EP2102486B1 - Injecteur avec une soupape de commande à compensation de pression axiale - Google Patents

Injecteur avec une soupape de commande à compensation de pression axiale Download PDF

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Publication number
EP2102486B1
EP2102486B1 EP07802985A EP07802985A EP2102486B1 EP 2102486 B1 EP2102486 B1 EP 2102486B1 EP 07802985 A EP07802985 A EP 07802985A EP 07802985 A EP07802985 A EP 07802985A EP 2102486 B1 EP2102486 B1 EP 2102486B1
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EP
European Patent Office
Prior art keywords
valve
chamber
valve piston
sleeve
pressure
Prior art date
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Active
Application number
EP07802985A
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German (de)
English (en)
Other versions
EP2102486A1 (fr
Inventor
François Rossignol
Stephan Amelang
Friedrich Howey
Olivier Charvet
Tony Dumont
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
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Robert Bosch GmbH
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Publication of EP2102486A1 publication Critical patent/EP2102486A1/fr
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Publication of EP2102486B1 publication Critical patent/EP2102486B1/fr
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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves

Definitions

  • the invention relates to an injector according to the preamble of claim 1.
  • the DE 103 53 169 A1 describes a common rail injector with a control valve for blocking and opening a fuel drain path from a control chamber.
  • a piezoelectric actuator is provided, which acts via a translation piston in the axial direction on a valve piston adjusting.
  • the fuel pressure can be influenced within a control chamber, the control chamber is supplied via a pressure channel with inlet throttle and an additional channel with fuel from a high-pressure fuel storage.
  • a nozzle needle is moved between an open position and a closed position, wherein the nozzle needle in its open position releases the fuel flow into the combustion chamber of an internal combustion engine. Since the known control valve is not pressure balanced in the axial direction, high actuating forces for opening the control valve are required.
  • the known control valve has as an adjustable valve element on an axially displaceable sleeve, which only is acted upon in the radial direction with fuel pressure from a high pressure area. Due to the use of a pressure balanced control valve only small actuating forces for opening the control valve are required, so that the setting task is performed in the known injector of an electromagnetic drive.
  • the overall configuration of the injector would have to be changed. In particular, the low-pressure chamber would have to be laid much further in the direction of the control chamber in the piezo-actuated injector.
  • the invention is therefore based on the object to propose an injector with an alternatively designed axially-pressure balanced valve, which is particularly suitable for the use of an electromagnetic actuator.
  • the invention is based on the idea, instead of an axially adjustable sleeve an adjustable in the axial direction Provide valve piston for opening and closing the control valve.
  • the valve piston (bolt) is disposed within a valve chamber which is hydraulically connected to the control chamber, so that when the control valve is open fuel through a fuel drain path from the control chamber via the valve chamber can flow to a low-pressure chamber. When the control valve is closed, the fuel drain path is blocked.
  • the valve piston is not guided according to the invention directly in a throttle plate, but in a sleeve which is received in the valve chamber.
  • a spring is provided, on the one hand on the valve piston, in particular on the underside of a valve head and on the other hand on the sleeve, in particular on the end face of the sleeve, supported. So that on the valve piston in the axial direction no or only minimal pressure forces act, so it is a pressure balanced in the axial direction control valve, it is provided that low pressure is applied to both end faces of the valve piston and that in the axial direction acted upon by low pressure (projection) Areas of the valve piston are equal on both sides.
  • valve seat facing the end face of the valve piston limits the low-pressure chamber or is directly connected hydraulically with this, is automatically low pressure on the end face.
  • the application of this (upper) end face opposite (lower) end face with low pressure can be realized, for example, that at the end facing away from the valve seat end of the valve piston, a connecting channel is performed, the immediately adjacent to this end face area hydraulically connected to the low pressure area of the injector.
  • fuel pressures in a range between approximately 0 and 10 bar prevail, whereas the fuel flowing from a high-pressure fuel reservoir into the injector is under a pressure in a range between approximately 1800 and 2000 bar.
  • the inventive design of the injector can be easily to the from DE 103 53 169 A1 transferred in this case, preferably in place of an additional fuel supply to the valve chamber, a low-pressure connection line can be provided to supply the nozzle needle facing the end face of the valve body with low pressure.
  • a piezo actuator instead of a piezo actuator, an electromagnetic drive can be used.
  • the sleeve is received with radial play in the valve chamber, so that pressurized fuel in the valve chamber exerts a radially inwardly acting force on the sleeve, so that a widening of the guide clearance between the sleeve and the valve piston avoided during operation and thus leakage losses are minimized.
  • the hydraulic connection between the control chamber and the valve chamber is realized via a drain passage with outlet throttle, wherein the cross sections of the outlet throttle and in which the control chamber supplying pressure channel arranged inlet throttle are coordinated such that when the control valve is open net fuel outflow results in the low pressure space.
  • the drainage channel opens into the valve chamber in a region between the sleeve and the valve chamber inner wall. This makes it possible to integrate the flow channel exclusively in a arranged between the control chamber and the valve chamber throttle plate.
  • the injector is particularly suitable for the use of a solenoid actuator, since due to the axial pressure balance of the control valve comparatively low actuating forces must be applied.
  • the electromagnetic drive has at least one electromagnet (coil) and at least one armature plate interacting therewith, the armature plate having to be operatively connected to the valve piston. Since in an electromagnetic drive no minimum pressure for acting on a translation piston of a piezo actuator must be present, the low pressure level can be lower, whereby the return system for the fuel can be designed more cost-effective overall.
  • the anchor plate is operatively connected to a push rod, for example, integrally formed therewith, wherein the armature plate facing away from the free end of the push rod on the valve piston, in particular the valve piston head, is centered.
  • the stroke of the electromagnetic drive can be adjusted via the variation of the length of the push rod.
  • valve piston To realize the centering of the push rod on the end face of the valve piston a concave-convex pairing between valve piston and push rod is advantageously realized, wherein preferably the push rod in the region of its free end convex and the end face of the valve piston is designed concave accordingly.
  • a weak biasing spring is preferably provided, which biases the armature plate and thus the push rod in the direction of the valve piston.
  • the spring force must be such that it is less than the spring force of the spring within the valve chamber, which presses the valve piston in the opposite direction in its valve seat.
  • the invention is provided in a further development that the push rod is guided within a stop sleeve, wherein the stop sleeve is received within the electromagnet of the solenoid drive and has a stop surface for the anchor plate.
  • valve chamber is limited on its side facing the control chamber of a throttle plate, the throttle plate thus forms the bottom surface of the valve chamber on which the guide sleeve is supported within the valve chamber.
  • this throttle plate is advantageously introduced and the drainage channel with outlet throttle from the control chamber.
  • a connecting channel which connects the nozzle needle facing the end face of the valve piston with the low pressure region of the injector, so preferably at least approximately the same (low) pressure prevails on both end faces of the valve piston.
  • a common rail injector 1 is shown.
  • the injector 1 has an injector body 2, a nozzle body 3 shown only in sections, and a valve body 4 lying against the injector body 2 and a throttle plate 5 arranged between the valve body 4 and the nozzle body 3.
  • a guide bore 7 is formed, in which an elongated nozzle needle 8 is guided axially movable.
  • the nozzle needle has a closing surface 10 with which it can be brought into tight contact with a needle seat 11 formed inside the nozzle body 3.
  • the nozzle needle 8 is biased by means of a biasing spring, not shown, in the direction of its closed position.
  • the upper end face 14 of the nozzle needle 8 protrudes into a control chamber 15, which is bounded on the opposite side of the end face 14 of the throttle plate 14.
  • the control chamber 15 is supplied via a pressure channel 16 with inlet throttle 17 and a connection pocket 20 in the valve body 4 with fuel under high pressure from a supply line 18, wherein the supply line 18 is connected to a fuel high-pressure accumulator, not shown, which is pressurized, for example via a radial piston pump ,
  • the supply channel 18 is simultaneously connected via a connecting bore 19 within the throttle plate 5 with the control chamber 15 radially enclosing the pressure chamber 13.
  • a connecting bore 19 within the throttle plate 5 with the control chamber 15 radially enclosing the pressure chamber 13.
  • control chamber 15 is hydraulically connected to a valve chamber 23 of a control valve 24 within the valve body 4.
  • the drainage channel 21 is part of a fuel drainage path from the control chamber to a arranged in the plane above the valve chamber 23 low-pressure space 25. From there, the fuel can flow through a return line, not shown.
  • a closing force is exerted on the nozzle needle 8 by a biasing spring, not shown, at the same time is exercised by the pressure prevailing in the control chamber 15 fuel pressure on the end face 14 of the nozzle needle 8, a closing force on this.
  • These closing forces act on the basis of the action of fuel pressure on a formed on the nozzle needle 8, not shown, step surface resulting opening force.
  • the control valve 24 is in a closed position and the fuel drain from the control chamber 15 is locked in the low pressure chamber 25, the stationary force acting on the nozzle needle 8 closing force is greater than the opening force, which is why the nozzle needle 8 then assumes its closed position.
  • the control valve 24 is then opened, fuel flows out of the control chamber and the nozzle needle 8 is lifted from its needle seat 11.
  • the flow cross sections of the inlet throttle 17 and the outlet throttle 21 are matched to one another such that the inflow through the pressure channel 16 is weaker than the outflow through the outlet channel 21 and thus results in a net outflow of fuel when the control valve 24 is open.
  • the resulting pressure drop in the control chamber 15 causes the amount of the closing force falls below the amount of the opening force and the nozzle needle 8 lifts off the needle seat 11.
  • an axially displaceable valve piston 26 is arranged, which is guided in a sleeve 27 with the least possible backlash.
  • the sleeve 27 is received with radial clearance within the valve chamber 23.
  • a helical spring 29 is arranged, which is supported on the one hand on an upper end face 30 of the sleeve 27 and on the other hand on a lower annular shoulder 31 of the valve piston head 28 and so the valve piston 26 in the plane of the drawing in the direction of low pressure space 25 on biases a valve seat 32.
  • the sleeve 27 is sealingly pressed on a bottom surface 33 of the valve chamber 23, the bottom surface 33 being formed by a surface of the throttle plate 5.
  • the cross-sectional area of the valve piston 26 sealed at the valve seat 32 corresponds to the cross-sectional area of the valve piston 26 guided inside the sleeve 27.
  • the diameter of the valve seat 32 corresponds to the inner diameter of the sleeve 27.
  • valve piston 26 Due to the at least approximate identity of the acted upon by low pressure surfaces of the valve piston, the valve piston is pressure balanced in the axial direction.
  • the drain passage 21 from the control chamber 25 opens into a pocket 37 in the valve body 4.
  • the pocket 37 is connected to an annular space 38 between sleeve 27 and valve chamber wall 39, so that fuel from the control chamber 15 can flow into the valve chamber 23.
  • the annular space 38 ensures that the guide clearance between valve piston 26 and sleeve 27 does not expand, so that leakage losses are minimized.
  • the fuel pressure within the valve chamber 23 ensures in that, in addition to the axial spring force of the helical spring 29, an axial force acts on the sleeve 27 in the direction of the throttle plate 5, so that the sleeve 27 sealingly bears against the bottom surface 33. Any leakage losses are removed via the connecting line 35.
  • an electromagnetic actuator 40 is arranged with an electromagnet 41.
  • the electromagnet 41 is received in a bore 42, which guides the electromagnet 41 over its inner diameter.
  • the electromagnet 41 is biased by a spring element 43 axially against the lower side in the drawing plane of the injector body 2.
  • a stepped bore 44 is provided, the axis of symmetry of which corresponds to the axis of symmetry of the valve piston 26.
  • a first shoulder 45 of the stepped bore 44 limits the axial mobility of an armature plate 46, which cooperates with the electromagnet 41.
  • a push rod 47 Centrally supported on the armature plate 46 and in a receiving bore of the armature plate 46 is a push rod 47 which transmits a movement of the armature plate 45 to the valve piston 26 and thus controls the movement of the valve piston 26.
  • the push rod 47 is centered with its convex free end 48 on the concave end face 34 of the valve piston 26.
  • the push rod 47 is guided in a stop sleeve 49 near the anchor plate 46, wherein the stop sleeve 49 is received in a central passage opening of the electromagnet 41.
  • the stop sleeve 49 has on its upper end face a stop surface 50 for abutment of the armature plate 46 upon energization of the electromagnet 41.
  • the armature plate 46 is pressed via a weak biasing spring 51, which is supported on the valve body 2, via the push rod 47 against the valve piston 26, so that these parts are in contact.
  • the contacting of the electromagnet 41 is guided via a housing part 52 in the upper plane in the drawing injector body to be able to lead the contact with the plug, not shown on the injector head, not shown.
  • Fig. 3 the installation situation of the anchor plate 46 is shown.
  • the armature plate 46 is received between the injector body 2 and the valve body 4.
  • the distance a between the valve body 4 and the underside of the armature plate 46 is the armature stroke when the electromagnet 41 is energized.
  • the distance b between the upper side of the armature plate 46 and the injector body 2 is the so-called overtravel. Since the push rod 47 and the anchor plate 46 at the closing time still have kinetic energy, they are moved in the direction of flight F until the anchor plate 46 abuts against the first shoulder 45 of the stepped bore 44.
  • This additional route is referred to as overrunning b and should be designed as low as possible to spend the control valve as soon as possible after an operation in a state of rest.
  • Fig. 4 shows a one-piece design between anchor plate 46 and push rod 47.
  • the armature stroke can be adjusted by a targeted grinding in the length of the push rod 47.

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

Claims (10)

  1. Injecteur pour l'injection de carburant dans des chambres de combustion de moteurs à combustion interne, notamment injecteur à rampe commune, comprenant une soupape de commande (24) qui comprend un piston de soupape (26) qui peut être déplacé dans la direction axiale au moyen d'un actionneur (40), de sorte qu'une voie d'écoulement de carburant conduisant d'une chambre de commande (15) à un espace basse pression (25) puisse être libérée ou bloquée, l'ouverture et le blocage de la voie d'écoulement de carburant influençant la pression dans la chambre de commande (15), qui peut être alimentée en carburant par le biais d'un canal de pression (16), de sorte qu'un pointeau de buse (8) connecté fonctionnellement à la chambre de commande (15) puisse être déplacé entre une position d'ouverture libérant le flux de carburant et une position de fermeture,
    caractérisé en ce que
    le piston de soupape (26), au niveau des deux côtés frontaux duquel s'applique une basse pression, est disposé dans une chambre de soupape (23) connectée hydrauliquement à la chambre de commande (15), et est guidé à l'intérieur d'une douille (27) reçue dans la chambre de soupape (23), et en ce qu'il est prévu dans la chambre de soupape (23) un ressort (29) s'appuyant à une extrémité contre la douille (27) et à l'autre extrémité contre le piston de soupape (26), qui presse le piston de soupape (26) sur un siège de soupape (32) et la douille (27) sur une surface de fond opposée (33), et en ce que le diamètre du piston de soupape à l'intérieur de la douille (27) correspond au diamètre de piston de soupape actif sur le siège de soupape (32).
  2. Injecteur selon la revendication 1, caractérisé en ce que la douille (27) est reçue avec un jeu radial dans la chambre de soupape (23).
  3. Injecteur selon la revendication 2, caractérisé en ce que la chambre de commande (18) est connectée par le biais d'un canal d'écoulement (21) à un étranglement d'écoulement (22) à la chambre de soupape (23), et en ce que le canal d'écoulement (21) débouche dans une région entre une paroi interne de chambre de soupape (39) et la douille (27) dans la chambre de soupape (23).
  4. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur (40) est un entraînement électromagnétique avec au moins un électroaimant (41) et avec au moins une plaque d'induit (46) coopérant avec celui-ci.
  5. Injecteur selon la revendication 4, caractérisé en ce que la plaque d'induit (46) est connectée fonctionnellement à une tige poussoir (47), dont l'extrémité libre (48) opposée à la plaque d'induit (46) est centrée sur l'extrémité du piston de soupape (26) tournée vers la plaque d'induit (46).
  6. Injecteur selon la revendication 5, caractérisé en ce que le centrage est réalisé par un appariement concave-convexe entre le piston de soupape (26) et la tige poussoir (27).
  7. Injecteur selon l'une quelconque des revendications 4 à 6, caractérisé en ce que la plaque d'induit (42) est sollicitée par une force de ressort par le biais d'un ressort de précontrainte (51) dans la direction du piston de soupape (26), la force de ressort du ressort de précontrainte (51) étant inférieure à la force de ressort du ressort (29) à l'intérieur de la chambre de soupape.
  8. Injecteur selon l'une quelconque des revendications 5 à 7, caractérisé en ce que l'électroaimant (41) de l'entraînement électromagnétique est traversé par une douille de butée (49) avec une surface de butée (56) pour la plaque d'induit (42), la tige poussoir (47) étant guidée à l'intérieur de la douille de butée (49) de manière déplaçable axialement.
  9. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que la surface de fond (33) de la chambre de soupape (23) est formée par une plaque d'étranglement (5).
  10. Injecteur selon la revendication 9, caractérisé en ce qu'un canal de connexion (35) est pratiqué à l'intérieur de la plaque d'étranglement (5), lequel fait partie d'une conduite de connexion qui alimente le côté frontal du piston de soupape (26) opposé au siège de soupape (32) en basse pression, notamment qui le relie hydrauliquement à l'espace basse pression (25) et/ou à une conduite de retour.
EP07802985A 2006-10-25 2007-08-29 Injecteur avec une soupape de commande à compensation de pression axiale Active EP2102486B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006050163A DE102006050163A1 (de) 2006-10-25 2006-10-25 Injektor mit axial-druckausgeglichenem Steuerventil
PCT/EP2007/058968 WO2008049669A1 (fr) 2006-10-25 2007-08-29 Injecteur avec une soupape de commande à compensation de pression axiale

Publications (2)

Publication Number Publication Date
EP2102486A1 EP2102486A1 (fr) 2009-09-23
EP2102486B1 true EP2102486B1 (fr) 2010-11-10

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Application Number Title Priority Date Filing Date
EP07802985A Active EP2102486B1 (fr) 2006-10-25 2007-08-29 Injecteur avec une soupape de commande à compensation de pression axiale

Country Status (8)

Country Link
US (1) US8113176B2 (fr)
EP (1) EP2102486B1 (fr)
JP (1) JP2010507746A (fr)
CN (1) CN101529081B (fr)
AT (1) ATE487874T1 (fr)
BR (1) BRPI0717354B1 (fr)
DE (2) DE102006050163A1 (fr)
WO (1) WO2008049669A1 (fr)

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US8622475B2 (en) 2008-12-15 2014-01-07 Bae Industries, Inc. Linear recliner assembly with threaded linear drive rod and rotatably engaged gear stop
DE102009027709A1 (de) * 2009-07-15 2011-01-20 Robert Bosch Gmbh Kraftstoffeinspritzventil
DE102009028979A1 (de) * 2009-08-28 2011-03-03 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine
DE102010031497A1 (de) * 2010-07-19 2012-01-19 Robert Bosch Gmbh Kraftstoffinjektor mit hydraulischer Kopplereinheit
AT510462B1 (de) 2010-09-22 2014-04-15 Bosch Gmbh Robert Verfahren zum überprüfen und instandsetzen eines kraftstoffinjektors
DE102011075750B4 (de) * 2011-05-12 2021-02-11 Vitesco Technologies GmbH Verfahren zum Ermitteln einer Position eines Verschlusselements eines Einspritzventils für eine Brennkraftmaschine
FR2988140B1 (fr) * 2012-03-15 2016-02-05 Bosch Gmbh Robert Soupape de regulation de pression d'accumulateur haute pression de carburant de moteur a combustion interne
US10077748B2 (en) 2014-12-23 2018-09-18 Cummins Inc. Fuel injector for common rail
CN106762289A (zh) * 2017-01-18 2017-05-31 哈尔滨工程大学 蓄压孔板式电控喷油器
CN109595108B (zh) * 2018-12-03 2023-09-01 成都威特电喷有限责任公司 紧凑型高压燃油喷射装置

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US20100071665A1 (en) 2010-03-25
CN101529081A (zh) 2009-09-09
BRPI0717354A2 (pt) 2014-01-21
DE102006050163A1 (de) 2008-04-30
DE502007005634D1 (de) 2010-12-23
ATE487874T1 (de) 2010-11-15
CN101529081B (zh) 2011-09-07
US8113176B2 (en) 2012-02-14
JP2010507746A (ja) 2010-03-11
BRPI0717354B1 (pt) 2019-04-09
EP2102486A1 (fr) 2009-09-23
WO2008049669A1 (fr) 2008-05-02

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