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EP2220360B1 - Soupape de commande pour injecteurs - Google Patents

Soupape de commande pour injecteurs Download PDF

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Publication number
EP2220360B1
EP2220360B1 EP08857497A EP08857497A EP2220360B1 EP 2220360 B1 EP2220360 B1 EP 2220360B1 EP 08857497 A EP08857497 A EP 08857497A EP 08857497 A EP08857497 A EP 08857497A EP 2220360 B1 EP2220360 B1 EP 2220360B1
Authority
EP
European Patent Office
Prior art keywords
closing element
switching valve
armature
closing
guide
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
EP08857497A
Other languages
German (de)
English (en)
Other versions
EP2220360A1 (fr
Inventor
Matthias Burger
Nadja Eisenmenger
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2220360A1 publication Critical patent/EP2220360A1/fr
Application granted granted Critical
Publication of EP2220360B1 publication Critical patent/EP2220360B1/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
    • F02M63/0014—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
    • 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 Nadelschlieli technique are available. This leads to steep maps and thus to a poor Kleinstmengenlub. However, this disadvantage can be compensated with very fast switching valves.
  • a control valve for a fast-switching fuel injection valve is 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.
  • a switching valve for fuel injectors in which a closing element actuated by a magnetic actuator drives a control chamber.
  • the magnetic actuator comprises an armature which is movably guided on a guide element adjoining the closing element, wherein a gap is formed when the switching valve is open between the armature and an end face of the closing element which acts as a lower stop, by which the abutment of the armature on the end face of the closing element is dampened.
  • 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 armature is movably guided on a guide element adjoining the closing element.
  • With open control valve is between the anchor and acting as a stop Face of the closing element formed a gap through which the abutment of the armature is damped on the end face of the closing element.
  • the inventive construction of the switching valve causes the closing element is placed in its seat when closing the switching valve, while the armature is moved along the guide member and the movement is damped by fuel contained in the gap between the armature and the end face of the closing element.
  • the entire mass of closing element and armature acts.
  • the impact pulse in the known from the prior art switching valves is greater than in the invention designed according to the switching valve. The bouncing is thus reduced. At the same time, reducing the bounce also reduces wear.
  • the spring element which acts on the armature is preferably a helical spring designed as a compression spring.
  • the spring element which acts on the armature is preferably a helical spring designed as a compression spring.
  • it is also any other, known in the art spring element used, which acts as a compression spring. If a helical spring designed as a compression spring is used, it preferably acts on an end face of the armature opposite the magnet assembly and moves it in the direction of the magnet assembly.
  • the spring element encloses the closing element of the switching valve.
  • the closing element and the guide element, on which the armature is guided integrally formed.
  • This construction also allows a completely pressure-balanced closure element, since the closure element is moved together with the guide element. Since the armature abuts against the upper stop, this pulls on a movement in the direction of the magnet assembly with the magnet turned on, the guide member also in the direction of the magnet assembly.
  • the closing element connected to the guide element lifts from its seat. In this way, a drainage channel is released from the control room. Fuel contained in the control room can flow out and the pressure in the control room decreases. Due to the decreasing pressure, the injection valve member lifts from its seat and releases at least one injection port for injecting fuel into a combustion chamber of the internal combustion engine.
  • the complete pressure equalization is achieved in that the closing element has an annular sealing surface or sealing edge, wherein the sleeve-shaped closing element has a constant inner diameter over its entire length.
  • the closing element and the guide element, on which the armature is guided are designed as two separate components. If the closing element and the guide element are designed as two separate components, the guide element with the armature, which bears against an upper stop on the guide element, is lifted in the direction of the magnet assembly with the magnet switched on to open the switching valve. It forms a gap between the guide element and the closing element. By a pressure force acting on the closing element, this is moved in the direction of the guide element, and the switching valve opens. So that a compressive force can act on the closing element, the closing element has a pressure surface, which adjoins a pressure chamber, which is connected to the control chamber via a drainage channel. On the pressure surface acting under system pressure fuel.
  • the pressure surface on the closing element of the end face, with which the closing element bears against the end face of the guide element opposite.
  • the closing element and the guide element thereby move on a common axis when opening and closing the switching valve.
  • the closing element is sleeve-shaped and has an annular sealing surface or sealing edge.
  • the pressure surface is formed by the fact that the inner diameter of the closing element increases in the region of the pressure chamber to the sealing surface or sealing edge.
  • the increase may, for example, be conical, parabolic, hyperbolic or any other geometry. Preferably, however, the increase is conical.
  • the sleeve-shaped closing element is guided on a guide pin.
  • the guide element for the armature is also guided on the guide pin, so that the closing element and the guide element can move only in the axial direction.
  • the closing element comprises a valve ball, with which a flow channel from the control chamber can be closed.
  • the closing element further comprises a receiving element for the valve ball, wherein on the receiving element, the end face is formed, which bears against the end face of the guide element.
  • the receiving element for the valve ball and the guide element are integrally formed. In this case, it is possible on the one hand, that the valve ball is firmly connected to the receiving element, alternatively, however, the ball can lie without a fixed connection in the receiving element.
  • Another advantage of the switching valve according to the invention is that a very precise production is possible by the leadership of the armature on the guide element and the parallelism of the upper and lower stop of the armature.
  • An elaborate setting process, in which the overstroke stop must be determined and corrected in the assembled state, is not required due to the component-independent manufacturing dimensions.
  • Another advantage of the valve according to the invention is due to the fact that at the moment of Anker simplyschwingens the closing element is pressed only by the closing spring, while the closing force results in the closed switching valve from the difference of the closing spring and acting on the armature spring element. For this reason, a greater spring force acts during the rebounding of the closing element than before the valve impact. This function additionally reduces bouncing.
  • FIG. 1 shows a schematic representation of a fuel injector with a pressure-balanced switching valve designed according to the invention.
  • 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 in the outlet channel 19.
  • 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.
  • the closing element 31 is pressure balanced.
  • the guide pin 39 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 thereby avoided that this pressed with a spring element 45 against the injector becomes.
  • 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 a guide element 49.
  • the guide element 49 is integrally formed with the closing element 31 in the embodiment shown here. Due to the spring force of the spring element 45 on the guide element 49, the closing element 31 is placed in the valve seat 35.
  • an armature 51 is movably guided.
  • the armature 51 cooperates with a magnet assembly 53 through which the switching valve 17 is actuated.
  • the stroke of the armature on the guide member 49 is limited by an upper stop 55 and a lower stop 57.
  • the upper stopper 55 is formed by, for example, a snap ring. However, the upper stop 55 can also be formed by any other, known in the art design element.
  • the magnet 61 which is usually designed as an electromagnet, is energized.
  • the armature 51 is attracted and moves in the direction of the magnet assembly 53. Since the armature 51 abuts the upper stop 55, this pulls the guide member 49 and thus the closing element 31, which is integrally formed with the guide member 49 upwards.
  • the sealing edge 33 of the closing element 31 rises from the valve seat 35 and releases a connection from the outlet channel 19 via a low-pressure chamber 63 in the return line 21. A bouncing of the armature 51 is thereby avoided that between the armature 51 and the magnet assembly 53, a squish gap 65 is formed.
  • the nip 65 is filled with fuel contained in the low-pressure space 63.
  • the fuel in the nip 65 is compressed and thus damps the movement of the armature 51.
  • the spring force of the spring element 59 in the direction of the magnet assembly 53 acts on the armature 51, so that a rebound of the armature 51 is reduced.
  • a gap 67 is formed between the armature 61 and the lower stop 57.
  • the gap 67 is filled with fuel.
  • the movement of the armature 51 is damped.
  • there is also an attenuation by the spring element 59 which exerts a force on the armature in the direction of the magnet assembly 53.
  • the fuel contained in the gap 67 which is compressed by the movement of the armature 61, simultaneously exerts a compressive force on the closing element 31, whereby it is held in the valve seat 35. Bouncing of the closing element 31 is thus further reduced.
  • the armature 61 is again placed against the upper stop 55 after swinging by means of the spring element 59.
  • the switching valve 17 is again in its initial position.
  • the stroke of the armature between the upper stop 55 and the lower stop 57 results from the height h 1 of the armature and the distance h 2 between the upper stop 55 and the lower stop 57. Since the upper and lower surfaces of the armature, the respectively abut on the upper stop 55 and the lower stop 57, are made in parallel, the height h 1 of the armature 51 and the distance h 2 between the upper stop 55 and the lower stop 57 can be measured very precisely, ground or manufactured. Thus, it is possible to measure the overtravel stop prior to assembly of the fuel injector 1 and optionally set exactly by selection groups. An elaborate setting process, in which the overtravel stop must be determined and corrected in the assembled state, is not required due to the component-independent dimensions h 1 and h 2 .
  • FIG. 2 is a section of a fuel injector with an inventively designed switching valve shown in a second embodiment. This in FIG. 2 shown switching valve 17 is in contrast to the in FIG. 1 illustrated switching valve not executed pressure balanced.
  • closing element 31 and guide element 49 in two parts.
  • the guide element 49 is in the closed state of the switching valve 17 with an end face 69 on an end face 71 of the closing element 31.
  • the end face 71 of the closing element 31 simultaneously serves as a lower stop 57 for the armature 61.
  • the magnet 61 of the magnet assembly 53 is energized.
  • the armature 51 bearing against the upper stop 55 moves in the direction of the magnet assembly 53.
  • the armature 51 carries along the guide element 49.
  • the guide element 49 lifts off from the closing element 31.
  • a gap forms between the guide element 49 and the closing element 31.
  • the pressure force of the fuel under low pressure acts on the gap in the low-pressure space 63.
  • a pressure surface 73 is formed on the closing element 31.
  • the pressure surface 73 adjoins the pressure chamber 43.
  • fuel under system pressure acts on the pressure surface 73. Because of the much higher pressure force, the closing element 31 is moved in the direction of the guide element 49.
  • the sealing edge 33 rises from the valve seat 35 and releases the connection from the discharge channel 19 into the return line 21.
  • the energization of the magnet 61 is stopped.
  • the guide member 49 is pressed in the direction of the closing element 31. Since the closing element 31 has been pressed against the guide element 49 due to the pressure force acting on the pressure surface 73, so that the end face 69 of the guide element 49 and the end face 71 of the closing element 31 are in contact, the closing element 31 is also moved by the movement of the guide element 49 , The closing element 31 is placed with the sealing edge 33 in the valve seat 35 and thus closes the connection from the discharge channel 19 in the return 21.
  • the armature 51 Since the armature 51 is guided freely on the guide member 49, this moves due its mass and inertia on, when the closing element 31 and the guide member 49 abruptly by striking the sealing edge 33 were stopped on the valve seat 35. The movement of the armature 51 is damped by the gap 67 formed between the armature 51 and the lower stopper 57, whereby the armature 51 is softly braked. As a result, the force applied by the armature force is reduced to the closing element 31 and reduces bouncing. At the same time the seat wear is reduced. In addition to acting as a damper gap 67, the armature 61 is also braked by the spring element 49. As soon as the armature 51 has come to a standstill, it is again moved in the direction of the magnet assembly 63 due to the spring force of the spring element 59, until it bears against the upper stop 55.
  • the upper stop 55 is formed integrally with the guide member 49. Due to the two-part design of guide member 49 and closing member 31, the anchor is not caught. This facilitates the assembly. Thus, the armature 51 is simply placed on the guide member 49, then guide member 49 and closing member 31 can be placed on the guide pin 39 and mounted in the injector.
  • guide pin 39 is also in the in FIG. 2 illustrated embodiment avoided that guide member 49 and closing member 31 can tilt or move in the radial direction. Only an axial movement along the guide pin 39 is possible.
  • FIG. 3 is a section of a fuel injector with an inventively designed switching valve shown in a third embodiment.
  • the switching valve 17 is not designed with an annular sealing edge 33, but with a valve ball 75th
  • guide element 49 and closing element 31 are formed in two parts.
  • the closing element 31 comprises the valve ball 75 and a receiving element 77 which receives the valve ball 75.
  • guide member 49 and receiving member 77 are integrally formed.
  • the magnet 61 of the magnet assembly 53 is also energized in the embodiment shown here.
  • the armature 51 is attracted by the magnet 61 and moves in the direction of the magnet assembly 53.
  • the armature 51 abuts on the upper stop 55 and thus pulls the guide member 49 in the direction of the magnet assembly 53.
  • guide member 49 and receiving member 77 are made in two parts, lifts the guide member 49 from the receiving element 77 from.
  • On the end face 81 of the receiving element 77 now acts only the pressure of the fuel contained in the low-pressure chamber 63.
  • valve ball 75 By acting on the valve ball 75 pressing force of the fuel under system pressure in the flow channel 19, the valve ball 75 is lifted together with the receiving element 77 from the valve seat 35 until it rests again on the end face 69 of the guide member 49. The connection from the drainage channel 19 in the return line 21 is released.
  • the receiving element 77 is moved in the direction of the magnetic assembly 53 by the movement of the armature 51.
  • the valve ball is lifted out of the valve seat 35 by the pressure of the fuel in the outlet channel 19 until it rests again in the receiving element 77 and thus the connection from the outlet channel 19 into the return line 21 is released.
  • integrally formed guide member 49 and receiving member 77 of the upper stopper 55 is preferably formed by a snap ring 79 which is used for example in a groove in the guide member 49.
  • a pin 83 is formed.
  • the pin 83 is enclosed by the spring element 59 and prevents tilting of the guide element 49.
  • the pin 83 serves as a guide for the spring element 39.

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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 (12)

  1. Soupape de commande pour injecteurs, en particulier 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 (53) et une armature (51), l'armature (51) étant guidée de manière déplaçable sur un élément de guidage (49) se raccordant à l'élément de fermeture (31) et lorsque la soupape de commande (17) est ouverte, une fente étant réalisée entre l'armature (51) et une surface frontale (71) de l'élément de fermeture (31) agissant en tant que butée inférieure (57), ladite fente permettant d'amortir la venue en butée de l'armature (51) sur la surface frontale (71) de l'élément de fermeture (31), caractérisée en ce que l'élément de fermeture (31) et l'élément de guidage (49) sont réalisés sous forme de douille et sont guidés sur une goupille de guidage (39).
  2. Soupape de commande selon la revendication 1, caractérisée en ce qu'un élément de ressort (59) agit sur l'armature (51), avec lequel élément de ressort l'armature (51) est appliquée contre une butée supérieure (55) lorsque la soupape de commande (17) est fermée.
  3. Soupape de commande selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que l'élément de fermeture (31) et l'élément de guidage (49) sur lequel est guidée l'armature (51), sont réalisés d'une seule pièce.
  4. Soupape de commande selon la revendication 3, caractérisée en ce que l'élément de fermeture (31) présente une surface d'étanchéité ou arête d'étanchéité (33) réalisée sous forme annulaire, l'élément de fermeture (31) réalisé sous forme de douille présentant sur toute sa longueur un diamètre intérieur constant (37).
  5. Soupape de commande selon la revendication 1, caractérisée en ce que l'élément de fermeture (31) et l'élément de guidage (49) sur lequel est guidée l'armature (51) sont réalisés sous forme de deux composants séparés.
  6. Soupape de commande selon la revendication 5, caractérisée en ce que l'élément de fermeture (31), lorsque la soupape de commande (17) est fermée, s'applique avec un côté frontal (71) contre un côté frontal (69) de l'élément de guidage (49).
  7. Soupape de commande selon la revendication 5 ou 6, caractérisée en ce que l'élément de fermeture (31) présente une surface de pression (73) qui se raccorde à un espace de pression (43) qui est connecté à l'espace de commande (9) par le biais d'un canal d'écoulement (19).
  8. Soupape de commande selon la revendication 7, caractérisée en ce que la surface de pression (73) au niveau de l'élément de fermeture (31) est opposée au côté frontal (71) avec lequel l'élément de fermeture (31) s'applique contre le côté frontal (69) de l'élément de guidage (49).
  9. Soupape de commande selon la revendication 7 ou 8, caractérisée en ce que l'élément de fermeture (31) est réalisé en forme de douille et présente une surface d'étanchéité ou une arête d'étanchéité (33) annulaire et la surface de pression (73) est formée par le fait que le diamètre intérieur (37) de l'élément de fermeture (31) augmente dans la région de l'espace de pression (43) vers la surface d'étanchéité ou l'arête d'étanchéité (33).
  10. Soupape de commande selon la revendication 5 ou 6, caractérisée en ce que l'élément de fermeture (31) comprend une bille de soupape (75) avec laquelle un canal d'écoulement (19) provenant de l'espace de commande (9) peut être fermé.
  11. Soupape de commande selon la revendication 10, caractérisée en ce que l'élément de fermeture (31) comprend un élément de réception (77) pour la bille de soupape (75), la surface frontale (71) étant réalisée sur l'élément de réception (77), laquelle s'applique contre la surface frontale (69) de l'élément de guidage (49).
  12. Soupape de commande selon la revendication 10, caractérisée en ce qu'un élément d'étranglement (23) est réalisé dans le canal d'écoulement (19).
EP08857497A 2007-12-03 2008-11-26 Soupape de commande pour injecteurs Not-in-force EP2220360B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007058069 2007-12-03
DE102007060395A DE102007060395A1 (de) 2007-12-03 2007-12-14 Schaltventil für Injektoren
PCT/EP2008/066183 WO2009071472A1 (fr) 2007-12-03 2008-11-26 Soupape de commande pour injecteurs

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EP2220360A1 EP2220360A1 (fr) 2010-08-25
EP2220360B1 true EP2220360B1 (fr) 2013-01-09

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EP08857497A Not-in-force EP2220360B1 (fr) 2007-12-03 2008-11-26 Soupape de commande pour injecteurs

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EP (1) EP2220360B1 (fr)
DE (2) DE102007060396A1 (fr)
WO (1) WO2009071472A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008005534A1 (de) * 2008-01-22 2009-07-23 Robert Bosch Gmbh Kraftstoffinjektor
DE102009002895A1 (de) 2009-05-07 2010-11-11 Robert Bosch Gmbh Kraftstoffinjektor mit Drucksensor
DE102009045623A1 (de) 2009-10-13 2011-04-14 Robert Bosch Gmbh Kraftstoff-Injektor
DE102009046332A1 (de) 2009-11-03 2011-05-05 Robert Bosch Gmbh Steuerventilanordnung
DE102010000827A1 (de) 2010-01-12 2011-07-14 Robert Bosch GmbH, 70469 Kraftstoffinjektor
DE102010002037A1 (de) 2010-02-17 2011-08-18 Robert Bosch GmbH, 70469 Elektromagnetischer Aktor
DE102010044012A1 (de) 2010-11-16 2012-05-16 Robert Bosch Gmbh Kraftstoffinjektor
KR101345431B1 (ko) * 2011-12-09 2013-12-27 주식회사 현대케피코 직분사 연료 인젝터
DE102012201413A1 (de) 2012-02-01 2013-08-01 Robert Bosch Gmbh Magnetventil für einen Kraftstoffinjektor
DE102012215448B3 (de) 2012-08-31 2013-12-12 Continental Automotive Gmbh Injektor zur Krafteinspritzung in eine Brennkraftmaschine
DE102012220027A1 (de) 2012-11-02 2014-05-08 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor
DE102013225376A1 (de) 2013-12-10 2015-06-11 Robert Bosch Gmbh Magnetventil für einen Kraftstoffinjektor
DE102013227063A1 (de) * 2013-12-23 2015-06-25 Robert Bosch Gmbh Kraftstoffinjektor
DE102015206205A1 (de) * 2015-04-08 2016-10-13 Robert Bosch Gmbh Gasventil
DE102015213141A1 (de) * 2015-07-14 2017-01-19 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102015216785A1 (de) 2015-09-02 2017-03-02 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschine
IT201600114608A1 (it) * 2016-11-14 2018-05-14 Magneti Marelli Spa Pompa di alimentazione carburante
DE102022131385A1 (de) * 2022-11-28 2024-05-29 Liebherr-Components Deggendorf Gmbh Injektor zum Einspritzen von Kraftstoff

Family Cites Families (5)

* 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
IT239878Y1 (it) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat Perfezionamenti ad una valvola di dosaggio a comando elettromagneticoper un iniettore di combustibile.
DE10123171A1 (de) 2001-05-12 2002-11-14 Bosch Gmbh Robert Magnetventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine
EP1621764B1 (fr) * 2004-06-30 2007-11-07 C.R.F. Società Consortile per Azioni Injecteur d'un moteur à combustion interne
DE102007044355A1 (de) 2007-06-21 2008-12-24 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor sowie Kraftstoffinjektor

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WO2009071472A1 (fr) 2009-06-11
EP2220360A1 (fr) 2010-08-25
DE102007060396A1 (de) 2009-06-04
DE102007060395A1 (de) 2009-06-04

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