JP4181247B2 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
JP4181247B2
JP4181247B2 JP19284398A JP19284398A JP4181247B2 JP 4181247 B2 JP4181247 B2 JP 4181247B2 JP 19284398 A JP19284398 A JP 19284398A JP 19284398 A JP19284398 A JP 19284398A JP 4181247 B2 JP4181247 B2 JP 4181247B2
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Prior art keywords
valve
annular
annular shoulder
fuel injection
tension nut
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Expired - Fee Related
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JP19284398A
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JPH1172063A (en
Inventor
ディットゥス ベルント
ハウク シュテファン
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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
    • 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
    • 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

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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)
  • Fuel-Injection Apparatus (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は内燃機関のための燃料噴射弁であって，弁保持体に固定的に締付けられた弁体とテンションナットとを備えており，弁体内には弁部材が孔内で軸方向に摺動可能に案内されており，その場合，孔が半径方向に拡張された圧力室を備えており，この圧力室内には，孔と並んで延びている少なくとも１つの供給通路が開口しており，かつ，テンションナットが，円錐形に形成された内側の環状肩で，圧力室の高さのところに配置されている弁体の環状段部に当接して，弁体を弁保持体に締付けている形式のものに関する。
【０００２】
【従来の技術】
この種の燃料噴射弁は例えばドイツ連邦共和国特許出願公開第１９５２３２４３号明細書に開示されている。
【０００３】
この燃料噴射弁では，弁体を軸方向で保持体に締め付けるテンションナットの環状肩の，保持体から遠い方の端部と，テンションナットと協働する，弁体の環状段部とが円錐形に形成されており，その場合，円錐形の環状段部と弁部材軸線とが挟む角度は，円錐形の環状肩と弁部材軸線とが挟む角度に比して小さい。
【０００４】
この形式で，局部化され，集中され，かつ同時に圧力負荷に抗して作用する力を弁体へ導入することができる。
【０００５】
しかし，この種の燃料噴射弁では，環状段部と環状肩とが互いに異なる円錐角を有する円錐形に構成されているにもかかわらず，テンションナットの締付け時に摩擦半径の変化を完全には回避できないことが，問題点として生じる。要するに，組付け前にはテンションナットと弁体との円錐面の円錐角が互いに異なっているためノズルとテンションナットとの間に線接触は生じるが，しかし，テンションナットの締付け時には，例えばノズルに比して極めて著しく柔らかいテンションナットの肩が周方向で種々異なって変形するか又はノズルの肩に種々異なって当接することにより，平面及び傾斜面の誤差が生じて，局所的に互いに異なる摩擦半径が生じてしまう。このことにより，摩擦半径と，その結果としてテンションナットの締付けトルクを介して生じる合力とが変化する。
【０００６】
【発明が解決しようとする課題】
本発明の課題は，摩擦半径と，その結果としてテンションナットの締付けトルクを介して生じる合力とが可能な限りコンスタントに維持されるように，冒頭に記載した燃料噴射弁を改良することにある。
【０００７】
【課題を解決するための手段】
上記課題は本発明によれば，請求項１に記載したように，弁体の環状段部がテンションナットの環状肩に面した側で，弁部材軸線から所定の間隔をおいて環状に延びる支持点を生じるように，湾曲して形成されており，この支持点に，円錐形の環状肩が組立状態で当接していることにより解決される。
【０００８】
【発明の効果】
環状段部が環状肩に面した側で，弁部材軸線から所定間隔をおいて環状に延びていて組立状態で円錐形の環状肩を当接させる支持点を形成するために，湾曲して形成されているようにした本発明による構成の有する特別大きな利点は，摩擦半径が環状段部のジオメトリ的な設計により決定されるため，摩擦半径が正確にコンスタントに維持されることにある。この摩擦半径は特に組立時でも，さらにはテンションナットの締付け状態でもコンスタントに維持され，その結果，テンションナットの締付けトルクにより生じる精密に規定された合力が弁体に作用する。
【０００９】
摩擦半径が精密に設定される他に，特別有利には，環状に延びる支持点だけに環状肩が当接するため，環状段部及び環状肩のわずかな位置の不正確さが，力の配分に，特にテンションナットにより弁体に作用する合力にネガティブに作用することはない。
【００１０】
環状段部が環状肩に面した側で湾曲して形成されていることについては，種々多様な構成が考えられる。
【００１１】
有利な１構成では，環状段部が，断面で見てほぼ円弧形の形状を有しており，この形状に，環状肩が環状に延びる支持点を形成して接線状に当接する。
【００１２】
環状段部の断面で見て円弧形の形状により，特に有利に，均一なかつ規定された力の導入が可能である。
【００１３】
別の有利な１構成では，環状段部が，角度を成して互いに隣接する少なくとも２つの面を備えており，その境界縁が環状に延びる支持点を形成している。
【００１４】
有利にはテンションナットの円錐形の環状肩は互いに異なって傾斜した２つの環状肩領域を備えており，その半径方向外側に位置する環状肩領域が環状に延びる支持点上に当接しており，かつ，弁部材軸線に対して比較的小さな角度を有していてエッジを介してこの環状肩領域に続いて設けられた半径方向で内側に位置する環状肩領域は無接触である。
【００１５】
【発明の実施の形態】
次に，図示の若干の実施例ににもとづいて本発明の構成を具体的に説明する。
【００１６】
図１に示した内燃機関のための燃料噴射弁は弁体１を有しており，この弁体は中間板３をはさんで，スリーブ状のテンションナット５によって，軸方向に弁保持体７に締付けられている。
【００１７】
弁体１は軸方向の孔９を備えており，この孔内には，ピストン状の弁部材１１が軸方向に摺動可能に案内されており，この弁部材はその一端で，弁体１の燃焼室側の円頭部１５の内向きの弁座１３と協働しており，この円頭部１５には弁座１３の下流に複数の噴口が配置されている。
【００１８】
弁体１は回転対称的な構成部材であって，上方の太い部分１９と，下方の細いシャフト部分２１とを備えており，このシャフト部分２１の燃焼室側の端部は円頭部１５により閉鎖されている。孔９の，上方の太い部分１９に配置された部分は弁部材１１の案内部２５のための案内孔２３として形成されている。
【００１９】
孔９の，シャフト部分２１内で延びる部分と，弁部材１１の軸部とは，弁座１３まで達する環状隙間２７を形成している。上方の太い部分１９内では，下方のシャフト部分２１の近くで，孔９の案内孔２３と環状隙間２７との間に，増径されたバックテーパ状の圧力室２９が配置されており，その外側の制限壁３１は有利には湾曲していて，環状隙間２７内へ移行している。弁保持体７の袋孔内に挿入されたばね３３が噴射弁の閉鎖時にばね受け３５を介して弁部材１１を弁座１３に当接せしめる。
【００２０】
燃料供給のために，弁体１の太い部分１９内にはその上方の端面を起点として，供給通路３７が案内孔２３と並んで圧力室２９へ延びている。この供給通路３７は上方から圧力室の側部へ開口している。圧力室２９の直径を可能な限り小さくし，かつ開口の横断面を十分に大きくするために，供給通路３７は案内孔２３に対して斜めに延びており，その場合，弁体１の上方の端面における供給通路の入口と弁部材軸線との間隔は，圧力室２９内への供給通路の入口と弁部材軸線との間隔に比して大きく，従って，中間壁３９の厚さは，供給通路３７の開口領域の近くで，かつ案内孔２３から圧力室２９への移行部の近くで，小さくなっている。
【００２１】
弁体１の上方の太い部分１９にかぶさって雌ねじ山４１で弁保持体７の雄ねじ山４３に螺合しているスリーブナットとして形成されたスリーブ状のテンションナット５は内側の円錐形の環状肩４４を備えており，この環状肩には，弁体がその上方の太い部分１９から下方の細長いシャフト部分２１への移行部の領域内の湾曲した環状段部４５で支持されている。
【００２２】
図１及び図２から分かるように，燃料噴射弁の１実施例では，縦断面で見て，環状段部４５がほぼ円弧形の形状を有しており，この形状に，環状肩４４が環状に延びる支持点６０を形成して接線状に当接している。
【００２３】
この場合，テンションスリーブ５の円錐形の環状肩４４は弁部材軸線７０に対して互いに異なって傾斜した２つの環状肩領域を有しており，その半径方向外側に位置する環状肩領域５２が環状段部４５に接線状に当接している。この環状肩領域５２には，エッジ５５を介して半径方向内側に位置していて弁部材軸線７０と比較的小さな角度を挟む環状肩領域５７が続いており，この環状肩領域５７は常に無接触である。
【００２４】
環状段部４５と，これに接線状に当接する環状肩４４とのこの構成により，弁部材軸線７０に関してコンスタントな摩擦半径Ｒreib が生じ，この摩擦半径は特に組立てられた状態でもそのまま正確に維持され，このことにより，テンションナット５の締付けトルクを介して生じて弁体１に作用する合力がコンスタントに維持される。
【００２５】
図３に示す別の実施例では，環状段部４５が環状肩４４に面した側に，角度を成して互いに隣接した２つの面４６，４７を備えており，その境界縁が環状に延びる支持点６０を形成している。この境界縁に環状肩４４が当接しており，このことにより，やはりこの場合も，規定された摩擦半径Ｒreib が可能となる。
【００２６】
両面のうちの一方の面４７は弁部材軸線７０に近い方の側で，弁部材軸線７０に対して直角に延びる環状端面４８へ移行しており，この環状端面により，テンションナット５がこの領域内で環状段部４５に当接しないことが保証される。
【００２７】
環状段部４５及び環状肩４４の上述の構成によって，予め規定された摩擦半径Ｒreib がテンションナット５の組付け時に極めて正確に維持されることが可能であり，このことにより，テンションナット５の締付けトルクを介して生じる合力が，組立時にコンスタントな規定された値を維持することが保証される。
【図面の簡単な説明】
【図１】本発明にもとづく燃料噴射弁の燃焼室側の部分の縦断面図である。
【図２】本発明にもとづく燃料噴射弁の環状段部と，これに当接する環状肩との拡大縦断面図である。
【図３】本発明の別の実施例にもとづく燃料噴射弁の環状段部と，これに当接する環状肩との拡大縦断面図である。
【符号の説明】
１ 弁体， ５ テンションナット， ７ 弁保持体， ９ 孔， １１ 弁部材， ２９ 圧力室， ３７ 供給通路， ４４ 環状肩， ４５ 環状段部， ４６ ，４７ 互いに隣接した面， ５２ 環状肩領域， ５５ エッジ，５７ 環状肩領域， ６０ 支持点， ７０ 弁部材軸線[0001]
BACKGROUND OF THE INVENTION
The present invention is a fuel injection valve for an internal combustion engine, and includes a valve body fixed to a valve holder and a tension nut, and a valve member is slid axially within a hole in the valve body. In which case the bore is provided with a pressure chamber with a radially expanded bore, in which at least one supply passage extending alongside the bore is open, In addition, the tension nut is an inner annular shoulder formed in a conical shape and abuts against the annular stepped portion of the valve element disposed at the height of the pressure chamber, and the valve element is fastened to the valve holder. It is related to the format.
[0002]
[Prior art]
This type of fuel injection valve is disclosed, for example, in German Offenlegungsschrift 19523243.
[0003]
In this fuel injection valve, the end of the annular shoulder of the tension nut that clamps the valve body to the holding body in the axial direction, the end far from the holding body, and the annular step of the valve body that cooperates with the tension nut are conical. In this case, the angle between the conical annular stepped portion and the valve member axis is smaller than the angle between the conical annular shoulder and the valve member axis.
[0004]
In this way, a localized, concentrated and simultaneously acting force against the pressure load can be introduced into the valve body.
[0005]
However, in this type of fuel injection valve, the change in the friction radius is completely avoided when the tension nut is tightened, even though the annular stepped portion and the annular shoulder have a conical shape with different cone angles. What cannot be done is a problem. In short, since the cone angle of the conical surface of the tension nut and the valve body is different from each other before assembly, line contact occurs between the nozzle and the tension nut. However, when tightening the tension nut, for example, the nozzle By contrast, the tension nut shoulders that are extremely soft compared to each other are deformed differently in the circumferential direction or abut against the nozzle shoulders differently, resulting in errors in the plane and the inclined surface, resulting in locally different friction radii. Will occur. This changes the friction radius and, consequently, the resultant force generated via the tightening torque of the tension nut.
[0006]
[Problems to be solved by the invention]
An object of the present invention is to improve the fuel injection valve described at the beginning so that the friction radius and, as a result, the resultant force generated via the tightening torque of the tension nut is maintained as constant as possible.
[0007]
[Means for Solving the Problems]
According to the present invention, as described in claim 1, the above-mentioned object is a support that extends annularly at a predetermined interval from the valve member axis on the side where the annular step portion of the valve body faces the annular shoulder of the tension nut. It is formed by bending so as to generate a point, and this is solved by a conical annular shoulder abutting on this supporting point in an assembled state.
[0008]
【The invention's effect】
On the side where the annular step faces the annular shoulder, it is curved to form a support point that extends annularly from the valve member axis at a predetermined interval and abuts the conical annular shoulder in the assembled state. A particularly significant advantage of the arrangement according to the invention that has been made is that the friction radius is determined precisely by the geometric design of the annular step, so that the friction radius is kept precisely constant. This friction radius is kept constant especially during assembly and even when the tension nut is tightened, and as a result, a precisely defined resultant force generated by the tightening torque of the tension nut acts on the valve body.
[0009]
In addition to the precise setting of the friction radius, it is particularly advantageous that the annular shoulder abuts only on the annularly extending support point, so that the slight position inaccuracy of the annular step and the annular shoulder is a factor in the force distribution. , In particular, it does not negatively affect the resultant force acting on the valve body by the tension nut.
[0010]
A variety of configurations are conceivable for the annular stepped portion being curved on the side facing the annular shoulder.
[0011]
In one advantageous configuration, the annular step has a generally arcuate shape when viewed in cross-section, with which the annular shoulder forms a support point extending annularly and abuts tangentially.
[0012]
Due to the arcuate shape when viewed in cross section of the annular step, it is particularly advantageous to introduce a uniform and defined force.
[0013]
In another advantageous configuration, the annular step comprises at least two faces that are adjacent to each other at an angle, the boundary edge of which forms a support point that extends annularly.
[0014]
Preferably, the conical annular shoulder of the tension nut has two annular shoulder regions which are inclined differently, the annular shoulder region located radially outwardly resting on an annularly extending support point, In addition, the annular shoulder region located radially inward and having a relatively small angle with respect to the valve member axis and following the annular shoulder region via the edge is contactless.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Next, the configuration of the present invention will be described in detail based on some illustrated embodiments.
[0016]
The fuel injection valve for an internal combustion engine shown in FIG. 1 has a valve body 1, which is sandwiched between intermediate plates 3 and is axially held by a sleeve-like tension nut 5. It is tightened.
[0017]
The valve body 1 is provided with an axial hole 9 in which a piston-like valve member 11 is guided so as to be slidable in the axial direction. The circular head 15 cooperates with the inward valve seat 13 of the circular head 15 on the combustion chamber side, and a plurality of injection holes are arranged in the circular head 15 downstream of the valve seat 13.
[0018]
The valve body 1 is a rotationally symmetric structural member and includes an upper thick portion 19 and a lower thin shaft portion 21, and the end of the shaft portion 21 on the combustion chamber side is formed by a circular head 15. It is closed. A portion of the hole 9 arranged in the upper thick portion 19 is formed as a guide hole 23 for the guide portion 25 of the valve member 11.
[0019]
A portion of the hole 9 extending in the shaft portion 21 and a shaft portion of the valve member 11 form an annular gap 27 that reaches the valve seat 13. In the upper thick portion 19, a back-tapered pressure chamber 29 having an increased diameter is disposed between the guide hole 23 of the hole 9 and the annular gap 27 near the lower shaft portion 21. The outer limiting wall 31 is preferably curved and transitions into the annular gap 27. The spring 33 inserted into the bag hole of the valve holder 7 brings the valve member 11 into contact with the valve seat 13 via the spring receiver 35 when the injection valve is closed.
[0020]
In order to supply fuel, a supply passage 37 extends into the pressure chamber 29 along with the guide hole 23, starting from the end face above the thick portion 19 of the valve body 1. The supply passage 37 opens from above to the side of the pressure chamber. In order to make the diameter of the pressure chamber 29 as small as possible and to make the cross section of the opening sufficiently large, the supply passage 37 extends obliquely with respect to the guide hole 23. The distance between the inlet of the supply passage at the end face and the valve member axis is larger than the distance between the inlet of the supply passage into the pressure chamber 29 and the valve member axis. It is small near the open area 37 and near the transition from the guide hole 23 to the pressure chamber 29.
[0021]
A sleeve-like tension nut 5 formed as a sleeve nut that covers the thick portion 19 above the valve body 1 and is screwed to the male thread 43 of the valve holder 7 with a female thread 41 has an inner conical annular shoulder. 44, on which the valve body is supported by a curved annular step 45 in the region of the transition from the thick part 19 above it to the elongate shaft part 21 below.
[0022]
As can be seen from FIGS. 1 and 2, in one embodiment of the fuel injection valve, the annular step 45 has a substantially arc shape when viewed in a longitudinal section. An annularly extending support point 60 is formed and abuts tangentially.
[0023]
In this case, the conical annular shoulder 44 of the tension sleeve 5 has two annular shoulder regions inclined differently from each other with respect to the valve member axis 70, and the annular shoulder region 52 located radially outward is annular. The step 45 is tangentially contacted. The annular shoulder region 52 is followed by an annular shoulder region 57 located radially inward via the edge 55 and sandwiching a relatively small angle with the valve member axis 70. The annular shoulder region 57 is always contactless. It is.
[0024]
This configuration of the annular step 45 and the annular shoulder 44 tangentially abutting it results in a constant friction radius Rreib with respect to the valve member axis 70, which is precisely maintained as it is, especially in the assembled state. As a result, the resultant force acting on the valve body 1 generated through the tightening torque of the tension nut 5 is constantly maintained.
[0025]
In another embodiment shown in FIG. 3, the annular step 45 has two surfaces 46 and 47 which are adjacent to each other at an angle on the side facing the annular shoulder 44, and the boundary edge extends annularly. A support point 60 is formed. An annular shoulder 44 is in contact with this border edge, which again allows a defined friction radius Rreib.
[0026]
One of the two surfaces 47 is on the side closer to the valve member axis 70 and is shifted to an annular end surface 48 extending at right angles to the valve member axis 70, and this annular end surface causes the tension nut 5 to move in this region. It is guaranteed that it does not come into contact with the annular step 45 inside.
[0027]
Due to the above-described configuration of the annular step 45 and the annular shoulder 44, the predefined friction radius Rreib can be maintained very accurately when the tension nut 5 is assembled, whereby the tension nut 5 is tightened. It is ensured that the resultant force generated through the torque maintains a constant prescribed value during assembly.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a portion on a combustion chamber side of a fuel injection valve according to the present invention.
FIG. 2 is an enlarged vertical sectional view of an annular step portion of a fuel injection valve according to the present invention and an annular shoulder abutting on the annular step portion.
FIG. 3 is an enlarged longitudinal sectional view of an annular step portion of a fuel injection valve according to another embodiment of the present invention and an annular shoulder abutting against the annular step portion.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Valve body, 5 Tension nut, 7 Valve holding body, 9 Hole, 11 Valve member, 29 Pressure chamber, 37 Supply passage, 44 Annular shoulder, 45 Annular step, 46, 47 The mutually adjacent surface, 52 Annular shoulder region, 55 edge, 57 annular shoulder region, 60 support point, 70 valve member axis

Claims (1)

内燃機関のための燃料噴射弁であって，弁保持体（７）に固定的に締付けられた弁体（１）とテンションナット（５）とを備えており，弁体内には弁部材（１１）が孔（９）内で軸方向に摺動可能に案内されており，その場合，孔（９）が半径方向に拡張された圧力室（２９）を備えており，この圧力室内には，孔（９）と並んで延びている少なくとも１つの供給通路（３７）が開口しており，かつ，テンションナット（５）が，円錐形に形成された内側の環状肩（４４）で，圧力室（２９）の高さのところに配置されている弁体（１）の環状段部（４５）に当接して，弁体を弁保持体（７）に締付けている形式のものにおいて，環状段部（４５）が環状肩（４４）に面した側で，弁部材軸線から所定の間隔（Ｒreib ）をおいて環状に延びる支持点（６０）を生じるように，湾曲して形成されており，この支持点に，円錐形の環状肩（４４）が組立状態で当接しており、環状段部（４５）が，角度を成して互いに隣接する少なくとも２つの面（４６，４７）を備えており，その境界縁が環状に延びる支持点（６０）を形成していることを特徴とする燃料噴射弁。A fuel injection valve for an internal combustion engine, comprising a valve body (1) fixed to a valve holder (7) and a tension nut (5), and a valve member (11 ) Is slidably guided in the axial direction in the hole (9), in which case the hole (9) is provided with a pressure chamber (29) which is expanded in the radial direction, At least one supply passage (37) extending side by side with the hole (9) is open, and the tension nut (5) is a pressure chamber with an inner annular shoulder (44) formed conically. In the type in which the valve body is fastened to the valve holder (7) in contact with the annular step portion (45) of the valve body (1) arranged at the height of (29). The portion (45) extends annularly at a predetermined interval (Rreib) from the valve member axis on the side facing the annular shoulder (44) To produce a lifting point (60) is formed curved, the supporting point, conical annular shoulder (44) is in contact with in the assembled state, an annular step portion (45), the angle A fuel injection valve comprising at least two surfaces (46, 47) which are adjacent to each other and whose boundary edge forms a support point (60) extending in an annular shape .
JP19284398A 1997-07-11 1998-07-08 Fuel injection valve Expired - Fee Related JP4181247B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19729843.5 1997-07-11
DE19729843A DE19729843A1 (en) 1997-07-11 1997-07-11 Fuel injector

Publications (2)

Publication Number Publication Date
JPH1172063A JPH1172063A (en) 1999-03-16
JP4181247B2 true JP4181247B2 (en) 2008-11-12

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DE (2) DE19729843A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19818200A1 (en) 1998-04-23 1999-10-28 Bosch Gmbh Robert Fuel injection valve for internal combustion engine
DE19956510A1 (en) 1999-11-25 2001-05-31 Bosch Gmbh Robert Fuel injection valve for internal combustion engine has axially movable control piston those controls maximum degree valve element opening at least partly in form of piezo-actuator
DE19959304A1 (en) 1999-12-09 2001-06-13 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10018663A1 (en) 2000-04-14 2001-10-25 Siemens Ag Injection valve with optimised surface geometry between nozzle body and clamp nut enabling optimised transfer of compression force to nozzle body
BR0017320B1 (en) * 2000-08-21 2009-01-13 needle position sensing device.
DE10114216B4 (en) * 2001-03-23 2006-11-30 Robert Bosch Gmbh Yield limit controlled screw connection
DE10115325A1 (en) 2001-03-28 2002-10-17 Bosch Gmbh Robert Fuel injector, for an IC motor, has a clamp system to hold the injector housing at the base body, with a convex curvature in a ball segment shape at the clamping surface for an increased sealing action
DE102009029116A1 (en) 2009-09-02 2011-03-03 Robert Bosch Gmbh Fuel injector
DE102012217991A1 (en) 2012-10-02 2014-04-03 Continental Automotive Gmbh Nozzle assembly for a fluid injector and fluid injector

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GB2024315A (en) * 1978-07-01 1980-01-09 Lucas Industries Ltd Fuel injection nozzle
JP2537983Y2 (en) * 1990-12-21 1997-06-04 株式会社ゼクセル Fuel injection nozzle
JPH07119583A (en) * 1993-10-26 1995-05-09 Hino Motors Ltd Fuel injection nozzle
DE19523243B4 (en) * 1995-06-27 2009-04-02 Robert Bosch Gmbh Fuel injection valve for internal combustion engines with a clamping nut with a conically formed annular shoulder

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DE19729843A1 (en) 1999-01-14
EP0890734B2 (en) 2010-07-07
EP0890734A2 (en) 1999-01-13
JPH1172063A (en) 1999-03-16
EP0890734B1 (en) 2004-11-03
DE59812198D1 (en) 2004-12-09

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