JP2006522887A - Fuel injection valve for internal combustion engine - Google Patents

Fuel injection valve for internal combustion engine Download PDF

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Publication number
JP2006522887A
JP2006522887A JP2006504224A JP2006504224A JP2006522887A JP 2006522887 A JP2006522887 A JP 2006522887A JP 2006504224 A JP2006504224 A JP 2006504224A JP 2006504224 A JP2006504224 A JP 2006504224A JP 2006522887 A JP2006522887 A JP 2006522887A
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conical section
fuel injection
valve
injection passage
injection valve
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ユルゲン　シューベルト
グロータ ベアーテ
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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1846—Dimensional characteristics of discharge orifices
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

本発明は、弁本体（１）を備えた燃料噴射弁であって、弁本体（１）内に圧力室（１９）が形成されていて、該圧力室（１９）の壁に、少なくとも１つの噴射通路（１１）の流入開口（３０）が配置されており、該噴射通路（１１）が弁本体（１）内を延びていて、弁本体（１）の外側において流出開口（３２）を形成している形式のものに関する。このような形式の燃料噴射弁おいて本発明の構成では、噴射通路（１１）が流れ方向で見て第１の円錐形区分（３５）と、該第１の円錐形区分に接続する第２の円錐形区分（３７）とを有しており、両円錐形区分（３５，３７）が流れ方向において先細になっていて、互いに異なった開放角（α１；α２）を有している。The present invention is a fuel injection valve provided with a valve body (1), wherein a pressure chamber (19) is formed in the valve body (1), and at least one of the pressure chambers (19) is formed on a wall of the pressure chamber (19). An inflow opening (30) of the injection passage (11) is arranged, the injection passage (11) extends in the valve body (1), and forms an outflow opening (32) outside the valve body (1). It is related to the format. In the fuel injection valve of this type, according to the configuration of the present invention, the injection passage (11) is viewed in the flow direction, and the first conical section (35) and the second conical section connected to the first conical section. Conical sections (37) and both conical sections (35, 37) are tapered in the flow direction and have different opening angles (α 1 ; α 2 ). .

Description

本発明は、ヨーロッパ特許公開第３５２９２６号明細書に基づいて公知の、内燃機関用の燃料噴射弁に関する。このような燃料噴射弁は、内部に圧力室が形成されている弁本体を有している。圧力室の壁からは、少なくとも１つの噴射通路が延びている。そして噴射通路の噴射開口は圧力室の壁に配置されており、これに対して流入開口は弁本体の外側に設けられている。   The present invention relates to a fuel injection valve for an internal combustion engine, known from EP-A-352926. Such a fuel injection valve has a valve body in which a pressure chamber is formed. At least one injection passage extends from the wall of the pressure chamber. The injection opening of the injection passage is arranged on the wall of the pressure chamber, whereas the inflow opening is provided outside the valve body.

従来技術に基づいて、噴射通路の種々様々なジオメトリが公知である。例えばヨーロッパ特許公開第３５２９２６号明細書に開示された噴射通路は、等しい形状で円錐形に形成されている。燃料は、円錐形に収斂する噴射通路によって加速され、高い流出速度で、かつそれに基づいて良好に霧化されて、内燃機関の燃焼室に噴射される。同じ形で円錐形に形成された噴射通路にはしかしながら次のような欠点がある。すなわちこのような噴射通路では、噴射通路への燃料の流入時に燃料流が比較的強く変向され、ひいては大きなエネルギ損失が発生し、その結果、有効な噴射圧が低くなってしまう。これにより霧化の程度が減じられ、燃料の最適な燃焼が損なわれてしまう。   Based on the prior art, various different geometries of the injection passage are known. For example, the injection passage disclosed in European Patent Publication No. 352926 is formed in an equal shape and a conical shape. The fuel is accelerated by an injection passage converging in a conical shape, and is atomized well at a high outflow speed and injected into the combustion chamber of the internal combustion engine. However, the injection passage formed in the same shape and conically has the following drawbacks. That is, in such an injection passage, when the fuel flows into the injection passage, the fuel flow is changed relatively strongly, and as a result, a large energy loss occurs, and as a result, the effective injection pressure is lowered. This reduces the degree of atomization and impairs optimal combustion of the fuel.

発明の利点
請求項１の特徴部に記載のように構成された本発明による燃料噴射弁には、公知のものに比べて、次のような利点がある。すなわち本発明による燃料噴射弁では、噴射通路が簡単に製造可能なジオメトリを有しており、噴射通路への燃料の流入時における変向損失が僅かしか発生せず、ひいては燃料噴流の良好な霧化と方向安定性とが得られる。そのために噴射通路は、長手方向で見て第１の円錐形区分と該第１の円錐形区分に接続する第２の円錐形区分とを有している。そして両円錐形区分は流れ方向において先細になっており、その結果噴射通路の横断面は、流入開口から流出開口に向かって減じられている。 Advantages of the Invention The fuel injection valve according to the present invention configured as described in the characterizing portion of claim 1 has the following advantages over the known ones. In other words, in the fuel injection valve according to the present invention, the injection passage has a geometry that can be easily manufactured, and only a small deflection loss occurs when the fuel flows into the injection passage. And directional stability are obtained. To that end, the injection passage has a first conical section and a second conical section connected to the first conical section as viewed in the longitudinal direction. The conical sections are then tapered in the flow direction, so that the cross section of the injection passage is reduced from the inflow opening towards the outflow opening.

噴射通路が、異なった開放角を備えた２つの別個の円錐形区分に分割されていることによって、それぞれの円錐形区分が別個の機能を引き受けることができ、それぞれの機能に各円錐形区分は個別に合わせられている。例えば強い円錐度は噴射通路内における燃料の高い加速を生ぜしめ、これに対して小さな円錐度は、主として良好な方向安定性を得るために寄与するので、噴射噴流は正確に燃焼室の所定の室領域に達する。噴射通路への燃料の流入時における変向損失が、従属的な役割しか果たさない場合には、両方の円錐形区分のうちのどちらが大きな円錐度を有するべきであるかは、自由に選択することができる。   By dividing the injection passage into two separate conical sections with different opening angles, each conical section can take on a separate function, with each cone section having a respective function. It is tailored individually. For example, a strong conicity results in a high acceleration of the fuel in the injection passage, whereas a small conicity contributes mainly to obtain a good directional stability, so that the injection jet is exactly the predetermined predetermined in the combustion chamber. Reach the room area. If the turning loss during the flow of fuel into the injection passage plays a subordinate role, it is free to choose which of both conical sections should have a greater degree of conicity. Can do.

本発明による燃料噴射弁の別の有利な構成は、請求項２以下に記載されている。   Another advantageous configuration of the fuel injection valve according to the invention is described in claims 2 and below.

本発明による燃料噴射弁の有利な構成では、噴射通路の第１の円錐形区分の開放角が、第２の円錐形区分の開放角よりも大きくなっている。このように構成されていると、燃料は噴射通路への流入時に僅かだけ方向転換をすればよく、当該箇所におけるエネルギ損失を減じることができる。小さな開口角を有する第２の円錐形区分によって、噴射噴流の良好な方向安定性と同時に、良好な霧化が得られる。この場合、第１の円錐形区分と第２の円錐形区分との間の移行部に形成された移行縁部が、丸く面取りされて形成されていると、特に有利である。これによって噴射通路においては僅かな乱流しか生ぜしめられず、ひいてはキャビテーションのおそれが減じられる。   In an advantageous configuration of the fuel injection valve according to the invention, the opening angle of the first conical section of the injection passage is greater than the opening angle of the second conical section. If comprised in this way, the fuel should just change a direction at the time of the inflow to an injection channel, and can reduce the energy loss in the said location. The second conical section with a small opening angle provides good atomization as well as good directional stability of the jet. In this case, it is particularly advantageous if the transition edge formed at the transition between the first conical section and the second conical section is rounded and chamfered. As a result, only a slight turbulent flow is generated in the injection passage, which in turn reduces the risk of cavitation.

本発明の別の有利な構成では、第１の円錐形区分の長さが第２の円錐形区分の長さよりも大きい。このように第１の円錐形区分が長く構成されていると、燃料は噴射通路内において効果的に加速され、これに対して燃料噴流の方向安定性の機能のためには、短い第２の円錐形区分が十分に働く。このような場合、第１の円錐形区分の長さが、第２の円錐形区分の長さよりも３倍〜１０倍大きいと、特に有利である。   In another advantageous configuration of the invention, the length of the first conical section is greater than the length of the second conical section. Thus, if the first conical section is configured to be long, the fuel is effectively accelerated in the injection passage, whereas for the function of directional stability of the fuel jet, a short second The conical section works well. In such a case, it is particularly advantageous if the length of the first conical section is 3 to 10 times greater than the length of the second conical section.

本発明のさらに別の有利な構成では、第１の円錐形区分が第２の円錐形区分よりも小さな開放角を有している。この噴射弁における特殊な状態に基づいて、噴射通路への燃料の流入時における変向損失に大きな意味がない場合には、噴射通路の円錐形区分のこの構成において、方向安定性に関する最適化を行うことができる。   In a further advantageous configuration of the invention, the first conical section has a smaller opening angle than the second conical section. Based on the special condition of this injection valve, if the deflection loss at the time of the fuel flow into the injection passage is not significant, this configuration of the conical section of the injection passage can be optimized for directional stability. It can be carried out.

図面
次に図面を参照しながら、本発明による燃料噴射弁の複数の実施例を説明する。 Drawings Next, a plurality of embodiments of a fuel injection valve according to the present invention will be described with reference to the drawings.

図１は、本発明による燃料噴射弁を示す縦断面図であり、
図２は、図１に示された燃料噴射弁の噴射通路の領域を拡大して示す図であり、
図３は、相応な幾何学寸法を備えた噴射通路をさらに拡大して示す図であり、
図４は、本発明による燃料噴射弁の噴射通路の別の実施例を示す図であり、
図５は、本発明による燃料噴射弁の噴射通路のさらに別の実施例を示す図である。 FIG. 1 is a longitudinal sectional view showing a fuel injection valve according to the present invention,
FIG. 2 is an enlarged view showing a region of an injection passage of the fuel injection valve shown in FIG.
FIG. 3 is a further enlarged view of an injection passage having a corresponding geometric dimension,
FIG. 4 is a view showing another embodiment of the injection passage of the fuel injection valve according to the present invention,
FIG. 5 is a view showing still another embodiment of the injection passage of the fuel injection valve according to the present invention.

実施例の記載
図１には、本発明による燃料噴射弁が縦断面図で示されている。弁本体１には盲孔３によって圧力室１９が形成されており、この圧力室１９は中央区分において半径方向に拡大されていて、残りの弁本体１は圧力室１９の周りに壁を形成している。圧力室１９の半径方向拡大部には、弁本体１内を延びている供給通路２５が開口しており、この供給通路２５を介して圧力室１９には、高圧下の燃料を満たすことができる。盲孔３の燃焼室側の端部には、円錐形の弁座９が形成されており、この弁座９からは、少なくとも１つの、しかしながら通常は複数の噴射通路１１が延びており、これらの噴射通路１１は燃料噴射弁の取付け状態において内燃機関の燃焼室に開口している。盲孔３にはピストン状の弁ニードル５が長手方向摺動可能に配置されている。弁ニードル５は、燃焼室とは反対側に位置する案内される区分１５で、盲孔３の案内区分２３においてシール作用をもって案内され、受圧肩部１３を形成しながら弁座９に向かって先細になっており、受圧肩部１３は圧力室１９の半径方向拡大部に配置されている。弁ニードル５の燃焼室側の端部には、ほぼ円錐形の弁シール面７が形成されており、この弁シール面７で弁ニードル５は弁座９と共働する。 DESCRIPTION OF THE EMBODIMENTS FIG. 1 shows a fuel injection valve according to the present invention in a longitudinal sectional view. A pressure chamber 19 is formed in the valve body 1 by a blind hole 3, which is enlarged radially in the central section and the remaining valve body 1 forms a wall around the pressure chamber 19. ing. A supply passage 25 extending through the valve body 1 is opened in the radially enlarged portion of the pressure chamber 19, and the pressure chamber 19 can be filled with fuel under high pressure via the supply passage 25. . A conical valve seat 9 is formed at the end of the blind hole 3 on the combustion chamber side, and at least one, but usually, a plurality of injection passages 11 extend from the valve seat 9. The injection passage 11 is open to the combustion chamber of the internal combustion engine when the fuel injection valve is attached. A piston-shaped valve needle 5 is disposed in the blind hole 3 so as to be slidable in the longitudinal direction. The valve needle 5 is a guided section 15 located on the opposite side of the combustion chamber and is guided with a sealing action in the guide section 23 of the blind hole 3, and tapers toward the valve seat 9 while forming a pressure receiving shoulder 13. The pressure receiving shoulder 13 is disposed in the radially expanded portion of the pressure chamber 19. A substantially conical valve seal surface 7 is formed at the end of the valve needle 5 on the combustion chamber side, and the valve needle 5 cooperates with the valve seat 9 on the valve seal surface 7.

弁ニードル５は燃焼室とは反対側の端部において閉鎖力によって負荷され、この閉鎖力は例えば、図示されていないばねエレメントによって生ぜしめられ、このばねエレメントによって弁ニードル５は弁座９に押し付けられる。この閉鎖力とは逆方向に、受圧肩部１３に対して液圧力が作用する。ばね力と液圧力とのどちらが上回っているかに応じて、弁ニードル５は弁座９から離反運動して噴射通路１１を開放するか、又は弁ニードル５は閉鎖力によって弁座９に押し付けられて、噴射通路１１が閉鎖される。弁ニードル５の開放された状態において燃料は、圧力室１９から噴射通路１１に流れ、さらにこの圧力室１９から内燃機関の燃焼室に噴射される。この噴射は高圧下で行われるので、燃料の良好な霧化が達成され、ひいては有害物質の少ない燃料が達成される。   The valve needle 5 is loaded by a closing force at the end opposite to the combustion chamber, and this closing force is generated, for example, by a spring element (not shown), which presses the valve needle 5 against the valve seat 9. It is done. The liquid pressure acts on the pressure-receiving shoulder 13 in the direction opposite to the closing force. Depending on whether the spring force or the hydraulic pressure is higher, the valve needle 5 moves away from the valve seat 9 to open the injection passage 11 or the valve needle 5 is pressed against the valve seat 9 by a closing force. The injection passage 11 is closed. In a state where the valve needle 5 is opened, the fuel flows from the pressure chamber 19 to the injection passage 11 and is injected from the pressure chamber 19 into the combustion chamber of the internal combustion engine. Since this injection is performed under high pressure, good atomization of the fuel is achieved, and as a result, a fuel with less harmful substances is achieved.

図２には、図１に示された燃料噴射弁の弁座９の領域が拡大されて示されている。噴射通路１１は流入開口３０を有しており、この流入開口３０は弁座９に配置されている。噴射通路１１の流出開口３２は弁本体１の外側に位置しており、その結果噴射通路１１は圧力室１９の壁を貫通している。噴射通路１１は第１の円錐形区分３５と第２の円錐形区分３７とを有しており、両区分３５，３７は互いに隣接している。第１の円錐形区分３５から第２の円錐形区分３７への移行部には、移行縁部３８が形成されており、この移行縁部３８は噴射通路１１の軸方向で見て例えば、流入開口３０と流出開口３２との間の真ん中に配置されている。図２には燃料噴射弁が開放された状態で示されており、つまり弁ニードル５は弁座９から持ち上がっている。これによって燃料は高圧下で圧力室１９から弁シール面７と弁座９との間を通って噴射通路１１に流れ込む。燃料は流入開口３０を通って噴射通路１１に流入し、この場合方向を変化させなくてはならず、この方向転換時にエネルギ損失が生じ、これにより有効噴射圧が低下する。第１の円錐形区分３５が円錐形に収斂する形状を有していることによって、燃料流は加速される。それというのは、横断面が流れ方向で見て連続的に減じられるからである。移行縁部３８を横断した後で燃料は第２の円錐形区分３７に達し、この第２の円錐形区分３７は小さな開口角を有しているので、燃料はここにおいて確かにさらに加速されるが、しかしながら第１の円錐形区分３５におけるほどには強く加速されず、このことは、噴射される燃料噴流の良好な一方向安定性に寄与する。   FIG. 2 shows an enlarged region of the valve seat 9 of the fuel injection valve shown in FIG. The injection passage 11 has an inflow opening 30, which is arranged in the valve seat 9. The outflow opening 32 of the injection passage 11 is located outside the valve body 1, and as a result, the injection passage 11 passes through the wall of the pressure chamber 19. The injection passage 11 has a first conical section 35 and a second conical section 37, which are adjacent to each other. A transition edge 38 is formed at the transition from the first conical section 35 to the second conical section 37 and this transition edge 38 is, for example, inflow in the axial direction of the injection passage 11. It is disposed in the middle between the opening 30 and the outflow opening 32. FIG. 2 shows the fuel injection valve in an open state, that is, the valve needle 5 is lifted from the valve seat 9. As a result, the fuel flows into the injection passage 11 from the pressure chamber 19 through the space between the valve seal surface 7 and the valve seat 9 under high pressure. The fuel flows into the injection passage 11 through the inflow opening 30 and in this case the direction must be changed, and energy loss occurs during this change of direction, thereby reducing the effective injection pressure. By having the shape of the first conical section 35 converging in a conical shape, the fuel flow is accelerated. This is because the cross section is continuously reduced when viewed in the flow direction. After traversing the transition edge 38, the fuel reaches the second conical section 37, which has a small opening angle, so that the fuel is certainly accelerated further here. However, it is not accelerated as strongly as in the first conical section 35, which contributes to good unidirectional stability of the injected fuel jet.

図３には噴射通路１１がさらに拡大されて示されている。第１の円錐形区分３５は開放角α１を有しており、この開口角α１は、第２の円錐形区分３７の開放角α２よりも大きい。第１の円錐形区分３５の長さはａで示されており、この場合長さａは有利には、第２の円錐形区分３７の長さｂよりも大きい。噴射噴流の形状に対する要求に応じて、長さａと長さｂとの比は任意に変化させることができる。第１の円錐形区分３５が、第２の円錐形区分３７の長さｂよりも３〜１０倍大きい長さａを有していると、特に有利であることが判明している。流入開口３０に形成された流入縁部４０は有利には丸く面取りされて形成されており、これによって当該領域における流れの剥離を回避すること及び変向損失を減じることができる。流出開口３２に形成された流出縁部４２はこれに対して丸く面取りされていても角張って形成されていてもよく、これによって、流出開口３２の噴射圧及び直径に応じて燃料噴流のより良好な霧化が生ぜしめる。 In FIG. 3, the injection passage 11 is further enlarged. The first conical segment 35 has an open angle alpha 1, the opening angle alpha 1 is larger than the opening angle alpha 2 of the second conical segment 37. The length of the first conical section 35 is indicated by a, where the length a is advantageously greater than the length b of the second conical section 37. Depending on the requirements for the shape of the jet, the ratio of length a to length b can be varied arbitrarily. It has been found to be particularly advantageous if the first conical section 35 has a length a that is 3 to 10 times greater than the length b of the second conical section 37. The inflow edge 40 formed in the inflow opening 30 is preferably formed with a rounded chamfer, so that flow separation in this region can be avoided and deflection losses can be reduced. The outflow edge 42 formed in the outflow opening 32 may be rounded or chamfered with respect thereto, so that a better fuel jet is produced depending on the injection pressure and diameter of the outflow opening 32. Neat atomization.

図４には本発明による噴射通路１１の別の実施例が示されている。噴射通路１１の構造は、図３に示された噴射通路１１の構造に相当しているが、第１の円錐形区分３５から第２の円錐形の区分３７への移行部に形成された移行縁部３８は、丸く面取りされている。移行縁部３８のこのような丸み付けは、大量の燃料を高い速度で噴射通路１１を通して流したい場合に、特に有利である。第１の円錐形区分３５と第２の円錐形の区分３７との間における移行部が角張っている場合には、この箇所において、噴射通路１１の壁からの燃料の流れ剥離が生じる可能性があり、これは、高められた流過抵抗として、ひいては低い有効噴射圧として現れる。   FIG. 4 shows another embodiment of the injection passage 11 according to the present invention. The structure of the injection passage 11 corresponds to the structure of the injection passage 11 shown in FIG. 3, but the transition formed at the transition from the first conical section 35 to the second conical section 37. The edge 38 is rounded and chamfered. Such rounding of the transition edge 38 is particularly advantageous when it is desired to flow a large amount of fuel through the injection passage 11 at a high velocity. If the transition between the first conical section 35 and the second conical section 37 is angular, fuel flow separation from the wall of the injection passage 11 may occur at this location. Yes, this manifests itself as an increased flow resistance and thus a low effective injection pressure.

図５には、本発明による噴射通路１１のさらに別の実施例が示されている。第１の円錐形区分３５の開口角α１と第２の円錐形区分３７の開口角α２との比は、上に述べた実施例とは逆になっており、つまり第１の円錐形区分３５の開口角α１は、第２の円錐形区分３７の開口角α２よりも小さい。この実施例においても、燃料の良好な霧化と同時に噴射噴流の良好な方向安定性とを保証する噴射通路１１が得られるが、この実施例における噴射通路１１の主機能は良好な霧化である。第１の円錐形区分３５は小さな円錐度をもって、つまり比較的小さな開口角α１をもって形成されているので、横断面は流出開口３２に向かってゆっくりとしか減少していない。これによって圧力損失は制限され、方向安定性が生ぜしめられる。第２の円錐形区分３７は比較的強く円錐形になっており、つまり大きな開口角α２をもって形成されている。これによって、噴射通路１１からの流出前における燃料の十分な加速を保証することができる。 FIG. 5 shows a further embodiment of the injection passage 11 according to the invention. The ratio of the aperture angle alpha 1 of the first conical segment 35 with an opening angle alpha 2 of the second conical segment 37, from the embodiment described above is reversed, i.e. first conical The opening angle α 1 of the section 35 is smaller than the opening angle α 2 of the second conical section 37. In this embodiment as well, an injection passage 11 is obtained that ensures good atomization of the fuel and at the same time good directional stability of the injection jet. The main function of the injection passage 11 in this embodiment is good atomization. is there. Since the first conical section 35 is formed with a small conicity, ie with a relatively small opening angle α 1 , the cross section decreases only slowly towards the outflow opening 32. This limits pressure loss and provides directional stability. Has become a second conical segment 37 is relatively strong conical, it is formed that is with a large opening angle alpha 2. Thereby, sufficient acceleration of the fuel before flowing out from the injection passage 11 can be ensured.

噴射通路１１の全長は、燃料噴射弁の型式に応じて０.５〜２ｍｍの間である。流出開口３２の直径は６０μｍ〜１５０μｍであり、これに対して流入開口３０の直径は少なくとも２０μｍの大きさ、有利には２０μｍ〜６０μｍである。   The total length of the injection passage 11 is between 0.5 and 2 mm depending on the type of the fuel injection valve. The diameter of the outflow opening 32 is 60 μm to 150 μm, whereas the diameter of the inflow opening 30 is at least 20 μm in size, preferably 20 μm to 60 μm.

本発明による燃料噴射弁を示す縦断面図である。It is a longitudinal cross-sectional view which shows the fuel injection valve by this invention. 図１に示された燃料噴射弁の噴射通路の領域を拡大して示す図である。It is a figure which expands and shows the area | region of the injection path of the fuel injection valve shown by FIG. 相応な幾何学寸法を備えた噴射通路をさらに拡大して示す図である。It is a figure which expands further and shows the injection path provided with the corresponding geometric dimension. 本発明による燃料噴射弁の噴射通路の別の実施例を示す図である。It is a figure which shows another Example of the injection path of the fuel injection valve by this invention. 本発明による燃料噴射弁の噴射通路のさらに別の実施例を示す図である。It is a figure which shows another Example of the injection path of the fuel injection valve by this invention.

Claims (10)

内燃機関用の燃料噴射弁であって、弁本体（１）内に圧力室（１９）が形成されていて、該圧力室（１９）の壁に、少なくとも１つの噴射通路（１１）の流入開口（３０）が配置されており、該噴射通路（１１）が弁本体（１）内を延びていて、弁本体（１）の外側において流出開口（３２）を形成している形式のものにおいて、噴射通路（１１）が流れ方向で見て第１の円錐形区分（３５）と、該第１の円錐形区分に接続する第２の円錐形区分（３７）とを有しており、両円錐形区分（３５，３７）が流れ方向において先細になっていて、互いに異なった開放角（α１；α２）を有していることを特徴とする、内燃機関用の燃料噴射弁。 A fuel injection valve for an internal combustion engine, wherein a pressure chamber (19) is formed in a valve body (1), and an inflow opening of at least one injection passage (11) is formed in a wall of the pressure chamber (19). (30) is disposed, the injection passage (11) extends in the valve body (1), and forms an outflow opening (32) outside the valve body (1). The injection passage (11) has a first conical section (35) as viewed in the flow direction and a second conical section (37) connected to the first conical section. A fuel injection valve for an internal combustion engine, characterized in that the shape sections (35, 37) are tapered in the flow direction and have different opening angles (α 1 ; α 2 ). 圧力室（１９）が、弁本体（１）内を延びる盲孔（３）として形成されていて、該盲孔（３）の底部に弁座（９）が形成されていて、該弁座（９）に噴射通路（１１）の流入開口（３０）が配置されている、請求項１記載の燃料噴射弁。   The pressure chamber (19) is formed as a blind hole (3) extending in the valve body (1), and a valve seat (9) is formed at the bottom of the blind hole (3). 9. The fuel injection valve according to claim 1, wherein the inflow opening (30) of the injection passage (11) is arranged in 9). 盲孔（３）内に弁ニードル（５）が長手方向摺動可能に配置されており、該弁ニードル（５）がその燃焼室側の端部に弁シール面（７）を有しており、該弁シール面（７）で弁ニードル（５）が弁座（９）と共働して、噴射通路（１１）の流入開口（３０）を開閉する、請求項２記載の燃料噴射弁。   A valve needle (5) is disposed in the blind hole (3) so as to be slidable in the longitudinal direction, and the valve needle (5) has a valve seal surface (7) at its end on the combustion chamber side. The fuel injection valve according to claim 2, wherein the valve needle (5) cooperates with the valve seat (9) at the valve seal surface (7) to open and close the inflow opening (30) of the injection passage (11). 弁座（９）が円錐面を形成している、請求項２記載の燃料噴射弁。   3. The fuel injection valve according to claim 2, wherein the valve seat (9) forms a conical surface. 第１の円錐形区分（３５）の開放角（α１）が、第２の円錐形区分（３７）の開放角（α２）よりも大きい、請求項１記載の燃料噴射弁。 The fuel injection valve according to claim 1, wherein the opening angle (α 1 ) of the first conical section (35) is larger than the opening angle (α 2 ) of the second conical section (37). 第１の円錐形区分（３５）の開放角（α１）が、第２の円錐形区分（３７）の開放角（α２）よりも小さい、請求項１記載の燃料噴射弁。 The fuel injection valve according to claim 1, wherein the opening angle (α 1 ) of the first conical section (35) is smaller than the opening angle (α 2 ) of the second conical section (37). 第１の円錐形区分（３５）から第２の円錐形区分（３７）への移行部に形成された移行縁部（３８）が、丸く面取りされている、請求項１記載の燃料噴射弁。   The fuel injection valve according to claim 1, wherein the transition edge (38) formed at the transition from the first conical section (35) to the second conical section (37) is rounded and chamfered. 壁から噴射通路（１１）の流入開口（３０）への移行部に形成された流入縁部（４０）が丸く面取りされて形成されている、請求項１記載の燃料噴射弁。   The fuel injection valve according to claim 1, wherein the inflow edge (40) formed at the transition from the wall to the inflow opening (30) of the injection passage (11) is rounded and chamfered. 第１の円錐形区分（３５）の長さ（ａ）が第２の円錐形区分（３７）の長さ（ｂ）よりも大きい、請求項１記載の燃料噴射弁。   The fuel injection valve according to claim 1, wherein the length (a) of the first conical section (35) is greater than the length (b) of the second conical section (37). 第１の円錐形区分（３５）の長さ（ａ）が、第２の円錐形区分（３７）の長さ（ｂ）よりも３倍〜１０倍大きい、請求項９記載の燃料噴射弁。   The fuel injection valve according to claim 9, wherein the length (a) of the first conical section (35) is 3 to 10 times greater than the length (b) of the second conical section (37).
JP2006504224A 2003-04-08 2004-01-23 Fuel injection valve for internal combustion engine Pending JP2006522887A (en)

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