JP2007051578A - Two stage supercharging system - Google Patents

Two stage supercharging system Download PDF

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JP2007051578A
JP2007051578A JP2005236710A JP2005236710A JP2007051578A JP 2007051578 A JP2007051578 A JP 2007051578A JP 2005236710 A JP2005236710 A JP 2005236710A JP 2005236710 A JP2005236710 A JP 2005236710A JP 2007051578 A JP2007051578 A JP 2007051578A
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engine
small
turbine
compressor
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Shinichiro Uematsu
真一郎 植松
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Hino Motors Ltd
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Hino Motors Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a two stage supercharging system suitable for an engine which is operated often under a condition keeping a high rotation speed area. <P>SOLUTION: This system is provided with a first turbocharger 17 operating a large diameter turbine 8 by exhaust gas G directly sent out from an engine 1 and compressing intake air A by a large diameter compressor 9, a second turbocharger 18 operating a small diameter turbine 3 by exhaust gas G sent out from the large diameter turbine 8 and compressing intake air A sent out from the large diameter compressor 9 by a small diameter compressor 4 and feeding the same to the engine 1, and a bypass passage 19 reaching a downstream side of an exhaust gas outlet from an upstream side of an exhaust gas inlet of the small diameter turbine 3. The bypass passage 19 is constructed of a bypass valve 20 built therein, exhaust gas G directly sent out from the engine 1 is led to the large diameter turbine 8, and energy of exhaust gas G in the high rotation speed area is effectively utilized. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明はエンジンの出力増大に用いる二段過給システムに関するものである。   The present invention relates to a two-stage supercharging system used for increasing engine output.

排気量を変えずにエンジンの出力を高めるためには、シリンダに送給すべき吸気流量を増やし、１サイクルあたりの燃料噴射量を多くする必要がある。   In order to increase the engine output without changing the exhaust amount, it is necessary to increase the intake flow rate to be supplied to the cylinder and increase the fuel injection amount per cycle.

また、エンジン排気経路から分流した排気を水冷式の管形熱交換器であるＥＧＲクーラ（ＥＧＲ:Exhaust Gas Recirculation）より冷却したうえエンジン吸気経路へ戻し、燃焼温度を下げてＮＯｘの発生を低減させる排気再循環も一般的に行なわれている。   In addition, the exhaust gas diverted from the engine exhaust path is cooled by an EGR cooler (EGR: Exhaust Gas Recirculation), which is a water-cooled tubular heat exchanger, and then returned to the engine intake path to lower the combustion temperature and reduce NOx generation. Exhaust gas recirculation is also commonly performed.

そこで近年、シリンダに送給すべき吸気流量を増やす手段として、エンジンに二段過給システムを採用することが提案されている（例えば、非特許文献１参照）。   In recent years, therefore, it has been proposed to employ a two-stage supercharging system for the engine as means for increasing the intake flow rate to be supplied to the cylinder (see, for example, Non-Patent Document 1).

図２は従来の二段過給システムの一例であり、車載のエンジン１の排気マニホールド２から直に送出される排気Ｇによって小径タービン３を作動させ且つ小径コンプレッサ４で圧縮した吸気Ａをエンジン１の吸気マニホールド５へ送給するターボチャージャ６と、小径タービン３から送出される排気Ｇ、あるいは当該小径タービン３の排気流入口の上流側から排気送出口の下流側へ至る小径タービン３用のバイパス通路７を経た排気Ｇによって大径タービン８を作動させ且つ大径コンプレッサ９で圧縮した吸気Ａを前記小径コンプレッサ４へ送給するターボチャージャ１０とを備え、前記バイパス通路７には、小径タービン３に対応するバイパスバルブ１１が組み込んである。   FIG. 2 shows an example of a conventional two-stage turbocharging system. The engine 1 is configured to operate the small-diameter turbine 3 by the exhaust G that is sent directly from the exhaust manifold 2 of the on-vehicle engine 1 and compress the intake air A compressed by the small-diameter compressor 4. Of the small-diameter turbine 3 that extends from the upstream side of the exhaust inlet of the small-diameter turbine 3 to the downstream side of the exhaust outlet. And a turbocharger 10 for operating the large-diameter turbine 8 by the exhaust G passing through the passage 7 and feeding the intake air A compressed by the large-diameter compressor 9 to the small-diameter compressor 4. The bypass passage 7 includes a small-diameter turbine 3. The bypass valve 11 corresponding to is incorporated.

更に、大径コンプレッサ９の空気吐出口と小径コンプレッサ４の空気吸入口の間には、低圧段インタクーラ１２が介装してあり、小径コンプレッサ４の空気吐出口とエンジン１の吸気マニホールド５の間には、高圧段インタクーラ１３が介装してある。   Further, a low-pressure intercooler 12 is interposed between the air discharge port of the large-diameter compressor 9 and the air intake port of the small-diameter compressor 4, and between the air discharge port of the small-diameter compressor 4 and the intake manifold 5 of the engine 1. A high-pressure stage intercooler 13 is interposed between the two.

この他に、エンジン排気経路の小径タービン３よりも上流側（具体的には排気マニホールド２）からエンジン吸気経路の高圧段インタクーラ１３よりも下流側（具体的には吸気マニホールド５）へ至るＥＧＲ管路１４を設け、当該ＥＧＲ管路１４に、分流した排気Ｇを冷却するＥＧＲクーラ１５と、エンジン吸気経路へ還流すべき排気Ｇの流量を調整するＥＧＲバルブ１６を組み込んでいる。   In addition, an EGR pipe that extends from the upstream side (specifically, the exhaust manifold 2) of the small-diameter turbine 3 in the engine exhaust path to the downstream side (specifically, the intake manifold 5) of the high-pressure stage intercooler 13 of the engine intake path. A passage 14 is provided, and an EGR cooler 15 that cools the shunted exhaust G and an EGR valve 16 that adjusts the flow rate of the exhaust G to be recirculated to the engine intake passage are incorporated in the EGR pipe 14.

エンジン１が稼働状態であるとき、排気マニホールド２から送出される排気Ｇの大部分は小径タービン３へ流入して小径コンプレッサ４を駆動した後、大径タービン８へ流入して大径コンプレッサ９を駆動する。   When the engine 1 is in operation, most of the exhaust G delivered from the exhaust manifold 2 flows into the small-diameter turbine 3 and drives the small-diameter compressor 4, and then flows into the large-diameter turbine 8 and causes the large-diameter compressor 9 to flow. To drive.

大径コンプレッサ９に流入し且つ圧縮された吸気Ａは、低圧段インタクーラ１２を経て小径コンプレッサ４に送給され、当該小径コンプレッサ４で再び圧縮されたうえ、高圧段インタクーラ１３を経て吸気マニホールド５へ送給される。   The compressed air A flowing into the large-diameter compressor 9 and compressed is fed to the small-diameter compressor 4 via the low-pressure stage intercooler 12, compressed again by the small-diameter compressor 4, and then to the intake manifold 5 via the high-pressure stage intercooler 13. Be sent.

よって、シリンダに送給すべき吸気流量が増え、１サイクルあたりの燃料噴射量を多くすれば、エンジン１の出力を高めることができる。   Therefore, if the intake air flow rate to be supplied to the cylinder increases and the fuel injection amount per cycle is increased, the output of the engine 1 can be increased.

また、排気Ｇの一部が排気マニホールド２からＥＧＲ管路１４へ流入し、ＥＧＲクーラ１５で冷却され且つＥＧＲバルブ１６で流量調整が行なわれた排気Ｇが、吸気Ａとともに吸気マニホールド５へ送給される。   Further, a part of the exhaust G flows from the exhaust manifold 2 into the EGR pipe 14, and the exhaust G cooled by the EGR cooler 15 and adjusted in flow rate by the EGR valve 16 is sent to the intake manifold 5 together with the intake A. Is done.

これにより、気筒内の燃焼温度の低下が図られ、ＮＯｘの発生が低減することになる。   Thereby, the combustion temperature in the cylinder is lowered, and the generation of NOx is reduced.

また、エンジン１が高回転数域に達した際には、小径タービン３の能力を上回るような高エネルギ（大流量で高圧力）の排気Ｇが当該小径タービン３に流れ込むことがないように（タービン内の圧力過上昇抑制と過回転防止のため）バイパスバルブ１１を開き、排気Ｇの一部をバイパス通路７から大径タービン８に導くようにしている。
エフ・ミロ（F. Millo）、エフ・マラモ（F. Mallamo）、ジー・ジャニオ・メゴ（G. Ganio Mego） ザ・ポテンシャル・オブ・デュアル・ステージ・ターボチャージング・アンド・ミラー・サイクル・フォー・エッチディー・ディーゼル・エンジン（The Potential of Dual Stage Turbocharging and Miller Cycle for HD Diesel Engines） エスエーイー・ペーパー（SAE Paper）2005-01-0221 Further, when the engine 1 reaches the high speed range, the exhaust G having high energy (large flow rate and high pressure) exceeding the capacity of the small diameter turbine 3 does not flow into the small diameter turbine 3 ( The bypass valve 11 is opened (in order to suppress excessive pressure rise in the turbine and prevent excessive rotation), and a part of the exhaust G is guided from the bypass passage 7 to the large-diameter turbine 8.
F. Millo, F. Mallamo, G. Ganio Mego The Potential of Dual Stage Turbocharging and Miller Cycle Four・ The Potential of Dual Stage Turbocharging and Miller Cycle for HD Diesel Engines SAE Paper 2005-01-0221

しかしながら、図２に示す二段過給システムでは、エンジンが高回転数域に達した際にバイパスバルブ１１を開くと、小径タービン３の排気送出口の背圧が上昇してターボチャージャ６の効率低下を招く。   However, in the two-stage turbocharging system shown in FIG. 2, when the bypass valve 11 is opened when the engine reaches a high engine speed range, the back pressure at the exhaust outlet of the small-diameter turbine 3 increases and the efficiency of the turbocharger 6 is increased. Incurs a decline.

このため、排気再循環が良好に行なわれなくなるとともにポンプ損失も増え、エンジン性能が損なわれる。   For this reason, exhaust gas recirculation is not performed well, pump loss increases, and engine performance is impaired.

本発明は上述した実情に鑑みてなしたもので、高回転数域を維持した状態での運転が多いエンジンに適した二段過給システムを提供することを目的としている。   The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a two-stage supercharging system suitable for an engine that is frequently operated in a state where a high engine speed range is maintained.

上記目的を達成するため本発明は、エンジンから直に送出される排気によって大径タービンを作動させ且つ大径コンプレッサで吸気を圧縮する第１のターボチャージャと、前記大径タービンから送出される排気によって小径タービンを作動させ且つ大径コンプレッサから送出される吸気を小径コンプレッサで圧縮してエンジンへ送給する第２のターボチャージャと、小径タービンの排気流入口の上流側から排気送出口の下流側へ至る小径タービン用バイパス通路とを備え、当該バイパス通路に、小径タービン用バイパスバルブを組み込んだ構成を採る。   In order to achieve the above object, the present invention provides a first turbocharger that operates a large-diameter turbine by exhaust directly delivered from an engine and compresses intake air by a large-diameter compressor, and exhaust delivered from the large-diameter turbine. A second turbocharger that operates the small-diameter turbine and compresses the intake air sent from the large-diameter compressor by the small-diameter compressor and sends it to the engine, and from the upstream side of the exhaust inlet of the small-diameter turbine to the downstream side of the exhaust outlet And a bypass passage for small-diameter turbines, and a bypass valve for small-diameter turbines is incorporated in the bypass passage.

また、エンジン排気経路の大径タービンよりも上流側からエンジン吸気経路の小径コンプレッサよりも下流側へ至るＥＧＲ管路を設け、当該ＥＧＲ管路にＥＧＲクーラとＥＧＲバルブを組み込んだ構成を採るようにする。   Also, an EGR pipe that extends from the upstream side of the large-diameter turbine in the engine exhaust path to the downstream side of the small-diameter compressor in the engine intake path is provided, and an EGR cooler and an EGR valve are incorporated in the EGR pipe. To do.

すなわち、エンジン高回転数域における高エネルギの排気を大径タービンに導き、大径コンプレッサの駆動力に変換して吸気を圧縮する。   That is, high-energy exhaust gas in the high engine speed range is guided to a large-diameter turbine and converted into driving force of a large-diameter compressor to compress the intake air.

エンジンが高回転数上限域を維持し続け、大径コンプレッサから送出される吸気流量が小径コンプレッサの能力を上回りそうな場合にはバイパスバルブを開き、大径タービンが送出する排気の一部をバイパス通路によって小径タービンの下流側へ導く。   When the engine continues to maintain the upper limit of the high engine speed and the intake air flow sent from the large-diameter compressor is likely to exceed the capacity of the small-diameter compressor, the bypass valve is opened and a part of the exhaust gas delivered by the large-diameter turbine is bypassed. It leads to the downstream side of the small diameter turbine by the passage.

また、エンジン低回転数域ではバイパスバルブを閉じ、大径タービンが送出する排気の全てを小径タービンに導く。   Further, in the engine low speed range, the bypass valve is closed, and all the exhaust gas delivered by the large diameter turbine is guided to the small diameter turbine.

本発明の二段過給システムによれば、下記のような優れた効果を奏し得る。   According to the two-stage supercharging system of the present invention, the following excellent effects can be obtained.

（１）エンジンから直に送出される排気を大径タービンに導くので、エンジン高回転数域における排気エネルギを有効に利用することができる。   (1) Since the exhaust gas sent directly from the engine is guided to the large-diameter turbine, the exhaust energy in the high engine speed range can be used effectively.

（２）また、エンジンが低回転数域を維持し続けている場合にはバイパスバルブを閉じ、大径タービンが送出する排気の全てを小径タービンに導くようにすれば、当該小径タービンの能力を最大限活かすことができる。   (2) If the engine continues to maintain a low engine speed range, the bypass valve is closed, and if all the exhaust gas delivered by the large-diameter turbine is guided to the small-diameter turbine, the capacity of the small-diameter turbine can be improved. You can make the most of it.

以下、本発明の実施の形態を図面に基づき説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は本発明の二段過給システムの一例であり、図中、図２と同一の符号を付した部分は同一物を表している。   FIG. 1 shows an example of a two-stage supercharging system according to the present invention. In the figure, the same reference numerals as those in FIG. 2 denote the same parts.

この二段過給システムは、車載のエンジン１の排気マニホールド２から直に送出される排気Ｇによって大径タービン８を作動させ且つ大径コンプレッサ９で吸気Ａを圧縮するターボチャージャ１７と、大径タービン８から送出される排気Ｇによって小径タービン３を作動させ且つ大径コンプレッサ９から送出される吸気Ａを小径コンプレッサ４で圧縮してエンジン１の吸気マニホールド５へ送給するターボチャージャ１８と、小径タービン３の排気流入口の上流側から排気送出口の下流側へ至る小径タービン３用のバイパス通路１９とを備え、当該バイパス通路１９には、小径タービン３に対応するバイパスバルブ２０が組み込んである。   This two-stage supercharging system includes a turbocharger 17 that operates a large-diameter turbine 8 by exhaust G that is sent directly from an exhaust manifold 2 of an in-vehicle engine 1 and compresses intake air A by a large-diameter compressor 9, and a large-diameter A turbocharger 18 that operates the small-diameter turbine 3 by the exhaust G delivered from the turbine 8 and compresses the intake air A delivered from the large-diameter compressor 9 by the small-diameter compressor 4 and supplies the compressed air to the intake manifold 5 of the engine 1. A bypass passage 19 for the small-diameter turbine 3 extending from the upstream side of the exhaust inlet of the turbine 3 to the downstream side of the exhaust outlet, and a bypass valve 20 corresponding to the small-diameter turbine 3 is incorporated in the bypass passage 19. .

更に、大径コンプレッサ９の空気吐出口と小径コンプレッサ４の空気吸入口の間には、低圧段インタクーラ１２が介装してあり、小径コンプレッサ４の空気吐出口とエンジン１の吸気マニホールド５の間には、高圧段インタクーラ１３が介装してある。   Further, a low-pressure intercooler 12 is interposed between the air discharge port of the large-diameter compressor 9 and the air intake port of the small-diameter compressor 4, and between the air discharge port of the small-diameter compressor 4 and the intake manifold 5 of the engine 1. A high-pressure stage intercooler 13 is interposed between the two.

この他に、エンジン排気経路の大径タービン８よりも上流側（具体的には排気マニホールド２）からエンジン吸気経路の高圧段インタクーラ１３よりも下流側（具体的には吸気マニホールド５）へ至るＥＧＲ管路１４を設け、当該ＥＧＲ管路１４に、分流した排気Ｇを冷却するＥＧＲクーラ１５と、エンジン吸気経路へ還流すべき排気Ｇの流量を調整するＥＧＲバルブ１６を組み込んでいる。   In addition, EGR from the upstream side of the large-diameter turbine 8 in the engine exhaust path (specifically, the exhaust manifold 2) to the downstream side (specifically, the intake manifold 5) of the high-pressure stage intercooler 13 in the engine intake path. A pipe line 14 is provided, and an EGR cooler 15 that cools the diverted exhaust gas G and an EGR valve 16 that adjusts the flow rate of the exhaust gas G to be returned to the engine intake path are incorporated in the EGR pipe line 14.

エンジン１が稼働状態であるとき、排気マニホールド２から送出される排気Ｇの大部分は大径タービン８へ流入して大径コンプレッサ９を駆動した後、小径タービン３へ流入して小径コンプレッサ４を駆動する。   When the engine 1 is in operation, most of the exhaust G delivered from the exhaust manifold 2 flows into the large-diameter turbine 8 and drives the large-diameter compressor 9, and then flows into the small-diameter turbine 3 and causes the small-diameter compressor 4 to flow. To drive.

大径コンプレッサ９に流入し且つ圧縮された吸気Ａは、低圧段インタクーラ１２を経て小径コンプレッサ４に送給され、当該小径コンプレッサ４で再び圧縮されたうえ、高圧段インタクーラ１３を経て吸気マニホールド５へ送給される。   The compressed air A flowing into the large-diameter compressor 9 and compressed is fed to the small-diameter compressor 4 via the low-pressure stage intercooler 12, compressed again by the small-diameter compressor 4, and then to the intake manifold 5 via the high-pressure stage intercooler 13. Be sent.

よって、シリンダに送給すべき吸気流量が増え、１サイクルあたりの燃料噴射量を多くすれば、エンジンの出力を高めることができる。   Therefore, if the intake air flow rate to be supplied to the cylinder is increased and the fuel injection amount per cycle is increased, the output of the engine can be increased.

また、排気Ｇの一部が排気マニホールド２からＥＧＲ管路１４へ流入し、ＥＧＲクーラ１５で冷却され且つＥＧＲバルブ１６で流量調整が行なわれた排気Ｇが、吸気Ａとともに吸気マニホールド５へ送給される。   Further, a part of the exhaust G flows from the exhaust manifold 2 into the EGR pipe 14, and the exhaust G cooled by the EGR cooler 15 and adjusted in flow rate by the EGR valve 16 is sent to the intake manifold 5 together with the intake A. Is done.

これにより、気筒内の燃焼温度の低下が図られ、ＮＯｘの発生が低減することになる。   Thereby, the combustion temperature in the cylinder is lowered, and the generation of NOx is reduced.

エンジン１が高回転数上限域を維持し続け、大径コンプレッサ９から送出される吸気Ａの流量が小径コンプレッサ４の能力を上回りそうな際にはバイパスバルブ２０を開き、大径タービン８が送出する排気Ｇの一部をバイパス通路１９によって小径タービン３の下流側へ導くようにし（小径コンプレッサ４の回転が大径コンプレッサ９で圧縮された吸気Ａの流れを阻害しない程度に）、小径タービン３内の圧力過上昇抑制と過回転防止を図る。   When the engine 1 continues to maintain the high engine speed upper limit range and the flow rate of the intake air A sent from the large-diameter compressor 9 seems to exceed the capacity of the small-diameter compressor 4, the bypass valve 20 is opened, and the large-diameter turbine 8 delivers. A part of the exhaust G to be directed is guided to the downstream side of the small-diameter turbine 3 by the bypass passage 19 (so that the rotation of the small-diameter compressor 4 does not hinder the flow of the intake air A compressed by the large-diameter compressor 9). To suppress excessive pressure rise and prevent over-rotation.

また、エンジン１が低回転数域を維持し続けている場合にはバイパスバルブ２０を閉じ、大径タービン８が送出する排気Ｇの全てを小径タービン３に導くようにして、当該小径タービン３の能力を最大限活かし、大径コンプレッサ９と小径コンプレッサ４により吸気Ａを逐次圧縮する。   When the engine 1 continues to maintain the low engine speed range, the bypass valve 20 is closed, and all the exhaust G sent from the large-diameter turbine 8 is guided to the small-diameter turbine 3. The intake A is sequentially compressed by the large-diameter compressor 9 and the small-diameter compressor 4 by making the most of the capacity.

なお、本発明の二段過給システムは、上述の実施の形態のみに限定されるものではなく、本発明の要旨を逸脱しない範囲において変更を加え得ることは勿論である。   It should be noted that the two-stage supercharging system of the present invention is not limited to the above-described embodiment, and it is needless to say that changes can be made without departing from the gist of the present invention.

本発明の二段過給システムは、様々な内燃機関に適用できる。   The two-stage supercharging system of the present invention can be applied to various internal combustion engines.

本発明の二段過給システムの一例を示す概念図である。It is a conceptual diagram which shows an example of the two-stage supercharging system of this invention. 従来の二段過給システムの一例を示す概念図である。It is a conceptual diagram which shows an example of the conventional two-stage supercharging system.

符号の説明Explanation of symbols

１ エンジン
２ 排気マニホールド（排気経路）
３ 小径タービン
４ 小径コンプレッサ
５ 吸気マニホールド（吸気経路）
８ 大径タービン
９ 大径コンプレッサ
１７ ターボチャージャ（第１のターボチャージャ）
１８ ターボチャージャ（第２のターボチャージャ）
１９ バイパス通路
２０ バイパスバルブ 1 Engine 2 Exhaust manifold (exhaust path)
3 Small-diameter turbine 4 Small-diameter compressor 5 Intake manifold (intake path)
8 Large-diameter turbine 9 Large-diameter compressor 17 Turbocharger (first turbocharger)
18 Turbocharger (second turbocharger)
19 Bypass passage 20 Bypass valve

Claims (2)

エンジンから直に送出される排気によって大径タービンを作動させ且つ大径コンプレッサで吸気を圧縮する第１のターボチャージャと、前記大径タービンから送出される排気によって小径タービンを作動させ且つ大径コンプレッサから送出される吸気を小径コンプレッサで圧縮してエンジンへ送給する第２のターボチャージャと、小径タービンの排気流入口の上流側から排気送出口の下流側へ至る小径タービン用バイパス通路とを備え、当該バイパス通路に、小径タービン用バイパスバルブを組み込んだことを特徴とする二段過給システム。   A first turbocharger that operates a large-diameter turbine by exhaust gas sent directly from an engine and compresses intake air by a large-diameter compressor; and a large-diameter compressor that operates a small-diameter turbine by exhaust gas sent from the large-diameter turbine A second turbocharger that compresses the intake air sent from the compressor with a small-diameter compressor and sends the compressed air to the engine, and a small-diameter turbine bypass passage that extends from the upstream side of the exhaust inlet of the small-diameter turbine to the downstream side of the exhaust outlet. A two-stage turbocharging system comprising a bypass valve for a small-diameter turbine incorporated in the bypass passage. エンジン排気経路の大径タービンよりも上流側からエンジン吸気経路の小径コンプレッサよりも下流側へ至るＥＧＲ管路を設け、当該ＥＧＲ管路にＥＧＲクーラとＥＧＲバルブを組み込んだ請求項１に記載の二段過給システム。   2. An EGR pipe that extends from an upstream side of a large-diameter turbine in an engine exhaust path to a downstream side of a small-diameter compressor in an engine intake path is provided, and an EGR cooler and an EGR valve are incorporated in the EGR pipe. Stage supercharging system.
JP2005236710A 2005-08-17 2005-08-17 Two stage supercharging system Pending JP2007051578A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007017843A1 (en) * 2007-04-16 2008-11-06 Siemens Ag turbocharger assembly
JP2012132370A (en) * 2010-12-22 2012-07-12 Mazda Motor Corp Diesel engine with turbo-supercharger

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50145713A (en) * 1974-05-16 1975-11-22
JPH03290028A (en) * 1990-04-06 1991-12-19 Toyota Motor Corp Fuel injector for series two-stage supercharging diesel engine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50145713A (en) * 1974-05-16 1975-11-22
JPH03290028A (en) * 1990-04-06 1991-12-19 Toyota Motor Corp Fuel injector for series two-stage supercharging diesel engine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007017843A1 (en) * 2007-04-16 2008-11-06 Siemens Ag turbocharger assembly
JP2012132370A (en) * 2010-12-22 2012-07-12 Mazda Motor Corp Diesel engine with turbo-supercharger

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