形成したプレートを複数個積層して隣接するプレート間に流体通路を画成し、かつ前記プレートの隣接する溝間の壁面の頂部と該頂部と対向する他のプレートとの間に間隙を設けた熱交換器において、
前記積層構造の最外側に位置するプレートの壁面はその頂部を対向する端部部材に当接させたことを特徴とする熱交換器。 A plurality of plates having a plurality of grooves formed on a surface thereof are stacked to define a fluid passage between adjacent plates, and a top of a wall surface between the adjacent grooves of the plate and another plate facing the top In a heat exchanger with a gap in between,
The wall surface of the plate located on the outermost side of the laminated structure has its top portion in contact with an opposing end member. 前記端部部材は、該プレートの壁面頂部に接合する板状部材である請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the end member is a plate-like member joined to the top of the wall surface of the plate. 前記端部部材は、該プレートよりも高い曲げ剛性を有する請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the end member has higher bending rigidity than the plate. 前記端部部材は、該プレートの壁面頂部との当接部間に流体通路を構成する溝が形成されている請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the end member is formed with a groove forming a fluid passage between contact portions with the top of the wall surface of the plate. 前記最外側のプレートが形成する流体通路は低温流体通路である請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the fluid passage formed by the outermost plate is a cryogenic fluid passage. 前記最外側のプレートは、流れ方向に沿って前記溝内にリブが形成されている請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the outermost plate has ribs formed in the grooves along a flow direction. 前記溝内のリブは、低温流体の出口領域の溝に形成されている請求項６に記載の熱交換器。   The heat exchanger according to claim 6, wherein the rib in the groove is formed in a groove in an outlet region of the cryogenic fluid. 前記端部部材は、該プレートとは反対側の表面にリブ構造が形成されている請求項1の記載の熱交換器。   2. The heat exchanger according to claim 1, wherein the end member has a rib structure formed on a surface opposite to the plate. 前記リブ構造は、低温流体の出口領域にてリブ間隔が密になるように形成されている請求項８に記載の熱交換器。   The heat exchanger according to claim 8, wherein the rib structure is formed so that a rib interval is close in a cold fluid outlet region. 前記端部部材は、多孔質構造を有している請求項1に記載の熱交換器。   2. The heat exchanger according to claim 1, wherein the end member has a porous structure. 前記プレートは、その両面に溝が形成されている請求項１に記載の熱交換器。   The heat exchanger according to claim 1, wherein the plate has grooves formed on both sides thereof.
JP2004103676A 2004-03-31 2004-03-31 Heat exchanger Pending JP2005291546A (en)

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