EP2914838A1 - Injecteur de carburant doté d'un actionneur piézoélectrique - Google Patents

Injecteur de carburant doté d'un actionneur piézoélectrique

Info

Publication number
EP2914838A1
EP2914838A1 EP13770891.3A EP13770891A EP2914838A1 EP 2914838 A1 EP2914838 A1 EP 2914838A1 EP 13770891 A EP13770891 A EP 13770891A EP 2914838 A1 EP2914838 A1 EP 2914838A1
Authority
EP
European Patent Office
Prior art keywords
coupler
fuel
nozzle needle
volume
plate
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.)
Granted
Application number
EP13770891.3A
Other languages
German (de)
English (en)
Other versions
EP2914838B1 (fr
Inventor
Holger Rapp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2914838A1 publication Critical patent/EP2914838A1/fr
Application granted granted Critical
Publication of EP2914838B1 publication Critical patent/EP2914838B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • 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
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve

Definitions

  • the invention relates to a fuel injector for a fuel injection system, in particular a common rail injection system, having the features of the preamble of claim 1.
  • Such a fuel injector comprises a nozzle needle which is guided in a liftable manner in a high-pressure bore of a nozzle body for releasing and closing at least one injection opening, a piezoactuator accommodated in a low-pressure region for direct control of the lifting movement of the nozzle needle and a coupling device via which the piezoactuator can be hydraulically coupled to the nozzle needle ,
  • German Offenlegungsschrift DE 10 2009 001 131 A1 discloses a fuel injector with a piezoactuator arranged in a low-pressure region of the injector for direct control of the stroke movement of a nozzle needle, in which the nozzle needle is arranged largely pressure-balanced.
  • a plunger-like extension is arranged on the nozzle-side end of the nozzle needle and is axially displaceable and tightly guided in a guide bore communicating with the combustion chamber.
  • the piezoelectric actuator can be hydraulically coupled to the nozzle needle via a coupler chamber.
  • the coupling takes place in such a way that when the piezoelectric actuator is energized, the nozzle needle assumes its closed position and the energization of the piezoelectric actuator must be interrupted to open it.
  • the piezoceramic of the actuator is exposed to a strong electric field for a long time during the operating period, as this is the case with non-inverse control. The result can be a significantly shortened life of the actuator.
  • the present invention is therefore an object of the invention to provide a fuel injector with a piezoelectric actuator for direct control of the lifting movement of a nozzle needle, which is durable.
  • a fuel injector with a piezoelectric actuator is to be specified, which does not control the nozzle needle inversely.
  • the injector comprises a nozzle needle which can be moved in a high-pressure bore of a nozzle body so as to release and close at least one injection opening, a piezoactuator accommodated in a low-pressure region for direct control of the lifting movement of the nozzle needle, and a coupling device by means of which the piezoactuator can be hydraulically coupled to the nozzle needle.
  • the coupling device comprises a coupler volume, which is formed within a sleeve-shaped coupler piston. The coupler piston is guided in a liftable manner via an inner pin defining the coupler volume in an axial direction.
  • an end section of the nozzle needle protrudes into the coupler volume or into a volume of fuel hydraulically connected to the coupler volume, so that the pressure in the coupler volume acts on the end face of this end section of the nozzle needle with an axial force acting in the closing direction.
  • This guide can be arranged either directly in a bottom part of the coupler piston or in a sealing sleeve arranged below the coupler piston.
  • the coupling device allows direct control of the nozzle needle, in which an elongation of the actuator causes the opening of the nozzle needle. In order to lift the nozzle needle out of its sealing seat, the sleeve-shaped coupling piston is moved in relation to the inner pin in the groove. tion of the sealing seat of the nozzle needle shifted, so that the
  • Coupler volume increased.
  • the associated pressure decrease in the
  • Coupler volume causes the nozzle needle is drawn into the coupler volume or in the associated with the coupler volume, located above the end portion of the nozzle needle fuel volume.
  • the nozzle needle lifts off from its sealing seat. Accordingly, a direction reversal is effected via the coupling device.
  • the piezo actuator only has to be charged if an injection is to take place. During the injection pauses the piezo actuator is discharged. As a result, the load of the piezoelectric actuator is reduced so that the life of the actuator increases. This is further helped by the fact that the piezoelectric actuator in a low pressure range of the fuel! Njektors is arranged, that is, that he is not exposed to high pressure.
  • actuator is also used in the following as a synonym for "actuator module”.
  • the specified coupling device is also simple and requires only a small space.
  • the coupler piston is acted upon by the spring force of a compression spring, which is supported on the one hand on the coupler piston and on the other side of the housing.
  • the spring force of the compression spring pushes the coupler piston in the direction of the piezoelectric actuator and causes in this way a provision of the
  • Coupling piston when the energization of the piezoelectric actuator is terminated and this contracts.
  • the spring force of the compression spring at rest ensures a bias of the actuator with a mechanical compressive stress. This avoids that at least parts of the actuator ceramic are exposed during operation of a tensile stress, which would lead to destruction of the actuator. In particular, this danger exists especially immediately after the end of the charging process of the actuator and immediately at the beginning of the unloading process.
  • a power transmission element is furthermore preferably arranged between the piezoelectric actuator and the coupling device.
  • This preferably comprises a pressure plate passing through, pin-shaped portion and a plate-shaped portion for axially supporting the sleeve-shaped coupler piston.
  • the pressure plate which is penetrated by the pin-shaped portion of the force transmission member, preferably serves the separation of the low pressure region of a high-pressure region of the fuel injector.
  • the diameter of the pin-shaped portion of the force transmission member is therefore preferably as small as possible and / or the guide clearance chosen as narrow as possible in the pressure plate for receiving the pin-shaped portion of the hole provided.
  • the pin-shaped portion of the force transmission member may be surrounded in the high pressure region by a sealing sleeve, which is preferably supported on the pressure plate via a biting edge. If at the same time the guide play in the pressure plate is designed to be large, this embodiment enables a displacement of the force transmission member including the sealing sleeve in the radial direction and thus a compensation of any axial offset. Furthermore, a very good sealing of the low-pressure region with respect to the high-pressure region is effected via the sealing sleeve.
  • the inner pin is made in one piece with the coupler plate.
  • the coupler plate serves as a further housing part and can be attached axially, for example, to the above-mentioned pressure plate.
  • the bore of the coupler plate, in which the inner pin is received must be provided with a sufficient clearance.
  • a flat or spherically shaped support surface is preferably formed on the inner journal, via which the inner journal is supported on the coupler plate.
  • the support surface formed on the inner pin is preferably designed plane and supported on a support surface of the coupler plate formed opposite.
  • this preferably has a spherically shaped support surface, via which the inner pin is supported on a plane flat, conical or spherical shaped support surface of the coupler plate.
  • an intermediate ring between the inner pin and the coupler plate are inserted, which preferably allows both a pivoting and a radial displacement of the inner pin relative to the coupler plate.
  • the coupler plate has at least one further recess serving as an inlet bore and / or as a passage opening.
  • a recess serving as an inlet bore is preferably arranged laterally and continues a feed bore formed in a holding body and arranged laterally.
  • the inlet bore may be slightly inclined running inwardly to connect the inlet bore of the holding body with the high-pressure bore in the nozzle body.
  • Coupling piston integrally connected power transmission elements provided.
  • Such power transmission elements may for example be formed pin-shaped and arranged at the same angular distance from each other in the axial extension of the coupler piston.
  • pin-shaped elements and part-circular wall pieces of the coupler piston can serve as a power transmission elements.
  • the recesses of the coupler plate are preferably adapted to the cross section of the power transmission elements. However, it must be ensured that the coupler piston remains axially displaceable.
  • the inner pin is acted upon by the spring force of a compression spring which is supported on the one hand on the coupler plate and on the other hand on a radially extending shoulder of the inner pin.
  • a compression spring which is supported on the one hand on the coupler plate and on the other hand on a radially extending shoulder of the inner pin.
  • the inner pin is arranged to be pivotable and / or radially displaceable.
  • the radially extending shoulder on the inner pin for supporting the spring is oriented radially inward, the spring can be made conical and engage with its tapering end in the recess formed on the inner pin.
  • the spring can also be cylindrical and be supported on a radially extending shoulder which extends radially outward. For this purpose, for example, be pressed onto the inner pin a sleeve.
  • the nozzle needle is acted upon by the spring force of a compression spring, said spring being supported on the one hand directly on the coupler piston or indirectly via a sealing sleeve on the coupler piston and on the other hand on the nozzle needle. Furthermore, the end portion of the nozzle needle directly in a bore in
  • the end section of the nozzle needle is guided in a liftable manner in a sealing sleeve, which is acted upon by the spring force of a compression spring in the direction of the coupler piston and is preferably arranged below the coupler piston.
  • the sealing sleeve between the coupler piston and the compression spring is arranged, so that the sealing sleeve is held by the spring force of the compression spring in contact with the lower end face of the coupler piston.
  • the sealing sleeve, the end section of the nozzle needle and the coupler piston preferably define one
  • Fuel volume connected to the coupler volume can be accomplished by projecting the end portion of the nozzle needle above its guide in the sealing sleeve through a bore in the bottom portion of the coupler piston into the coupler volume and providing a large diameter clearance between the bore in the bottom portion of the coupler piston and the end portion of the nozzle needle.
  • Another way to connect the volume enclosed by the sealing fuel volume with the coupler volume is to execute the nozzle needle only so long that the upper end face of its end portion in the region of the sealing sleeve below the lower end face of the coupler piston and that of the sealing sleeve, the End portion of the nozzle needle and the lower end face of the coupler piston limited volume via a passage in the bottom part of the coupler piston with the original of the coupler piston and the inner pin enclosed
  • Coupler volume is connected.
  • the passage is preferably designed as a bore, wherein the diameter of which may now be smaller than the diameter of the end section of the nozzle needle.
  • the passage is designed as a throttle point.
  • Such an embodiment of the passage as a throttle point counteracts the excitation of hydraulic and / or mechanical vibrations in the region of the nozzle needle.
  • the embodiments in which the nozzle needle is guided in a sealing sleeve, allow the compensation of axial offset tolerances between the
  • Coupler piston and the nozzle needle wherein at the same time on the guide gap between the sealing sleeve and the nozzle needle, the coupler volume is sealed against the high-pressure region.
  • the coupling device is intrinsically safe. Because in the event of a fault, for example accidentally permanently charged actuator, the coupler volume fills gradually, thus causing the closing of the nozzle needle.
  • the high-pressure volume surrounding the coupling device can at the same time be used as an additional pressure reservoir (so-called
  • a defined throttle point is preferably provided in the flow region between the nozzle needle and the high-pressure bore, so that a closing force always acts on the nozzle needle in the open state. Because with an open nozzle, the pressure at the nozzle seat is always slightly smaller due to the throttle point than in the area of the coupling device. Such a throttle point also counteracts or dampens hydraulic and mechanical vibrations in the region of the nozzle needle. Furthermore, this counteracts a pressure increase in the coupler volume beyond the system pressure.
  • the force transmission member is acted upon by the spring force of a compression spring, which on the one hand directly or indirectly via a sealing sleeve on the pressure plate and on the other hand on the plate-shaped portion of
  • Power transmission member is supported.
  • the compression spring holds the sealing sleeve in contact with the pressure plate. In this way, an optimized seal is effected.
  • the arrangement of a sealing sleeve with simultaneous formation of a sufficiently large sized guide clearance between the force transmission member and the pressure plate allows a radial displacement tion of the power transmission member relative to the pressure plate. Thus, this arrangement also compensates for any axial misalignment.
  • an adjusting piece be arranged between the force transmission member and the piezoelectric actuator.
  • the height of the adjusting piece can be used to influence the height of the coupler volume.
  • the actuator force is transmitted uniformly to the power transmission member via the adjusting piece.
  • such a setting piece can also be arranged between the force transmission member and the coupler piston.
  • a sleeve-shaped housing part is arranged between the coupler plate and the nozzle body, which receives the coupling device at least partially.
  • the sleeve-shaped housing part is therefore subjected to high pressure, which surrounds the coupling device.
  • it can serve as a so-called "minirail".
  • the injector has the advantage of a long service life.
  • the piezoelectric actuator is arranged in the low-pressure region, on the other hand can be coupled via a direction-reversing coupler with the nozzle needle, so that it is only charged when an injection is to take place. During the injection pauses the piezo actuator is discharged.
  • the proposed for rea ltechnik a reversal coupling device is simple and requires little space. Due to the arrangement of the coupling device in the high-pressure region, wherein the high-pressure fuel surrounds the coupling device, a guide play widening in a guide region of the coupling device is counteracted. As a result, the pressure and temperature-dependent functional influence of the
  • Coupler leakage reduced.
  • the compensation of any axial offsets can also be realized.
  • the individual components such as nozzle needle, coupler piston, power transmission member.
  • these components in any places in several components can be separated, for example, if this offers advantages for the production or assembly.
  • the power transmission elements penetrating the coupler plate may be integral with the coupler piston or integral with the force transmitting member.
  • they can be present as separate components.
  • the recorded in the low pressure region of a holding body piezoelectric actuator can - as shown in the following drawings - be encapsulated, or alternatively be sealed by a diaphragm against the actuator space filling, under low pressure fuel, the membrane is preferably inserted sealingly between the actuator head and the inner wall of the holder body , Further preferably, the intermediate space between the actuator and the holding body may be filled with a thermally conductive potting compound to optimize the heat dissipation.
  • FIG. 6a shows a partial longitudinal section through a coupling device of a further fuel according to the invention! njektors
  • FIG. 6b shows a partial longitudinal section through a coupling device, which represents an alternative embodiment to the coupling device according to FIG. 6a
  • Figure 7a-c each have a longitudinal section through a coupling device of a fuel according to the invention! Njektors in the area of the inner pin and
  • FIG. 1 The longitudinal section of Figure 1 shows the fuel injector according to the invention in the closed position. Shown is a in a holding body 4 of the fuel! Njektors recorded piezoelectric actuator 6, which is supported via an adjusting piece 30 to a power transmission member 14.
  • the power transmission member 14 has a pin-shaped portion 16, with which it passes through a pressure plate 15 to come into abutment with the setting piece 30. At its other end, the force transmission member 14 on a plate-shaped portion 17, which cooperates with a coupling device 7.
  • the diameter of the pin-shaped portion 16 is chosen to be significantly smaller than that of the plate-shaped portion, at the same time, the pin-shaped portion 16 receiving bore of the pressure plate 15 has a narrow guide gap.
  • the coupling device 7 comprises a sleeve-shaped coupler piston 9, within which a coupler volume 8 is formed.
  • the coupler piston 9 is guided axially displaceably via an inner journal 10, so that the coupler volume 8 can be changed via an axial displacement of the coupler piston 9.
  • a bore is formed, in which an end portion 12 of a nozzle needle 3 is received axially displaceable.
  • the piezoactuator 6 When the piezoactuator 6 is energized and expands, it presses the adjusting piece 30 and the force applied thereto.
  • the transmission member 14 thereby moves the sleeve-shaped coupler piston 9 against the spring force of a compression spring 13 in the direction of the sealing seat. This increases the coupler volume 8, which has the consequence that the pressure in the coupler volume 8 decreases and the nozzle needle 3 against the spring force of a compression spring 25 opens. If the energization of the piezoelectric actuator 6 is terminated, this contracts again, wherein the compression spring 13, the coupler piston 9 and the power transmission member 14 resets in the respective starting position.
  • the coupler volume 8 decreases and the pressure increase in the coupler volume 8 as well as the spring force of the compression spring 25 cause the nozzle needle 3 to be reset in its sealing seat.
  • the nozzle needle 3 is arranged for lifting this in a high-pressure bore 1 of the nozzle body 2.
  • the fuel injector in the open position is shown in FIG.
  • the enlarged detail of Figure 2 shows the fuel injector of Figure 1 in
  • Coupler volume 8 the nozzle needle 3 is hydraulically coupled to the piezoelectric actuator 6.
  • the coupler volume 8 and the pressure prevailing in the coupler volume 8 pressure via an axial displacement of the coupler piston 9 can be changed, wherein the axial displacement of the coupler piston 9 is effected via the piezoelectric actuator 6.
  • the force of the piezoelectric actuator 6 pushes the coupler piston 9 in the direction of the sealing seat of the nozzle needle 3, whereby the pressure in the coupler volume 8 decreases and the nozzle needle 3 opens against the direction of force of the piezoelectric actuator 6.
  • a direction reversal is thus effected via the coupling device 7 shown in FIG. 2, which causes the nozzle needle 3 to move toward the piezoactuator 6 when the piezoactuator 6 is elongated.
  • FIG. 3 shows a cross section through the injector of FIG. 1, the section being laid through a coupler plate 20.
  • the diameter range of the inner pin 10, which is embodied here in one piece with the coupler plate 20, is identified separately in FIG. 3.
  • This diameter range of the inner pin 10 is surrounded by recesses, wherein two kidney-shaped recesses 22 as passage openings for force transmission elements 33 of the coupler piston 9th and a laterally arranged recess serve as an inlet bore 21.
  • the inner pin 10 may also be designed as a separate component and received in a bore 19 of the coupler plate.
  • the storage of the inner pin 10 in the bore 19 of the coupler plate 20 may be configured differently. Concrete embodiments of this can be seen in FIGS. 7a-c and 8a-c.
  • FIGS. 7a-c show embodiments by means of which a possible axial offset can be compensated.
  • the inner pin 10 is for this purpose in the bore 19 of the coupler plate 20 radially displaceable (see Figure 7a) or pivotable (see
  • FIG. 7b A combination of the two degrees of freedom can be achieved by the embodiment according to FIG. 7 c, in which an intermediate ring 32 is arranged between the inner journal 10 and the coupler plate 20.
  • the intermediate ring 32 allows both a radial displacement of the inner pin 10 against the intermediate ring 32 and thus with respect to the coupler plate 20 and a pivoting of the intermediate ring 32 and thus the inner pin 10 relative to the coupler plate 20th
  • the inner pin 10 can also be acted on by the spring force of a compression spring 23, which is supported on the one hand by a radial shoulder 24 of the inner pin 10 and on the other hand by the coupler plate 20. Since the radial shoulder 24 extends radially inward is the compression spring
  • FIG. 5 An alternative embodiment of a fuel injector according to the invention is shown in FIG. 5, in which the force transmission member 14 is surrounded by a sealing sleeve 29 in the region of its pin-shaped portion 16.
  • the sealing sleeve 29 is supported on the pressure plate 15 and is held by the spring force of a compression spring 28 into contact with the pressure plate 15.
  • the compression spring 28 on the one hand on the sealing sleeve 29 and on the other hand supported on the plate-shaped portion 17 of the power transmission member 14.
  • the pin-shaped portion 16th the power transmission member 14 receiving bore of the pressure plate 15 also has a larger guide play, so that a radial displacement of the power transmission member 14 in order to compensate for any axial offset is possible.
  • a sealing of the low-pressure region 5 with respect to the high-pressure region 18 is effected via the sealing sleeve 29.
  • this embodiment has the further advantage that the pressure prevailing in the high-pressure region 18 causes a reduction of the guide clearance between the sealing sleeve 29 and the force-transmitting member 14. In this way, the normally unavoidable rise of the leakage at the guide of the force transmission member 14 in the pressure plate 15 is counteracted with increasing high pressure.
  • a comparable arrangement can-as shown in FIG. 6a-also be provided for sealing the coupler volume 8 with respect to the high-pressure region 18, wherein a sealing sleeve 26 surrounds the end portion 12 of the nozzle needle 3.
  • the bore, in which the end portion 12 of the nozzle needle 3 is received provided with sufficient guide play, so that over a radial displacement of the nozzle needle 3 and the sealing sleeve 26, a compensation of any axial offset is possible.
  • the sealing sleeve 26 is in turn axially biased by a compression spring 25 relative to the coupler piston 9, wherein the compression spring 25 is supported on the one hand on a radially extending shoulder 27 of the nozzle needle 3 and on the other hand on the sealing sleeve 26.
  • FIG. 6b A further development of the embodiment shown in FIG. 6a is shown in FIG. 6b.
  • the guided in the sealing sleeve 26 end portion 12 of the nozzle needle 3 is designed such that its upper end face is already arranged in the sealing sleeve 26, ie below the lower end face of the coupler piston 9.
  • the diameter of the bore in the bottom part 1 1 of the coupler piston 9 can be significantly reduced. Namely, this hole no longer needs to receive the nozzle needle 3, but only a hydraulic connection between the actual coupler volume 8 and a coupler volume A, which is formed between the coupler piston 9 and the inner journal 10, and a
  • the bore in the bottom part 1 1 of the coupler piston 9 may further, regardless of whether it receives the end portion 12 of the nozzle needle 3 or not, also be designed as a passage channel with non-circular cross-section.
  • the high pressure surrounding the coupling device 7 can serve as an additional pressure accumulator or as a so-called “minirail.”
  • the coupling device 7 is surrounded by a sleeve-shaped housing part 31 which is arranged between the coupler plate 20 and the nozzle body 2.
  • the holding body 4, the pressure plate 15, the coupler plate 20, the housing part 31 and the nozzle body 2 can be axially clamped against one another via a clamping nut (not shown)

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

Abstract

L'invention concerne un injecteur de carburant pour un système d'injection de carburant, en particulier un système d'injection à rampe commune, comprenant une aiguille d'injecteur (3) guidée en déplacement axial dans un alésage haute pression (1) d'un corps d'injecteur (2), pour l'ouverture et la fermeture d'au moins un orifice d'injection, un actionneur piézoélectrique (6) logé dans une région basse pression (5), pour la commande directe du déplacement de l'aiguille d'injecteur (3), ainsi qu'un dispositif de couplage (7) assurant le couplage hydraulique de l'actionneur piézoélectrique (6) avec l'aiguille d'injecteur (3). Selon l'invention, le dispositif de couplage (7) comprend un volume de couplage (8) formé à l'intérieur d'un piston de couplage (9), le piston de couplage (9) étant déplaçable axialement par l'intermédiaire d'un téton intérieur (10) délimitant le volume de couplage (8) dans une direction axiale, une partie terminale (12) de l'aiguille d'injecteur (3) faisant saillie à l'intérieur du volume de couplage (8) ou d'un volume de carburant relié au volume de couplage (8).
EP13770891.3A 2012-10-30 2013-09-26 Injecteur de carburant doté d'un actionneur piézoélectrique Not-in-force EP2914838B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012219867.9A DE102012219867A1 (de) 2012-10-30 2012-10-30 Kraftstoffinjektor mit Piezoaktor
PCT/EP2013/070073 WO2014067720A1 (fr) 2012-10-30 2013-09-26 Injecteur de carburant doté d'un actionneur piézoélectrique

Publications (2)

Publication Number Publication Date
EP2914838A1 true EP2914838A1 (fr) 2015-09-09
EP2914838B1 EP2914838B1 (fr) 2019-08-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13770891.3A Not-in-force EP2914838B1 (fr) 2012-10-30 2013-09-26 Injecteur de carburant doté d'un actionneur piézoélectrique

Country Status (4)

Country Link
EP (1) EP2914838B1 (fr)
CN (1) CN104769269B (fr)
DE (1) DE102012219867A1 (fr)
WO (1) WO2014067720A1 (fr)

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Publication number Priority date Publication date Assignee Title
GB201415539D0 (en) * 2014-09-03 2014-10-15 Delphi International Operations Luxembourg S.�.R.L. Fuel injector
DE102015219912B3 (de) * 2015-10-14 2017-04-06 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoffeinspritzung
DE102015224554A1 (de) 2015-12-08 2017-06-08 Robert Bosch Gmbh Dosiervorrichtung für ein elektrisch isolierendes Medium
CN106870230B (zh) * 2017-01-06 2019-09-24 中国第一汽车股份有限公司 一种共轨喷油器

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JP2010019147A (ja) * 2008-07-09 2010-01-28 Nippon Soken Inc 燃料噴射弁
DE102009001131A1 (de) 2008-12-09 2010-06-10 Robert Bosch Gmbh Kraftstoffinjektor
JP5024320B2 (ja) * 2009-03-25 2012-09-12 株式会社デンソー 燃料噴射弁
DE102010040581A1 (de) * 2010-02-24 2011-08-25 Robert Bosch GmbH, 70469 Kraftstoffinjektor sowie Verfahren zur Herstellung und/oder Montage einer Düsennadel-Baugruppe
DE102010029123A1 (de) * 2010-05-19 2011-11-24 Robert Bosch Gmbh Kraftstoffinjektor mit hydraulischer Kopplereinheit

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EP2914838B1 (fr) 2019-08-28
CN104769269B (zh) 2018-01-19
WO2014067720A1 (fr) 2014-05-08
DE102012219867A1 (de) 2014-04-30
CN104769269A (zh) 2015-07-08

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