JP3759796B2 - Supply structure of exhaust gas recirculation gas engine - Google Patents

Supply structure of exhaust gas recirculation gas engine Download PDF

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JP3759796B2
JP3759796B2 JP29199096A JP29199096A JP3759796B2 JP 3759796 B2 JP3759796 B2 JP 3759796B2 JP 29199096 A JP29199096 A JP 29199096A JP 29199096 A JP29199096 A JP 29199096A JP 3759796 B2 JP3759796 B2 JP 3759796B2
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air supply
air
supply port
exhaust gas
liner
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JPH10141144A (en
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徹 武本
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Yanmar Co Ltd
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Yanmar Co Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

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Description

【０００１】
【発明の属する技術分野】
本発明は、特にコージェネレーター駆動用等、通常において高負荷運転が長時間行われるようなタイプの排気再循環式ガスエンジンについての給気構造に関する。
【０００２】
【従来の技術】
従来、排気中のＮＯX 低減策として、自動車用ガソリンエンジンや、コージェネレーション用ディーゼルエンジン等においては、排気を低温処理して給気系に再循環する排気再循環方式（ＥＧＲ）を採用したものが公知となっている。
しかし、ガスエンジンにおいては、従来、ＥＧＲは採用されていない。
【０００３】
【発明が解決しようとする課題】
コージェネレーション駆動用等に適用するようなガスエンジンは、排気ＮＯX の低減効果もさることながら、通常時に高負荷運転が長時間なされることから、ノッキング対策として、ＥＧＲを採用することが有効である。ＥＧＲにより、燃焼室内の温度上昇が抑制されるので、シリンダライナ内壁面付近のエンドガスが自然着火するノッキング限界（正味平均有効圧の上限値）が上昇し、その分、出力向上に繋がるのである。
ディーゼルエンジンの場合は火花点火式ではないため、ノッキングは起こりえない。また、自動車用ガソリンエンジンでは、ノッキング限界に達するほどの高負荷にて運転されることはめったにない。
【０００４】
しかし、ＥＧＲを採用するにおいては、各気筒の燃焼室に均一に、元の空燃混合気とＥＧＲによる排気との混合気（ＥＧＲ混合気）を供給すると、不具合がある。
というのは、元の空燃混合気は、点火プラグの点火に適した空燃比（空気過剰率）に調合されており、点火プラグ付近にＥＧＲ混合気を供給すると、燃焼が不安定化し、あまりＥＧＲ率（元の空燃混合気に対するＥＧＲ排気の混合率）が高い場合には、失火してしまうおそれもある。
理想的には、気筒の燃焼室にて、点火プラグ付近は、燃焼に適する空燃比に設定した元の空燃混合気（ＥＧＲ率０％）が存在し、その周囲にＥＧＲ混合気が存在して、気筒内の温度上昇を抑止できる状態にするのがよい。
【０００５】
【課題を解決するための手段】
本発明は、以上のような課題を解決すべく、次のような手段を用いるものである。
請求項１においては、一部の冷却済み排気を給気系に導入し、空燃混合気に混合する排気再循環系を有する排気再循環式ガスエンジンにおいて、各気筒につき、点火プラグ付近に臨む点火プラグ側給気ポート３と、気筒壁面側に臨むライナ側給気ポート４とを設け、前者の点火プラグ側給気ポート３を空燃混合気のみを供給する給気系に、後者のライナ側給気ポート４を、空燃混合気と排気再循環系からの排気との混合気を供給する給気系に、それぞれ連結し、該点火プラグ側給気ポート３よりシリンダライナ２内の燃焼室に供給された給気は、シリンダヘッド１の中央付近に配設する点火プラグ７の電極付近に流れ、一方、ライナ側給気ポート４から燃焼室内への給気は、シリンダーライナ２の内壁面に沿って、燃焼室内にリング状に広がり、シリンダライナ２内の燃焼室内にて、中心部の点火プラグ側給気ポート３による給気圏と、その周囲のライナ側給気ポート４による給気圏と、二層に分かれた給気圏を形成するものである。
【０００６】
請求項２においては、一部の冷却済み排気を給気系に導入し、空燃混合気に混合する排気再循環系を有する排気再循環式ガスエンジンにおいて、各気筒につき、点火プラグ付近に臨む点火プラグ側給気ポート３と、気筒壁面側に臨むライナ側給気ポート４とを設け、前者の点火プラグ側給気ポート３を空燃混合気のみを供給する給気系に、後者のライナ側給気ポート４を排気再循環系からの排気のみを供給する給気系に、それぞれ連結し、該点火プラグ側給気ポート３よりシリンダライナ２内の燃焼室に供給された給気は、シリンダヘッド１の中央付近に配設する点火プラグ７の電極付近に流れ、一方、ライナ側給気ポート４から燃焼室内への給気は、シリンダーライナ２の内壁面に沿って、燃焼室内にリング状に広がり、シリンダライナ２内の燃焼室内にて、中心部の点火プラグ側給気ポート３による給気圏と、その周囲のライナ側給気ポート４による給気圏と、二層に分かれた給気圏を形成するものである。
【０００７】
【発明の実施の形態】
本発明の実施の形態を添付の図面を基に説明する。
図１は排気再循環式ガスエンジンを、一定空燃比で、かつ一定回転数にて運転した場合における、ＥＧＲ率に対する排気ＮＯX 量及びノッキング限界給気圧の相関を示す図、図２は各気筒における点火プラグ側給気ポート３及びライナ側給気ポート４の配置構成を示す平面略図、図３は同じく側面略図、図４は空燃混合気Ａ供給用の第一給気系αと混合気Ｃ供給用の第二給気系βを有するガスエンジンの吸排気系配管略図、図５は空燃混合気Ａ供給用の第一給気系α’とＥＧＲ排気Ｂ供給用の第二給気系β’を有するガスエンジンの吸排気系配管略図である。
【０００８】
まず、排気再循環方式（ＥＧＲ）によるガスエンジンにおけるＮＯX 低減効果とノッキング限界の上昇効果とを図１より説明する。
ＥＧＲ率は、ＥＧＲ混合気Ｃにおける、元の給気用空燃混合気Ａに対するＥＧＲによる排気Ｂの混合率（Ｂ／Ａ）を示している。
更に図１のグラフは、空燃混合気Ａの空燃比（空気過剰率）を一定とし、一定回転数にてエンジン駆動している状態におけるものである。この条件下にてＥＧＲ率を上げるほど、燃焼時の気筒内温度の上昇を抑止でき、排気中ＮＯX 量Ｙを低減でき、更にノッキング限界Ｘを上昇させることができ、出力向上に繋げることができるのである。
【０００９】
このように、ＥＧＲ率を上げるほど、排気の低ＮＯX 化と給気圧のノッキング限界値の上昇効果の両方を得られるが、空燃混合気Ａの空燃比は、点火プラグが良好に点火する状態に設定されており、これにＥＧＲ排気Ｂが混合されたＥＧＲ混合気Ｃでは、点火は不安定化する。
【００１０】
これを解決する方法として、まず、ガスエンジンにおける各気筒におけるシリンダヘッド１において、図２及び図３のように、給気ポートとして、点火プラグ側給気ポート３とライナ側給気ポート４とを設けている。なお、５・６は排気ポート、７は点火プラグである。
点火プラグ側給気ポート３よりシリンダライナ２内の燃焼室に供給された給気は、シリンダヘッド１の中央付近に配設する点火プラグ７の電極付近に流れていく。一方、ライナ側給気ポート４から燃焼室内への給気は、シリンダーライナ２の内壁面に沿って、燃焼室内にリング状に広がる。
従って、シリンダライナ２内の燃焼室内にて、中心部に点火プラグ側給気ポート３による給気圏、その周囲にライナ側給気ポート４による給気圏と、二層に分かれた給気圏が形成される。
【００１１】
そして、点火プラグ側給気ポート３からの給気は、点火プラグ７の点火に適するように空燃比が調合された元の空燃混合気Ａとし、ライナ側給気ポート４からの給気は、シリンダライナ２内壁面付近の温度上昇を抑止して、低ＮＯX 化及びノッキング限界給気圧の上昇を図るべく、ＥＧＲ混合気ＣまたはＥＧＲ排気Ｂとするものである。
【００１２】
図４は、このうち、ライナ側給気ポート４からの給気をＥＧＲ混合気Ｃとする場合の、排気再循環式ガスエンジンにおける吸排気系構造を示すものである。
本実施例では、給気系として、元の空燃混合気Ａのみを供給する第一給気系αと、ＥＧＲ混合気Ｃを供給する第二給気系βとを設けている。第一給気系αの構造について説明すると、ガスエンジンの複数のシリンダヘッド１・１・・・の中からいくつかのシリンダヘッド１（本実施例では、ガスエンジン全体でシリンダヘッド１を６個設けており、その中の３個のシリンダヘッド１）より排気マニホルド８ａを配管し、排気マニホルド８ａからの排気を第一給気系αの過給機１３のタービン部１３ａに通した後、三元触媒９に導入する。
一方、空気がエアクリーナー１１を介して空燃混合器１２に導入されて、燃料ガスと混合され、給気としての空燃混合気Ａが、過給機１３のブロア部１３ｂより、給気冷却器１４及びスロットル１５を介して、給気マニホルド１６に供給され、各シリンダヘッド１の点火プラグ側給気ポート３より、前記の如く、各シリンダライナ２内の燃焼室に、点火プラグ７付近の給気として供給される。
【００１３】
次に、第二給気系βについて説明する。前記の排気マニホルド８ａを連結するシリンダヘッド１・１・１以外のシリンダヘッド１・１・１より排気マニホルド８ｂを延設し、排気マニホルド８ｂからの排気を、第二給気系βの過給機２２のタービン部２２ａに通した後、前記の三元触媒９に導入する。即ち、全シリンダヘッド１からの排気は、全て三元触媒９を通過して、ＮＯX 、ＣＯ、ＨＣが除去された状態で、排気放出管１０より放出され、また、一部を、ＥＧＲ排気Ｂとして、ＥＧＲ管１７より、ＥＧＲ冷却器１８を介して、ＥＧＲ混合器２１に導入する。また、空気がエアクリーナー１９を介して空燃混合器２０に導入されて燃料ガスと混合され、空燃混合気Ａとなり、更に、空燃混合気ＡはＥＧＲ混合器２１に導入されて、ＥＧＲ管１７からの排気Ｂと混合されてＥＧＲ混合気Ｃとなり、過給機２２のブロア部２２ｂより、給気冷却器２３及びスロットル２４を介して給気マニホルド２５に供給され、各シリンダヘッドヘッド１のライナ側給気ポート４より、前記の如く、各シリンダライナ２内の燃焼室に、ライナ側の給気として供給される。
【００１４】
図５は、ライナ側給気ポート４からの給気をＥＧＲによる排気Ｂのみとする場合の、排気再循環式ガスエンジンにおける吸排気系構造を示すものである。本実施例では、給気系として、空燃混合気Ａのみを供給する第一給気系α’と、ＥＧＲ排気Ｂを供給する第二給気系β’とを設けている。第一給気系α’の構造について説明すると、ガスエンジンのシリンダヘッド１・１・・・より排気マニホルド２６を配管し、排気の一部を第一給気系α’用の過給機３１のタービン部３１ａに通した後、三元触媒２７に導入する。一方、空気が、エアクリーナー２９を介して空燃混合器３０に導入されて、燃料ガスと混合され、給気としての空燃混合気Ａが、過給機３１のブロア部３１ｂより給気冷却器３２及びスロットル３３を介して給気マニホルド３４に供給され、各シリンダヘッド１の点火プラグ側給気ポート３より、前記の如く、各シリンダライナ２内の燃焼室に、点火プラグ７付近の給気として供給される。
【００１５】
次に、第二給気系β’について説明する。
前記の排気マニホルド２６より一部の排気を第二給気系β’用の過給機３７のタービン部３７ａに通した後、前記の三元触媒２７に導入する。即ち、全シリンダヘッド１からの排気は、全て三元触媒２７を通過し、排気放出管２８より放出され、また、一部を、ＥＧＲ用の排気Ｂとして、ＥＧＲ管３５より、ＥＧＲ冷却器３６を介して、過給機３７のブロア部３７ｂに供給し、該ブロア部３７ｂより、給気冷却器３８及びスロットル３９を介して、給気マニホルド４０に供給され、各シリンダヘッド１のライナ側給気ポート４より、前記の如く、各シリンダライナ２内の燃焼室に、ライナ側の給気として供給される。
【００１６】
図４の実施例におけるスロットル１５・２４、また、図５の実施例におけるすスロットル３３・３９は、点火プラグ７の点火状況やノッキング限界の上昇度等を検出しながら、電子ガバナ制御により、負荷に合わせて最適に開度調整されるものである。
【００１７】
【発明の効果】
本発明は以上のように構成したので、次のような効果を奏する。
即ち、一部の冷却済み排気を給気系に導入し、空燃混合気に混合する排気再循環系を有する排気再循環式ガスエンジンにおいて、請求項１記載の如き構成とすることによりガスエンジンの各気筒燃焼室において、点火プラグ付近には点火に適するように調合された元の給気としての空燃混合気が供給され、その周囲を囲むようにシリンダライナに沿って環状に、空燃混合気と排気再循環系からの排気との混合気が供給されて、シリンダライナ内壁面付近の温度上昇を抑止する。従って、点火は正常になされる一方で、排気再循環方式の利点であるＮＯX の低減化と給気圧のノッキング限界値の上昇による出力向上が得られるのである。
【００１８】
また、請求項２記載の構成とすることにより、ガスエンジンの各気筒燃焼室において、点火プラグ付近には点火に適するように調合された元の給気としての空燃混合気が供給され、その周囲を囲むようにシリンダライナに沿って環状に、排気再循環系からの排気が供給されて、シリンダライナ内壁面付近の温度上昇を抑止する。従って、点火は正常になされる一方で、排気再循環方式の利点であるＮＯX の低減化と、給気圧のノッキング限界値の上昇による出力向上が得られるのである。
【図面の簡単な説明】
【図１】 排気再循環式ガスエンジンを、一定の空燃比で、かつ一定回転数にて運転した場合における、ＥＧＲ率に対する排気ＮＯX 量及びノッキング限界給気圧の相関を示す図である。
【図２】 各気筒における点火プラグ側給気ポート３及びライナ側給気ポート４の配置構成を示す平面略図である。
【図３】 同じく側面略図である。
【図４】 空燃混合気Ａ供給用の第一給気系αと混合気Ｃ供給用の第二給気系βを有するガスエンジンの吸排気系配管略図である。
【図５】 空燃混合気Ａ供給用の第一給気系α’とＥＧＲ排気Ｂ供給用の第二給気系β’を有するガスエンジンの吸排気系配管略図である。
【符号の説明】
Ａ 空燃混合気
Ｂ ＥＧＲ排気
Ｃ ＥＧＲ混合気（空燃混合気とＥＧＲ排気との混合気）
１ シリンダヘッド
２ シリンダライナ
３ 点火プラグ側給気ポート
４ ライナ側給気ポート
７ 点火プラグ
１６ 給気マニホルド
１７ ＥＧＲ管
２５ 給気マニホルド
３４ 給気マニホルド
３５ ＥＧＲ管
４０ 給気マニホルド[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an air supply structure for an exhaust gas recirculation gas engine of a type in which high load operation is normally performed for a long time, such as for driving a co-generator.
[0002]
[Prior art]
Conventionally, as a NO X reduction measures in the exhaust, and motor gasoline engines, in a diesel engine or the like cogeneration, which employs an exhaust recirculation system to recirculate the air supply system and exhaust by low temperature treatment (EGR) Is known.
However, conventionally, EGR has not been adopted in gas engines.
[0003]
[Problems to be solved by the invention]
Gas engine as applicable to cogeneration drive or the like, even more than the effect of reducing the exhaust NO X, since the high-load operation is made long in the normal, as knocking measures, is effective to employ the EGR is there. Since the temperature rise in the combustion chamber is suppressed by EGR, the knocking limit (upper limit value of the net average effective pressure) at which the end gas near the inner wall surface of the cylinder liner is ignited rises, and the output is increased correspondingly.
In the case of a diesel engine, knocking cannot occur because it is not a spark ignition type. Also, gasoline engines for automobiles are rarely operated at a high load that reaches the knocking limit.
[0004]
However, in the case of adopting EGR, there is a problem if an air-fuel mixture (EGR air-fuel mixture) of original air-fuel mixture and exhaust gas by EGR is uniformly supplied to the combustion chamber of each cylinder.
This is because the original air-fuel mixture is blended to an air-fuel ratio (excess air ratio) suitable for ignition of the spark plug, and if EGR mixture is supplied near the spark plug, the combustion becomes unstable and not much When the EGR rate (mixing rate of EGR exhaust with respect to the original air-fuel mixture) is high, there is a risk of misfire.
Ideally, in the combustion chamber of the cylinder, in the vicinity of the spark plug, the original air-fuel mixture (EGR rate 0%) set to an air-fuel ratio suitable for combustion exists, and there is an EGR mixture around it. Thus, it is preferable that the temperature rise in the cylinder be suppressed.
[0005]
[Means for Solving the Problems]
The present invention uses the following means in order to solve the above problems.
In claim 1, in an exhaust gas recirculation gas engine having an exhaust gas recirculation system in which a part of cooled exhaust gas is introduced into an air supply system and mixed with an air-fuel mixture, each cylinder faces the vicinity of a spark plug. An ignition plug side air supply port 3 and a liner side air supply port 4 facing the cylinder wall surface are provided, and the latter liner is used as an air supply system for supplying only the air / fuel mixture to the former ignition plug side air supply port 3. The side air supply port 4 is connected to an air supply system that supplies a mixture of air-fuel mixture and exhaust gas from the exhaust gas recirculation system , and combustion in the cylinder liner 2 is performed from the spark plug side air supply port 3. The supply air supplied to the chamber flows in the vicinity of the electrode of the spark plug 7 disposed in the vicinity of the center of the cylinder head 1, while the supply air from the liner side supply port 4 to the combustion chamber is within the cylinder liner 2. Along the wall surface, it spreads in a ring shape in the combustion chamber , In the combustion chamber in the cylinder liner 2, to form the air supply area by the spark plug side air supply port 3 of the central portion, and the air supply sphere by liner side air supply port 4 surrounding the supply air zone which is divided into two layers Is.
[0006]
According to claim 2, in an exhaust gas recirculation gas engine having an exhaust gas recirculation system in which part of cooled exhaust gas is introduced into an air supply system and mixed with an air-fuel mixture, each cylinder faces the vicinity of a spark plug. An ignition plug side air supply port 3 and a liner side air supply port 4 facing the cylinder wall surface are provided, and the latter liner is used as an air supply system for supplying only the air / fuel mixture to the former ignition plug side air supply port 3. The side air supply port 4 is connected to an air supply system that supplies only exhaust gas from the exhaust gas recirculation system, and the air supplied from the spark plug side air supply port 3 to the combustion chamber in the cylinder liner 2 is The air flows into the vicinity of the electrode of the spark plug 7 disposed near the center of the cylinder head 1. On the other hand, the air supplied from the liner-side air supply port 4 into the combustion chamber is ringed into the combustion chamber along the inner wall surface of the cylinder liner 2. Cylinder liner 2 At the combustion chamber, the air supply area by the spark plug side air supply port 3 of the central portion, and the air supply sphere by liner side air supply port 4 surrounding forms an air supply sphere, divided into two layers.
[0007]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described with reference to the accompanying drawings.
Figure 1 is an exhaust recirculation gas engine, when the plant is operated at a constant air-fuel ratio, and at a constant rotational speed, illustrates the correlation of the exhaust amount of NO X and knocking limit boost pressure for the EGR rate, Figure 2 each of the cylinders Fig. 3 is a schematic plan view showing the arrangement of the spark plug side air supply port 3 and the liner side air supply port 4 in Fig. 3, Fig. 3 is a schematic side view, and Fig. 4 is a first air supply system? FIG. 5 is a schematic diagram of an intake / exhaust system piping of a gas engine having a second supply system β for supplying C, and FIG. 5 is a first supply system α ′ for supplying air-fuel mixture A and a second supply for supplying EGR exhaust B 2 is a schematic diagram of intake and exhaust system piping of a gas engine having a system β ′.
[0008]
First, the NO x reduction effect and the knocking limit increase effect in the gas engine by the exhaust gas recirculation system (EGR) will be described with reference to FIG.
The EGR rate indicates the mixing rate (B / A) of exhaust B by EGR with respect to the original air-fuel mixture A for air supply in the EGR mixture C.
Further, the graph of FIG. 1 shows a state in which the air-fuel ratio (excess air ratio) of the air-fuel mixture A is constant and the engine is driven at a constant rotational speed. The higher the EGR rate at this condition, can suppress rise in the temperature in the cylinder during combustion, can reduce the exhaust amount of NO X Y, it is possible to further increase the knock limit X, it can lead to improvement in output It can be done.
[0009]
Thus, higher the EGR rate, is obtained both increasing effect of knock limit value of the low NO X reduction and boost pressure of the exhaust air-fuel ratio of the air-fuel mixture A, the ignition plug is favorably ignited In the EGR air-fuel mixture C in which the EGR exhaust gas B is mixed with this, the ignition becomes unstable.
[0010]
As a method for solving this, first, in the cylinder head 1 in each cylinder of the gas engine, as shown in FIGS. 2 and 3, the spark plug side air supply port 3 and the liner side air supply port 4 are provided as the air supply ports. Provided. 5 and 6 are exhaust ports, and 7 is a spark plug.
The air supplied from the spark plug side air supply port 3 to the combustion chamber in the cylinder liner 2 flows near the electrode of the spark plug 7 disposed near the center of the cylinder head 1. On the other hand, the air supply from the liner side air supply port 4 into the combustion chamber spreads in a ring shape along the inner wall surface of the cylinder liner 2.
Accordingly, in the combustion chamber in the cylinder liner 2, an air supply area by the spark plug side air supply port 3 is formed at the center, and an air supply area by the liner side air supply port 4 is formed around the air supply area. The
[0011]
The air supply from the spark plug side air supply port 3 is the original air / fuel mixture A in which the air-fuel ratio is adjusted so as to be suitable for ignition of the spark plug 7, and the air supply from the liner side air supply port 4 is , thus suppressing the temperature rise in the vicinity of the wall surface inside the cylinder liner 2, to achieve an increase in the low NO X reduction and knocking limit boost pressure, it is an EGR mixture C or EGR exhaust B.
[0012]
FIG. 4 shows an intake / exhaust system structure in an exhaust gas recirculation gas engine when the air supply from the liner side air supply port 4 is an EGR mixture C.
In this embodiment, a first air supply system α that supplies only the original air-fuel mixture A and a second air supply system β that supplies the EGR mixture C are provided as the air supply system. The structure of the first air supply system α will be described. Among the plurality of cylinder heads 1... Of the gas engine, several cylinder heads 1 (in this embodiment, six cylinder heads 1 are provided for the entire gas engine). The exhaust manifold 8a is piped from the three cylinder heads 1), and the exhaust from the exhaust manifold 8a is passed through the turbine section 13a of the supercharger 13 of the first air supply system α. The catalyst is introduced into the original catalyst 9.
On the other hand, air is introduced into the air / fuel mixer 12 via the air cleaner 11 and mixed with the fuel gas, and the air / fuel mixture A as the supply air is supplied and cooled from the blower portion 13 b of the supercharger 13. Is supplied to the intake manifold 16 through the compressor 14 and the throttle 15 and from the ignition plug side intake port 3 of each cylinder head 1 to the combustion chamber in each cylinder liner 2 as described above, near the ignition plug 7. Supplied as air supply.
[0013]
Next, the second air supply system β will be described. The exhaust manifold 8b is extended from the cylinder heads 1, 1 and 1 other than the cylinder heads 1, 1 and 1 connecting the exhaust manifold 8a, and the exhaust from the exhaust manifold 8b is supercharged by the second air supply system β. After passing through the turbine section 22 a of the machine 22, it is introduced into the three-way catalyst 9. That is, all the exhaust from all cylinder heads 1 passes through the three-way catalyst 9 and is discharged from the exhaust discharge pipe 10 with NO x , CO, and HC removed, and part of it is EGR exhaust. B is introduced into the EGR mixer 21 through the EGR cooler 18 from the EGR pipe 17. Further, air is introduced into the air / fuel mixer 20 through the air cleaner 19 and mixed with the fuel gas to become the air / fuel mixture A, and further, the air / fuel mixture A is introduced into the EGR mixer 21 and EGR. The EGR mixture C is mixed with the exhaust B from the pipe 17 and is supplied from the blower portion 22b of the supercharger 22 to the supply manifold 25 via the supply cooler 23 and the throttle 24. Each cylinder head 1 As described above, the air is supplied from the liner side air supply port 4 to the combustion chambers in the cylinder liners 2 as liner side air supply.
[0014]
FIG. 5 shows an intake / exhaust system structure in an exhaust gas recirculation gas engine when the air supply from the liner side air supply port 4 is only exhaust B by EGR. In this embodiment, a first air supply system α ′ that supplies only the air-fuel mixture A and a second air supply system β ′ that supplies EGR exhaust B are provided as the air supply system. The structure of the first air supply system α ′ will be described. The exhaust manifold 26 is piped from the cylinder heads 1... Of the gas engine, and a part of the exhaust gas is supercharged 31 for the first air supply system α ′. After passing through the turbine part 31 a, it is introduced into the three-way catalyst 27. On the other hand, air is introduced into the air-fuel mixer 30 via the air cleaner 29 and mixed with the fuel gas, and the air-fuel mixture A as the supply air is cooled by the air supply from the blower portion 31 b of the supercharger 31. Is supplied to the intake manifold 34 via the compressor 32 and the throttle 33, and from the ignition plug side intake port 3 of each cylinder head 1 to the combustion chamber in each cylinder liner 2 as described above, Supplied as qi.
[0015]
Next, the second air supply system β ′ will be described.
A part of the exhaust from the exhaust manifold 26 passes through the turbine portion 37a of the supercharger 37 for the second air supply system β ′, and is then introduced into the three-way catalyst 27. That is, all the exhaust from all the cylinder heads 1 passes through the three-way catalyst 27 and is discharged from the exhaust discharge pipe 28. Further, a part of the exhaust is used as the exhaust B for EGR, and the EGR cooler 36 is supplied from the EGR pipe 35. Is supplied to the blower portion 37b of the supercharger 37, and is supplied from the blower portion 37b to the supply manifold 40 via the supply air cooler 38 and the throttle 39, and is supplied to the liner side of each cylinder head 1. As described above, the air is supplied to the combustion chamber in each cylinder liner 2 from the air port 4 as the air supply on the liner side.
[0016]
The throttles 15 and 24 in the embodiment of FIG. 4 and the throttles 33 and 39 in the embodiment of FIG. 5 are controlled by electronic governor control while detecting the ignition state of the spark plug 7 and the degree of increase in the knocking limit. The opening is adjusted optimally according to the above.
[0017]
【The invention's effect】
Since the present invention is configured as described above, the following effects can be obtained.
That is, in the exhaust gas recirculation type gas engine having an exhaust gas recirculation system that introduces a part of the cooled exhaust gas into the air supply system and mixes it with the air-fuel mixture, the gas engine is configured as described in claim 1. In each of the cylinder combustion chambers, an air-fuel mixture as the original supply air prepared so as to be suitable for ignition is supplied in the vicinity of the spark plug, and the air-fuel mixture is annularly formed along the cylinder liner so as to surround the periphery. An air-fuel mixture of the air-fuel mixture and the exhaust gas from the exhaust gas recirculation system is supplied to suppress a temperature rise near the inner wall surface of the cylinder liner. Therefore, ignition while made successfully, improved output due to the increase of knocking limit reduction and boost pressure of an advantage of the exhaust gas recirculation mode NO X is that obtained.
[0018]
Further, with the configuration according to claim 2, in each cylinder combustion chamber of the gas engine, an air-fuel mixture as an original supply air prepared so as to be suitable for ignition is supplied in the vicinity of the spark plug. Exhaust gas from the exhaust gas recirculation system is supplied in an annular shape along the cylinder liner so as to surround the periphery, thereby suppressing a temperature rise near the inner wall surface of the cylinder liner. Therefore, ignition while made successfully, the reduction of the NO X is an advantage of the exhaust gas recirculation system, is the improvement in output due to an increase in knocking limit boost pressure is obtained.
[Brief description of the drawings]
FIG. 1 is a graph showing a correlation between an exhaust gas NO x amount and a knocking limit supply air pressure with respect to an EGR rate when an exhaust gas recirculation gas engine is operated at a constant air-fuel ratio and at a constant rotational speed.
FIG. 2 is a schematic plan view showing an arrangement configuration of a spark plug side air supply port 3 and a liner side air supply port 4 in each cylinder.
FIG. 3 is a schematic side view of the same.
4 is a schematic view of intake and exhaust system piping of a gas engine having a first air supply system α for supplying air-fuel mixture A and a second air supply system β for supplying air-fuel mixture C. FIG.
FIG. 5 is a schematic view of an intake / exhaust system piping of a gas engine having a first air supply system α ′ for supplying air / fuel mixture A and a second air supply system β ′ for supplying EGR exhaust B;
[Explanation of symbols]
A Air-fuel mixture B EGR exhaust C EGR mixture (air-fuel mixture and EGR exhaust)
1 Cylinder Head 2 Cylinder Liner 3 Spark Plug Side Air Supply Port 4 Liner Side Air Supply Port 7 Spark Plug 16 Air Supply Manifold 17 EGR Pipe 25 Air Supply Manifold 34 Air Supply Manifold 35 EGR Pipe 40 Air Supply Manifold

Claims (2)

一部の冷却済み排気を給気系に導入し、空燃混合気に混合する排気再循環系を有する排気再循環式ガスエンジンにおいて、各気筒につき、点火プラグ付近に臨む点火プラグ側給気ポート３と、気筒壁面側に臨むライナ側給気ポート４とを設け、前者の点火プラグ側給気ポート３を空燃混合気のみを供給する給気系に、後者のライナ側給気ポート４を、空燃混合気と排気再循環系からの排気との混合気を供給する給気系に、それぞれ連結し、該点火プラグ側給気ポート３よりシリンダライナ２内の燃焼室に供給された給気は、シリンダヘッド１の中央付近に配設する点火プラグ７の電極付近に流れ、一方、ライナ側給気ポート４から燃焼室内への給気は、シリンダーライナ２の内壁面に沿って、燃焼室内にリング状に広がり、シリンダライナ２内の燃焼室内にて、中心部の点火プラグ側給気ポート３による給気圏と、その周囲のライナ側給気ポート４による給気圏と、二層に分かれた給気圏を形成することを特徴とする排気再循環式ガスエンジンの給気構造。In an exhaust gas recirculation type gas engine having an exhaust gas recirculation system that introduces some cooled exhaust gas into the air supply system and mixes it with the air-fuel mixture, the spark plug side air supply port facing the vicinity of the spark plug for each cylinder 3 and a liner side air supply port 4 facing the cylinder wall surface side, and the latter liner side air supply port 4 is provided to the air supply system for supplying only the air-fuel mixture to the former spark plug side air supply port 3. Are connected to an air supply system for supplying an air / fuel mixture and an exhaust gas from the exhaust gas recirculation system, and supplied to the combustion chamber in the cylinder liner 2 through the ignition plug side air supply port 3. The air flows in the vicinity of the electrode of the spark plug 7 disposed near the center of the cylinder head 1, while the air supplied from the liner side air supply port 4 into the combustion chamber burns along the inner wall surface of the cylinder liner 2. Cylinder liner 2 spreads in a ring shape in the room To at the combustion chamber, the air supply area by the spark plug side air supply port 3 of the central portion, and the air supply sphere by liner side air supply port 4 surrounding, and forming a supply air zone which is divided into two layers Exhaust gas recirculation gas engine air supply structure. 一部の冷却済み排気を給気系に導入し、空燃混合気に混合する排気再循環系を有する排気再循環式ガスエンジンにおいて、各気筒につき、点火プラグ付近に臨む点火プラグ側給気ポート３と、気筒壁面側に臨むライナ側給気ポート４とを設け、前者の点火プラグ側給気ポート３を空燃混合気のみを供給する給気系に、後者のライナ側給気ポート４を排気再循環系からの排気のみを供給する給気系に、それぞれ連結し、該点火プラグ側給気ポート３よりシリンダライナ２内の燃焼室に供給された給気は、シリンダヘッド１の中央付近に配設する点火プラグ７の電極付近に流れ、一方、ライナ側給気ポート４から燃焼室内への給気は、シリンダーライナ２の内壁面に沿って、燃焼室内にリング状に広がり、シリンダライナ２内の燃焼室内にて、中心部の点火プラグ側給気ポート３による給気圏と、その周囲のライナ側給気ポート４による給気圏と、二層に分かれた給気圏を形成することを特徴とする排気再循環式ガスエンジンの給気構造。In an exhaust gas recirculation type gas engine having an exhaust gas recirculation system that introduces some cooled exhaust gas into the air supply system and mixes it with the air-fuel mixture, the spark plug side air supply port facing the vicinity of the spark plug for each cylinder 3 and a liner side air supply port 4 facing the cylinder wall surface side, and the latter liner side air supply port 4 is provided to the air supply system for supplying only the air-fuel mixture to the former spark plug side air supply port 3. The supply air that is connected to an air supply system that supplies only exhaust gas from the exhaust gas recirculation system and is supplied from the ignition plug side air supply port 3 to the combustion chamber in the cylinder liner 2 is near the center of the cylinder head 1. On the other hand, the air supplied from the liner side air supply port 4 into the combustion chamber spreads in a ring shape in the combustion chamber along the inner wall surface of the cylinder liner 2. Inside the combustion chamber in 2, Parts and supply air zone by the spark plug side air supply port 3 of the air supply area by surrounding the liner side air supply port 4 thereof, the exhaust gas recirculation type gas engine and forming a supply air zone which is divided into two layers Air supply structure.
JP29199096A 1996-11-01 1996-11-01 Supply structure of exhaust gas recirculation gas engine Expired - Fee Related JP3759796B2 (en)

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