EP1526275B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP1526275B1
EP1526275B1 EP20040105090 EP04105090A EP1526275B1 EP 1526275 B1 EP1526275 B1 EP 1526275B1 EP 20040105090 EP20040105090 EP 20040105090 EP 04105090 A EP04105090 A EP 04105090A EP 1526275 B1 EP1526275 B1 EP 1526275B1
Authority
EP
European Patent Office
Prior art keywords
elastic sealing
fuel injection
injection valve
lifting element
valve according
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 - Fee Related
Application number
EP20040105090
Other languages
German (de)
English (en)
Other versions
EP1526275A1 (fr
Inventor
Klaus Noller
Uwe Liskow
Martin Maier
Michael Huebel
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
Priority claimed from DE102004015622A external-priority patent/DE102004015622A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1526275A1 publication Critical patent/EP1526275A1/fr
Application granted granted Critical
Publication of EP1526275B1 publication Critical patent/EP1526275B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M61/04—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
    • 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
    • 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
    • F02M2200/705—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
    • F02M2200/706—Valves for filling or emptying hydraulic chamber
    • 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 fuel injection valve according to the preamble of the main claim (WO-A-01/29403). It is already known a fuel injection valve from US 4,858,439, which has a hydraulic coupler having a base body with two hollow cylinders, in each of which a piston is guided, and two acting as elastic sealing elements Wellbälge for sealing against the environment. The first bellows seals the coupler between the main body and the first piston and the second bellows seals the coupler between the main body and the second piston. Between the two pistons a liquid-filled coupler gap is provided.
  • a disadvantage is that the two corrugated bellows are mechanically heavily loaded when liquid exits through movement of the piston from the coupler gap, since the corrugated bellows must absorb the exiting from the coupler gap liquid as additional volume.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that in a simple manner, the mechanical load of the at least one elastic sealing element is reduced by a lifting element is provided, the axially operatively connected between the pot-shaped cylinder and a piston operatively connected to the head is movably mounted, with a seal between the cylinder and the lifting element and between the lifting element and the head part is provided.
  • the lifting element shifts when liquid emerges from the coupler gap and provides an additional compensating volume, so that the at least one elastic sealing element is exposed to a lower mechanical load compared to the prior art.
  • the hydraulic coupler can operate in this way with higher internal pressures, so that the fuel injection valve can be switched at a higher frequency.
  • a first elastic sealing element is provided as a seal between the lifting element and the cylinder and a second elastic sealing element as a seal between the lifting element and the head part.
  • a stepped bellows is provided as a seal, the one Has first sealing portion and a second sealing portion, which are integrally connected to each other via a shoulder formed as a lifting element.
  • the head part is operatively connected via a piston rod with the piston.
  • first elastic sealing element and the second elastic sealing element or the stepped bellows is made of steel, since a steel sealing element ensures a hermetic seal of the hydraulic coupler over the entire life of the fuel injection valve.
  • the first elastic sealing element or the first elastic sealing portion has a wave number between three and eight. In this way, the rigidity of the first elastic sealing element or of the first elastic sealing section and its mechanical load is reduced.
  • the second elastic sealing element or the second elastic sealing portion has a wave number between three and twelve. In this way, the rigidity of the second elastic sealing element or of the second elastic sealing section and its mechanical load is reduced.
  • the lifting element is guided axially on the piston rod and / or on the cylinder, so that the lifting element does not tilt during the axial movement.
  • the lifting element is formed lid-shaped, since in this way space is saved.
  • a coupler gap and between the lifting element and the cup-shaped cylinder a compensation gap is provided, wherein the coupler gap and the compensation gap are flow-connected via at least one throttle element. Due to the throttle element, the hydraulic coupler behaves as a rigid component during fast movement processes and as a flexible and length-compensating component during slow movement processes.
  • FIG. 1 shows a schematically illustrated fuel injection valve
  • FIG. 2 shows a hydraulic coupler according to the invention according to a first exemplary embodiment
  • FIG. 3 shows a hydraulic coupler according to the invention according to a second exemplary embodiment
  • FIG hydraulic coupler according to a third embodiment is shown in simplified form in the drawing and explained in more detail in the following description.
  • FIG. 1 shows a fuel injection valve, in which, for example, an inventively designed hydraulic coupler is used.
  • the fuel injection valve is used to inject fuel into a combustion chamber of an internal combustion engine and is used for example in the so-called direct injection.
  • the fuel injection valve has a valve housing 1 with an input channel 2 for the fuel.
  • a schematically illustrated actuator 3 for the axial adjustment of a valve needle 4 is arranged in the valve housing 1.
  • the valve needle 4 is provided axially movable in the valve housing 1 and has, for example, a needle shaft 7 facing the actuator 3 and a valve closing body 8 facing away from the actuator 3.
  • the actuator 3 transmits its movement via a so-called hydraulic coupler 9 to the needle shaft 7 of the valve needle 4, whereby the cooperating with a valve seat 10 valve closing body 8 opens or closes the fuel injection valve.
  • the fuel injection valve has, for example, a so-called ball-cone seat, wherein the valve seat 10 is formed, for example, conical and the valve closing body 8 has a cooperating with the valve seat 10 ball or radius section 11. When the fuel injection valve is closed, the valve closing body 8 lies on the entire circumference of the Valve seat 10 with line or surface contact tightly, which is hereinafter referred to as sealing seat 12.
  • the actuator 3 is designed, for example, a piezoelectric or magnetostrictive actuator and encapsulated with respect to the fuel.
  • a piezoelectric actuator is proposed, for example, in German Patent Application 103 19 599, the content of which is expressly intended to be part of the disclosure of this application.
  • the piezoelectric actuator 3 consists of a plurality of piezoceramic layers, which perform an expansion in the axial direction by applying an electrical voltage. In this case, the so-called inverse piezoelectric effect is utilized in which electrical energy is converted into mechanical energy.
  • the elongation of the piezoceramic layers generated by the application of the electrical voltage is transmitted via the hydraulic coupler 9 to the valve needle 4, wherein the valve needle 4 carries out, for example, a stroke of 40 to 50 micrometers.
  • the actuator 3 is shortened by switching off the electrical voltage and the valve needle 4 is moved back by means of a spring 15 in the direction of the valve seat 10 and closes the fuel injection valve.
  • the hydraulic coupler 9 must compensate for the differences in the different linear expansion, to ensure that the Fuel injection valve with the valve needle 4 regardless of the respective temperature of the fuel injection valve at an opening movement in each case performs the same stroke as the actuator 3. There may be no lift losses occur in which the stroke of the actuator 3 is not completely transferred to the valve needle 4, so that the Stroke of the valve needle 4 is smaller than the stroke of the actuator.
  • the fuel is passed in the valve housing 1, starting from the inlet channel 2 to the valve closing body 8 upstream of the sealing seat 12.
  • the valve closing body 8 lifts off from the sealing seat 12, whereby a connection to the combustion chamber of the internal combustion engine is opened, so that fuel flows out into the combustion chamber via an outlet gap formed between the valve closing body 8 and the valve seat 10.
  • the output gap expands, for example, in the flow direction and thus acts as a diffuser. The larger the stroke of the valve needle 4 in the opening direction, the larger the output gap and the more fuel is injected into the combustion chamber per unit time.
  • the fuel injection valve is for example a so-called outward-opening valve, wherein the valve needle 4 executes a stroke in the direction away from the actuator 3, but may of course also be a so-called inwardly opening valve.
  • FIG. 2 shows a hydraulic coupler according to the invention according to a first embodiment.
  • the hydraulic coupler 9 is clamped between the actuator 3 and the valve needle 4 and has, for example, a cup-shaped cylinder 16 with a pot bottom 18 and a piston 17 which is axially movable in the pot-shaped cylinder 16.
  • the pot bottom 18 of the pot-shaped cylinder 16 abuts against the valve needle 4.
  • the diameter of the piston 17 facing the inner side 20 of the cup-shaped cylinder 16 is slightly larger than the diameter of the piston 17th
  • the piston 17 is for example cylindrical.
  • a piston rod 19 is provided, which has a relative to the piston 17 smaller radial extent and extending axially in a direction away from the piston 17.
  • the piston rod 19 is for example cylindrical, but may also have a different shape.
  • the piston rod 19 has, for example, at its end facing away from the piston 17 on the piston rod 19 mounted on a head portion 31 which rests against the actuator 3.
  • the head part 31 is for example cylindrical, but may also have a different shape.
  • the head part 31 has a passage opening 32, into which the piston rod 19 projects at least, and is, for example, bonded to the piston rod 19 in a materially bonded manner.
  • the head part 31 can also be joined together with the piston rod 19 in other ways.
  • a lifting element 22 is provided in the hydraulic coupler 9, which is mounted axially movable between the cup-shaped cylinder 16 and the head 17 operatively connected to the piston 17.
  • the first embodiment is provided as a seal on the hydraulic coupler 9, a first elastic sealing element 23 between the lifting element 22 and the cylinder 16 and a second elastic sealing element 24 between the lifting element 22 and the head part 31 relative to the fuel in the fuel injection valve.
  • the first elastic sealing element 23 and the second elastic sealing element 24 are designed such that they give the lifting element 22 sufficient degree of freedom for an axial movement between the cup-shaped cylinder 16 and the head 17 operatively connected to the piston 17.
  • the lifting element 22 is formed, for example, lid-shaped and has a passage 29 through which the piston rod 19 engages.
  • the lifting element 22 is guided for axial movement, for example on the piston rod 19, wherein the passage 29 in its radial extent is slightly larger than the piston rod 19.
  • the lifting element 22 for example, a concentric with the passage 29 arranged guide shoulder 30, the starting from the cylinder 16 facing away from the end face of the lifting element 22, starting in the direction away from the cylinder 16.
  • the first elastic sealing element 23 and / or the second elastic sealing element 24 are formed, for example, as corrugated bellows and a plurality of annular circumferential waves or folds 27 on.
  • the first elastic sealing element 23 and the second elastic sealing element 24 are elastically formed in this way in the axial direction and made for example of steel.
  • the first elastic sealing element 23 and the second elastic sealing element 24 have the lowest possible spring rigidity.
  • the first elastic sealing element 23 has, for example, three to eight shafts 27, preferably five shafts 27, the second elastic sealing element 24 has a wave number of three to twelve, preferably nine. In this way, the respectively optimum for the function of the coupler stiffness of the elastic sealing elements 23,24 is achieved.
  • a shaft 27 of two, for example, approximately parallel to each other running shaft walls 34 and the shaft walls 34 connecting wave arc 35 is formed.
  • the wall thickness of the elastic sealing elements 23,24 is about 50 to 100 microns.
  • the first elastic sealing element 23 has, for example, a wave height of three to six millimeters measured in the radial direction between two adjacent wave sheets 35, and the second elastic sealing element 24 has a wave height of one to two millimeters measured in the radial direction.
  • the cylinder 16 has on its outer circumference on an annular circumferential shoulder 25 which extends from the lifting element 22 facing the end face 21 of the cylinder 16 up to a first shoulder 26 of the heel 25.
  • the first elastic sealing element 23 is connected at one end to the first shoulder 26 of the shoulder 25 and at the other end to the lifting element 22, for example, the circumference, cohesively or non-positively, for example by means of a welded connection, and is axially from the shoulder 25 axially guided.
  • the second elastic sealing element 24 is connected at its one end to the guide shoulder 30, for example, the circumference of the lifting element 22 and at its other end to the head part 31 cohesively or non-positively, for example with a designated inner mounting paragraph.
  • a spring element 33 for example a helical spring, is arranged, which rests with its one end on an end face of the lifting element 22 and with its other end against a second shoulder 36 of the head part 31 and between the lifting element 22 and the second shoulder 36 of the head part 31 is kept under tension.
  • the cylinder 16, the piston 17, the piston rod 19, the lifting element 22, the passage 29 of the lifting element 22, the head part 31, the through hole 32 of the head part 31, the first elastic sealing element 23, the second elastic sealing element 24 and the spring element 33 are For example, arranged concentrically to an axis 37 of the hydraulic coupler 9.
  • a compensating gap 43 is provided with a compensating volume.
  • the size of the coupler gap 38 is variable depending on the axial position of the piston 17.
  • the compensation gap 43 is fluidly connected to the coupler gap 38 via at least one connecting channel 44 provided in the piston 17 and a throttle element 45 adjoining the connecting channel 44 in the piston 17 and vice versa.
  • the connecting channel 44 extends, for example, starting from an end face of the piston 17 facing the lifting element 22 in the direction of the pot bottom 18 and is flow-connected via the throttle element 45 to the coupler gap 38.
  • the hydraulic coupler 9 includes an internal space 39, which hermetically by means of the elastic sealing elements 23,24 within the fuel injector is sealed from the fuel.
  • the interior 39 of the hydraulic coupler 9 is filled with a liquid, for example fuel or a second medium such as silicone oil or Fomblin.
  • the spring element 33 presses the lifting element 22 in the direction of the cylinder 16 and generates in this way an overpressure in the interior 39 of the hydraulic coupler 9. Furthermore, the spring element 33 presses the head part 31 in the direction of the actuator 3.
  • the piston rod 19 has a filling channel 46, which opens into the interior 39 of the hydraulic coupler 9.
  • the filling channel 46 is sealed after filling the hydraulic coupler 9 with liquid by means of a closure body 47, for example a ball, with respect to the fuel in the fuel injection valve.
  • the hydraulic coupler 9 compensates the difference in length resulting from the difference in elongation by changing its axial length such that the hydraulic Coupler 9 with the head part 31 is always applied to the actuator 3 and with the bottom of the pot 18 always on the valve needle 4. In this way it is achieved that no gap between the actuator 3 and the valve needle 4 can form, so that it is always ensured that the stroke of the actuator 3 is completely transferred to the valve needle 4 and no lifting losses occur.
  • the extension of the actuator 3 is transmitted to the valve needle 4 via the head part 31, the piston rod 19, the piston 17, the coupler gap 38 and the cylinder 16.
  • the hydraulic coupler 9 behaves as an extremely rigid component, since in the short time almost no liquid from the coupler gap 38 through the Throttle element 45 can flow.
  • the coupler gap 38 remains constant, the stroke of the actuator 3 is completely transferred to the valve needle 4.
  • the coupler gap 38 decreases or increases because the liquid has sufficient time to flow out of the coupler gap 38 via the restrictor 45 or into the coupler gap 38 ,
  • the piston 17 moves with its piston rod 19 and the head part 31 in the direction away from the pot bottom 18 direction, thereby increasing the coupler gap 38.
  • liquid from the compensation gap 43 and / or the rest of the interior 39 flow through the connecting channel 44 and the throttle element 45 in the coupler gap 38. Since the compensation gap 43 has delivered liquid, it is reduced by movement of the lifting element 22 in the direction of the cylinder 16.
  • the overpressure the liquid in the hydraulic coupler 9 is for example 5 to 20 bar.
  • the piston 17 moves with its piston rod 19 and the head part 31 in the direction of the bottom of the pot 18, thereby reducing the coupler gap 38.
  • Liquid must escape from the coupler gap 38 through the restrictor element 45 and the connecting channel 44 flow into the compensation gap 43 and / or the remaining interior 39.
  • the volume of the compensation gap 43 must increase as the lifting element 22 moves in the direction away from the cylinder 16.
  • each necessary compensation volume is provided in the compensation gap 43.
  • the additional volume for the exiting from the coupler gap 38 liquid does not have, as in the prior art, are formed by axial and / or radial expansion of the elastic sealing elements, which means a high mechanical load, but arises in a simple manner without additional burden
  • the elastic sealing elements 23,24 by the displacement of the lifting element 22. Since the elastic sealing elements 23,24 are mechanically stressed during operation of the fuel injector, a higher permissible internal pressure of the liquid can be generated in the hydraulic coupler 9 as in the prior art, without to change the spring stiffness of the elastic sealing elements 23,24.
  • FIG 3 shows a hydraulic coupler according to the invention according to a second embodiment.
  • the hydraulic coupler according to Figure 3 differs from the hydraulic coupler according to Figure 2 in that the sealing serving second elastic sealing element 24 has a greater number of shafts 27 than in the first embodiment. In this way, the rigidity of the second elastic sealing element 24 is reduced. Because of the higher number of waves 27 of the second elastic sealing element 24, the lifting element 22 is not guided on the piston rod 19, but on the inner side 20 of the cylinder 16. In addition, only a single throttle element 45 and a single connecting channel 44 is provided, wherein the connecting channel 44 and the filling channel 46 are arranged in alignment with each other and open into each other.
  • the passage channel 29 is designed to be enlarged radially outward compared to the first embodiment, wherein the guide shoulder 30 of the lifting element 22 is disposed on the end facing the bottom of the pot 18 and the inside 20 in contact with the cylinder 16th extends.
  • the diameter of the guide shoulder 30 is slightly smaller on an outer surface 50 than the diameter of the cylinder 16 on the inner side 20.
  • the guide shoulder 30 has on the outer surface 50 at least one axially disposed groove 51 to the liquid volume in the region of the first elastic sealing element 23 and the compensating gap 43 with the remaining liquid volume of the hydraulic coupler 9 to connect.
  • the second elastic sealing element 24 extends from the guide shoulder 30, starting through the through-passage 29 to the head part 31 of the piston rod 19.
  • FIG. 4 shows a hydraulic coupler according to the invention according to a third embodiment.
  • the hydraulic coupler according to Figure 4 differs from the hydraulic coupler of Figure 3 and Figure 2 in that the lifting element 22 is not formed as a separate cover, but as a shoulder 56 of a stepped bellows 53.
  • the stepped bellows 53 which is made of steel for example, acts as an elastic sealing element and consists for example of a first elastic sealing portion 54, which achieves a seal of the hydraulic coupler 9 between the cylinder 16 and the lifting element 22, from the lifting element 22 in the form the shoulder 56 and a second elastic sealing portion 55, which causes a seal of the hydraulic coupler 9 between the lifting element 22 and the head part 31.
  • the stepped corrugated bellows 53 has in the first elastic sealing portion 54 and in the second elastic sealing portion 55 a plurality of annular circumferential waves or folds 27.
  • the first sealing portion 54 is integrally connected, for example, via the shoulder 56 forming the lifting element 22 with the second sealing portion 55, wherein the diameter of the first sealing portion 54, for example, larger is formed as the diameter of the second sealing portion 55th
  • the first elastic sealing portion 54 has analogously to the first elastic sealing element 23 according to the first and second embodiments, for example, a wave number between three and eight and the second elastic sealing portion 55 analogous to the second elastic sealing element 24, for example, a wave number between three and twelve.
  • the lifting element 22 runs, for example, starting from an outer shaft 27 of the first sealing section 54 facing the second sealing section 55 radially inwards and then for connection to an outer shaft 27 of the second sealing section 55 facing the first sealing section 54 in the axial direction.
  • a bearing plate 57 is provided for supporting the spring element 33.
  • the spring element 33 acts on the lifting disk 22 via the bearing disk 57 and in this way generates an overpressure in the interior 39 of the hydraulic coupler 9.
  • the stepped corrugated bellows 53 with the integrated lifting element 22 can be produced more cost-effectively than separate individual parts 22, 23, 24 according to the first and second exemplary embodiments, which still have to be connected to one another in an additional production step.

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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)

Claims (12)

  1. Injecteur de carburant, en particulier pour l'injection directe de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un coupleur hydraulique qui présente un vérin en forme de pot et un piston axialement mobile dans le vérin en forme de pot,
    caractérisé en ce qu'
    on prévoit un élément de levage (22) logé de façon mobile axialement entre le vérin (16) en forme de pot et une pièce de tête (31) en liaison active avec le piston (17), une garniture d'étanchéité étant prévue entre le vérin (16) et l'élément de levage (22) et entre l'élément de levage (22) et la pièce de tête (31).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    on prévoit un premier élément d'étanchéité élastique (23) comme garniture d'étanchéité entre l'élément de levage (22) et le vérin (16) et un deuxième élément d'étanchéité élastique (24) comme garniture d'étanchéité entre l'élément de levage (22) et la pièce de tête (31).
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    on prévoit comme garniture d'étanchéité un boudin ondulé étagé (53) qui présente un premier segment d'étanchéité élastique (54) et un second segment d'étanchéité élastique (55) reliés l'un à l'autre d'un seul tenant par un épaulement (56) conçu en forme d'élément de levage (22).
  4. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    le premier élément d'étanchéité élastique (23) et le second élément d'étanchéité élastique (24) présentent la forme d'un boudin ondulé avec une ou plusieurs ondulations (27).
  5. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce que
    la pièce de tête (31) est reliée de façon active au piston (17) par une tige de piston (19).
  6. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce que
    le premier élément d'étanchéité élastique (23) et le second élément d'étanchéité élastique (24) ou le boudin ondulé étagé (53) sont fabriqués en acier.
  7. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce que
    le premier élément d'étanchéité élastique (23) ou le premier segment d'étanchéité élastique (54) présente un nombre d'ondulations compris entre trois et huit.
  8. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce que
    le deuxième élément d'étanchéité élastique (24) ou le deuxième segment d'étanchéité élastique (55) présente un nombre d'ondulations compris entre trois et douze.
  9. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce qu'
    un élément de ressort (33) est disposé entre l'élément de levage (22) et la pièce de tête (31).
  10. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    l'élément de levage (22) présente un talon de guidage (30) qui est guidé axialement le long de la tige de piston (19) et/ou du vérin (16).
  11. Injecteur de carburant selon la revendication 2,
    caractérisé en ce que
    l'élément de levage (22) présente la forme d'un couvercle.
  12. Injecteur de carburant selon l'une quelconque des revendications 2 ou 3,
    caractérisé en ce qu'
    on prévoit un interstice de couplage (38) entre le vérin (16) et le piston (17) et un interstice de compensation (43) entre l'élément de levage (22) et le vérin (16) en forme de pot, l'interstice de couplage (38) et l'interstice de compensation (43) étant reliés de façon fluidique par au moins un élément d'étranglement (45).
EP20040105090 2003-10-21 2004-10-15 Injecteur de carburant Expired - Fee Related EP1526275B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10348775 2003-10-21
DE10348775 2003-10-21
DE102004015622A DE102004015622A1 (de) 2003-10-21 2004-03-31 Brennstoffeinspritzventil
DE102004015622 2004-03-31

Publications (2)

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DE102012202909A1 (de) * 2012-02-27 2013-08-29 Robert Bosch Gmbh Ventil zum Zumessen von Fluid

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JPH0656162B2 (ja) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 ストロ−ク可変装置
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19962177A1 (de) * 1999-12-22 2001-07-12 Siemens Ag Hydraulische Vorrichtung zum Übertragen einer Aktorbewegung
DE10030232A1 (de) * 2000-06-20 2002-01-17 Siemens Ag Vorrichtung zum Übertragen einer Bewegung mit Spielausgleich
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DE502004002606D1 (de) 2007-02-22

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