EP2229527B1 - Soupape de commande pour injecteurs - Google Patents

Soupape de commande pour injecteurs Download PDF

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Publication number
EP2229527B1
EP2229527B1 EP08859206A EP08859206A EP2229527B1 EP 2229527 B1 EP2229527 B1 EP 2229527B1 EP 08859206 A EP08859206 A EP 08859206A EP 08859206 A EP08859206 A EP 08859206A EP 2229527 B1 EP2229527 B1 EP 2229527B1
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EP
European Patent Office
Prior art keywords
closing element
sleeve
switching valve
pressure
face
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.)
Not-in-force
Application number
EP08859206A
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German (de)
English (en)
Other versions
EP2229527A1 (fr
Inventor
Matthias Burger
Hans-Christoph Magel
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2229527A1 publication Critical patent/EP2229527A1/fr
Application granted granted Critical
Publication of EP2229527B1 publication Critical patent/EP2229527B1/fr
Not-in-force 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
    • 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a switching valve for injectors, in particular for fuel injectors, according to the preamble of claim 1.
  • Fuel injectors are used to supply fuel to combustion chambers of an internal combustion engine.
  • the fuel is injected under high pressure into the combustion chambers.
  • high-pressure accumulator injection systems are used in which the injection pressure is independent of the speed and load of the internal combustion engine.
  • the pollutants resulting from the combustion can be reduced.
  • a significant increase in the injection pressure is necessary.
  • Fuel injectors which can be used at the required pressures, are leak-free. For this purpose, a low-pressure stage is dispensed with. Due to the absence of the low-pressure stage, however, only small needle closing forces are available. This leads to steep maps and thus to a poor Kleinstmengenmen. However, this disadvantage can be compensated with very fast switching valves.
  • a switching valve for a fuel injector with a hydraulic damping device is off DE 196 50 865 A1 known.
  • an armature disc and a damping sleeve are guided axially movable on an anchor bolt.
  • the damping sleeve has an end-side annular chamber into which an annular shoulder formed on the armature disk engages during an opening movement of the armature pin.
  • a control valve for a fast-switching fuel injection valve is still off DE 10 2007 028 485 known.
  • a pressure chamber is limited by a control sleeve which is movably mounted in its longitudinal direction.
  • the control sleeve has on a front side on a sealing surface, with which it cooperates with a valve seat which is formed on a valve body.
  • a recess in the pressure chamber facing side of the valve body is formed.
  • the control sleeve and the recess in the valve body are formed so that a deformation of the control sleeve and valve body by the pressure in the pressure chamber to no or only very little movement between the valve seat and the sealing surface of the control sleeve leads.
  • fast-switching valves have the disadvantage that due to a bounce characteristic map ripples occur.
  • On the one hand results in a bouncing of the closing element due to a hard stop in conjunction with a fast closing element.
  • the hard hit results from the bouncing of metal on metal.
  • these bumpers which occur when the closing element hits, have a negative influence on the function of the fuel injector and generally lead to large lift / stroke spreads.
  • solenoid-operated switching valves a squish gap is formed at the upper stroke stop between armature and magnet, which dampens the stop and thus reduces bouncing.
  • such a nip can not be attached to the valve seat due to its sealing functions to reduce the impact of the closing element in the valve seat.
  • An inventively designed switching valve for injectors in particular for fuel injectors, comprises a closing element with which a control chamber for actuating an injection valve member is pressure-relieved.
  • the closing element is driven by a magnetic actuator comprising a magnet assembly and an armature.
  • the closing element is connected to a stop element such that the stop element and the closing element enclose a damping space, wherein the damping space is filled with liquid, the amount of which remains substantially constant during a movement of the closing element, so that closing element and stop element move together.
  • the pressure in the damping chamber first decreases. Due to the decreasing pressure, a force acts on the stop element, by means of which the stop element is moved together with the closing element.
  • the volume of the damping chamber does not change with a constant amount of liquid. In this way, the position of the stop element to the closing element remains unchanged.
  • the pressure in the damping chamber initially increases.
  • the stop element is moved with the closing element.
  • striking forms between the stop member and a stop surface of a nip, through which the movement is damped and a large part of the stop pulse is received.
  • the movement of the closing element is damped by the increasing in a swinging pressure in the damping chamber. Bouncing or valve seat wear is prevented, since a large part of the impact pulse has already been destroyed by the abutment of the stop element.
  • the stop element is designed in the form of a sleeve. If the stop element is designed in the form of a sleeve, it is preferred if the closing element is guided in a sleeve, wherein between a pointing in the direction of the magnet assembly upper end surface of the sleeve and one of the upper end surface of the sleeve opposite end face of the closing element of the damping chamber is formed , In order to adapt the position of the stop element to the position of the closing element when the switching valve is closed, it is preferred if the upper end face of the sleeve is closed by an annular edge such that the inside of the annular edge and the outside of the end face of the closing element when closing the switching valve and form an annular gap with the switching valve closed.
  • the annular gap acts as a throttle relative to the surrounding space, so that the pressure in the damping chamber is higher than the surrounding pressure.
  • a complete filling of the damping chamber is ensured with liquid.
  • a liquid equalization which is necessary, for example, if, for example, by seat wear first changes the position of the closing element to the stop element. In this way, the function of the stop element is always guaranteed. For example, liquid can flow out via the annular gap if a smaller volume of the damping chamber is required to compensate for the positions.
  • Another advantage of the inventive construction of the switching valve is that the hydraulic damping force is only a function of the anchor speed. Unlike a nip, the armature stroke has no effect on the damping force. In this way, even with a lift drift, e.g. can be due to a valve seat wear, ensures that the valve closes at any time.
  • the sleeve is movable relative to the closing element in the axial direction.
  • the damper acts only when closing ⁇ en, but not when opening the valve. In this way, an unwanted delaying the valve opening movement is prevented.
  • the opening movement of the closing element increases the volume of the damping chamber. This reduces the pressure in the damping chamber. Since the sleeve is movable relative to the closing element in the axial direction, the sleeve can initially move together with the closing element, so that the volume of the damping chamber can remain substantially constant and no force must be overcome, due to a reduced pressure in the damping chamber on the closing element acts. A quick opening of the switching valve is thus possible.
  • a plate-shaped extension is formed on the sleeve and a spring element is with one side on the plate-shaped extension of the Sleeve and placed against the anchor with the other side.
  • the spring element is preferably designed as a compression spring coil spring.
  • the closing element is preferably sleeve-shaped and guided on a guide pin.
  • an annular space is formed on the guide pin between an upper and a lower guide of the closing element.
  • the annular space serves as a leakage collecting space of liquid which flows as leakage through the lower guide. Since the leakage gap between the lower guide and the closing element is in hydraulic communication with the drainage channel from the control chamber, the leakage collecting space is filled with liquid.
  • the upper guide and the lower guide are each formed as leakage gaps, so that the upper guide and the lower guide act as a pressure divider and the pressure in the annulus by the gap of the upper guide and the lower guide is adjustable. Due to the upper guide, the pressure in the leakage chamber is higher than in the low pressure region. Due to the throttle also acting as lower guide but lower than the system pressure. When the injector is used as a fuel injector in high-pressure accumulator injection systems, system pressures of well over 1000 bar occur.
  • the annular space which serves as a leakage collecting space, is advantageously connected via a channel in the closing element with the damper space between the upper end face of the sleeve and the end face of the closing element.
  • liquid can flow from the leakage collecting space into the damping chamber.
  • the damping chamber is always filled with liquid, wherein the liquid flows in through the channel and can flow out of the damping chamber along the annular gap.
  • Another advantage is that the pressure of the liquid in the damping chamber is above the boiling pressure and the liquid is thus gas-free. In this way, the damping function of the damping chamber is ensured.
  • the closing element is sleeve-shaped and guided on the guide pin, the closing element preferably has an annular sealing surface or Sealing edge on and over its entire length constant inner diameter. Since the under system pressure fuel acts only on the inside of the closing element, occur through the constant inner diameter only radial compressive forces. As a result, the closing element is pressure balanced and no pressure forces to open or close the switching valve must be overcome. As a result, even low switching forces are sufficient to allow a quick switching of the switching valve.
  • the single FIGURE shows a fuel injector with inventively designed switching valve.
  • the single FIGURE shows a schematic representation of a fuel injector with an inventively designed pressure-balanced switching valve.
  • a fuel injector 1 comprises an injection valve member 3, with which at least one, not shown here injection port for injecting fuel into a combustion chamber of an internal combustion engine can be released or closed.
  • the injection valve member 3 is guided in a valve piece 5 and delimited with an upper end face 7 a control chamber 9.
  • the control chamber 9 is filled via an inlet throttle 11 with fuel under system pressure.
  • the inlet throttle 11 connects the control chamber 9 with an annular space 13, which surrounds the valve piece 5 and in turn is connected to a high-pressure accumulator, not shown here, via an inlet channel 15.
  • the control chamber 9 In order to release the at least one injection opening, the control chamber 9 is depressurized.
  • a switching valve 17 opens, whereby a connection from a flow channel 19 is released to a fuel return line 21 and fuel can flow out of the control chamber 9.
  • the pressure in the control chamber 9 decreases and the injection valve member 3 rises from its valve seat and releases the injection port.
  • a throttle element 23 is formed.
  • the switching valve closes the connection from the outlet channel 19 to the return line 21.
  • fuel under system pressure flows into the control chamber 9, the pressure in the control chamber 9 increases. Due to the increasing pressure force, the injection valve member 3 is placed back in his seat and closes the at least one injection port.
  • the closing movement of the injection valve member 3 is supported by a spring element 25.
  • the spring element 25 is preferably designed as a helical spring compression spring.
  • valve piece 5 in which the injection valve member 3 is guided, is mounted with a valve clamping nut 27 in the injector 29.
  • the switching valve 17, with which the opening and closing of the fuel injector for injecting fuel into the combustion chamber of the internal combustion engine is controlled, comprises a closing element 31.
  • the closing element 31 has a sealing edge 33, which is placed in a valve seat 35 for closing.
  • the switching valve 17 is pressure balanced.
  • the sealing edge 33 is annular.
  • the closing element 31 has a constant inner diameter 37. In this way, the pressure of the under system pressure fuel acts only in the radial direction on the closing element 31. Thus act on opposite surfaces on the closing element 31 always only the same pressure forces.
  • a guide pin 39 In order to avoid that the closing element 31 tilts or slips in the radial direction, this is guided on a guide pin 39.
  • the guide pin ends with a lower end face 41 above the drainage channel 19 and thus delimits, together with the closing element 31, a pressure chamber 43. With the side opposite the pressure chamber 43, the guide pin 39 rests against the injector housing. A displacement of the guide pin 39 is avoided in that this is pressed with a spring element 45 against the injector.
  • the spring element 45 is preferably designed as a compression spring coil spring. With one side, the spring element 45 acts against an end face on an extension 47 of the guide pin and with another side on the closing element 31st
  • the spring element 45 also serves as a closing spring. By the spring force of the spring element 45 on the closing element 31, this is placed in the valve seat 35.
  • the closure member 31 is further connected to an armature 49.
  • the armature 49 cooperates with a magnet assembly 51 through which the switching valve 17 is actuated.
  • the magnet assembly 51 generally includes a solenoid 53 and a core 55 that surrounds the coil 53.
  • the switching valve 17 To start the injection process, the switching valve 17 must be opened.
  • the coil 53 is energized.
  • a magnetic field is formed by which the armature 49 is attracted and moves in the direction of the magnet assembly 51. Since the armature 49 is connected to the closing element 31, this also pulls the closing element 31 upwards.
  • the closing element 31 rises from the valve seat 35 and releases a connection from the outlet channel 19 via a low-pressure chamber 57 into the return line 21.
  • a bouncing of the armature 49 is thereby avoided that between the armature 49 and the magnet assembly 51, a nip 59 is formed.
  • the nip 59 is filled with fuel contained in the low-pressure chamber 57. The fuel in the nip 59 is compressed, thus damping the movement of the armature 49.
  • the injection valve member 3 To end the injection process, the injection valve member 3 must be put back in its seat to close the injection port.
  • the switching valve 17 must first close the connection from the outlet channel 19 into the return line 21.
  • the energization of the coil 53 is terminated, the magnetic field coincides.
  • the spring force of the spring element 45 which acts on the closing element 31, the closing element 31 is moved in the direction of the valve seat 35 until the sealing edge 33 is in the valve seat 35.
  • the inlet throttle 11 1 stationary fuel flows under system pressure from the annular space 13 into the control chamber 9.
  • the pressure in the control chamber 9 increases and thus also acting on the upper end face 7 of the injection valve member 3 compressive force.
  • Due to the increasing pressure force on the upper end face 7 of the injection valve member 3, the injection valve member 3 is placed back in his seat and thus closes the at least one injection port.
  • the injection process is finished.
  • the closing element 31 is enclosed by a sleeve 61.
  • an upper end face 63 is formed on the sleeve 61.
  • the upper end surface 63 of the sleeve 61 is opposite to an end face 65 of the closing element 31, so that between the upper end face 63 of the sleeve 61 and the end face 65 of the closing element 63, a gap is formed.
  • the upper end face 63 of the sleeve 61 is further closed by an annular edge 67 such that between the inside of the annular edge 67 and the outside of the end face 65 of the closing element 31, an annular gap 69 is formed.
  • a damping chamber 71 is enclosed between the upper end face 63 of the sleeve 61 and the end face 65 of the closing element 31 and the annular edge 67.
  • the damping chamber 71 is filled with liquid.
  • the closing movement of the sleeve 61 is supported by a spring element 83.
  • the spring element 83 is preferably designed as a helical spring compression spring and acts as a positioning spring for the sleeve 61.
  • the spring element 83 acts with one side on an extension 85 on the sleeve 61 and the other side on the armature 49. In its basic position is the Sleeve 61 on the valve piece 5.
  • a lower guide 73 and an upper guide 75 is formed on the guide pin 39.
  • the closing member 31 is guided along the upper guide 75 and the lower guide 73.
  • an annular space 77 is formed between the upper guide 75 and the lower guide 73.
  • the annular space 77 serves as a leakage collecting space. Due to the high pressure of the fuel in the pressure chamber 43, the pressure of the fuel in the annular space 77 is higher than in the low pressure chamber 57.
  • the annular space 77 is connected via a channel 79 with the damping chamber 71 is connected. Through the channel 79 fuel flows into the damping chamber 71. This ensures that the damping chamber 71 is always filled with liquid. Due to the higher pressure of the liquid in the annular space 77, the formation of gas bubbles in the damping chamber 71 is avoided at the same time.
  • the channel 79 is preferably made by laser drilling or by erosion.
  • the damping effect of the damping chamber 71 is not ineffective due to the hydraulic connection of the annular space 77 with the damping chamber 71 via the channel 79, it is necessary that the throttle effect on the lower guide 73 and the upper guide 75 is much smaller than the throttling on Annular gap 69.
  • the sleeve 61 is movable along a guide 81 relative to the closing element 31 in the axial direction.
  • Advantage of this embodiment is that the damping chamber 71 only acts as a damper when closing the switching valve 17 and not also when opening the switching valve 17. This prevents unwanted delaying the valve opening movement.
  • the switching valve 17 is opened, firstly the closing element 31 moves in the direction of the magnet assembly 63. This leads to an enlargement of the volume of the damping space 71, since the end face 65 of the closing element 31 moves out of the damping space 71. This leads to a pressure drop in the damping chamber 71. Since the sleeve is movable, it is initially also moved in the direction of the magnet assembly 51. The decreasing pressure in the damping chamber 71 does not lead to a delay of the opening movement of the closing element but to a movement of the sleeve 61st
  • the residual stroke from which the movement of the closing element 31 is damped before the sealing edge 33 strikes the valve seat 35, results from the height h 1 of the sleeve 61 and the distance h 2 between the end face 65 of the closing element 31 and the sealing edge 33.
  • the two dimensions h 1 and h 2 can be very precisely measured, ground and manufactured.
  • the Studentsdeckungshack resulting from the difference of the height h 1 of the sleeve 61 and the distance h 2 between the end face 65 of the closing element 31 and the sealing edge 33, and by which the residual stroke is defined, can be measured before assembly of the injector 1 and if necessary, be precisely set by selection groups.
  • Another advantage of the switching valve 17 designed according to the invention is also that the volume of the damping chamber 71 has no influence on the function, since the liquid, when used as fuel injector thus the fuel at the low pressure level in the return can be considered incompressible.

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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)
  • Magnetically Actuated Valves (AREA)

Claims (11)

  1. Soupape de commutation pour injecteurs, notamment pour injecteurs de carburant (1), comprenant un élément de fermeture (31) avec lequel un espace de commande (9) pour l'actionnement d'un organe de soupape d'injection (3) peut être détendu en pression, l'élément de fermeture (31) étant commandé par un actionneur magnétique, comprenant un module magnétique (51) et un induit (49), l'élément de fermeture (31) étant connecté à un élément de butée de telle sorte que l'élément de butée et l'élément de fermeture (31) entourent un espace d'amortissement (71), l'espace d'amortissement (71) étant rempli de liquide, caractérisée en ce que dans le cas d'un mouvement de l'élément de fermeture (31), la quantité de liquide dans l'espace d'amortissement (71) reste essentiellement constante, de telle sorte que l'élément de fermeture (31) et l'élément de butée se déplacent en commun.
  2. Soupape de commutation selon la revendication 1, caractérisée en ce que l'élément de butée est réalisé sous forme de douille (61).
  3. Soupape de commutation selon la revendication 2, caractérisée en ce que l'élément de fermeture (31) est guidé dans la douille (61), l'espace d'amortissement (71) étant réalisé entre une face frontale supérieure (63) de la douille (61) tournée dans la direction du module magnétique (51) et une face frontale (65) de l'élément de fermeture (31) opposée à la face frontale supérieure (63) de la douille (61).
  4. Soupape de commutation selon la revendication 3, caractérisée en ce que la face frontale supérieure (63) de la douille (61) est fermée par une arête annulaire (67) de telle sorte que le côté intérieur de l'arête annulaire (67) et le côté extérieur de la face frontale (65) de l'élément de fermeture (31) constituent une fente annulaire (69) lors de la fermeture de la soupape de commutation (17) et lorsque la soupape de commutation (17) est fermée.
  5. Soupape de commutation selon l'une quelconque des revendications 1 à 4, caractérisée en ce que la douille (61) peut être déplacée dans la direction axiale par rapport à l'élément de fermeture (31).
  6. Soupape de commutation selon la revendication 5, caractérisée en ce qu'un élargissement (85) en forme de plateau est réalisé sur la douille (61) et un élément de ressort (83) est placé avec un côté sur l'élargissement (85) en forme de plateau contre la douille (61) et avec l'autre côté contre l'induit (49).
  7. Soupape de commutation selon l'une quelconque des revendications 1 à 6, caractérisée en ce que l'élément de fermeture (31) est réalisé en forme de douille et est guidé sur une goupille de guidage (39).
  8. Soupape de commutation selon la revendication 7, caractérisée en ce qu'un espace annulaire (77) est réalisé au niveau de la goupille de guidage (39) entre un guide supérieur (75) et un guide inférieur (73) de l'élément de fermeture (31).
  9. Soupape de commutation selon la revendication 8, caractérisée en ce que des fentes de fuite sont à chaque fois réalisées par le guide supérieur (75) et le guide inférieur (73), de telle sorte que le guide supérieur (75) et le guide inférieur (73) agissent en tant que diviseurs de pression et que la pression dans l'espace annulaire (77) puisse être ajustée par la dimension de la fente du guide supérieur (75) et du guide inférieur (73).
  10. Soupape de commutation selon la revendication 8 ou 9, caractérisée en ce que l'espace annulaire (77) est connecté par le biais d'un canal (79) dans l'élément de fermeture (31) à l'espace d'amortissement (71) entre la face frontale (63) de la douille (61) et la face frontale (65) de l'élément de fermeture (31).
  11. Soupape de commutation selon l'une quelconque des revendications 7 à 10, caractérisée en ce que l'élément de fermeture (31) présente une face d'étanchéité ou arête d'étanchéité (33) réalisée sous forme annulaire et présente un diamètre intérieur constant (37) sur toute sa longueur.
EP08859206A 2007-12-10 2008-11-14 Soupape de commande pour injecteurs Not-in-force EP2229527B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710059265 DE102007059265A1 (de) 2007-12-10 2007-12-10 Schaltventil für Injektoren
PCT/EP2008/065591 WO2009074426A1 (fr) 2007-12-10 2008-11-14 Soupape de commande pour injecteurs

Publications (2)

Publication Number Publication Date
EP2229527A1 EP2229527A1 (fr) 2010-09-22
EP2229527B1 true EP2229527B1 (fr) 2013-03-13

Family

ID=40243768

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08859206A Not-in-force EP2229527B1 (fr) 2007-12-10 2008-11-14 Soupape de commande pour injecteurs

Country Status (4)

Country Link
EP (1) EP2229527B1 (fr)
CN (1) CN101896715B (fr)
DE (1) DE102007059265A1 (fr)
WO (1) WO2009074426A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029009A1 (de) * 2009-08-31 2011-03-03 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19650865A1 (de) 1996-12-07 1998-06-10 Bosch Gmbh Robert Magnetventil
DE10122168A1 (de) 2001-05-08 2002-11-14 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine

Also Published As

Publication number Publication date
EP2229527A1 (fr) 2010-09-22
CN101896715A (zh) 2010-11-24
CN101896715B (zh) 2012-07-04
DE102007059265A1 (de) 2009-06-18
WO2009074426A1 (fr) 2009-06-18

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