JP2010534790A - Fuel injection valve with pressure balance type control valve - Google Patents

Fuel injection valve with pressure balance type control valve Download PDF

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JP2010534790A
JP2010534790A JP2010518597A JP2010518597A JP2010534790A JP 2010534790 A JP2010534790 A JP 2010534790A JP 2010518597 A JP2010518597 A JP 2010518597A JP 2010518597 A JP2010518597 A JP 2010518597A JP 2010534790 A JP2010534790 A JP 2010534790A
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valve
seat
pressure side
control
chamber
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JP5193299B2 (en
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ラップ ホルガー
シュテックライン ヴォルフガング
アイゼンメンガー ナディア
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Robert Bosch GmbH
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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing

Abstract

本発明は、内燃機関のための燃料噴射弁であって、弁ニードル（４）を含み、弁ニードルはその軸線方向運動によって少なくとも１つの噴射孔（５）の開口部を制御するようになっており、高圧側（１４）に接続された制御室（１７）を含み、制御室の圧力は弁ニードル（４）に作用しており、制御弁（２３）を含み、制御弁は、半径方向で、制御室（１７）に接続された高圧側の弁室（２２）と低圧側の弁室（２４）との間に設けられた１つの弁座（２６）と、摺動自在に案内された１つの制御弁部材（２５）とを備え、制御弁部材は高圧側の弁室（２２）を半径方向で画定し、かつ弁座（２６）と協働する形式のものに関する。本発明に基づき、
制御弁部材（２５）は、半径方向で高圧側の弁室（２２）内へ突出する環状突出部（２９）を有し、環状突出部の、弁座（２６）に向いている段部面（２９ａ）は、弁座（２６）と協働するシール面を形成している。The invention is a fuel injection valve for an internal combustion engine, comprising a valve needle (4), which valve needle controls the opening of at least one injection hole (5) by its axial movement. A control chamber (17) connected to the high pressure side (14), the pressure of the control chamber acting on the valve needle (4), including the control valve (23), the control valve being radially The valve seat (26) provided between the high pressure side valve chamber (22) and the low pressure side valve chamber (24) connected to the control chamber (17) was slidably guided. And a control valve member of the type that radially defines the high-pressure side valve chamber (22) and cooperates with the valve seat (26). In accordance with the present invention,
The control valve member (25) has an annular protrusion (29) protruding into the high pressure side valve chamber (22) in the radial direction, and the stepped surface of the annular protrusion facing the valve seat (26). (29a) forms a sealing surface which cooperates with the valve seat (26).

Description

本発明は、内燃機関のための燃料噴射弁であって、弁ニードルを含んでおり、該弁ニードルは該弁ニードルの軸線方向運動によって少なくとも１つの噴射孔の開口部を制御するようになっており、高圧側に接続された制御室を含んでおり、該制御室の圧力は直接又は間接的に前記弁ニードルに作用するようになっており、制御弁を含んでおり、該制御弁は、半径方向で、前記制御室に接続された高圧側の弁室と低圧側の弁室との間に設けられた弁座と、摺動自在に案内された制御弁部材とを備えており、該制御弁部材は前記高圧側の弁室の半径方向を画定し、つまり半径方向の画定部をなしていて、かつ前記弁座と協働（接触）するようになっている形式のものに関する。   The present invention is a fuel injection valve for an internal combustion engine, which includes a valve needle that is adapted to control the opening of at least one injection hole by axial movement of the valve needle. A control chamber connected to the high-pressure side, the pressure of the control chamber acting on the valve needle directly or indirectly, including a control valve, A valve seat provided between a high-pressure side valve chamber and a low-pressure side valve chamber connected to the control chamber in a radial direction, and a control valve member guided slidably, The control valve member defines a radial direction of the valve chamber on the high-pressure side, that is, a type in which the control valve member forms a radially defined portion and cooperates (contacts) with the valve seat.

前記形式の燃料噴射弁は、例えば欧州特許出願公開第１６１２４０３Ａ１号明細書に開示されている。   A fuel injection valve of this type is disclosed, for example, in EP 1612403 A1.

前記公知の燃料噴射弁においては、１つ若しくは複数の噴射孔がノズルニードルの軸線方向運動（長手方向運動）により開閉制御されるようになっている。制御室内の圧力に基づき、閉鎖力は間接的に弁ピストンを介してノズルニードルに生ぜしめられ、その結果、ノズルニードルは、制御室内に相応に高い燃料圧を作用させてある場合に、閉鎖位置に保たれている。噴射を行う場合には、制御室は、電磁弁として形成された制御弁を用いて逃がし室に接続される。制御弁は、制御弁部材（制御弁構成要素）として弁スリーブを有しており、弁スリーブは環状室の外側を画定しており、環状室は流出絞りを介して制御室に接続されている。弁スリーブは、力から解放された状態若しくは圧力バランスした状態で作動され、つまり、弁スリーブには、環状室内の燃料圧により発生して弁スリーブをその運動方向で移動させるような力は作用していない。弁スリーブは、閉鎖ばねによって弁座に向けて押圧されていて、その結果、環状室を外側に対して閉鎖している。噴射を行う場合には、弁スリーブは電磁石と用いて弁座から持ち上げられ、つまり離間され、このような離間運動は、液力の力成分が生じていないことに基づき、閉鎖ばねの比較的小さい閉鎖力を克服することにより極めて迅速に行われる。これにより、制御室は逃がし室に接続されて、放圧される。   In the known fuel injection valve, one or a plurality of injection holes are controlled to be opened and closed by the axial movement (longitudinal movement) of the nozzle needle. Based on the pressure in the control chamber, a closing force is indirectly applied to the nozzle needle via the valve piston, so that the nozzle needle is in the closed position when a correspondingly high fuel pressure is applied in the control chamber. It is kept in. When performing injection, the control chamber is connected to the escape chamber using a control valve formed as a solenoid valve. The control valve has a valve sleeve as a control valve member (control valve component), the valve sleeve defines the outside of the annular chamber, and the annular chamber is connected to the control chamber via an outflow restrictor. . The valve sleeve is operated in a state where it is released from the force or in a pressure balanced state. Not. The valve sleeve is pressed towards the valve seat by a closing spring, so that the annular chamber is closed to the outside. In the case of injection, the valve sleeve is lifted from the valve seat with an electromagnet, i.e. separated, such a separation movement being relatively small in the closing spring based on the absence of a hydraulic force component. This is done very quickly by overcoming the closing force. As a result, the control chamber is connected to the escape chamber and released.

弁スリーブは圧力バランスされており、それというのは、弁スリーブを摺動自在（摺動可能）に案内している案内部の直径と、静止状態で弁スリーブによって密閉又はシールされる弁座の座直径とが互いに同じ大きさであるからである。このような構成により、静止状態では軸線方向（開放方向若しくは閉鎖方向）での圧力又は押圧力は生じておらず、半径方向の圧力が生じているだけである。座直径を案内直径（案内部の直径）と異ならせると、軸線方向の液力（圧力又は押圧力）が生じることになる。案内部と弁座とを多くの場合にそうであるように１つの構成要素内に組み込んであり場合には、座直径を案内直径と異ならせることは、液力が開放方向で生じるように行われている。逆の場合には弁スリーブをもはや弁本体に装着することができなくなる。シール座において面積をバランスしてある場合には欠点として、作動中に開放方向の液力が常に生じており、該液力は極端な場合には弁の不都合な開放、つまり漏れを生ぜしめてしまうことになる。   The valve sleeve is pressure balanced because of the diameter of the guide which slidably guides the valve sleeve and the valve seat which is sealed or sealed by the valve sleeve in a stationary state. This is because the seat diameter is the same size. With such a configuration, in the stationary state, no pressure or pressing force in the axial direction (opening direction or closing direction) is generated, but only radial pressure is generated. When the seat diameter is made different from the guide diameter (diameter of the guide portion), a hydraulic force (pressure or pressing force) in the axial direction is generated. In the case where the guide and the valve seat are integrated in one component as is often the case, making the seat diameter different from the guide diameter is such that the hydraulic force occurs in the opening direction. It has been broken. In the opposite case, the valve sleeve can no longer be mounted on the valve body. If the area of the seal seat is balanced, the disadvantage is that there is always a hydraulic force in the opening direction during operation, which in the extreme case causes an inadvertent opening of the valve, i.e. leakage. It will be.

さらに知られている構成においては、案内部は弁座から独立して別（第２）の構成部分（構成要素）内に形成されており、該構成部分は、不動の構成部分に支えられている。この場合には座直径は、静止状態で閉鎖方向の液力を生ぜしめるように、案内直径から異ならせて形成されている。このような構成においては面積バランスの場合に、漏れの発生しない程度に面積バランスを高め、ひいては面圧を低下させることができることになる。しかしながら欠点として、閉鎖方向に作用する液力は、アクチュエータによる開放に際して付加的にアクチュエータによって克服されねばならないものであり、したがって高い出力のアクチュエータを必要とすることになり、このことは殊に電磁式のアクチュエータにとって欠点である。   In a further known configuration, the guide is formed in a separate (second) component (component) independently of the valve seat, which component is supported by a stationary component. Yes. In this case, the seat diameter is formed different from the guide diameter so as to generate a fluid force in the closing direction in a stationary state. In such a configuration, in the case of area balance, the area balance can be increased to the extent that leakage does not occur, and consequently the surface pressure can be reduced. However, as a disadvantage, the hydraulic force acting in the closing direction must additionally be overcome by the actuator upon opening by the actuator, and thus requires a high power actuator, which is particularly electromagnetic. This is a drawback for the actuator of

本発明においては、静止状態で軸線方向の液力が弁スリーブに作用せず、このような力バランスの状態が弁スリーブと弁座との間の面積バランスの場合にも十分に保たれるようにするために、本発明の構成によれば、制御弁部材は、半径方向で高圧側の弁室内へ突出する環状突出部を有しており、該環状突出部の、弁座に向いている段部面は、弁座と協働（接触）するシール面を形成（画定）している。このような構成により、作動時間の経過に伴って生じるような開放方向の液力の発生を避けることができ、閉鎖ばね力を小さくすることができ、ひいては摩耗を減少させることができるようになっている。   In the present invention, the fluid force in the axial direction does not act on the valve sleeve in a stationary state, and such a force balance state is sufficiently maintained even in the case of an area balance between the valve sleeve and the valve seat. Therefore, according to the configuration of the present invention, the control valve member has an annular protrusion that protrudes radially into the high pressure side valve chamber, and faces the valve seat of the annular protrusion. The step surface forms (defines) a sealing surface that cooperates (contacts) with the valve seat. With such a configuration, it is possible to avoid the generation of hydraulic force in the opening direction that occurs with the passage of operating time, to reduce the closing spring force, and to reduce wear. ing.

制御弁と概略的に示す供給構成要素とを有する本発明に基づく燃料噴射弁の縦断面図である。1 is a longitudinal sectional view of a fuel injection valve according to the present invention having a control valve and a supply component schematically shown. 弁スリーブにトロイド状の輪郭を有しかつ弁座に円錐座を有する制御弁の第１の変化例の、図１のＩＩの部位の詳細図である。FIG. 2 is a detailed view of the portion II of FIG. 1 of a first variation of a control valve having a toroidal profile on the valve sleeve and a conical seat on the valve seat. 弁スリーブにトロイダル状の輪郭を有しかつ弁座に円錐座を有する制御弁の第３の変化例の、図２のＩＩの部位の詳細図である。FIG. 4 is a detailed view of the portion II of FIG. 2 of a third variation of the control valve having a toroidal profile on the valve sleeve and a conical seat on the valve seat. 弁スリーブにトロイド状の輪郭を有しかつ弁座に円錐座を有する制御弁の第３の変化例の、図１のＩＩの部位の詳細図である。FIG. 6 is a detailed view of the portion II of FIG. 1 of a third variation of the control valve having a toroidal profile on the valve sleeve and a conical seat on the valve seat. 弁ニードルを有する制御弁の実施形態を示す図である。FIG. 3 shows an embodiment of a control valve having a valve needle.

図１には、本発明に基づく燃料噴射弁を縦断面図で示してあり、該燃料噴射弁は、複数の構成部分から成る、つまり複数構造（ここでは簡略的に一体として示す）の保持本体１及びノズル本体２を含んでおり、この場合に、保持本体（ホルダー部材）１とノズル本体２とは、締め付けナット３によって相互に圧着されている。ノズル本体２内には、ノズルニードル（弁ニードル）４を縦方向移動可能（長手方向移動可能）に配置してあり、該ノズルニードルは該ノズルニードルの縦方向運動（長手方向運動）によって少なくとも１つの噴射孔５の開口部を制御するようになっている。燃料は、１つの圧力室６を介して図示の実施形態で複数の噴射孔５に供給されるようになっており、前記圧力室は、ノズルニードル４を取り囲んでいて、つまりノズルニードル４の周囲に画成されていて、供給通路７を介して高圧の燃料で満たされるようになっている。ノズルニードル４を噴射孔５から離間する方向に運動させて、噴射孔５の開放のための位置、つまり開放位置へ移すと、燃料は圧力室６から噴射孔５を介して、図示省略の内燃機関の燃焼室内へ噴射される。逆に、ノズルニードル４を噴射孔５の閉鎖のための位置、つまり閉鎖位置へ移す、つまり弁座に接触又は当接させると、噴射孔５はノズルニードル４によって閉じられる。   FIG. 1 is a longitudinal sectional view of a fuel injection valve according to the present invention. The fuel injection valve is composed of a plurality of components, that is, a holding body having a plurality of structures (shown here as a single unit). 1 and the nozzle body 2. In this case, the holding body (holder member) 1 and the nozzle body 2 are pressure-bonded to each other by a tightening nut 3. A nozzle needle (valve needle) 4 is disposed in the nozzle body 2 so as to be movable in the vertical direction (movable in the longitudinal direction). The openings of the two injection holes 5 are controlled. The fuel is supplied to the plurality of injection holes 5 in the illustrated embodiment through one pressure chamber 6, and the pressure chamber surrounds the nozzle needle 4, that is, around the nozzle needle 4. And is filled with high-pressure fuel via the supply passage 7. When the nozzle needle 4 is moved in a direction away from the injection hole 5 and moved to a position for opening the injection hole 5, that is, to an open position, fuel flows from the pressure chamber 6 through the injection hole 5 to an internal combustion engine (not shown). It is injected into the combustion chamber of the engine. On the contrary, when the nozzle needle 4 is moved to a position for closing the injection hole 5, that is, when the nozzle needle 4 is brought into contact with or contacted with the valve seat, the injection hole 5 is closed by the nozzle needle 4.

保持本体１内には、ノズルニードル４に対して同軸にかつ該保持本体の縦軸方向（長手方向）に延びる縦軸孔８を画成してあり、該縦軸孔内には制御ピストン９を縦軸方向移動可能に配置してある。制御ピストン９は、押圧片１０を介してノズルニードル４に接続されていて、したがってノズルニードル４と同期して縦軸線方向に運動させられるようになっている。制御ピストン９は、ノズル本体２に向いている側の端部をばね１１によって取り囲まれており、該ばねは、一方で保持本体１内の段部に支えられ、かつ他方で押圧片１０に支えられており、その結果、ばね１１のばね力によって押圧片１０がノズル本体２に向けて押圧され、ひいてはノズルニードル４が閉鎖位置へ押圧される。   In the holding body 1, a vertical axis hole 8 is defined which extends coaxially with the nozzle needle 4 and extends in the longitudinal direction (longitudinal direction) of the holding body. Are arranged so as to be movable in the vertical axis direction. The control piston 9 is connected to the nozzle needle 4 via the pressing piece 10, and thus can be moved in the vertical axis direction in synchronization with the nozzle needle 4. The end of the control piston 9 facing the nozzle body 2 is surrounded by a spring 11, which is supported on the one hand by a step in the holding body 1 and on the other hand by a pressing piece 10. As a result, the pressing piece 10 is pressed toward the nozzle body 2 by the spring force of the spring 11, and the nozzle needle 4 is pressed to the closed position.

燃料を高圧で供給するために、高圧ポンプ１２を設けてあり、該高圧ポンプは燃料タンク１３から燃料を圧縮して、蓄圧室１４へ送り、該蓄圧室内に燃料は高圧下で蓄えられるようになっている。高圧の燃料は、高圧管路１５を介して、かつ燃料噴射弁に形成された高圧接続部１６を介して燃料噴射弁に供給されて、噴射孔５から内燃機関の燃焼室内に噴射される。   In order to supply the fuel at a high pressure, a high-pressure pump 12 is provided. The high-pressure pump compresses the fuel from the fuel tank 13 and sends it to the pressure accumulating chamber 14 so that the fuel is stored in the pressure accumulating chamber under a high pressure. It has become. The high-pressure fuel is supplied to the fuel injection valve via the high-pressure line 15 and the high-pressure connection 16 formed in the fuel injection valve, and is injected from the injection hole 5 into the combustion chamber of the internal combustion engine.

制御ピストン９は、ノズル本体２と逆の側の端部でもって制御室１７を画定しており、該制御室は流入孔１８を用いて、該流入孔内の流入絞り１９を介して供給通路７に接続されている。さらに制御室１７は、保持本体１及び制御弁本体２１内に設けられている縦軸孔２０を介して、高圧側の弁室２２に接続されており、該弁室は制御弁２３を介して低圧側の弁室（逃がし室）２４に接続されるようになっている。制御弁２３は制御室１７内の燃料圧力の降下のために用いられ、制御スリーブ若しくは弁スリーブ２５として形成された制御部材（制御構成要素）を有しており、該制御部材、つまり制御スリーブ若しくは弁スリーブ２５は、プランジャー状のケーシングピン３３に沿って案内されており、該ケーシングピンは所定の案内直径ｄF を有している。この場合に弁スリーブ２５は縦軸方向運動可能であり、閉鎖位置で、所定の座直径ｄｓの弁座２６に接触しており、したがって、弁スリーブ２５により半径方向外側を画定された高圧側の弁室２２は、逃がし室２４に対して密閉されている。弁スリーブ２５は、案内直径ｄF と座直径（シール直径又は接触線直径）ｄｓとが互いに同じ大きさであるので、圧力をバランスされており、つまり、静止状態では開放方向の圧力も閉鎖方向の圧力も弁スリーブ２５には作用しないようになっている。弁スリーブ２５は閉鎖ばね２７によって負荷（付勢）されており、該閉鎖ばねは弁スリーブ２５に閉鎖力を生ぜしめ、つまり弁スリーブ２５を弁座２６に向けて押圧している。電磁石２８によって弁スリーブ２５は弁座２６から持ち上げられるようになっており、これによって高圧側の弁室２２は逃がし室２４に接続され、ひいては縦軸孔２０を介して制御室１７も逃がし室２４に接続される。 The control piston 9 defines a control chamber 17 at an end opposite to the nozzle body 2, and the control chamber uses an inflow hole 18 and supplies a supply passage through an inflow throttle 19 in the inflow hole. 7 is connected. Further, the control chamber 17 is connected to a high-pressure side valve chamber 22 via a vertical axis hole 20 provided in the holding main body 1 and the control valve main body 21, and the valve chamber is connected via a control valve 23. A low pressure side valve chamber (relief chamber) 24 is connected. The control valve 23 is used for lowering the fuel pressure in the control chamber 17 and has a control member (control component) formed as a control sleeve or valve sleeve 25, the control member, i.e. the control sleeve or the valve sleeve 25 is guided along the plunger-shaped casing pin 33, the casing pin has a predetermined guide diameter d F. In this case, the valve sleeve 25 is movable in the longitudinal direction and, in the closed position, is in contact with a valve seat 26 of a predetermined seat diameter d s and is therefore on the high pressure side defined radially outwardly by the valve sleeve 25. The valve chamber 22 is sealed with respect to the escape chamber 24. The valve sleeve 25 is balanced in pressure because the guide diameter d F and the seat diameter (seal diameter or contact line diameter) d s are equal to each other, that is, in the stationary state, the pressure in the opening direction is also closed. The pressure in the direction does not act on the valve sleeve 25. The valve sleeve 25 is loaded (biased) by a closing spring 27, which generates a closing force on the valve sleeve 25, that is, presses the valve sleeve 25 toward the valve seat 26. The electromagnet 28 lifts the valve sleeve 25 from the valve seat 26, whereby the high pressure side valve chamber 22 is connected to the escape chamber 24, and the control chamber 17 is also connected to the escape chamber 24 via the vertical axis hole 20. Connected to.

燃料噴射弁の機能は従来技術により十分に知られており、ここでは簡単に述べるにとどめる。噴射のためには、電磁石２８は給電され、その結果、弁スリーブ２５を弁座２６から引き離すことになる。これによって、高圧側の弁室２２が、常に低い燃料圧力の作用している逃がし室２４に接続される。縦軸孔２０を介して制御室１７が放圧（圧力降下）され、結果として、制御ピストン９に作用する液力（圧力）は低下し、したがって、ノズルニードル４は、圧力室６内の燃料圧によって開放方向の圧力を受けているので、弁座から離されて、噴射孔５を開放するようになっている。噴射の終了のためには、電磁石２８は無電流状態に切り換えられ、その結果、弁スリーブ２５は閉鎖ばね２７の押圧力（付勢力）に基づき再び弁座１６に接触せしめられる。流入孔１８を介した燃料の流入により、制御室１７内の圧力は再び増大し、ひいては、制御ピストン９に作用する液力が増大し、結果として、最終的に制御ピストン９が再びノズル本体２に向けて運動させられ、ひいてはノズルニードル４を閉鎖位置へ押圧して戻すようになっている。   The function of the fuel injection valve is well known from the prior art and will be briefly described here. For injection, the electromagnet 28 is energized, resulting in the valve sleeve 25 being pulled away from the valve seat 26. Thereby, the valve chamber 22 on the high pressure side is connected to the escape chamber 24 in which a low fuel pressure is always acting. As a result, the hydraulic force (pressure) acting on the control piston 9 is reduced, so that the nozzle needle 4 is allowed to move the fuel in the pressure chamber 6 to the fuel in the pressure chamber 6. Since the pressure in the opening direction is received by the pressure, the injection hole 5 is opened away from the valve seat. In order to end the injection, the electromagnet 28 is switched to a non-current state, and as a result, the valve sleeve 25 is brought into contact with the valve seat 16 again based on the pressing force (biasing force) of the closing spring 27. Due to the inflow of fuel through the inflow hole 18, the pressure in the control chamber 17 increases again, and as a result, the hydraulic force acting on the control piston 9 increases, and as a result, the control piston 9 finally returns to the nozzle body 2 again. In other words, the nozzle needle 4 is pushed back to the closed position.

図２に示してあるように、高圧側の弁室２２は、弁座近傍の領域で弁スリーブ２５の内側の環状突出部（環状段部）２９によって狭くされている。しかしながら、弁スリーブ２５と制御弁本体２１との間の接触線は、内側へ移動しておらず、つまり、ｄｓ≒ｄF である。したがって、制御弁２３は中立状態でやはり力、つまり圧力をバランス（圧力バランス）されており、それというのは、環状突出部（環状段部）２９の両方の段部面２９ａ，２９ｂに作用する液力は、互いに相殺されるからである。換言すれば、環状突出部２９は、軸方向の液力を弁スリーブ２５に生ぜしめるものではない。弁スリーブ２５と弁座２６との間の面積バランスに際して、面積は半径方向外側にも、半径方向内側にも適切に増大される。このような構成により、制御弁２３は閉鎖状態でも著しく圧力バランスされており、バランスに有効な面積は増大され、かつ弁座２６における摩耗の原因となる面圧は著しく減少される。 As shown in FIG. 2, the high-pressure side valve chamber 22 is narrowed by an annular protrusion (annular step portion) 29 inside the valve sleeve 25 in the region near the valve seat. However, the contact line between the valve sleeve 25 and the control valve body 21 does not move inward, that is, d s ≈d F. Therefore, the control valve 23 is also balanced in force, that is, pressure (pressure balance) in the neutral state, which acts on both stepped surfaces 29a and 29b of the annular projecting portion (annular stepped portion) 29. This is because the hydraulic forces cancel each other. In other words, the annular protrusion 29 does not cause the valve sleeve 25 to generate axial hydraulic force. In the area balance between the valve sleeve 25 and the valve seat 26, the area is appropriately increased both radially outward and radially inward. With this configuration, the control valve 23 is significantly pressure balanced even in the closed state, the effective area for balancing is increased, and the contact pressure that causes wear on the valve seat 26 is significantly reduced.

図２ａに示してある実施形態において、弁座２６は、所定の円錐角αK の１つの円錐面によって形成（画成又は画定）されている。弁スリーブ２５はシール縁部３０を有しており、該シール縁部（シールエッジ）は、所定の円錐角αV1（αV1＞αK ）の低圧側の円錐面３０ａと所定の円錐角αV2（αV2＜αK ）の高圧側の円錐面３０ｂ、つまり環状突出部２９の段部面２９ｂとによって画成（規定）されている。換言すれば、両方の円錐面３０ａ，３０ｂの交差部位に所定の直径ｄｓのシール縁部３０が生じ、つまり形成されている。弁座２６における円錐輪郭及び弁スリーブにおける二重円錐輪郭（ダブル円錐輪郭）に基づき、面積バランス（面圧バランス）は、シール縁部３０から出発して半径方向内側でも半径方向外側でも同様に行われている。面積バランスの限界は、半径方向外側では制御弁本体２１の外径ｄａによって画定され、かつ半径方向内側では弁スリーブ２５の内径ｄｉによって画定されている。別の実施形態では、面積バランスの半径方向外側における限界は、弁スリーブ２５における直径ｄａの座境界縁部又は座画定縁部によって画定されるようになっている。ｄｉとｄａとの間の弁座境界は、小さい行程で生じる弁座力、ひいては実施形態毎のばらつきを小さくするものである。 In Aru embodiment shown in Figure 2a, the valve seat 26 is formed (defined or defined) by a single conical surface of the predetermined cone angle alpha K. The valve sleeve 25 has a seal edge 30. The seal edge (seal edge) has a predetermined cone angle α V1 (α V1 > α K ) and a predetermined cone angle α. V2 (α V2 <α K) high-pressure side of the conical surface 30b of, that has been defined (defined) by the stepped portion surface 29b of the annular projection 29. In other words, a seal edge 30 having a predetermined diameter d s is formed, that is, formed at the intersection of both conical surfaces 30a, 30b. Based on the conical contour in the valve seat 26 and the double conical contour (double conical contour) in the valve sleeve, the area balance (surface pressure balance) starts from the seal edge 30 in the same way both radially inward and radially outward. It has been broken. Limit area balance, the radially outward is defined by an outer diameter d a of the control valve body 21, and on the radially inward is defined by the inner diameter d i of the valve sleeve 25. In another embodiment, the limit in the radially outer area balance is adapted to be defined by the seat boundary edge or seat defining edges of the diameter d a of the valve sleeve 25. The valve seat boundary between d i and d a reduces the valve seat force generated in a small stroke, and hence variation among the embodiments.

図２ｂに示してある実施形態において、シール面、並びに弁スリーブ３０の段部面２９ｂは、所定の円錐角αV の１つの円錐面によって形成（画定）されている。弁座２６は、座シール縁部３１を有しており、該座シール縁部は、所定の円錐角αV1（αV1＜αV ）の低圧側の円錐面２６ａと所定の円錐角αV2（αV2＞αV ）の高圧側の円錐面２６ｂとによって画成（規定）されている。換言すれば、両方の円錐面２６ａ，２６ｂの交差部位に所定の直径ｄｓの座シール縁部３１が生じている。弁座２６における二重円錐輪郭及び弁スリーブにおける円錐輪郭に基づき、面積バランスは、座シール縁部３１から出発して半径方向内側でも半径方向外側でも同様に行われている。半径方向外側における面積バランスの画定は、制御弁本体２１の外径ｄａによって行われ、かつ半径方向内側における面積バランスの画定は、弁スリーブ２５の内径ｄｉによって行われている。 In Aru embodiment shown in FIG. 2b, the sealing surface, and a stepped portion surface 29b of the valve sleeve 30 is formed (defined) by a single conical surface of the predetermined cone angle alpha V. The valve seat 26 has a seat seal edge 31. The seat seal edge has a predetermined cone angle α V1 (α V1 <α V ) and a predetermined cone angle α V2. (Α V2 > α V ) and the conical surface 26b on the high pressure side (defined). In other words, the seat sealing edge 31 of a given diameter d s occurs at an intersection of both conical surfaces 26a, 26b. Based on the double conical contour in the valve seat 26 and the conical contour in the valve sleeve, the area balance is similarly performed starting from the seat seal edge 31 both radially inward and radially outward. Defining area balance in the radial direction outwardly, carried out by the outside diameter d a of the control valve body 21, and defines the area balance in radially inwardly is effected by the inner diameter d i of the valve sleeve 25.

図２ｃに示してある実施形態において、弁座２６は、所定の円錐角αK の１つの円錐面によって形成（画定）されている。シール面、並びに弁スリーブ２５の段部面２９ｂは、環状に延びる、つまり全周にわたって延びるトーラス（半径Ｒ）として形成されており、この場合に所定の直径ｄｓで弁座線（接触線）３２が生じており、弁座線（線状接触部）において環状のトーラス（回転円弧面）に対する接線は所定の円錐角αK を有している。弁座２６の円錐輪郭及び弁スリーブ２５のトロイダル状の輪郭に基づき、面積バランスは、弁座線３２から出発して半径方向内側でも半径方向外側でも同様に行われている。半径方向外側における面積バランスの画定は、制御弁本体２１の外径ｄａによって行われ、かつ半径方向内側における面積バランスの画定は、弁スリーブ２５の内径ｄｉによって行われている。図示を省略してあるものの、別の実施形態では逆の配置形式で、つまり弁スリーブのシール面が１つの円錐面によって形成（画定）され、かつ弁座が環状のトーラスによって形成（画定）されていてよいものである。 In Aru embodiment shown in FIG. 2c, the valve seat 26 is formed (defined) by a single conical surface of the predetermined cone angle alpha K. Sealing surface, and the stepped portion surface 29b of the valve sleeve 25, annularly extending, i.e. is formed as torus (radius R) extending over the entire circumference, the valve seating line at a predetermined diameter d s in this case (contact line) 32 occurs, and the tangent to the annular torus (rotating arc surface) in the valve seat line (linear contact portion) has a predetermined cone angle α K. Based on the conical contour of the valve seat 26 and the toroidal contour of the valve sleeve 25, the area balance is similarly performed starting from the valve seat line 32 both radially inward and radially outward. Defining area balance in the radial direction outwardly, carried out by the outside diameter d a of the control valve body 21, and defines the area balance in radially inwardly is effected by the inner diameter d i of the valve sleeve 25. Although not shown, in another embodiment, the arrangement is reversed, i.e., the sealing surface of the valve sleeve is formed (defined) by one conical surface, and the valve seat is formed (defined) by an annular torus. It is good.

図３には、制御弁２３の別の実施形態を示してあり、この場合に同じ若しくは同一機能の構成部分には、図２の符号と同じ符号を付してある。図３に示す制御弁２３は、ここでは弁ニードル２５として形成された弁部材、及び二部構造の弁ケーシング（案内部分３４と座部分３５）を有している。弁ニードル２５は、案内部分３４の軸線方向孔３６内に摺動自在に案内されている。座部分３５は弁座２６を有しており、該弁座は、半径方向で、ここでは環状に形成された高圧側の弁室２２と低圧側の弁室２４との間に設けられている。高圧側の弁室２２には、制御室から到来する高圧管路２０を開口させてある。弁ニードル２５は、高圧側の弁室２２の半径方向内側を画定しており、かつ半径方向で高圧側の弁室２２内へ突出する環状突出部（張り出す環状突出部）を有しており、該環状突出部の、弁座２６に向いている段部面２９ａは、弁座２６と協働（接触）するシール面を画定している。弁座２６の座直径ｄｓと弁ニードル２５の案内直径ｄF とは、有利には互いに同じ大きさである。弁ニードル２５のシール面は、図２ｂの場合と同じように、１つの円錐面によって画定されており、かつ弁座２６は、１つの座シール縁部３１を有しており、該座シール縁部は、低圧側の円錐面２６ａと高圧側の円錐面２６ｂとによって画成（規定）されており、低圧側の円錐面２６ａの円錐角は、弁ニードル２５のシール面の円錐角よりも小さくなっており、かつ高圧側の円錐面２６ｂの円錐角は、弁ニードル２５のシール面の円錐角よりも大きくなっている。 FIG. 3 shows another embodiment of the control valve 23. In this case, components having the same or the same function are denoted by the same reference numerals as those in FIG. The control valve 23 shown in FIG. 3 has a valve member formed here as a valve needle 25 and a two-part valve casing (guide part 34 and seat part 35). The valve needle 25 is slidably guided in the axial hole 36 of the guide portion 34. The seat portion 35 has a valve seat 26, which is provided between the high-pressure side valve chamber 22 and the low-pressure side valve chamber 24 which are formed in an annular shape in the radial direction. . A high-pressure line 20 coming from the control chamber is opened in the valve chamber 22 on the high-pressure side. The valve needle 25 defines an inner side in the radial direction of the valve chamber 22 on the high-pressure side, and has an annular projecting portion (a projecting annular projecting portion) projecting into the valve chamber 22 on the high-pressure side in the radial direction. The stepped surface 29a of the annular projection facing the valve seat 26 defines a sealing surface that cooperates (contacts) with the valve seat 26. The seat diameter d s of the valve seat 26 and the guide diameter d F of the valve needle 25 are preferably of the same size. The sealing surface of the valve needle 25 is defined by one conical surface, as in FIG. 2b, and the valve seat 26 has one seat sealing edge 31, which is the seat sealing edge. The portion is defined (defined) by a low pressure side conical surface 26 a and a high pressure side conical surface 26 b, and the conical angle of the low pressure side conical surface 26 a is smaller than the conical angle of the sealing surface of the valve needle 25. In addition, the cone angle of the conical surface 26 b on the high pressure side is larger than the cone angle of the seal surface of the valve needle 25.

図３に示す制御弁２３の図示省略の実施形態においては、弁座２６と弁ニードル２５のシール面は図２ａ及び図２ｃに示すように形成されている。   In the embodiment of the control valve 23 not shown in FIG. 3, the sealing surfaces of the valve seat 26 and the valve needle 25 are formed as shown in FIGS. 2a and 2c.

１ 保持本体、 ２ ノズル本体、 ３ 締め付けナット、 ４ ノズルニードル、 ５ 噴射孔、 ６ 圧力室、 ７ 供給通路、 ８ 縦軸孔、 ９ 制御ピストン、 １０ 押圧片、 １１ ばね、 １２ 高圧ポンプ、 １３ 燃料タンク、 １４ 蓄圧室、 １５ 高圧管路、 １６ 高圧接続部、 １７ 制御室、 １８ 流入孔、 １９ 流入絞り、 ２０ 縦軸孔、 ２１ 制御弁本体、 ２２ 弁室、 ２３ 制御弁、 ２４ 弁室、 ２５ 弁スリーブ、 ２６ 弁座、 ２７ 閉鎖ばね、 ２８ 電磁石、 ２９ 環状突出部、 ３０，３１ シール縁部、 ３３ ケーシングピン、 ３４ 案内部分、 ３５ 座部分   DESCRIPTION OF SYMBOLS 1 Holding body, 2 Nozzle body, 3 Clamping nut, 4 Nozzle needle, 5 Injection hole, 6 Pressure chamber, 7 Supply passage, 8 Vertical axis hole, 9 Control piston, 10 Pressing piece, 11 Spring, 12 High pressure pump, 13 Fuel Tank, 14 pressure accumulating chamber, 15 high pressure pipe, 16 high pressure connection, 17 control chamber, 18 inflow hole, 19 inflow throttle, 20 vertical axis hole, 21 control valve body, 22 valve chamber, 23 control valve, 24 valve chamber, 25 valve sleeve, 26 valve seat, 27 closing spring, 28 electromagnet, 29 annular projection, 30, 31 seal edge, 33 casing pin, 34 guide part, 35 seat part

Claims (9)

内燃機関のための燃料噴射弁であって、
弁ニードル（４）を含んでおり、該弁ニードルは該弁ニードルの軸線方向運動によって少なくとも１つの噴射孔（５）の開口部を制御するようになっており、
高圧側（１４）に接続された制御室（１７）を含んでおり、該制御室の圧力は少なくとも間接的に前記弁ニードル（４）に作用するようになっており、
制御弁（２３）を含んでおり、該制御弁は、半径方向で、前記制御室（１７）に接続された高圧側の弁室（２２）と低圧側の弁室（２４）との間に設けられた１つの弁座（２６）と、摺動自在に案内された１つの制御弁部材（２５）とを備えており、該制御弁部材は前記高圧側の弁室（２２）を半径方向で画定していて、かつ前記弁座（２６）と協働するようになっている形式のものにおいて、
前記制御弁部材（２５）は、半径方向で前記高圧側の弁室（２２）内へ突出する環状突出部（２９）を有しており、該環状突出部の、前記弁座（２６）に向いている段部面（２９ａ）は、弁座（２６）と協働するシール面を形成していることを特徴とする、内燃機関のための燃料噴射弁。 A fuel injection valve for an internal combustion engine,
A valve needle (4), which is adapted to control the opening of at least one injection hole (5) by axial movement of the valve needle;
A control chamber (17) connected to the high pressure side (14), the pressure of the control chamber acting at least indirectly on the valve needle (4);
A control valve (23), which is radially arranged between the high pressure side valve chamber (22) and the low pressure side valve chamber (24) connected to the control chamber (17). One valve seat (26) provided and one control valve member (25) guided in a slidable manner are provided, and the control valve member defines the valve chamber (22) on the high pressure side in the radial direction. In the form defined by and adapted to cooperate with said valve seat (26),
The control valve member (25) has an annular projection (29) projecting radially into the high pressure side valve chamber (22), and the valve seat (26) of the annular projection is formed on the valve seat (26). Fuel injection valve for an internal combustion engine, characterized in that the facing step surface (29a) forms a sealing surface which cooperates with the valve seat (26). 前記弁座（２６）は、１つの円錐面によって形成されており、前記制御弁部材（２５）の前記シール面はシール縁部（３０）を有しており、該シール縁部は、低圧側の円錐面（３０ａ）と高圧側の円錐面（３０ｂ）とによって画定されており、前記低圧側の円錐面（３０ａ）の円錐角（αV1）は、前記弁座（２６）の円錐角（αK ）よりも大きくなっており、前記高圧側の円錐面（３０ｂ）の円錐角（αV2）は、前記弁座（２６）の円錐角（αK ）よりも小さくなっている請求項１に記載の燃料噴射弁。 The valve seat (26) is formed by one conical surface, and the seal surface of the control valve member (25) has a seal edge (30), which is on the low pressure side. Is defined by a conical surface (30a) and a conical surface (30b) on the high-pressure side, and the conical angle (α V1 ) of the conical surface (30a) on the low-pressure side is the conical angle of the valve seat (26) ( alpha K) is larger than the cone angle of the conical surface of the high-pressure side (30b) (alpha V2) is claim 1 which is smaller than the cone angle (alpha K) of the valve seat (26) The fuel injection valve described in 1. 前記制御弁部材（２５）のシール面は、１つの円錐面によって形成されており、前記弁座（２６）は座シール縁部（３１）を有しており、該座シール縁部は、低圧側の円錐面（２６ａ）と高圧側の円錐面（２６ｂ）とによって画定されており、前記低圧側の円錐面（２６ａ）の円錐角（αK1）は、前記制御弁部材（２５）の円錐角（αV ）よりも小さくなっており、前記高圧側の円錐面（２６ｂ）の円錐角（αK2）は前記制御弁部材（２５）の円錐角（αV ）よりも大きくなっている請求項１に記載の燃料噴射弁。 The sealing surface of the control valve member (25) is formed by a conical surface, the valve seat (26) has a seat sealing edge (31), and the seat sealing edge is low pressure. A conical surface (26a) on the side and a conical surface (26b) on the high pressure side, the cone angle (α K1 ) of the conical surface (26a) on the low pressure side is the cone of the control valve member (25) angle (alpha V) is smaller than the cone angle (alpha K2) is claims is larger than the cone angle of the control valve member (25) (α V) of the conical surface of the high-pressure side (26b) Item 4. The fuel injection valve according to Item 1. 前記弁座（２６）は１つの円錐面によって形成されており、かつ前記制御弁部材（２５）のシール面は環状のトーラスとして形成されており、又は、前記弁座（２６）は環状のトーラスとして形成されており、かつ記制御弁部材（２５）のシール面は１つの円錐面によって形成されている請求項１に記載の燃料噴射弁。   The valve seat (26) is formed by a conical surface and the sealing surface of the control valve member (25) is formed as an annular torus, or the valve seat (26) is an annular torus. The fuel injection valve according to claim 1, wherein the control valve member (25) has a sealing surface formed by a single conical surface. 前記制御弁部材（２５）は、弁スリーブとして形成されている請求項１から４のいずれか１項に記載の燃料噴射弁。   The fuel injection valve according to any one of claims 1 to 4, wherein the control valve member (25) is formed as a valve sleeve. 前記高圧側の弁室（２２）は前記弁スリーブ（２５）内に設けられている請求項５に記載の燃料噴射弁。   The fuel injection valve according to claim 5, wherein the high pressure side valve chamber (22) is provided in the valve sleeve (25). 前記制御弁部材（２５）は、弁ニードルとして形成されている請求項１から４のいずれか１項に記載の燃料噴射弁。   The fuel injection valve according to any one of claims 1 to 4, wherein the control valve member (25) is formed as a valve needle. 前記弁座（２６）の座直径（ｄｓ）と前記制御弁部材（２５）の案内直径（ｄF ）とは互いに同じ大きさである請求項１から７のいずれか１項に記載の燃料噴射弁。 The fuel according to the seat diameter (d s) and any one of the guide diameter (d F) from claim 1 are mutually the same size 7 of the control valve member (25) of the valve seat (26) Injection valve. 前記弁座（２６）の座直径（ｄｓ）は、前記制御弁部材（２５）の案内直径（ｄF ）よりも小さくなっており、又は前記制御弁部材（２５）の案内直径（ｄF ）よりも大きくなっている請求項１から７のいずれか１項に記載の燃料噴射弁。 Seat diameter of the valve seat (26) (d s), the guide diameter (d F of the control valve guide diameter member (25) (d F) which is smaller than, or the control valve member (25) The fuel injection valve according to any one of claims 1 to 7, wherein the fuel injection valve is larger than.
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