EP1915527B1 - Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant - Google Patents

Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant Download PDF

Info

Publication number
EP1915527B1
EP1915527B1 EP06819042.0A EP06819042A EP1915527B1 EP 1915527 B1 EP1915527 B1 EP 1915527B1 EP 06819042 A EP06819042 A EP 06819042A EP 1915527 B1 EP1915527 B1 EP 1915527B1
Authority
EP
European Patent Office
Prior art keywords
cone
valve member
injection valve
seat
wear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06819042.0A
Other languages
German (de)
English (en)
Other versions
EP1915527A1 (fr
Inventor
Holger Rapp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1915527A1 publication Critical patent/EP1915527A1/fr
Application granted granted Critical
Publication of EP1915527B1 publication Critical patent/EP1915527B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F02M61/166—Selection of particular materials
    • 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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9038—Coatings

Definitions

  • the invention relates to a UNEtdrosseltes injection valve member for fuel injectors, in particular for injector-controlled injectors, which are used in high-pressure accumulator injection systems.
  • actuator-controlled fuel injectors For injecting fuel into combustion chambers of self-igniting internal combustion engines, actuator-controlled fuel injectors are used whose injectors have a conically shaped seat in the nozzle body.
  • the conical seat opens at a defined diameter, which is also referred to as a blind hole diameter, in a blind hole, from which then the injection openings of the nozzle are fed.
  • the injection openings are not located in the abovementioned blind hole but at the level of a pointed cone of the injection valve member in the seat of the injector body.
  • the first-mentioned variant with a conical seat in the injector body has a geometric seat diameter (contact line injection valve member / injector body in the powerless state), at which the injection valve member at the end facing away from the injection openings adjoins a seat cone.
  • the injection valve member has a smaller cone angle than the injector body.
  • this seat cone is delimited on the injection valve member by a cylindrical projection of defined diameter.
  • G0-measure The distance that is established in the force and pressure-free state between the injection valve member and the injector body at an edge between the seat cone and said cylindrical projection.
  • the tip cone follows on this undercut.
  • the injection valve member has a larger cone angle than the injector body or nozzle body. Consequently, the gap between the injection valve member and the injector body continuously grows between the lower edge of the undercut and the blind hole diameter.
  • the distance, which sets in the non-pressurized state between the injection valve member and the injector body at the blind hole diameter is referred to as G3-measure, the distance which is established at the transition between the undercut and the tip cone, referred to as G-measure.
  • the variable over the switching state of a switching valve control chamber pressure at the circular surface formed by the guide diameter causes a defined closing force on the needle-shaped injection valve member.
  • the opening force may only be slightly larger than the stationary with the switching valve open adjusting closing force.
  • the seat diameter is chosen only slightly smaller than that theoretical seat diameter, in which just after the opening of the switching valve, a balance of forces between opening and closing force, the injection valve member does not open.
  • the diameter of the cylindrical projection must still be below the above-mentioned theoretical limit. It follows that the seat cone of the injection valve member builds very short in such fuel injectors.
  • a pressure field is formed whose course is dependent on the stroke of the injection valve member and the fine geometry of the gap between the injection valve member and the injector body or the nozzle body.
  • This pressure field can change very much over the life of the injection valve member at the same stroke, since the fine geometry of the gap between the injection valve member to the body changes when the needle-shaped injection valve member during operation of the fuel injector successively in the nozzle body or in the injector body incorporated. Due to the very short seat cone (length 150 ⁇ m), the pressure field below this seat cone changes when the seat is worn Injection valve member only very little. In contrast, this pressure field undergoes a considerable change under the peak cone and consequently also in the undercut.
  • the wear protection layer is first removed on the seat cone and at the transition between the undercut and the top cone.
  • the wear rate in the injector body or in the nozzle body initially increases considerably.
  • the surface pressure decreases below the region of the injection valve member which is no longer coated with the wear protection layer, while it clearly increases at the still coated region of the wear protection layer.
  • the resulting gap geometry has in the powerless state an inhomogeneous seat gap between the injection valve member and the injector body.
  • the injection valve member sits only on an annular transition between still existing and worn through wear protection layer. Since this area during operation of the fuel injector, ie approaches the end of the broken fiber laser tip cone, it comes inevitably even at very low wear depths to leakage and a significant increase in quantity.
  • the wear protection layer considerably reduces the progress of wear on the nozzle body or on the injector body, precisely this property leads, in the case of the seat geometry used, to a significantly increased sensitivity of tightness and injection quantity as a function of the wear depth.
  • the document DE 10 2004 013 600.9 describes the preamble of claim 1.
  • seat geometries are developed with which a coated with a wear protection layer seat of an injection valve member is optimized with respect to its drift behavior.
  • the seat cone has been lengthened and the seat angle of the injection valve member has been reduced.
  • Both measures cause an increase of the G0-measure, so that this optimized seat geometry is of the same order of magnitude as the G3-measure. This can avoid that the wear protection layer on the seat is prematurely completely rubbed through.
  • an annular transition between still coated and already stripped regions now forms on both the tip cone and on the seat cone, so that the injection valve member rests on both annular transitions at low system pressures.
  • the injection valve member Since the upper of these two transitions lies on the sealing seat cone, the injection valve member remains tight over the entire pressure range and prevents the increase in volume associated with leakage. However, this function is retained only as long as on both sealing surface portions of the injection valve member still cone sections are obtained with preserved wear protection layer. Once one of the sealing surface sections has completely lost its wear protection layer, there is only one transition between uncoated and coated area of the injection valve member, on which the injection valve member is seated at low pressures. If this area lies on the tip cone of the injection valve member, leakage and an increase in volume again occur. On the other hand, if the transition is on the seat cone, the injection valve member will remain tight, but a considerable decrease in volume will occur.
  • the object of the invention is to optimize the wear occurring over the service life of a fuel injector and to significantly reduce the risk of occurring leaks and an increase in volume or a significant decrease in quantity over the service life of the fuel injector.
  • the seat angle of the injection valve member is selected to be greater than the seat angle in the injector body while the tip cone of the injection valve member is selected to be smaller than the seat angle in the injector or nozzle body.
  • the previously executed undercut can be omitted, the cylindrical approach, however, remains. This results between the cylindrical projection and the blind hole diameter now a concave gap.
  • the angles and lengths of the cone sections on the injection valve member are chosen so that this rests in a powerless state at the level of the cylindrical projection and adjusts a small gap at the blind hole diameter, whose height is referred to below as G3-measure.
  • the G3 dimension is preferably dimensioned in such a way that, although it is very small, it is in any case greater than 0 when the manufacturing tolerances are utilized.
  • the greatest distance between the injection valve member and the Injektor- or nozzle body is now at the height of the intersection between the seat cone and the tip cone within a concave gap between the injection valve member and the nozzle / injector body (G dimension).
  • the wear of the wear protection layer no longer begins at the two mutually facing ends of the cone sections of the injection valve member, but at the ends facing away from each other (blind hole diameter at the top cone and cylindrical projection on the seat cone).
  • the two transition points between the existing and already worn wear protection layer no longer away from each other (divergent wear protection layer wear) but to move towards each other (converging wear protection layer wear).
  • angles and lengths of the conical sections can also be designed so that the seat of the injection valve member initially rests only at the blind hole inlet in the new state and has a gap on the cylindrical projection. Equally well, a transition dimensioning is possible in which arises depending on the actual value of the angle within their tolerances a support on the cylindrical approach or the blind hole diameter.
  • the tip cone of the injection valve member can be wholly or partially executed with a targeted out-of-roundness at the injection valve member or on the injector body or nozzle body (eg laser grooves in the injection valve member), which ensures a Entdrosselung this seating area even if the preferably needle-shaped injection valve member slowly into the Injektor stresses or ., incorporates the nozzle body.
  • the de-throttled area ends securely before the intersection between the seat cone and the tip cone.
  • the beginning or the end of the de-throttled region can be marked by a circumferential groove in the injection valve member or in the injector or nozzle body in order to achieve a uniform flow of the Entschrosselten bodies.
  • the seat is designed such that the injection valve member initially rests on the blind hole diameter, then instead of the tip cone the seat cone can be throttled and the tip cone assumes the sealing function.
  • the intersection between seat cone and tip cone on the injection valve member may be provided with a radius or a defined edge break.
  • the concave seat shape can also be brought about by any other contour of the injection valve member, through which a concave gap between injection valve member and injector body or nozzle body is formed.
  • the concave gap has no further local maxima in addition to the maximum of its gap height.
  • the concave gap can also be created by a non-linear conical contour of the body seat.
  • the wear protection layers used today which are made of, for example, amorphous diamond-like carbon
  • other materials for forming the wear protection layer may also be used, e.g. Silicate layers on the body seat or nitriding layers in the body seat.
  • FIG. 1 The representation according to FIG. 1 is a section of a fuel injector 10 can be seen, which is constructed rotationally symmetrical to a symmetry axis 12.
  • a preferably needle-shaped injection valve member 14 cooperates with an inner sealing surface 20 of a nozzle or injector body 18.
  • Figure 1.1 shows a reproduced in an elevation of 50: 1 detail view of FIG. 1 , With an elevation 24 of 50: 1, the injection valve member 14 is shown. This includes a tip cone 26 and a seat 30, between which an annular groove 16 or an undercut 28 are arranged.
  • the tip cone 26 of the injection valve member 14 is at a distance G3 from the inner sealing surface 20 of the nozzle or injector body 18.
  • the dimension G is the distance of the injection valve member 14 from the inner sealing surface 20 of the nozzle or injector body 18 in the area of the undercut 28 or the Annular groove 16 and the transition to the tip cone 26 identified while the measure G0, the distance between the injection valve member 14 and the inner sealing surface 20 of the nozzle or injector body 18 at the edge of the seat 30 to a cylindrical projection of the injection valve member 14 has.
  • the tip cone 26 has a first sealing surface 34, while the seat cone 30, on which the seat of the injection valve member 14 is formed in the nozzle or injector body 18, comprises a second sealing surface 36.
  • FIG. 2 shows a representation of the geometry of an optimized with respect to their drift behavior with a wear protection layer injector.
  • Both the first sealing surface 34 from the tip cone 26 and the second sealing surface 36 on the seat cone 30 are provided with wear protection layers 40, 42.
  • the wear protection layers 40, 42 are usually applied continuously on the entire surface of the injection valve member 14.
  • the undercut 28 (annular groove 16) is usually co-coated.
  • Analogous to the representation of the Figure 1.1 are in the illustration according to FIG. 2 the distances G3, G0 and G entered.
  • the first sealing surface 34 and the second sealing surface 36 according to the embodiment in FIG. 2 are provided with wear protection layers 40, 42.
  • the wear protection layer 40, 42 is usually present continuously on the entire surface of the injection valve member 14, at least in the region of the seal. It may be a continuously applied layer, wherein also the undercut 28 is usually co-coated in the region of the annular groove 16.
  • the wear protection layer 40, 42 is usually present continuously on the entire surface of the injection valve member 14, at least in the region of the seal. It may be a continuously applied layer, wherein also the undercut 28 is usually co-coated in the region of the annular groove 16.
  • FIG. 2 illustrated variant is such that in progressive wear between injection valve member 14 and nozzle or injector 18, a divergent wear of the wear protection layers 40 and 42 and the inner sealing surface 20 of the nozzle or injector body 18 occurs. This means that the new sealing edges, which respectively adjust
  • FIG. 3 shows the inventively proposed seat geometry with a concave throttle gap.
  • the cone angles of the tip cone 26 and the seat 30 are reversed, such as FIG. 4 is removable.
  • the cone angle of the tip cone 26 is denoted by ⁇
  • the cone angle of the seat 30 is denoted by ⁇ .
  • the dimension G3 at the blind hole inlet 22 is substantially lower than in the FIG. 2 illustrated embodiment.
  • the dimension G at the transition between the tip cone 26 and seat 30 is considerably larger, compared with the dimension G in the embodiment according to FIG. 2 , so that at the in FIG. 3 illustrated embodiment, a concave throttle gap 70 by the sealing surface 20 and the nozzle or injector body and the lateral surface of the preferably needle-shaped injection valve member 14 sets.
  • first sealing surface 34 on the tip cone 26 as well as the second sealing surface 36 on the seat cone 30 are each coated with a first continuous wear protection layer 40 and a second continuous wear protection layer 42.
  • These wear protection layers may be made of, for example, amorphous, diamond-like carbon, or may also be applied to the body seat, for example, as silicate layers or nitriding layers.
  • first wear-resistant layer 40 or second wear-resistant layer 42 is understood to mean a wear protection layer applied continuously to tip cone 26 and seat cone 30, which also covers the transition region between tip cone 26 and seat cone 30 in the region of the undercut 28.
  • the undercut is omitted, a cylindrical projection 43 (see. FIG. 4 ) at the injection valve member 14 is maintained. Between the cylindrical projection 43 and the blind hole diameter 32 (see. FIG. 4 ) at the blind hole inlet 22, now results in a concave throttle gap 70.
  • the cone angle ⁇ and ⁇ (see. FIG. 4 ) and lengths of the cone portions 26 and 30 are selected so that the injection valve member 14 rests in the powerless state at the level of the cylindrical projection 43 and at the blind hole diameter a small gap, whose height corresponds to the G3 measure adjusts.
  • the G3 dimension is preferably dimensioned as small as possible, however, in such a way that, when the manufacturing tolerances are utilized, in each case it remains greater than zero.
  • the greatest distance between the preferably needle-shaped injection valve member 14 and the nozzle or injector body 18 is now at the level of the intersection between seat 30 and tip cone 26 a; here lies the G-measure.
  • FIG. 4 shows a different representation of the geometric relationships according to FIG. 3 .
  • FIG. 4 shows that the preferably needle-shaped injection valve member 14 has a pressure stage 44. Between the compression stage 44 and the seat 30, the cylindrical projection 43 extends.
  • the fuel injector 10 includes the injection valve member 14, on which runs below the seat 30 of the top cone 26.
  • the tip cone 26 is formed at a cone angle ⁇ , which is smaller than the cone angle ⁇ , in which the inner sealing surface 20 of the nozzle or injector body 18 extends, with respect to the vertical.
  • the cone angle ⁇ , in which the seat cone 30 is formed is chosen to be greater than the cone angle ⁇ of the inner sealing surface 20 of the nozzle or injector body 18th
  • the lengths and the cone angles ⁇ , ⁇ of tip cone 26 and seat cone 30 are selected so that the preferably needle-shaped injection valve member 14 rests in the powerless state at the level of the cylindrical projection 43 on the inner sealing surface 20 of the nozzle or injector 18. It turns at the blind hole inlet 22, taking into account the blind hole diameter 32, the dimension G3.
  • the greatest distance lies between the preferably needle-shaped injection valve member 14 and the inner sealing surface 20 of the nozzle or injector body 18 at the level of the intersection between the apex angle 26 and the seat cone 30.
  • the lateral surface of the tip cone 26 is provided with the first wear protection layer 40, while the lateral surface of the seat 30 is provided with the second wear protection layer 42. Both the first wear protection layer 40 and the second wear protection layer 42 are continuously applied to the tip cone 26 and seat 30 as a layer.
  • the wear protection layer 40, 42 may be formed of amorphous, diamond-like carbon as well as a silicate or nitride layer. These surfaces define the concave gap 70 between the outer contour of the injection valve member 14 and the inner sealing surface 20 of the nozzle or injector body 18.
  • the moderately worn condition is identified by reference numeral 48. 48.1 shows a wear profile on the outer contour of the injection valve member 14 in the region of the seat cone 30 and tip cone 26, while the reference numeral 48.2 marks the wear profile of the inner sealing surface 20 of the nozzle or injector body 18. From the illustration according to Figure 5.1 shows that in the moderately worn state 48, the injection valve member 14 has buried in the inner sealing surface 20 of the nozzle or injector body 20. In the inner sealing surface 20, a slope 52 has been formed and a corresponding edge of the seat 30 notch.
  • the wear profile 48.1 of the injection valve member 14 is characterized in that the first sealing surface 34 has an abrasion region 50, as well as the second sealing surface 36 on the seat 30th
  • a first annular width 60 is defined by the first bevel 52, which adjoins an intermediate annular surface 64.
  • the notch in the inner sealing surface 20 in the region of the seat 30 defines a second annular width 62.
  • the in Figure 5.2 shown advanced wear which is identified by reference numeral 54, is further advanced on the first sealing surface 34 of the apex cone 26 and on the second sealing surface 36 of the seat 30 of the needle-shaped injection valve member 14.
  • the abrasion region 50 on the first sealing surface 34 as shown in FIG Figure 5.1 has, as in Figure 5.2 shown enlarged at the first sealing surface 34 on the abrasion region 56.
  • a wear profile 54.1 on the outer contour of the injection valve member 14 is characterized by larger wear regions 56 on the first sealing surface 34 and the second sealing surface 36.
  • the forming on the inner sealing surface 20 of the nozzle or injector body 18 wear profile 54.2 characterized in that a second slope 58 above the blind hole inlet 22 is much more pronounced, whereas the intermediate ring surface 64 on the inner sealing surface 20 between the second slope 58 and by the seat 30 generated notch in the inner sealing surface 20 is substantially shorter.
  • the first ring width 60 continuously increases while the intermediate ring surface 64 continuously decreases.
  • the notch in the inner sealing surface 20 is deeper and the second ring width 62 is slightly increased.
  • the wear of the wear-resistant layers 40 and 42 no longer starts at the two mutually facing ends of the tip cone 26 and the seat 30, but at the opposite ends, with respect to the tip cone 26 at the blind hole diameter 32 and with respect to the seat 30 below of the cylindrical approach. Consequently, the two transitions between still existing and already abraded wear protection layer 40, 42 no longer run away from each other (divergent C-layer wear), but according to the invention proposed solution to each other (converging wear protection layer wear). This ensures, in particular, that the seat cone 30 and the tip cone 26 completely lose their respective wear protection layers 40 and 42 at the same time, since the two transitions described above inevitably result in the intersection between seat 30 and tip cone 26 unite. This safely eliminates the risk of a single-sided needle seat.
  • FIG. 6 shows the inventively proposed injection valve member in the closed state in a state of wear
  • the in Figure 5.2 corresponds to the worn state shown.
  • FIG. 6 shows that the preferably needle-shaped injection valve member 14 rests on the second slope 58 of the inner sealing surface 20 of the nozzle or injector body 18.
  • At the first sealing surface 34 of the injection valve member 14 is still a residue 72 of the wear protection layer 40 in the region of the blind hole inlet 22.
  • the first intermediate ring width 60 and the second intermediate ring width 62 unite at the inner sealing surface 20 of the nozzle or injector body 18 into a single annular surface.
  • Abrasion region 56 as shown in FIG Figure 5.2 on the first sealing surface 34 of the tip cone 26 lies on the second slope 58 on the inner sealing surface 20 (see also illustration according to FIG Figure 5.2 ) on.
  • the converging wear protection layer wear is in the figure sequence according to Figures 5.1 and 5.2 indicated by the arrow 76.
  • the tip cone 26 of the injection valve member 14 may be wholly or partially executed with a targeted out-of-roundness at the injection valve member 14 and the nozzle or injector 18 be (eg laser grooves in the injection valve member 14), which ensures a Entschrosselung this seating area even when the injection valve member slowly into the inner sealing surface 20 of the nozzle body and the injector body 18 incorporated.
  • the entsch throttled area must be sure before the intersection between the seat 30 ends with the top cone 26.
  • the beginning or the end of the de-throttled region ie the region of the injection valve member 14 which is formed in a targeted out-of-roundness, by a circumferential groove in the preferably needle-shaped injection valve member 14 or in the nozzle or injector 18 are marked to a uniform Flow to the de-throttled points (eg shown as laser groove).
  • the seat is designed such that the injection valve member 14 initially rests on the blind hole diameter 32, the seat cone 30 can be throttled in place of the tip cone 26 and the tip cone 26 can assume the sealing function.
  • the intersection between the seat 30 and the top cone 26 may be provided with a radius or with a defined edge break.
  • the concave seat shape can also be accomplished by any other contour of the injection valve member 14, which has a concave gap between the needle-shaped injection valve member 14 and the nozzle or injector body generated.
  • the concave gap 70 has no further local maxima in addition to the absolute maximum of its gap height.
  • the concave gap 70 may also be created by a non-linear conical contour of the inner sealing surface 20.
  • the materials for the wear protection layers 40 and 42 which are made of amorphous diamond-like carbon, other abrasion resistant materials can be used.

Landscapes

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

Claims (12)

  1. Injecteur de carburant (10) pour moteurs à combustion interne, présentant un organe (14) de soupape d'injection sur lequel est formé un cône de siège (30) avec lequel l'organe (14) de soupape d'injection coopère par un déplacement longitudinal avec une surface d'étanchéité (20) réalisée sur un corps d'injecteur (18) et libère ou ferme ainsi un écoulement de carburant vers au moins une ouverture d'injection, le cône de siège (30) étant doté d'une couche (42) de protection contre l'usure,
    caractérisé en ce que
    un cône (26) en pointe à un angle de cône α, est formé à l'extrémité de l'organe (14) de soupape d'injection située du côté de la chambre de combustion,
    en ce que le cône de siège (30) est formé à un angle de cône β,
    en ce que l'angle de cône β est supérieur à l'angle de cône γ de la surface d'étanchéité (20) et
    en ce que l'angle de cône α, du cône en pointe (26) est inférieur à l'angle de cône γ de la surface d'étanchéité (20).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que les surfaces coniques du cône de siège (30) et du cône en pointe (26) forment avec la surface d'étanchéité (20) un interstice concave (70).
  3. Injecteur de carburant selon la revendication 2, caractérisé en ce que l'interstice concave (70) s'étend entre une entrée (22) en puits aveugle ménagée dans le corps d'injecteur (18) et un emplacement de transition entre le cône de siège (30) et un appendice cylindrique de l'organe (14) de soupape d'injection.
  4. Injecteur de carburant selon la revendication 3, caractérisé en ce que lorsque l'organe (14) de soupape d'injection est en position fermée, le maximum G de la distance entre l'organe (14) de soupape d'injection et le corps d'injecteur (18) est situé à l'emplacement de l'intersection entre le cône de siège (30) et le cône en pointe (26).
  5. Injecteur de carburant selon la revendication 3, caractérisé en ce que lorsque l'organe (14) de soupape d'injection est en position fermée, un interstice plus petit défini par une distance G3 > 0 s'établit sur l'entrée (22) en trou oblong réalisée à un diamètre (32) de trou oblong et l'organe (14) de soupape d'injection.
  6. Injecteur de carburant selon la revendication 4, caractérisé en ce que l'emplacement de l'intersection entre le cône de siège (30) et le cône en pointe (26) est doté d'un arrondi ou d'un chanfrein définis.
  7. Injecteur de carburant selon la revendication 1, caractérisé en ce que tout ou partie du cône en pointe (26) réalisé sur l'organe (14) de soupape d'injection ou de la surface (20) du corps d'injecteur (18) présente un défaut de rotondité.
  8. Injecteur de carburant selon la revendication 4, caractérisé en ce qu'en plus du maximum de distance G, l'interstice concave (70) ne présente aucun autre maximum local de la distance entre l'organe (14) de soupape d'injection et le corps d'injecteur (18).
  9. Injecteur de carburant selon la revendication 1, caractérisé en ce que lorsque l'organe (14) de soupape d'injection est à l'état neuf, il repose par son cône en pointe (26) sur une entrée (22) en trou aveugle et en ce que le cône en pointe (26) libère ou interrompt l'écoulement de carburant à la place du cône de siège (30).
  10. Injecteur de carburant selon la revendication 7, caractérisé en ce qu'une partie du cône en pointe (26). dotée d'un défaut de rotondité se termine en avant de l'emplacement d'intersection entre le cône en pointe (26) et le cône de siège (30) sur l'organe (14) de soupape d'injection et en ce que l'extrémité de la partie du cône en pointe (26) dotée d'un défaut de rotondité est délimitée par une rainure périphérique ménagée dans l'organe (14) de soupape d'injection ou dans le corps d'injecteur (18).
  11. Injecteur de carburant selon la revendication 1, caractérisé en ce que le cône de siège (30) et le cône en pointe (26) sont tous deux dotés de couches (40, 42) de protection contre l'usure, l'usure des extrémités mutuellement opposées des couches (40, 42) de protection contre l'usure prévues sur le cône de, siège (30) et le cône en pointe (26) convergeant l'une vers l'autre lorsque l'organe (14) de soupape d'injection est en fonctionnement.
  12. Injecteur de carburant selon la revendication 11, caractérisé en ce que l'usure de la première couche (14) de protection contre l'usure prévue sur le cône en pointe (26) s'établit en partant de l'entrée (22) en trou aveugle et en ce que l'usure de la deuxième couche (42) de protection contre l'usure s'établit partant de l'emplacement de transition entre le cône de siège (30) et un appendice cylindrique de l'organe (14) de soupape d'injection.
EP06819042.0A 2005-08-11 2006-06-13 Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant Not-in-force EP1915527B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510037955 DE102005037955A1 (de) 2005-08-11 2005-08-11 Teilentdrosseltes Einspritzventilglied für Kraftstoffinjektoren
PCT/EP2006/063116 WO2007017302A1 (fr) 2005-08-11 2006-06-13 Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant

Publications (2)

Publication Number Publication Date
EP1915527A1 EP1915527A1 (fr) 2008-04-30
EP1915527B1 true EP1915527B1 (fr) 2018-03-14

Family

ID=36790400

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06819042.0A Not-in-force EP1915527B1 (fr) 2005-08-11 2006-06-13 Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant

Country Status (3)

Country Link
EP (1) EP1915527B1 (fr)
DE (1) DE102005037955A1 (fr)
WO (1) WO2007017302A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019220072A1 (de) 2019-12-18 2021-06-24 Robert Bosch Gmbh Einspritzdüse zur Einspritzung von Kraftstoff unter hohem Druck

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0283154A1 (fr) * 1987-03-14 1988-09-21 LUCAS INDUSTRIES public limited company Injecteur de combustible
DE4117910A1 (de) * 1991-05-31 1992-12-03 Yaroslavskij Z Dizel Noj Appar Einspritzduese fuer brennkraftmaschinen
DE19844638A1 (de) * 1998-09-29 2000-03-30 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10000501A1 (de) * 2000-01-08 2001-07-19 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10133433A1 (de) * 2001-07-10 2003-02-20 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10315821A1 (de) * 2002-11-11 2004-05-27 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102004013600A1 (de) 2004-03-19 2005-10-06 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
WO2007017302A1 (fr) 2007-02-15
EP1915527A1 (fr) 2008-04-30
DE102005037955A1 (de) 2007-02-15

Similar Documents

Publication Publication Date Title
DE19612738C2 (de) Speichereinspritzsystem für Brennkraftmaschinen
DE19946827C1 (de) Ventil zum Steuern von Flüssigkeiten
WO1999058844A1 (fr) Injecteur de carburant pour moteur a combustion interne
EP1129287B1 (fr) Buse d'injection pour moteurs a combustion interne avec pointeau pourvu d'une rainure annulaire
EP1045978A1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne
EP2470771B1 (fr) Injecteur de carburant
DE19634933B4 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2006063912A1 (fr) Soupape d'injection de carburant pour moteur a combustion interne
WO2004092576A1 (fr) Injecteur de carburant pour moteur a combustion interne
DE10100390A1 (de) Einspritzventil
EP1430218B1 (fr) Soupape, en particulier soupape d'injection de carburant
EP1346143A1 (fr) Soupape d'injection de carburant destinee a des moteurs a combustion interne
DE10205218A1 (de) Ventil zur Steuerung einer Verbindung in einem Hochdruckflüssigkeitssystem, insbesondere einer Kraftstoffeinspitzeinrichtung für eine Brennkraftmaschine
EP1915527B1 (fr) Element de soupape d'injection reduisant partiellement l'etranglement pour injecteurs de carburant
DE102012211169A1 (de) Kraftstoffinjektor
EP2167808B1 (fr) Injecteur haute pression pour moteurs à combustion interne à appui de tige de commande à charge de flambage croissante par l'intermédiaire de carburant haute pression
DE102010040940A1 (de) Düsenbaugruppe für einen Kraftstoffinjektor
DE102018208361A1 (de) Verfahren zum Betreiben eines Kraftstoffinjektors, Kraftstoffinjektor
EP1412633B1 (fr) Injecteur de carburant a compensation de pression de fermeture
EP1483499A1 (fr) Systeme pour moduler en pression le comportement d'injection
DE10048933A1 (de) Ventil zum Steuern von Flüssigkeiten
EP3999736B1 (fr) Injecteur de carburant destiné à des moteurs à combustion interne
EP3980639B1 (fr) Injecteur de carburant et procédé pour faire fonctionner un injecteur de carburant
AT511731B1 (de) Kavitationsoptimierte drosselbohrungen
EP1387947A1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20080311

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20081104

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20171215

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 979145

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502006015836

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180314

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180615

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502006015836

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180716

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20181217

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180630

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180613

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180630

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 979145

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180613

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190822

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180314

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20060613

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180714

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006015836

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210101