JP4550991B2 - Fuel / water injection internal combustion engine - Google Patents

Fuel / water injection internal combustion engine Download PDF

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JP4550991B2
JP4550991B2 JP2000349832A JP2000349832A JP4550991B2 JP 4550991 B2 JP4550991 B2 JP 4550991B2 JP 2000349832 A JP2000349832 A JP 2000349832A JP 2000349832 A JP2000349832 A JP 2000349832A JP 4550991 B2 JP4550991 B2 JP 4550991B2
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hydraulic oil
water
fuel
passage
pump
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JP2002155825A (en
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禎範 永江
龍夫 高石
裕幸 石田
建一 岩永
明 沼田
武 新井
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Mitsubishi Heavy Industries Ltd
Japan Petroleum Energy Center JPEC
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Mitsubishi Heavy Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B47/00—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines
    • F02B47/02—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines the substances being water or steam
    • 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
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/022—Adding fuel and water emulsion, water or steam
    • F02M25/0221—Details of the water supply system, e.g. pumps or arrangement of valves
    • F02M25/0225—Water atomisers or mixers, e.g. using ultrasonic waves
    • 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
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/022—Adding fuel and water emulsion, water or steam
    • F02M25/0227—Control aspects; Arrangement of sensors; Diagnostics; Actuators
    • 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
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/022—Adding fuel and water emulsion, water or steam
    • F02M25/0228—Adding fuel and water emulsion
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Public Health (AREA)
  • Water Supply & Treatment (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、燃料噴射ポンプから燃料通路を経て供給された高圧の燃料と、水供給ポンプから供給された水とを１つの燃料噴射弁から燃焼室内に噴射するように構成された燃料・水噴射内燃機関に関する。
【０００２】
【従来の技術】
デイーゼル機関においては、窒素酸化物（ＮＯｘ）低減のための有効な技術として、燃料噴射弁から燃料と水とを燃焼室内に噴射する燃料・水噴射デイーゼル機関が提案されている。
かかる技術の一つとして、本件出願人の出願に係る特許第２７７２１１４号の発明がある。図１０はかかる発明の構成を示し、図において、００１は燃料噴射ポンプ、３は燃料噴射弁、０１は燃料タンク、０２は燃料給油ポンプ、０１９は水タンク、０１８は水供給ポンプ、０１６は燃料噴射弁への水の供給を制御する制御弁、０２０は該制御弁０１６に開閉制御するコントロール装置である。
【０００３】
かかる燃料・水噴射デイーゼル機関において、水タンク０１９より水供給ポンプ０１８によって圧送された水は水供給管０１７を通り前記制御弁０１６に送られる。燃料噴射ポンプ００１の燃料吐出休止期間中に、前記コントロール装置０２０を介して前記制御弁０１６は開弁され、所定量の水を供給管０１５を介して前記燃料噴射弁３の水供給路０２１に送り込む。
このとき、燃料噴射ポンプ００１の逆止弁０７の開弁圧力Ｐｒ、前記水供給路０２１の燃料弁内逆止弁４の開弁圧力Ｐｐ、燃料噴射弁３の針弁０１１の開弁圧力Ｐ０とすると、
Ｐ０＞Ｐｒ、Ｐ０＞Ｐｐ
と設定されているため、前記燃料噴射弁３の水供給路０２１に供給された水は、燃料弁内逆止弁４を経て水通路０３０及び燃料と水との合流部０３１を通り燃料通路０２２内に流入する。
【０００４】
前記燃料通路０２２内の合流部０３１よりも燃料噴射ポンプ００１側にある燃料は該燃料噴射ポンプ００１の方向に高圧燃料管０８を通して押し戻される。その結果、前記燃料噴射弁３内には油溜部０１２及び該油溜部０１２から合流部０３１までの容積分の燃料で満たされ、該合流部０３１の上流側の燃料通路０２２には所定量の水が満たされ、さらにその上流側には再び燃料が満たされた層状状態となっている。
【０００５】
次いで、前記燃料噴射ポンプ００１の吐出が開始されて燃料噴射弁３内の燃料が圧縮され、圧力が上昇して該燃料噴射弁３の開弁圧力Ｐ０以上になると、針弁０１１が開かれ噴射が開始される。該噴射は、前記のように層状状態にある燃料及び水のうち、先ず燃料が噴射され、着火遅れ期間を経た後、燃焼を開始する。
引き続き水が燃焼中の先行燃料噴霧火炎をめがけて噴射される。このとき噴射される水も噴霧となってその内部に燃焼室内の空気を取り込んでいるため、先行噴射された燃料に空気を供給する形となって燃焼が活発化される。
そして、最後に残りの燃料が、先行した水噴霧の中に噴射され燃焼する。かかる燃料と水の噴射に伴う熱的影響により火炎の温度上昇が抑えられ、ＮＯｘの発生が抑制される。
【０００６】
【発明が解決しようとする課題】
図１０に示される特許第２７７２１１４号の発明においては、燃料噴射弁３に燃料と水とを層状に充填した後、高圧燃料により燃焼室内に押し出して噴射し、かかる燃料と水の噴射に伴う熱的影響により火炎の温度上昇が抑えられ、ＮＯｘの発生が抑制される。
しかしながら、かかる従来技術にあっては、燃料噴射弁３への注水量を、コントロール装置０２０により制御弁０１６のストローク及び開弁タイミングを変化させて制御しているため、所要の注水量及び注水タイミングを得るには該制御弁０１６の制御精度を高く維持することを要し、注水制御に困難を伴う。
また、かかる従来技術にあっては、前記のように、制御弁０１６を高い制御精度で以って制御操作することから、該制御弁０１６について高精度のタイミング制御を行うコントロール装置０２０、該制御弁０１６に操作力を付与するための作動油圧発生装置及び電気的駆動装置等の制御操作機器を必要とするため、装置コストが高騰する。等の問題点を有している。
【０００７】
本発明は、かかる従来技術の課題に鑑み、比較的簡単な制御方法で以って高精度の注水制御を行い得、かつ注水量の制御操作機器の装置コストが低減された燃料・水噴射内燃機関を提供することを目的とする。
【０００８】
【課題を解決するための手段】
本発明はかかる課題を解決するため、請求項１記載の発明として、燃料と水とを燃焼室に噴射する燃料・水噴射内燃機関であって、燃料噴射ポンプと連通する燃料通路と逆止弁とを内蔵しかつ該燃料通路と合流する水供給路とを有する燃料噴射弁と、前記燃料噴射ポンプが休止している間に所定量の水を前記水供給路を通じて合流部から前記燃料通路内に供給する水供給手段を備えるとともに、前記燃料噴射弁の油溜部の容積と前記合流部から油溜部までの容積の合計が全燃料噴射量の５％以上７５％以下である燃料・水噴射内燃機関において、
水供給ポンプから水通路を経た水が収容される水室内の圧力と該水室に対し注水ピストンを隔てて形成された作動油室内の圧力との圧力差により前記水を前記燃料噴射弁に圧送する、注水ピストン装置を前記水通路に設けるとともに、作動油入口通路から導入された作動油を加圧して前記注水ピストン装置の作動油室に作動油通路を経て送給する作動油ポンプを設け、
該注水ピストン装置は、ピストンが、シリンダからなる水室内を往復摺動自在に嵌合され、前記圧力差により移動せしめられる自由ピストンにて構成され、前記水室出口の前記水通路には前記燃料噴射弁に向かう流れのみを可能とする注水逆止弁が設けられるとともに、前記水室入口の前記水通路には該水室に向かう流れのみを可能とする注水逆止弁が設けられ、
更に前記作動油ポンプは、プランジャバレル内に往復摺動自在に嵌合されたプランジャの往復動によりプランジャ室内の作動油を前記注水ピストン装置に送出すると共に、該プランジャの有効行程を変化させることにより作動油送出流量を調整可能に構成し、且つ前記作動油ポンプに設けられた作動油カムのプロフィールを所要の形状に設定することにより、該作動油ポンプによる作動油の供給タイミングを調整可能に構成し、
前記作動油カムのプロフィール形状を、前記燃料噴射ポンプの燃料吐出休止期間中に、作動油ポンプの作動油カムの回転により作動油室に入った高圧の作動油を前記注水ピストンの作動油室側に作用させて前記注水ピストンの水室内に導入されていた水を燃料噴射弁に送り込ませるプロフィール形状に設定したことを特徴とする燃料・水噴射内燃機関を提案する。
【００１１】
請求項２ないし３記載の発明は、ジャーク式ポンプからなる前記作動油ポンプの具体的構成に係り、請求項２の発明においては、ジャーク式ポンプからなる前記作動油ポンプは、
前記プランジャ室の圧力により開弁して該プランジャ室内の作動油を前記注水ピストン装置に送出する作動油吐出弁と、前記プランジャ室と前記作動油通路とを前記作動油吐出弁をバイパスする戻り通路に設けられて該作動油通路からプランジャに向かう流れのみを可能とする作動油逆止弁とを備えてなる。
【００１２】
請求項３の発明においては、前記ジャーク式ポンプからなる前記作動油ポンプは、前記プランジャ室と作動油通路との間に、作動油通路面積を縮小する絞り機構を設けてなる。
【００１３】
請求項４記載の発明は、請求項１において、前記注水ピストン装置の作動油室と前記作動油ポンプへの作動油入口管に作動油を供給するための作動油タンクとを接続する作動油戻り通路、並びに機関回転数、機関負荷等の機関運転条件により該作動油戻り通路を開閉する電磁弁を設けて、前記作動油タンクから作動油入口通路、作動油ポンプ、作動油通路、注水ピストン装置、電磁弁、及び作動油戻り通路をこの順に経て前記作動油タンクに至る作動油の循環路を形成したことを特徴とする。
【００１４】
かかる発明によれば、通常用いられているジャーク式燃料噴射ポンプ等の、作動油供給タイミング及び作動油流量を調整可能な作動油ポンプにより、作動油供給タイミング及び作動油流量を調整して、作動油を注水ピストン装置に供給あるいはこれを遮断することにより、該注水ピストン装置を作動させ、該注水ピストン装置によって燃料噴射弁への水の供給、遮断をなさしめるようにしたので、ジャーク式燃料噴射ポンプと同様な構造の作動油ポンプの作動油供給タイミング及び作動油流量を調整するのみという比較的簡単な制御手段で、注水量及び注水タイミングを高精度で制御できる。
【００１５】
また、前記のように、ジャーク式燃料噴射ポンプと同様な作動油供給タイミング及び作動油流量を調整可能な作動油ポンプと、シリンダ内にフリーピストン構造の注水ピストンを嵌合した簡単な構造の注水ピストン装置とを組み合わせて燃料噴射弁への水の供給システムを構成したので、従来技術のような電子制御の制御弁、該制御弁のタイミング制御を行うコントロール装置、該制御弁に操作力を付与するための作動油圧発生装置及び電気的駆動装置等の格別な制御操作機器が不要となり、きわめて簡単かつ低コストの装置で以って、燃料・水噴射システムを構成することができる。
【００１６】
また請求項３の発明によれば、絞り機構によって、注水ピストン装置の注水ピストンの振動等を伴う急激な移動を緩和することができ、これによって、注水ピストン装置への作動油の供給が脈動等を伴うことなくなされることとなり、注水ピストン装置による水の供給動作が安定化される。
また、簡単な構造の絞り機構を設ければ済むので、構造が簡単化され低コストとなる。
【００１７】
さらに請求項４の発明によれば、前記作動油タンクから作動油入口通路、作動油ポンプ、作動油通路、注水ピストン装置、電磁弁、及び作動油戻り通路をこの順に経て前記作動油タンクに至る作動油の循環路を形成し、該循環路の作動油戻り通路を電磁弁により機関運転条件に適応したタイミングで開閉するので、作動油が毎サイクル作動油タンクに戻されて該作動油タンクにて冷却されることとなり、作動油の温度上昇が抑制されるとともに、注水ピストン装置における作動油の残圧が完全に除去されて次のステップにおける水の供給が抵抗なくスムーズになされる。これにより、作動油ポンプ及び注水ピストン装置による水の供給作用が安定化される。
【００１８】
【発明の実施の形態】
以下、本発明を図に示した実施例を用いて詳細に説明する。但し、この実施例に記載される構成部品の寸法、材質、形状、その相対配置などは特に特定的な記載が無い限り、この発明の範囲をそれのみに限定する趣旨ではなく単なる説明例に過ぎない。
【００１９】
図１は本発明の第１実施例に係るデイーゼル機関の燃料・水噴射システムの構成図、図２は第２実施例に係るデイーゼル機関の燃料・水噴射システムの構成図、
図３は第３実施例に係るデイーゼル機関の燃料・水噴射システムの構成図、図４は注水ピストン装置の断面図、図５は前記第１実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図、図６は前記第２実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図、図７は前記第３実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図である。図８は前記第１ないし第３実施例における燃料噴射弁の断面図である。図９は前記第１ないし第３実施例の作用説明図である。
【００２０】
図１に示される第１実施例において、１は燃料噴射ポンプで、図５に示されるような公知のジャーク式燃料噴射ポンプからなる。３はその詳細が図８に示されている燃料噴射弁である。また、６はその詳細が図８に示されている作動油ポンプである。
１３は燃料タンク、３１は該燃料タンク１３と前記燃料噴射ポンプ１の燃料入口とを接続する燃料供給管、１２は前記燃料供給管３１に設けられ燃料タンク１３内の燃料を燃料噴射ポンプ１に送給する燃料供給ポンプである。２は前記燃料噴射ポンプ１からの高圧燃料出口と前記燃料噴射弁３の燃料入口とを接続する高圧燃料管である。
【００２１】
５は注水ピストン装置であり詳細は後述する。１１は注水タンク、３４は該注水タンク１１と前記注水ピストン装置５の水入口とを接続する注水管、１０は該注水管３４に設けられて注水タンク１１内の水を注水ピストン装置５に送給する注水ポンプである。３２は前記注水ピストン装置５の水出口と前記燃料噴射弁３の水入口とを接続する注水管である。
１５は作動油タンク、３３は該作動油タンク１５と前記作動油ポンプ６の作動油入口とを接続する作動油入口管、１４は該作動油入口管３３に設けられ作動油タンク１５内の作動油を作動油ポンプ６に送給する作動油供給ポンプである。また、３５は前記作動油ポンプ６の作動油出口と前記注水ピストン装置５の作動油入口とを接続する作動油管である。
【００２２】
前記燃料噴射ポンプ及び作動油ポンプの詳細を示す図５において、１は燃料噴射ポンプで次のように構成されている。
２５はプランジャバレル２４の内周に往復摺動自在に嵌合されたプランジャ、１７は燃料吐出弁、１８は燃料逆止弁であり、該プランジャ２５の上動によりプランジャ室２５ａ内の燃料を高圧に加圧し、該高圧燃料が前記燃料吐出弁１７を押し開いて前記高圧燃料管２に吐出されるようになっている。
該燃料噴射ポンプ１は、前記のように公知のジャーク式燃料噴射ポンプからなり、燃料調整ラック（図示省略）の往復動により前記プランジャ２５の有効行程を変化させることにより、高圧燃料管２に吐出される燃料噴射量を調整するように構成されている。１３は燃料タンク、３１は燃料供給管、１２は燃料供給ポンプである（何れも図１参照）。
１１０は前記燃料調整ラックの位置即ち燃料噴射量を検出するラック位置検出器で、該ラック位置検出器１１０からの燃料調整ラック位置（燃料噴射量）の検出信号は後述するコントローラ１０６に入力される。１１１は機関回転数を検出する回転数検出器で、該回転数検出器１１１からの機関回転数の検出信号も前記コントローラ１０６に入力される。
【００２３】
６は作動油ポンプで次のように構成されている。
１０１はポンプケース、１０２は該ポンプケース１０１の内部に固着されたプランジャバレル、１０３は該プランジャバレル１０２の内周に往復摺動自在に嵌合されたプランジャ、１０３ａは該プランジャバレル１０２内のプランジャ１０３上面に臨んで形成されたプランジャ室、０１１１は前記プランジャバレル１０２に設けられた給油孔である。１１３は前記プランジャ１０３の下端に固定されたタペット、１１５は該タペット１１３に支持されたプランジャスプリングで、該タペット１１３を図１に示す作動油カム１１４に押圧している。
８は前記プランジャ室１０３ａの出口側に設けられた作動油吐出弁で、前記燃料噴射ポンプ１の燃料吐出弁１７と同様な構造を有する。７は作動油逆止弁で、前記燃料噴射ポンプ１の燃料逆止弁１８と同様な構造を有し、
前記燃料吐出弁１７が設けられている吐出弁室と前記プランジャ室１０３ａとを接続する戻り通路に設けられている。
【００２４】
１０９は前記プランジャ１０３の回転機構１１２に噛合される吐出流量調整用のラック、１０８は該ラック１０９に噛合されるピニオンである。１０７はアクチュエータで、後述するコントローラ１０６からの制御信号により作動し、その出力端が前記ピニオン１０８に連結されており、前記アクチュエータ１０７の操作力によりピニオン１０８が回転して前記ラック１０９を往復動せしめ、該ラック１０９に噛合しているプランジャ１０３の回転機構１１２を介してプランジャ１０３を回転させることによりその有効行程を変化させて、作動油管３５を通して前記注水ピストン装置５への作動油流量を調整するように構成されている。
１０６はコントローラで、前記回転数検出器１１１からの機関回転数の検出信号及び前記ラック位置検出器１１０からの燃料調整ラック位置（燃料噴射量）の検出信号が入力され、これらの検出信号に基づき機関の運転状態に対応する作動油流量を算出し、前記アクチュエータ１０７に該作動油流量に相当する操作信号を出力する。
また、１５は作動油タンク、３３は作動油入口管、１４は作動油ポンプである（何れも図１参照）。
【００２５】
前記燃料噴射弁３の詳細を示す図８において、０９は本体、０３３はノズルチップ、０１０は該ノズルチップ０３３の先端部に複数穿孔された噴孔、０１１は該ノズルチップ０３３内に往復摺動可能に嵌合された針弁、０１４は該針弁０１１の開弁圧力を設定する針弁ばね、０１２は前記針弁０１１の先端部が臨む油溜部である。０２２は入口端が前記高圧燃料管２に接続され出口端が前記油溜部０１２に接続される燃料通路である。０２１は入口端が前記注水ピストン装置５からの注水管３２に接続され出口端が前記ノズルチップ０３３下部に形成された水通路０３０に接続される水供給通路である。また、前記水通路０３０の出口端は前記燃料通路０２２の下部に合流されて合流部０３１を形成している。
【００２６】
４は前記水供給通路０２１に設けられた燃料弁内逆止弁で、前記注水管３２側から合流部０３１側に向かう流れのみを許容するように、かつその開弁圧力Ｐｐを前記針弁０１１の開弁圧力Ｐ０よりも小さく構成されている。
以上に示された燃料噴射弁３の基本構造は図１０に示される特許第２７７２１１４号の発明における燃料噴射弁と同様である。
【００２７】
前記注水ピストン装置の詳細を示す図４において、５１はシリンダ、５２は該シリンダ５１内に往復摺動自在に嵌合された注水ピストン、５６は該注水ピストン５２の外周部に嵌挿されたシールリングである。前記シリンダ５１内は、前記注水ピストン５２により水室５３と作動油室５４とに区画されており、該注水ピストン５２は、前記作動油室５４と水室５３との圧力差により移動せしめられる自由ピストンにて構成される。
【００２８】
前記作動油室５４には、前記作動油ポンプ６からの作動油が前記作動油管３５及び作動油入口５５を経て導入されるようになっている。９は入口側の注水逆止弁で、前記注水管３４に接続され該注水管３４側から水室５３に向かう流れのみを許容するように、球状の弁体９ａを所定の開弁圧力に設定されたばね９ｂにて押圧して構成されている。また、１６は出口側の注水逆止弁で、前記注水管３２に接続され前記水室５３側から該注水管３２に向かう流れのみを許容するように、球状の弁体１６ａを所定の開弁圧力に設定されたばね１６ｂにて押圧して構成されている。
【００２９】
かかる構成からなる燃料・水噴射システムを備えたデイーゼル機関の運転時において、注水タンク１１内の水が注水ポンプ１０によって加圧されて、前記注水ピストン装置５の水室５３内の圧力が作動油室５４側の圧力つまり作動油ポンプ６の作動油逆止弁７の開弁圧力よりも大きくなると、前記注水タンク１１より注水ポンプ１０によって圧送された水は注水管３４を通り前記注水逆止弁９を押し開けて前記注水ピストン装置の水室５３に導入される。
一方、作動油ポンプ６においては、作動油カム１１４がリフトせず、プランジャ１０３が下方にあるとき、作動油タンク１５内の作動油が作動油供給ポンプ１４により作動油入口管３３を及び給油孔０１１１を経てプランジャ室１０３ａに導入される。
そして、前記燃料噴射ポンプ１の燃料吐出休止期間中に、作動油ポンプ６の作動油カム１１４の回転によりタペット１１３及びプランジャ１０３が押し上げられると、プランジャ室１０３ａ内の作動油は該プランジャ１０３により加圧されて作動油吐出弁８を押し上げて作動油管３５を通り注水ピストン装置５の作動油室５４に入る。
【００３０】
該作動油室５４に入った高圧の作動油は注水ピストン５２の作動油室側５２ｂに作用し、該作動油の圧力と水室側５２ａに作用する水の圧力との圧力差により、
前記注水ピストン５２は図１、４の左方つまり水室５３の容積を縮小する方向に移動せしめられ、これにより該水室５３内に導入されていた水は注水逆止弁１６を押し開け、注水管３２を通って燃料噴射弁３の水供給路０２１に送り込まれる。
このとき、燃料噴射ポンプ１の燃料逆止弁１８の開弁圧力Ｐｒ、前記水供給路０２１の燃料弁内逆止弁４の開弁圧力Ｐｐ、燃料噴射弁３の針弁０１１の開弁圧力Ｐ０とすると、
Ｐ０＞Ｐｒ、Ｐ０＞Ｐｐ
と設定されているため、前記燃料噴射弁３の水供給路０２１に供給された水は、燃料弁内逆止弁４を経て水通路０３０及び燃料と水との合流部０３１を通り燃料通路０２２内に流入する。
【００３１】
前記燃料通路０２２内の合流部０３１よりも燃料噴射ポンプ１側にある燃料は該燃料噴射ポンプ１の方向に高圧燃料管２を通して押し戻される。その結果、前記燃料噴射弁３内には油溜部０１２及び該油溜部０１２から合流部０３１までの容積分の燃料で満たされ、該合流部０３１の上流側の燃料通路０２２には所定量の水が満たされ、さらにその上流側には再び燃料が満たされた層状状態となっている。
次いで、図９の“燃料噴射”状態に示すように、前記燃料噴射ポンプ１の吐出が開始されて燃料噴射弁３内の燃料が圧縮され、圧力が上昇して該燃料噴射弁３の開弁圧力Ｐ０以上になると、針弁０１１が開かれ噴射が開始される。該噴射は、前記のように層状状態にある燃料及び水のうち、先ず燃料が噴射され、着火遅れ期間を経た後、燃焼を開始する。引き続き水が燃焼中の先行燃料噴霧火炎をめがけて噴射される。このとき噴射される水も噴霧となってその内部に燃焼室内の空気を取り込んでいるため、先行噴射された燃料に空気を供給する形となって燃焼が活発化される。
そして、最後に残りの燃料が、先行した水噴霧の中に噴射され燃焼する。かかる燃料と水の噴射に伴う熱的影響により火炎の温度上昇が抑えられ、ＮＯｘの発生が抑制される。
【００３２】
前記作動時において、前記コントローラ１０６には、前記回転数検出器１１１からの機関回転数の検出信号及び前記ラック位置検出器１１０からの燃料調整ラック位置（燃料噴射量）の検出信号が入力される。そして、該コントローラ１０６は、これらの検出信号に基づき機関の運転状態に対応する作動油流量を算出し、前記アクチュエータ１０７に該作動油流量に相当する操作信号を出力する。
該アクチュエータ１０７の操作力によりピニオン１０８が回転して前記ラック１０９が往復動せしめられ、該ラック１０９に噛合しているプランジャ１０３の回転機構１１２を介してプランジャ１０３を回転することによりその有効行程が変化し、前記注水ピストン装置５への作動油流量が調整される。これにより、該作動油によって前記燃料噴射弁３に供給される水の量が調整される。
また、前記作動油ポンプ６に設けられた作動油カム１１４のプロフィールを所要の形状に設定することにより、該作動油ポンプ６による作動油の供給タイミングを調整し、これにより、前記注水ピストン装置５による燃料噴射弁３への水の供給タイミングを調整することができる。
【００３３】
かかる実施例によれば、通常用いられているジャーク式燃料噴射ポンプと同様な構造の作動油ポンプ６により、作動油供給タイミング及び作動油流量を調整して、作動油を注水ピストン装置５に供給あるいはこれを遮断することにより、該注水ピストン装置５を作動させ、該注水ピストン装置５によって燃料噴射弁３への水の供給、遮断をなさしめるようにしたので、ジャーク式燃料噴射ポンプと同様な構造の作動油ポンプ６の作動油供給タイミング及び作動油流量を調整するのみという比較的簡単な制御手段で、注水量及び注水タイミングを高精度で制御できる。
また、前記のように、ジャーク式燃料噴射ポンプと同様な構造の作動油ポンプ６と、シリンダ５１内にフリーピストン構造の注水ピストン５２を嵌合した簡単な構造の注水ピストン装置５とを組み合わせて燃料噴射弁３への水の供給システムを構成したので、従来技術のような格別な電子制御装置が不要となり、きわめて簡単かつ低コストの装置で以って、燃料・水噴射システムを構成することができる。
【００３４】
図２及び図６に示される第２実施例においては、前記作動油ポンプ６の吐出部において、前記第１実施例における作動油吐出弁８及び作動油逆止弁７を除去し、これに代えて絞り機構４０を設けている。
かかる実施例によれば、作動油ポンプ６と注水ピストン装置５との間の作動油通路に絞り機構４０を設けたので、該絞り機構４０によって、前記注水ピストン装置５の注水ピストン５２の振動等を伴う急激な移動を緩和することができ、これによって、注水ピストン装置５への作動油の供給が脈動等を伴うことなくなされることとなり、注水ピストン装置５による水の供給動作が安定化される。
また、第１実施例のような作動油吐出弁８及び作動油逆止弁７に比べて、簡単な構造の絞り機構４０を設ければ済むので、構造が簡単化され低コストとなる。
その他の構成は前記第１実施例と同様であり、これと同一の部材は同一の符号で示す。
【００３５】
図３及び図６に示される第３実施例において、３６は前記注水ピストン装置５の作動油室５４と前記作動油タンク１５とを接続する作動油戻り管、３００は該作動油戻り管３６の管路を開閉する電磁弁であり、該作動油戻り管３６及び電磁弁３００を設けることにより、 前記作動油タンク１５から作動油入口管３３、作動油供給ポンプ１４、作動油入口管３３、作動油ポンプ６、作動油管３５、注水ピストン装置５、電磁弁３００、及び作動油戻り管３６をこの順に経て前記作動油タンク１５に至る作動油の循環路を形成している。
【００３６】
３０１は電磁弁駆動装置で、前記第１、第２実施例と同様にクランク軸、カム軸等の回転軸３０３の回転数検出信号が回転数検出器１１１から入力されるとともに、機関の負荷あるいは出力等の機関負荷の検出信号が負荷検出器３０４から入力される。
そして該電磁弁駆動装置３０１においては、前記作動油ポンプ６から作動油が注水ピストン装置５の作動油室５４に供給され、該注水ピストン装置５の注水ピストン５２が図４の左動して水室５３内の水を前記燃料噴射弁３に送出した後、前記電磁弁３００を開き、作動油室５４内の作動油を作動油戻り管３６を介して作動油タンク１５に戻す。
また、前記電磁弁駆動装置３０１においては、前記回転数検出信号及び機関負荷の検出信号に基づき機関の運転条件に適応した開閉タイミングでもって電磁弁３００を開閉操作する。
かかる操作により、作動油室５４内の作動油の残圧は完全に除去され、次のステップにおける水室５３内への水の供給が抵抗なくスムーズになされる。
【００３７】
かかる実施例によれば、前記作動油タンク１５から、作動油供給ポンプ１４、作動油ポンプ６、注水ピストン装置５、電磁弁３００、及び作動油戻り管３６をこの順に経て前記作動油タンク１５に至る作動油の循環路を形成し、該循環路の作動油戻り通路を電磁弁３００により機関運転条件に適応したタイミングで開閉するので、作動油が毎サイクル作動油タンク１５に戻されて該作動油タンク１５にて冷却されることとなり、作動油の温度上昇が抑制されるとともに、作動油室５４内の作動油の残圧が完全に除去されて次のステップにおける水室５３内への水の供給が抵抗なくスムーズになされる。これにより、作動油ポンプ６及び注水ピストン装置５による水の供給作用が安定化される。
【００３８】
【発明の効果】
以上記載のごとく本発明によれば、作動油ポンプにより作動油供給タイミング及び作動油流量を調整して、作動油を注水ピストン装置に供給あるいはこれを遮断することにより、該注水ピストン装置によって燃料噴射弁への水の供給、遮断をなさしめるようにしたので、通常用いられているジャーク式燃料噴射ポンプと同様な構造の作動油ポンプの作動油供給タイミング及び作動油流量を調整するのみという比較的簡単な制御手段で、注水量及び注水タイミングを高精度で制御できる。
【００３９】
また、前記のように、作動油供給タイミング及び作動油流量を調整可能な作動油ポンプと、シリンダ内にフリーピストン構造の注水ピストンを嵌合した簡単な構造の注水ピストン装置とを組み合わせて燃料噴射弁への水の供給システムを構成したので、従来技術のような電子制御による格別な制御操作機器が不要となり、きわめて簡単かつ低コストの装置で以って、燃料・水噴射システムを構成することができる。
【００４０】
また、請求項３のように構成すれば、絞り機構によって、注水ピストン装置の注水ピストンの振動等を伴う急激な移動を緩和することができ、これによって、注水ピストン装置への作動油の供給が脈動等を伴うことなくなされることとなり、注水ピストン装置による水の供給動作が安定化される。
また、簡単な構造の絞り機構を設ければ済むので、構造が簡単化され低コストとなる。
【００４１】
さらに、請求項４のように構成すれば、前記作動油タンクから、作動油ポンプ、注水ピストン装置、電磁弁、及び作動油戻り通路をこの順に経て前記作動油タンクに至る作動油の循環路を形成し、該循環路の作動油戻り通路を電磁弁により機関運転条件に適応したタイミングで開閉するので、作動油が毎サイクル作動油タンクに戻されて該作動油タンクにて冷却されることとなり、作動油の温度上昇が抑制されるとともに、注水ピストン装置における作動油の残圧が完全に除去されて次のステップにおける水の供給が抵抗なくスムーズになされる。これにより、作動油ポンプ及び注水ピストン装置による水の供給作用が安定化される。
【００４２】
以上、要するに本発明によれば、作動油供給タイミング及び作動油流量を調整可能な作動油ポンプと、シリンダ内にフリーピストン構造の注水ピストンを嵌合した簡単な構造の注水ピストン装置とを組み合わせるという、比較的簡単な制御手段で以って高精度の注水量及び注水タイミング制御を行い得るとともに、注水量の制御操作機器の装置コストが低減された燃料・水噴射内燃機関を提供することができる。
【図面の簡単な説明】
【図１】 本発明の第１実施例に係るデイーゼル機関の燃料・水噴射システムの構成図である。
【図２】 第２実施例に係るデイーゼル機関の燃料・水噴射システムの構成図である。
【図３】 第３実施例に係るデイーゼル機関の燃料・水噴射システムの構成図である。
【図４】 注水ピストン装置の断面図である。
【図５】 前記第１実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図である。
【図６】 前記第２実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図である。
【図７】 前記第３実施例における燃料噴射ポンプ及び作動油ポンプの構造を示す断面図である。
【図８】 前記第１ないし第３実施例における燃料噴射弁の断面図である。
【図９】 前記第１ないし第３実施例の作用説明図である。
【図１０】 従来技術を示す要部構成図である。
【符号の説明】
１ 燃料噴射ポンプ
２ 高圧燃料管
３ 燃料噴射弁
４ 燃料弁内逆止弁
５ 注水ピストン装置
６ 作動油ポンプ
７ 作動油逆止弁
８ 作動油吐出弁
９ 注水逆止弁
１０ 注水ポンプ
０１０ 噴孔
１１ 注水タンク
０１１ 針弁
１２ 燃料供給ポンプ
０１２ 油溜部
１３ 燃料タンク
１４ 作動油供給ポンプ
１５ 作動油タンク
１６ 注水逆止弁
１７ 燃料吐出弁
１８ 燃料逆止弁
２４ プランジャバレル
２５ プランジャ
３２ 注水管
０３１ 合流部
３４ 注水管
３５ 作動油管
３６ 作動油戻り管
４０ 絞り機構
５１ シリンダ
５２ 注水ピストン
５３ 水室
５４ 作動油室
１０２ プランジャバレル
１０３ プランジャ
１０３ａ プランジャ室
１０６ コントローラ
１０７ アクチュエータ
１０９ ラック
１１０ ラック位置検出器
１１１ 回転数検出器
１１４ 作動油カム
３００ 電磁弁
３０１ 電磁弁駆動装置
３０４ 負荷検出器[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a fuel / water injection system configured to inject a high-pressure fuel supplied from a fuel injection pump through a fuel passage and water supplied from a water supply pump into a combustion chamber from one fuel injection valve. The present invention relates to an internal combustion engine.
[0002]
[Prior art]
In the diesel engine, as an effective technique for reducing nitrogen oxide (NOx), a fuel / water injection diesel engine that injects fuel and water from a fuel injection valve into a combustion chamber has been proposed.
As one of such techniques, there is an invention of Japanese Patent No. 2772114 relating to the application of the present applicant. FIG. 10 shows the configuration of the invention, in which 001 is a fuel injection pump, 3 is a fuel injection valve, 01 is a fuel tank, 02 is a fuel oil pump, 019 is a water tank, 018 is a water supply pump, and 016 is a fuel. A control valve 020 that controls the supply of water to the injection valve is a control device that controls opening and closing of the control valve 016.
[0003]
In such a fuel / water injection diesel engine, water pumped from the water tank 019 by the water supply pump 018 is sent to the control valve 016 through the water supply pipe 017. During the fuel discharge suspension period of the fuel injection pump 001, the control valve 016 is opened via the control device 020, and a predetermined amount of water is supplied to the water supply path 021 of the fuel injection valve 3 via the supply pipe 015. Send it in.
At this time, the valve opening pressure Pr of the check valve 07 of the fuel injection pump 001, the valve opening pressure Pp of the check valve 4 in the fuel valve of the water supply path 021 and the valve opening pressure P of the needle valve 011 of the fuel injection valve 3 are shown. 0 Then,
P 0 > Pr, P 0 > Pp
Therefore, the water supplied to the water supply passage 021 of the fuel injection valve 3 passes through the water passage 030 and the fuel-water junction portion 031 through the fuel valve check valve 4 and the fuel passage 022. Flows in.
[0004]
The fuel that is closer to the fuel injection pump 001 than the junction 031 in the fuel passage 022 is pushed back through the high-pressure fuel pipe 08 toward the fuel injection pump 001. As a result, the fuel injection valve 3 is filled with an oil reservoir 012 and a volume of fuel from the oil reservoir 012 to the merging portion 031, and a predetermined amount is placed in the fuel passage 022 upstream of the merging portion 031. It is in a layered state where the water is filled and the upstream side is filled with fuel again.
[0005]
Next, the discharge of the fuel injection pump 001 is started, the fuel in the fuel injection valve 3 is compressed, the pressure rises, and the valve opening pressure P of the fuel injection valve 3 is increased. 0 If it becomes above, needle valve 011 will be opened and injection will be started. In the injection, the fuel is first injected from the fuel and water in the layered state as described above, and after the ignition delay period, the combustion starts.
Subsequently, water is injected over the burning fuel spray flame. Since the water injected at this time is also sprayed and the air in the combustion chamber is taken into the inside thereof, the combustion is activated by supplying air to the previously injected fuel.
Finally, the remaining fuel is injected into the preceding water spray and burned. The thermal effect accompanying the injection of fuel and water suppresses the rise in flame temperature and suppresses the generation of NOx.
[0006]
[Problems to be solved by the invention]
In the invention of Japanese Patent No. 2772114 shown in FIG. 10, the fuel injection valve 3 is filled with fuel and water in layers, and then injected into the combustion chamber by high-pressure fuel and injected, and the heat accompanying the injection of the fuel and water The increase in the temperature of the flame is suppressed by the influence of the target, and the generation of NOx is suppressed.
However, in this prior art, the water injection amount to the fuel injection valve 3 is controlled by the control device 020 by changing the stroke of the control valve 016 and the valve opening timing. Therefore, it is necessary to maintain a high control accuracy of the control valve 016, and water injection control is difficult.
Further, in this conventional technique, as described above, since the control valve 016 is controlled with high control accuracy, the control device 020 that performs highly accurate timing control on the control valve 016, the control device Since a control operating device such as an operating hydraulic pressure generator and an electric drive device for applying an operating force to the valve 016 is required, the device cost increases. And so on.
[0007]
In view of the problems of the prior art, the present invention is capable of performing highly accurate water injection control with a relatively simple control method, and is a fuel / water-injection internal combustion engine in which the device cost of the operation device for controlling the water injection amount is reduced. The purpose is to provide an institution.
[0008]
[Means for Solving the Problems]
In order to solve this problem, the present invention provides a fuel / water-injection internal combustion engine that injects fuel and water into a combustion chamber according to the first aspect of the present invention, wherein the fuel passage communicates with a fuel injection pump and a check valve. And a fuel injection valve having a water supply passage that merges with the fuel passage, and a predetermined amount of water from the joining portion through the water supply passage into the fuel passage while the fuel injection pump is stopped. The fuel / water is provided with water supply means for supplying to the fuel, and the sum of the volume of the oil reservoir of the fuel injection valve and the volume from the junction to the oil reservoir is not less than 5% and not more than 75% of the total fuel injection amount In an injection internal combustion engine,
The water is pumped to the fuel injection valve by the pressure difference between the pressure in the water chamber in which water passing through the water passage from the water supply pump is accommodated and the pressure in the hydraulic oil chamber formed across the water injection piston with respect to the water chamber. Providing a water injection piston device in the water passage, and providing a hydraulic oil pump that pressurizes the hydraulic oil introduced from the hydraulic oil inlet passage and feeds it to the hydraulic oil chamber of the water injection piston device through the hydraulic oil passage;
The water injection piston device has a piston , It is composed of a free piston that is slidably fitted in a water chamber composed of a cylinder and is moved by the pressure difference, and allows only a flow toward the fuel injection valve in the water passage at the water chamber outlet. A water check valve is provided, and the water passage at the water chamber inlet is provided with a water check valve that allows only a flow toward the water chamber,
Further, the hydraulic oil pump sends hydraulic oil in the plunger chamber to the water injection piston device by reciprocating movement of a plunger that is slidably reciprocated in the plunger barrel, and changes the effective stroke of the plunger. The hydraulic oil delivery flow rate is adjustable, and the hydraulic oil cam profile provided in the hydraulic oil pump is set to a required shape to adjust the hydraulic oil supply timing by the hydraulic oil pump. And
The profile shape of the hydraulic oil cam is set so that the high-pressure hydraulic oil that has entered the hydraulic oil chamber by the rotation of the hydraulic oil cam of the hydraulic oil pump during the fuel discharge suspension period of the fuel injection pump is the hydraulic oil chamber side of the water injection piston. The profile shape is set so that the water introduced into the water chamber of the water injection piston is fed into the fuel injection valve. A fuel / water-injection internal combustion engine is proposed.
[0011]
Claim 2 to 3 The described invention The Consists of Jerk type pump Said Claims relating to the specific configuration of the hydraulic oil pump 2 In the invention of The Consists of Jerk type pump Said The hydraulic oil pump
A hydraulic oil discharge valve that opens by the pressure in the plunger chamber and sends hydraulic oil in the plunger chamber to the water injection piston device; and a return passage that bypasses the hydraulic oil discharge valve between the plunger chamber and the hydraulic oil passage And a hydraulic oil check valve that allows only a flow from the hydraulic oil passage toward the plunger.
[0012]
Claim 3 In the present invention, the jerk type pump is used. Said The hydraulic oil pump is provided with a throttle mechanism for reducing the hydraulic oil passage area between the plunger chamber and the hydraulic oil passage.
[0013]
Claim 4 The invention described in claim 1 is a hydraulic oil return passage connecting the hydraulic oil chamber of the water injection piston device and the hydraulic oil tank for supplying hydraulic oil to the hydraulic oil inlet pipe to the hydraulic oil pump, and An electromagnetic valve that opens and closes the hydraulic oil return passage according to engine operating conditions such as engine speed, engine load, etc. is provided, and from the hydraulic oil tank, a hydraulic oil inlet passage, a hydraulic oil pump, a hydraulic fluid passage, a water injection piston device, a solenoid valve And a hydraulic oil circulation path that reaches the hydraulic oil tank through the hydraulic oil return passage in this order.
[0014]
According to this invention, the hydraulic oil supply timing and the hydraulic oil flow rate are adjusted by the hydraulic oil pump capable of adjusting the hydraulic oil supply timing and the hydraulic oil flow rate, such as a commonly used jerk type fuel injection pump. The oil injection piston device is operated by supplying or shutting off the oil to the water injection piston device, and the water injection piston device supplies and shuts off the water to the fuel injection valve. The amount of water injection and the timing of water injection can be controlled with high accuracy by a relatively simple control means that only adjusts the hydraulic oil supply timing and hydraulic oil flow rate of the hydraulic oil pump having the same structure as the pump.
[0015]
In addition, as described above, water injection with a simple structure in which a hydraulic oil pump capable of adjusting the hydraulic oil supply timing and hydraulic oil flow rate, similar to the jerk type fuel injection pump, and a free piston structure water injection piston is fitted in the cylinder. Since the water supply system to the fuel injection valve is configured in combination with the piston device, the electronically controlled control valve as in the prior art, the control device for controlling the timing of the control valve, and operating force applied to the control valve Therefore, special control operation equipment such as a working hydraulic pressure generator and an electric drive device are not required, and the fuel / water injection system can be configured with an extremely simple and low-cost device.
[0016]
And claims 3 According to the invention, the throttling mechanism can alleviate a rapid movement accompanied by vibration of the water injection piston of the water injection piston device, so that the supply of hydraulic oil to the water injection piston device is not accompanied by pulsation or the like. As a result, the water supply operation by the water injection piston device is stabilized.
Further, since it is only necessary to provide a diaphragm mechanism having a simple structure, the structure is simplified and the cost is reduced.
[0017]
Further claims 4 According to the invention, the circulation of the working oil from the working oil tank to the working oil tank through the working oil inlet passage, the working oil pump, the working oil passage, the water injection piston device, the solenoid valve, and the working oil return passage in this order. Since the hydraulic fluid return passage of the circulation passage is opened and closed at a timing adapted to the engine operating conditions by a solenoid valve, the hydraulic oil is returned to the hydraulic oil tank every cycle and cooled in the hydraulic oil tank As a result, the temperature rise of the hydraulic oil is suppressed, and the residual pressure of the hydraulic oil in the water injection piston device is completely removed, so that water is smoothly supplied in the next step without resistance. Thereby, the water supply action by the hydraulic oil pump and the water injection piston device is stabilized.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are merely illustrative examples and not intended to limit the scope of the present invention unless otherwise specified. Absent.
[0019]
FIG. 1 is a configuration diagram of a fuel / water injection system for a diesel engine according to a first embodiment of the present invention. FIG. 2 is a configuration diagram of a fuel / water injection system for a diesel engine according to a second embodiment.
FIG. 3 is a block diagram of a fuel / water injection system for a diesel engine according to a third embodiment, FIG. 4 is a cross-sectional view of a water injection piston device, and FIG. 5 shows the structures of a fuel injection pump and a hydraulic oil pump in the first embodiment. FIG. 6 is a sectional view showing the structure of the fuel injection pump and hydraulic oil pump in the second embodiment, and FIG. 7 is a sectional view showing the structure of the fuel injection pump and hydraulic oil pump in the third embodiment. is there. FIG. 8 is a sectional view of the fuel injection valve in the first to third embodiments. FIG. 9 is a diagram for explaining the operation of the first to third embodiments.
[0020]
In the first embodiment shown in FIG. 1, reference numeral 1 denotes a fuel injection pump, which is a known jerk type fuel injection pump as shown in FIG. 3 is a fuel injection valve whose details are shown in FIG. Reference numeral 6 denotes a hydraulic oil pump whose details are shown in FIG.
Reference numeral 13 denotes a fuel tank, 31 denotes a fuel supply pipe connecting the fuel tank 13 and the fuel inlet of the fuel injection pump 1, and 12 denotes a fuel supply pipe 31 provided with fuel in the fuel tank 13 to the fuel injection pump 1. This is a fuel supply pump for feeding. Reference numeral 2 denotes a high-pressure fuel pipe that connects a high-pressure fuel outlet from the fuel injection pump 1 and a fuel inlet of the fuel injection valve 3.
[0021]
Reference numeral 5 denotes a water injection piston device, which will be described in detail later. 11 is a water injection tank, 34 is a water injection pipe connecting the water injection tank 11 and the water inlet of the water injection piston device 5, and 10 is provided in the water injection pipe 34 to send water in the water injection tank 11 to the water injection piston device 5. It is a water injection pump to supply. A water injection pipe 32 connects the water outlet of the water injection piston device 5 and the water inlet of the fuel injection valve 3.
Reference numeral 15 denotes a hydraulic oil tank, 33 denotes a hydraulic oil inlet pipe connecting the hydraulic oil tank 15 and the hydraulic oil inlet of the hydraulic oil pump 6, and 14 denotes an operation in the hydraulic oil tank 15 provided in the hydraulic oil inlet pipe 33. The hydraulic oil supply pump supplies oil to the hydraulic oil pump 6. Reference numeral 35 denotes a hydraulic oil pipe that connects the hydraulic oil outlet of the hydraulic oil pump 6 and the hydraulic oil inlet of the water injection piston device 5.
[0022]
In FIG. 5 showing the details of the fuel injection pump and the hydraulic oil pump, reference numeral 1 denotes a fuel injection pump configured as follows.
A plunger 25 is fitted to the inner periphery of the plunger barrel 24 so as to be reciprocally slidable, 17 is a fuel discharge valve, and 18 is a fuel check valve. When the plunger 25 moves upward, the fuel in the plunger chamber 25a is pressurized. The high pressure fuel is discharged to the high pressure fuel pipe 2 by pushing the fuel discharge valve 17 open.
The fuel injection pump 1 is a known jerk type fuel injection pump as described above, and is discharged to the high-pressure fuel pipe 2 by changing the effective stroke of the plunger 25 by reciprocation of a fuel adjustment rack (not shown). The fuel injection amount is adjusted. Reference numeral 13 denotes a fuel tank, 31 denotes a fuel supply pipe, and 12 denotes a fuel supply pump (both refer to FIG. 1).
A rack position detector 110 detects the position of the fuel adjustment rack, that is, a fuel injection amount. A detection signal of the fuel adjustment rack position (fuel injection amount) from the rack position detector 110 is input to the controller 106 described later. . Reference numeral 111 denotes a rotational speed detector for detecting the engine rotational speed, and the engine rotational speed detection signal from the rotational speed detector 111 is also input to the controller 106.
[0023]
6 is a hydraulic oil pump and is comprised as follows.
101 is a pump case, 102 is a plunger barrel fixed to the inside of the pump case 101, 103 is a plunger fitted to the inner periphery of the plunger barrel 102 so as to be slidable back and forth, and 103 a is a plunger in the plunger barrel 102 Reference numeral 103 denotes a plunger chamber formed so as to face the upper surface, and reference numeral 0111 denotes an oil supply hole provided in the plunger barrel 102. 113 is a tappet fixed to the lower end of the plunger 103, 115 is a plunger spring supported by the tappet 113, and presses the tappet 113 against the hydraulic oil cam 114 shown in FIG.
A hydraulic oil discharge valve 8 is provided on the outlet side of the plunger chamber 103a and has a structure similar to that of the fuel discharge valve 17 of the fuel injection pump 1. 7 is a hydraulic oil check valve having the same structure as the fuel check valve 18 of the fuel injection pump 1;
It is provided in a return passage connecting the discharge valve chamber in which the fuel discharge valve 17 is provided and the plunger chamber 103a.
[0024]
Reference numeral 109 denotes a discharge flow rate adjusting rack engaged with the rotation mechanism 112 of the plunger 103, and reference numeral 108 denotes a pinion engaged with the rack 109. An actuator 107 is operated by a control signal from the controller 106 described later, and its output end is connected to the pinion 108. The pinion 108 is rotated by the operating force of the actuator 107 to reciprocate the rack 109. The effective stroke is changed by rotating the plunger 103 via the rotation mechanism 112 of the plunger 103 meshed with the rack 109, and the hydraulic oil flow rate to the water injection piston device 5 is adjusted through the hydraulic oil pipe 35. It is configured as follows.
Reference numeral 106 denotes a controller to which an engine speed detection signal from the speed detector 111 and a fuel adjustment rack position (fuel injection amount) detection signal from the rack position detector 110 are input, and based on these detection signals. The hydraulic fluid flow rate corresponding to the engine operating state is calculated, and an operation signal corresponding to the hydraulic fluid flow rate is output to the actuator 107.
Further, 15 is a hydraulic oil tank, 33 is a hydraulic oil inlet pipe, and 14 is a hydraulic oil pump (both see FIG. 1).
[0025]
In FIG. 8 showing the details of the fuel injection valve 3, 09 is a main body, 033 is a nozzle tip, 010 is a plurality of perforated holes at the tip of the nozzle tip 033, and 011 is reciprocally slid into the nozzle tip 033. A needle valve that can be fitted, 014 is a needle valve spring that sets the valve opening pressure of the needle valve 011, and 012 is an oil reservoir that faces the tip of the needle valve 011. Reference numeral 022 denotes a fuel passage having an inlet end connected to the high pressure fuel pipe 2 and an outlet end connected to the oil reservoir 012. Reference numeral 021 denotes a water supply passage whose inlet end is connected to the water injection pipe 32 from the water injection piston device 5 and whose outlet end is connected to a water passage 030 formed below the nozzle tip 033. The outlet end of the water passage 030 is joined to the lower portion of the fuel passage 022 to form a joining portion 031.
[0026]
Reference numeral 4 denotes a check valve inside the fuel valve provided in the water supply passage 021, which allows only a flow from the water injection pipe 32 side toward the merging portion 031 side, and its valve opening pressure Pp is set to the needle valve 011. Valve opening pressure P 0 It is smaller than that.
The basic structure of the fuel injection valve 3 shown above is the same as that of the fuel injection valve in the invention of Japanese Patent No. 2772114 shown in FIG.
[0027]
In FIG. 4 showing the details of the water injection piston device, 51 is a cylinder, 52 is a water injection piston fitted in the cylinder 51 so as to be slidable in a reciprocating manner, and 56 is a seal fitted into the outer periphery of the water injection piston 52. It is a ring. The cylinder 51 is partitioned into a water chamber 53 and a hydraulic oil chamber 54 by the water injection piston 52, and the water injection piston 52 is free to be moved by a pressure difference between the hydraulic oil chamber 54 and the water chamber 53. Consists of a piston.
[0028]
The hydraulic oil from the hydraulic oil pump 6 is introduced into the hydraulic oil chamber 54 via the hydraulic oil pipe 35 and the hydraulic oil inlet 55. Reference numeral 9 denotes an inlet side water check valve, which is connected to the water injection pipe 34 and sets the spherical valve body 9a to a predetermined valve opening pressure so as to allow only a flow from the water injection pipe 34 toward the water chamber 53. It is configured to be pressed by the spring 9b. Reference numeral 16 denotes an outlet side water injection check valve, which is connected to the water injection pipe 32 and opens a spherical valve body 16a to allow a flow from the water chamber 53 side toward the water injection pipe 32. It is configured to be pressed by a spring 16b set to a pressure.
[0029]
During operation of the diesel engine having the fuel / water injection system having such a configuration, water in the water injection tank 11 is pressurized by the water injection pump 10, and the pressure in the water chamber 53 of the water injection piston device 5 is changed to hydraulic oil. When the pressure on the chamber 54 side, that is, the opening pressure of the hydraulic oil check valve 7 of the hydraulic oil pump 6 becomes larger, the water pumped from the water injection tank 11 by the water injection pump 10 passes through the water injection pipe 34 and the water injection check valve. 9 is pushed open and introduced into the water chamber 53 of the water injection piston device.
On the other hand, in the hydraulic oil pump 6, when the hydraulic oil cam 114 does not lift and the plunger 103 is below, the hydraulic oil in the hydraulic oil tank 15 passes through the hydraulic oil inlet pipe 33 and the oil supply hole by the hydraulic oil supply pump 14. It is introduced into the plunger chamber 103a through 0111.
When the tappet 113 and the plunger 103 are pushed up by the rotation of the hydraulic oil cam 114 of the hydraulic oil pump 6 during the fuel discharge suspension period of the fuel injection pump 1, the hydraulic oil in the plunger chamber 103 a is added by the plunger 103. The hydraulic oil discharge valve 8 is pushed up and enters the hydraulic oil chamber 54 of the water injection piston device 5 through the hydraulic oil pipe 35.
[0030]
The high-pressure hydraulic oil that has entered the hydraulic oil chamber 54 acts on the hydraulic oil chamber side 52b of the water injection piston 52, and due to the pressure difference between the pressure of the hydraulic oil and the pressure of water acting on the water chamber side 52a,
The water injection piston 52 is moved to the left in FIGS. 1 and 4, that is, in the direction of reducing the volume of the water chamber 53, so that the water introduced into the water chamber 53 pushes the water injection check valve 16 open. It is fed into the water supply path 021 of the fuel injection valve 3 through the water injection pipe 32.
At this time, the valve opening pressure Pr of the fuel check valve 18 of the fuel injection pump 1, the valve opening pressure Pp of the fuel valve check valve 4 of the water supply path 021, and the valve opening pressure of the needle valve 011 of the fuel injection valve 3. P 0 Then,
P 0 > Pr, P 0 > Pp
Therefore, the water supplied to the water supply passage 021 of the fuel injection valve 3 passes through the water passage 030 and the fuel-water junction portion 031 through the fuel valve check valve 4 and the fuel passage 022. Flows in.
[0031]
The fuel that is closer to the fuel injection pump 1 than the junction 031 in the fuel passage 022 is pushed back through the high-pressure fuel pipe 2 in the direction of the fuel injection pump 1. As a result, the fuel injection valve 3 is filled with an oil reservoir 012 and a volume of fuel from the oil reservoir 012 to the merging portion 031, and a predetermined amount is placed in the fuel passage 022 upstream of the merging portion 031. It is in a layered state where the water is filled and the upstream side is filled with fuel again.
Next, as shown in the “fuel injection” state of FIG. 9, the discharge of the fuel injection pump 1 is started, the fuel in the fuel injection valve 3 is compressed, and the pressure rises to open the fuel injection valve 3. Pressure P 0 If it becomes above, needle valve 011 will be opened and injection will be started. In the injection, the fuel is first injected from the fuel and water in the layered state as described above, and after the ignition delay period, the combustion starts. Subsequently, water is injected over the burning fuel spray flame. Since the water injected at this time is also sprayed and the air in the combustion chamber is taken into the inside thereof, the combustion is activated by supplying air to the previously injected fuel.
Finally, the remaining fuel is injected into the preceding water spray and burned. The thermal effect accompanying the injection of fuel and water suppresses the rise in flame temperature and suppresses the generation of NOx.
[0032]
During the operation, the controller 106 receives the engine speed detection signal from the speed detector 111 and the fuel adjustment rack position (fuel injection amount) detection signal from the rack position detector 110. . The controller 106 calculates a hydraulic oil flow rate corresponding to the engine operating state based on these detection signals, and outputs an operation signal corresponding to the hydraulic oil flow rate to the actuator 107.
The pinion 108 is rotated by the operating force of the actuator 107 to cause the rack 109 to reciprocate. By rotating the plunger 103 via the rotation mechanism 112 of the plunger 103 meshing with the rack 109, the effective stroke is achieved. The hydraulic oil flow rate to the water injection piston device 5 is adjusted. Thus, the amount of water supplied to the fuel injection valve 3 by the hydraulic oil is adjusted.
Further, by setting the profile of the hydraulic oil cam 114 provided in the hydraulic oil pump 6 to a required shape, the supply timing of the hydraulic oil by the hydraulic oil pump 6 is adjusted, thereby the water injection piston device 5. The supply timing of water to the fuel injection valve 3 can be adjusted.
[0033]
According to this embodiment, the hydraulic oil is supplied to the water injection piston device 5 by adjusting the hydraulic oil supply timing and the hydraulic oil flow rate by the hydraulic oil pump 6 having a structure similar to that of a commonly used jerk type fuel injection pump. Alternatively, by blocking this, the water injection piston device 5 is operated, and the water injection piston device 5 supplies and shuts off the water to the fuel injection valve 3, so that it is the same as the jerk type fuel injection pump. With a relatively simple control means that only adjusts the hydraulic oil supply timing and hydraulic oil flow rate of the hydraulic oil pump 6 having the structure, the water injection amount and the water injection timing can be controlled with high accuracy.
Further, as described above, the hydraulic oil pump 6 having the same structure as the jerk type fuel injection pump is combined with the water injection piston device 5 having a simple structure in which the water injection piston 52 having a free piston structure is fitted in the cylinder 51. Since the water supply system to the fuel injection valve 3 is configured, a special electronic control device as in the prior art is not required, and the fuel / water injection system is configured with a very simple and low-cost device. Can do.
[0034]
In the second embodiment shown in FIGS. 2 and 6, the hydraulic oil discharge valve 8 and the hydraulic oil check valve 7 in the first embodiment are removed from the discharge portion of the hydraulic oil pump 6 and replaced with this. The diaphragm mechanism 40 is provided.
According to this embodiment, since the throttle mechanism 40 is provided in the hydraulic oil passage between the hydraulic oil pump 6 and the water injection piston device 5, vibration of the water injection piston 52 of the water injection piston device 5, etc. by the throttle mechanism 40. Therefore, the supply of hydraulic oil to the water injection piston device 5 can be performed without pulsation or the like, and the water supply operation by the water injection piston device 5 is stabilized. The
Further, as compared with the hydraulic oil discharge valve 8 and the hydraulic oil check valve 7 as in the first embodiment, it is only necessary to provide the throttle mechanism 40 having a simple structure, so that the structure is simplified and the cost is reduced.
Other configurations are the same as those of the first embodiment, and the same members are denoted by the same reference numerals.
[0035]
In the third embodiment shown in FIGS. 3 and 6, reference numeral 36 denotes a hydraulic oil return pipe that connects the hydraulic oil chamber 54 of the water injection piston device 5 and the hydraulic oil tank 15, and reference numeral 300 denotes the hydraulic oil return pipe 36. This is an electromagnetic valve that opens and closes a pipeline. By providing the hydraulic oil return pipe 36 and the electromagnetic valve 300, the hydraulic oil inlet pipe 33, the hydraulic oil supply pump 14, the hydraulic oil inlet pipe 33, the operation is operated from the hydraulic oil tank 15. A hydraulic oil circulation path that reaches the hydraulic oil tank 15 through the oil pump 6, the hydraulic oil pipe 35, the water injection piston device 5, the electromagnetic valve 300, and the hydraulic oil return pipe 36 in this order is formed.
[0036]
Reference numeral 301 denotes an electromagnetic valve drive device, which receives a rotation speed detection signal of a rotation shaft 303 such as a crankshaft and a camshaft from the rotation speed detector 111 as well as the engine load or the same as in the first and second embodiments. An engine load detection signal such as an output is input from the load detector 304.
In the electromagnetic valve driving device 301, hydraulic oil is supplied from the hydraulic oil pump 6 to the hydraulic oil chamber 54 of the water injection piston device 5, and the water injection piston 52 of the water injection piston device 5 moves to the left in FIG. After the water in the chamber 53 is sent to the fuel injection valve 3, the electromagnetic valve 300 is opened, and the hydraulic oil in the hydraulic oil chamber 54 is returned to the hydraulic oil tank 15 via the hydraulic oil return pipe 36.
Further, in the electromagnetic valve driving device 301, the electromagnetic valve 300 is opened / closed at an opening / closing timing adapted to the engine operating conditions based on the rotation speed detection signal and the engine load detection signal.
By this operation, the residual pressure of the hydraulic oil in the hydraulic oil chamber 54 is completely removed, and the water supply into the water chamber 53 in the next step is smoothly performed without resistance.
[0037]
According to this embodiment, from the hydraulic oil tank 15 to the hydraulic oil tank 15 through the hydraulic oil supply pump 14, the hydraulic oil pump 6, the water injection piston device 5, the electromagnetic valve 300, and the hydraulic oil return pipe 36 in this order. The hydraulic oil circulation path is formed, and the hydraulic oil return path of the circulation path is opened and closed at a timing adapted to the engine operating conditions by the electromagnetic valve 300, so that the hydraulic oil is returned to the hydraulic oil tank 15 every cycle and the operation is performed. The oil tank 15 is cooled, the temperature rise of the hydraulic oil is suppressed, and the residual pressure of the hydraulic oil in the hydraulic oil chamber 54 is completely removed, so that water into the water chamber 53 in the next step is obtained. Is smoothly supplied without resistance. Thereby, the water supply action by the hydraulic oil pump 6 and the water injection piston device 5 is stabilized.
[0038]
【The invention's effect】
As described above, according to the present invention, the hydraulic oil pump adjusts the hydraulic oil supply timing and the hydraulic oil flow rate, and supplies or shuts off the hydraulic oil to the water injection piston device. Since the supply and shutoff of water to the valve are performed, the hydraulic oil supply timing and hydraulic oil flow rate of the hydraulic oil pump having the same structure as that of a commonly used jerk type fuel injection pump are only adjusted. With simple control means, the water injection amount and water injection timing can be controlled with high accuracy.
[0039]
Further, as described above, the fuel injection is performed by combining the hydraulic oil pump capable of adjusting the hydraulic oil supply timing and hydraulic oil flow rate with the simple structure of the water injection piston device in which the water injection piston of the free piston structure is fitted in the cylinder. Since the water supply system to the valve is configured, there is no need for special control operation equipment by electronic control as in the prior art, and the fuel / water injection system is configured with a very simple and low-cost device. Can do.
[0040]
Claims 3 With this configuration, the throttling mechanism can mitigate abrupt movement of the water injection piston device accompanied by vibrations of the water injection piston device, so that the supply of hydraulic oil to the water injection piston device is accompanied by pulsation, etc. The water supply operation by the water injection piston device is stabilized.
Further, since it is only necessary to provide a diaphragm mechanism having a simple structure, the structure is simplified and the cost is reduced.
[0041]
And claims 4 With this configuration, a hydraulic oil circulation path is formed from the hydraulic oil tank to the hydraulic oil tank through the hydraulic oil pump, the water injection piston device, the electromagnetic valve, and the hydraulic oil return passage in this order. Since the hydraulic fluid return passage of the road is opened and closed at a timing adapted to the engine operating conditions by a solenoid valve, the hydraulic oil is returned to the hydraulic oil tank every cycle and cooled by the hydraulic oil tank. The rise is suppressed, and the residual pressure of the hydraulic oil in the water injection piston device is completely removed, so that water is smoothly supplied in the next step without resistance. Thereby, the water supply action by the hydraulic oil pump and the water injection piston device is stabilized.
[0042]
As described above, according to the present invention, the hydraulic oil pump capable of adjusting the hydraulic oil supply timing and the hydraulic oil flow rate is combined with the water injection piston device having a simple structure in which the water injection piston of the free piston structure is fitted in the cylinder. In addition, it is possible to provide a fuel / water-injection internal combustion engine in which the water injection amount and the water injection timing control can be performed with a relatively simple control means, and the device cost of the water injection amount control operation device is reduced. .
[Brief description of the drawings]
1 is a configuration diagram of a fuel / water injection system for a diesel engine according to a first embodiment of the present invention;
FIG. 2 is a configuration diagram of a fuel / water injection system of a diesel engine according to a second embodiment.
FIG. 3 is a configuration diagram of a fuel / water injection system for a diesel engine according to a third embodiment;
FIG. 4 is a cross-sectional view of a water injection piston device.
FIG. 5 is a cross-sectional view showing structures of a fuel injection pump and a hydraulic oil pump in the first embodiment.
FIG. 6 is a cross-sectional view showing structures of a fuel injection pump and a hydraulic oil pump in the second embodiment.
FIG. 7 is a sectional view showing structures of a fuel injection pump and a hydraulic oil pump in the third embodiment.
FIG. 8 is a cross-sectional view of the fuel injection valve in the first to third embodiments.
FIG. 9 is an operation explanatory view of the first to third embodiments.
FIG. 10 is a main part configuration diagram showing a conventional technique.
[Explanation of symbols]
1 Fuel injection pump
2 High-pressure fuel pipe
3 Fuel injection valve
4 Check valve in fuel valve
5 Water injection piston device
6 Hydraulic oil pump
7 Hydraulic oil check valve
8 Hydraulic oil discharge valve
9 Water check valve
10 Water injection pump
010 injection hole
11 Water injection tank
011 Needle valve
12 Fuel supply pump
012 Oil reservoir
13 Fuel tank
14 Hydraulic oil supply pump
15 Hydraulic oil tank
16 Water check valve
17 Fuel discharge valve
18 Fuel check valve
24 Plunger barrel
25 Plunger
32 Water injection pipe
031 Junction
34 Water injection pipe
35 Hydraulic oil pipe
36 Hydraulic oil return pipe
40 Aperture mechanism
51 cylinders
52 Water injection piston
53 Water Chamber
54 Hydraulic oil chamber
102 Plunger barrel
103 Plunger
103a Plunger chamber
106 controller
107 Actuator
109 racks
110 Rack position detector
111 RPM detector
114 Hydraulic oil cam
300 Solenoid valve
301 Solenoid valve driving device
304 Load detector

Claims (4)

燃料と水とを燃焼室に噴射する燃料・水噴射内燃機関であって、燃料噴射ポンプと連通する燃料通路と逆止弁とを内蔵しかつ該燃料通路と合流する水供給路とを有する燃料噴射弁と、前記燃料噴射ポンプが休止している間に所定量の水を前記水供給路を通じて合流部から前記燃料通路内に供給する水供給手段を備えるとともに、前記燃料噴射弁の油溜部の容積と前記合流部から油溜部までの容積の合計が全燃料噴射量の５％以上７５％以下である燃料・水噴射内燃機関において、
水供給ポンプから水通路を経た水が収容される水室内の圧力と該水室に対し注水ピストンを隔てて形成された作動油室内の圧力との圧力差により前記水を前記燃料噴射弁に圧送する、注水ピストン装置を前記水通路に設けるとともに、作動油入口通路から導入された作動油を加圧して前記注水ピストン装置の作動油室に作動油通路を経て送給する作動油ポンプを設け、
該注水ピストン装置は、ピストンが、シリンダからなる水室内を往復摺動自在に嵌合され、前記圧力差により移動せしめられる自由ピストンにて構成され、前記水室出口の前記水通路には前記燃料噴射弁に向かう流れのみを可能とする注水逆止弁が設けられるとともに、前記水室入口の前記水通路には該水室に向かう流れのみを可能とする注水逆止弁が設けられ、
更に前記作動油ポンプは、プランジャバレル内に往復摺動自在に嵌合されたプランジャの往復動によりプランジャ室内の作動油を前記注水ピストン装置に送出すると共に、該プランジャの有効行程を変化させることにより作動油送出流量を調整可能に構成し、且つ前記作動油ポンプに設けられた作動油カムのプロフィールを所要の形状に設定することにより、該作動油ポンプによる作動油の供給タイミングを調整可能に構成し、
前記作動油カムのプロフィール形状を、前記燃料噴射ポンプの燃料吐出休止期間中に、作動油ポンプの作動油カムの回転により作動油室に入った高圧の作動油を前記注水ピストンの作動油室側に作用させて前記注水ピストンの水室内に導入されていた水を燃料噴射弁に送り込ませるプロフィール形状に設定したことを特徴とする燃料・水噴射内燃機関。A fuel / water-injection internal combustion engine for injecting fuel and water into a combustion chamber, having a fuel passage communicating with a fuel injection pump and a check valve, and having a water supply passage joined to the fuel passage And an oil reservoir for supplying a predetermined amount of water from the junction to the fuel passage through the water supply passage while the fuel injection pump is stopped, and an oil reservoir for the fuel injection valve In a fuel / water-injection internal combustion engine in which the total volume from the merging portion to the oil reservoir is 5% to 75% of the total fuel injection amount,
The water is pumped to the fuel injection valve by the pressure difference between the pressure in the water chamber in which water passing through the water passage from the water supply pump is accommodated and the pressure in the hydraulic oil chamber formed across the water injection piston with respect to the water chamber. Providing a water injection piston device in the water passage, and providing a hydraulic oil pump that pressurizes the hydraulic oil introduced from the hydraulic oil inlet passage and feeds it to the hydraulic oil chamber of the water injection piston device through the hydraulic oil passage;
The water injection piston device is constituted by a free piston that is slidably fitted in a water chamber composed of a cylinder and is moved by the pressure difference, and the fuel passage is provided in the water passage at the outlet of the water chamber. A water injection check valve that allows only a flow toward the injection valve is provided, and a water injection check valve that enables only a flow toward the water chamber is provided in the water passage at the water chamber inlet,
Further, the hydraulic oil pump sends hydraulic oil in the plunger chamber to the water injection piston device by reciprocating movement of a plunger that is slidably reciprocated in the plunger barrel, and changes the effective stroke of the plunger. The hydraulic oil delivery flow rate is adjustable, and the hydraulic oil cam profile provided in the hydraulic oil pump is set to a required shape to adjust the hydraulic oil supply timing by the hydraulic oil pump. And
The profile shape of the hydraulic oil cam is set so that the high-pressure hydraulic oil that has entered the hydraulic oil chamber by the rotation of the hydraulic oil cam of the hydraulic oil pump during the fuel discharge suspension period of the fuel injection pump is the hydraulic oil chamber side of the water injection piston. A fuel / water-injection internal combustion engine characterized in that the profile shape is set so that the water introduced into the water chamber of the water injection piston is fed into the fuel injection valve . ジャーク式ポンプからなる前記作動油ポンプは、前記プランジャ室の圧力により開弁して該プランジャ室内の作動油を前記注水ピストン装置に送出する作動油吐出弁と、前記プランジャ室と前記作動油通路とを前記作動油吐出弁をバイパスする戻り通路に設けられて該作動油通路からプランジャに向かう流れのみを可能とする作動油逆止弁とを備えてなることを特徴とする請求項１記載の燃料・水噴射内燃機関。  The hydraulic oil pump comprising a jerk-type pump is opened by a pressure in the plunger chamber, and a hydraulic oil discharge valve that sends the hydraulic oil in the plunger chamber to the water injection piston device, the plunger chamber, the hydraulic oil passage, The fuel according to claim 1, further comprising: a hydraulic oil check valve provided in a return passage that bypasses the hydraulic oil discharge valve to allow only a flow from the hydraulic oil passage toward the plunger. -Water injection internal combustion engine. 前記ジャーク式ポンプからなる前記作動油ポンプは、前記プランジャ室と作動油通路との間に、作動油通路面積を縮小する絞り機構を設けてなることを特徴とする請求項１記載の燃料・水噴射内燃機関。  2. The fuel / water according to claim 1, wherein the hydraulic oil pump comprising the jerk type pump is provided with a throttle mechanism for reducing the hydraulic oil passage area between the plunger chamber and the hydraulic oil passage. Injection internal combustion engine. 前記注水ピストン装置の作動油室と前記作動油ポンプへの作動油入口管に作動油を供給するための作動油タンクとを接続する作動油戻り通路、並びに機関回転数、機関負荷等の機関運転条件により該作動油戻り通路を開閉する電磁弁を設けて、前記作動油タンクから作動油入口通路、作動油ポンプ、作動油通路、注水ピストン装置、電磁弁、及び作動油戻り通路をこの順に経て前記作動油タンクに至る作動油の循環路を形成したことを特徴とする請求項１記載の燃料・水噴射内燃機関。  The hydraulic oil return passage connecting the hydraulic oil chamber of the water injection piston device and the hydraulic oil tank for supplying hydraulic oil to the hydraulic oil inlet pipe to the hydraulic oil pump, and the engine operation such as the engine speed and the engine load Provide an electromagnetic valve that opens and closes the hydraulic oil return passage according to conditions, and passes through the hydraulic oil inlet passage, hydraulic oil pump, hydraulic oil passage, water injection piston device, electromagnetic valve, and hydraulic oil return passage in this order from the hydraulic oil tank. 2. The fuel / water-injection internal combustion engine according to claim 1, wherein a circulation path for hydraulic oil reaching the hydraulic oil tank is formed.
JP2000349832A 2000-11-16 2000-11-16 Fuel / water injection internal combustion engine Expired - Lifetime JP4550991B2 (en)

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