JP2004204850A - Fuel injection valve for internal combustion engine - Google Patents

Fuel injection valve for internal combustion engine Download PDF

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Publication number
JP2004204850A
JP2004204850A JP2003425670A JP2003425670A JP2004204850A JP 2004204850 A JP2004204850 A JP 2004204850A JP 2003425670 A JP2003425670 A JP 2003425670A JP 2003425670 A JP2003425670 A JP 2003425670A JP 2004204850 A JP2004204850 A JP 2004204850A
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Prior art keywords
valve
contact surface
fuel injection
blind hole
injection valve
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JP2003425670A
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Japanese (ja)
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Andreas Koeninger
ケーニンガー アンドレーアス
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Robert Bosch GmbH
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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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To improve sealing at a contact surface of a valve body in a fuel injection valve. <P>SOLUTION: This fuel injection valve for an internal combustion engine is formed with a ring groove on the side of the contact surface of a dead-end hole in the valve body. The ring groove is expanded by high-pressure fuel in the dead-end hole, so that a range for an opening of the dead-end hole is lifted at the contact surface a little, the contact surface of the valve body is pressed against another component member, and the surface pressure for the opening of the dead-end hole is increased, thus improving sealing. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

本発明は、内燃機関のための燃料噴射弁に関する。   The invention relates to a fuel injection valve for an internal combustion engine.

このような燃料噴射弁は、ドイツ連邦共和国特許出願公開第１００２４７０３号明細書から公知である。この燃料噴射弁は、弁体を備えており、この弁体に袋穴が形成されており、この袋穴は弁体の接触面から出発しており、袋穴の閉鎖端部に複数の噴射開口が形成されており、これらの噴射開口は、内燃機関に燃料噴射弁を組み付けた状態で燃焼室に開口している。袋穴には、弁ニードルが縦方向移動可能に配置されており、この弁ニードルは燃焼室側の端部で、弁体に形成された弁座と協働して、噴射開口を開閉する。弁ニードルと袋穴の壁との間に残るスペースは、流入管路を介して高圧下の燃料で充填され、この燃料は、弁ニードルが噴射開口を開放すると、噴射開口を通って燃焼室に噴射される。   Such a fuel injector is known from DE 100 24 703 A1. The fuel injection valve includes a valve body, and a blind hole is formed in the valve body. The blind hole starts from a contact surface of the valve body, and a plurality of injection holes are provided at a closed end of the blind hole. Openings are formed, and these injection openings open to the combustion chamber with the fuel injection valve assembled to the internal combustion engine. A valve needle is arranged in the blind hole so as to be movable in the vertical direction. The valve needle cooperates with a valve seat formed on the valve body at the end on the combustion chamber side to open and close the injection opening. The space remaining between the valve needle and the wall of the blind hole is filled with fuel under high pressure via the inlet line, which fuel passes through the injection opening to the combustion chamber when the valve needle opens the injection opening. It is injected.

弁体は、袋穴の出発する接触面で、燃料噴射弁の別の構成部材、たとえば中間ディスクまたは保持体の接触面に接触している。弁体は、緊締装置、たとえば緊締ナットによって別の構成部材に押圧されており、これによって接触面で袋穴の適当なシールが維持される。しかしながら袋穴における高圧によって、弁体と別の構成部材との間で漏れが生じる。なぜならば緊締装置による力は任意に高めることができず、比較的大きな接触面に基づいてごく僅かな面圧しか達成することができないからである。
ドイツ連邦共和国特許出願公開第１００２４７０３号明細書 The valve body is in contact with another component of the fuel injection valve at the starting contact surface of the blind hole, for example, the contact surface of the intermediate disk or the holder. The valve body is pressed against another component by a clamping device, for example a clamping nut, so that a suitable seal of the blind hole is maintained at the contact surface. However, the high pressure in the blind hole causes a leak between the valve body and another component. This is because the force of the clamping device cannot be increased arbitrarily and only a small surface pressure can be achieved on the basis of the relatively large contact surface.
DE 100 24 703 A1

したがって本発明の課題は、冒頭で述べたような形式の燃料噴射弁を改良して、従来技術の欠点を解消することである。   It is therefore an object of the present invention to improve a fuel injector of the type mentioned at the outset and to overcome the disadvantages of the prior art.

この課題を解決するための本発明の装置によれば、接触面に対して間隔をおいて、弁体の袋穴にリング溝が形成されている。   According to the device of the present invention for solving this problem, a ring groove is formed in the blind hole of the valve body at a distance from the contact surface.

請求項１に記載の構成を備えた本発明の燃料噴射弁の有する利点によれば、弁体の接触面におけるシールが改善される。このために弁体の袋穴において、接触面の傍にリング溝が形成されている。袋穴における高圧燃料によって、リング溝の拡張が生じるので、接触面において袋穴の開口をめぐる領域が僅かに持ち上げられ、（弁体の接触面が）別の構成部材に押し付けられる。これによって袋穴の開口をめぐる面圧が高まり、その結果としてシールが改善される。   According to the advantages of the fuel injection valve of the present invention having the configuration described in claim 1, the sealing at the contact surface of the valve body is improved. For this purpose, a ring groove is formed near the contact surface in the blind hole of the valve body. The high-pressure fuel in the blind hole causes an expansion of the ring groove, so that the area surrounding the opening of the blind hole in the contact surface is raised slightly and pressed against another component (the contact surface of the valve body). This increases the surface pressure around the opening of the blind hole and consequently improves the seal.

シールの理想的な作用は、１〜３ｍｍの深さを有するリング溝で得られ、この場合接触面に対する間隔は有利には０．５〜１．５ｍｍであるのが望ましい。   The ideal action of the seal is obtained with a ring groove having a depth of 1 to 3 mm, in which case the distance to the contact surface is preferably 0.5 to 1.5 mm.

リング溝による切欠効果を制限して、安定性の減少に抗して作用させるために、有利にはリング溝の横断面を半円状に選択する。この場合リング溝の領域においてシャープなエッジを回避するのが望ましい。なぜならば１５０ＭＰａまでの高圧が存在する場合に、これによって生じる切欠応力によって、弁体の著しい安定性低下がもたらされ得るからである。   In order to limit the notch effect of the ring groove and to counteract the reduced stability, the cross-section of the ring groove is preferably selected to be semicircular. In this case, it is desirable to avoid sharp edges in the region of the ring groove. This is because, when high pressures of up to 150 MPa are present, the resulting notch stress can lead to a significant reduction in the stability of the valve body.

次に本発明の実施例を図示し、詳しく説明する。   Next, an embodiment of the present invention is illustrated and described in detail.

図１には、本発明の燃料噴射弁を縦断面図で示した。燃料噴射弁は弁体１を備えており、この弁体１は接触面５０で、中間ディスク３の接触面５５に接触する。中間ディスク３自体は保持体５に接触しており、弁体１は、保持体５の雄ねじ山に係合する緊締ナット７によって、中間ディスク３ひいては保持体５に押し付けられている。弁体１には、直径で段部を有する袋穴１０が形成されており、この袋穴１０は接触面５０から出発して、閉鎖端部で実質的に円錐形の弁座１４によって画設されている。弁体１の燃焼室側の端部には複数の噴射開口１６が形成されており、これらの噴射開口１６は内燃機関の燃焼室に開口している。袋穴１０には、プランジャ状の弁ニードル１２が縦方向可動に配置されており、この弁ニードル１２は弁座側の端部で弁シール面１５を備えており、この弁シール面１５は弁座１４と協働して、弁が形成される。この弁は、弁ニードル１２と袋穴１０の壁との間に存在するリングギャップ１８の、噴射開口１６に対する接続を開閉する。   FIG. 1 is a longitudinal sectional view of the fuel injection valve of the present invention. The fuel injection valve has a valve element 1, which contacts the contact surface 55 of the intermediate disk 3 at the contact surface 50. The intermediate disk 3 itself is in contact with the holder 5, and the valve body 1 is pressed against the intermediate disk 3 and thus the holder 5 by a tightening nut 7 which engages with the external thread of the holder 5. The valve body 1 is formed with a blind hole 10 having a step in diameter, which starts from the contact surface 50 and is defined by a substantially conical valve seat 14 at the closed end. Have been. A plurality of injection openings 16 are formed at the end of the valve body 1 on the combustion chamber side, and these injection openings 16 open to the combustion chamber of the internal combustion engine. A plunger-shaped valve needle 12 is disposed in the blind hole 10 so as to be movable in the vertical direction. The valve needle 12 has a valve seal surface 15 at an end on the valve seat side. In cooperation with the seat 14, a valve is formed. This valve opens and closes the connection of the ring gap 18 present between the valve needle 12 and the wall of the blind hole 10 to the injection opening 16.

弁座とは反対側の端部で袋穴１０は拡張されており、拡張部分にスリーブ２２が配置されており、このスリーブ２２は弁ニードル１２の、弁座とは反対側の端部区分を包囲していて、かつ中間ディスク３に接触している。さらに弁ニードル１２は、支持リング２６によって取り囲まれており、この支持リング２６は弁ニードル１２のリング肩部に支持されている。支持リング２６とスリーブ２２との間に閉鎖ばね２４が配置されており、この閉鎖ばね２４は弁ニードル１２を取り囲む圧縮コイルばねとして形成されている。閉鎖ばね２４のプレロード（予荷重）によって、弁座１４に向かう閉鎖力が弁ニードル１２に及ぼされ、この閉鎖力は弁ニードル１２を弁シール面１５で弁座１４に押し付ける。   At the end opposite the valve seat, the blind hole 10 is expanded, and a sleeve 22 is arranged in the expanded portion, which sleeve 22 defines the end section of the valve needle 12 opposite the valve seat. Surrounding and in contact with the intermediate disk 3. Furthermore, the valve needle 12 is surrounded by a support ring 26, which is supported on the ring shoulder of the valve needle 12. A closing spring 24 is arranged between the support ring 26 and the sleeve 22, and is formed as a compression coil spring surrounding the valve needle 12. The preload of the closing spring 24 exerts a closing force on the valve needle 12 towards the valve seat 14, which forces the valve needle 12 against the valve seat 14 at the valve sealing surface 15.

弁ニードル１２は、袋穴１０における中央区分１１２で案内され、この中央区分１１２に４つの研磨部２０が設けられており、これらの研磨部２０によって噴射開口１６に向かう燃料流が得られる。中央区分１１２の、弁座に向いた端部に受圧肩部９が形成されており、この受圧肩部９はリングギャップ１８における燃料圧によって負荷される。袋穴１０は、保持体５および中間ディスク３内で延びる流入通路８を介して、高圧下の燃料で充填することができ、この燃料は、弁ニードル１２が弁座１４から持ち上げられると、研磨部２０とリングギャップ１８とを通って噴射開口に流入する。   The valve needle 12 is guided in a central section 112 in the blind hole 10, which is provided with four polishing sections 20, by means of which a fuel flow towards the injection opening 16 is obtained. At the end of the central section 112 facing the valve seat, a pressure-receiving shoulder 9 is formed, which is loaded by the fuel pressure in the ring gap 18. The blind hole 10 can be filled with fuel under high pressure via an inlet passage 8 extending in the holding body 5 and the intermediate disk 3, and this fuel is polished when the valve needle 12 is lifted from the valve seat 14. It flows into the injection opening through the part 20 and the ring gap 18.

スリーブ２２と、弁ニードル１２の、弁座とは反対側の端面と、中間ディスク３とによって制御室３０が画設されており、この制御室３０は燃料で充填されていて、かつ適当な圧力が存在する場合に、弁座１４に向かう、すなわち閉鎖ばね２４の力と同じ方向で作用するハイドロリック力を弁ニードル１２に及ぼす。制御室３０は、流入絞り３２を介して流入通路８と結合されているので、流入通路８から常に燃料が制御室３０に継続的に流入し、それも制御室３０に低圧が作用するまで流入する。さらに制御室３０は、流出絞り３４を介して漏れ室３６と結合可能であり、この場合この結合は制御弁４０によって開閉することができる。一方では流出絞り３４の適当な寸法設定によって、また他方では流入絞り３２の適当な寸法設定によって、制御弁４０の開放状態では、流入絞り３２を介して制御室に流入する燃料よりも多くの燃料が流出絞り３４を介して制御室３０から流出する。これによって流入通路８における圧力に対して制御室３０における圧力が低下し、弁ニードル１２は受圧肩部９に作用するハイドロリック力によって弁座１４から持ち上げられ、噴射開口１６を解放する。制御弁４０の閉鎖に基づいて、流入絞り３２を介して継続的に流入する燃料によって、制御室３０に、新たに、流入通路８における圧力に相当する圧力である高圧燃料が形成される。これによって生じる、弁ニードル１２の端面に作用するハイドロリック力および閉鎖ばね２４の力が、受圧肩部９および弁シール面１５に作用するハイドロリック力を超えるので、弁ニードル１２は、弁座１４に接触するように戻され、噴射開口１６が閉鎖される。   A control chamber 30 is defined by the sleeve 22, the end face of the valve needle 12 opposite the valve seat and the intermediate disk 3, which is filled with fuel and has a suitable pressure. Exerts a hydraulic force on the valve needle 12 towards the valve seat 14, ie in the same direction as the force of the closing spring 24. Since the control chamber 30 is connected to the inflow passage 8 through the inflow restrictor 32, the fuel always flows from the inflow passage 8 into the control chamber 30 continuously until the low pressure acts on the control chamber 30. I do. Furthermore, the control chamber 30 can be connected to the leak chamber 36 via an outlet throttle 34, which can be opened and closed by a control valve 40. With the appropriate sizing of the outlet throttle 34 on the one hand and the appropriate sizing of the inlet throttle 32 on the other hand, when the control valve 40 is open, more fuel than fuel flows into the control chamber via the inlet throttle 32. Flows out of the control chamber 30 through the outflow restrictor 34. As a result, the pressure in the control chamber 30 is reduced with respect to the pressure in the inflow passage 8, and the valve needle 12 is lifted from the valve seat 14 by the hydraulic force acting on the pressure receiving shoulder 9, thereby releasing the injection opening 16. Due to the closing of the control valve 40, a high-pressure fuel, which is a pressure corresponding to the pressure in the inflow passage 8, is newly formed in the control chamber 30 by the fuel continuously flowing through the inflow throttle 32. As a result, the hydraulic force acting on the end face of the valve needle 12 and the force of the closing spring 24 exceed the hydraulic force acting on the pressure-receiving shoulder 9 and the valve sealing surface 15, so that the valve needle 12 is mounted on the valve seat 14. And the ejection opening 16 is closed.

燃料噴射弁を前述のような形式で運転すると、常に噴射圧下の燃料が供給通路８ひいては袋穴１０に存在する。弁体１の接触面５０が中間ディスク３の接触面５５に接触してシール面を形成する箇所で漏れが生じないようにするために、緊締ナット７の押圧力はこれに応じて高くする必要がある。しかしながらこの力は、材料に関して限界が設けられるので、前記箇所における完全なシールは、緊締ナット７の押圧力だけによって得られるとは限らない。接触面５０において袋穴を形成する開口の周りの押圧力をさらに高めるために、接触面５０の近くで袋穴１０にリング溝４２が設けられており、このリング溝４２は、直径方向でみて全体的に袋穴１０の壁に沿って延びている。図２には、この領域を更に拡大して示した。ここでは判りやすくするために、スリーブ２２および弁ニードル１２を省略して弁体１だけを示した。   When the fuel injection valve is operated in the above-described manner, the fuel under the injection pressure always exists in the supply passage 8 and thus the blind hole 10. The pressing force of the tightening nut 7 needs to be correspondingly high in order to prevent leakage at the point where the contact surface 50 of the valve element 1 contacts the contact surface 55 of the intermediate disk 3 and forms a sealing surface. There is. However, this force is limited with respect to the material, so that a perfect seal at said location cannot always be obtained solely by the pressing force of the clamping nut 7. To further increase the pressing force around the opening forming the blind hole in the contact surface 50, a ring groove 42 is provided in the blind hole 10 near the contact surface 50, and the ring groove 42 is viewed in a diametrical direction. It generally extends along the wall of the blind hole 10. FIG. 2 shows this region further enlarged. Here, for simplicity, only the valve element 1 is shown without the sleeve 22 and the valve needle 12.

リング溝４２は、図２の左半部では、無圧状態で示しており、ここでは接触面５０は一平面を成している。図２の右半部では、リング溝４２は、袋穴１０に高圧が存在する状態で示した。圧力によってとりわけ弁体１の縦方向でリング溝４２が拡張されるので、袋穴１０の開口をめぐる接触面５０の領域が膨脹し、この領域は、中間ディスク３の接触面５５に押圧される。判りやすくするために、この変形に関して図２では極端に誇張して示した。１５０ＭＰａ以上の高圧でも、鋼が使用される場合、膨脹は数マイクロメートルである。しかしながら袋穴１０の開口をめぐる面圧の上昇は相当なものであって、これは良好なシールをもたらし、ひいては漏れの防止をもたらす。   The ring groove 42 is shown in a non-pressure state in the left half of FIG. 2, where the contact surface 50 forms one plane. In the right half of FIG. 2, the ring groove 42 is shown in a state where a high pressure exists in the blind hole 10. As a result of the pressure, in particular in the longitudinal direction of the valve body 1, the ring groove 42 is expanded, so that the area of the contact surface 50 surrounding the opening of the blind hole 10 expands, which is pressed against the contact surface 55 of the intermediate disk 3. . For the sake of simplicity, this deformation has been exaggerated in FIG. Even at high pressures, above 150 MPa, when steel is used, the expansion is a few micrometers. However, the increase in surface pressure around the opening of the blind hole 10 is considerable, which leads to a good seal and thus to the prevention of leakage.

所望の効果を得るために、リング溝４２は、一方では深く設けて、かつ接触面５０に対して僅かな間隔を有するようにする必要があるが、また他方では深いリング溝４２によって強い切欠効果が生じ、ひいてはこの領域において弁体１の強度低下が生じ、これによって燃料噴射弁の機能を損なうような可塑変形が生じ得る。さらに接触面に対するリング溝４２の間隔は、製作技術的な理由から任意に低減できるものではない。   In order to obtain the desired effect, the ring groove 42 needs to be provided deeply on the one hand and have a slight spacing with respect to the contact surface 50, but on the other hand the strong notch effect due to the deep ring groove 42 And, in this region, the strength of the valve body 1 is reduced, which may cause plastic deformation that impairs the function of the fuel injection valve. Furthermore, the interval between the ring grooves 42 with respect to the contact surface cannot be arbitrarily reduced for reasons of manufacturing technology.

理想的な効果を得るためには、接触面５０に対する間隔ａが０．５〜１．５ｍｍの場合には、リング溝の深さｔは１〜３ｍｍとなっている。切欠応力をできるだけ僅かに維持するためには、リング溝４２は半円状の横断面で設けられており、この場合選択的に、その形状から幾分かは異なる形状、たとえば半分の楕円形にすることもできる。   In order to obtain an ideal effect, when the distance a to the contact surface 50 is 0.5 to 1.5 mm, the depth t of the ring groove is 1 to 3 mm. In order to keep the notch stress as low as possible, the ring groove 42 is provided with a semicircular cross section, in which case it is optionally possible to have a somewhat different shape, for example a half elliptical shape. You can also.

本発明の燃料噴射弁を示す縦断面図である。It is a longitudinal section showing a fuel injection valve of the present invention.

図１の縦断面図をリング溝の領域で拡大した図である。FIG. 2 is an enlarged view of a longitudinal sectional view of FIG. 1 in an area of a ring groove.

符号の説明Explanation of reference numerals

１ 弁体、 ３ 中間ディスク、 ５ 保持体、 ７ 緊締ナット、 ８ 流入通路、 ９ 受圧肩部、 １０ 袋穴、 １２ 弁ニードル、 １４ 弁座、 １５ 弁シール面、 １６ 噴射開口、 １８ リングギャップ、 ２０ 研磨部、 ２２ スリーブ、 ２４ 閉鎖ばね、 ２６ 支持リング、 ３０ 制御室、 ３２ 流入絞り、 ３４ 流出絞り、 ３６ 漏れ油室、 ４０ 制御弁、 ４２ リング溝、 ５０ 接触面、 ５５ 接触面、 １１２ 中央区分、 ａ 間隔、 ｔ 深さ   DESCRIPTION OF SYMBOLS 1 valve body, 3 intermediate disk, 5 holding body, 7 tightening nut, 8 inflow passage, 9 pressure receiving shoulder, 10 bag hole, 12 valve needle, 14 valve seat, 15 valve seal surface, 16 injection opening, 18 ring gap, Reference Signs List 20 polishing part, 22 sleeve, 24 closing spring, 26 support ring, 30 control chamber, 32 inflow restrictor, 34 outflow restrictor, 36 leak oil chamber, 40 control valve, 42 ring groove, 50 contact surface, 55 contact surface, 112 center Classification, a spacing, t depth

Claims (7)

内燃機関のための燃料噴射弁であって、弁体（１）が設けられており、該弁体（１）が接触面（５０）で、燃料噴射弁の別の構成部材（３）の接触面（５５）に接触していて、かつ装置（７）によって前記別の構成部材（３）に押し付けられており、弁体（１）に袋穴（１０）が形成されており、該袋穴（１０）が、弁体（１）の接触面（５０）から出発しており、袋穴（１０）には、少なくとも一時的に高圧下の燃料が存在しており、弁体（１）の接触面（５０）が、該接触面（５０）における袋穴（１０）の開口の周りでシール面として形成されている形式のものにおいて、
接触面（５０）に対して間隔をおいて、弁体（１）の袋穴（１０）にリング溝（４２）が形成され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, comprising a valve element (1), said valve element (1) being in contact with another contact member (3) of a fuel injection valve at a contact surface (50). Surface (55) and being pressed against said further component (3) by means of a device (7), wherein a blind hole (10) is formed in the valve body (1); (10) starts from the contact surface (50) of the valve element (1), and at least temporarily fuel under high pressure is present in the blind hole (10). In the form wherein the contact surface (50) is formed as a sealing surface around the opening of the blind hole (10) in the contact surface (50),
A fuel injection valve for an internal combustion engine, characterized in that a ring groove (42) is formed in a blind hole (10) of a valve body (1) at a distance from a contact surface (50). リング溝（４２）が、周方向で見て袋穴（１０）の壁に沿って延びている、請求項１記載の燃料噴射弁。   2. The fuel injection valve according to claim 1, wherein the ring groove (42) extends along the wall of the blind hole (10) as viewed in the circumferential direction. リング溝（４２）が、１ｍｍから３ｍｍまでの深さ（ｔ）を有している、請求項２記載の燃料噴射弁。   3. The fuel injector according to claim 2, wherein the ring groove (42) has a depth (t) of 1 mm to 3 mm. リング溝が、２ｍｍよりも少なく、有利には０．５ｍｍから１．５ｍｍまでの、接触面に対する間隔を有している、請求項２記載の燃料噴射弁。   3. The fuel injection valve according to claim 2, wherein the ring groove has a distance to the contact surface of less than 2 mm, preferably from 0.5 mm to 1.5 mm. リング溝（４２）が、実質的に半円状の横断面を有している、請求項２記載の燃料噴射弁。   3. The fuel injection valve according to claim 2, wherein the ring groove (42) has a substantially semicircular cross section. 袋穴（１０）の閉鎖端部に噴射開口（１６）が配置されている、請求項１記載の燃料噴射弁。   2. The fuel injection valve according to claim 1, wherein an injection opening (16) is arranged at the closed end of the blind hole (10). 袋穴（１０）に弁ニードル（１２）が配置されており、該弁ニードル（１２）が、噴射開口（１６）を開閉するようになっている、請求項６記載の燃料噴射弁。   7. The fuel injection valve according to claim 6, wherein a valve needle (12) is arranged in the blind hole (10), the valve needle (12) opening and closing the injection opening (16).
JP2003425670A 2002-12-23 2003-12-22 Fuel injection valve for internal combustion engine Withdrawn JP2004204850A (en)

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DE102004005451A1 (en) * 2004-02-04 2005-08-25 Robert Bosch Gmbh Fuel injection system for internal combustion engines
DE102005038444A1 (en) * 2005-05-02 2006-11-09 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102005054927A1 (en) * 2005-11-17 2007-05-31 Siemens Ag Fuel injector for common rail diesel injection for diesel engine, has nozzle needle which has steps in its shaft and damping chamber is formed in area of steps between shaft of nozzle needle and housing wall
DE102006029392A1 (en) * 2006-06-27 2008-01-03 Robert Bosch Gmbh injector
DE102008000171B4 (en) * 2007-01-31 2017-04-06 Denso Corporation Injector and plate component for this
DE102007017126A1 (en) * 2007-04-11 2008-10-16 Robert Bosch Gmbh Injection Module
DE102008040381A1 (en) * 2008-07-14 2010-01-21 Robert Bosch Gmbh High pressure resistant fuel injector
EP2336543A3 (en) * 2009-12-21 2013-07-03 Robert Bosch GmbH Fuel injector valve for combustion engines
JP5375762B2 (en) * 2010-07-14 2013-12-25 株式会社デンソー Fuel injection device
DE102011078429A1 (en) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Fuel injector
CN104265534B (en) * 2014-08-05 2017-05-03 中国第一汽车股份有限公司无锡油泵油嘴研究所 Oil injecting speed-variable common rail system oil injector

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DE10008554A1 (en) * 2000-02-24 2001-08-30 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10024703A1 (en) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Injection arrangement for fuel storage injection system has valve unit blocking auxiliary channel and outlet path in alternation

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