EP1078157B1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
EP1078157B1
EP1078157B1 EP99957920A EP99957920A EP1078157B1 EP 1078157 B1 EP1078157 B1 EP 1078157B1 EP 99957920 A EP99957920 A EP 99957920A EP 99957920 A EP99957920 A EP 99957920A EP 1078157 B1 EP1078157 B1 EP 1078157B1
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EP
European Patent Office
Prior art keywords
valve
fuel injection
lever
segments
injection valve
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.)
Expired - Lifetime
Application number
EP99957920A
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German (de)
English (en)
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EP1078157A1 (fr
Inventor
Hubert Stier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1078157A1 publication Critical patent/EP1078157A1/fr
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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F02M51/0607—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means the actuator being hollow, e.g. with needle passing through the hollow space
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical

Definitions

  • the invention relates to a fuel injection valve according to the preamble of claim 1.
  • a fuel injection valve according to the preamble of claim 1 is already known.
  • a piezoelectric actuator When originating from this document translation device is a piezoelectric actuator is loaded to open the valve needle. In this case, the piezoelectric actuator expands and moves a primary piston against the force of a spring. Inside the primary piston, a secondary piston is provided which is fixedly connected to a valve needle. In the secondary piston, a small spring is provided, which is arranged between an inner surface of the primary piston and the secondary piston.
  • the primary piston and the secondary piston a fuel-filled working space is limited. In this case, the working space is designed so that only by a movement of the primary piston and / or the secondary piston, a change in the volume of the working space can be achieved. The movement of the primary piston therefore causes the secondary piston to move.
  • the surfaces effectively available upon movement of the pistons to displace the volume may be determined by the diameters of primary pistons and Secondary piston can be specified. The translation results from the ratio of these areas.
  • a disadvantage of this known translation device is the relatively complex and not optimized in terms of compactness design. Furthermore, the small spring provided in the secondary piston is insufficient to directly actuate the fuel injection valve. The actuation of the fuel injection valve therefore takes place in the cited document via an additional amplifying device. This amplification device is relatively expensive and requires additional space.
  • Another disadvantage is that a large mass must be moved to actuate the valve by the actuator and the action of the actuator via elastic and / or resilient components and hydraulic fluids, resulting in relatively long switching times, so that the fuel injector is not fast switching Fuel injector suitable for high switching frequencies.
  • a fuel injection valve is already known, which is designed as a diesel fuel injection valve for fuel injection systems of self-igniting internal combustion engines.
  • the fuel injection valve has a piezoelectric actuator and an indirectly actuatable by the actuator via a control piston and by the high hydraulic pressure of the diesel fuel by means of a valve needle valve closing body which cooperates with a valve seat surface to a sealing seat on.
  • a translation device for the translation of an actuator stroke of the actuator is arranged in a larger valve needle lift of the valve needle.
  • the translation device comprises a lever plate in the form of a spring washer, which is clamped between a pressure body and a support body.
  • the pressure body and the support body each have protruding collar, wherein the collar of the pressure body are arranged on a larger diameter than the collar of the support body and the collar of both pressure and support body act on the lever plate.
  • the collars of the support body form the tilting points of the lever plate.
  • the lever plate is fastened to a lifting element, which executes an axial movement within the supporting body when the piezoelectric actuator is excited by the tilting lever plate.
  • the axial lifting of the lifting element leads to the opening of a closed with a ball control valve and thus indirectly to open the fuel injection valve.
  • a fluid control valve which has a piezoelectric actuator and a lever sleeve arranged between the actuator and an axially movable plunger for translating an actuator stroke of the actuator into a larger plunger stroke.
  • the lever sleeve has a tubular base body and at one end face of the base body at least two radially extending lever tongues with axially projecting collar.
  • a base plate of the actuator abuts against the serving as tilting collar of the two lever tongues, whereby these tilted in energized piezoelectric actuator inwards and the plunger can perform an axial lifting movement for opening and closing the fluid control valve in the region of a sealing seat.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that results from the simple solution of the translation device, a cost-effective and significantly more compact design. Furthermore, no hydraulic medium is needed. Thus, the new solution is also suitable for blistering fuel gasoline.
  • the Hubübersky by the radially extending rigid lever segments of high stiffness and therefore allows high switching frequencies, which can be used as a fast-switching fuel injection valve, the fuel injection valve.
  • the lever segments have embossments extending from the center of the lever plate to the edge of the lever plate. As a result, the lever segments are additionally stiffened, which allows even shorter switching times.
  • a plurality of lever segments are provided, which are separated by recesses.
  • the lever segments are connected to each other in an advantageous manner, so that the arrangement of the individual lever segments is fixed to each other and is not defined by an additional attachment.
  • the lever plate of two different types of segments of which one type of segments is designed as a rigid lever segments and the other type of segments is designed as elastic, flexible spring segments.
  • one type of segments is designed as a rigid lever segments and the other type of segments is designed as elastic, flexible spring segments.
  • the lever plate also takes over the function of the return spring or the compression spring, which can save components.
  • the lever segments are mounted on a thin, elastic and flexible retaining disc.
  • This allows the rigid lever segments to bring each other in a solid, non-contact arrangement.
  • this results in special design options for the Lever segments of the lever plate, which are not or only with difficulty in the manufacture of the lever plate in one piece.
  • the retaining washer made of a metal sheet or plastic, in particular polyamide. This results in a petrol-resistant, cost-effective and compact construction of the lever plate.
  • the actuator acts via a tubular pressure sleeve at a central bearing point on the lever segments, that the lever segments abut against the valve housing at an outer bearing point and that the lever segments at an inner support point attack the valve needle. Due to the lever plate a particularly cost-effective, space-saving and low-maintenance design of the translation device is given. It is advantageous if the pressure sleeve is partially enclosed by the actuator, wherein the actuator has a recess for this purpose. As a result, the pressure sleeve can run in the interior of the actuator, resulting in a particularly space-saving embodiment.
  • the interior of the pressure sleeve may be formed as a fuel line and / or space for additional components such.
  • B. compression springs, return springs, support and fasteners offer.
  • the pressure sleeve is widened on the side of the lever segments.
  • a return spring acts on the lever segments and that a compression spring on the valve needle on the lever segments in the opposite direction to Compressive spring acts, wherein the compression spring exerts a greater torque on the lever segments than the return spring.
  • the opening force on the valve needle which is given by the force of the compression spring on the lever segments, which can be adjusted taking into account the actuator movement and the valve needle mass on the opening movement, the opening speed.
  • the force acting on the valve needle restoring force can be determined by the force of the return spring. Taking into account the actuator movement of the actuator and the valve needle mass can be adjusted by the closing movement of the valve needle, given closing speed.
  • the fuel injection valve is an outwardly opening fuel injection valve, that the actuator in the pressure sleeve in a central support point acts on the lever segments, that the lever segments rest in an outer bearing point on the valve housing, that the lever segments via an inner support point on the Acting valve needle and that a compression spring acts on the lever segments, wherein the torque with which the compression spring acts on the lever segments, is directed opposite to the torque and the actuator acts on the lever segments.
  • the stroke ratio of an actuator stroke the actuator in a valve needle lift of the valve needle can be chosen favorably.
  • valve needle which is pressed by the restoring force of the return spring against the lever segments, experiencing no radial force at the inner support point and thus tension-free in the radial direction against the valve seat with any assistance is pressed by suitable needle guides.
  • Fig. 1 shows in a partial axial sectional view of an inventive fuel injection valve 1.
  • the fuel injection valve 1 is designed as an inwardly opening fuel injection valve 1.
  • the fuel injection valve 1 is used in particular for the direct injection of fuel, in particular of gasoline, into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine as so-called gasoline direct injection valve.
  • the fuel injection valve 1 according to the invention is also suitable for other applications.
  • the fuel injection valve 1 has an actuatable by means of a valve needle 2 valve closing body 3.
  • the valve closing body 3 is formed in one piece with the valve needle 2 in the exemplary embodiment.
  • the valve closing body 3 is designed frustoconically, wherein the truncated cone tapers in Abspritzraum.
  • the valve closing body 3 cooperates with a formed on a valve seat body 4 valve seat surface 5 to a sealing seat.
  • the valve needle 2 is guided in its movement along the valve axis 6 by valve needle guides 7, 8.
  • the valve seat body 4 and the valve needle guides 7, 8 are located in a front discharge-side part of a Valve housing 9.
  • the supply of the fuel via a fuel port 10, which is located in the rear part of the valve housing 11.
  • actuator 13 which may be performed piezoelectric or magnetostrictive.
  • the actuation of the actuator 13 via an electrical control signal.
  • the electrical supply line required for this purpose is to be connected via a connection socket 14 in the rear part of the valve housing 11 to the fuel injection valve 1.
  • this expands and counteracts the force of a biasing spring 15 in the rear part of the valve housing 11 on a tubular pressure sleeve 16 in the middle part of the valve housing 12 a.
  • the tubular pressure sleeve 16 moves in the direction of the fuel port 10 in the rear part of the valve housing eleventh
  • the fuel supply into a fuel chamber 17 is that an inner fuel passage 18 in the tubular pressure sleeve 16, an inner fuel passage 19 in a tubular support member 20, suitable passages in a lever plate 21 and / or in the lever plate 21 facing part of the tubular pressure sleeve 16th and the valve needle guide 7, 8 are provided, through which the fuel is introduced into the fuel chamber 17.
  • a return spring 22, which is located inside the tubular pressure sleeve 16 acts on the valve needle 2, so that the frusto-conical valve closing body 3 of the valve needle 2 is pressed against the valve seat surface 5 of the valve seat 4, whereby no fuel the fuel chamber 17 can escape into the combustion chamber of an internal combustion engine.
  • the biasing spring 15 acts in the rear part of the valve housing 11 via the tubular pressure sleeve 16 in the middle part of the valve housing 12 at a central support point 23 so on the lever plate 21 that a force acting on the lever plate 21 compression spring 24, without actuation of the actuator 13 is inhibited by the tubular pressure sleeve 16.
  • the compression spring 24 engages on the lever plate 21 on the valve needle 2 at an inner support point 25.
  • the return spring 22 is located on the opposite side of the valve needle 2 to the fixedly arranged in the pressure sleeve 16 tubular support element 20 at.
  • the fuel valve 1 In order to inject the fuel into the combustion chamber of the internal combustion engine, the fuel valve 1 is actuated via the actuator 13. As described above, the tubular pressure sleeve 16 moves upon actuation of the actuator 13 in the direction of the rear part of the valve housing 11, whereby the tubular pressure sleeve 16 is no longer acting on the lever plate 21 against the compression spring 24. Since the compression spring 24 acts with a larger torque on the lever plate 21 than the return spring 22, lever segments 26, 27 of the lever plate 21 are tilted, wherein the lever segments 26, 27 are supported on the outer abutment point 28 on the front discharge-side part of the valve housing 9.
  • valve needle 2 When tilting the lever segments 26, 27 of the lever plate 21, the valve needle 2, which is guided by the valve needle guides 7, 8, along the valve axis 6 in the direction of the fuel port 10, whereby the frusto-conical valve closing body 3 lifts from the valve seat surface 5 of the valve seat 4 and releases the sealing seat. Due to the resulting gap between the valve closing body 3 and the valve seat 4, fuel is discharged from the fuel chamber 17 of the fuel injection valve 1 into the combustion chamber of the internal combustion engine.
  • the biasing spring 15 acts via the tubular pressure sleeve 16 at the central support point 23 on the lever segments 26, 27 of the lever plate 21, wherein the caused by the biasing spring 15, acting on the lever plate 21 Torque is greater than that caused by the compression spring 24 torque, so that the lever segments 26, 27 of the lever plate 21 are returned to their original position, wherein the lever segments 26, 27 are supported on the outer abutment point 28 on the front discharge-side part of the valve housing 9.
  • the compression spring 24 no longer acts on the valve needle 2 via the lever plate 21 at the inner support point 25.
  • the valve needle 2 is in its closed position in which the valve closing body 3 with the valve seat body 4 on the valve seat surface 5 forms a sealing seat, pushed back and thus the escape of fuel from the fuel chamber 17 is interrupted in the combustion chamber of the internal combustion engine.
  • the return spring 22 can be acted upon with an adjustable bias, so that can be set by the return spring 22 predetermined contact force for pressing the valve closing body 3 of the valve needle 2 against the valve seat surface 5 of the valve seat 4.
  • Fig. 2 shows in a partial axial sectional view of a second embodiment of a fuel injection valve according to the invention 1.
  • this embodiment in contrast to the in Fig. 1 illustrated embodiment to an outwardly opening fuel injector 1.
  • Already described elements are provided with matching reference numerals. On a repetitive description is omitted in this respect.
  • the Aktorhub the actuator 13 takes place upon actuation of the fuel injection valve 1 in the direction of the front part of the valve housing 9, whereby the actuator 13 via the tubular pressure sleeve 16 at the central support point 23 directly to the lever plate 21st acts.
  • the biasing spring 15 off Fig. 1 can therefore be omitted. Since, in order to close the fuel injection valve 1, the frusto-conical valve closing body 3 widening in the discharge direction must be pressed against the valve seat body 4 in the direction of the rear part of the valve housing 11, the return spring 22 acts with a force along the valve axis 6 in the direction of the rear one Part of the valve housing 11 on the valve needle 2 a. In this case, the return spring 22 can be supported directly on the valve needle guide 8 or an additional support element can be provided.
  • the compression spring 24 acts in the same way as in Fig. 1 at the central support point 23 on the lever segments 26, 27 of the lever plate 21 a.
  • the actuator 13 is actuated, wherein this expands and acts on the lever plate 21 via the tubular pressure sleeve 16 at the central support point 23 and, since the generated by the actuator force of the actuator 13 and the lever segments 26, 27 acting Torque is greater than the torque acting on the lever segments 26, 27 of the lever plate 21 by the force of the return spring 22 is moved against the restoring force of the return spring 22, whereby the lever segments 26, 27 act on the inner support point 25 on the valve needle 2 and these along move the valve axis 6 in the direction of the valve seat body 4, whereby the frusto-conical valve-closing body 3 lifts off on the valve seat surface 5 from the valve seat body 4 and releases the sealing seat. Due to the resulting gap between valve closing body 3 and valve seat 4, there is the escape of fuel from the fuel chamber 17 of the fuel injection valve 1 in the combustion chamber of the internal combustion engine.
  • the compression spring 24 acts on the lever segments 26, 27 of the lever plate 21 and returns them to their original position.
  • the actuator 13 acts via the tubular pressure sleeve 16 and over the Lever plate 21 no longer at the inner support point 25 on the valve needle 2, whereby the return spring 22, the valve needle 2 along the valve axis 6 in the direction of the rear part of the valve housing 11 resets and thus the frusto-conical valve closing body 3 pressed against the valve seat surface 5 against the valve seat body 4 becomes.
  • the contact pressure for pressing the valve closing body 3 against the valve seat surface 5 of the valve seat body 4 can be adjusted by the axial position of the valve needle guide 8.
  • Fig. 3 shows the front view of an embodiment of the lever plate 21.
  • the lever plate 21 has an inner recess 29, lever segments 30, 31, 32 which are separated by outer recesses 33, 34, 35 and connecting webs 36, 37, 38, each of which two of the lever segments 30, 31, 32 together, on.
  • the lever segments 30, 31, 32 have z. B. the shape of Kreisausschnitten or sectors.
  • the inner recess 29 and the outer recesses 33, 34, 35 can also serve as a fuel feedthrough.
  • the lever segments 30, 31, 32 are rigid, which is due to the material thickness of the lever segments 30, 31, 32 and / or radially extending embossments 39, 40, 41, in Fig. 3 can be reached only on a lever segment 32 example, reach.
  • the shape of the inner recess 29, the outer recesses 33, 34, 35 is not on the illustrated shape and number, the lever segments 30, 31, 32 are not on the number shown and the embossments 39, 40, 41 are also not on the shown form and number limited.
  • not necessarily all lever segments 30, 31, 32 of a lever plate 21 have the same type of stiffening.
  • lever segments 30, 31, 32 are marked by imprints 39, 40, 41 in the following figures. To simplify the presentation and description, as well as in the Fig. 3 , only three lever segments 30, 31, 32 shown.
  • Fig. 4 is the section through the lever segment 32 of the lever plate 21, in Fig. 3 and is indicated by the intersection line labeled IV - IV.
  • the embossments 39, 40, 41 can be attached both on the equilateral side as the embossment 39 and the embossment 41, as well as each other as the embossing 39 and 40.
  • the embossments can be formed equally strong, such as embossment 39 and embossment 40, as well as different degrees, such as embossing 40 and 41.
  • Fig. 5 shows the front view of an alternative embodiment of the invention lever plate 21. Already described elements are provided with matching reference numerals. On a repetitive description is omitted in this respect.
  • the inner recess 29 and the outer recesses 33, 34, 35 are not separated from each other in this embodiment.
  • the lever segments 30, 31, 32 of the lever plate 21 are interconnected by connecting webs 36, 37, 38, which extend circumferentially on the outer edge 41 a of the lever plate 21. In contrast to the lever segments 30, 31, 32 off Fig. 3 Therefore, the lever segments 30, 31, 32 are tilted inwards.
  • Fig. 6 shows the front view of another embodiment of the lever plate 21 according to the invention. Already described elements are provided with matching reference numerals.
  • the lever plate 21 has an inner recess 29 and outer slot-like, radially star-shaped extending recesses 33, 34, 35, 42, 43, 44, which are interconnected on.
  • the resulting segments 30, 31, 32, 45, 46, 47 of the lever plate 21 are divided into two different ways of segments 30, 31, 32, 45, 46, 47, one of which is formed as a type of segments as rigid lever segments 30, 31, 32 and the other type of segments as elastic, flexible spring segments 45, 46, 47.
  • the segments are held together by the connecting webs 36, 37, 38, 48, 49, 50, which are located on the outer edge 41 a of the lever plate 21.
  • Fig. 7 shows the front view of another alternative embodiment of the invention lever plate 21.
  • the lever segments 30, 31, 32 of the lever plate 21 are not held together by connecting webs in this embodiment, but are mounted on a thin, elastic and flexible retaining plate 51.
  • an inner recess 29 may be provided, which allows a better bending of the thin, elastic and flexible retaining disk 51 or a fuel flow through them.
  • the thin, elastic and flexible retaining plate 51 is made of a fuel-resistant material such.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Mechanically-Actuated Valves (AREA)

Abstract

L'invention concerne une soupape d'injection de carburant (1), notamment une soupape d'injection pour des systèmes d'injection de carburant de moteurs à combustion interne. Cette soupape présente un premier actionneur piézo-électrique ou magnétostrictif (13), un obturateur de soupape (3) qui peut être actionné par l'actionneur (13) au moyen d'un pointeau (2) et qui coopère avec une surface de siège de soupape (5) pour former un siège d'étanchéité, et une unité de transmission placée entre l'actionneur (13) et le pointeau (2), servant à transformer la course de l'actionneur (13) en une course plus importante du pointeau (2). Cette unité de transmission présente au moins une plaque de levage (21) qui comporte au moins un segment de levage (26, 27) rigide, s'étendant dans le sens radial.

Claims (14)

  1. Injecteur de carburant (1), notamment injecteur pour des installations d'injection de carburant de moteurs à combustion interne comportant un actionneur magnétostrictif ou piézo-électrique (13), un organe d'obturation de soupape (3) actionné par l'actionneur (13), par l'intermédiaire d'une aiguille d'injecteur (2), cet organe coopérant avec une surface formant siège de soupape (5) pour former un siège d'étanchéité ainsi qu'une installation de démultiplication entre l'actionneur (13) et l'aiguille d'injecteur (2) pour démultiplier la course de l'actionneur (13) et réaliser une course plus grande de l'aiguille d'injecteur 2), l'installation de démultiplication ayant au moins une plaque-levier (21),
    caractérisé en ce que
    la plaque-levier (21) comporte un segment de levier (26, 27, 30-32) radial, rigide, et au moins un segment de levier (26, 27, 30-32) ayant des déformations à partir du centre de la plaque-levier (21) vers le bord (41a) de la plaque-levier (21).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé par
    plusieurs segments de levier (26, 27, 30-32) séparés les uns des autres par des découpes (29, 33-35, 42-44).
  3. Injecteur de carburant selon l'une des revendications 1 ou 2,
    caractérisé en ce que
    la plaque-levier (21) est formée de deux types de segment différents, l'un des types de segment étant constitué par des segments de levier rigides (30-32) et l'autre type de segment étant constitué par des segments de ressort (45-47) élastiques souples.
  4. Injecteur de carburant selon l'une des revendications 1 à 3,
    caractérisé en ce que
    les segments de levier (30-32) sont fixés sur un disque de fixation (51) mince, élastique et souple.
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que
    le disque de fixation (51) est une tôle.
  6. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que
    le disque de fixation (51) est en une matière élastique, notamment un polyamide.
  7. Injecteur de carburant selon l'une des revendications 1 à 6,
    caractérisé en ce que
    l'injecteur (1) s'ouvre vers l'intérieur,
    l'actionneur (13) agit par l'intermédiaire d'un manchon de poussée (16), tubulaire, contre un point d'appui médian (23) sur les segments de levier (26, 27),
    les segments de levier (26, 27) s'appliquent contre un point d'appui extérieur (28) du boîtier de soupape (9) et
    des segments de levier (26, 27) agissent en un point d'appui intérieur (25) contre l'aiguille d'injecteur (2).
  8. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    le manchon de poussée (16) est entouré au moins par segments par l'actionneur (13) et celui-ci (13) comporte à cet effet une découpe.
  9. Injecteur de carburant selon l'une des revendications 7 ou 8,
    caractérisé en ce que
    le manchon de poussée (16) est élargi du côté des segments de levier (26, 27).
  10. Injecteur de carburant selon l'une des revendications 7 à 9,
    caractérisé en ce que
    la distance moyenne du point d'appui extérieur (28) par rapport à l'axe d'injecteur (6) est supérieure à la distance moyenne de la surface d'appui moyenne (23) par rapport à l'axe d'injecteur (6) et
    la distance moyenne du point d'appui moyen par rapport à l'axe d'injecteur (6) est supérieure à la distance moyenne du point d'appui intérieur (25) par rapport à l'axe d'injecteur (6).
  11. Injecteur de carburant selon l'une des revendications 7 à 10,
    caractérisé par
    un ressort de compression (24) agissant sur les segments de levier (26, 27),
    un ressort de rappel (22) agit par l'intermédiaire de l'aiguille d'injecteur (2) sur les segments de levier (26, 27) dans la direction opposée à la direction d'action du ressort de compression (24),
    le ressort de compression (24) exerçant un couple plus grand sur les segments de levier (26, 27) que le ressort de rappel (22).
  12. Injecteur de carburant selon l'une des revendications 1 à 6,
    caractérisé en ce que
    l'injecteur (1) s'ouvre vers l'extérieur,
    l'actionneur (13) agit par l'intermédiaire d'un manchon de poussée (16) en un point d'appui médian sur les segments de levier (26, 27),
    les segments de levier (26, 27) s'appliquent contre un point d'appui extérieur (28) du le boîtier d'injecteur (12),
    les segments de levier (26, 27) agissent sur l'aiguille d'injecteur (2) par un point d'appui intérieur (25),
    un ressort de compression (24) agit sur les segments de levier (26, 27), le couple par lequel le ressort de compression (24) agit sur les segments de levier (26, 27) est dirigé en sens opposé du couple par lequel l'actionneur (13) agit sur les segments de levier (26, 27).
  13. Injecteur de carburant selon la revendication 12,
    caractérisé en ce que
    la distance moyenne du point d'appui extérieur (28) par rapport à l'axe d'injecteur (6) est supérieure à la distance moyenne du point d'appui intermédiaire (23) par rapport à l'axe d'injecteur (6) et
    la distance moyenne du point d'appui intermédiaire (23) par rapport à l'axe d'injecteur (6) est supérieure à la distance moyenne du point d'appui intérieur (25) par rapport à l'axe d'injecteur (6).
  14. Injecteur de carburant selon les revendications 13 ou 14,
    caractérisé en ce qu'
    un ressort de rappel (22) agit sur l'aiguille d'injecteur (2), la force par laquelle le ressort de rappel (22) agit sur l'aiguille d'injecteur (2) est dirigée en sens opposé de celle de la force par laquelle les segments de levier (26, 27) agissent sur l'aiguille d'injecteur (2).
EP99957920A 1999-03-12 1999-10-20 Soupape d'injection de carburant Expired - Lifetime EP1078157B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19911048A DE19911048A1 (de) 1999-03-12 1999-03-12 Brennstoffeinspritzventil
DE19911048 1999-03-12
PCT/DE1999/003356 WO2000055492A1 (fr) 1999-03-12 1999-10-20 Soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP1078157A1 EP1078157A1 (fr) 2001-02-28
EP1078157B1 true EP1078157B1 (fr) 2008-03-05

Family

ID=7900734

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99957920A Expired - Lifetime EP1078157B1 (fr) 1999-03-12 1999-10-20 Soupape d'injection de carburant

Country Status (6)

Country Link
US (1) US6494382B1 (fr)
EP (1) EP1078157B1 (fr)
JP (1) JP2002539370A (fr)
KR (1) KR20010043148A (fr)
DE (2) DE19911048A1 (fr)
WO (1) WO2000055492A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1325227B1 (fr) * 2000-10-11 2006-07-05 Siemens VDO Automotive Corporation Ensemble compensateur a membrane souple pour injecteur de carburant et procede correspondant
US6749127B2 (en) 2002-02-11 2004-06-15 Siemens Vdo Automotive Corporation Method of filling fluid in a thermal compensator
DE20220800U1 (de) * 2002-10-24 2004-04-08 Vermes Technik Gmbh & Co. Kg Piezoelektrisches Aktorsystem
DE10307003B3 (de) * 2003-02-19 2004-05-13 Siemens Ag Einspritzventil für die Einspritzung von Kraftstoff in eine Verbrennungskraftmaschine
DE10326707B3 (de) * 2003-06-11 2005-01-27 Westport Germany Gmbh Ventilvorrichtung und Verfahren zum Einblasen von gasförmigem Kraftstoff
US8074625B2 (en) 2008-01-07 2011-12-13 Mcalister Technologies, Llc Fuel injector actuator assemblies and associated methods of use and manufacture
US9309846B2 (en) 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
US20140131466A1 (en) 2012-11-12 2014-05-15 Advanced Green Innovations, LLC Hydraulic displacement amplifiers for fuel injectors
JP6138502B2 (ja) * 2013-02-04 2017-05-31 日立オートモティブシステムズ株式会社 燃料噴射弁
WO2018066327A1 (fr) * 2016-10-03 2018-04-12 日立オートモティブシステムズ株式会社 Soupape d'injection de carburant
CN113811397A (zh) * 2019-05-12 2021-12-17 诺信公司 具有机械放大器的分配系统

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DE1751543A1 (de) 1968-06-15 1970-08-27 Kloeckner Humboldt Deutz Ag Elektrisch steuerbares Einspritzventil
US4022166A (en) * 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
JPS601369A (ja) * 1983-06-16 1985-01-07 Nippon Soken Inc 燃料噴射弁
US4695034A (en) * 1984-11-27 1987-09-22 Stec Inc. Fluid control device
JPS62157274A (ja) 1985-12-28 1987-07-13 Aisan Ind Co Ltd 燃料噴射弁
JPH0364662A (ja) * 1989-08-03 1991-03-20 Nissan Motor Co Ltd 燃料噴射弁
JPH02112664A (ja) * 1989-09-20 1990-04-25 Hitachi Ltd 圧電式燃料噴射弁
US5636615A (en) * 1995-02-21 1997-06-10 Diesel Technology Company Fuel pumping and injection systems
JP3740733B2 (ja) * 1996-02-13 2006-02-01 いすゞ自動車株式会社 内燃機関の燃料噴射装置
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
JPH11132127A (ja) * 1996-11-13 1999-05-18 Denso Corp 燃料噴射弁及びその組立方法
DE19706469A1 (de) * 1997-02-19 1998-08-27 Daimler Benz Ag Speichereinspritzsystem für eine mehrzylindrige Brennkraftmaschine mit magnetventilgesteuerten Kraftstoffeinspritzventilen

Also Published As

Publication number Publication date
KR20010043148A (ko) 2001-05-25
JP2002539370A (ja) 2002-11-19
EP1078157A1 (fr) 2001-02-28
US6494382B1 (en) 2002-12-17
DE19911048A1 (de) 2000-09-14
WO2000055492A1 (fr) 2000-09-21
DE59914675D1 (de) 2008-04-17

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