EP1078157B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

Info

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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP1078157A1 (en
Inventor
Hubert Stier
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 EP1078157A1 publication Critical patent/EP1078157A1/en
Application granted granted Critical
Publication of EP1078157B1 publication Critical patent/EP1078157B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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.

Abstract

The invention relates to a fuel injection valve (1), especially a fuel injection valve for fuel injection systems of internal combustion engines, comprising a piezoelectric or magnetostrictive actuator (13), a valve closing body (3) which can be actuated by the actuator (13) by means of a valve needle (2) and which interacts with a valve seating (5) to form a tight seat. The inventive fuel injection valve also comprises a multiplication device which is arranged between the actuator (13) and the valve needle (2) and which is provided for multiplying an actuator stroke of the actuator (13) into a larger valve needle stroke of the valve needle (2). To this end, the multiplication device comprises at least one lever plate (21) which has at least one radially extending rigid lever segment (26, 27).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Anspruchs 1.The invention relates to a fuel injection valve according to the preamble of claim 1.

Aus der DE 195 19 192 C1 ist bereits ein Brennstoffeinspritzventil nach der Gattung des Anspruchs 1 bekannt. Bei der aus dieser Druckschrift hervorgehenden Übersetzungseinrichtung wird zum Öffnen der Ventilnadel ein Piezoaktor geladen. Dabei dehnt sich der Piezoaktor aus und bewegt einen Primärkolben gegen die Kraft einer Feder. Im Inneren des Primärkolbens ist ein Sekundärkolben vorgesehen, der mit einer Ventilnadel fest verbunden ist. Im Sekundärkolben ist eine kleine Feder vorgesehen, die zwischen einer Innenfläche des Primärkolbens und dem Sekundärkolben angeordnet ist. Durch den Primärkolben und den Sekundärkolben wird ein mit Brennstoff gefüllter Arbeitsraum begrenzt. Dabei ist der Arbeitsraum so gestaltet, daß nur durch eine Bewegung des Primärkolbens und/oder des Sekundärkolbens eine Änderung des Volumens des Arbeitsraums erreicht werden kann. Durch die Bewegung des Primärkolbens kommt es daher zu einer Bewegung des Sekundärkolbens. Die bei einer Bewegung der Kolben zur Verdrängung des Volumens effektiv zur Verfügung stehenden Flächen können durch die Durchmesser von Primärkolben und Sekundärkolben vorgegeben werden. Die Übersetzung ergibt sich aus dem Verhältnis dieser Flächen.From the DE 195 19 192 C1 a fuel injection valve according to the preamble of claim 1 is already known. 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. By 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.

Nachteilig ist bei dieser bekannten Übersetzungseinrichtung die relativ aufwendige und hinsichtlich der Kompaktheit nicht optimierte Bauform. Des weiteren reicht die im Sekundärkolben vorgesehene kleine Feder nicht aus, um direkt das Brennstoffeinspritzventil zu betätigen. Die Betätigung des Brennstoffeinspritzventils erfolgt daher in der genannten Druckschrift über eine zusätzliche Verstärkungseinrichtung. Diese Verstärkungseinrichtung ist relativ aufwendig und benötigt einen zusätzlichen Raumbedarf.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.

Ein weiterer Nachteil ist, daß zum Betätigen des Ventils durch den Aktor eine große Masse bewegt werden muß und die Einwirkung des Aktors über elastische und/oder federnde Bauelemente und Druckflüssigkeiten erfolgt, wodurch sich relativ lange Schaltzeiten ergeben, so daß sich das Brennstoffeinspritzventil nicht als schnellschaltendes Brennstoffeinspritzventil für hohe Schaltfrequenzen eignet.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.

Aus der EP 0 790 402 A2 ist bereits ein Brennstoffeinspritzventil bekannt, das als Dieselkraftstoff-Einspritzventil für Brennstoffeinspritzanlagen von selbstzündenden Brennkraftmaschinen ausgeführt ist. Das Brennstoffeinspritzventil weist einen piezoelektrischen Aktor und einen indirekt von dem Aktor über einen Steuerkolben und durch den hohen hydraulischen Druck des Dieselkraftstoffs mittels einer Ventilnadel betätigbaren Ventilschließkörper, der mit einer Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, auf. Zwischen dem Aktor und dem Steuerkolben ist eine Übersetzungseinrichtung zur Übersetzung eines Aktorhubs des Aktors in einen größeren Ventilnadelhub der Ventilnadel angeordnet. Die Übersetzungseinrichtung umfasst eine Hebelplatte in Form einer Federscheibe, die zwischen einem Druckkörper und einem Abstützkörper eingespannt ist. Der Druckkörper und der Abstützkörper weisen jeweils hervorstehende Kragen auf, wobei die Kragen des Druckkörpers auf einem größeren Durchmesser angeordnet sind als die Kragen des Abstützkörpers und die Kragen beider Druck- und Abstützkörper auf die Hebelplatte einwirken. Die Kragen des Abstützkörpers bilden die Kipppunkte der Hebelplatte. Die Hebelplatte ist an einem Hubelement befestigt, das bei erregtem piezoelektrischen Aktor durch die kippende Hebelplatte eine axiale Bewegung innerhalb des Abstützkörpers ausführt. Das axiale Anheben des Hubelements führt zum Öffnen eines mit einer Kugel verschlossenen Steuerventils und damit indirekt zum Öffnen des Brennstoffeinspritzventils.From the EP 0 790 402 A2 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. Between the actuator and the control piston, 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.

Aus der US 4,695,034 A ist bereits ein Fluidregelventil bekannt, das einen piezoelektrischen Aktor und eine zwischen dem Aktor und einem axial bewegbaren Stößel angeordnete Hebelhülse zur Übersetzung eines Aktorhubs des Aktors in einen größeren Stößelhub aufweist. Die Hebelhülse besitzt einen rohrförmigen Grundkörper und an einer Stirnseite des Grundkörpers wenigstens zwei radial verlaufende Hebelzungen mit axial hervorstehenden Kragen auf. Eine Grundplatte des Aktors liegt an den als Kipppunkte dienenden Kragen der beiden Hebelzungen an, wodurch diese bei erregtem piezoelektrischen Aktor nach innen verkippt werden und der Stößel eine axiale Hubbewegung zum Öffnen und Schließen des Fluidregelventils im Bereich eines Dichtsitzes vollführen kann.From the US 4,695,034 A For example, a fluid control valve is already known 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.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß sich durch die einfache Lösung der Übersetzungseinrichtung eine kostengünstige und erheblich kompaktere Bauweise ergibt. Des weiteren wird kein Hydraulikmedium benötigt. Damit ist die neue Lösung auch für den zur Blasenbildung neigenden Brennstoff Benzin geeignet. Außerdem ist die Hubübersetzung durch die radial verlaufenden starren Hebelsegmente von hoher Steifigkeit und ermöglicht daher hohe Schaltfrequenzen, wodurch sich das Brennstoffeinspritzventil auch als schnellschaltendes Brennstoffeinspritzventil verwenden läßt.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. In addition, the Hubübersetzung 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.

Die Hebelsegmente weisen vom Mittelpunkt der Hebelplatte zum Rand der Hebelplatte verlaufende Prägungen auf. Dadurch werden die Hebelsegmente zusätzlich versteift, was noch kürzere Schaltzeiten ermöglicht.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.

Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.

In vorteilhafter Weise sind mehrere Hebelsegmente vorgesehen, die durch Aussparungen voneinander getrennt sind. Dadurch kommt es zum einen zu einer Aufteilung der Belastung auf die Hebelsegmente, zum anderen sind die Hebelsegmente in vorteilhafter Weise miteinander verbunden, so daß die Anordnung der einzelnen Hebelsegmente zueinander fest vorgegeben ist und nicht durch eine zusätzliche Befestigung definiert wird. Durch die Aussparungen werden außerdem Spannungen in den Hebelsegmenten vermieden, was sich auf die Funktionsweise der Hubübersetzung günstig auswirkt.Advantageously, a plurality of lever segments are provided, which are separated by recesses. This results in a division of the load on the lever segments, on the other hand, 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. By the recesses also stresses in the lever segments are avoided, which has a favorable effect on the operation of the Hubübersetzung.

In vorteilhafter Weise besteht die Hebelplatte aus zwei verschiedenen Arten von Segmenten, von denen die eine Art von Segmenten als starre Hebelsegmente ausgebildet ist und die andere Art von Segmenten als elastische, biegsame Federsegmente ausgebildet ist. Zusätzlich zu den durch die starren Hebelsegmente gegebenen und oben schon besprochenen Vorteilen ergeben sich weitere besondere Vorteile durch die elastischen, biegsamen Federelemente. Denn durch letztere übernimmt die Hebelplatte auch die Funktion der Rückstellfeder oder der Druckfeder, wodurch sich Bauteile einsparen lassen.Advantageously, 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. In addition to the advantages given by the rigid lever segments and discussed above, there are further particular advantages due to the elastic, flexible spring elements. Because of the latter, the lever plate also takes over the function of the return spring or the compression spring, which can save components.

Vorteilhaft sind die Hebelsegmente auf einer dünnen, elastischen und biegsamen Haltescheibe befestigt. Dadurch lassen sich die starren Hebelsegmente zueinander in eine feste, kontaktfreie Anordnung bringen. Außerdem ergeben sich dadurch besondere Gestaltungsmöglichkeiten für die Hebelsegmente der Hebelplatte, die bei der Fertigung der Hebelplatte aus einem Stück nicht oder nur schwer möglich sind. In vorteilhafter Weise besteht die Haltescheibe aus einem Metallblech oder aus Kunststoff, insbesondere Polyamid. Damit ergibt sich eine benzinbeständige, kostengünstige und kompakte Bauweise der Hebelplatte.Advantageously, 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. In addition, 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. Advantageously, 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.

Vorteilhaft ist es, wenn das Brennstoffeinspritzventil ein nach innen öffnendes Brennstoffeinspritzventil ist, daß der Aktor über eine rohrförmige Druckhülse an einer mittleren Auflagestelle an den Hebelsegmenten einwirkt, daß die Hebelsegmente an einer äußeren Auflagestelle an dem Ventilgehäuse anliegen und daß die Hebelsegmente an einer inneren Auflagestelle an der Ventilnadel angreifen. Durch die Hebelplatte ist dadurch eine besonders kostengünstige, platzsparende und wartungsarme Ausführung der Übersetzungseinrichtung gegeben. Vorteilhaft ist es, wenn die Druckhülse abschnittsweise vom Aktor umschlossen ist, wobei der Aktor hierfür eine Aussparung aufweist. Dadurch kann die Druckhülse im Inneren des Aktors verlaufen, wodurch sich eine besonders platzsparende Ausführungsform ergibt. Außerdem kann das Innere der Druckhülse als Brennstoffleitung ausgebildet sein und/oder Platz für zusätzliche Bauteile, wie z. B. Druckfedern, Rückstellfedern, Auflage- und Befestigungselemente bieten. Des weiteren ist es vorteilhaft, daß die Druckhülse auf der Seite der Hebelsegmente verbreitert ist. Damit läßt sich bei vorgegebenem Abstand der inneren Auflagestelle zur Ventilachse der Abstand der mittleren Auflagestelle zur Ventilachse einstellen und sich somit ein geeignetes Übersetzungsverhältnis der Übersetzungseinrichtung wählen, wodurch sich das Verhältnis von Ventilnadelhub zu Aktorhub einstellen läßt. Insbesondere kann dadurch auch für eine Druckhülse mit sehr geringem Durchmesser ein geeignetes Übersetzungsverhältnis erreicht werden.It is advantageous, when the fuel injection valve is an inwardly opening fuel injection valve, that 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. In addition, 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. Furthermore, it is advantageous that the pressure sleeve is widened on the side of the lever segments. Thus, at a given distance of the inner support point to the valve axis of the distance of the central support point to the valve axis set and thus choose a suitable ratio of the translation device, which can adjust the ratio of valve needle to Aktorhub. In particular, a suitable transmission ratio can thereby also be achieved for a pressure sleeve with a very small diameter.

Vorteilhaft ist es, daß eine Rückstellfeder auf die Hebelsegmente einwirkt und daß eine Druckfeder über die Ventilnadel auf die Hebelsegmente in Gegenrichtung zur Druckfeder einwirkt, wobei die Druckfeder ein größeres Drehmoment auf die Hebelsegmente ausübt als die Rückstellfeder. Bei einer Betätigung des Ventils kann dadurch die Öffnungskraft auf die Ventilnadel, die durch die Kraft der Druckfeder auf die Hebelsegmente gegeben ist, vorgegeben werden, wodurch sich unter Berücksichtigung der Aktorbewegung und der Ventilnadelmasse über die Öffnungsbewegung die Öffnungsgeschwindigkeit einstellen läßt. Außerdem läßt sich die auf die Ventilnadel einwirkende Rückstellkraft durch die Kraft der Rückstellfeder vorgeben. Unter Berücksichtigung der Aktorbewegung des Aktors und der Ventilnadelmasse läßt sich dadurch die durch die Schließbewegung der Ventilnadel, gegebene Schließgeschwindigkeit einstellen. Bei geschlossenem Brennstoffeinspritzventil ist die Druckfeder über die Hebelsegmente durch die Druckhülse blockiert, wodurch das Drehmoment der Rückstellfeder ausreicht, die Ventilnadel gegen den Druck in der Brennstoffkammer auf den Ventilsitz zu drücken, so daß sich ein Dichtsitz ergibt. Bei dieser Anordnung wird das Öffnen und Schließen des Brennstoffeinspritzventils nur indirekt über die Betätigung des Aktors gesteuert. Die zum Öffnen und Schließen des Ventils auf die Ventilnadel einwirkenden Kräfte sind dabei durch die Druckfeder und die Rückstellfeder gegeben. Durch die Kombination mit vernachlässigbar schweren Hebelsegmenten und einer geringen zu betätigenden Masse der Ventilnadel lassen sich besonders hohe Schaltfrequenzen realisieren.It is advantageous that 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. Upon actuation of the valve can thereby 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. In addition, 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. When the fuel injection valve is closed, the compression spring is blocked by the lever sleeve segments through the pressure sleeve, whereby the torque of the return spring is sufficient to push the valve needle against the pressure in the fuel chamber on the valve seat, so that there is a sealing seat. In this arrangement, the opening and closing of the fuel injection valve is controlled only indirectly via the actuation of the actuator. The forces acting on the valve needle for opening and closing the valve are given by the pressure spring and the return spring. The combination with negligibly heavy lever segments and a low mass of the valve needle to be actuated make it possible to achieve particularly high switching frequencies.

Es ist vorteilhaft, wenn das Brennstoffeinspritzventil ein nach außen öffnendes Brennstoffeinspritzventil ist, daß der Aktor bei der Druckhülse in einem mittleren Auflagestelle auf die Hebelsegmente einwirkt, daß die Hebelsegmente in einer äußeren Auflagestelle an dem Ventilgehäuse anliegen, daß die Hebelsegmente über eine innere Auflagestelle auf die Ventilnadel einwirken und daß eine Druckfeder auf die Hebelsegmente einwirkt, wobei das Drehmoment, mit dem die Druckfeder auf die Hebelsegmente einwirkt, entgegengesetzt zu dem Drehmoment gerichtet ist und der Aktor auf die Hebelsegmente einwirkt. Die Hubübersetzung eines Aktorhubs des Aktors in einen Ventilnadelhub der Ventilnadel läßt sich dadurch günstig wählen. Beim Schließen des Ventils nach erfolgter Betätigung des Aktors ergibt sich der vorteil, daß die Ventilnadel, die durch die Rückstellkraft der Rückstellfeder gegen die Hebelsegmente gedrückt wird, an der inneren Auflagestelle keine radiale Kraft erfährt und somit in radialer Richtung verspannungsfrei gegen den Ventilsitz unter eventueller Zuhilfenahme von geeigneten Nadelführungen gepreßt wird.It is advantageous if 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. When closing the valve after the actuation of the actuator there is the advantage that the 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.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen auszugsweisen axialen Schnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils mit einer Übersetzungseinrichtung, wobei das Brennstoffeinspritzventil als ein innenöffnendes Brennstoffeinspritzventil ausgeführt ist;
Fig. 2
einen auszugsweisen axialen Schnitt durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils, wobei das Brennstoffeinspritzventil als ein außenöffnendes Brennstoffeinspritzventil ausgeführt ist;
Fig. 3
eine Vorderansicht einer Hebelplatte, die bei den in den Fig. 1 und 2 dargestellten Ausführungsbeispielen verwendet wird, in einer vergrößerten Darstellung;
Fig. 4
einen Schnitt durch ein Prägungen aufweisendes Hebelsegment, das ein Segment der Hebelplatte ist, entlang der Linie IV - IV in Fig. 3;
Fig. 5
ein weiteres Ausführungsbeispiel der Hebelplatte, wobei die Hebelsegmente durch Aussparungen voneinander getrennt sind;
Fig. 6
ein weiteres Ausführungsbeispiel der Hebelplatte, wobei neben den starren Hebelsegmenten auch elastische, biegsame Federsegmente vorgesehen sind und
Fig. 7
ein weiteres Ausführungsbeispiel der Hebelplatte, wobei die Hebelsegmente auf einer Haltescheibe befestigt sind.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a partial axial section through a first embodiment of a fuel injection valve according to the invention with a translation device, wherein the fuel injection valve is designed as an inwardly opening fuel injection valve;
Fig. 2
a partial axial section through a second embodiment of a fuel injection valve according to the invention, wherein the fuel injection valve is designed as an outwardly opening fuel injection valve;
Fig. 3
a front view of a lever plate, which in the in Fig. 1 and 2 illustrated embodiments is used, in an enlarged view;
Fig. 4
a section through a stampings having lever segment, which is a segment of the lever plate, along the line IV - IV in Fig. 3 ;
Fig. 5
a further embodiment of the lever plate, wherein the lever segments are separated by recesses;
Fig. 6
a further embodiment of the lever plate, wherein in addition to the rigid lever segments and elastic, flexible spring segments are provided and
Fig. 7
a further embodiment of the lever plate, wherein the lever segments are mounted on a retaining disc.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Fig. 1 zeigt in einer auszugsweise axialen Schnittdarstellung ein erfindungsgemäßes Brennstoffeinspritzventil 1. Das Brennstoffeinspritzventil 1 ist als ein nach innen öffnendes Brennstoffeinspritzventil 1 ausgeführt. Das Brennstoffeinspritzventil 1 dient insbesondere zum direkten Einspritzen von Brennstoff, insbesondere von Benzin, in einen Brennraum einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine als sog. Benzindirekteinspritzventil. Das erfindungsgemäße Brennstoffeinspritzventil 1 eignet sich jedoch auch für andere Anwendungsfälle. 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. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

Das Brennstoffeinspritzventil 1 weist einen mittels einer Ventilnadel 2 betätigbaren Ventilschließkörper 3 auf. Der Ventilschließkörper 3 ist im Ausführungsbeispiel mit der Ventilnadel 2 einteilig ausgebildet. Der Ventilschließkörper 3 ist kegelstumpfförmig ausgeführt, wobei der Kegelstumpf in Abspritzrichtung zuläuft. Der Ventilschließkörper 3 wirkt mit einer an einem Ventilsitzkörper 4 ausgebildeten Ventilsitzfläche 5 zu einem Dichtsitz zusammen. Die Ventilnadel 2 wird bei ihrer Bewegung entlang der Ventilachse 6 durch Ventilnadelführungen 7, 8 geführt. Der Ventilsitzkörper 4 und die Ventilnadelführungen 7, 8 befinden sich in einem vorderen abspritzseitigen Teil eines Ventilgehäuses 9. Die Zuführung des Brennstoffs erfolgt über einen Brennstoffanschluß 10, der sich im hinteren Teil des Ventilgehäuses 11 befindet.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 Abspritzrichtung. 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.

Zur Betätigung des Brennstoffeinspritzventils 1 dient ein im mittleren Teil des Ventilgehäuses 12 vorgesehener Aktor 13, der piezoelektrisch oder magnetostriktiv ausgeführt sein kann. Die Betätigung des Aktors 13 erfolgt über ein elektrisches Steuersignal. Die hierfür erforderliche elektrische Zuleitung ist über eine Anschlußbuchse 14 im hinteren Teil des Ventilgehäuses 11 an das Brennstoffeinspritzventil 1 anzuschließen. Bei Betätigung des Aktors 13 dehnt sich dieser aus und wirkt entgegen der Kraft einer Vorspannfeder 15 im hinteren Teil des Ventilgehäuses 11 auf eine rohrförmige Druckhülse 16 im mittleren Teil des Ventilgehäuses 12 ein. Bei Betätigung des Aktors 13 verschiebt sich daher die rohrförmige Druckhülse 16 in Richtung des Brennstoffanschlußes 10 in den hinteren Teil des Ventilgehäuses 11.To actuate the fuel injection valve 1 is provided in the middle part of the valve housing 12 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. Upon actuation of the actuator 13, 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. Upon actuation of the actuator 13, therefore, the tubular pressure sleeve 16 moves in the direction of the fuel port 10 in the rear part of the valve housing eleventh

Die Brennstoffzuführung in eine Brennstoffkammer 17 besteht darin, daß eine innere Brennstoffdurchführung 18 in der rohrförmigen Druckhülse 16, eine innere Brennstoffdurchführung 19 in einem rohrförmigen Auflageelement 20, geeignete Durchführungen in einer Hebelplatte 21 und/oder in dem der Hebelplatte 21 zugewandten Teil der rohrförmigen Druckhülse 16 und der Ventilnadelführung 7, 8 vorgesehen sind, durch die der Brennstoff in die Brennstoffkammer 17 eingeleitet wird.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.

Im geschlossenen Zustand des Brennstoffeinspritzventils 1 wirkt eine Rückstellfeder 22, die sich im Inneren der rohrförmigen Druckhülse 16 befindet, auf die Ventilnadel 2 ein, so daß der kegelstumpfförmige Ventilschließkörper 3 der Ventilnadel 2 gegen die Ventilsitzfläche 5 des Ventilsitzes 4 gepreßt wird, wodurch kein Brennstoff aus der Brennstoffkammer 17 in den Brennraum einer Brennkraftmaschine entweichen kann. Dabei wirkt die Vorspannfeder 15 im hinteren Teil des Ventilgehäuses 11 über die rohrförmige Druckhülse 16 im mittleren Teil des Ventilgehäuses 12 an einer mittleren Auflagestelle 23 so auf die Hebelplatte 21 ein, daß eine auf die Hebelplatte 21 einwirkende Druckfeder 24, ohne Betätigung des Aktors 13, durch die rohrförmige Druckhülse 16 gehemmt ist. Dabei greift die Druckfeder 24 über die Hebelplatte 21 an der Ventilnadel 2 an einer inneren Auflagestelle 25 an. Die Rückstellfeder 22 liegt an der der Ventilnadel 2 gegenüberliegenden Seite an dem fest in der Druckhülse 16 angeordneten rohrförmigen Auflageelement 20 an.In the closed state of the fuel injection valve 1, 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. In this case, 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. In this case, 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.

Um den Brennstoff in den Brennraum der Brennkraftmaschine einzuspritzen, wird das Brennstoffventil 1 über den Aktor 13 betätigt. Wie oben beschrieben, bewegt sich die rohrförmige Druckhülse 16 bei Betätigung des Aktors 13 in Richtung des hinteren Teiles des Ventilgehäuses 11, wodurch die rohrförmige Druckhülse 16 nicht mehr über die Hebelplatte 21 entgegen der Druckfeder 24 wirkt. Da die Druckfeder 24 mit einem größeren Drehmoment auf die Hebelplatte 21 einwirkt als die Rückstellfeder 22, werden Hebelsegmente 26, 27 der Hebelplatte 21 verkippt, wobei sich die Hebelsegmente 26, 27 an der äußeren Auflagestelle 28 am vorderen abspritzseitigen Teil des Ventilgehäuses 9 abstützen. Bei der Verkippung der Hebelsegmente 26, 27 der Hebelplatte 21 verschiebt sich die Ventilnadel 2, die durch die Ventilnadelführungen 7, 8 geführt wird, entlang der Ventilachse 6 in Richtung des Brennstoffanschlußes 10, wodurch der kegelstumpfförmige Ventilschließkörper 3 von der Ventilsitzfläche 5 des Ventilsitzes 4 abhebt und den Dichtsitz freigibt. Durch den entstehenden Spalt zwischen dem Ventilschließkörper 3 und Ventilsitz 4 kommt es zum Austritt von Brennstoff aus der Brennstoffkammer 17 des Brennstoffeinspritzventils 1 in die Brennkammer der Brennkraftmaschine.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. 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.

Nach Abschalten des Aktors 13 wirkt die Vorspannfeder 15 über die rohrförmige Druckhülse 16 an der mittleren Auflagestelle 23 auf die Hebelsegmente 26, 27 der Hebelplatte 21 ein, wobei das durch die Vorspannfeder 15 hervorgerufene, auf die Hebelplatte 21 einwirkende Drehmoment größer als das durch die Druckfeder 24 hervorgerufene Drehmoment ist, so daß die Hebelsegmente 26, 27 der Hebelplatte 21 in ihre Ausgangsstellung zurückgestellt werden, wobei sich die Hebelsegmente 26, 27 an der äußeren Auflagestelle 28 am vorderen abspritzseitigen Teil des Ventilgehäuses 9 abstützen. Dadurch wirkt die Druckfeder 24 nicht mehr über die Hebelplatte 21 an der inneren Auflagestelle 25 auf die Ventilnadel 2 ein. Durch die Rückstellfeder 22, die sich an ihrem dem hinteren Teil des Ventilgehäuses 11 zugewandten Ende an dem rohrförmigen Auflageelement 20 im Inneren der rohrförmigen Druckhülse 16 abstützt, wird die Ventilnadel 2 in ihre Schließstellung, in der der Ventilschließkörper 3 mit dem Ventilsitzkörper 4 an der Ventilsitzfläche 5 einen Dichtsitz bildet, zurückgeschoben und somit der Austritt von Brennstoff aus der Brennstoffkammer 17 in die Brennkammer der Brennkraftmaschine unterbrochen. Durch Variation der axialen Lage des rohrförmigen Auflageelements 20 kann die Rückstellfeder 22 mit einer einstellbaren Vorspannung beaufschlagt werden, so daß sich die durch die Rückstellfeder 22 vorgegebene Anpreßkraft zum Anpressen des Ventilschließkörpers 3 der Ventilnadel 2 gegen die Ventilsitzfläche 5 des Ventilsitzes 4 einstellen läßt.After switching off the actuator 13, 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. As a result, the compression spring 24 no longer acts on the valve needle 2 via the lever plate 21 at the inner support point 25. By the return spring 22, which is supported at its the rear part of the valve housing 11 facing the end of the tubular support member 20 in the interior of the tubular pressure sleeve 16, 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. By varying the axial position of the tubular support member 20, 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 zeigt in einer auszugsweisen axialen Schnittdarstellung ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1. Bei diesem Ausführungsbeispiel handelt es sich im Unterschied zu dem in Fig. 1 dargestellten Ausführungsbeispiel um ein nach außen öffnendes Brennstoffeinspritzventil 1. Bereits beschriebene Elemente sind mit übereinstimmenden Bezugszeichen versehen. Auf eine wiederholende Beschreibung wird insoweit verzichtet. Fig. 2 shows in a partial axial sectional view of a second embodiment of a fuel injection valve according to the invention 1. In 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.

Bei diesem Ausführungsbeispiel erfolgt der Aktorhub des Aktors 13 bei Betätigung des Brennstoffeinspritzventils 1 in Richtung des vorderen Teils des Ventilgehäuses 9, wodurch der Aktor 13 über die rohrförmige Druckhülse 16 an der mittleren Auflagestelle 23 direkt auf die Hebelplatte 21 einwirkt. Die Vorspannfeder 15 aus Fig. 1 kann daher entfallen. Da zum Schließen des Brennstoffeinspritzventils 1 der kegelstumpfförmige, sich in Abspritzrichtung erweiternde Ventilschließkörper 3 in Richtung des hinteren Teils des Ventilgehäuses 11 an der Ventilsitzfläche 5 gegen den Ventilsitzkörper 4 gepreßt werden muß, wirkt die Rückstellfeder 22 mit einer Kraft entlang der Ventilachse 6 in Richtung des hinteren Teils des Ventilgehäuses 11 auf die Ventilnadel 2 ein. Dabei kann sich die Rückstellfeder 22 direkt an der Ventilnadelführung 8 abstützen oder auch ein zusätzliches Auflageelement vorgesehen werden. Die Druckfeder 24 wirkt in der gleichen Weise wie in Fig. 1 an der mittleren Auflagestelle 23 auf die Hebelsegmente 26, 27 der Hebelplatte 21 ein.In this embodiment, 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.

Zur Betätigung des Brennstoffeinspritzventils 1 wird der Aktor 13 betätigt, wobei sich dieser ausdehnt und über die rohrförmige Druckhülse 16 an der mittleren Auflagestelle 23 auf die Hebelplatte 21 einwirkt und, da das durch die Aktorkraft des Aktors 13 erzeugte und auf die Hebelsegmente 26, 27 einwirkende Drehmoment größer als das durch die Kraft der Rückstellfeder 22 auf die Hebelsegmente 26, 27 der Hebelplatte 21 einwirkende Drehmoment ist, entgegen der Rückstellkraft der Rückstellfeder 22 bewegt, wodurch die Hebelsegmente 26, 27 an der inneren Auflagestelle 25 auf die Ventilnadel 2 einwirken und diese entlang der Ventilachse 6 in Richtung auf den Ventilsitzkörper 4 bewegen, wodurch sich der kegelstumpfförmige Ventilschließkörper 3 an der Ventilsitzfläche 5 vom Ventilsitzkörper 4 abhebt und den Dichtsitz freigibt. Durch den entstandenen Spalt zwischen Ventilschließkörper 3 und Ventilsitz 4 kommt es zum Austritt von Brennstoff aus der Brennstoffkammer 17 des Brennstoffeinspritzventils 1 in die Brennkammer der Brennkraftmaschine.For actuating the fuel injection valve 1, 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.

Nach Abschalten des Aktors 13 wirkt die Druckfeder 24 auf die Hebelsegmente 26, 27 der Hebelplatte 21 ein und stellt diese in ihre Ausgangsstellung zurück. Dadurch wirkt der Aktor 13 über die rohrförmige Druckhülse 16 und über die Hebelplatte 21 nicht mehr an der inneren Auflagestelle 25 auf die Ventilnadel 2 ein, wodurch die Rückstellfeder 22 die Ventilnadel 2 entlang der Ventilachse 6 in Richtung des hinteren Teils des Ventilgehäuses 11 zurückstellt und somit der kegelstumpfförmige Ventilschließkörper 3 an der Ventilsitzfläche 5 gegen den Ventilsitzkörper 4 gepreßt wird. Entsprechend der Ausführung zu Fig. 1 kann die Anpreßkraft zum Anpressen des Ventilschließkörpers 3 gegen die Ventilsitzfläche 5 des Ventilsitzkörpers 4 durch die axiale Lage der Ventilnadelführung 8 eingestellt werden.After switching off the actuator 13, the compression spring 24 acts on the lever segments 26, 27 of the lever plate 21 and returns them to their original position. As a result, 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. According to the execution too Fig. 1 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 zeigt die Vorderansicht eines Ausführungsbeispiels der erfindungsgemäßen Hebelplatte 21. Die Hebelplatte 21 weist eine innere Aussparung 29, Hebelsegmente 30, 31, 32, die durch äußere Aussparungen 33, 34, 35 voneinander getrennt sind und Verbindungsstege 36, 37, 38, von denen jeder je zwei der Hebelsegmente 30, 31, 32 zusammenhält, auf. Beim Verkippen der beispielsweise jeweils um 120° versetzt voneinander angeordneten Hebelsegmente 30, 31, 32 werden Spannungen in den Verbindungsstegen 36, 37, 38 erzeugt. Die Hebelsegmente 30, 31, 32 besitzen z. B. die Gestalt von Kreisausschnitten bzw.- sektoren. Durch die innere Aussparung 29 werden die Spannungen in den Verbindungsstegen 36, 37, 38 reduziert. Die innere Aussparung 29 und die äußeren Aussparungen 33, 34, 35 können auch als Brennstoffdurchführung dienen. Die Hebelsegmente 30, 31, 32 sind starr ausgeführt, was sich durch die Materialstärke der Hebelsegmente 30, 31, 32 und/oder radial verlaufende Prägungen 39, 40, 41, die in Fig. 3 nur an einem Hebelsegment 32 beispielhaft angedeutet sind, erreichen läßt. Die Form der inneren Aussparung 29, der äußeren Aussparungen 33, 34, 35 ist nicht auf die dargestellte Form und Anzahl, die Hebelsegmente 30, 31, 32 sind nicht auf die dargestellte Anzahl und die Prägungen 39, 40, 41 sind ebenfalls nicht auf die dargestellte Form und Anzahl beschränkt. Außerdem müssen nicht notwendigerweise alle Hebelsegmente 30, 31, 32 einer Hebelplatte 21 die gleiche Art der Versteifung aufweisen. 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. When tilting the lever segments 30, 31, 32, which are each offset by 120 ° from one another, stresses are generated in the connecting webs 36, 37, 38. The lever segments 30, 31, 32 have z. B. the shape of Kreisausschnitten or sectors. By the inner recess 29, the voltages in the connecting webs 36, 37, 38 are reduced. 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. In addition, not necessarily all lever segments 30, 31, 32 of a lever plate 21 have the same type of stiffening.

Zur deutlicheren Darstellung sind in den folgenden Figuren die Hebelsegmente 30, 31, 32 durch Prägungen 39, 40, 41 kenntlich gemacht. Zur Vereinfachung der Darstellung und Beschreibung sind, wie auch in der Fig. 3, nur jeweils drei Hebelsegmente 30, 31, 32 dargestellt.For a clearer illustration, the 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.

In Fig. 4 ist der Schnitt, der durch das Hebelsegment 32 der Hebelplatte 21, in Fig. 3 gelegt ist und durch die mit IV - IV bezeichnete Schnittlinie gekennzeichnet ist, dargestellt. Die Prägungen 39, 40, 41 können sowohl gleichseitig wie die Prägung 39 und die Prägung 41, als auch gegenseitig wie die Prägung 39 und 40 angebracht sein. Außerdem können die Prägungen gleich stark, wie Prägung 39 und Prägung 40, als auch unterschiedlich stark, so wie Prägung 40 und 41 ausgebildet sein.In 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. In addition, 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 zeigt die Vorderansicht eines alternativen Ausführungsbeispiels der erfindungsgemäßen Hebelplatte 21. Bereits beschriebene Elemente sind mit übereinstimmenden Bezugszeichen versehen. Auf eine wiederholende Beschreibung wird insoweit verzichtet. Die innere Aussparung 29 und die äußeren Aussparungen 33, 34, 35 sind in diesem Ausführungsbeispiel nicht voneinander getrennt. Die Hebelsegmente 30, 31, 32 der Hebelplatte 21 sind durch Verbindungsstege 36, 37, 38, die am äußeren Rand 41a der Hebelplatte 21 umfangsmäßig verlaufen, miteinander verbunden. Im Gegensatz zu den Hebelsegmenten 30, 31, 32 aus Fig. 3 werden die Hebelsegmente 30, 31, 32 daher nach innen verkippt. 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 zeigt die Vorderansicht eines weiteren Ausführungsbeispiels der erfindungsgemäßen Hebelplatte 21. Bereits beschriebene Elemente sind mit übereinstimmenden Bezugszeichen versehen. Die Hebelplatte 21 weist eine innere Aussparung 29 und äußere schlitzartige, sich radial sternförmig erstreckende Aussparungen 33, 34, 35, 42, 43, 44, die miteinander verbunden sind, auf. Die dadurch entstehenden Segmente 30, 31, 32, 45, 46, 47 der Hebelplatte 21 untergliedern sich in zwei verschiedene Arten von Segmenten 30, 31, 32, 45, 46, 47, von denen die eine Art von Segmenten als starre Hebelsegmente 30, 31, 32 und die andere Art von Segmenten als elastische, biegsame Federsegmente 45, 46, 47 ausgebildet ist. Die Segmente werden dabei von den Verbindungsstegen 36, 37, 38, 48, 49, 50, die sich am äußeren Rand 41a der Hebelplatte 21 befinden, zusammengehalten. 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 zeigt die Vorderansicht eines weiteren alternativen Ausführungsbeispiels der erfindungsgemäßen Hebelplatte 21. Bereits beschriebene Elemente sind mit übereinstimmenden Bezugszeichen versehen. Die Hebelsegmente 30, 31, 32 der Hebelplatte 21 werden in diesem Ausführungsbeispiel nicht durch Verbindungsstege zusammengehalten, sondern sind auf einer dünnen, elastischen und biegsamen Haltescheibe 51 befestigt. In der dünnen, elastischen und biegsamen Haltescheibe 51 kann eine innere Aussparung 29 vorgesehen werden, die ein besseres Durchbiegen der dünnen, elastischen und biegsamen Haltescheibe 51 oder einen Brennstoffdurchfluß durch diese ermöglicht. Dabei ist die dünne, elastische und biegsame Haltescheibe 51 aus einem brennstoffbeständigen Material, wie z. B. Metallblech oder einem Kunststoffmaterial wie Polyamid gefertigt. Fig. 7 shows the front view of another alternative embodiment of the invention lever plate 21. Already described elements are provided with matching reference numerals. 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. In the thin, elastic and flexible retaining disc 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. In this case, the thin, elastic and flexible retaining plate 51 is made of a fuel-resistant material such. B. metal sheet or a plastic material such as polyamide.

Claims (14)

  1. Fuel injection valve (1), in particular injection valve for fuel injection systems of internal combustion engines, having a piezoelectric or magnetostrictive actuator (13), a valve closing body (3) which can be actuated by the actuator (13) by means of a valve needle (2) and which interacts with a valve seat face (5) to form a sealing seat, and a booster device, which is arranged between the actuator (13) and the valve needle (2), for boosting an actuator stroke of the actuator (13) into a larger valve needle stroke of the valve needle (2), with the booster device comprising at least one lever plate (21),
    characterized
    in that the lever plate (21) has at least one radially running rigid lever segment (26, 27, 30-32), and the at least one lever segment (26, 27, 30-32) has embossings (39-41) which run from the central point of the lever plate (21) to the edge (41a) of the lever plate (21).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that a plurality of lever segments (26, 27, 30-32) are provided, which lever segments (26, 27, 30-32) are separated from one another by cutouts (29, 33-35, 42-44).
  3. Fuel injection valve according to Claim 1 or 2,
    characterized
    in that the lever plate (21) is composed of two different types of segments, one of which types of segments is embodied as rigid lever segments (30-32) and the other of which types of segments is embodied as elastic, flexible spring segments (45-47).
  4. Fuel injection valve according to one of Claims 1 to 3,
    characterized
    in that the lever segments (30-32) are fastened to a thin, elastic and flexible holding disc (51).
  5. Fuel injection valve according to Claim 4,
    characterized
    in that the holding disc (51) is composed of a metal sheet.
  6. Fuel injection valve according to Claim 4,
    characterized
    in that the holding disc (51) is composed of a plastic material, in particular polyamide.
  7. Fuel injection valve according to one of Claims 1 to 6,
    characterized
    in that the fuel injection valve (1) is an inwardly-opening fuel injection valve (1),
    in that the actuator (13) acts by means of a tubular pressure sleeve (16) on a central contact point (23) on the lever segments (26, 27),
    in that the lever segments (26, 27) bear against an outer contact point (28) on a valve housing (9), and
    in that the lever segments (26, 27) engage on an inner contact point (25) on the valve needle (2).
  8. Fuel injection valve according to Claim 7,
    characterized
    in that the pressure sleeve (16) is surrounded at least in sections by the actuator (13), with the actuator (13) having a cutout for this purpose.
  9. Fuel injection valve according to Claim 7 or 8,
    characterized
    in that the pressure sleeve (16) is widened on the side of the lever segments (26, 27).
  10. Fuel injection valve according to one of Claims 7 to 9,
    characterized
    in that the mean spacing of the outer contact point (28) to the valve axis (6) is greater than the mean spacing of the central contact point (23) to the valve axis (6), and in that the mean spacing of the central contact point (23) to the valve axis (6) is greater than the mean spacing of the inner contact point (25) to the valve axis (6).
  11. Fuel injection valve according to one of Claims 7 to 10,
    characterized
    in that a pressure spring (24) acts on the lever segments (26, 27),
    in that a restoring spring (22) acts via the valve needle (2) on the lever segments (26, 27) in the opposite direction to the pressure spring (24), with the pressure spring (24) exerting a greater torque on the lever segments (26, 27) than the restoring spring (22).
  12. Fuel injection valve according to one of Claims 1 to 6,
    characterized
    in that the fuel injection valve (1) is an outwardly-opening fuel injection valve (1),
    in that the actuator (13) acts by means of a pressure sleeve (16) on a central contact point (23) on the lever segments (26, 27),
    in that the lever segments (26, 27) bear against an outer contact point (28) on a valve housing (12),
    in that the lever segments (26, 27) act via an inner contact point (25) on the valve needle (2),
    in that a pressure spring (24) acts on the lever segments (26, 27), wherein the torque with which the pressure spring (24) acts on the lever segments (26, 27) is aligned counter to the torque with which the actuator (13) acts on the lever segments (26, 27).
  13. Fuel injection valve according to Claim 12,
    characterized
    in that the mean spacing of the outer contact point (28) to the valve axis (6) is greater than the mean spacing of the central contact point (23) to the valve axis (6), and in that the mean spacing of the central contact point (23) to the valve axis (6) is greater than the mean spacing of the inner contact point (25) to the valve axis (6).
  14. Fuel injection valve according to Claim 12 or 13,
    characterized
    in that a restoring spring (22) acts on the valve needle (2), wherein the force with which the restoring spring (22) acts on the valve needle (2) is aligned counter to the force with which the lever segments (26, 27) act on the valve needle (2).
EP99957920A 1999-03-12 1999-10-20 Fuel injection valve Expired - Lifetime EP1078157B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19911048A DE19911048A1 (en) 1999-03-12 1999-03-12 Fuel injector
DE19911048 1999-03-12
PCT/DE1999/003356 WO2000055492A1 (en) 1999-03-12 1999-10-20 Fuel injection valve

Publications (2)

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

Family

ID=7900734

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99957920A Expired - Lifetime EP1078157B1 (en) 1999-03-12 1999-10-20 Fuel injection valve

Country Status (6)

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

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002031344A1 (en) * 2000-10-11 2002-04-18 Siemens Vdo Automotive Corporation Dual-spring compensator assembly for a fuel injector and method
US6749127B2 (en) 2002-02-11 2004-06-15 Siemens Vdo Automotive Corporation Method of filling fluid in a thermal compensator
DE20220800U1 (en) * 2002-10-24 2004-04-08 Vermes Technik Gmbh & Co. Kg Positioning system with piezoactuator has links between piezoactuator and transmission lever provided as rolling butt contact forming line contact and transmission lever is preloaded by spring
DE10307003B3 (en) * 2003-02-19 2004-05-13 Siemens Ag IC engine fuel injection valve has actuator controlling displacement of valve needle spring biased into closure position for fuel injection bores
DE10326707B3 (en) * 2003-06-11 2005-01-27 Westport Germany Gmbh Valve device and method for injecting gaseous fuel
US8074625B2 (en) 2008-01-07 2011-12-13 Mcalister Technologies, Llc Fuel injector actuator assemblies and associated methods of use and manufacture
US20140131466A1 (en) 2012-11-12 2014-05-15 Advanced Green Innovations, LLC Hydraulic displacement amplifiers for fuel injectors
US9309846B2 (en) 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
JP6138502B2 (en) * 2013-02-04 2017-05-31 日立オートモティブシステムズ株式会社 Fuel injection valve
JP6731492B2 (en) * 2016-10-03 2020-07-29 日立オートモティブシステムズ株式会社 Fuel injection valve
KR20220005584A (en) * 2019-05-12 2022-01-13 노드슨 코포레이션 Distribution system with mechanical amplifier

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1751543A1 (en) * 1968-06-15 1970-08-27 Kloeckner Humboldt Deutz Ag Electrically controllable injection valve
US4022166A (en) 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
JPS601369A (en) * 1983-06-16 1985-01-07 Nippon Soken Inc Fuel injection valve
US4695034A (en) * 1984-11-27 1987-09-22 Stec Inc. Fluid control device
JPS62157274A (en) * 1985-12-28 1987-07-13 Aisan Ind Co Ltd Fuel injection valve
JPH0364662A (en) 1989-08-03 1991-03-20 Nissan Motor Co Ltd Fuel injection valve
JPH02112664A (en) 1989-09-20 1990-04-25 Hitachi Ltd Piezoelectric type fuel injection valve
US5636615A (en) * 1995-02-21 1997-06-10 Diesel Technology Company Fuel pumping and injection systems
JP3740733B2 (en) * 1996-02-13 2006-02-01 いすゞ自動車株式会社 Fuel injection device for internal combustion engine
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
JPH11132127A (en) * 1996-11-13 1999-05-18 Denso Corp Fuel injection valve and assembling method thereof
DE19706469A1 (en) * 1997-02-19 1998-08-27 Daimler Benz Ag Accumulator injection system for a multi-cylinder internal combustion engine with solenoid-controlled fuel injection valves

Also Published As

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

Similar Documents

Publication Publication Date Title
EP1831537B1 (en) Injector for a fuel-injection system in an internal combustion engine
EP1115970A1 (en) Fuel injection valve
EP1772618A1 (en) Common rail injector
WO1998040623A1 (en) Valve for controlling fluids
DE10145620A1 (en) Valve for controlling liquids
EP1078157B1 (en) Fuel injection valve
EP1552135B1 (en) Fuel injection device for an internal combustion engine
EP1929149B1 (en) Injection nozzle
WO1999018349A1 (en) Directly controlled injection valve, especially a fuel injection valve
WO2007000371A1 (en) Injector with a pressure intensifier that can be switched on
WO1999015779A1 (en) Injection valve
EP1563182A1 (en) Injector with a directly-actuated compound nozzle needle for fuel injection in an internal combustion engine
EP2440770B1 (en) Injection valve with transmission unit
EP1552136A1 (en) Fuel injection device for an internal combustion engine
WO2012034748A1 (en) Fuel injection valve
WO2001038712A2 (en) Fuel injection valve for internal combustion engines
EP1319127B1 (en) Valve configuration for control valves
DE10353045A1 (en) Fuel injection valve
DE19958705A1 (en) Valve with improved stop geometry
EP2458194B1 (en) Fuel injector valve for combustion engines
EP1256709B1 (en) Solenoid valve for controlling an injection valve of an internal combustion engine
EP1658427A1 (en) Fuel injection valve for internal combustion engines
EP1961953A1 (en) Multiway valve
DE3608494A1 (en) ELECTRICALLY CONTROLLABLE ACTUATOR
WO2001096732A1 (en) Valve for regulating fluids

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

17P Request for examination filed

Effective date: 20010321

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 59914675

Country of ref document: DE

Date of ref document: 20080417

Kind code of ref document: P

ET Fr: translation filed
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

26N No opposition filed

Effective date: 20081208

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

Effective date: 20081020

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

Ref country code: GB

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

Effective date: 20081020

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

Ref country code: IT

Payment date: 20091023

Year of fee payment: 11

Ref country code: FR

Payment date: 20091110

Year of fee payment: 11

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

Ref country code: FR

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

Effective date: 20101102

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110630

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 NON-PAYMENT OF DUE FEES

Effective date: 20101020

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

Ref country code: DE

Payment date: 20111205

Year of fee payment: 13

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: 20130501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59914675

Country of ref document: DE

Effective date: 20130501