EP1456527B1 - Dispositif pour translater une deviation d'un actionneur, notamment pour une soupape d'injection - Google Patents

Dispositif pour translater une deviation d'un actionneur, notamment pour une soupape d'injection Download PDF

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Publication number
EP1456527B1
EP1456527B1 EP02804848A EP02804848A EP1456527B1 EP 1456527 B1 EP1456527 B1 EP 1456527B1 EP 02804848 A EP02804848 A EP 02804848A EP 02804848 A EP02804848 A EP 02804848A EP 1456527 B1 EP1456527 B1 EP 1456527B1
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EP
European Patent Office
Prior art keywords
piston
chamber
housing
ring
bellows
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Expired - Lifetime
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EP02804848A
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German (de)
English (en)
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EP1456527A1 (fr
Inventor
Willibald SCHÜRZ
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Siemens AG
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Siemens AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • 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
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • 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
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the invention relates to a device for translating a deflection of an actuator according to the preamble of patent claim 1.
  • Injectors such as e.g. Piezoelectric injection valves, use an actuator whose maximum deflection is relatively small in a control.
  • an injection needle or a servo valve for controlling an injection needle can be safely operated, a translation of the deflection of the actuator is required.
  • For the translation corresponding translation devices are used.
  • a hydraulic device for transmitting an actuator movement has a first piston element which is fixedly connected to an actuator.
  • a second piston element is provided, which is connected to an actuator.
  • a hydraulic chamber is provided between the first piston element and the second piston element.
  • a storage chamber is formed, which is connected to the hydraulic chamber via a throttle gap.
  • the storage chamber comprises a pressure-loaded storage chamber region, whose range limits are formed elastically. The range limits are represented by Faltenbalganowskiowski biased by a biasing spring relative to the housing of the injection valve. By biasing the storage chamber area, a pressure is provided in the storage chamber, which ensures a reliable filling of the hydraulic chamber.
  • a fuel injection valve which has a piezoelectric or magnetostrictive actuator having. Between the actuator and a valve needle, a lifting device is provided with two mutually movable reciprocating piston. The lifting device is hermetically sealed against a valve interior.
  • the first reciprocating piston is operatively connected to the actuator and has a hollow cylindrical shape which is open on one side and whose opening is arranged facing away from the actuator. In the cylinder opening of the second piston is guided.
  • the first reciprocating piston is again in a hollow cylindrical housing. Between an end surface of the housing and the first and the second piston, a transmission chamber is formed.
  • the second piston is in operative connection with an injection needle. Between the first and the second piston, a piston chamber is formed.
  • a second bellows circumferentially sealed With the housing and a piston rod of the second piston, a second bellows circumferentially sealed, so that a first pressure chamber is formed. Likewise, with the housing and the first piston, a first bellows circumferentially sealed, so that a second pressure chamber is formed.
  • the piston chamber is connected via openings with the first and with the second pressure chamber.
  • a tension spring is provided which biases the first and second pistons in opposite directions.
  • the injection valve described is formed relatively large due to the arrangement of the tension spring.
  • the piston chamber has a relatively large dead volume. The dead volume leads to a restriction of the dynamics of movement of the first and second pistons.
  • the valve has a piezoelectric unit for actuating a valve member axially displaceable in a bore of a valve body. This is formed with an adjoining the piezoelectric unit actuator piston and at least one adjacent to a valve closure member actuating piston. Between the piston, a working as a hydraulic ratio hydraulic chamber is arranged. The valve closure member cooperates with at least one valve seat and separates a low pressure area from a high pressure area. The hydraulic chamber is connected via a sealing gap with a valve system pressure chamber, which is sealed by a bellows-like membrane.
  • a fuel injection valve with an actuator which actuates a valve needle.
  • a hydraulic lifting device is provided with two mutually movable reciprocating piston.
  • the lifting device is a hermetically sealed against a valve interior assembly and has a housing with at least one flexible section in the axial direction.
  • WO 01/96733 A1 discloses a valve for controlling fluids with a piezoactuator and a hydraulic booster.
  • the hydraulic booster has a first piston, a second piston and a pressure chamber arranged between the two pistons.
  • a valve member is connected to the second piston and can be brought into contact with at least one first valve seat.
  • a separate adjusting element is present as a single component.
  • the object of the invention is to provide a device for translating a deflection of an actuator, which is simpler in construction.
  • the piston chamber is hydraulically connected to the compensation chamber via a bore.
  • the connection with the compensation chamber allows a quick outflow of the fluid from the piston chamber.
  • a movement of the first piston is made possible against the second piston without a larger counterforce.
  • Another advantage of the invention is that the dead volume in the piston chamber is reduced.
  • the advantage of the invention is achieved in that the clamping element is arranged for biasing the second piston outside of the piston chamber. Since the clamping element is arranged outside the piston chamber, the piston chamber can be made substantially smaller. Due to the smaller piston chamber an overall greater dynamics in the transmission of the movement of the first piston and the second piston is achieved.
  • a tension spring is provided as the clamping means, which is clamped between the housing and an abutment ring.
  • the abutment ring is attached to a piston rod of the second piston.
  • the arrangement of an abutment ring provides a simple and reliable contact surface for the tension spring.
  • the abutment ring in the form of a sleeve on which a support collar is formed.
  • the contact ring is connected via a lock washer with the piston rod.
  • a sleeve-shaped contact ring tilting of the tension spring is avoided.
  • the formation of a support collar a secure contact surface for the tension spring provided.
  • a lock washer also a safe and simple connection technology between the abutment ring and the piston rod is formed. For a reliable operation of the transmission device is achieved with a great long-term stability.
  • a second tension spring is provided, which is also disposed outside the piston chamber and is clamped between the housing and a piston rod of the first piston.
  • a bias of the first piston is achieved in the opposite direction to the bias of the second piston.
  • a starting position of the first piston is reliably set. As a result, it is not necessary, for example, to firmly connect the first piston to an actuator.
  • the second tension spring is arranged outside the housing and clamped between the first and the second bellows and the piston rod of the first piston. In this way, in addition to the bias of the piston rod, a pressure in the compensation chamber is additionally generated, which is limited by the first and the second bellows.
  • the piston chamber is hydraulically connected via a bore with a sealing region, which is arranged outside the housing and is preferably sealed by a bellows, which is circumferentially tightly connected to the housing and the second piston. In this way, a quick emptying of the piston chamber is made possible.
  • the piston chamber is additionally hydraulically connected via a bore with the compensation chamber. The connection with the compensation chamber allows a quick outflow of the fluid from the piston chamber. Thus, a movement of the first piston is made possible against the second piston without a larger counterforce.
  • a further advantageous embodiment is to close the housing via a ring, wherein a piston rod of the first piston is guided through the opening of the ring.
  • the ring preferably has a closable bore for filling the device with fluid.
  • the figure shows a schematic cross section through the device according to the invention for transmitting a deflection of an actuator to an actuator.
  • the transmission device according to the invention can be used with any type of actuator and actuator, but is particularly suitable for use in an injection valve, for example, for controlling a servo valve by a piezoelectric actuator.
  • first piston 1 which has a sleeve shape open on one side.
  • the sleeve-shaped part of the piston defines a piston chamber 3, in which a second piston 2 is guided.
  • the first and the second piston 1, 2 limit the piston chamber 3.
  • the first piston 1 is in turn guided in a cylindrical chamber 48 of a housing 4, which has an end face 5 at the end face to the first piston 1.
  • an opening 6 is introduced through which a piston rod 7 of the second piston 2 is guided.
  • the piston rod 7 has a smaller diameter than the second piston 2.
  • the piston rod 7 passes via an annular shoulder 8 in the widened diameter of the second piston 2. Between the end face 5, the shoulder 8 and an annular end face 9 of the first piston 1, a transmission chamber 10 is formed.
  • the transmission chamber 10 is hydraulically connected to the piston chamber 3 via a first sealing gap 11 which is formed between a side wall of the second piston 2 and an inner wall of the first piston 1.
  • the piston chamber 3 is bounded by an end face 47 of the first piston 1 and an end face 49 of the second piston 2.
  • the transmission chamber 10 is connected via a second sealing gap 12, which is formed between the outer wall of the first piston 1 and the inner wall of the housing 4, with a further sealing gap 13.
  • the further sealing gap 13 is formed between a closing ring 14 and a first portion 16 of a second piston rod 17.
  • the first piston 3 merges via a second shoulder 15 into the first section 16 of the second piston rod 17.
  • the first section 16 is substantially cylindrical in shape and merges via a third shoulder 21 into a second section 18 of the second piston rod 17.
  • the second section 18 of the second piston rod 17 has a substantially cylindrical shape and has a smaller diameter than the first section 16.
  • the end ring 14 has a circumferential annular groove 20 which is formed on the outer edge region of the end ring 14 and is associated with an annular end face 19 of the housing 4.
  • the tapered by the annular groove 20 inner diameter of the end ring 4 is adapted to the inner diameter of the cylindrical recess of the housing 4.
  • the closing ring 14 is connected to the housing 4, for example via a circumferential, sealed weld seam.
  • a first bellows 22 which is formed substantially sleeve-shaped, with a first end portion to the third paragraph 21 circumferentially tightly attached.
  • the first bellows 22 is preferably made of a metallic material and therefore preferably connected by a weld with the metallic second piston 2 circumferentially tight.
  • a second end of the first bellows 22 is connected to a connecting ring 23 circumferentially sealed. Through the opening of the connecting ring 23 of the second portion 18 of the second piston rod 17 is guided.
  • connection ring 23 has a fourth shoulder 24, over which the diameter of the connection ring 23 increases.
  • a second bellows 25 which is substantially cylindrical in shape, connected to the connecting ring 23 circumferentially sealed.
  • the second bellows 25 is circumferentially connected with its other edge region to an end face of the closing ring 14, which faces the connection ring 23. In this way, a compensation chamber 26 is formed between the first and second bellows 22, 25 and the connecting ring 23.
  • the compensation chamber 26 is hydraulically connected via the further sealing gap 13 and the second sealing gap 12 with the transmission chamber 10.
  • the hydraulic connection is designed in such a way that pressure differences between the transmission chamber 10 and the compensation chamber 26 are compensated only if the pressure differences last a minimum time.
  • the sealing gaps and selected geometries set the minimum time such that the time required to transmit a force from the first piston to the second piston must be exceeded before pressure equalization occurs. This ensures that the transmission of force from the first piston to the second piston 1, 2 is possible with virtually no losses, but nevertheless pressure differences that last for a long time are compensated. As a result, a complete filling of the transformer chamber 10 is made possible even with temperature fluctuations or wear. In this way, it is ensured that the transmitter chamber 10 is always completely filled with a transmission fluid, such as e.g. a pressure oil is filled.
  • the compensation chamber 26 is connected via a hydraulic connection with the piston chamber 3 in connection.
  • the hydraulic connection allows a rapid pressure equalization between the compensation chamber 26 and the piston chamber.
  • a securing groove 28 is introduced, in which a locking washer 29 is attached.
  • a second connection ring 30 On the locking washer 29 is a second connection ring 30 at.
  • a first spring 31 is clamped.
  • the first spring 31 exerts a biasing force on the first connection ring 23 and thus on the first and second bellows 22, 25.
  • the transmission fluid which is located in the compensation chamber 26, pressurized.
  • the closing ring 14 has a continuous second bore 32. Transmission fluid can be introduced from outside into the third sealing gap 13 and the volume hydraulically connected to the third sealing gap 13 via the second bore 32.
  • the second bore 32 is closed after filling all the volumes which are hydraulically connected to the sealing gap 13 via a closing element 33.
  • the closing element 33 is formed in the form of a sphere.
  • the housing 4 tapers in the outer diameter in the region of the first piston rod 7 via a shoulder to a ring member 34 with a smaller outer diameter.
  • the ring member 34 surrounds the first piston rod 7.
  • the first piston rod 7 extends up to a predetermined distance from the ring member 34.
  • the ring member 34 has an annular second end face 35, which is arranged substantially perpendicular to the longitudinal direction of the first piston rod 7.
  • a third end ring 36 is circumferentially tightly connected to the piston rod 7.
  • the third end ring 36 has an annular third end face 37 which faces the ring part 34.
  • a third bellows 38 is formed, which is formed substantially in the shape of a cylinder and with an end portion on the second end face of the ring member 34 and with the other end portion on the third end face 37 of the third end ring 36 circumferentially tightly secured.
  • a third sealing gap 50 which is formed between the housing 4 and the piston rod 7 and is in communication with the transmission chamber 10, reliably sealed.
  • a second securing groove 39 is formed, in which a second locking washer 40 is inserted.
  • a fourth connection ring 41 On an inner side of the second lock washer 40, which faces the housing 4, a fourth connection ring 41 abuts. Between the fourth connection ring 41 and the housing 4, a second spring 42 is clamped. The second spring 42 rests on a fourth end face 43 of the housing 4, which is formed by the shoulder of the housing 4, in which the housing 4 passes from a larger outer diameter to the annular part 34 with the smaller outer diameter.
  • the second piston 2 has a centered to the end face 49 of the second piston 2 introduced third bore 44, which extends from the end face 49 into the piston rod 7 in an edge region of the piston rod 7, which is arranged at the same height as the third bellows 38 is.
  • This is a hydraulically conductive connection between the piston chamber 3 and a compensation chamber 45, which is bounded by the piston rod 7 and the third bellows 38.
  • the piston chamber is designed in the form of a blind hole with a centrally tapered blind hole 46.
  • the blind hole 46 is hydraulically connected via the first bore 27 with the third sealing gap 13.
  • the translation device functions as follows:
  • the volumes formed in the transfer device are hydraulically connected to the transfer chamber 10 are completely filled with a liquid medium, which is preferably incompressible.
  • the first piston 1 is held by the first spring 31 in a starting position with bias.
  • the starting position is set, for example, by the abutment of the first piston with the second shoulder 15 on the connection ring 14.
  • the second piston 2 is in a rest position in an output length in which the second piston 2 is biased by the second spring 42.
  • the rest position is determined, for example, by the abutment of the second piston 2 with the shoulder 8 on the end face 5 of the housing 4.
  • the piston rods 7, 17 of the first and second pistons 1, 2 are biased in the rest position by the housing 4 in the opposite direction.
  • the volume formed between the pistons 1, 2 and the housing 4 and between the bellows 22, 25 and between the third bellows 38 and the piston rod 7 is filled with a transfer medium, in particular with a hydraulic fluid.
  • the filling takes place via the second bore 32, which is subsequently closed with the closing element 33.
  • the idle state of the first and second piston is preferably also determined by the fact that the first and the second piston rod 7, 17 abut against an actuator or on an actuator, so that a play-free operative connection between the actuator and the actuator is given.
  • the actuator may be formed, for example, as a piezoelectric actuator. If the actuator is then actuated, the actuator displaces the first piston 1 in the direction of the housing 4. Due to the hydraulic coupling of the second piston 2 via the transmission chamber 10 to the first piston 1, the second piston 2 and the piston rod 7 of the second piston 2 become also moved away from the housing against the direction of movement of the first piston 1. Is the piston rod 7 in operative connection with an injection needle, then the injection needle is lifted from a sealing seat, for example by the movement of the piston rod 7, so that an injection of fuel into an internal combustion engine can take place. In another embodiment, a servo valve is opened or closed, for example by the actuation of the second piston, so that a pressure change can act on an injection needle and thereby the injection needle is lifted from a sealing seat.
  • the volume located in the piston chamber 3 can be made small. Due to the small volume of the piston chamber 3, the total volume is reduced, which is filled with transfer medium. Thus, unnecessary dead volume in the transfer device reduced. This improves the functionality of the transmission device.
  • the transfer medium in the compensation chamber 26 is pressurized.
  • a play-free coupling between the first and the second piston 1, 2 and a corresponding actuator or actuator is reliably ensured.
  • the first spring 31 is coupled to the piston rod 17 of the first piston 1, the pressure in the compensation chamber 26 is increased upon actuation of the first piston 1 by the actuator.
  • the total pressure on the outside of the transmission chamber 10 is increased upon actuation of the transmission device, so that escape of transmission medium from the transmission chamber 10 is made more difficult.

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

Abstract

La présente invention concerne un dispositif pour translater une déviation d'un actionneur, notamment pour une soupape d'injection. Ce dispositif comprend principalement deux pistons qui peuvent se déplacer l'un par rapport à l'autre et qui sont couplés sans jeu l'un à l'autre par l'intermédiaire d'une chambre de translateur. Cette chambre de translateur est remplie d'un milieu de translateur et est connectée à une chambre de compensation par l'intermédiaire d'un espace d'étanchéité. Cet espace d'étanchéité ne compense que les différences de pression de longue durée entre la chambre de translateur et la chambre de compensation. Un des deux pistons est précontraint dans une position de départ sur un ressort monté à l'extérieur. La disposition du ressort à l'extérieur du piston permet de réduire le volume mort entre les pistons. Le fonctionnement du dispositif translateur selon cette invention se voit ainsi globalement amélioré.

Claims (9)

  1. Dispositif pour multiplier une course d'un actionneur, en particulier pour un injecteur, comprenant un boîtier (4) dans lequel des premier et second pistons (1, 2) sont montés mobiles,
       le premier piston (1), le second piston (2) et le boîtier (4) limitant une chambre de transmetteur (10),
       la chambre de transmetteur (10) étant remplie d'un milieu transmetteur et la position du premier piston (1) fixant la position du second piston (2),
       la chambre de transmetteur (10) étant reliée à une chambre d'équilibrage (26) par une conduite hydraulique (11, 12), la conduite hydraulique (11, 12) n'équilibrant que les différences de pression de longue durée entre la chambre d'équilibrage (26) et la chambre de transmetteur (10),
       la chambre d'équilibrage (26) étant limitée par un premier et/ou un second soufflets (22, 25),
       une fente de joint étant formée entre le boîtier (4) et le second piston (2) et étant fermée à joint étanche au moyen d'un troisième soufflet (38),
       un moyen de contrainte (42) étant prévu, qui précontraint le second piston (2) dans une position de repos,
       le moyen de contrainte (42), formé d'un ressort de contrainte, étant serré entre le boîtier (4) et le second
       piston (2),
       caractérisé en ce que le boîtier (4) présente une première chambre (48) munie d'une paroi terminale (5),
       en ce que le premier piston (1) est guidé dans une chambre de piston (3),
       en ce que le premier piston (1) présente une seconde chambre de piston,
       en ce que le second piston (2) est guidé dans la seconde chambre de piston,
       en ce que, dans la paroi terminale (8) du boîtier (4), est formé un perçage (6) à travers lequel passe une tige de piston (7) du second piston (2),
       en ce que la chambre de transmetteur (10) est formée entre la paroi terminale (8) du boîtier (4) et deux surfaces de pression (8, 9) des premier et second pistons (1, 2),
       en ce que les premier et second pistons (1, 2) limitent une autre chambre (46) et
       en ce que l'autre chambre (46) est reliée à la chambre d'équilibrage (26) par une conduite hydraulique (27).
  2. Dispositif selon la revendication 1, caractérisé en ce que le ressort de contrainte (42) est appuyé contre une surface d'appui (43) du boîtier (4),
       en ce qu'il est prévu une bague d'appui (41) qui est fixée à la tige de piston (7) et
       en ce que le ressort de contrainte (42) est serré entre la bague d'appui (41) et le boîtier (4).
  3. Dispositif selon la revendication 2, caractérisé en ce que la bague d'appui
       (41) est de la forme d'un manchon muni d'une embase de portée,
       en ce que la bague d'appui est reliée à la tige de piston (7) par une bague d'arrêt (40).
  4. Dispositif selon une des revendications 1 ou 2, caractérisé en ce qu'il est prévu un second ressort de contrainte (31),
       en ce que le second ressort de contrainte (31) est serré entre le boîtier (4) et une tige de piston (17) du premier piston (1).
  5. Dispositif selon une des revendications 1 ou 2, caractérisé en ce qu'il est prévu un second ressort de contrainte (31),
       en ce que le second ressort de contrainte (31) est serré entre les premier et second soufflets (22, 25) et la tige de piston (17) du premier piston (1).
  6. Dispositif selon la revendication 5, caractérisé en ce que les premier et second soufflets (22, 25) sont reliés à une bague de raccordement (23) en forme de manchon,
       en ce que la bague de raccordement (23) présente un bord d'appui périphérique en face du côté de raccordement des premier et second soufflets (22, 25),
       en ce que le second ressort de contrainte (31) est appuyé sur le bord d'appui,
       en ce qu'une deuxième bague d'appui (30) est réalisée sous la forme d'un manchon muni d'une embase de portée,
       en ce que la seconde bague d'appui (30) est reliée à la tige de piston (17) du premier piston (1) par une bague d'arrêt (29).
  7. Dispositif selon une des revendications 1 à 6, caractérisé en ce que la première chambre de piston du boîtier (4) présente une région marginale périphérique (19) dans la région ouverte,
       en ce qu'une bague (14) est fixée à joint étanche le long de la périphérie sur la région marginale (19),
       en ce que le premier soufflet (22) est soudé à joint étanche le long de la périphérie à une région marginale présentant la bague (14),
       en ce que la seconde région marginale du premier soufflet est reliée à une bague de raccordement (23),
       en ce que le second soufflet (25) est relié au second piston (2) à joint étanche le long de la périphérie par une première région marginale et en ce que la seconde région marginale du second soufflet est reliée à la bague de raccordement (23).
  8. Dispositif selon la revendication 7, caractérisé en ce que la bague (14)
       présente un perçage obturable (32), qui sert pour le remplissage de la chambre d'équilibrage (26).
  9. Dispositif selon une des revendications 1 à 8, caractérisé en ce que le second piston (2) présente un perçage (44) qui s'étend depuis une surface frontale (49) qui limite la chambre de piston jusqu'à une région dans laquelle le troisième soufflet (38) est disposé pour fermer à joint étanche une troisième fente d'étanchéité (50) qui est formée entre le second piston (2) et le boîtier (4).
EP02804848A 2001-12-17 2002-12-05 Dispositif pour translater une deviation d'un actionneur, notamment pour une soupape d'injection Expired - Lifetime EP1456527B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10162045 2001-12-17
DE10162045A DE10162045B4 (de) 2001-12-17 2001-12-17 Vorrichtung zum Übersetzen einer Auslenkung eines Aktors, insbesondere für ein Einspritzventil
PCT/DE2002/004465 WO2003052261A1 (fr) 2001-12-17 2002-12-05 Dispositif pour translater une deviation d'un actionneur, notamment pour une soupape d'injection

Publications (2)

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EP1456527A1 EP1456527A1 (fr) 2004-09-15
EP1456527B1 true EP1456527B1 (fr) 2005-09-21

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EP02804848A Expired - Lifetime EP1456527B1 (fr) 2001-12-17 2002-12-05 Dispositif pour translater une deviation d'un actionneur, notamment pour une soupape d'injection

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Country Link
US (1) US7077377B2 (fr)
EP (1) EP1456527B1 (fr)
DE (2) DE10162045B4 (fr)
WO (1) WO2003052261A1 (fr)

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DE10347769B3 (de) * 2003-10-14 2005-01-13 Siemens Ag Stellgerät
DE10350062A1 (de) * 2003-10-27 2005-05-25 Robert Bosch Gmbh Aktormodul und Verfahren zu dessen Herstellung
US7726625B2 (en) 2003-12-05 2010-06-01 Continental Automotive Gmbh Device, method for producing the device, chamber device and transfer device
DE10357189A1 (de) 2003-12-08 2005-07-07 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10358723A1 (de) * 2003-12-15 2005-07-07 Robert Bosch Gmbh Brennstoffeinspritzventil
EP1555427B1 (fr) * 2004-01-13 2007-10-10 Delphi Technologies, Inc. Injecteur de carburant
DE602005002758T2 (de) 2004-01-13 2008-07-24 Delphi Technologies, Inc., Troy Kraftstoffeinspritzventil
DE102005025953A1 (de) * 2005-06-06 2006-12-07 Siemens Ag Einspritzventil und Ausgleichselement für ein Einspritzventil
DE102010027278B4 (de) * 2010-07-15 2020-07-02 Metismotion Gmbh Thermisch volumenneutraler Hubübertrager sowie Dosierventil mit einem solchen Hubübertrager und Verwendung des Dosierventils
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Also Published As

Publication number Publication date
WO2003052261A1 (fr) 2003-06-26
DE10162045B4 (de) 2005-06-23
EP1456527A1 (fr) 2004-09-15
US7077377B2 (en) 2006-07-18
DE10162045A1 (de) 2003-06-26
US20040237519A1 (en) 2004-12-02
DE50204348D1 (de) 2006-02-02

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