EP2229527B1 - On-off valve for injectors - Google Patents

On-off valve for injectors Download PDF

Info

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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP2229527A1 (en
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
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 EP2229527A1 publication Critical patent/EP2229527A1/en
Application granted granted Critical
Publication of EP2229527B1 publication Critical patent/EP2229527B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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.

Landscapes

  • 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)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Schaltventil für Injektoren, insbesondere für Kraftstoffinjektoren, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a switching valve for injectors, in particular for fuel injectors, according to the preamble of claim 1.

Kraftstoffinjektoren werden eingesetzt, um Brennräume einer Verbrennungskraftmaschine mit Kraftstoff zu versorgen. Der Kraftstoff wird dabei unter hohem Druck in die Brennräume eingespritzt. Insbesondere bei selbstzündenden Verbrennungskraftmaschinen kommen Hochdruckspeichereinspritzsysteme zur Anwendung, bei denen der Einspritzdruck unabhängig von der Drehzahl und Last der Verbrennungskraftmaschine ist. Hierdurch lassen sich die bei der Verbrennung entstehenden Schadstoffe reduzieren. Um eine weitere Reduzierung der Schadstoffe zu erreichen, ist jedoch eine signifikante Erhöhung des Einspritzdruckes notwendig.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. Particularly in self-igniting internal combustion engines, high-pressure accumulator injection systems are used in which the injection pressure is independent of the speed and load of the internal combustion engine. As a result, the pollutants resulting from the combustion can be reduced. In order to achieve a further reduction of the pollutants, however, a significant increase in the injection pressure is necessary.

Kraftstoffinjektoren, die bei den geforderten Drücken eingesetzt werden können, werden leckagefrei ausgeführt. Hierzu wird auf eine Niederdruckstufe verzichtet. Durch das Fehlen der Niederdruckstufe stehen jedoch nur geringe Nadelschließkräfte zur Verfügung. Dies führt zu steilen Kennfeldern und somit zu einer schlechten Kleinstmengenfähigkeit. Dieser Nachteil kann jedoch mit sehr schnell schaltenden Ventilen kompensiert werden.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 Kleinstmengenfähigkeit. However, this disadvantage can be compensated with very fast switching valves.

Ein Schaltventil für einen Kraftstoffinjektor mit einer hydraulischen Dämpfungseinrichtung ist aus DE 196 50 865 A1 bekannt. Bei diesem Schaltventil sind an einem Ankerbolzen eine Ankerscheibe und eine Dämpfungshülse axial beweglich geführt. Die Dämpfungshülse weist eine stirnseitige Ringkammer auf, in die ein an der Ankerscheibe ausgebildeter ringförmiger Ansatz bei einer Öffnungsbewegung des Ankerbolzens eingreift. Durch das Eingreifen des Ansatzes in den Ringraum entsteht durch das Komprimieren der Hydraulikflüssigkeit innerhalb der Ringkammer eine Dämpfung der Bewegung des Ankerbolzens.A switching valve for a fuel injector with a hydraulic damping device is off DE 196 50 865 A1 known. In this switching valve, 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. By engaging the approach in the annulus formed by compressing the hydraulic fluid within the annular chamber, a damping of the movement of the anchor bolt.

Aus EP 12 56 709 A2 ist ein Schaltventil für einen Kraftstoffinjektor bekannt, bei dem an einem Ankerbolzen eine Ankerplatte gleitend verschiebbar angeordnet ist und bei dem der Ankerbolzen eine Anschlagfläche aufweist, die bei einem Öffnungshub gegen eine gehäusefeste Schulter anschlägt.Out EP 12 56 709 A2 a switching valve for a fuel injector is known in which an armature plate is slidably disposed on an anchor bolt and in which the anchor bolt has a stop surface which abuts against a housing-fixed shoulder during an opening stroke.

Ein Steuerventil für ein schnell schaltendes Kraftstoffeinspritzventil ist weiterhin aus DE 10 2007 028 485 bekannt. Bei diesem wird ein Druckraum von einer Steuerhülse begrenzt, die in ihrer Längsrichtung beweglich gelagert ist. Die Steuerhülse weist an einer Stirnseite eine Dichtfläche auf, mit der sie mit einem Ventilsitz zusammenwirkt, der an einem Ventilkörper ausgebildet ist. Im Ventilkörper ist eine Ausnehmung in der dem Druckraum zugewandten Seite des Ventilkörpers ausgebildet. Die Steuerhülse und die Ausnehmung im Ventilkörper sind so ausgebildet, dass eine Verformung von Steuerhülse und Ventilkörper durch den Druck im Druckraum zu keiner oder nur zu sehr geringer Bewegung zwischen dem Ventilsitz und der Dichtfläche der Steuerhülse führt.A control valve for a fast-switching fuel injection valve is still off DE 10 2007 028 485 known. In this, 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. In the 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.

Schnell schaltende Ventile haben jedoch den Nachteil, dass aufgrund eines Prellens Kennfeldwelligkeiten auftreten. Einerseits ergibt sich ein Prellen des Schließelementes aufgrund eines harten Anschlages in Verbindung mit einem schnellen Schließelement. Der harte Anschlag resultiert aus dem Aufprellen von Metall auf Metall. Diese Preller, die beim Aufschlagen des Schließelementes auftreten, haben jedoch einen negativen Einfluss auf die Funktion des Kraftstoffinjektors und führen im Allgemeinen zu großen Hub/Hub-Streuungen. Bei magnetgesteuerten Schaltventilen wird am oberen Hubanschlag zwischen Anker und Magnet ein Quetschspalt ausgebildet, der den Anschlag dämpft und so das Prellen reduziert. Ein solcher Quetschspalt kann jedoch am Ventilsitz aufgrund dessen Dichtfunktionen nicht angebracht werden, um den Einschlagimpuls des Schließelementes im Ventilsitz zu reduzieren.However, 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. However, 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. In 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. However, 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.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Ein erfindungsgemäß ausgebildetes Schaltventil für Injektoren, insbesondere für Kraftstoffinjektoren, umfasst ein Schließelement, mit dem ein Steuerraum zur Betätigung eines Einspritzventilgliedes druckentlastbar ist. Das Schließelement wird durch einen Magnetaktor, umfassend eine Magnetbaugruppe und einen Anker, angesteuert. Das Schließelement ist mit einem Anschlagelement derart verbunden, dass das Anschlagelement und das Schließelement einen Dämpfungsraum umschließen, wobei der Dämpfungsraum mit Flüssigkeit befüllt ist, deren Menge bei einer Bewegung des Schließelementes im Wesentlichen konstant bleibt, so dass sich Schließelement und Anschlagelement gemeinsam bewegen.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.

Während der Öffnungsbewegung des Schließelementes nimmt der Druck im Dämpfungsraum zunächst ab. Aufgrund des abnehmenden Drucks wirkt eine Kraft auf das Anschlagelement, durch die das Anschlagelement mit dem Schließelement mitbewegt wird. Das Volumen des Dämpfungsraumes ändert sich bei gleich bleibender Menge an Flüssigkeit nicht. Auf diese Weise bleibt die Position des Anschlagelementes zum Schließelement unverändert. Beim Schließen des Schaltventils nimmt der Druck im Dämpfungsraum zunächst zu. Das Anschlagelement wird mit dem Schließelement mitbewegt. Beim Anschlagen bildet sich zwischen dem Anschlagelement und einer Anschlagfläche ein Quetschspalt aus, durch den die Bewegung gedämpft wird und ein großer Teil des Anschlagimpulses aufgenommen wird. Die Bewegung des Schließelementes wird durch den bei einem Durchschwingen zunehmenden Druck im Dämpfungsraum gedämpft. Ein Prellen oder ein Ventilsitzverschleiß wird verhindert, da ein großer Teil des Einschlagimpulses bereits durch das Anschlagen des Anschlagelementes vernichtet worden ist.During the opening movement of the closing element, 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. When closing the switching valve, the pressure in the damping chamber initially increases. The stop element is moved with the closing element. When 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.

In einer bevorzugten Ausführungsform ist das Anschlagelement in Form einer Hülse ausgebildet. Wenn das Anschlagelement in Form einer Hülse ausgebildet ist, ist es bevorzugt, wenn das Schließelement in einer Hülse geführt ist, wobei zwischen einer in Richtung der Magnetbaugruppe weisenden oberen Stirnfläche der Hülse und einer der oberen Stirnfläche der Hülse gegenüberliegenden Stirnfläche des Schließelementes der Dämpfungsraum ausgebildet ist. Um bei geschlossenem Schaltventil die Position des Anschlagelementes an die Position des Schließelements anzupassen, ist es bevorzugt, wenn die obere Stirnfläche der Hülse derart von einer ringförmigen Kante abgeschlossen ist, dass die Innenseite der ringförmigen Kante und die Außenseite der Stirnfläche des Schließelementes beim Schließen des Schaltventils und bei geschlossenem Schaltventil einen Ringspalt ausbilden. Der Ringspalt wirkt gegenüber dem umgebenden Raum als Drossel, so dass der Druck im Dämpfungsraum höher ist als der umgebende Druck. Hierdurch wird eine vollständige Befüllung des Dämpfungsraumes mit Flüssigkeit gewährleistet. Zudem kann auf diese Weise ein Flüssigkeitsausgleich erfolgen, der zum Beispiel notwendig ist, wenn sich zum Beispiel durch Sitzverschleiß zunächst die Position des Schließelementes zum Anschlagelement ändert. Auf diese Weise wird die Funktion des Anschlagelementes immer gewährleistet. So kann über den Ringspalt zum Beispiel Flüssigkeit ausströmen, wenn zum Ausgleich der Positionen ein kleineres Volumen des Dämpfungsraumes erforderlich ist.In a preferred embodiment, 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. As a result, a complete filling of the damping chamber is ensured with liquid. In addition, can be done in this way 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.

Ein weiterer Vorteil des erfindungsgemäßen Aufbaus des Schaltventils ist, dass die hydraulische Dämpfungskraft nur eine Funktion der Ankergeschwindigkeit ist. Anders als bei einem Quetschspalt hat der Ankerhub keinen Einfluss auf die Dämpfungskraft. Auf diese Weise wird auch bei einem Hubdrift, der z.B. durch einen Ventilsitzverschleiß begründet sein kann, sichergestellt, dass das Ventil jederzeit schließt.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.

In einer bevorzugten Ausführungsform ist die Hülse relativ zum Schließelement in axiale Richtung bewegbar. Vorteil dieser Ausführungsform ist, dass der Dämpfer nur beim Schlie-βen, jedoch nicht beim Öffnen des Ventils wirkt. Auf diese Weise wird ein ungewolltes Verzögern der Ventilöffnungsbewegung verhindert. Durch die Öffnungsbewegung des Schließelementes wird das Volumen des Dämpfungsraumes vergrößert. Hierdurch sinkt der Druck im Dämpfungsraum ab. Da die Hülse relativ zum Schließelement in axialer Richtung bewegbar ist, kann sich die Hülse zunächst mitsamt dem Schließelement mitbewegen, so dass das Volumen des Dämpfungsraumes im Wesentlichen konstant bleiben kann und keine Kraft überwunden werden muss, die aufgrund eines verminderten Druckes im Dämpfungsraum auf das Schließelement wirkt. Ein schnelles Öffnen des Schaltventils ist somit möglich.In a preferred embodiment, the sleeve is movable relative to the closing element in the axial direction. Advantage of this embodiment is that the damper acts only when closing βen, 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.

In einer bevorzugten Ausführungsform ist an der Hülse eine tellerförmige Erweiterung ausgebildet und ein Federelement ist mit einer Seite auf die tellerförmige Erweiterung an der Hülse und mit der anderen Seite gegen den Anker gestellt. Das Federelement ist vorzugsweise eine als Druckfeder ausgebildete Spiralfeder. Durch das Federelement wird die Hülse bei geschlossenem Schaltventil in ihren Anschlag gestellt. Hierdurch kann eine Änderung der Position von Schließelement und Hülse, wie sie zum Beispiel bei einem Hubdrift auftritt, ausgeglichen werden. Das Volumen des Dämpfungsraumes ändert sich dabei, bleibt jedoch dann während des nächsten Öffnungs- und Schließvorganges wieder konstant, um die Dämpfungsfunktion zu erfüllen.In a preferred embodiment, 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. By the spring element, the sleeve is placed with the switching valve closed in its stop. As a result, a change in the position of closing element and sleeve, as occurs for example in a Hubdrift, be compensated. The volume of the damping chamber changes while remaining constant during the next opening and closing operation in order to fulfill the damping function.

Damit das Schließelement nicht verkantet oder sich in radialer Richtung verschiebt und so eine Funktionsstörung des Injektors hervorruft, ist das Schließelement vorzugsweise hülsenförmig ausgebildet und auf einem Führungsstift geführt. In einer bevorzugten Ausführungsform ist am Führungsstift zwischen einer oberen und einer unteren Führung des Schließelementes ein ringförmiger Raum ausgebildet. Der ringförmige Raum dient als Leckagesammelraum von Flüssigkeit, die als Leckage über die untere Führung strömt. Da der Leckagespalt zwischen der unteren Führung und dem Schließelement in hydraulischer Verbindung mit dem Ablaufkanal aus dem Steuerraum steht, wird der Leckagesammelraum mit Flüssigkeit befüllt.So that the closing element is not tilted or displaced in the radial direction and thus causes a malfunction of the injector, the closing element is preferably sleeve-shaped and guided on a guide pin. In a preferred embodiment, 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.

Vorzugsweise werden die obere Führung und die untere Führung jeweils als Leckagespalte ausgebildet, so dass die obere Führung und die untere Führung als Druckteiler wirken und der druck im Ringraum durch das Spaltmaß der oberen Führung und der unteren Führung einstellbar ist. Aufgrund der oberen Führung ist der Druck im Leckageraum höher als im Niederdruckbereich. Aufgrund der ebenfalls als Drossel wirkenden unteren Führung jedoch niedriger als der Systemdruck. Bei Einsatz des Injektors als Kraftstoffinjektor in Hochdruckspeichereinspritzsystemen treten hierbei Systemdrücke von weit über 1000 bar auf.Preferably, 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.

Der ringförmige Raum, der als Leckagesammelraum dient, ist vorteilhafterweise über einen Kanal im Schließelement mit dem Dämpferraum zwischen der oberen Stirnfläche der Hülse und der Stirnfläche des Schließelementes verbunden. Auf diese Weise kann Flüssigkeit aus dem Leckagesammelraum in den Dämpfungsraum strömen. Auf diese Weise wird sichergestellt, dass der Dämpfungsraum immer mit Flüssigkeit befüllt ist, wobei die Flüssigkeit über den Kanal einströmt und entlang des Ringspaltes wieder aus dem Dämpfungsraum ausströmen kann. Ein weiterer Vorteil ist, dass der Druck der Flüssigkeit im Dämpfungsraum oberhalb dem Siededruck liegt und die Flüssigkeit so gasfrei vorliegt. Auf diese Weise wird die Dämpfungsfunktion des Dämpfungsraumes sichergestellt.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. In this way, liquid can flow from the leakage collecting space into the damping chamber. In this way it is ensured that 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.

Wenn das Schließelement hülsenförmig ausgebildet und auf dem Führungsstift geführt ist, weist das Schließelement vorzugsweise eine ringförmig ausgebildete Dichtfläche oder Dichtkante auf und einen über seine gesamte Länge konstanten Innendurchmesser. Da der unter Systemdruck stehende Kraftstoff nur auf die Innenseite des Schließelementes wirkt, treten durch den konstanten Innendurchmesser nur radiale Druckkräfte auf. Hierdurch ist das Schließelement druckausgeglichen und es müssen keine Druckkräfte zum Öffnen oder Schließen des Schaltventiles überwunden werden. Hierdurch sind bereits geringe Schaltkräfte ausreichend, um ein schnelles Schalten des Schaltventils zu ermöglichen.If 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.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Eine Ausführungsform der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description.

Die einzige Figur zeigt einen Kraftstoffinjektor mit erfindungsgemäß ausgebildetem Schaltventil.The single FIGURE shows a fuel injector with inventively designed switching valve.

Ausführungsformen der ErfindungEmbodiments of the invention

Die einzige Figur zeigt eine schematische Darstellung eines Kraftstoffinjektors mit einem erfindungsgemäß ausgebildeten druckausgeglichenen Schaltventil.The single FIGURE shows a schematic representation of a fuel injector with an inventively designed pressure-balanced switching valve.

Ein Kraftstoffinjektor 1 umfasst ein Einspritzventilglied 3, mit dem mindestens eine, hier nicht dargestellte Einspritzöffnung zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine freigegeben oder verschlossen werden kann. Das Einspritzventilglied 3 ist in einem Ventilstück 5 geführt und begrenzt mit einer oberen Stirnfläche 7 einen Steuerraum 9. Der Steuerraum 9 wird über eine Zulaufdrossel 11 mit unter Systemdruck stehendem Kraftstoff befüllt. Die Zulaufdrossel 11 verbindet den Steuerraum 9 mit einem Ringraum 13, der das Ventilstück 5 umschließt und seinerseits mit einem hier nicht dargestellten Hochdruckspeicher über einen Zulaufkanal 15 verbunden ist. Durch die Druckkraft des unter Systemdruck stehenden Kraftstoffes im Steuerraum 9, der auf die obere Stirnfläche 7 des Einspritzventilgliedes 3 wirkt, wird dieses in einen hier nicht dargestellten Ventilsitz gestellt und verschließt so die mindestens eine Einspritzöffnung.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. By the pressure force of the fuel under system pressure in the control chamber 9, which acts on the upper end face 7 of the injection valve member 3, this is placed in a valve seat, not shown here, and thus closes the at least one injection port.

Um die mindestens eine Einspritzöffnung freizugeben, wird der Steuerraum 9 druckentlastet. Hierzu öffnet ein Schaltventil 17, wodurch eine Verbindung aus einem Ablaufkanal 19 zu einem Kraftstoffrücklauf 21 freigegeben wird und Kraftstoff aus dem Steuerraum 9 ausströmen kann. Der Druck im Steuerraum 9 sinkt und das Einspritzventilglied 3 hebt sich aus seinem Ventilsitz und gibt die Einspritzöffnung frei. Um Druckpulsationen zu reduzieren, ist im Ablaufkanal. 19 ein Drosselelement 23 ausgebildet.In order to release the at least one injection opening, the control chamber 9 is depressurized. For this purpose, 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. To reduce pressure pulsations is in the drainage channel. 19, a throttle element 23 is formed.

Um den Einspritzvorgang zu beenden, schließt das Schaltventil die Verbindung aus dem Ablaufkanal 19 zum Rücklauf 21. Über die Zulaufdrossel 11 strömt unter Systemdruck stehender Kraftstoff in den Steuerraum 9, der Druck im Steuerraum 9 steigt an. Durch die zunehmende Druckkraft wird das Einspritzventilglied 3 wieder in seinen Sitz gestellt und verschließt die mindestens eine Einspritzöffnung.In order to terminate the injection process, the switching valve closes the connection from the outlet channel 19 to the return line 21. Via the inlet throttle 11 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.

Die Schließbewegung des Einspritzventilgliedes 3 wird durch ein Federelement 25 unterstützt. Das Federelement 25 ist vorzugsweise eine als Spiralfeder ausgebildete Druckfeder.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.

Das Ventilstück 5, in dem das Einspritzventilglied 3 geführt ist, wird mit einer Ventilspannmutter 27 im Injektorgehäuse 29 montiert.The valve piece 5, in which the injection valve member 3 is guided, is mounted with a valve clamping nut 27 in the injector 29.

Das Schaltventil 17, mit dem das Öffnen und Schließen des Kraftstoffinjektors zum Einspritzen von Kraftstoff in den Brennraum der Verbrennungskraftmaschine gesteuert wird, umfasst ein Schließelement 31. Das Schließelement 31 weist eine Dichtkante 33 auf, die zum Schließen in einen Ventilsitz 35 gestellt wird. Alternativ ist es auch möglich, anstelle der Dichtkante 33 eine Dichtfläche vorzusehen.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. Alternatively, it is also possible to provide a sealing surface instead of the sealing edge 33.

In der in der Figur dargestellten Ausführungsform ist das Schaltventil 17 druckausgeglichen. Die Dichtkante 33 ist ringförmig ausgebildet. Weiterhin weist das Schließelement 31 einen konstanten Innendurchmesser 37 auf. Auf diese Weise wirkt der Druck des unter Systemdruck stehenden Kraftstoffs nur in radiale Richtung auf das Schließelement 31. Somit wirken auf gegenüberliegende Flächen am Schließelement 31 immer nur gleiche Druckkräfte.In the embodiment shown in the figure, the switching valve 17 is pressure balanced. The sealing edge 33 is annular. Furthermore, 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.

Um zu vermeiden, dass das Schließelement 31 kippt oder in radiale Richtung verrutscht, ist dieses auf einem Führungsstift 39 geführt. Der Führungsstift endet mit einer unteren Stirnfläche 41 oberhalb dem Ablaufkanal 19 und begrenzt so zusammen mit dem Schließelement 31 einen Druckraum 43. Mit der dem Druckraum 43 gegenüberliegenden Seite liegt der Führungsstift 39 am Injektorgehäuse an. Ein Verschieben des Führungsstiftes 39 wird dadurch vermieden, dass dieser mit einem Federelement 45 gegen das Injektorgehäuse gepresst wird. Das Federelement 45 ist vorzugsweise eine als Druckfeder ausgebildete Spiralfeder. Mit einer Seite wirkt das Federelement 45 gegen eine Stirnfläche an einer Erweiterung 47 des Führungsstiftes und mit einer anderen Seite auf das Schließelement 31.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

Das Federelement 45 dient gleichzeitig als Schließfeder. Durch die Federkraft des Federelementes 45 auf das Schließelement 31 wird dieses in den Ventilsitz 35 gestellt.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.

Das Schließelement 31 ist weiterhin mit einem Anker 49 verbunden. Der Anker 49 wirkt mit einer Magnetbaugruppe 51 zusammen, durch die das Schaltventil 17 betätigt wird. Die Magnetbaugruppe 51 umfasst im Allgemeinen eine als Elektromagnet wirkende Spule 53 und einen Kern 55, der die Spule 53 umschließt.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.

Um den Einspritzvorgang zu starten, muss das Schaltventil 17 geöffnet werden. Hierzu wird die Spule 53 bestromt. Es bildet sich ein Magnetfeld aus, durch das der Anker 49 angezogen wird und sich in Richtung der Magnetbaugruppe 51 bewegt. Da der Anker 49 mit dem Schließelement 31 verbunden ist, zieht dieser das Schließelement 31 ebenfalls nach oben. Das Schließelement 31 hebt sich aus dem Ventilsitz 35 und gibt eine Verbindung vom Ablaufkanal 19 über einen Niederdruckraum 57 in den Rücklauf 21 frei. Ein Prellen des Ankers 49 wird dabei dadurch vermieden, dass zwischen dem Anker 49 und der Magnetbaugruppe 51 ein Quetschspalt 59 ausgebildet ist. Der Quetschspalt 59 ist mit im Niederdruckraum 57 enthaltenen Kraftstoff befüllt. Der Kraftstoff im Quetschspalt 59 wird komprimiert und dämpft so die Bewegung des Ankers 49.To start the injection process, the switching valve 17 must be opened. For this purpose, 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.

Durch die freigegebene Verbindung vom Ablaufkanal 19 über den Niederdruckraum 57 zum Rücklauf 21 strömt Kraftstoff aus dem Steuerraum 9. Der Druck im Steuerraum 9 nimmt ab. Hierdurch wird die auf die obere Stirnfläche 7 des Einspritzventilgliedes 3 wirkende Druckkraft reduziert. Das Einspritzventilglied 3 wird aus seinem Sitz gehoben und gibt so die mindestens eine Einspritzöffnung des Kraftstoffinjektors 1 frei. Kraftstoff wird in einen Brennraum der Verbrennungskraftmaschine eingespritzt.Due to the released connection from the outlet channel 19 via the low-pressure chamber 57 to the return line 21, fuel flows out of the control chamber 9. The pressure in the control chamber 9 decreases. As a result, the force acting on the upper end face 7 of the injection valve member 3 compressive force is reduced. The injection valve member 3 is lifted out of its seat and thus releases the at least one injection opening of the fuel injector 1. Fuel is injected into a combustion chamber of the internal combustion engine.

Um den Einspritzvorgang zu beenden, muss das Einspritzventilglied 3 wieder in seinen Sitz gestellt werden, um die Einspritzöffnung zu verschließen. Hierzu muss zunächst das Schaltventil 17 die Verbindung vom Ablaufkanal 19 in den Rücklauf 21 schließen. Hierzu wird die Bestromung der Spule 53 beendet, das Magnetfeld fällt zusammen. Aufgrund der Federkraft des Federelementes 45, die auf das Schließelement 31 wirkt, wird das Schließelement 31 in Richtung des Ventilsitzes 35 bewegt, bis die Dichtkante 33 im Ventilsitz 35 steht. Über die Zulaufdrossel 11 1 strömt unter Systemdruck stehender Kraftstoff aus dem Ringraum 13 in den Steuerraum 9. Der Druck im Steuerraum 9 nimmt zu und damit auch die auf die obere Stirnfläche 7 des Einspritzventilgliedes 3 wirkende Druckkraft. Aufgrund der zunehmenden Druckkraft auf die obere Stirnfläche 7 des Einspritzventilgliedes 3 wird das Einspritzventilglied 3 wieder in seinen Sitz gestellt und verschließt so die mindestens eine Einspritzöffnung. Der Einspritzvorgang ist beendet.To end the injection process, the injection valve member 3 must be put back in its seat to close the injection port. For this purpose, the switching valve 17 must first close the connection from the outlet channel 19 into the return line 21. For this purpose, the energization of the coil 53 is terminated, the magnetic field coincides. Due to 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. Via 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.

Um ein Rückprellen des Schließelementes 31 zu verhindern und gleichzeitig den Verschleiß am Ventilsitz 35 zu minimieren, ist das Schließelement 31 von einer Hülse 61 umschlossen. An der Hülse 61 ist eine obere Stirnfläche 63 ausgebildet. Die obere Stirnfläche 63 der Hülse 61 liegt einer Stirnfläche 65 des Schließelementes 31 gegenüber, so dass sich zwischen der oberen Stirnfläche 63 der Hülse 61 und der Stirnfläche 65 des Schließelementes 63 ein Spalt ausbildet. Die obere Stirnfläche 63 der Hülse 61 ist weiterhin von einer ringförmigen Kante 67 derart abgeschlossen, dass zwischen der Innenseite der ringförmigen Kante 67 und der Außenseite der Stirnfläche 65 des Schließelementes 31 ein Ringspalt 69 ausgebildet ist. Auf diese Weise wird zwischen der oberen Stirnfläche 63 der Hülse 61 und der Stirnfläche 65 des Schließelementes 31 sowie der ringförmigen Kante 67 ein Dämpfungsraum 71 umschlossen. Der Dämpfungsraum 71 ist mit Flüssigkeit befüllt.In order to prevent rebounding of the closing element 31 and at the same time to minimize the wear on the valve seat 35, the closing element 31 is enclosed by a sleeve 61. On the sleeve 61, an upper end face 63 is formed. 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. In this way, 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.

Beim Öffnen des Schaltventils 17 bewegt sich zunächst das Schließelement 31, so dass das Volumen des Dämpfungsraumes 71 zunimmt. Dies führt zu einer Druckabnahme im Dämpfungsraum 71. Da davon ausgegangen werden kann, dass die Flüssigkeit im Wesentlichen inkompressibel ist, führt bereits eine sehr geringe Änderung des Volumens zu einer starken Druckänderung. Diese Druckänderung führt dazu, dass die Hülse 61 zusammen mit dem Schließelement in Richtung der Magnetbaugruppe 51 bewegt wird. Die Position der Hülse 61 relativ zum Schließelement 31 ändert sich nicht.When opening the switching valve 17, first the closing element 31 moves, so that the volume of the damping chamber 71 increases. This leads to a decrease in pressure in the damping chamber 71. Since it can be assumed that the liquid is essentially incompressible, even a very small change in the volume leads to a strong change in pressure. This pressure change causes the sleeve 61 is moved together with the closing element in the direction of the magnet assembly 51. The position of the sleeve 61 relative to the closing element 31 does not change.

Beim Schließen des Schaltventils 17 werden das Schließelement 31 und die Hülse 61 wieder in Richtung des Ventilsitzes 35 bewegt. Zwischen der Hülse 61 und deren Auflagefläche am Ventilstück 5 bildet sich ein Quetschspalt aus, der den Einschlag der Hülse 61 dämpft. Auf diese Weise wird ein Großteil des Einschlagimpulses vernichtet. Das Schließelement 17 bewegt sich dabei weiter, so dass dieses mit der Stirnfläche 65 in den Dämpfungsraum 71 eindringt. Das Volumen des Dämpfungsraumes 71 wird verkleinert. Hierdurch wird die im Dämpfungsraum 71 enthaltene Flüssigkeit komprimiert. Die Bewegung des Schließelementes 31 wird gedämpft. Aufgrund ihrer Position zueinander schlagen Schließelement 31 und Hülse 61 gleichzeitig an. Sobald das Schließelement anschlägt, steht die Dichtkante 33 im Ventilsitz 35 und die Verbindung vom Ablaufkanal 19 in den Rücklauf 21 ist geschlossen. Da durch diesen Schließprozess ein Großteil des Ventilnadelschließimpulses kurz vor dem Einschlag in den Ventilsitz 35 vernichtet wird, wird ein Rückprellen des Schließelementes 31 verhindert.When closing the switching valve 17, the closing element 31 and the sleeve 61 are again moved in the direction of the valve seat 35. Between the sleeve 61 and the bearing surface on the valve piece 5, a nip is formed, which dampens the impact of the sleeve 61. In this way, a large part of the impact pulse is destroyed. The closing element 17 continues to move, so that this penetrates with the end face 65 in the damping chamber 71. The volume of the damping chamber 71 is reduced. As a result, the liquid contained in the damping chamber 71 is compressed. The movement of the closing element 31 is damped. Due to their position to each other strike closing member 31 and sleeve 61 at the same time. As soon as the closing element abuts, the sealing edge 33 is in the valve seat 35 and the connection from the outlet channel 19 in the return line 21 is closed. Since a large part of the valve needle closing pulse is destroyed by this closing process just before the impact into the valve seat 35, a rebounding of the closing element 31 is prevented.

Die Schließbewegung der Hülse 61 wird durch ein Federelement 83 unterstützt. Das Federelement 83 ist vorzugsweise eine als Spiralfeder ausgebildete Druckfeder und wirkt als Positionierfeder für die Hülse 61. Hierzu wirkt das Federelement 83 mit einer Seite auf eine Erweiterung 85 an der Hülse 61 und mit der anderen Seite auf den Anker 49. In ihrer Grundposition liegt die Hülse 61 auf dem Ventilstück 5 auf.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. For this purpose, 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.

Am Führungsstift 39 ist eine untere Führung 73 und eine obere Führung 75 ausgebildet. Das Schließelement 31 wird entlang der oberen Führung 75 und der unteren Führung 73 geführt. Zwischen der oberen Führung 75 und der unteren Führung 73 ist ein Ringraum 77 ausgebildet. Der Ringraum 77 dient als Leckagesammelraum. Entlang der unteren Führung 73 dringt Kraftstoff aus dem Druckraum 43 als Leckage in den Leckagesammelraum 77. Aufgrund des hohen Drucks des Kraftstoffs im Druckraum 43 ist der Druck des Kraftstoffs im Ringraum 77 höher als in Niederdruckraum 57. Der Ringraum 77 ist über einen Kanal 79 mit dem Dämpfungsraum 71 verbunden. Über den Kanal 79 strömt Kraftstoff in den Dämpfungsraum 71. Hierdurch wird sichergestellt, dass der Dämpfungsraum 71 immer mit Flüssigkeit befüllt ist. Aufgrund des höheren Drucks der Flüssigkeit in Ringraum 77 wird gleichzeitig die Bildung von Gasblasen im Dämpfungsraum 71 vermieden.On the guide pin 39, a lower guide 73 and an upper guide 75 is formed. The closing member 31 is guided along the upper guide 75 and the lower guide 73. Between the upper guide 75 and the lower guide 73, an annular space 77 is formed. 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.

Der Kanal 79 wird vorzugsweise durch eine Laserbohrung oder durch Erosion hergestellt.The channel 79 is preferably made by laser drilling or by erosion.

Damit die Dämpfungswirkung des Dämpfungsraumes 71 aufgrund der hydraulischen Verbindung des Ringraumes 77 mit dem Dämpfungsraum 71 über den Kanal 79 nicht unwirksam ist, ist es erforderlich, dass die Drosselwirkung an der unteren Führung 73 und der oberen Führung 75 sehr viel kleiner ist als die Drosselung am Ringspalt 69.Thus, 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.

Die Hülse 61 ist entlang einer Führung 81 relativ zum Schließelement 31 in axialer Richtung bewegbar. Vorteil dieser Ausführungsform ist es, dass der Dämpfungsraum 71 nur beim Schließen des Schaltventils 17 als Dämpfer wirkt und nicht auch beim Öffnen des Schaltventils 17. Hierdurch wird ein ungewolltes Verzögern der Ventilöffnungsbewegung verhindert. Beim Öffnen des Schaltventils 17 bewegt sich zunächst das Schließelement 31 in Richtung der Magnetbaugruppe 63. Dies führt zu einer Vergrößerung des Volumens des Dämpfungsraums 71, da sich die Stirnfläche 65 des Schließelementes 31 aus dem Dämpfungsraum 71 bewegt. Dies führt zu einem Druckabfall im Dämpfungsraum 71. Da die Hülse bewegbar ist, wird diese zunächst ebenfalls in Richtung der Magnetbaugruppe 51 bewegt. Der abnehmende Druck im Dämpfungsraum 71 führt nicht zu einer Verzögerung der Öffnungsbewegung des Schließelementes sondern zu einer Bewegung der Hülse 61.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. When 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

Damit auch bei auf dem Ventilstück 5 aufliegender Hülse 61 die Verbindung vom Ablaufkanal 19 in den Rücklauf 21 nicht verschlossen ist, ist in der Hülse ein Kanal 87 ausgebildet, über den Kraftstoff aus dem Druckraum 43 bei geöffnetem Schaltventil 17 in den Niederdruckraum 57 strömen kann.Thus, even when resting on the valve piece 5 sleeve 61, the connection from the flow channel 19 in the return line 21 is not closed, a channel 87 is formed in the sleeve, can flow through the fuel from the pressure chamber 43 with the switching valve 17 open in the low-pressure chamber 57.

Der Resthub, ab dem die Bewegung des Schließelementes 31 gedämpft wird, bevor die Dichtkante 33 auf den Ventilsitz 35 einschlägt, ergibt sich aus der Höhe h1 der Hülse 61 und dem Abstand h2 zwischen der Stirnfläche 65 des Schließelementes 31 und der Dichtkante 33. Die zwei Maße h1 und h2 können sehr präzise gemessen, eingeschliffen und gefertigt werden. Das Überdeckungsmaß, das sich aus der Differenz der Höhe h1 der Hülse 61 und dem Abstand h2 zwischen der Stirnfläche 65 des Schließelementes 31 und der Dichtkante 33 ergibt, und durch das der Resthub definiert wird, kann vor dem Zusammenbau des Injektors 1 gemessen und gegebenenfalls durch Auswahlgruppen exakt eingestellt werden. Ein auf wändiger Einstellprozess, bei dem das Maß im zusammengebauten Zustand ermittelt und korrigiert werden muss, ist aufgrund der bauteilunabhängigen Fertigungsmaße h1 und h2 nicht erforderlich. Die Einfachheit des Einstellprozesses wird auch dadurch begründet, dass beide Maße h1 und h2 auf den gleichen Bezugspunkt, nämlich den Ventilsitz 35, ausgerichtet sind. Dies ist bei dem erfindungsgemäßen Injektor 1 darauf zurückzuführen, dass das Ventilstück 5 eine plangeschliffene Oberfläche aufweist, die einerseits den Ventilsitz 35 ausbildet und auf der auch die Hülse 61 aufliegt.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 Überdeckungsmaß 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. An on wähliger adjustment process, in which the measure in the assembled state must be determined and corrected, is not required due to the component-independent manufacturing dimensions h 1 and h 2 . The simplicity of the adjustment process is also justified by the fact that both dimensions h 1 and h 2 are aligned with the same reference point, namely the valve seat 35. In the case of the injector 1 according to the invention, this is due to the fact that the valve piece 5 has a surface-ground surface which, on the one hand, forms the valve seat 35 and on which the sleeve 61 rests.

Ein weiterer Vorteil des erfindungsgemäß ausgebildeten Schaltventils 17 ist auch, dass das Volumen des Dämpfungsraums 71 keinen Einfluss auf die Funktion hat, da die Flüssigkeit, bei Einsatz als Kraftstoffinjektor somit der Kraftstoff, bei dem geringen Druckniveau im Rücklauf als inkompressibel betrachtet werden kann.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.

Claims (11)

  1. Switching valve for injectors, in particular for fuel injectors (1), comprising a closing element (31) by means of which a control chamber (9) can be relieved of pressure for the actuation of an injection valve element (3), wherein the closing element (31) is operated by a magnet actuator comprising a magnet assembly (51) and an armature (49), wherein the closing element (31) is connected to a stop element in such a way that the stop element and the closing element (31) enclose a damping chamber (71), wherein the damping chamber (71) is filled with liquid, characterized in that, during a movement of the closing element (31), the amount of liquid in the damping chamber (71) remains substantially constant, such that the closing element (31) and stop element move conjointly.
  2. Switching valve according to Claim 1, characterized in that the stop element is formed as a sleeve (61).
  3. Switching valve according to Claim 2, characterized in that the closing element (31) is guided in the sleeve (61), wherein the damping chamber (71) is formed between an upper end face (63), which points in the direction of the magnet assembly (51), of the sleeve (61) and an end face (65), which is situated opposite the upper end face (63) of the sleeve (61), of the closing element (31).
  4. Switching valve according to Claim 3, characterized in that the upper end face (63) of the sleeve (61) is terminated by an annular edge (67) in such a way that the inner side of the annular edge (67) and the outer side of the end face (65) of the closing element (31) form an annular gap (69) during the closing of the switching valve (17) and when the switching valve (17) is closed.
  5. Switching valve according to one of Claims 1 to 4, characterized in that the sleeve (61) is movable in the axial direction relative to the closing element (31).
  6. Switching valve according to Claim 5, characterized in that a plate-shaped widened portion (85) is formed on the sleeve (61) and a spring element (83) is mounted with one side on the plate-shaped widened portion (85) on the sleeve (61) and with the other side against the armature (49).
  7. Switching valve according to one of Claims 1 to 6, characterized in that the closing element (31) is of sleeve-shaped form and is guided on a guide pin (39).
  8. Switching valve according to Claim 7, characterized in that an annular chamber (77) is formed on the guide pin (39) between an upper guide (75) and a lower guide (73) of the closing element (31).
  9. Switching valve according to Claim 8, characterized in that leakage gaps are formed in each case by the upper guide (75) and the lower guide (73), such that the upper guide (75) and the lower guide (73) act as pressure distributors and the pressure in the annular chamber (77) can be set by means of the gap dimension of the upper guide (75) and of the lower guide (73).
  10. Switching valve according to Claim 8 or 9, characterized in that the annular chamber (77) is connected via a duct (79) in the closing element (31) to the damping chamber (71) between the upper end face (63) of the sleeve (61) and the end face (65) of the closing element (31).
  11. Switching valve according to one of Claims 7 to 10, characterized in that the closing element (31) has a sealing surface or sealing edge (33) of annular form and has a constant inner diameter (37) over its entire length.
EP08859206A 2007-12-10 2008-11-14 On-off valve for injectors Not-in-force EP2229527B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710059265 DE102007059265A1 (en) 2007-12-10 2007-12-10 Switching valve for injectors
PCT/EP2008/065591 WO2009074426A1 (en) 2007-12-10 2008-11-14 On-off valve for injectors

Publications (2)

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

Family

ID=40243768

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08859206A Not-in-force EP2229527B1 (en) 2007-12-10 2008-11-14 On-off valve for injectors

Country Status (4)

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

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029009A1 (en) * 2009-08-31 2011-03-03 Robert Bosch Gmbh Injector for injecting fuel

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19650865A1 (en) 1996-12-07 1998-06-10 Bosch Gmbh Robert magnetic valve
DE10122168A1 (en) 2001-05-08 2002-11-14 Bosch Gmbh Robert Solenoid valve for controlling an injection valve of an internal combustion engine

Also Published As

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

Similar Documents

Publication Publication Date Title
EP2220360B1 (en) Switching valve for injectors
EP1259729B1 (en) Electromagnetic valve for controlling an injection valve of an internal combustion engine
EP1332282B1 (en) Electromagnetic valve for controlling an injection valve of an internal combustion engine
EP1387940B1 (en) Fuel injection valve for internal combustion engines
EP2628938B1 (en) Fuel injector valve
WO2009121646A1 (en) Solenoid valve with multiple-part armature without armature guide
DE10060812A1 (en) Fuel injection system for internal combustion engines
DE10060811A1 (en) Fuel injection system for internal combustion engines
EP2510215B1 (en) Fuel injector
EP1387937B1 (en) Fuel injection valve for internal combustion engines with damping chamber reducing pressure oscillations
WO2008049666A1 (en) Injector having a control valve which has a conical stroke stop face
EP2100026A1 (en) Fuel injector having a solenoid valve with a spherical seat
WO2002092991A1 (en) Electromagnetic valve for controlling an injection valve of an internal combustion engine
WO2008110408A1 (en) Fuel injector comprising an improved control valve
DE102007058766A1 (en) Control valve for a fuel injector
DE102009045728A1 (en) Magnetic valve for use in common-rail injector, has valve housing actuated by armatures in uncontrolled state of magnetic coil, where movement of housing is delayed using damping elements in direction of valve seat
EP2229527B1 (en) On-off valve for injectors
WO2009074427A1 (en) On-off valve for injectors
EP2733345A1 (en) Pressure control valve for a high pressure storage tank of a combustion engine
DE102008000697A1 (en) Switching valve for injectors, particularly for fuel injectors, has closing element, with which control chamber is pressure released for actuating injection valve unit
DE102008000929A1 (en) Hydraulic damping
EP1887213B1 (en) Fuel injector with direct pin control and servo-valve support
EP2275666A1 (en) Fuel injector with pressure-equalised control valve
EP3095998B1 (en) Fuel injector
WO2008128884A1 (en) Fuel injector with a magnetic valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20100712

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 600950

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008009501

Country of ref document: DE

Effective date: 20130508

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130613

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130624

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130613

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130313

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130715

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130713

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

26N No opposition filed

Effective date: 20131216

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008009501

Country of ref document: DE

Effective date: 20131216

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20131130

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20131114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131130

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131114

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 600950

Country of ref document: AT

Kind code of ref document: T

Effective date: 20131114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131114

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20081114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190124

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20191121

Year of fee payment: 12

Ref country code: IT

Payment date: 20191120

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008009501

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200603

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201130

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20201114