JP4031393B2 - EGR cooler - Google Patents

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Publication number
JP4031393B2
JP4031393B2 JP2003148184A JP2003148184A JP4031393B2 JP 4031393 B2 JP4031393 B2 JP 4031393B2 JP 2003148184 A JP2003148184 A JP 2003148184A JP 2003148184 A JP2003148184 A JP 2003148184A JP 4031393 B2 JP4031393 B2 JP 4031393B2
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egr gas
egr
pipe
tube
rectifying
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JP2004346919A (en
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信昭 吉田
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UD Trucks Corp
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UD Trucks Corp
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    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape

Description

【０００１】
【発明の属する技術分野】
本発明は、ディーゼルエンジンのＥＧＲ装置に用いるＥＧＲクーラーに関する。
【０００２】
【従来の技術】
ディーゼルエンジン（以下、「エンジン」という）の燃焼時に発生する窒素酸化物（ＮＯX ）を低減するため、従来、排ガスの一部をエンジンの吸気系に排気還流（以下、「ＥＧＲ」という）させるＥＧＲ装置が知られている。
窒素酸化物は、高温の排ガスのもとで空気中の酸素と窒素が反応して生成されるため、ＥＧＲ装置は、ＥＧＲによって燃焼温度を下げることでＯ2＋Ｎ2→２ＮＯの反応を抑制して窒素酸化物の排出を低減させるものである。
【０００３】
そして、吸気系にＥＧＲさせるＥＧＲガスの温度を下げるほど、燃焼時のスモークの悪化を抑え、窒素酸化物の発生が減少することが知られている。
そこで、昨今では、エンジンの吸気系と排気系との間に接続したＥＧＲパイプに、エンジン冷却水等を冷媒とするＥＧＲクーラーを装着し、ＥＧＲパイプを流下するＥＧＲガスをこのＥＧＲクーラーで熱交換させてＥＧＲガス温度を下げる方法が広く採用されている（例えば、下記の特許文献１，２参照。）。
【０００４】
図９乃至図１１は特許文献２に開示されたＥＧＲクーラーを示し、このＥＧＲクーラー１は、筒状に成形されたシェル３内に、その長手方向に沿って複数の均一内径のチューブ５を収容し、シェル３のＥＧＲガス上流側端部とＥＧＲガス下流側端部に取り付くディフューザ７，９に、夫々、ＥＧＲガス導入パイプ（ＥＧＲパイプ）１１とＥＧＲガス導出パイプ（ＥＧＲパイプ）１３を接続すると共に、ＥＧＲガス導入パイプ１１側のシェル３の周壁に冷却水導入パイプ１５を接続し、また、ＥＧＲガス導出パイプ１３側のシェル３の周壁に冷却水導出パイプ１７を接続したもので、チューブ５は、夫々、シェル３の両端部に取り付くエンドプレート１９に挿着されて両ディフューザ７，９内に開口している。
【０００５】
そして、シェル３の中央には、断面円形形状の冷却水誘導部材２１がシェル３の長手方向に沿ってエンドプレート１９間に装着されており、図１１に示すようにシェル３内に導入された冷却水Ｗが、この冷却水誘導部材２１により渦流や旋回流となってシェル３の中心部から外周方向へ誘導されるようになっている。
而して、斯かる構造によって、シェル３内には、冷却水導入パイプ１５から冷却水導出パイプ１７に至る冷却水流路が形成されると共に、ＥＧＲガス導入パイプ１１からチューブ５を経てＥＧＲガス導出パイプ１３に至るＥＧＲガス流路が形成されており、ＥＧＲクーラー１内に導入されたＥＧＲガスＧがチューブ５内を流下する際に、シェル３内に導入された冷却水Ｗで熱交換されてＥＧＲガス温度が下がるようになっている。
【０００６】
【特許文献１】
特開２００３−７４４１７号公報（段落番号「００１０」〜「００３０」、図１）
【特許文献２】
特開２００３−８３１７４号公報（段落番号「００１８」〜「００２２」、図３）
【０００７】
【発明が解決しようとする課題】
ところで、ＥＧＲされたＥＧＲガスＧはある程度の流速を有しているため、ＥＧＲクーラー１内に導入されたＥＧＲガスＧがディフューザ７内で拡散せずにそのまま直進して、ＥＧＲガスＧの多くがシェル３の中心部に配置されたチューブ５内を流下しているのが実情であった。
【０００８】
しかし、斯様にシェル３の中心部のチューブ５に多くのＥＧＲガスＧが集中して流下すると、周辺部に配置されたチューブ５による熱交換がなされないために所期の冷却効率を確保することができず、また、斯様に中心部のチューブ５に多くのＥＧＲガスＧが集中して流下すると、これらのチューブ５に早期目詰まりが発生して冷却効率が更に悪化してしまう虞も指摘されていた。
【０００９】
本発明は斯かる実情に鑑み案出されたもので、シェル内に収容したチューブ内にＥＧＲガスを均等に流下させることで、冷却効率の向上を図ったＥＧＲ装置のＥＧＲクーラーを提供することを目的とする。
【００１０】
【課題を解決するための手段】
斯かる目的を達成するため、請求項１に係る発明は、周壁に冷却水導入パイプと冷却水導出パイプが接続された筒状のシェルの両端部に、ディフューザを介してＥＧＲガス導入パイプとＥＧＲガス導出パイプを接続し、シェルの両端部を閉塞するエンドプレート間に、ディフューザ内に開口する複数のチューブを挿着したＥＧＲ装置のＥＧＲクーラーに於て、上記各チューブのＥＧＲガス上流側端部と、ＥＧＲガス導入パイプが接続されたディフューザのＥＧＲガス導入口との間に複数の整流管を配置し、当該各整流管を介してＥＧＲガスを各チューブに導くと共に、各整流管のＥＧＲガス上流側端部を断面六角形状に成形し、これらをハニカム状に集合，接合させて上記ＥＧＲガス導入口の内周に一体的に接合し、上記チューブの外周に冷却フィンを設けたことを特徴とする。
【００１１】
そして、請求項２に係る発明は、周壁に冷却水導入パイプと冷却水導出パイプが接続された筒状のシェルの両端部に、ディフューザを介してＥＧＲガス導入パイプとＥＧＲガス導出パイプを接続し、シェルの両端部を閉塞するエンドプレート間に、ディフューザ内に開口する複数のチューブを挿着したＥＧＲ装置のＥＧＲクーラーに於て、上記各チューブのＥＧＲガス上流側端部と、ＥＧＲガス導入パイプが接続されたディフューザのＥＧＲガス導入口との間に複数の整流管を配置し、当該各整流管を介してＥＧＲガスを各チューブに導くと共に、各整流管の流路面積を、ＥＧＲガス上流側端部からＥＧＲガス下流側端部へ順次拡大させて、上記チューブの外周に冷却フィンを設けたことを特徴とする。
【００１２】
（作用）
各請求項に係るＥＧＲクーラーによれば、シェル内に収容されたＥＧＲガスがチューブ内を流下する際に、シェル内に導入された冷却水で熱交換されてＥＧＲガス温度が下げられるが、ＥＧＲガスは、各整流管を介してＥＧＲガス導入パイプから各チューブに均等に導かれることとなる。
そして、チューブを流下するＥＧＲガスの熱は、冷却フィンを介して冷却水に伝達されて熱交換される。
また、請求項１に係る発明は、断面六角形状に成形した各整流管のＥＧＲガス上流側端部をハニカム状に集合させて、これらをＥＧＲガス導入口の内周に一体的に接合した構造上、各整流管とディフューザのＥＧＲガス導入口との間に無駄な隙間が生じることがなく、また、斯様にハニカム状に集合，接合することで整流管の強度が向上する。
【００１３】
そして、請求項２に係る発明は、各整流管の流路面積を、ＥＧＲガス上流側端部からＥＧＲガス下流側端部へ順次拡大させたため、整流管内を流下するＥＧＲガスの流速が、ベルヌーイの定理によってＥＧＲガス下流側端部へと次第に遅くなる。
この結果、整流管のない従来構造に比し、チューブ内を流下するＥＧＲガスの流速が遅くなって、冷却水との熱交換時間が長くなる。
【００１４】
【発明の実施の形態】
以下、本発明の実施形態を図面に基づいて詳細に説明する。
【００１５】
図１乃至図４は請求項１及び請求項２に係るＥＧＲクーラーの一実施形態を示し、図１に於て、２３は円筒状に成形されたシェルで、そのＥＧＲガス上流側端部とＥＧＲガス下流側端部に取り付くディフューザ２５，２７に、夫々、ＥＧＲガス導入パイプ（ＥＧＲパイプ）２９とＥＧＲガス導出パイプ（ＥＧＲパイプ）３１が接続されている。
【００１６】
そして、図２及び図３に示すようにシェル２３内には、その長手方向に沿って複数の均一内径の円筒状のチューブ３３が収容されており、各チューブ３３は、シェル２３の両端部に取り付くエンドプレート３５，３７に挿着されて両ディフューザ２５，２７内に開口している。
また、各チューブ３３のＥＧＲガス上流側外周とＥＧＲガス下流側外周には、夫々、伝熱面積を拡大して冷却水Ｗとの冷却効率を高めるために複数の側面視矩形状の薄肉で長尺な冷却フィン３９が、周方向に夫々４５°の間隔を空けてチューブ３３の長手方向に突設されている。
【００１７】
更にまた、図１乃至図３に示すようにＥＧＲガス導出パイプ３１側のシェル２３の底部周壁には、冷却水導入パイプ４１がシェル２３の中心方向に向かって接続されると共に、ＥＧＲガス導入パイプ２９側のシェル２３の上部周壁に、冷却水導出パイプ４３がシェル２３の中心方向に向かって接続されており、冷却水導入パイプ４１と冷却水導出パイプ４３は１８０°の間隔を以って配置されている。
【００１８】
而して、上述の如き構成によって、本実施形態に係るＥＧＲクーラー４５も、シェル２３内に冷却水導入パイプ４１から冷却水導出パイプ４３に至る冷却水流路が形成されると共に、ＥＧＲガス導入パイプ２９からチューブ３３を経てＥＧＲガス導出パイプ３１に至るＥＧＲガス流路が形成されているが、本実施形態は上述の如き従来と同様の構成に加え、図２及び図４に示すようにディフューザ２５内に開口する各チューブ３３のＥＧＲガス上流側端部４７と、ＥＧＲガス導入パイプ２９が接続されたディフューザ２５のＥＧＲガス導入口４９との間に複数の整流管５１を接続したことを特徴とする。
【００１９】
即ち、図３に示すように本実施形態では、シェル２３の中心部に１本のチューブ３３が配置されると共に、当該チューブ３３を中心に６本のチューブ３３が６０°の間隔を空けて放射状に配置されているが、図２に示すように各チューブ３３のＥＧＲガス上流側端部４７に、整流管５１の断面円形形状に成形されたＥＧＲガス下流側端部５３が接続されている。
【００２０】
一方、図４に示すように整流管５１のＥＧＲガス上流側端部５５は、既述したチューブ３３の配列に対応して配置されているが、断面円形形状に成形されたディフューザ２５のＥＧＲガス導入口４９との間に無駄な隙間が生じることを避けるために断面六角形状に成形され、これらがハニカム状に集合，接合してＥＧＲガス導入口４９の内周に一体的に接合されている。
【００２１】
そして、上述の如く整流管５１のＥＧＲガス上流側端部５５はハニカム状に集合，接合しているが、図２に示すように整流管５１のＥＧＲガス下流側端部５３側は、互いに徐々に離間し乍ら、夫々、対応するチューブ３３に向かって延設されている。そして、各流管５１は、ＥＧＲガス上流側端部５５からＥＧＲガス下流側端部５３へ流路面積が順次拡大するように設けられており、各整流管５１を介してＥＧＲガスＧが各チューブ３３に均等に導かれるようになっている。
【００２２】
その他、図４中、５７は整流管５１のＥＧＲガス上流側端部５５の外周とディフューザ２５のＥＧＲガス導入口４９の内周との隙間を閉塞する薄肉な閉塞部材で、当該閉塞部材５７は整流管５１とディフューザ２５との間に溶接されている。
本実施形態はこのように構成されているから、図示しないエンジンの排気系からＥＧＲされてＥＧＲクーラー４５内に導入されたＥＧＲガスＧは、チューブ３３内を流下する際に、シェル２３内に導入された冷却水Ｗで熱交換されてＥＧＲガス温度が下げられるが、ＥＧＲガスＧは、各整流管５１を介してＥＧＲガス導入パイプ２９から各チューブ３３に均等に導かれ、そして、ＥＧＲガスＧの熱は、複数の冷却フィン３９を介して冷却水Ｗに伝達されて熱交換されることとなる。
また、各整流管５１の流路面積が、ＥＧＲガス上流側端部５５からＥＧＲガス下流側端部５３へ順次拡大しているため、整流管５１内を流下するＥＧＲガスＧの流速が、ベルヌーイの定理によってＥＧＲガス下流側端部５３へと次第に遅くなる。
この結果、整流管５１のない従来構造に比し、チューブ３３内を流下するＥＧＲガスＧの流速が遅くなって、冷却水Ｗとの熱交換時間が長くなる。
そして、各整流管５１のＥＧＲガス上流側端部５５を断面六角形状に成形し、これらをハニカム状に集合，接合させてディフューザ２５のＥＧＲガス導入口４９の内周に一体的に接合したため、各整流管５１とＥＧＲガス導入口４９との間に無駄な隙間が生じることがなく、また、斯様にハニカム状に集合，接合することで整流管５１の強度が向上する。
【００２３】
このように本実施形態によれば、ＥＧＲガスＧがシェル２３の中心部に位置するチューブ３３のみならず、その周辺部に位置するチューブ３３内を均等に流下するため、図９の従来例に比しＥＧＲクーラー４５本来の所期の冷却効率を得ることができると共に、中心部に位置するチューブ３３の早期目詰まりを防止することができることとなった。
【００２４】
而も、上記整流管５１は、現行のＥＧＲクーラーにも取付けが容易であるため、既販のエンジンについても対応可能である。
また、既述したように本実施形態は、各整流管５１の流路面積をＥＧＲガス上流側端部５５からＥＧＲガス下流側端部５３へ順次拡大させたため、整流管５１内を流下するＥＧＲガスＧの流速が、ベルヌーイの定理によってＥＧＲガス下流側端部５３へと次第に遅くなり、この結果、整流管５１のない従来構造に比し、チューブ３３内を流下するＥＧＲガスＧの流速が遅くなって冷却水Ｗとの熱交換時間が長くなる。このようにＥＧＲガスＧと冷却水Ｗとの熱交換時間が長くなることで、本実施形態によれば、熱交換効率が上がって冷却効率が向上することとなった。
更にまた、本実施形態は、各整流管５１のＥＧＲガス上流側端部５５を断面六角形状に成形し、これらをハニカム状に集合，接合させてディフューザ２５のＥＧＲガス導入口４９の内周に一体的に接合したため、各整流管５１とＥＧＲガス導入口４９との間に無駄な隙間が生じることがなくなると共に、斯様にハニカム状に集合，接合することで整流管５１の強度が向上する利点を有する。
加えて、本実施形態は、各チューブ３３の外周に冷却フィン３９を設けて伝熱面積を拡大したため、冷却水Ｗとの冷却効率が更に向上し、この結果、ＥＧＲガス温度が低下することにより、ＥＧＲガス下流側の配管やガスケット等の材質についても耐熱性の低い材料が使用可能となり、また、ＥＧＲガス温度の低下によって材料各部の耐久性が向上する優れた利点を有する。
【００２５】
そして、冷却フィン３９の高さを変えて伝熱面積を調節することで、ＥＧＲクーラーの様々な仕様に対応することが可能である。
尚、チューブの外周に設ける冷却フィンの形状は、既述した実施形態に限定されるものではなく、例えば図５乃至図８に示すように様々な形態が選択可能である。
【００２６】
図５に示す実施形態は、チューブ３３の外周に所謂鉢巻き形状の冷却フィン３９-1を所定間隔を空けてチューブ３３の外周に複数突設したものであり、図６に示す実施形態は、側面視翼形状の冷却フィン３９-2を、所定間隔を空けて複数突設したものである。
また、図７に示す実施形態は、チューブ３３の外周に冷却フィン３９-3を螺旋状に突設したものであり、図８に示す実施形態は、チューブ３３の外周にブレード形状の冷却フィン３９-4を所定間隔を空けて複数突設したもので、既述した冷却フィン３９と同様、ＥＧＲクーラーの仕様に応じ各冷却フィン３９-1〜３９-4の高さを自由に変更すればよい。
【００２７】
而して、これらの冷却フィンフィン３９-1〜３９-4を用いたＥＧＲクーラーによっても、図１のＥＧＲクーラー４５と同様、冷却水Ｗとの冷却効率が向上するため、所期の目的を達成することが可能である。
更に、既述した整流管５１は、チューブに応じその本数を適宜変更可能である。
【００２８】
【発明の効果】
以上述べたように、各請求項に係る発明によれば、整流管に案内されてＥＧＲガスがシェル内のチューブ内を均等に流下するため、従来に比しＥＧＲクーラー本来の所期の冷却効率を得ることができると共に、シェルの中心部に位置するチューブの早期目詰まりを防止することが可能となった。
【００２９】
そして、整流管は現行のＥＧＲクーラーにも取付けが容易であるため、既販のエンジンについても対応可能である。
また、チューブの外周に冷却フィンを設けて伝熱面積を拡大したため、冷却水との冷却効率が更に向上し、この結果、ＥＧＲガス温度が低下することにより、ＥＧＲガス下流側の配管やガスケット等の材質についても耐熱性の低い材料が使用可能となると共に、ＥＧＲガス温度の低下によって材料各部の耐久性が向上する優れた利点を有する。
そして、冷却フィンの高さを変えて伝熱面積を調節することで、ＥＧＲクーラーの様々な仕様に対応することが可能である。
更に、請求項１に係る発明は、各整流管のＥＧＲガス上流側端部を断面六角形状に成形し、これらをハニカム状に集合，接合させてディフューザのＥＧＲガス導入口の内周に一体的に接合したため、各整流管とＥＧＲガス導入口との間に無駄な隙間が生じることがなくなると共に、斯様にハニカム状に集合，接合することで整流管の強度が向上する利点を有する。
【００３０】
また、請求項２に係る発明は、各整流管の流路面積をＥＧＲガス上流側端部からＥＧＲガス下流側端部へ順次拡大させたため、整流管内を流下するＥＧＲガスの流速が、ベルヌーイの定理によってＥＧＲガス下流側端部へと次第に遅くなり、この結果、整流管のない従来構造に比し、チューブ内を流下するＥＧＲガスの流速が遅くなって冷却水との熱交換時間が長くなる。そして、このようにＥＧＲガスと冷却水との熱交換時間が長くなることで、熱交換効率が上がって冷却効率が向上する利点を有する。
【図面の簡単な説明】
【図１】請求項１及び請求項２の一実施形態に係るＥＧＲクーラーの全体斜視図である。
【図２】図１のII−II線断面図である。
【図３】図２のIII−III線断面図である。
【図４】図２のIV−IV線断面図である。
【図５】冷却フィンの変形例を示すチューブの側面図である。
【図６】冷却フィンの変形例を示すチューブの側面図である。
【図７】冷却フィンの変形例を示すチューブの側面図である。
【図８】冷却フィンの変形例を示すチューブの側面図である。
【図９】従来のＥＧＲクーラーの全体斜視図である。
【図１０】図９のＸ−Ｘ線断面図である。
【図１１】図９のXI−XI線断面図である。
【符号の説明】
２３ シェル
２５，２７ ディフューザ
２９ ＥＧＲガス導入パイプ
３１ ＥＧＲガス導出パイプ
３３ チューブ
３５，３７ エンドプレート
３９，３９-1，３９-2，３９-3，３９-4 冷却フィン
４１ 冷却水導入パイプ
４３ 冷却水導出パイプ
４５ ＥＧＲクーラー
４７ チューブのＥＧＲガス上流側端部
４９ ディフューザのＥＧＲガス導入口
５１ 整流管
５３ 整流管のＥＧＲガス下流側端部
５５ 整流管のＥＧＲガス上流側端部
Ｇ ＥＧＲガス
Ｗ 冷却水[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an EGR cooler used for an EGR device of a diesel engine.
[0002]
[Prior art]
In order to reduce nitrogen oxide (NO x ) generated during combustion of a diesel engine (hereinafter referred to as “engine”), conventionally, a part of the exhaust gas is exhausted to the engine intake system (hereinafter referred to as “EGR”). EGR devices are known.
Since nitrogen oxides are produced by the reaction of oxygen and nitrogen in the air under high temperature exhaust gas, the EGR device suppresses the reaction of O 2 + N 2 → 2NO by lowering the combustion temperature with EGR. This reduces nitrogen oxide emissions.
[0003]
It is known that as the temperature of the EGR gas to be EGRed into the intake system is lowered, the deterioration of smoke during combustion is suppressed and the generation of nitrogen oxides is reduced.
Therefore, nowadays, an EGR cooler that uses engine coolant or the like as a refrigerant is attached to the EGR pipe connected between the intake system and the exhaust system of the engine, and the EGR gas flowing down the EGR pipe exchanges heat with this EGR cooler. The method of lowering the EGR gas temperature is widely adopted (see, for example, Patent Documents 1 and 2 below).
[0004]
9 to 11 show an EGR cooler disclosed in Patent Document 2. This EGR cooler 1 accommodates a plurality of tubes 5 having a uniform inner diameter along the longitudinal direction in a cylindrical shell 3. Then, an EGR gas introduction pipe (EGR pipe) 11 and an EGR gas outlet pipe (EGR pipe) 13 are connected to the diffusers 7 and 9 attached to the EGR gas upstream end and the EGR gas downstream end of the shell 3, respectively. At the same time, a cooling water introduction pipe 15 is connected to the peripheral wall of the shell 3 on the EGR gas introduction pipe 11 side, and a cooling water outlet pipe 17 is connected to the peripheral wall of the shell 3 on the EGR gas outlet pipe 13 side. Are inserted into end plates 19 that are attached to both ends of the shell 3, and are opened in the diffusers 7 and 9.
[0005]
A cooling water guiding member 21 having a circular cross section is mounted between the end plates 19 along the longitudinal direction of the shell 3 at the center of the shell 3 and introduced into the shell 3 as shown in FIG. The cooling water W is guided as a vortex or swirl by the cooling water guiding member 21 from the center of the shell 3 toward the outer periphery.
Thus, with this structure, a cooling water flow path from the cooling water introduction pipe 15 to the cooling water extraction pipe 17 is formed in the shell 3, and the EGR gas is extracted from the EGR gas introduction pipe 11 through the tube 5. An EGR gas flow path leading to the pipe 13 is formed, and when the EGR gas G introduced into the EGR cooler 1 flows down through the tube 5, heat is exchanged with the cooling water W introduced into the shell 3. The EGR gas temperature is lowered.
[0006]
[Patent Document 1]
Japanese Unexamined Patent Publication No. 2003-74417 (paragraph numbers “0010” to “0030”, FIG. 1)
[Patent Document 2]
JP 2003-83174 A (paragraph numbers “0018” to “0022”, FIG. 3)
[0007]
[Problems to be solved by the invention]
By the way, since the EGR gas G subjected to EGR has a certain flow velocity, the EGR gas G introduced into the EGR cooler 1 goes straight without being diffused in the diffuser 7, and most of the EGR gas G The actual situation was flowing down through the tube 5 arranged at the center of the shell 3.
[0008]
However, when a large amount of EGR gas G flows down to the tube 5 at the center of the shell 3 in this way, heat exchange is not performed by the tube 5 disposed in the peripheral portion, so that the expected cooling efficiency is ensured. In addition, when a large amount of EGR gas G flows down in the central tube 5 in this way, there is a risk that these tubes 5 will be clogged early and cooling efficiency will be further deteriorated. It was pointed out.
[0009]
The present invention has been made in view of the foregoing circumstances, by uniformly flow down the EGR gas into the tube accommodated in the shell, to provide an EGR cooler EGR apparatus with improved cooling efficiency and purpose.
[0010]
[Means for Solving the Problems]
In order to achieve such an object, the invention according to claim 1 is directed to an EGR gas introduction pipe and an EGR through a diffuser at both ends of a cylindrical shell having a cooling water introduction pipe and a cooling water outlet pipe connected to a peripheral wall. In an EGR cooler of an EGR apparatus in which a plurality of tubes opened in a diffuser are inserted between end plates that connect gas outlet pipes and close both ends of the shell, upstream ends of the EGR gases of the tubes And a plurality of rectifying pipes are arranged between the EGR gas inlets of the diffuser connected to the EGR gas introducing pipes, and the EGR gas is guided to the respective tubes through the rectifying pipes. The upstream end is formed into a hexagonal cross section, these are assembled and joined in a honeycomb shape, and integrally joined to the inner periphery of the EGR gas inlet, and the tube is cooled to the outer periphery of the tube. Characterized in that a fin.
[0011]
In the invention according to claim 2, the EGR gas inlet pipe and the EGR gas outlet pipe are connected via a diffuser to both ends of a cylindrical shell having a cooling wall inlet pipe and a cooling water outlet pipe connected to the peripheral wall. In the EGR cooler of the EGR apparatus in which a plurality of tubes opened in the diffuser are inserted between the end plates that close both ends of the shell, the EGR gas upstream end of each tube and the EGR gas introduction pipe A plurality of rectifying pipes are arranged between the EGR gas inlets of the diffuser connected to the EGR gas, the EGR gas is guided to the respective tubes through the rectifying pipes, and the flow passage area of each rectifying pipe is set to the upstream of the EGR gas A cooling fin is provided on the outer periphery of the tube, which is sequentially enlarged from the side end portion to the EGR gas downstream end portion .
[0012]
(Function)
According to the EGR cooler according to each claim, when the EGR gas accommodated in the shell flows down in the tube, the EGR gas temperature is lowered by the heat exchange with the cooling water introduced into the shell. The gas is evenly guided to each tube from the EGR gas introduction pipe via each rectifying tube.
And the heat | fever of EGR gas which flows down a tube is transmitted to cooling water via a cooling fin, and is heat-exchanged.
The invention according to claim 1 is a structure in which the upstream end portions of the EGR gas upstream of each rectifying pipe formed in a hexagonal cross section are assembled in a honeycomb shape and are integrally joined to the inner periphery of the EGR gas inlet. In addition, there is no useless gap between each rectifier tube and the EGR gas inlet of the diffuser, and the strength of the rectifier tube is improved by gathering and joining in a honeycomb shape.
[0013]
In the invention according to claim 2, since the flow passage area of each rectifying pipe is sequentially expanded from the EGR gas upstream end to the EGR gas downstream end, the flow rate of the EGR gas flowing down the rectifying pipe is Bernoulli. According to the theorem, the EGR gas downstream end is gradually delayed.
As a result, the flow rate of the EGR gas flowing down in the tube is slower and the heat exchange time with the cooling water is longer than in a conventional structure without a rectifying tube.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
[0015]
1 to 4 show an embodiment of an EGR cooler according to claims 1 and 2, in which reference numeral 23 denotes a shell formed in a cylindrical shape, its EGR gas upstream end and EGR. An EGR gas introduction pipe (EGR pipe) 29 and an EGR gas outlet pipe (EGR pipe) 31 are connected to the diffusers 25 and 27 attached to the gas downstream side end portions, respectively.
[0016]
As shown in FIGS. 2 and 3, a plurality of cylindrical tubes 33 having a uniform inner diameter are accommodated in the shell 23 along the longitudinal direction, and each tube 33 is disposed at both ends of the shell 23. It is inserted into the end plates 35 and 37 to be attached, and opens in the diffusers 25 and 27.
Also, the EGR gas upstream outer periphery and the EGR gas downstream outer periphery of each tube 33 are long and thin with a plurality of rectangular shapes in side view in order to increase the heat transfer area and increase the cooling efficiency with the cooling water W, respectively. The small cooling fins 39 project in the longitudinal direction of the tube 33 with an interval of 45 ° in the circumferential direction.
[0017]
Furthermore, as shown in FIGS. 1 to 3, a cooling water introduction pipe 41 is connected to the bottom peripheral wall of the shell 23 on the EGR gas outlet pipe 31 side toward the center of the shell 23, and the EGR gas introduction pipe The cooling water outlet pipe 43 is connected to the upper peripheral wall of the shell 23 on the 29th side toward the center of the shell 23, and the cooling water inlet pipe 41 and the cooling water outlet pipe 43 are arranged at an interval of 180 °. Has been.
[0018]
Thus, in the EGR cooler 45 according to this embodiment, the cooling water flow path from the cooling water introduction pipe 41 to the cooling water outlet pipe 43 is formed in the shell 23 and the EGR gas introduction pipe is configured as described above. Although EGR gas passage leading to the EGR gas lead pipe 31 from 29 through tube 33 is formed, the present embodiment in addition to the same manner as described above, such as the conventional configuration, the diffuser 25 as shown in FIGS. 2 and 4 A plurality of rectifying pipes 51 are connected between an EGR gas upstream side end portion 47 of each tube 33 opened inside and an EGR gas introduction port 49 of a diffuser 25 to which an EGR gas introduction pipe 29 is connected. To do.
[0019]
That is, as shown in FIG. 3, in this embodiment, one tube 33 is arranged at the center of the shell 23, and six tubes 33 centering on the tube 33 are spaced radially by 60 °. However, as shown in FIG. 2, the EGR gas downstream end portion 53 formed in a circular cross section of the rectifying pipe 51 is connected to the EGR gas upstream end portion 47 of each tube 33.
[0020]
On the other hand, as shown in FIG. 4, the EGR gas upstream end portion 55 of the rectifying pipe 51 is arranged corresponding to the arrangement of the tubes 33 described above, but the EGR gas of the diffuser 25 formed in a circular cross section. In order to avoid useless gaps between the inlet 49 and the inlet 49, it is formed into a hexagonal cross section, and these are assembled and joined in a honeycomb shape and integrally joined to the inner periphery of the EGR gas inlet 49. .
[0021]
As described above, the EGR gas upstream end portion 55 of the rectifying pipe 51 is gathered and joined in a honeycomb shape, but the EGR gas downstream end portion 53 side of the rectifying pipe 51 is gradually joined to each other as shown in FIG. spaced乍Ra in, respectively, are extended toward the corresponding tube 3 3. And each flow pipe 51 is provided so that a flow path area may be sequentially expanded from the EGR gas upstream side end portion 55 to the EGR gas downstream side end portion 53, and the EGR gas G is passed through each rectifying pipe 51. The tube 33 is guided evenly.
[0022]
In addition, in FIG. 4, 57 is a thin blocking member that closes the gap between the outer periphery of the EGR gas upstream end 55 of the rectifying pipe 51 and the inner periphery of the EGR gas inlet 49 of the diffuser 25. It is welded between the rectifying pipe 51 and the diffuser 25.
Since the present embodiment is configured as described above, the EGR gas G that has been EGRed from an exhaust system of an engine (not shown) and introduced into the EGR cooler 45 is introduced into the shell 23 when flowing down through the tube 33. The EGR gas temperature is lowered by the heat exchange with the cooled cooling water W, but the EGR gas G is evenly guided from the EGR gas introduction pipe 29 to each tube 33 through the respective rectifying pipes 51, and the EGR gas G The heat is transferred to the cooling water W through the plurality of cooling fins 39 and heat exchange is performed.
In addition, since the flow passage area of each rectifying pipe 51 gradually increases from the EGR gas upstream end 55 to the EGR gas downstream end 53, the flow rate of the EGR gas G flowing through the rectifying pipe 51 is Bernoulli. According to the theorem, the EGR gas downstream end portion 53 gradually becomes slower.
As a result, the flow rate of the EGR gas G flowing down in the tube 33 becomes slower and the heat exchange time with the cooling water W becomes longer than in the conventional structure without the rectifying pipe 51.
And since the EGR gas upstream side end portion 55 of each rectifying pipe 51 is formed into a hexagonal cross section, these are assembled and joined in a honeycomb shape and integrally joined to the inner periphery of the EGR gas inlet 49 of the diffuser 25. There is no useless gap between each rectifying pipe 51 and the EGR gas inlet 49, and the strength of the rectifying pipe 51 is improved by gathering and joining in a honeycomb shape.
[0023]
As described above, according to the present embodiment, the EGR gas G flows down uniformly not only in the tube 33 located in the center portion of the shell 23 but also in the tube 33 located in the peripheral portion thereof. In contrast, the original expected cooling efficiency of the EGR cooler 45 can be obtained, and early clogging of the tube 33 located in the center can be prevented.
[0024]
In addition, the rectifying pipe 51 can be easily attached to an existing EGR cooler, and can be applied to an already-sold engine.
In addition, as described above, in the present embodiment, the flow passage area of each rectifying pipe 51 is sequentially expanded from the EGR gas upstream end 55 to the EGR gas downstream end 53, so that EGR flows down in the rectifying pipe 51. The flow rate of the gas G gradually becomes slower toward the EGR gas downstream end 53 by Bernoulli's theorem, and as a result, the flow rate of the EGR gas G flowing down in the tube 33 is slower than in the conventional structure without the rectifying pipe 51. The heat exchange time with the cooling water W becomes longer. As described above, since the heat exchange time between the EGR gas G and the cooling water W is increased, according to the present embodiment, the heat exchange efficiency is increased and the cooling efficiency is improved.
Furthermore, in this embodiment, the EGR gas upstream end portion 55 of each rectifying pipe 51 is formed in a hexagonal cross section, and these are assembled and joined in a honeycomb shape to the inner periphery of the EGR gas inlet 49 of the diffuser 25. Since they are integrally joined, useless gaps are not generated between the respective rectifying pipes 51 and the EGR gas introduction ports 49, and the strength of the rectifying pipes 51 is improved by gathering and joining in a honeycomb shape. Have advantages.
In addition, in the present embodiment, the cooling fin 39 is provided on the outer periphery of each tube 33 to expand the heat transfer area, so that the cooling efficiency with the cooling water W is further improved, and as a result, the EGR gas temperature is lowered. Also, materials having low heat resistance can be used for materials such as piping and gaskets on the downstream side of the EGR gas, and there is an excellent advantage that durability of each part of the material is improved due to a decrease in EGR gas temperature.
[0025]
And it is possible to respond | correspond to the various specifications of an EGR cooler by changing the height of the cooling fin 39 and adjusting a heat-transfer area.
The shape of the cooling fin provided on the outer periphery of the tube is not limited to the above-described embodiment, and various forms can be selected as shown in FIGS. 5 to 8, for example.
[0026]
In the embodiment shown in FIG. 5, a plurality of so-called headband-shaped cooling fins 39-1 are provided on the outer periphery of the tube 33 so as to protrude from the outer periphery of the tube 33 at a predetermined interval. The embodiment shown in FIG. A plurality of cooling fins 39-2 having a sight shape are provided with a predetermined interval.
In the embodiment shown in FIG. 7, cooling fins 39-3 are spirally provided on the outer periphery of the tube 33. In the embodiment shown in FIG. 8, the blade-shaped cooling fins 39 are provided on the outer periphery of the tube 33. -4 is protruded at a predetermined interval, and the height of each of the cooling fins 39-1 to 39-4 may be freely changed in accordance with the specifications of the EGR cooler, similar to the cooling fin 39 described above. .
[0027]
Thus, even with the EGR cooler using these cooling fin fins 39-1 to 39-4, the cooling efficiency with the cooling water W is improved similarly to the EGR cooler 45 of FIG. It is possible to achieve.
Furthermore, the number of the rectifying tubes 51 described above can be changed as appropriate according to the tube .
[0028]
【The invention's effect】
As described above, according to the inventions according to the claims, the EGR gas is guided to the rectifying pipe and flows down evenly in the tube in the shell. As a result, the tube located at the center of the shell can be prevented from being clogged early.
[0029]
And since the rectifier tube can be easily attached to the current EGR cooler, it can be applied to a commercially available engine.
Also, since an enlarged heat transfer area is provided a cooling fin on the outer circumference of the tubing, the cooling efficiency of the cooling water is further improved, as a result, by the EGR gas temperature decreases, Ya EGR gas downstream side of the pipe also it has an advantage of improving the durability of the material each part heat-resistant material having low are available and Do Rutotomoni, by a decrease in the EGR gas temperature on the material of the gasket or the like.
And it is possible to respond | correspond to various specifications of an EGR cooler by changing the height of a cooling fin and adjusting a heat-transfer area.
Furthermore, in the invention according to claim 1, the EGR gas upstream end of each rectifying pipe is formed in a hexagonal cross section, and these are assembled and joined in a honeycomb shape so as to be integrated with the inner periphery of the EGR gas inlet of the diffuser. Therefore, there is no need to create a useless gap between each rectifier tube and the EGR gas introduction port, and there is an advantage that the strength of the rectifier tube is improved by gathering and joining in a honeycomb shape.
[0030]
In the invention according to claim 2, since the flow passage area of each rectifying pipe is sequentially expanded from the EGR gas upstream end to the EGR gas downstream end, the flow rate of the EGR gas flowing down the rectifying pipe is Theorem gradually slows down toward the end of the EGR gas downstream, resulting in a slower flow rate of EGR gas flowing down the tube and a longer time for heat exchange with cooling water than in a conventional structure without a rectifying tube. . And since heat exchange time with EGR gas and cooling water becomes long in this way, it has the advantage that heat exchange efficiency goes up and cooling efficiency improves.
[Brief description of the drawings]
1 is an overall perspective view of an EGR cooler according to an embodiment of claims 1 and 2;
2 is a cross-sectional view taken along line II-II in FIG.
3 is a cross-sectional view taken along line III-III in FIG.
4 is a cross-sectional view taken along line IV-IV in FIG.
FIG. 5 is a side view of a tube showing a modified example of a cooling fin.
FIG. 6 is a side view of a tube showing a modified example of a cooling fin.
FIG. 7 is a side view of a tube showing a modified example of a cooling fin.
FIG. 8 is a side view of a tube showing a modified example of a cooling fin.
FIG. 9 is an overall perspective view of a conventional EGR cooler.
10 is a cross-sectional view taken along line XX of FIG.
11 is a cross-sectional view taken along line XI-XI in FIG.
[Explanation of symbols]
23 Shell 25, 27 Diffuser 29 EGR gas introduction pipe 31 EGR gas outlet pipe 33 Tube 35, 37 End plate 39, 39-1, 39-2, 39-3, 39-4 Cooling fin 41 Cooling water introduction pipe 43 Cooling water Outlet pipe 45 EGR cooler 47 EGR gas upstream end 49 of the tube EGR gas inlet 51 of the diffuser Rectifier pipe 53 EGR gas downstream end 55 of the rectifier pipe EGR gas upstream end G EGR gas W of the rectifier pipe Cooling water

Claims (2)

周壁に冷却水導入パイプと冷却水導出パイプが接続された筒状のシェルの両端部に、ディフューザを介してＥＧＲガス導入パイプとＥＧＲガス導出パイプを接続し、シェルの両端部を閉塞するエンドプレート間に、ディフューザ内に開口する複数のチューブを挿着したＥＧＲ装置のＥＧＲクーラーに於て、
上記各チューブのＥＧＲガス上流側端部と、ＥＧＲガス導入パイプが接続されたディフューザのＥＧＲガス導入口との間に複数の整流管を配置し、当該各整流管を介してＥＧＲガスを各チューブに導くと共に、
各整流管のＥＧＲガス上流側端部を断面六角形状に成形し、これらをハニカム状に集合，接合させて上記ＥＧＲガス導入口の内周に一体的に接合し、
上記チューブの外周に冷却フィンを設けたことを特徴とするＥＧＲクーラー。 An end plate that connects the EGR gas introduction pipe and the EGR gas lead pipe through a diffuser to both ends of a cylindrical shell having a cooling water introduction pipe and a cooling water lead pipe connected to the peripheral wall, and closes both ends of the shell. In the EGR cooler of the EGR device in which a plurality of tubes opened in the diffuser are inserted ,
A plurality of rectifying tubes are arranged between the EGR gas upstream end of each tube and the EGR gas introducing port of the diffuser connected to the EGR gas introducing pipe, and the EGR gas is supplied to each tube through the rectifying tube. And lead to
The EGR gas upstream end of each rectifying tube is formed into a hexagonal cross section, and these are assembled and joined in a honeycomb shape and integrally joined to the inner periphery of the EGR gas inlet,
An EGR cooler characterized in that a cooling fin is provided on the outer periphery of the tube . 周壁に冷却水導入パイプと冷却水導出パイプが接続された筒状のシェルの両端部に、ディフューザを介してＥＧＲガス導入パイプとＥＧＲガス導出パイプを接続し、シェルの両端部を閉塞するエンドプレート間に、ディフューザ内に開口する複数のチューブを挿着したＥＧＲ装置のＥＧＲクーラーに於て、An end plate that connects the EGR gas introduction pipe and the EGR gas extraction pipe to both ends of a cylindrical shell having a cooling water introduction pipe and a cooling water extraction pipe connected to the peripheral wall via a diffuser, and closes both ends of the shell. In the EGR cooler of the EGR device in which a plurality of tubes opened in the diffuser are inserted,
上記各チューブのＥＧＲガス上流側端部と、ＥＧＲガス導入パイプが接続されたディフューザのＥＧＲガス導入口との間に複数の整流管を配置し、当該各整流管を介してＥＧＲガスを各チューブに導くと共に、A plurality of rectifying pipes are arranged between the EGR gas upstream end of each tube and the EGR gas introducing port of the diffuser to which the EGR gas introducing pipe is connected, and the EGR gas is supplied to each tube through the rectifying pipe. And lead to
各整流管の流路面積を、ＥＧＲガス上流側端部からＥＧＲガス下流側端部へ順次拡大させて、The flow passage area of each rectifying pipe is sequentially expanded from the EGR gas upstream end to the EGR gas downstream end,
上記チューブの外周に冷却フィンを設けたことを特徴とするＥＧＲクーラー。An EGR cooler characterized in that a cooling fin is provided on the outer periphery of the tube.
JP2003148184A 2003-05-26 2003-05-26 EGR cooler Expired - Fee Related JP4031393B2 (en)

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JP2009002300A (en) * 2007-06-25 2009-01-08 Nissan Diesel Motor Co Ltd Egr cooler
SE534011C2 (en) * 2008-09-22 2011-03-29 K A Ekstroem & Son Ab Heat exchanger and carbon black production plant adapted for carbon black production
JP5048695B2 (en) * 2009-02-27 2012-10-17 株式会社小松製作所 EGR cooler
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JP4997336B2 (en) * 2010-01-29 2012-08-08 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド Large two-cycle diesel engine with exhaust gas recirculation system
CN102840788A (en) * 2012-09-19 2012-12-26 常州大学 Inlet and outlet head of gas plate heat exchanger
CN104197771B (en) * 2014-09-12 2016-01-20 甘肃蓝科石化高新装备股份有限公司 A kind of current equalizing structure for heat exchanger plate bundle gas access
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