JP3829499B2 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
JP3829499B2
JP3829499B2 JP27608498A JP27608498A JP3829499B2 JP 3829499 B2 JP3829499 B2 JP 3829499B2 JP 27608498 A JP27608498 A JP 27608498A JP 27608498 A JP27608498 A JP 27608498A JP 3829499 B2 JP3829499 B2 JP 3829499B2
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heat source
source fluid
tank
passage
fluid inlet
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JP2000105097A (en
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尚規 杉本
充 木全
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Denso Corp
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Denso Corp
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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
    • F28F9/0217—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions the partitions being separate elements attached to header boxes
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/035—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other with U-flow or serpentine-flow inside the conduits
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0391—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 plate-like or laminated conduits a single plate being bent to form one or more conduits
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0091—Radiators
    • F28D2021/0096—Radiators for space heating

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、一般的に言って、空気と熱源流体（温水等）との間で熱交換を行う熱交換器に関するもので、より具体的には、車両用空調装置における温水式暖房用熱交換器に用いて好適なものである。
【０００２】
【従来の技術】
従来、車両用空調装置における温水式暖房用熱交換器では、特開平９−２５０８９５号公報記載のように、空気流れ方向の前後で温水がＵターンして流れるものが知られている。この前後Ｕターン方式のものでは、熱交換コア部の一端側に配置される温水入出用タンクを図９のごとく構成している。すなわち、この温水入出用タンク１４内部に仕切り板２３を配置し、この仕切り板２３により、タンク１４の内部空間を温水入口パイプ２０と連通する温水入口空間２４および温水出口パイプ２１と連通する温水出口空間２５とに空気流れ方向Ａの前後に仕切っている。
【０００３】
温水入口パイプ２０からの温水は、温水入口空間２４から熱交換コア部のチューブのうち、空気流れ方向前後の片側のチューブ通路を通過し、その後に、熱交換コア部の他端側でＵターンする。その後、温水は熱交換コア部のチューブのうち、空気流れ方向前後の他の片側のチューブ通路を通過してからタンク内の温水出口空間２５に流入し、温水出口パイプ２１から外部へ流出する。
【０００４】
【発明が解決しようとする課題】
ところで、上記の従来構造によると、空気流れ方向Ａと直交方向に真っ直ぐに延びる仕切り板２３により２つの空間２４、２５を仕切っているので、これらの空間２４、２５とそれぞれ連通するように温水入口、出口パイプ２０、２１を配置する際、２つの空間２４、２５の空気流れ方向Ａの厚さ寸法をそれぞれ温水入口、出口パイプ２０、２１より大きくする必要がある。その結果、タンク１４の全体の空気流れ方向Ａの厚さ寸法Ｄがどうしても大きくなってしまい、熱交換器の小型化を阻害している。
【０００５】
また、上記の従来構造によると、温水入口、出口パイプ２０、２１の位置が必然的に図９の寸法Ｌだけずれることになり、両パイプ２０、２１を同一直線上に配置できない。その結果、暖房用熱交換器を例えば水平配置する場合には、温水入口、出口パイプ２０、２１の上下方向での設置高さを必然的に異なる高さにしなければならず、この両パイプ２０、２１の位置選択の自由度が低くなり、暖房用熱交換器の車両搭載性を悪化させる。
【０００６】
また、タンク１４は、タンク本体部１６とこれに接合されるシートメタル（図示せず）とにより所定のタンク形状を構成するようになっており、そして、このシートメタルに仕切り板２３の端部が接合されるのであるが、シートメタルにはチューブの端部が挿通され、接合されるチューブ穴が形成され、複雑な凹凸形状になっているので、シートメタルや仕切り板２３の成形上の寸法ばらつきによりシートメタルと仕切り板２３の端部との間に隙間が発生して、接合（ろう付け）不良を発生しやすい。
【０００７】
この仕切り板２３の接合不良が発生すると、温水入口、出口パイプ２０、２１の間を短絡する内部温水洩れが発生して、熱交換器の放熱性能を低下させる。さらには、暖房用熱交換器への温水流量を調整して吹出空気温度を調整するタイプの空調装置では、温水流量の微小流量調整時に内部温水洩れにより、暖房用熱交換器の吹出空気温度分布を悪化させるという問題が生じる。
【０００８】
本発明は上記点に鑑みてなされたもので、熱交換コア部の一端側に配置される流体入出用タンクの内部空間を空気流れ方向の前後において熱源流体入口側と熱源流体出口側の空間に仕切る熱交換器において、タンクの空気流れ方向の厚さ寸法を縮小することを目的とする。
また、本発明は、仕切り板の接合不良による内部流体洩れを防止することを他の目的とする。
【０００９】
【課題を解決するための手段】
上記目的を達成するため、請求項１〜５記載の発明では、熱源流体入口パイプ（２０）および熱源流体出口パイプ（２１）を熱源流体入出用タンク（１４）に対して空気流れ方向（Ａ）と直交方向に延びる略一直線上に配置し、
仕切り板（２３）に、タンク（１４）内の熱源流体出口空間（２５）側へ湾曲して、熱源流体入口パイプ（２０）からの熱源流体をチューブ（１２）の第１通路（１２ａ）に案内する第１湾曲部（２３ｂ）を形成するとともに、
仕切り板（２３）に、熱源流体入口空間（２４）側へ湾曲して、チューブ（１２）の第２通路（１２ｂ）からの熱源流体を熱源流体出口パイプ（２１）に案内する第２湾曲部（２３ｃ）を形成したことを特徴としている。
【００１０】
これによると、熱源流体の出入口パイプ（２０、２１）を略一直線上に配置しても、仕切り板（２３）により入口側熱源流体と出口側熱源流体との仕切り作用を発揮するとともに、第１、第２湾曲部（２３ｂ）による案内作用によって熱源流体のスムースな流れを確保することができる。
よって、熱源流体の入出作用に支障をきたすことなく、出入口パイプ（２０、２１）の直線的配置によりタンク（１４）の空気流れ方向の厚さ寸法（Ｄ）を縮小することができ、熱交換器を小型化できる。
【００１１】
また、出入口パイプ（２０、２１）の直線的配置により、例えば、熱交換器水平配置の場合に、出入口パイプ（２０、２１）をともに上下方向の同一高さに配置することができる。従来のように、出入口パイプ（２０、２１）を異なった高さ位置に配置しなければならない場合に比して、出入口パイプ（２０、２１）の位置選択の自由度が増して車両等への搭載性を改善できる。
【００１２】
本発明は、請求項２に記載のように、熱交換コア部（１１）の他端側に、第１通路（１２ａ）からの温水を第２通路（１２ｂ）へＵターンさせるＵターン用タンク（１５）を配置した熱交換器において好適に実施できる。
また、本発明は、具体的には、請求項３に記載のように、熱源流体入口パイプ（２０）および熱源流体出口パイプ（２１）を熱源流体入出用タンク（１４）に対して空気流れ方向（Ａ）と直交方向の両端側に配置し、仕切り板（２３）の２つの湾曲部（２３ｂ）（２３ｃ）を、熱源流体入口パイプ（２０）および熱源流体出口パイプ（２１）に対応して空気流れ方向（Ａ）と直交方向の両端側に配置し、２つの湾曲部（２３ｂ）（２３ｃ）の間には熱源流体入出用タンク（１４）の中央部に位置する平板部（２３ａ）を一体に形成した構成とすることができる。
【００１３】
特に、請求項４記載の発明では、チューブは、空気流れ方向（Ａ）と平行な断面偏平状の偏平チューブ（１２）であり、また、熱源流体入出用タンク（１４）は、偏平チューブ（１２）の端部を固定するシートメタル（１８）と、熱源流体入口パイプ（２０）および熱源流体出口パイプ（２１）が配置されるタンク本体部（１６）とから構成されており、
シートメタル（１８）には偏平チューブ（１２）の端部が挿入され、接合される複数の長穴状のチューブ挿入穴（２２）を設けるとともに、この複数の長穴状のチューブ挿入穴（２２）相互の間に嵌合穴（２６）を設け、
仕切り板（２３）のうち、シートメタル（１８）側の端部（２３ｄ）に、嵌合穴（２６）に嵌合される嵌合突起（２７）を設け、嵌合穴（２６）に嵌合突起（２７）を嵌合した状態で、仕切り板（２３）をシートメタル（１８）に接合することを特徴としている。
【００１４】
これによると、熱交換器をろう付けにより一体接合する場合に、シートメタル（１８）や仕切り板（２３）の成形上の寸法ばらつきがあっても、嵌合穴（２６）と嵌合突起（２７）との嵌合部によりろう付けの起点となる接触部を必ず形成することができ、シートメタル（１８）と仕切り板（２３）との間の接合（ろう付け）性を向上できる。これにより、仕切り板（２３）の接合不良による内部流体洩れを防止することができる。
【００１５】
また、請求項５記載の発明では、請求項４における嵌合穴（２６）の代わりに、複数の長穴状のチューブ挿入穴（２２）相互の間に、このチューブ挿入穴（２２）と連通するスリット状嵌合溝（３０）を設け、このスリット状嵌合溝（３０）に仕切り板（２３）の嵌合突起（２７）を嵌合した状態で、仕切り板（２３）をシートメタル（１８）に接合することを特徴としている。
【００１６】
これによっても、スリット状嵌合溝（３０）と嵌合突起（２７）との嵌合部によりろう付けの起点となる接触部を必ず形成することができるので、請求項４と同様に、シートメタル（１８）と仕切り板（２３）との間の接合（ろう付け）性を向上して、仕切り板（２３）の接合不良による内部流体洩れを防止することができる。
【００１７】
特に、請求項５記載の発明によると、スリット状嵌合溝（３０）をチューブ挿入穴（２２）と連通するように形成しているから、仕切り板（２３）にチューブ挿入穴（２２）周縁部のバーリング形状等に対応した複雑な形状を設ける必要がなくなる。そのため、仕切り板（２３）の接合（ろう付け）性をより一層向上できる。
【００１８】
なお、上記各手段の括弧内の符号は、後述する実施形態記載の具体的手段との対応関係を示すものである。
【００１９】
【発明の実施の形態】
以下、本発明の実施の形態を図に基づいて説明する。
（第１実施形態）
図１は第１実施形態による熱交換器の全体形状を示すもので、車両用空調装置における温水式の暖房用熱交換器に適用した例を示している。この熱交換器１０では、車両エンジン（図示せず）から供給される温水（エンジン冷却水）を熱源流体として用い、この温水の熱を暖房空気中に放熱することより暖房空気を加熱するようになっている。
【００２０】
この熱交換器１０では、熱交換コア部１１を偏平チューブ１２とコルゲートフィン１３とにより構成している。図１では中央部に破断部があるため縦長となっているが、実際は、熱交換用コア部１１の上下方向寸法に比して左右方向の幅方向寸法が大きい横長形状になっている。
偏平チューブ１２は、熱交換コア部１１への暖房用空気の流れ方向Ａに対して平行な偏平状（図３参照）に形成されており、この偏平チューブ１２は図１、３の左右方向に多数個並列配置されている。そして、この多数個の偏平チューブ１２の相互間に波形状に成形されたコルゲートフィン１３を配置し接合している。このコルゲートフィン１１ａには周知のごとく暖房用空気の流れ方向に対して所定角度で斜めに多数のルーバ（図示せず）が切り起こし成形されている。
【００２１】
また、偏平チューブ１２は、図３に示すように空気流れ方向（チューブ断面長手方向）Ａの中央部に仕切り部１２ｃを有し、この仕切り部１２ｃによりチューブ内通路を第１通路（風下側通路）１２ａと第２通路（風上側通路）１２ｂとに仕切っている。ここで、偏平チューブ１２内部の第１通路１２ａは温水入口側の通路であって風下側に位置し、また、第２通路１２ｂは温水出口側の通路であって風上側に位置することにより、温水流れと空気流れとが対向流型に構成してある。これにより、熱交換コア部１１は、偏平チューブ１２の第１通路（風下通路）１２ａにより構成される第１コア部１１ａと、第２通路（風上通路）１２ｂにより構成される第２コア部１１ｂが空気流れ方向Ａの前後に区分して形成される。
【００２２】
偏平チューブ１２は、１枚の平板状のアルミニウム薄板材を曲げ成形して、両通路１２ａ、１２ｂの中間部位に仕切り部１２ｃを形成した断面偏平状に成形されるもので、その具体的材質としては、例えば、芯材（Ａ３０００系）の片面（チューブ外側の面）にろう材（Ａ４０００系）をクラッドしたアルミニウムクラッド材を用いる。コルゲートフィン１３はろう材をクラッドしないアルミニウムベア材（Ａ３０００系）を波形状に成形したものである。
【００２３】
熱交換器１０では、熱交換用コア部１１の両端側には、それぞれ、偏平チューブ１２への温水の分配、偏平チューブ１２からの温水の集合を行う第１、第２タンク１４、１５が配置されている。熱交換用コア部１１の一端（上端）側の第１タンク１４は温水入出用のタンクで、他端（下端）側の第２タンク１５は温水のＵターン用のタンクである。図１において、矢印Ｂは温水のＵターン方向を示しており、この温水のＵターンにより偏平チューブ１２内の両通路１２ａ、１２ｂを温水が上下逆方向に流れる。
【００２４】
第１、第２の両タンク１４、１５はそれぞれタンク本体部１６、１７とシートメタル１８、１９とにより所定のタンク形状（細長い直方体状）を構成している。
次に、温水入出用の第１タンク１４の具体的構造を図２により詳細に説明すると、タンク本体部１６の左右方向の一端（左端）側の上面壁面には温水入口パイプ２０の取付穴１６ａが形成され、この取付穴１６ａに温水入口パイプ２０が挿入され、接合されている。また、タンク本体部１６の左右方向の他端（右端）側には温水出口パイプ２１の取付穴１６ｂが形成され、この取付穴１６ｂに温水出口パイプ２１が挿入され、接合されている。
【００２５】
ここで、上記の温水入口パイプ２０および温水出口パイプ２１はいずれも円形の丸パイプであり、かつ、この両パイプ２０、２１は図２（ａ）に示すようにタンク左右方向（空気流れ方向Ａと直交方向）に延びる同一直線上に配置されている。一方、シートメタル１８は図２（ｂ）、（ｃ）に示すようにタンク本体部１６の開口端を閉じる板形状になっており、そして、シートメタル１８には偏平チューブ１２の端部を挿入するための長穴状のチューブ挿入穴２２（図３）がタンク左右方向に多数、並列に形成されている。このチューブ挿入穴２２の周縁部には、図３に示すようにタンク内側へ突出する打ち出し部２２ａがバーリング加工されており、この打ち出し部２２ａにより偏平チューブ１２の端部とシートメタル１８とを確実に接触させて接合している。
【００２６】
次に、温水出入口側の第１タンク１４の内部には仕切り板２３が配置されている。この仕切り板２３は第１タンク１４の内部空間を空気流れ方向Ａの前後に仕切るためのもので、空気流れ方向Ａの下流側に温水入口パイプ２０と連通する温水入口空間２４を区画し、空気流れ方向Ａの上流側に温水出口パイプ２１と連通する温水出口空間２５を区画する。
【００２７】
このように、両空間２４、２５を区画することと、両パイプ２０、２１を前述のごとくタンク左右方向に延びる同一直線上に配置することとを両立させるために、仕切り板２３の具体的形状は以下のごとく工夫してある。
すなわち、仕切り板２３において、タンク左右方向の中央部位にはタンク本体部１６の前後の壁面と平行に延びる平板部２３ａが形成され、そして、仕切り板２３のうち、タンク左右方向の両側部位には第１、第２湾曲部２３ｂ、２３ｃが形成されている。ここで、左側の第１湾曲部２３ｂは平板部２３ａから温水出口空間２５側へ向かって湾曲することより、温水入口パイプ２０からの流入温水が図２（ｂ）のごとく温水入口空間２４を経てスムースに偏平チューブ１２内の第１通路１２ａ内に案内され流入するようにしてある。
【００２８】
また、右側の第２湾曲部２３ｃは平板部２３ａから逆に温水入口空間２４側へ向かって湾曲することより、偏平チューブ１２内の第２通路１２ｂからの温水が図２（ｃ）のごとく温水出口空間２５を経てスムースに温水出口パイプ２０へ向かって案内されるようにしてある。
仕切り板２３のうち、シートメタル１８側の端部２３ｄはタンク左右方向に沿ってタンク左右方向の全長にわたって直線状に延びる部分を形成しており、この端部２３ｄとシートメタル１８とのろう付け性向上のために次のような工夫がしてある。すなわち、シートメタル１８において、長穴状のチューブ挿入穴２２相互の間には仕切り部１２ｃに隣接して矩形状の嵌合穴２６が開けてある。一方、仕切り板２３のうち、シートメタル１８側の端部２３ｄには嵌合突起２７がシートメタル１８側へ突出形成されている。この嵌合突起２７は嵌合穴２６に対応して嵌合穴２６と同数設けられ、嵌合穴２６内に嵌合し得る大きさに設計されている。
【００２９】
また、仕切り板２３の端部２３ｄにおいて、この嵌合突起２７相互の間には、偏平チューブ１２の端部のうち、仕切り部１２ｃと当接する凹部２８、およびシートメタル１８のチューブ挿入穴２２の周縁部の打ち出し部（バーリング部）２２ａと嵌合する円弧部２９が形成されている。
なお、仕切り板２３のうち、この端部２３ｄと反対側の端部２３ｅ（図３）は左右の湾曲部２３ｂ、２３ｃと平板部２３ａとの組み合わせからなる曲がり形状（図２（ａ）の平面形状参照）でもって、タンク本体部１６の上面壁の内面に接合される。
【００３０】
温水Ｕターン用の第２タンク１５は、偏平チューブ１２の第１通路１２ａからの温水を矢印Ｂのように第２通路１２ｂへ向かってＵターンさせるものであるから、タンク内部空間を仕切る必要はなく、タンク内部は１つの空間を形成している。従って、シートメタル１９には、図３のチューブ挿入穴２２に相当する長穴状のチューブ挿入穴（図示せず）を開けておくだけでよい。
【００３１】
また、コア部１１のチューブ積層方向の最外側（図１の左右両端部）に位置するコルゲートフィン１３のさらに外側にはサイドプレート２９、３０が配設され、このサイドプレート２９、３０は最外側のコルゲートフィン１３およびシートメタル１８、１９に接合される。
なお、タンク本体部１６、１７およびシートメタル１８、１９は芯材（Ａ３０００系）の片面（外側面）のみにろう材（Ａ４０００系）をクラッドした片面アルミニウムクラッド材で成形され、仕切り板２３は芯材（Ａ３０００系）の両面にろう材（Ａ４０００系）をクラッドした両面アルミニウムクラッド材で成形されている。
【００３２】
上記した熱交換器では、その他の部材もすべてアルミニウム（アルミニウム合金を含む）で形成され、図１の組付状態に組付けた後に、この組付体をろう付け炉に搬入して、各部材間を一体ろう付けすることより、熱交換器全体の組付が完了する。
ところで、このろう付け前の組付工程において、仕切り板２３はシートメタル１８に対して嵌合突起２７を嵌合穴２６に嵌合するから、仕切り板２３やシートメタル１８の成形上の寸法ばらつきが生じても、嵌合突起２７と嵌合穴２６との嵌合部では、この両者間の相対位置調整により寸法ばらつきを吸収できる。従って、成形上の寸法ばらつきに影響されることなく、仕切り板２３とシートメタル１８間の接触部を常に確実に形成できる。
【００３３】
その結果、この嵌合突起２７と嵌合穴２６との嵌合接触部をろう付けの起点として、仕切り板２３とシートメタル１８とを良好にろう付けにより接合できる。そのため、仕切り板２３の接合不良によるタンク１４内での内部温水洩れ（温水入口、出口パイプ２０、２１の間を短絡する温水流れ）の発生を防止できる。
次に、上記構成において作動を説明すると、熱交換器１０の温水入出用タンク１４の温水入口パイプ２０と温水出口パイプ２１は、車両走行用の水冷式エンジン（図示せず）の温水回路に接続されるので、車両エンジンの運転時には車両側ウォータポンプの作動により温水が循環する。車両エンジンからの温水は入口パイプ２０から仕切り板２３の湾曲部２３ｂの案内によりタンク１４内の温水入口空間２４内に流入し、ここから、偏平チューブ１２の第１通路１２ａ内にスムースに流入する。
【００３４】
温水は第１通路１２ａを通過した後、Ｕターン用のタンク１５に至り、ここで、温水は図１の矢印Ｂのように流れ方向を反転して偏平チューブ１２の第２通路１２ｂ内に流入する。次に、温水は、この第２通路１２ｂを通過した後、タンク１４内の温水出口空間２５内に流入し、仕切り板２３の湾曲部２３ｃの案内により温水は温水出口空間２５から温水出口パイプ２１へスムースに流れる。
【００３５】
一方、車両用空調装置の送風機により空調空気は矢印Ａ方向に送風され、偏平チューブ１２とコルゲートフィン１３との間の空隙部を通過する。このとき、送風空気は偏平チューブ１２内の温水と熱交換して加熱され、温風となる。車室内への吹出空気温度の調整は、例えば、熱交換器１０への温水流量を温水弁（図示せず）により調整することにより行うことができる。
【００３６】
なお、熱交換器１０において、偏平チューブ１２の温水入口側の第１通路１２ａを空気流れ方向Ａの下流側に配置し、温水出口側の第２通路１２ｂを空気流れ方向Ａの上流側に配置することにより、効率の良い対向流の熱交換を行うことができる。
（第２実施形態）
図６〜図８は第２実施形態であり、仕切り板２３のうち、シートメタル１８側の端部２３ｄとシートメタル１８とのろう付け性向上のための組付構造の他の例である。
【００３７】
第１実施形態では、シートメタル１８において、長穴状のチューブ挿入穴２２相互の間に仕切り部１２ｃに隣接して矩形状の嵌合穴２６を開けているが、第２実施形態ではこの嵌合穴２６を廃止し、その代わりに、シートメタル１８において、長穴状のチューブ挿入穴２２の中央位置（偏平チューブ１２の仕切り部１２ｃと同一位置）に、チューブ挿入穴２２と連通するスリット状の嵌合溝３０を開けている。このスリット状の嵌合溝３０はチューブ挿入穴２２の長手方向（空気流れ方向Ａ）と直交する方向に延びるものである。
【００３８】
一方、仕切り板２３のうち、シートメタル１８側の端部２３ｄに突出形成される嵌合突起２７は上記スリット状の嵌合溝３０に嵌合するため、第１実施形態の場合より幅広く形成してある。
ところで、第１実施形態では円弧部２９をチューブ挿入穴２２の周縁部の打ち出し部（バーリング部）２２ａと嵌合する形状に成形する必要があり、その寸法精度を出すのが難しい。これに対し、第２実施形態によると、嵌合突起２７相互の間には第１実施形態の円弧部２９を形成する必要がなくなって、偏平チューブ１２の端部の仕切り部１２ｃと当接する凹部２８を設けるだけでよい。その結果、第１実施形態に比して第２実施形態の方が仕切り板２３とシートメタル１８とのろう付け性をより一層向上できる。
【００３９】
なお、第２実施形態では、チューブ挿入穴２２と連通するスリット状嵌合溝３０の形成により、シートメタル１８の剛性が低下して、シートメタル１８が変形しやすくなる恐れがあるので、スリット状嵌合溝３０をタンク左右方向（空気流れ方向Ａと直交方向）に連続して形成せずに、タンク左右方向の途中部位にスリット状嵌合溝３０を分断して、チューブ挿入穴２２相互間の部位を空気流れ方向Ａで連結する部分を形成した方が好ましい。
【００４０】
（他の実施形態）
なお、上記した実施形態では、熱交換器のチューブ１２として一枚の金属薄板にて第１、第２の通路１２ａ、１２ｂを一体成形するタイプのものについて説明したが、第１、第２の通路１２ａ、１２ｂをそれぞれ独立に成形した２本のチューブで構成してもよいことは勿論である。
【００４１】
また、温水入出用のタンク１４において、温水入口パイプ２０と温水出口パイプ２１とを完全に一直線上に配置せず、微小量だけ、この両パイプ２０、２１をずらして配置しても実用上は差し支えない。
また、上記した実施形態では、本発明を車両用空調装置における温水式暖房用熱交換器に適用した場合について説明したが、本発明はこれに限らず、温水等の熱源流体と空気との間で熱交換を行う熱交換器一般に広く適用可能である。例えば、冷水と空気との間で熱交換を行う冷水式の冷房用熱交換器に本発明を適用してもよい。
【図面の簡単な説明】
【図１】本発明の第１実施形態を示す熱交換器の斜視図である。
【図２】（ａ）は図１の熱交換器における温水入出用タンクの上面図、（ｂ）は（ａ）のＣ−Ｃ断面図、（ｃ）は（ａ）のＤ−Ｄ断面図である。
【図３】図１の熱交換器の要部の分解斜視図である。
【図４】図３の組付状態の断面図で、図５のＥ−Ｅ断面を示す。
【図５】図３の組付状態の上面図である。
【図６】本発明の第２実施形態を示すもので、図３に相当する要部の分解斜視図である。
【図７】図６の組付状態の断面図で、図８のＦ−Ｆ断面を示す。
【図８】図６の組付状態の上面図である。
【図９】従来の熱交換器における温水入出用タンクの断面図である。
【符号の説明】
１１…熱交換コア部、１２…偏平チューブ、１２ａ…第１通路、
１２ｂ…第２通路、１３…コルゲートフィン、１４…温水入出用タンク、
１５…温水Ｕターン用タンク、１６、１７…タンク本体部、
１８、１９…シートメタル、２０…温水入口パイプ、２１…温水出口パイプ、
２２…チューブ挿入穴、２３…仕切り板、２３ａ…平板部、
２３ｂ、２３ｃ…第１、第２湾曲部、２６…嵌合穴、２７…嵌合突起、
３０…スリット状嵌合溝。[0001]
BACKGROUND OF THE INVENTION
TECHNICAL FIELD The present invention generally relates to a heat exchanger that exchanges heat between air and a heat source fluid (hot water or the like), and more specifically, heat exchange for hot water heating in a vehicle air conditioner. It is suitable for use in a vessel.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, a hot water heating heat exchanger in a vehicle air conditioner is known in which hot water flows in a U-turn before and after the air flow direction as described in JP-A-9-250895. In this front-rear U-turn type, the hot water in / out tank disposed on one end side of the heat exchange core is configured as shown in FIG. That is, a partition plate 23 is arranged inside the hot water inlet / outlet tank 14, and the partition plate 23 allows the hot water outlet space 24 and the hot water outlet pipe 21 to communicate the internal space of the tank 14 with the hot water inlet pipe 20. The space 25 is partitioned before and after the air flow direction A.
[0003]
Hot water from the hot water inlet pipe 20 passes through the tube passage on one side of the tube of the heat exchange core part from the hot water inlet space 24 and before and after the air flow direction, and then U-turns on the other end side of the heat exchange core part. To do. Thereafter, the hot water passes through the tube passage on the other side of the heat exchange core portion before and after the air flow direction, and then flows into the hot water outlet space 25 in the tank and flows out from the hot water outlet pipe 21 to the outside.
[0004]
[Problems to be solved by the invention]
By the way, according to the above conventional structure, since the two spaces 24 and 25 are partitioned by the partition plate 23 extending straight in the direction orthogonal to the air flow direction A, the hot water inlet is connected to each of the spaces 24 and 25. When the outlet pipes 20 and 21 are arranged, it is necessary to make the thickness dimension in the air flow direction A of the two spaces 24 and 25 larger than the hot water inlet and the outlet pipes 20 and 21, respectively. As a result, the thickness dimension D of the entire tank 14 in the air flow direction A inevitably increases, which hinders the downsizing of the heat exchanger.
[0005]
Further, according to the above-described conventional structure, the positions of the hot water inlet and outlet pipes 20 and 21 are inevitably shifted by the dimension L in FIG. 9, and the pipes 20 and 21 cannot be arranged on the same straight line. As a result, when the heating heat exchanger is disposed horizontally, for example, the installation heights of the hot water inlet and outlet pipes 20 and 21 in the vertical direction must be different from each other. , 21 position selection freedom is reduced, and the vehicle mountability of the heating heat exchanger is deteriorated.
[0006]
The tank 14 is configured to have a predetermined tank shape by the tank main body 16 and a sheet metal (not shown) joined thereto, and the end of the partition plate 23 is formed on the sheet metal. However, since the end of the tube is inserted into the sheet metal and the tube hole to be joined is formed and has a complicated uneven shape, the dimensions in forming the sheet metal and the partition plate 23 are formed. Due to the variation, a gap is generated between the sheet metal and the end portion of the partition plate 23, and a bonding (brazing) defect is likely to occur.
[0007]
When the joining failure of the partition plate 23 occurs, an internal hot water leak that short-circuits between the hot water inlet and the outlet pipes 20 and 21 occurs, thereby degrading the heat dissipation performance of the heat exchanger. Furthermore, in the type of air conditioner that adjusts the temperature of the blown air by adjusting the flow rate of hot water to the heat exchanger for heating, the temperature distribution of the blown air in the heat exchanger for heating is caused by internal hot water leakage when adjusting the minute flow rate of the hot water flow rate. The problem of worsening occurs.
[0008]
The present invention has been made in view of the above points, and the internal space of the fluid inlet / outlet tank disposed on one end side of the heat exchange core portion is divided into a space on the heat source fluid inlet side and the heat source fluid outlet side in the air flow direction. The purpose of the partitioning heat exchanger is to reduce the thickness dimension of the tank in the air flow direction.
Another object of the present invention is to prevent internal fluid leakage due to poor bonding of partition plates.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, according to the first to fifth aspects of the present invention, the heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21) are arranged in the air flow direction (A) with respect to the heat source fluid inlet / outlet tank (14). Arranged on a substantially straight line extending in a direction orthogonal to the
The partition plate (23) curves toward the heat source fluid outlet space (25) in the tank (14), and the heat source fluid from the heat source fluid inlet pipe (20) flows into the first passage (12a) of the tube (12). Forming the first curved portion (23b) to be guided;
A second bending portion that curves toward the heat source fluid inlet space (24) and guides the heat source fluid from the second passage (12b) of the tube (12) to the heat source fluid outlet pipe (21) in the partition plate (23). (23c) is formed.
[0010]
According to this, even if the inlet / outlet pipes (20, 21) for the heat source fluid are arranged substantially in a straight line, the partition plate (23) exerts the partition action between the inlet side heat source fluid and the outlet side heat source fluid, and the first A smooth flow of the heat source fluid can be ensured by the guiding action by the second bending portion (23b).
Therefore, the thickness dimension (D) in the air flow direction of the tank (14) can be reduced by the linear arrangement of the inlet / outlet pipes (20, 21) without hindering the input / output operation of the heat source fluid, and heat exchange The device can be downsized.
[0011]
Further, due to the linear arrangement of the inlet / outlet pipes (20, 21), for example, in the case of horizontal heat exchanger arrangement, the inlet / outlet pipes (20, 21) can be arranged at the same height in the vertical direction. Compared to the case where the entrance / exit pipes (20, 21) must be arranged at different height positions as in the prior art, the degree of freedom in selecting the position of the entrance / exit pipes (20, 21) is increased, so Mountability can be improved.
[0012]
According to the present invention, as described in claim 2, a U-turn tank that makes U-turn the hot water from the first passage (12a) to the second passage (12b) on the other end side of the heat exchange core portion (11). It can implement suitably in the heat exchanger which has arrange | positioned (15).
Further, according to the present invention, specifically, the heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21) are arranged in the direction of air flow with respect to the heat source fluid inlet / outlet tank (14). (A) are arranged at both ends in the direction orthogonal to the two curved portions (23b) (23c) of the partition plate (23) corresponding to the heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21). A flat plate portion (23a) located at the center portion of the heat source fluid inlet / outlet tank (14) is disposed between the two curved portions (23b) and (23c). It can be set as the structure formed integrally.
[0013]
In particular, in the invention of claim 4, the tube is a flat tube (12) having a flat cross section parallel to the air flow direction (A), and the heat source fluid inlet / outlet tank (14) is a flat tube (12). ) And a tank body (16) in which the heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21) are arranged,
The end portion of the flat tube (12) is inserted into the sheet metal (18), and a plurality of long hole-like tube insertion holes (22) to be joined are provided, and the plurality of long hole-like tube insertion holes (22) are provided. ) Provide a fitting hole (26) between them,
A fitting projection (27) to be fitted into the fitting hole (26) is provided at the end (23d) on the sheet metal (18) side of the partition plate (23), and fitted into the fitting hole (26). The partition plate (23) is joined to the sheet metal (18) with the mating protrusion (27) fitted.
[0014]
According to this, when the heat exchanger is integrally joined by brazing, the fitting hole (26) and the fitting projection ( 27), a contact portion serving as a starting point of brazing can be formed without fail, and the joining (brazing) property between the sheet metal (18) and the partition plate (23) can be improved. Thereby, internal fluid leakage due to poor bonding of the partition plate (23) can be prevented.
[0015]
In the invention according to claim 5, instead of the fitting hole (26) in claim 4, the tube insertion hole (22) communicates with each other between the plurality of elongated tube insertion holes (22). In the state where the slit-like fitting groove (30) is provided, and the fitting projection (27) of the partition plate (23) is fitted into the slit-like fitting groove (30), the partition plate (23) is made of sheet metal ( 18).
[0016]
Also according to this, since the contact portion that becomes the starting point of brazing can be surely formed by the fitting portion between the slit-like fitting groove (30) and the fitting protrusion (27), The joining (brazing) property between the metal (18) and the partition plate (23) can be improved, and internal fluid leakage due to poor joining of the partition plate (23) can be prevented.
[0017]
In particular, according to the invention described in claim 5, since the slit-like fitting groove (30) is formed so as to communicate with the tube insertion hole (22), the periphery of the tube insertion hole (22) is formed in the partition plate (23). It is not necessary to provide a complicated shape corresponding to the burring shape of the part. Therefore, the joining (brazing) property of the partition plate (23) can be further improved.
[0018]
In addition, the code | symbol in the bracket | parenthesis of each said means shows a corresponding relationship with the specific means of embodiment description later mentioned.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 shows the overall shape of a heat exchanger according to the first embodiment, and shows an example applied to a hot water heating heat exchanger in a vehicle air conditioner. In this heat exchanger 10, warm water (engine cooling water) supplied from a vehicle engine (not shown) is used as a heat source fluid, and the heating air is heated by radiating the heat of the warm water into the heating air. It has become.
[0020]
In this heat exchanger 10, the heat exchange core portion 11 is constituted by a flat tube 12 and a corrugated fin 13. In FIG. 1, the center portion has a fractured portion and is vertically long. However, in actuality, the heat exchanging core portion 11 has a horizontally long shape in which the widthwise dimension in the left-right direction is larger.
The flat tube 12 is formed in a flat shape (see FIG. 3) parallel to the flow direction A of the heating air to the heat exchange core portion 11, and the flat tube 12 extends in the left-right direction in FIGS. Many are arranged in parallel. And the corrugated fin 13 shape | molded by the waveform between the many flat tubes 12 is arrange | positioned and joined. As is well known, a number of louvers (not shown) are cut and raised on the corrugated fins 11a at a predetermined angle with respect to the flow direction of the heating air.
[0021]
Further, as shown in FIG. 3, the flat tube 12 has a partition portion 12c at the center of the air flow direction (tube cross-sectional longitudinal direction) A, and the partition portion 12c serves as a first passage (leeward side passage). ) 12a and a second passage (windward passage) 12b. Here, the first passage 12a inside the flat tube 12 is a passage on the warm water inlet side and located on the leeward side, and the second passage 12b is a passage on the warm water outlet side and located on the windward side. The hot water flow and the air flow are configured in a counterflow type. Thereby, the heat exchange core part 11 is the 2nd core part comprised by the 1st core part 11a comprised by the 1st channel | path (leeward passage) 12a of the flat tube 12, and the 2nd channel | path (windward passage) 12b. 11b is formed separately in front and rear in the air flow direction A.
[0022]
The flat tube 12 is formed by bending a single flat aluminum sheet material into a flat cross-sectional shape in which a partition portion 12c is formed at an intermediate portion between both passages 12a and 12b. For example, an aluminum clad material in which a brazing material (A4000 series) is clad on one side (surface outside the tube) of a core material (A3000 series) is used. The corrugated fin 13 is formed by corrugated aluminum bare material (A3000 series) that is not clad with a brazing material.
[0023]
In the heat exchanger 10, first and second tanks 14 and 15 for distributing hot water to the flat tube 12 and collecting hot water from the flat tube 12 are arranged on both ends of the heat exchange core 11, respectively. Has been. The first tank 14 on one end (upper end) side of the heat exchanging core 11 is a hot water in / out tank, and the second tank 15 on the other end (lower end) side is a U-turn tank for hot water. In FIG. 1, an arrow B indicates the U-turn direction of the hot water, and the hot water flows up and down in both the passages 12 a and 12 b in the flat tube 12 by the U-turn of the hot water.
[0024]
The first and second tanks 14 and 15 each have a predetermined tank shape (elongated rectangular parallelepiped shape) by the tank main body portions 16 and 17 and the sheet metals 18 and 19.
Next, the specific structure of the first tank 14 for entering and leaving the hot water will be described in detail with reference to FIG. 2. The mounting hole 16 a of the hot water inlet pipe 20 is formed on the upper wall surface of the tank body 16 on one end (left end) side in the left-right direction. The hot water inlet pipe 20 is inserted into the attachment hole 16a and joined. A mounting hole 16b for the hot water outlet pipe 21 is formed on the other end (right end) side in the left-right direction of the tank body 16, and the hot water outlet pipe 21 is inserted into and joined to the mounting hole 16b.
[0025]
Here, each of the hot water inlet pipe 20 and the hot water outlet pipe 21 is a circular round pipe, and both the pipes 20 and 21 are arranged in the tank lateral direction (air flow direction A as shown in FIG. 2A). Are arranged on the same straight line extending in the direction perpendicular to the direction. On the other hand, the sheet metal 18 has a plate shape that closes the open end of the tank body 16 as shown in FIGS. 2B and 2C, and the end of the flat tube 12 is inserted into the sheet metal 18. A large number of elongated tube insertion holes 22 (FIG. 3) are formed in parallel in the left-right direction of the tank. As shown in FIG. 3, a punched portion 22a protruding to the inside of the tank is burringed at the peripheral edge of the tube insertion hole 22, and the end of the flat tube 12 and the sheet metal 18 are securely connected by the punched portion 22a. It is in contact with and joined.
[0026]
Next, a partition plate 23 is disposed inside the first tank 14 on the warm water inlet / outlet side. This partition plate 23 is for partitioning the internal space of the first tank 14 in the front and rear direction of the air flow direction A, and defines a hot water inlet space 24 communicating with the hot water inlet pipe 20 on the downstream side of the air flow direction A. A hot water outlet space 25 communicating with the hot water outlet pipe 21 is defined on the upstream side in the flow direction A.
[0027]
Thus, in order to achieve both the partitioning of the spaces 24 and 25 and the disposition of the pipes 20 and 21 on the same straight line extending in the left-right direction of the tank as described above, the specific shape of the partition plate 23 Is devised as follows.
That is, in the partition plate 23, a flat plate portion 23a extending in parallel with the front and rear wall surfaces of the tank main body portion 16 is formed at a central portion in the left-right direction of the tank. First and second curved portions 23b and 23c are formed. Here, the first curved portion 23b on the left side is curved from the flat plate portion 23a toward the hot water outlet space 25, so that the inflowing hot water from the hot water inlet pipe 20 passes through the hot water inlet space 24 as shown in FIG. It is smoothly guided and flows into the first passage 12a in the flat tube 12.
[0028]
Further, since the second curved portion 23c on the right side is curved toward the hot water inlet space 24 side from the flat plate portion 23a, the hot water from the second passage 12b in the flat tube 12 is heated as shown in FIG. The hot water outlet pipe 20 is smoothly guided through the outlet space 25.
Of the partition plate 23, the end 23 d on the sheet metal 18 side forms a portion extending linearly over the entire length in the left-right direction of the tank along the left-right direction of the tank, and brazing the end 23 d and the sheet metal 18. The following measures have been taken to improve performance. That is, in the sheet metal 18, a rectangular fitting hole 26 is formed adjacent to the partition portion 12 c between the elongated hole-like tube insertion holes 22. On the other hand, in the partition plate 23, a fitting protrusion 27 is formed to protrude toward the sheet metal 18 at an end 23d on the sheet metal 18 side. The same number of fitting protrusions 27 as the fitting holes 26 are provided corresponding to the fitting holes 26, and the fitting protrusions 27 are designed to have a size capable of fitting into the fitting holes 26.
[0029]
Further, at the end 23 d of the partition plate 23, between the fitting protrusions 27, the recess 28 that contacts the partition 12 c and the tube insertion hole 22 of the sheet metal 18 among the ends of the flat tube 12. A circular arc portion 29 is formed to be fitted to a peripheral portion (burring portion) 22a.
Of the partition plate 23, an end 23e (FIG. 3) opposite to the end 23d is a curved shape (a plane of FIG. 2A) formed by a combination of left and right curved portions 23b, 23c and a flat plate portion 23a. The shape of the tank body 16 is joined to the inner surface of the upper surface wall.
[0030]
The second tank 15 for the hot water U-turn makes the U-turn the hot water from the first passage 12a of the flat tube 12 toward the second passage 12b as shown by an arrow B, and therefore it is necessary to partition the tank internal space. The inside of the tank forms a single space. Therefore, it is only necessary to make a long hole-like tube insertion hole (not shown) corresponding to the tube insertion hole 22 of FIG.
[0031]
Further, side plates 29 and 30 are disposed on the outer side of the corrugated fins 13 located on the outermost side (left and right end portions in FIG. 1) of the core portion 11 in the tube stacking direction. The corrugated fins 13 and the sheet metals 18 and 19 are joined.
The tank body parts 16 and 17 and the sheet metals 18 and 19 are formed of a single-sided aluminum clad material in which a brazing material (A4000 series) is clad only on one side (outer side) of the core material (A3000 series). It is formed of a double-sided aluminum clad material in which a brazing material (A4000 series) is clad on both sides of a core material (A3000 series).
[0032]
In the above heat exchanger, all other members are also formed of aluminum (including an aluminum alloy), and after assembling in the assembled state of FIG. The assembly of the entire heat exchanger is completed by brazing the gap together.
By the way, in the assembly process before brazing, since the partition plate 23 fits the fitting protrusions 27 into the fitting holes 26 with respect to the sheet metal 18, dimensional variation in molding of the partition plate 23 and the sheet metal 18. Even if this occurs, in the fitting portion between the fitting protrusion 27 and the fitting hole 26, the dimensional variation can be absorbed by adjusting the relative position between them. Therefore, the contact portion between the partition plate 23 and the sheet metal 18 can always be reliably formed without being affected by the dimensional variation in molding.
[0033]
As a result, the partition plate 23 and the sheet metal 18 can be satisfactorily joined by brazing using the fitting contact portion between the fitting protrusion 27 and the fitting hole 26 as a starting point of brazing. Therefore, it is possible to prevent the occurrence of internal hot water leakage (warm water flow that short-circuits between the hot water inlet and the outlet pipes 20 and 21) in the tank 14 due to poor connection of the partition plate 23.
Next, the operation in the above configuration will be described. The hot water inlet pipe 20 and the hot water outlet pipe 21 of the hot water inlet / outlet tank 14 of the heat exchanger 10 are connected to a hot water circuit of a water-cooled engine (not shown) for vehicle travel. Therefore, the hot water circulates by the operation of the vehicle-side water pump during operation of the vehicle engine. Hot water from the vehicle engine flows into the hot water inlet space 24 in the tank 14 from the inlet pipe 20 by the guide of the curved portion 23b of the partition plate 23, and smoothly flows into the first passage 12a of the flat tube 12 from here. .
[0034]
The hot water passes through the first passage 12a and then reaches the U-turn tank 15, where the hot water reverses the flow direction as shown by the arrow B in FIG. 1 and flows into the second passage 12b of the flat tube 12. To do. Next, the hot water passes through the second passage 12b and then flows into the hot water outlet space 25 in the tank 14, and the hot water is guided from the hot water outlet space 25 to the hot water outlet pipe 21 by guidance of the curved portion 23c of the partition plate 23. It flows smoothly.
[0035]
On the other hand, the conditioned air is blown in the direction of arrow A by the blower of the vehicle air conditioner and passes through the gap between the flat tube 12 and the corrugated fin 13. At this time, the blown air is heated by exchanging heat with the warm water in the flat tube 12 to become warm air. Adjustment of the temperature of the air blown into the passenger compartment can be performed, for example, by adjusting the flow rate of hot water to the heat exchanger 10 using a hot water valve (not shown).
[0036]
In the heat exchanger 10, the first passage 12a on the warm water inlet side of the flat tube 12 is disposed on the downstream side in the air flow direction A, and the second passage 12b on the warm water outlet side is disposed on the upstream side in the air flow direction A. By doing so, it is possible to perform efficient countercurrent heat exchange.
(Second Embodiment)
6-8 is 2nd Embodiment, and is the other example of the assembly | attachment structure for the brazing property improvement of the edge part 23d by the side of the sheet metal 18 and the sheet metal 18 among the partition plates 23. FIG.
[0037]
In the first embodiment, in the sheet metal 18, a rectangular fitting hole 26 is opened adjacent to the partition portion 12 c between the long hole-like tube insertion holes 22. In the second embodiment, this fitting is performed. The joint hole 26 is abolished, and instead, in the sheet metal 18, a slit shape communicating with the tube insertion hole 22 at the center position of the elongated hole-shaped tube insertion hole 22 (the same position as the partition portion 12 c of the flat tube 12). The fitting groove 30 is opened. The slit-like fitting groove 30 extends in a direction orthogonal to the longitudinal direction (air flow direction A) of the tube insertion hole 22.
[0038]
On the other hand, in the partition plate 23, the fitting protrusion 27 formed to protrude from the end portion 23d on the sheet metal 18 side is fitted to the slit-like fitting groove 30, so that it is formed wider than the case of the first embodiment. It is.
By the way, in 1st Embodiment, it is necessary to shape | mold the circular arc part 29 in the shape fitted with the punching part (burring part) 22a of the peripheral part of the tube insertion hole 22, and it is difficult to get the dimensional accuracy. On the other hand, according to the second embodiment, there is no need to form the arc portion 29 of the first embodiment between the fitting protrusions 27, and the concave portion that contacts the partition portion 12 c at the end of the flat tube 12. It is only necessary to provide 28. As a result, the brazing property between the partition plate 23 and the sheet metal 18 can be further improved in the second embodiment compared to the first embodiment.
[0039]
In the second embodiment, the formation of the slit-like fitting groove 30 that communicates with the tube insertion hole 22 reduces the rigidity of the sheet metal 18 and the sheet metal 18 may be easily deformed. Instead of continuously forming the fitting groove 30 in the left-right direction of the tank (perpendicular to the air flow direction A), the slit-like fitting groove 30 is divided in the middle of the left-right direction of the tank, and the tube insertion holes 22 are separated from each other. It is preferable to form a portion that connects these parts in the air flow direction A.
[0040]
(Other embodiments)
In the above-described embodiment, the type in which the first and second passages 12a and 12b are integrally formed with a single thin metal plate as the tube 12 of the heat exchanger has been described. Of course, the passages 12a and 12b may be formed of two tubes formed independently.
[0041]
Further, in the hot water inlet / outlet tank 14, the hot water inlet pipe 20 and the hot water outlet pipe 21 are not completely arranged in a straight line, but even if the pipes 20, 21 are shifted by a minute amount, they are practically used. There is no problem.
Further, in the above-described embodiment, the case where the present invention is applied to a hot water heating heat exchanger in a vehicle air conditioner has been described. However, the present invention is not limited to this, and a heat source fluid such as hot water and an air are not used. In general, it can be widely applied to heat exchangers that perform heat exchange. For example, the present invention may be applied to a cold water type cooling heat exchanger that performs heat exchange between cold water and air.
[Brief description of the drawings]
FIG. 1 is a perspective view of a heat exchanger showing a first embodiment of the present invention.
2A is a top view of a hot water inlet / outlet tank in the heat exchanger of FIG. 1, FIG. 2B is a sectional view taken on line CC in FIG. 2A, and FIG. 2C is a sectional view taken on line DD in FIG. It is.
3 is an exploded perspective view of a main part of the heat exchanger of FIG. 1. FIG.
4 is a cross-sectional view of the assembled state of FIG. 3, showing a cross section taken along line EE of FIG.
FIG. 5 is a top view of the assembled state of FIG. 3;
6 shows a second embodiment of the present invention, and is an exploded perspective view of a main part corresponding to FIG. 3. FIG.
7 is a cross-sectional view of the assembled state of FIG. 6, showing a cross-section FF of FIG.
8 is a top view of the assembled state of FIG. 6;
FIG. 9 is a sectional view of a hot water inlet / outlet tank in a conventional heat exchanger.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11 ... Heat exchange core part, 12 ... Flat tube, 12a ... 1st channel | path,
12b ... second passage, 13 ... corrugated fin, 14 ... warm water tank
15 ... Tank for hot water U-turn, 16, 17 ... Tank body,
18, 19 ... sheet metal, 20 ... hot water inlet pipe, 21 ... hot water outlet pipe,
22 ... Tube insertion hole, 23 ... Partition plate, 23a ... Flat plate part,
23b, 23c ... 1st, 2nd bending part, 26 ... Fitting hole, 27 ... Fitting protrusion,
30: A slit-like fitting groove.

Claims (5)

熱源流体が流通するチューブ（１２）と、このチューブ（１１２）に接合されたフィン部材（１３）とからなる熱交換コア部（１１）を備え、
前記チューブ（１２）により構成される熱源流体の通路が、前記熱交換コア部（１１）への空気流れ方向（Ａ）の前後において入口側の第１通路（１２ａ）と出口側の第２通路（１２ｂ）に分割されており、
前記熱交換コア部（１１）の一端側に、前記第１通路（１２ａ）および前記第２通路（１２ｂ）への熱源流体入出用のタンク（１４）を配置するとともに、
前記熱源流体入出用タンク（１４）内に前記空気流れ方向（Ａ）と直交方向に延びる仕切り板（２３）を配置し、この仕切り板（２３）により前記熱源流体入出用タンク（１４）の内部空間を熱源流体入口空間（２４）と熱源流体出口空間（２５）とに仕切り、
前記熱源流体入出用タンク（１４）に、前記熱源流体入口空間（２４）に連通する熱源流体入口パイプ（２０）および前記熱源流体出口空間（２５）に連通する熱源流体出口パイプ（２１）を配置し、
前記熱源流体入口空間（２４）に前記第１通路（１２ａ）を連通させ、前記熱源流体出口空間（２５）に前記第２通路（１２ｂ）を連通させる熱交換器において、
前記熱源流体入口パイプ（２０）および前記熱源流体出口パイプ（２１）を前記熱源流体入出用タンク（１４）に対して前記空気流れ方向（Ａ）と直交方向に延びる略一直線上に配置し、
前記仕切り板（２３）に、前記熱源流体出口空間（２５）側へ湾曲して、前記熱源流体入口パイプ（２０）からの熱源流体を前記第１通路（１２ａ）に案内する第１湾曲部（２３ｂ）を形成するとともに、
前記仕切り板（２３）に、前記熱源流体入口空間（２４）側へ湾曲して、前記第２通路（１２ｂ）からの熱源流体を前記熱源流体出口パイプ（２１）に案内する第２湾曲部（２３ｃ）を形成したことを特徴とする熱交換器。A heat exchange core portion (11) comprising a tube (12) through which a heat source fluid flows and a fin member (13) joined to the tube (112);
The heat source fluid passage constituted by the tube (12) has a first passage (12a) on the inlet side and a second passage on the outlet side before and after the air flow direction (A) to the heat exchange core portion (11). (12b),
While disposing a tank (14) for heat source fluid in and out of the first passage (12a) and the second passage (12b) on one end side of the heat exchange core portion (11),
A partition plate (23) extending in a direction orthogonal to the air flow direction (A) is disposed in the heat source fluid input / output tank (14), and the partition plate (23) allows the inside of the heat source fluid input / output tank (14). Partition the space into a heat source fluid inlet space (24) and a heat source fluid outlet space (25);
A heat source fluid inlet pipe (20) communicating with the heat source fluid inlet space (24) and a heat source fluid outlet pipe (21) communicating with the heat source fluid outlet space (25) are disposed in the heat source fluid inlet / outlet tank (14). And
In the heat exchanger, the first passage (12a) is communicated with the heat source fluid inlet space (24), and the second passage (12b) is communicated with the heat source fluid outlet space (25).
The heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21) are arranged on a substantially straight line extending in a direction perpendicular to the air flow direction (A) with respect to the heat source fluid inlet / outlet tank (14),
A first curved portion (curved on the partition plate (23) toward the heat source fluid outlet space (25) to guide the heat source fluid from the heat source fluid inlet pipe (20) to the first passage (12a) ( 23b)
A second curved portion (curved on the partition plate (23) toward the heat source fluid inlet space (24) to guide the heat source fluid from the second passage (12b) to the heat source fluid outlet pipe (21). A heat exchanger characterized by forming 23c). 前記熱交換コア部（１１）の他端側に、前記第１通路（１２ａ）からの温水を前記第２通路（１２ｂ）へＵターンさせるＵターン用タンク（１５）を配置したことを特徴とする請求項１に記載の熱交換器。A U-turn tank (15) for U-turning hot water from the first passage (12a) to the second passage (12b) is disposed on the other end side of the heat exchange core portion (11). The heat exchanger according to claim 1. 前記熱源流体入口パイプ（２０）および前記熱源流体出口パイプ（２１）は前記熱源流体入出用タンク（１４）に対して前記空気流れ方向（Ａ）と直交方向の両端側に配置され、
前記仕切り板（２３）の前記２つの湾曲部（２３ｂ）（２３ｃ）は、前記熱源流体入口パイプ（２０）および前記熱源流体出口パイプ（２１）に対応して前記空気流れ方向（Ａ）と直交方向の両端側に配置され、
前記２つの湾曲部（２３ｂ）（２３ｃ）の間には前記熱源流体入出用タンク（１４）の中央部に位置する平板部（２３ａ）が一体に形成されていることを特徴とする請求項１または２に記載の熱交換器。The heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21) are disposed on both ends of the heat source fluid inlet / outlet tank (14) in the direction orthogonal to the air flow direction (A),
The two curved portions (23b) (23c) of the partition plate (23) are orthogonal to the air flow direction (A) corresponding to the heat source fluid inlet pipe (20) and the heat source fluid outlet pipe (21). Arranged at both ends of the direction,
The flat plate part (23a) located in the center part of the said heat source fluid inlet / outlet tank (14) is integrally formed between the said two curved parts (23b) (23c). Or the heat exchanger of 2. 前記チューブは、前記空気流れ方向（Ａ）と平行な断面偏平状の偏平チューブ（１２）であり、
また、前記熱源流体入出用タンク（１４）は、前記偏平チューブ（１２）の端部を固定するシートメタル（１８）と、前記熱源流体入口パイプ（２０）および前記熱源流体出口パイプ（２１）が配置されるタンク本体部（１６）とから構成されており、
前記シートメタル（１８）には前記偏平チューブ（１２）の端部が挿入され、接合される複数の長穴状のチューブ挿入穴（２２）が設けられており、
この複数の長穴状のチューブ挿入穴（２２）相互の間に嵌合穴（２６）が設けられており、
前記仕切り板（２３）のうち、前記シートメタル（１８）側の端部（２３ｄ）に、前記嵌合穴（２６）に嵌合される嵌合突起（２７）が設けられており、
前記嵌合穴（２６）に前記嵌合突起（２７）を嵌合した状態で、前記仕切り板（２３）を前記シートメタル（１８）に接合することを特徴とする請求項１ないし３のいずれか１つに記載の熱交換器。The tube is a flat tube (12) having a flat cross section parallel to the air flow direction (A),
The heat source fluid inlet / outlet tank (14) includes a sheet metal (18) for fixing an end of the flat tube (12), the heat source fluid inlet pipe (20), and the heat source fluid outlet pipe (21). It is composed of the tank body part (16) to be arranged,
The sheet metal (18) is provided with a plurality of elongated tube insertion holes (22) into which the ends of the flat tubes (12) are inserted and joined,
A fitting hole (26) is provided between the plurality of elongated hole-like tube insertion holes (22),
Of the partition plate (23), a fitting projection (27) fitted into the fitting hole (26) is provided at an end (23d) on the sheet metal (18) side,
The partition plate (23) is joined to the sheet metal (18) in a state in which the fitting protrusion (27) is fitted in the fitting hole (26). The heat exchanger as described in any one. 前記チューブは、前記空気流れ方向（Ａ）と平行な断面偏平状の偏平チューブ（１２）であり、
また、前記熱源流体入出用タンク（１４）は、前記偏平チューブ（１２）の端部を固定するシートメタル（１８）と、前記熱源流体入口パイプ（２０）および前記熱源流体出口パイプ（２１）が配置されるタンク本体部（１６）とから構成されており、
前記シートメタル（１８）には前記偏平チューブ（１２）の端部が挿入され、接合される複数の長穴状のチューブ挿入穴（２２）が設けられており、
この複数の長穴状のチューブ挿入穴（２２）相互の間に、このチューブ挿入穴（２２）と連通するスリット状嵌合溝（３０）が設けられており、
前記仕切り板（２３）のうち、前記シートメタル（１８）側の端部（２３ｄ）に、前記スリット状嵌合溝（３０）に嵌合される嵌合突起（２７）が設けられており、
前記スリット状嵌合溝（３０）に前記嵌合突起（２７）を嵌合した状態で、前記仕切り板（２３）を前記シートメタル（１８）に接合することを特徴とする請求項１ないし３のいずれか１つに記載の熱交換器。The tube is a flat tube (12) having a flat cross section parallel to the air flow direction (A),
The heat source fluid inlet / outlet tank (14) includes a sheet metal (18) for fixing an end of the flat tube (12), the heat source fluid inlet pipe (20), and the heat source fluid outlet pipe (21). It is composed of the tank body part (16) to be arranged,
The sheet metal (18) is provided with a plurality of elongated tube insertion holes (22) into which the ends of the flat tubes (12) are inserted and joined,
A slit-like fitting groove (30) communicating with the tube insertion hole (22) is provided between the plurality of elongated hole-like tube insertion holes (22).
In the partition plate (23), an end (23d) on the sheet metal (18) side is provided with a fitting protrusion (27) fitted into the slit-like fitting groove (30),
The said partition plate (23) is joined to the said sheet metal (18) in the state which fitted the said fitting protrusion (27) in the said slit-shaped fitting groove (30). The heat exchanger as described in any one of these.
JP27608498A 1998-09-29 1998-09-29 Heat exchanger Expired - Fee Related JP3829499B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101497347B1 (en) * 2007-06-05 2015-03-04 한라비스테온공조 주식회사 Heat exchanger

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001031278A1 (en) * 1999-10-28 2001-05-03 Siemens Westinghouse Power Corporation Heat exchanger
KR20040005902A (en) * 2001-03-29 2004-01-16 쇼와 덴코 가부시키가이샤 Header for use in heat exchangers, heat exchanger and method for manufacturing the same
DE102004003789A1 (en) * 2004-01-23 2005-08-18 Behr Gmbh & Co. Kg heat exchangers
DE102004027402A1 (en) * 2004-06-04 2005-12-22 Behr Gmbh & Co. Kg heat exchangers
EP1731864A1 (en) * 2005-06-11 2006-12-13 Modine Manufacturing Company Metallic heat exchanger and method for manufacturing the same
KR100957665B1 (en) * 2005-06-11 2010-05-12 모다인 매뉴팩츄어링 컴파니 Fully-Metal Heat Exchanger and Method for its Production
JP4731212B2 (en) * 2005-06-16 2011-07-20 株式会社日本クライメイトシステムズ Heat exchanger
KR100831876B1 (en) * 2006-08-22 2008-05-22 모딘코리아 유한회사 Header tank and heat exchanger including the same
JP4850634B2 (en) * 2006-09-01 2012-01-11 株式会社ティラド Heat exchanger
DE102008029958A1 (en) * 2008-06-26 2009-12-31 Behr Gmbh & Co. Kg Heat exchanger for a motor vehicle
DE102009021180A1 (en) 2009-05-13 2010-11-18 Behr Gmbh & Co. Kg Heat exchanger for use as heating device in motor vehicle air conditioning system, has inlet and outlet connecting pieces, where inlet axis of inlet piece and/or outlet axis of outlet piece are aligned to area level at specific angle
DE102009043689A1 (en) 2009-10-01 2011-04-07 Behr Gmbh & Co. Kg Heat exchanger
AU2011201083B2 (en) 2010-03-18 2013-12-05 Modine Manufacturing Company Heat exchanger and method of manufacturing the same
US9309839B2 (en) 2010-03-18 2016-04-12 Modine Manufacturing Company Heat exchanger and method of manufacturing the same
DE102010053478B4 (en) * 2010-12-04 2018-05-30 Modine Manufacturing Co. Heat exchanger and production process for heat exchangers
DE102012200516A1 (en) * 2012-01-13 2013-07-18 Behr Gmbh & Co. Kg Heat exchanger for motor car, has tube sheet whose adjacent regions are stepped between two pipes at different levels
GB2521574B (en) * 2012-10-10 2019-01-16 Trane Int Inc A header for an evaporator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08254399A (en) * 1995-01-19 1996-10-01 Zexel Corp Heat exchanger
JPH08240395A (en) * 1995-03-06 1996-09-17 Zexel Corp Heat exchanger
JPH09250895A (en) * 1996-03-14 1997-09-22 Zexel Corp Heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101497347B1 (en) * 2007-06-05 2015-03-04 한라비스테온공조 주식회사 Heat exchanger

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