EP2021617B1 - Fuel injector comprising a pressure-compensated control valve - Google Patents

Fuel injector comprising a pressure-compensated control valve Download PDF

Info

Publication number
EP2021617B1
EP2021617B1 EP07727028A EP07727028A EP2021617B1 EP 2021617 B1 EP2021617 B1 EP 2021617B1 EP 07727028 A EP07727028 A EP 07727028A EP 07727028 A EP07727028 A EP 07727028A EP 2021617 B1 EP2021617 B1 EP 2021617B1
Authority
EP
European Patent Office
Prior art keywords
armature
fuel injector
valve
injector according
valve seat
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.)
Active
Application number
EP07727028A
Other languages
German (de)
French (fr)
Other versions
EP2021617A1 (en
Inventor
Nadja Eisenmenger
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 EP2021617A1 publication Critical patent/EP2021617A1/en
Application granted granted Critical
Publication of EP2021617B1 publication Critical patent/EP2021617B1/en
Active 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • 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
    • 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 an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1, such as in WO 03/002868 or EP 1319827 Tide.
  • An injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member is actuated via a solenoid-operated control valve is for example off EP-A 1612 403 known.
  • a flow restrictor from a control room in the fuel return can be closed or released.
  • the control chamber is bounded on one side by a control piston with which an injection valve member is actuated, which releases or closes at least one injection opening into the combustion chamber of the internal combustion engine.
  • the outlet throttle is received in a body, which is provided on the side facing away from the control chamber with a tapered valve seat.
  • a closing element is adjustable, which is connected to the armature of the solenoid valve.
  • an edge is formed on the closing element, which is provided against the conically shaped seat.
  • the closing element moves on an axial rod, which is integrally connected to the body in which the drainage throttle is formed.
  • an injection valve member for releasing and closing at least one injection port by a solenoid valve trained control valve controlled.
  • a sealing surface is formed, which is adjustable for closing the control valve in a valve seat.
  • the armature of the solenoid valve is movable without an armature guide between an upper and a lower stroke stop.
  • Characterized in that the sealing surface is formed on the armature, which is adjustable for closing the control valve in the valve seat, can be dispensed with an additional closing element, as provided in the prior art. This minimizes the mass of moving components. By minimizing the mass of the moving components, shorter switching times can be realized.
  • Another advantage of forming the sealing surface directly at the armature of the solenoid valve is that the solenoid valve thereby requires little space.
  • a liquid-tight closure of the solenoid valve by the sealing surface is placed on the anchor in the valve seat, is achieved by the fact that the sealing surface is aligned with the anchor on the lower stroke stop.
  • This alignment takes place in a preferred embodiment by means of a resilient guide lip, which is formed on the armature.
  • the guide lip is preferably formed on the outer diameter of the armature. If the anchor begins to wobble during the closing movement, the anchor will first strike with the guide lip. In the further movement is characterized in that the guide lip is designed resiliently, the armature aligned so that the sealing surface rests flat on the valve seat and thus a liquid-tight connection is generated.
  • the movement of the armature in the lower stroke stop is carried out by means of a spring element.
  • the spring element is preferably a helical spring designed as a compression spring.
  • the inner diameter of the spring element preferably corresponds substantially to the inner diameter of the valve seat. Due to the elasticity of the resilient guide lip is achieved that is lost to this little of the spring force of the spring element.
  • the guide lip and the sealing surface on the armature and the stop surface and the valve seat of the control valve are ground to the same height.
  • the upper stroke stop is preferably formed by an annular surface.
  • the armature is designed so that the respective opposite surfaces on which an axial compressive force acts are the same size and are acted upon by the same pressure.
  • the anchor is a Run bore whose diameter corresponds substantially to the inner diameter of the valve seat.
  • a push rod is received in the bore.
  • the bore is honed in a preferred embodiment.
  • the push rod and the bore are made in a tight leadership game.
  • the abutment surface for the resilient guide lip and the valve seat are formed on a valve piece. This is accommodated in the injector housing. By forming the abutment surface and the valve seat on the valve piece, it is possible to produce them on an outer surface. It is not necessary to just grind an end face of a hole.
  • the spring force of the spring element by which the movement of the armature is supported by the magnet in the valve seat, is preferably adjusted by a disc. This is done by the spring element is biased by the disc. The larger the axial extent of the disc, the stronger the spring element is biased and the greater the spring force acting on the anchor.
  • the disc is arranged on the side facing away from the armature of the spring element. In a preferred embodiment, however, the disc is arranged between the spring element and the armature. Advantage of this arrangement is that the disc with which the spring force is adjusted, so can be used in addition to the centering of the armature.
  • the push rod in another embodiment comprises a pressure pin and a bolt, wherein the bolt is received in the bore in the armature and the pressure pin is enclosed by the spring element.
  • the tilting is avoided in particular by the fact that the bolt is tiltable relative to the pressure pin. This is achieved, for example, in that the mutually facing ends of the pressure pin and the bolt are crowned, ie preferably in the form of a spherical section.
  • any further, known in the art design is possible, with which the bolt can be bent relative to the pressure pin from the axial alignment.
  • FIG. 1 shows a section of an inventively designed fuel injector with solenoid valve in a first embodiment.
  • a control piston 2 with which an injection valve member, not shown here, is actuated is actuated by a solenoid valve 3. At least one injection opening is released or closed by the injection valve member, thus controlling the injection of fuel into a combustion chamber of an internal combustion engine.
  • the movement of the control piston 2 takes place hydraulically.
  • the control piston 2 opens with the side facing away from the injection valve member in a control chamber 4.
  • the control chamber 4 is connected to a fuel inlet 6.
  • fuel under system pressure can flow into the control chamber 4.
  • the outlet throttle 7 with an in FIG. 1 not shown return hydraulically connected.
  • the outlet throttle 7 can be closed by means of the solenoid valve 3.
  • a sealing surface 8 which is formed on the armature 9 of the solenoid valve 3, placed in a valve seat 10.
  • the sealing surface 8 and the valve seat 10 form a flat seat.
  • any further, known in the art valve seat in which no axial forces acting on the closing element.
  • a bore 11 is formed in the armature 9, in which a pressure rod 12 is received. So that no axial pressure forces act on the armature 9 when the valve is closed, the diameter of the bore 11 is substantially equal to the inner diameter of the sealing surface 8.
  • Another object of the push rod 12 is to seal the bore 11 against leakage currents. For this reason, it is necessary that the push rod 12 and the bore 11 are made in a close guide play. Compared with the known from the prior art fuel injectors, however, it is not necessary to manufacture the bore 11 and the sealing surface 8 on the armature 9 in a clamping in order to obtain a precise rectangular alignment of the sealing surface 8 and 9 hole. As a result, the manufacture of the armature 9 is simplified.
  • the upper stroke stop of the armature 9 is formed by an annular surface 14, which is designed as a lower end face of a Hubanschlaghülse 15.
  • a bore 16 is formed in the Hubanschlagshülse 15, in which a spring element 17 is received.
  • the spring element 17 is preferably designed as a compression spring coil spring which is supported on one side of the armature 9 and the other side on a disc 18.
  • the disc 18 is placed against an end face 19 of the bore 16. By means of the axial extent of the disc 18, the spring force can be adjusted, with which the spring element 17 acts on the armature 9.
  • the solenoid valve 3 comprises a magnet 20 which is accommodated in a magnetic core 21.
  • the support of the elastic guide lip 13, which rests on the support surface 22 and the sealing surface 8 ground on the armature 9 to a height.
  • the stroke of the armature 9 is limited by the Hubanschlaghülse 15.
  • the armature 9 and the magnetic core 21 are enclosed by a sleeve 23, by the axial extent of the stroke is determined.
  • To adjust the stroke is the Hubanschlaghülse 15 with an end face 24 on the sleeve 23 on this.
  • valve piece 25 which is received in the injector 26.
  • a bore 29 is formed in this for each pin 28.
  • the pins 28 are each surrounded by a lower disc 30, an upper disc 31 and an intermediate sealing ring 32.
  • the inventively embodied solenoid valve 3 can be used both inversely controlled fuel injectors as well as not inversely controlled fuel injectors.
  • the magnet 20 of the solenoid valve 3 is energized in a non-inversely controlled fuel injector. Not inverted means that when energized magnet 20, the at least one injection port is released and fuel is injected into the combustion chamber of the internal combustion engine.
  • a magnetic field is formed, through which the armature 9 is attracted by the magnet 20 and thus moves in the direction of the magnet 20.
  • the sealing surface 8 of the armature 9 lifts out of the valve seat 10 and a connection from the control chamber 4 via the outlet throttle 7 in the return, not shown here is released. Due to the released connection, fuel can drain from the control chamber 4. This leads to a pressure drop in the control chamber 4.
  • the stroke of the armature 9 is limited by the Hubanschlaghülse 15 by the armature 9 abuts against the annular surface 14 of the Hubanschlaghülse 15.
  • An axial guidance of the armature 9 is effected by an extension 34 on the armature 9, which is guided in the bore 16 of the Hubantschhülse 15.
  • the holes 16 and the extension 34 are not mating ground on anchor 9, so that despite the small stroke, generally in the range between 0.02 to 0.04 millimeters, a tumbling of the armature 9 is not can be prevented.
  • the resilient guide lip 13 is formed on the armature 9. Due to the resilient guide lip 13, the armature 9 is prevented from tilting even when the spring force of the spring element 17 acts unevenly on the armature. If there is a tilting of the armature 9, the resilient guide lip 13 abuts against the support surface 22 and thereby prevents further tilting of the armature. 9
  • An inversely controlled fuel injector differs from the non-inversely controlled fuel injector in that, when the magnet is energized, the at least one injection opening is closed and the at least one injection opening is released when the magnet is not energized.
  • the control piston 2 and the injection valve member are coupled to each other hydraulically, which is lifted in a movement of the control piston 2 in the direction of the injection valve member from the seat and the at least one injection opening releases and is energized with energized magnet of the control piston 2 in the direction of the control chamber 4 , whereby the injection valve member is placed in its seat and closes the at least one injection opening.
  • FIG. 2 is a second embodiment of an inventively designed solenoid valve 3 is shown.
  • the FIG. 2 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that a disc 35, with which the spring force of the spring element 17 is adjusted, is received between the spring element 17 and the armature 9.
  • the spring element 17 is supported with one side against the disc 25 and with the other side against the end face 19 of the bore 16.
  • the centering of the armature 9 is required so that it does not move radially and so the sealing surface 8 is no longer placed on the armature 9 on the valve seat 10 when the outlet throttle 7 is closed.
  • FIG. 3 shows a solenoid valve 3 in a third embodiment.
  • the push rod 12 comprises a bolt 36 and a pressure pin 37.
  • the bolt 36 is guided in the bore 11 in the armature 9.
  • the push rod 12 includes the pressure pin 37 and the bolt 36, it is avoided that the armature 9 can tilt on the push rod 12 when it begins to wobble due to uneven application of force by the spring element 17.
  • the bolt 36 and the pressure pin 37 are designed so that the bolt 36 can tilt over the pressure pin 37 from the axial direction.
  • at least either the pressure pin 37 on the side facing the bolt 36 or the bolt 36 on the side facing the pressure pin 37 is preferably provided with a crowned end face.
  • having a spherical design means that the end face is designed in the form of a spherical segment, a paraboloid or a hyperboloid.
  • both the end face of the pressure pin 37 facing the pin 36 and the end face of the pin 36 facing the pressure pin 37 are crowned.
  • a ball is received between the bolt 36 and the pressure pin 37.
  • the ball performs the same task as the spherically shaped facing end faces of the bolt 36 and the pressure pin 37th
  • Task of the push rod 12 is in all three embodiments, as shown in the Figure 1 to 3 are shown to absorb axial compressive forces.
  • the push rod 12 is supported against the end face 19 of the bore 16 in the Hubanschlaghülse 15.
  • the pressure force exerted on the push rod 12 is transmitted to the Hubanschlagshülse 15.

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)

Abstract

In a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, an injection valve member for opening and closing at least one injection opening is triggered by a control valve embodied as a magnet valve. On the armature of the magnet valve, a sealing face is embodied that for closing the control valve is positionable into a valve seat. The armature of the magnet valve is movable, without armature guidance, between an upper and a lower stroke stop. Because the sealing face, which for closing the control valve is positionable into the valve seat, is embodied on the armature, an additional closing element of the kind provided in the prior art can be dispensed with.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine gemäß dem Oberbegriff des Anspruchs 1, wie z.B. in WO 03/002868 oder EP 1319827 gezeit.The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1, such as in WO 03/002868 or EP 1319827 Tide.

Ein Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine, bei welchem ein Einspritzventilglied über ein magnetbetriebenes Steuerventil angesteuert wird ist zum Beispiel aus EP-A 1612 403 bekannt. Mit Hilfe des Steuerventils ist eine Ablaufdrossel aus einem Steuerraum in den Kraftstoffrücklauf verschließbar oder freigebbar. Der Steuerraum wird an einer Seite durch einen Steuerkolben begrenzt, mit welchem ein Einspritzventilglied angesteuert wird, welches mindestens eine Einspritzöffnung in den Brennraum der Verbrennungskraftmaschine freigibt oder verschließt. Die Ablaufdrossel ist in einen Körper aufgenommen, welcher auf der dem Steuerraum abgewandten Seite mit einem sich verjüngenden Ventilsitz versehen ist. In diesen Ventilsitz ist ein Schließelement stellbar, welches mit dem Anker des Magnetventils verbunden ist. Hierzu ist am Schließelement eine Kante ausgebildet, welche gegen den konisch ausgeformten Sitz gestellt wird. Das Schließelement bewegt sich auf einer axialen Stange, welche mit dem Körper, in den die Ablaufdrossel ausgebildet ist, einstückig verbunden ist.An injector for injecting fuel into a combustion chamber of an internal combustion engine, in which an injection valve member is actuated via a solenoid-operated control valve is for example off EP-A 1612 403 known. With the help of the control valve, a flow restrictor from a control room in the fuel return can be closed or released. The control chamber is bounded on one side by a control piston with which an injection valve member is actuated, which releases or closes at least one injection opening into the combustion chamber of the internal combustion engine. The outlet throttle is received in a body, which is provided on the side facing away from the control chamber with a tapered valve seat. In this valve seat, a closing element is adjustable, which is connected to the armature of the solenoid valve. For this purpose, an edge is formed on the closing element, which is provided against the conically shaped seat. The closing element moves on an axial rod, which is integrally connected to the body in which the drainage throttle is formed.

Damit das Ventil flüssigkeitsdicht schließt, ist es notwendig, hochpräzise Oberflächen herzustellen und eine hochgenaue Passung des Schließelementes auf der axialen Stange vorzusehen. Hierdurch wird das Schließelement exakt geführt und so sichergestellt, dass dieses den Sitz flüssigkeitsdicht verschließt.For the valve to close in a liquid-tight manner, it is necessary to produce high-precision surfaces and to provide a high-precision fit of the closing element on the axial rod. As a result, the closing element is exactly guided and thus ensured that it seals the seat liquid-tight.

Offenbarung der ErfindungDisclosure of the invention

Bei einem erfindungsgemäß ausgebildeten Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine wird ein Einspritzventilglied zum Freigeben und Verschließen mindestens einer Einspritzöffnung durch ein als Magnetventil ausgebildetes Steuerventil angesteuert. Am Anker des Magnetventils ist eine Dichtfläche ausgebildet, welche zum Verschließen des Steuerventils in einen Ventilsitz stellbar ist. Der Anker des Magnetventils ist ohne Ankerführung zwischen einem oberen und einem unteren Hubanschlag bewegbar. Dadurch, dass am Anker die Dichtfläche ausgebildet ist, die zum Verschließen des Steuerventil in den Ventilsitz stellbar ist, kann auf ein zusätzliches Schließelement, wie es im Stand der Technik vorgesehen ist, verzichtet werden. Hierdurch lässt sich die Masse der bewegten Bauteile minimieren. Durch die Minimierung der Masse der bewegten Bauteile lassen sich kürzere Schaltzeiten realisieren. Ein weiterer Vorteil davon, die Dichtfläche direkt am Anker des Magnetventils auszubilden, liegt darin, dass das Magnetventil hierdurch wenig Bauraum benötigt.In an inventively designed fuel injector for injecting fuel into a combustion chamber of an internal combustion engine is an injection valve member for releasing and closing at least one injection port by a solenoid valve trained control valve controlled. At the armature of the solenoid valve, a sealing surface is formed, which is adjustable for closing the control valve in a valve seat. The armature of the solenoid valve is movable without an armature guide between an upper and a lower stroke stop. Characterized in that the sealing surface is formed on the armature, which is adjustable for closing the control valve in the valve seat, can be dispensed with an additional closing element, as provided in the prior art. This minimizes the mass of moving components. By minimizing the mass of the moving components, shorter switching times can be realized. Another advantage of forming the sealing surface directly at the armature of the solenoid valve is that the solenoid valve thereby requires little space.

Ein flüssigkeitsdichtes Verschließen des Magnetventils, indem die Dichtfläche am Anker in den Ventilsitz gestellt wird, wird dadurch erreicht, dass die Dichtfläche am Anker am unteren Hubanschlag ausgerichtet wird. Diese Ausrichtung erfolgt in einer bevorzugten Ausführungsform mittels einer federnden Führungslippe, welche am Anker ausgebildet ist. Die Führungslippe ist dabei vorzugsweise am Außendurchmesser des Ankers ausgebildet. Wenn der Anker so bei der Schließbewegung zu taumeln beginnt, wird der Anker zunächst mit der Führungslippe anschlagen. In der weiteren Bewegung wird dadurch, dass die Führungslippe federnd ausgeführt ist der Anker so ausgerichtet, dass die Dichtfläche am Anker plan auf dem Ventilsitz aufliegt und so eine flüssigkeitsdichte Verbindung erzeugt wird. Die Bewegung des Ankers in den unteren Hubanschlag wird mit Hilfe eines Federelementes ausgeführt. Das Federelement ist dabei vorzugsweise eine als Druckfeder ausgebildete Spiralfeder. Damit die Krafteinleitung möglichst dicht im Bereich des Ventilssitzes erfolgt, entspricht der Innendurchmesser des Federelementes vorzugsweise im Wesentlichen dem Innendurchmesser des Ventilsitzes. Aufgrund der Elastzitität der federnden Führungslippe wird erreicht, dass an dieser nur wenig der Federkraft des Federelementes verloren geht.A liquid-tight closure of the solenoid valve by the sealing surface is placed on the anchor in the valve seat, is achieved by the fact that the sealing surface is aligned with the anchor on the lower stroke stop. This alignment takes place in a preferred embodiment by means of a resilient guide lip, which is formed on the armature. The guide lip is preferably formed on the outer diameter of the armature. If the anchor begins to wobble during the closing movement, the anchor will first strike with the guide lip. In the further movement is characterized in that the guide lip is designed resiliently, the armature aligned so that the sealing surface rests flat on the valve seat and thus a liquid-tight connection is generated. The movement of the armature in the lower stroke stop is carried out by means of a spring element. The spring element is preferably a helical spring designed as a compression spring. Thus, the introduction of force as close as possible in the region of the valve seat, the inner diameter of the spring element preferably corresponds substantially to the inner diameter of the valve seat. Due to the elasticity of the resilient guide lip is achieved that is lost to this little of the spring force of the spring element.

In einer bevorzugten Ausführungsform sind die Führungslippe und die Dichtfläche am Anker sowie die Anschlagfläche und der Ventilsitz des Steuerventils auf gleiche Höhe geschliffen. Hierdurch lässt sich der Ventilsitz des Magnetventils kostengünstig fertigen, da das Paaren mit einem zweiten Bauteil entfällt.In a preferred embodiment, the guide lip and the sealing surface on the armature and the stop surface and the valve seat of the control valve are ground to the same height. As a result, the valve seat of the solenoid valve can be manufactured cost-effectively, since the pairing with a second component is eliminated.

Der obere Hubanschlag wird vorzugsweise durch eine Ringfläche gebildet. Durch das Anschlagen an die Ringfläche richtet sich der Anker, der während der Flugphase ins Taumeln geraten kann, wieder aus.The upper stroke stop is preferably formed by an annular surface. By hitting the ring surface, the anchor, which can get into tumbling during the flight phase, aligns again.

Um einen axialen Druckausgleich zu erreichen, ist der Anker so gestaltet, das die jeweils gegenüberliegenden Flächen, auf die eine axiale Druckkraft wirkt, gleich groß sind und vom gleichen Druck beaufschlagt werden. Um dies zu erreichen, ist im Anker eine Bohrung ausgeführt, deren Durchmesser im Wesentlichen dem Innendurchmesser des Ventilsitzes entspricht. Zur Aufnahme der Druckkräfte ist in der Bohrung eine Druckstange aufgenommen. Um den Kraftstoffleckagestrom durch den Spalt zwischen der Bohrung und der Druckstange möglichst gering zu halten, wird die Bohrung in einer bevorzugten Ausführungsform gehont. Auch sind die Druckstange und die Bohrung in einem engen Führungsspiel gefertigt. Es ist jedoch nicht erforderlich, die Bohrung und die Dichtfläche am Anker in einer Einspannung zu fertigen, um eine präzise rechtwinklige Ausrichtung von Dichtfläche und Bohrung zu erhalten. Hierdurch wird die Fertigung des Ankers vereinfacht.In order to achieve an axial pressure equalization, the armature is designed so that the respective opposite surfaces on which an axial compressive force acts are the same size and are acted upon by the same pressure. To achieve this, the anchor is a Run bore whose diameter corresponds substantially to the inner diameter of the valve seat. To accommodate the pressure forces a push rod is received in the bore. In order to minimize the fuel leakage through the gap between the bore and the push rod, the bore is honed in a preferred embodiment. Also, the push rod and the bore are made in a tight leadership game. However, it is not necessary to fabricate the bore and the sealing surface on the anchor in a clamping to obtain a precise right-angled alignment of sealing surface and bore. As a result, the production of the armature is simplified.

Im Allgemeinen sind die Anschlagfläche für die federnde Führungslippe und der Ventilsitz an einem Ventilstück ausgebildet. Dieses ist im Injektorgehäuse aufgenommen. Durch das Ausbilden der Anschlagfläche und des Ventilsitzes am Ventilstück, ist es möglich, diese an einer außenliegenden Oberfläche herzustellen. Es ist nicht erforderlich, eine Stirnfläche einer Bohrung eben zu schleifen.In general, the abutment surface for the resilient guide lip and the valve seat are formed on a valve piece. This is accommodated in the injector housing. By forming the abutment surface and the valve seat on the valve piece, it is possible to produce them on an outer surface. It is not necessary to just grind an end face of a hole.

Die Federkraft des Federelementes, durch welche die Bewegung des Ankers vom Magneten in den Ventilsitz unterstützt wird, wird vorzugsweise durch eine Scheibe eingestellt. Dies erfolgt dadurch, dass das Federelement durch die Scheibe vorgespannt wird. Je größer die axiale Ausdehnung der Scheibe ist, desto stärker wird das Federelement vorgespannt und umso größer ist die Federkraft, die auf den Anker wirkt.The spring force of the spring element, by which the movement of the armature is supported by the magnet in the valve seat, is preferably adjusted by a disc. This is done by the spring element is biased by the disc. The larger the axial extent of the disc, the stronger the spring element is biased and the greater the spring force acting on the anchor.

Im Allgemeinen ist die Scheibe auf der dem Anker abgewandten Seite des Federelementes angeordnet. In einer bevorzugten Ausführungsform ist die Scheibe jedoch zwischen dem Federelement und dem Anker angeordnet. Vorteil dieser Anordnung ist, dass die Scheibe, mit der die Federkraft eingestellt wird, so zusätzlich zum Zentrieren des Ankers verwendet werden kann.In general, the disc is arranged on the side facing away from the armature of the spring element. In a preferred embodiment, however, the disc is arranged between the spring element and the armature. Advantage of this arrangement is that the disc with which the spring force is adjusted, so can be used in addition to the centering of the armature.

Um zu vermeiden, dass der Anker bei der Öffnungs- bzw. Schließbewegung verkantet, umfasst die Druckstange in einer weiteren Ausfiihrungsform einem Druckstift und einen Bolzen, wobei der Bolzen in der Bohrung im Anker aufgenommen ist und der Druckstift vom Federelement umschlossen ist. Das Verkanten wird insbesondere dadurch vermieden, dass der Bolzen gegenüber dem Druckstift kippbar ist. Dies wird zum Beispiel dadurch erreicht, dass die einander zugewandten Enden des Druckstiftes und des Bolzens ballig, d. h. vorzugsweise in Form eines Kugelabschnittes, ausgeführt sind. Alternativ ist es auch möglich, zwischen dem Druckstift und dem Bolzen eine Kugel aufzunehmen. Auch ist jede weitere, dem Fachmann bekannte Gestaltung möglich, mit der sich der Bolzen gegenüber dem Druckstift aus der axialen Ausrichtung abknicken lässt.In order to avoid that the armature canted during the opening or closing movement, the push rod in another embodiment comprises a pressure pin and a bolt, wherein the bolt is received in the bore in the armature and the pressure pin is enclosed by the spring element. The tilting is avoided in particular by the fact that the bolt is tiltable relative to the pressure pin. This is achieved, for example, in that the mutually facing ends of the pressure pin and the bolt are crowned, ie preferably in the form of a spherical section. Alternatively, it is also possible to take a ball between the pressure pin and the bolt. Also, any further, known in the art design is possible, with which the bolt can be bent relative to the pressure pin from the axial alignment.

Zeichnungdrawing

Im Folgenden wird die Erfindung anhand einer Zeichnung näher beschrieben.
Darin zeigt:

  • Figur 1 einen Ausschnitt aus einen Kraftstoffinjektor mit einem erfindungsgemäß ausgebildeten Magnetventil in einer ersten Ausführungsform,
  • Figur 2 ein erfindungsgemäß ausgeführtes Magnetventil in einer zweiten Ausführungsform,
  • Figur 3 ein erfindungsgemäß ausgeführtes Magnetventil in einer dritten Ausführungsform.
In the following the invention will be described in more detail with reference to a drawing.
It shows:
  • FIG. 1 a detail of a fuel injector with an inventively designed solenoid valve in a first embodiment,
  • FIG. 2 a solenoid valve according to the invention in a second embodiment,
  • FIG. 3 an inventively designed solenoid valve in a third embodiment.

Ausführungsbeispieleembodiments

Figur 1 zeigt einen Ausschnitt aus einem erfindungsgemäß ausgebildeten Kraftstoffinjektor mit Magnetventil in einer ersten Ausführungsform. FIG. 1 shows a section of an inventively designed fuel injector with solenoid valve in a first embodiment.

Bei einem erfindungsgemäß ausgebildeten Kraftstoffinjektor 1 wird ein Steuerkolben 2 mit dem ein hier nicht dargestelltes Einspritzventilglied angesteuert wird, durch ein Magnetventil 3 angesteuert. Durch das Einspritzventilglied wird mindestens eine Einsphtzöfnung freigegeben oder verschlossen und so das Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine gesteuert.In a fuel injector 1 designed according to the invention, a control piston 2 with which an injection valve member, not shown here, is actuated, is actuated by a solenoid valve 3. At least one injection opening is released or closed by the injection valve member, thus controlling the injection of fuel into a combustion chamber of an internal combustion engine.

Die Bewegung des Steuerkolbens 2 erfolgt hydraulisch. Hierzu mündet der Steuerkolben 2 mit der dem Einspritzventilglied abgewandten Seite in einen Steuerraum 4. Über eine Zulaufdrossel 5 ist der Steuerraum 4 mit einem Kraftstoffzulauf 6 verbunden. Hierdurch kann unter Systemdruck stehender Kraftstoff in den Steuerraum 4 einströmen. Über eine Ablaufdrossel 7 ist der Steuerraum 4 entlastbar. Hierzu ist die Ablaufdrossel 7 mit einem in Figur 1 nicht dargestellten Rücklauf hydraulisch verbunden. Um den Steuerraum 4 mit unter Systemdruck stehende Kraftstoffe füllen zu können, ist die Ablaufdrossel 7 mit Hilfe des Magnetventils 3 verschließbar. Hierzu wird bei den erfindungsgemäß ausgebildeten Magnetventil 3 eine Dichtfläche 8, die am Anker 9 des Magnetventils 3 ausgebildet ist, in einen Ventilsitz 10 gestellt. In der hier dargestellten Ausführungsform bilden die Dichtfläche 8 und der Ventilsitz 10 einen Flachsitz. Es ist jedoch auch jeder weitere, dem Fachmann bekannte Ventilsitz, bei dem keine axialen Kräfte auf das Schließelement wirken, denkbar.The movement of the control piston 2 takes place hydraulically. For this purpose, the control piston 2 opens with the side facing away from the injection valve member in a control chamber 4. About an inlet throttle 5, the control chamber 4 is connected to a fuel inlet 6. As a result, fuel under system pressure can flow into the control chamber 4. About an outlet throttle 7, the control chamber 4 is relieved. For this purpose, the outlet throttle 7 with an in FIG. 1 not shown return hydraulically connected. In order to fill the control chamber 4 with fuel under system pressure, the outlet throttle 7 can be closed by means of the solenoid valve 3. For this purpose, in the inventively embodied solenoid valve 3, a sealing surface 8, which is formed on the armature 9 of the solenoid valve 3, placed in a valve seat 10. In the embodiment shown here, the sealing surface 8 and the valve seat 10 form a flat seat. However, it is also conceivable any further, known in the art valve seat, in which no axial forces acting on the closing element.

Um bei verschlossenem Magnetventil 3 die in axialer Richtung wirkende Druckkraft aufzunehmen, ist im Anker 9 eine Bohrung 11 ausgebildet, in der eine Druckstange 12 aufgenommen ist. Damit bei verschlossenem Ventil keine axialen Druckkräfte auf den Anker 9 wirken, ist der Durchmesser der Bohrung 11 im Wesentlichen gleich dem Innendurchmesser der Dichtfläche 8. Eine weitere Aufgabe der Druckstange 12 ist es, die Bohrung 11 gegen Leckageströme abzudichten. Aus diesem Grund ist es notwendig, dass die Druckstange 12 und die Bohrung 11 in einem engen Führungsspiel gefertigt sind. Gegenüber den aus dem Stand der Technik bekannten Kraftstoffinjektoren ist es jedoch nicht erforderlich, die Bohrung 11 und die Dichtfläche 8 am Anker 9 in einer Einspannung zu fertigen, um eine präzise rechtwinklige Ausrichtung von Dichtfläche 8 und Bohrung 9 zu erhalten. Hierdurch wird die Fertigung des Ankers 9 vereinfacht.In order to receive the pressure force acting in the axial direction when the solenoid valve 3 is closed, a bore 11 is formed in the armature 9, in which a pressure rod 12 is received. So that no axial pressure forces act on the armature 9 when the valve is closed, the diameter of the bore 11 is substantially equal to the inner diameter of the sealing surface 8. Another object of the push rod 12 is to seal the bore 11 against leakage currents. For this reason, it is necessary that the push rod 12 and the bore 11 are made in a close guide play. Compared with the known from the prior art fuel injectors, however, it is not necessary to manufacture the bore 11 and the sealing surface 8 on the armature 9 in a clamping in order to obtain a precise rectangular alignment of the sealing surface 8 and 9 hole. As a result, the manufacture of the armature 9 is simplified.

Um den Anker 9 am unteren Hubanschlag, d.h. wenn die Dichtfläche 8 im Ventilsitz 10 steht, auszurichten, ist an diesem eine elastische Führungslippe 13 ausgebildet. Der obere Hubanschlag des Ankers 9 wird durch eine Ringfläche 14 gebildet, welche als untere Stirnfläche einer Hubanschlaghülse 15 ausgeführt ist.To move the armature 9 at the lower stroke stop, i. When the sealing surface 8 is in the valve seat 10 to align, an elastic guide lip 13 is formed on this. The upper stroke stop of the armature 9 is formed by an annular surface 14, which is designed as a lower end face of a Hubanschlaghülse 15.

In der hier dargestellten Ausführungsform ist in der Hubanschlagshülse 15 eine Bohrung 16 ausgebildet, in der ein Federelement 17 aufgenommen ist. Das Federelement 17 ist vorzugsweise eine als Druckfeder ausgeführte Spiralfeder, welche sich mit einer Seite am Anker 9 und mit der anderen Seite an einer Scheibe 18 abstützt. Die Scheibe 18 dabei gegen eine Stirnfläche 19 der Bohrung 16 gestellt. Mittels der axialen Ausdehnung der Scheibe 18 lässt sich die Federkraft einstellen, mit der das Federelement 17 auf den Anker 9 wirkt.In the embodiment shown here, a bore 16 is formed in the Hubanschlagshülse 15, in which a spring element 17 is received. The spring element 17 is preferably designed as a compression spring coil spring which is supported on one side of the armature 9 and the other side on a disc 18. The disc 18 is placed against an end face 19 of the bore 16. By means of the axial extent of the disc 18, the spring force can be adjusted, with which the spring element 17 acts on the armature 9.

Weiterhin umfasst das Magnetventil 3 einen Magneten 20, der in einem Magnetkern 21 aufgenommen ist. Die Spannungsversorgung des Magneten 20 erfolgt über Stifte 28.Furthermore, the solenoid valve 3 comprises a magnet 20 which is accommodated in a magnetic core 21. The power supply of the magnet 20 via pins 28th

Um eine ebene Auflage der Dichtfläche 8 am Anker 9 auf dem Ventilsitz 10 zu erreichen, sind der Ventilsitz 10 sowie eine Auflagefläche 22, auf der die elastische Führungslippe 13 aufliegt, wenn der Anker 9 am unteren Hubanschlag liegt, auf eine Höhe geschliffen. Ebenso sind die Auflage der elastischen Führungslippe 13, die auf der Auflagefläche 22 aufliegt und die Dichtfläche 8 am Anker 9 auf eine Höhe geschliffen.In order to achieve a flat support of the sealing surface 8 on the armature 9 on the valve seat 10, the valve seat 10 and a support surface 22 on which the elastic guide lip 13 rests when the armature 9 is located at the lower stroke stop, ground to a height. Likewise, the support of the elastic guide lip 13, which rests on the support surface 22 and the sealing surface 8 ground on the armature 9 to a height.

Der Hub des Ankers 9 wird durch die Hubanschlaghülse 15 begrenzt. Um den Hub einzustellen, sind der Anker 9 und der Magnetkern 21 von einer Hülse 23 umschlossen, durch deren axiale Ausdehnung der Hub festgelegt wird. Zur Einstellung des Hubes liegt hierzu die Hubanschlaghülse 15 mit einer Stirnfläche 24 auf der Hülse 23 auf.The stroke of the armature 9 is limited by the Hubanschlaghülse 15. To adjust the stroke, the armature 9 and the magnetic core 21 are enclosed by a sleeve 23, by the axial extent of the stroke is determined. To adjust the stroke is the Hubanschlaghülse 15 with an end face 24 on the sleeve 23 on this.

Die Zulaufdrossel 5, die Ablaufdrossel 7 sowie der Ventilsitz 10 und die Auflagefläche 22 sind an einem Ventilstück 25 ausgebildet, welches im Injektorgehäuse 26 aufgenommen ist. Die Befestigung des Ventilstückes 25 im Injektorgehäuse 26 erfolgt mittels einer Ventilspannschraube 27.The inlet throttle 5, the outlet throttle 7 and the valve seat 10 and the bearing surface 22 are formed on a valve piece 25 which is received in the injector 26. The attachment of the valve piece 25 in the injector 26 by means of a valve clamping screw 27th

Um die Stifte 28 durch die Hubanschlaghülse 15 zu führen, ist in dieser für jeden Stift 28 eine Bohrung 29 ausgebildet. Zur Abdichtung und Zentrierung der Stifte 28 der Bohrung 29 sind die Stifte 28 jeweils von einer unteren Scheibe 30, einer oberen Scheibe 31 und einem dazwischen liegenden Dichtring 32 umschlossen.To guide the pins 28 through the Hubanschlaghülse 15, a bore 29 is formed in this for each pin 28. For sealing and centering of the pins 28 of the bore 29, the pins 28 are each surrounded by a lower disc 30, an upper disc 31 and an intermediate sealing ring 32.

Die Befestigung der Hubanschlaghülse 15 am Injektorgehäuse 26 erfolgt in der hier dargestellten Ausführungsform mit Hilfe einer Spannmutter 33.The attachment of Hubanschlaghülse 15 on the injector 26 takes place in the embodiment shown here by means of a clamping nut 33rd

Das erfindungsgemäß ausgebildete Magnetventil 3 ist sowohl bei invers angesteuerten Kraftstoffinjektoren als auch bei nicht invers angesteuerten Kraftstoffinjektoren einsetzbar.The inventively embodied solenoid valve 3 can be used both inversely controlled fuel injectors as well as not inversely controlled fuel injectors.

Um den Einspritzvorgang zu starten wird bei einem nicht invers angesteuerten Kraftstoffmjektor der Magnet 20 des Magnetventils 3 bestromt. Nicht invers angesteuert bedeutet dabei, dass bei bestromtem Magneten 20 die mindestens eine Einspritzöffnung freigegeben ist und Kraftstoff in den Brennraum der Verbrennungskraftmaschine eingespritzt wird. Durch das Bestromen des Magneten 20 bildet sich ein Magnetfeld aus, durch welches der Anker 9 vom Magneten 20 angezogen wird und sich damit in Richtung des Magneten 20 bewegt. Hierdurch hebt sich die Dichtfläche 8 des Ankers 9 aus dem Ventilsitz 10 und eine Verbindung aus dem Steuerraum 4 über die Ablaufdrossel 7 in den hier nicht dargestellten Rücklauf wird freigegeben. Aufgrund der freigegeben Verbindung kann Kraftstoff aus dem Steuerraum 4 ablaufen. Dies führt zu einem Druckabfall im Steuerraum 4. Durch den Druckabfall im Steuerraum 4 nimmt die Druckkraft, welche auf den Steuerkolben 2 wirkt ab und der Steuerkolben 2 wird in den Steuerraum 4 hineinbewegt. Durch diese Bewegung des Steuerkolbens 2 hebt sich das Einspritzventilglied aus seinem Sitz und gibt so die mindesten eine Einspritzöffnung frei. Der Einspritzvorgang beginnt.To start the injection process, the magnet 20 of the solenoid valve 3 is energized in a non-inversely controlled fuel injector. Not inverted means that when energized magnet 20, the at least one injection port is released and fuel is injected into the combustion chamber of the internal combustion engine. By energizing the magnet 20, a magnetic field is formed, through which the armature 9 is attracted by the magnet 20 and thus moves in the direction of the magnet 20. As a result, the sealing surface 8 of the armature 9 lifts out of the valve seat 10 and a connection from the control chamber 4 via the outlet throttle 7 in the return, not shown here is released. Due to the released connection, fuel can drain from the control chamber 4. This leads to a pressure drop in the control chamber 4. Due to the pressure drop in the control chamber 4, the pressure force which acts on the control piston 2 decreases and the control piston 2 is moved into the control chamber 4. As a result of this movement of the control piston 2, the injection valve member lifts out of its seat and thus releases the at least one injection opening. The injection process begins.

Der Hub des Ankers 9 wird durch die Hubanschlaghülse 15 begrenzt, indem der Anker 9 an die Ringfläche 14 der Hubanschlaghülse 15 anschlägt.The stroke of the armature 9 is limited by the Hubanschlaghülse 15 by the armature 9 abuts against the annular surface 14 of the Hubanschlaghülse 15.

Eine axiale Führung des Ankers 9 erfolgt durch einen Fortsatz 34 am Anker 9, der in der Bohrung 16 der Hubanschlaghülse 15 geführt ist. Um den Kraftstoffinjektor günstig herstellen zu können, sind jedoch die Bohrungen 16 und der Fortsatz 34 an Anker 9 nicht paarungsgeschliffen, so dass trotz des geringen Hubes, im Allgemeinen im Bereich zwischen 0,02 bis 0,04 Millimetern, ein Taumeln des Ankers 9 nicht verhindert werden kann.An axial guidance of the armature 9 is effected by an extension 34 on the armature 9, which is guided in the bore 16 of the Hubanschlaghülse 15. In order to produce the fuel injector low, however, the holes 16 and the extension 34 are not mating ground on anchor 9, so that despite the small stroke, generally in the range between 0.02 to 0.04 millimeters, a tumbling of the armature 9 is not can be prevented.

Um beim Verschließen der Ablaufdrossel 7, wodurch der Einspritzvorgang beendet wird, sicherzustellen, dass die Dichtfläche 8 am Anker 9 flüssigkeitsdicht in den Ventilsitz 10 gestellt ist, ist am Anker 9 die federnde Führungslippe 13 ausgebildet. Durch die federnde Führungslippe 13 wird der Anker 9 auch bei einer ungleichmäßig auf den Anker wirkenden Federkraft des Federelementes 17 am Kippen gehindert. Wenn es zu einem Kippen des Ankers 9 kommt, schlägt die federnde Führungslippe 13 an der Auflagefläche 22 an und verhindert hierdurch ein weiteres Verkippen des Ankers 9.In order to ensure when closing the outlet throttle 7, whereby the injection process is terminated, to ensure that the sealing surface 8 is placed liquid-tight in the valve seat 10 on the armature 9, the resilient guide lip 13 is formed on the armature 9. Due to the resilient guide lip 13, the armature 9 is prevented from tilting even when the spring force of the spring element 17 acts unevenly on the armature. If there is a tilting of the armature 9, the resilient guide lip 13 abuts against the support surface 22 and thereby prevents further tilting of the armature. 9

Zum Beenden des Einspritzvorganges wird die Bestromung des Magneten 20 beendet. Mit Hilfe des Federelements 17 wird der Anker 9 vom Magneten wegbewegt, so dass sich die Dichtfläche 8 in den Ventilsitz 10 stellt. Die Ablaufdrossel 7 wird hierdurch verschlossen. Im Steuerraum 4, der über den Kraftstoffzulauf 6 und die Zulaufdrossel 5 mit unter Systemdruck stehenden Kraftstoff befüllt wird, baut sich wieder Systemdruck auf. Hierdurch steigt die Druckkraft, die auf den Steuerkolben 2 wirkt. Der Steuerkolben 2 wird in Richtung des Einspritzventilgliedes bewegt und führt so dazu, dass das Einspritzventilglied in seinen Sitz gestellt wird und so die mindestens eine Einspritzöffnung verschließt.To end the injection process, the energization of the magnet 20 is stopped. With the aid of the spring element 17, the armature 9 is moved away from the magnet, so that the sealing surface 8 is placed in the valve seat 10. The outlet throttle 7 is thereby closed. In the control chamber 4, which is filled via the fuel inlet 6 and the inlet throttle 5 with fuel under system pressure, system pressure builds up again. As a result, the pressure force acting on the control piston 2 increases. The control piston 2 is moved in the direction of the injection valve member and thus results in that the injection valve member is placed in its seat and thus closes the at least one injection opening.

Ein invers angesteuerter Kraftstoffinjektor unterscheidet sich vom nicht invers angesteuerten Kraftstoffinjektor dadurch, dass bei bestromtem Magneten die mindestens eine Einspritzöffnung verschlossen ist und bei nicht bestromtem Magneten die mindestens eine Einspritzöffnung freigegeben ist. Hierzu sind der Steuerkolben 2 und das Einspritzventilglied so miteinander hydraulisch gekoppelt, das bei einer Bewegung des Steuerkolbens 2 in Richtung des Einspritzventilgliedes dieses aus dem Sitz gehoben wird und die mindestens eine Einspritzöffnung freigibt und bei bestromtem Magneten der Steuerkolben 2 in Richtung des Steuerraumes 4 bewegt wird, wodurch das Einspritzventilglied in sein Sitz gestellt wird und die mindestens eine Einspritzöffnung verschließt.An inversely controlled fuel injector differs from the non-inversely controlled fuel injector in that, when the magnet is energized, the at least one injection opening is closed and the at least one injection opening is released when the magnet is not energized. For this purpose, the control piston 2 and the injection valve member are coupled to each other hydraulically, which is lifted in a movement of the control piston 2 in the direction of the injection valve member from the seat and the at least one injection opening releases and is energized with energized magnet of the control piston 2 in the direction of the control chamber 4 , whereby the injection valve member is placed in its seat and closes the at least one injection opening.

In Figur 2 ist eine zweite Ausführungsform eines erfindungsgemäß ausgebildeten Magnetventils 3 dargestellt. Die in Figur 2 dargestellte Ausführungsform unterscheidet sich von der in Figur 1 dargestellten Ausführungsform dadurch, dass eine Scheibe 35, mit der die Federkraft des Federelementes 17 eingestellt wird, zwischen dem Federelement 17 und dem Anker 9 aufgenommen ist. Somit stützt sich das Federelement 17 mit einer Seite gegen die Scheibe 25 und mit der anderen Seite gegen die Stirnfläche 19 der Bohrung 16 ab. Durch die in Figur 2 dargestellte Ausführungsform dient die Scheibe 25 gleichzeitig zum Zentrieren des Ankers 9. Das Zentrieren des Ankers 9 ist erforderlich, damit dieser nicht radial verschiebt und so die Dichtfläche 8 am Anker 9 nicht mehr auf den Ventilsitz 10 platziert ist, wenn die Ablaufdrossel 7 verschlossen ist.In FIG. 2 is a second embodiment of an inventively designed solenoid valve 3 is shown. In the FIG. 2 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that a disc 35, with which the spring force of the spring element 17 is adjusted, is received between the spring element 17 and the armature 9. Thus, the spring element 17 is supported with one side against the disc 25 and with the other side against the end face 19 of the bore 16. By the in FIG. 2 The centering of the armature 9 is required so that it does not move radially and so the sealing surface 8 is no longer placed on the armature 9 on the valve seat 10 when the outlet throttle 7 is closed.

Figur 3 zeigt ein Magnetventil 3 in einer dritten Ausführungsfom. FIG. 3 shows a solenoid valve 3 in a third embodiment.

Die in Figur 3 dargestellte Ausführungsform unterscheidet sich von der in Figur 1 dargestellten Ausführungsform dadurch, dass die Druckstange 12 einen Bolzen 36 und einen Druckstift 37 umfasst. Der Bolzen 36 ist in der Bohrung 11 im Anker 9 geführt.
Dadurch, dass die Druckstange 12 den Druckstift 37 und den Bolzen 36 umfasst, wird vermieden, dass der Anker 9 an der Druckstange 12 verkanten kann, wenn dieser aufgrund ungleichmäßiger Kraftbeaufschlagung durch das Federelement 17 zu taumeln beginnt. Hierzu sind der Bolzen 36 und der Druckstift 37 so ausgeführt, dass der Bolzen 36 gegenüber dem Druckstift 37 aus der axialen Richtung abkippen kann. Vorzugsweise ist hierzu zumindest entweder der Druckstift 37 auf der dem Bolzen 36 zugewandten Seite oder der Bolzen 36 auf der dem Druckstift 37 zugewandten Seite mit einer ballig ausgebildeten Stirnfläche versehen. Ballig ausgebildet bedeutet dabei, dass die Stirnfläche in Form eines Kugelabschnittes, eines Paraboloids oder eines Hyperboloids ausgeführt ist. In einer bevorzugten Ausführungsform sind sowohl die dem Bolzen 36 zuweisende Stirnfläche des Druckstiftes 37 als auch die dem Druckstift 37 zuweisende Stirnfläche des Bolzen 36 ballig ausgeführt.In the FIG. 3 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that the push rod 12 comprises a bolt 36 and a pressure pin 37. The bolt 36 is guided in the bore 11 in the armature 9.
Characterized in that the push rod 12 includes the pressure pin 37 and the bolt 36, it is avoided that the armature 9 can tilt on the push rod 12 when it begins to wobble due to uneven application of force by the spring element 17. For this purpose, the bolt 36 and the pressure pin 37 are designed so that the bolt 36 can tilt over the pressure pin 37 from the axial direction. For this purpose, at least either the pressure pin 37 on the side facing the bolt 36 or the bolt 36 on the side facing the pressure pin 37 is preferably provided with a crowned end face. In this case, having a spherical design means that the end face is designed in the form of a spherical segment, a paraboloid or a hyperboloid. In a preferred embodiment, both the end face of the pressure pin 37 facing the pin 36 and the end face of the pin 36 facing the pressure pin 37 are crowned.

In einer weiteren Ausführungsform ist zwischen dem Bolzen 36 und dem Druckstift 37 eine Kugel aufgenommen. In diesem Fall führt die Kugel die gleiche Aufgabe aus wie die ballig geformten einander zugewandten Stirnflächen des Bolzens 36 und des Druckstiftes 37.In a further embodiment, a ball is received between the bolt 36 and the pressure pin 37. In this case, the ball performs the same task as the spherically shaped facing end faces of the bolt 36 and the pressure pin 37th

Aufgabe der Druckstange 12 ist in allen drei Ausführungsbeispielen, wie sie in den Figur 1 bis 3 dargestellt sind, axiale Druckkräfte aufzunehmen. Hierzu stützt sich die Druckstange 12 gegen die Stirnfläche 19 der Bohrung 16 in der Hubanschlaghülse 15 ab. Hierdurch wird die auf Druckstange 12 ausgeübte Druckkraft an die Hubanschlagshülse 15 übertragen.Task of the push rod 12 is in all three embodiments, as shown in the Figure 1 to 3 are shown to absorb axial compressive forces. For this purpose, the push rod 12 is supported against the end face 19 of the bore 16 in the Hubanschlaghülse 15. As a result, the pressure force exerted on the push rod 12 is transmitted to the Hubanschlagshülse 15.

Neben den in Figur 1 bis 3 dargestellten Ausführungsformen, bei der sich das Federelement 17 bzw. die Scheibe 18 und die Druckstange 12 gegen die Stirnfläche 19 der Bohrung 16 in der Hubanschlaghülse 15 abstützen, ist es auch möglich, dass die Bohrung 16 die Hubanschlagshülse vollständig durchzieht und sich die Scheibe 18 bzw. das Federelement 17 sowie die Druckstange 12 direkt am Injektorgehäuse abstützen. In diesem Fall wird die Bohrung 16 durch das Injektorgehäuse verschlossen.In addition to the in Figure 1 to 3 illustrated embodiments, in which the spring element 17 and the disc 18 and the push rod 12 are supported against the end face 19 of the bore 16 in the Hubanschlaghülse 15, it is also possible that the bore 16 completely passes through the Hubanschlagshülse and the disc 18 and Support the spring element 17 and the push rod 12 directly on the injector. In this case, the bore 16 is closed by the injector housing.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Kraftstoffinjektorfuel injector
22
Steuerkolbenspool
33
Magnetventilmagnetic valve
44
Steuerraumcontrol room
55
Zulaufdrosselinlet throttle
66
KraftstoffzulaufFuel supply
77
Ablaufdrosseloutlet throttle
88th
Dichtflächesealing surface
99
Ankeranchor
1010
Ventilsitzvalve seat
1111
Bohrungdrilling
1212
Druckstangepushrod
1313
elastische Führungslippeelastic guide lip
1414
Ringflächering surface
1515
Hubanschlaghülsestroke stop sleeve
1616
Bohrungdrilling
1717
Federelementspring element
1818
Scheibedisc
1919
Stirnflächeface
2020
Magnetmagnet
2121
Magnetkernmagnetic core
2222
Auflageflächebearing surface
2323
Hülseshell
2424
Stirnflächeface
2525
Ventilstückvalve piece
2626
Injektorgehäuseinjector
2727
VentilspannschraubeValve clamping screw
2828
Stiftpen
2929
Bohrungdrilling
3030
untere Scheibelower disc
3131
obere Scheibeupper disc
3232
Dichtringseal
3333
Spannungsmuttervoltage mother
3434
Fortsatzextension
3535
Scheibedisc
3636
Bolzenbolt
3737
Druckstiftpushpin

Claims (10)

  1. Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, in which fuel injector an injection valve member is actuated by a control valve, designed as a solenoid valve (3), in order to open and close an injection opening, and an armature (9) of the solenoid valve is movable between an upper and a lower stroke stop, wherein, for the closure of the control valve, a sealing surface (8) formed on the armature (9) interacts with a valve seat (10), characterized in that the armature (9) has a bore (11) which substantially corresponds to the inner diameter of the valve seat (10) and in which a pressure rod (12) is guided with a close fit such that the pressure rod (12) absorbs the acting axial pressure forces.
  2. Fuel injector according to Claim 1, characterized in that a resilient guide lip (13) is formed on the armature (9), which guide lip, at the lower stroke stop, rests on a contact surface (22) such that the armature (9) is aligned.
  3. Fuel injector according to Claim 2, characterized in that the guide lip (13) and the sealing surface (8) on the armature (9) and the contact surface (22) and the valve seat (10) of the control valve are ground to the same height.
  4. Fuel injector according to one of Claims 1 to 3, characterized in that the upper stroke stop is formed by an annular surface (14).
  5. Fuel injector according to one of Claims 2 to 4, characterized in that the contact surface (22) and the valve seat (10) are formed on a valve piece (25).
  6. Fuel injector according to one of Claims 1 to 5, characterized in that the spring force of a spring element (17) which assists the movement of the armature (9) from the magnet (20) into the valve seat (10) is set by means of a disc (18).
  7. Fuel injector according to Claim 6, characterized in that the disc (18) is held between the armature (9) and the spring element (17) and is thus additionally used for centring the armature (9).
  8. Fuel injector according to one of Claims 1 to 7, characterized in that the pressure rod (12) comprises a pressure pin (37) and a stud (36), wherein the stud (36) is held in a bore (11) in the armature (9) and the pressure pin (37) is surrounded by the spring element (17).
  9. Fuel injector according to Claim 8, characterized in that those ends of the stud (36) and of the pressure pin (37) which face towards one another are of spherical design.
  10. Fuel injector according to Claim 8, characterized in that a ball is held between the stud (36) and the pressure pin (37).
EP07727028A 2006-05-10 2007-03-19 Fuel injector comprising a pressure-compensated control valve Active EP2021617B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006021736A DE102006021736A1 (en) 2006-05-10 2006-05-10 Fuel injector with pressure compensated control valve
PCT/EP2007/052550 WO2007128612A1 (en) 2006-05-10 2007-03-19 Fuel injector comprising a pressure-compensated control valve

Publications (2)

Publication Number Publication Date
EP2021617A1 EP2021617A1 (en) 2009-02-11
EP2021617B1 true EP2021617B1 (en) 2011-11-23

Family

ID=38157536

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07727028A Active EP2021617B1 (en) 2006-05-10 2007-03-19 Fuel injector comprising a pressure-compensated control valve

Country Status (8)

Country Link
US (1) US8371516B2 (en)
EP (1) EP2021617B1 (en)
JP (2) JP5054762B2 (en)
CN (1) CN101490405B (en)
AT (1) ATE534815T1 (en)
DE (1) DE102006021736A1 (en)
RU (1) RU2451821C2 (en)
WO (1) WO2007128612A1 (en)

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006053128A1 (en) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Injector for injecting fuel
DE102007018472A1 (en) * 2007-04-19 2008-10-23 Robert Bosch Gmbh Fuel injector with solenoid valve
DE102007025961A1 (en) * 2007-06-04 2008-12-11 Robert Bosch Gmbh injector
DE102007044361A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector
DE102007044362A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector
DE102007047425A1 (en) 2007-10-04 2009-04-09 Robert Bosch Gmbh Control valve for a fuel injector
DE102007052361A1 (en) * 2007-11-02 2009-05-07 Robert Bosch Gmbh Elastic seat for switching valves
DE102008003348A1 (en) * 2008-01-07 2009-07-09 Robert Bosch Gmbh fuel injector
DE102008002146A1 (en) 2008-06-02 2009-12-03 Robert Bosch Gmbh Fuel injector with seat hole nozzle
DE102008040161A1 (en) * 2008-07-04 2010-01-07 Robert Bosch Gmbh Solenoid valve for a fuel injector and fuel injector
DE102008040637A1 (en) * 2008-07-23 2010-01-28 Robert Bosch Gmbh Fuel injection valve device
DE102009029116A1 (en) * 2009-09-02 2011-03-03 Robert Bosch Gmbh Fuel injector
DE102009045335A1 (en) * 2009-10-05 2011-04-07 Robert Bosch Gmbh injector
DE102009046563A1 (en) * 2009-11-10 2011-05-12 Robert Bosch Gmbh fuel injector
DE102010001486A1 (en) * 2010-02-02 2011-08-04 Robert Bosch GmbH, 70469 Control valve arrangement of a fuel injector
JP5637009B2 (en) * 2011-02-24 2014-12-10 株式会社デンソー Injector
JP5637008B2 (en) * 2011-02-24 2014-12-10 株式会社デンソー Injector
JP2013174158A (en) * 2012-02-24 2013-09-05 Nabtesco Corp Solenoid valve
DE102012221543A1 (en) * 2012-11-26 2014-05-28 Robert Bosch Gmbh valve means
DE102014225293A1 (en) 2014-12-09 2016-06-09 Robert Bosch Gmbh fuel injector
DE102015202726A1 (en) * 2015-02-16 2016-08-18 Robert Bosch Gmbh Control valve assembly
DE102016225580A1 (en) * 2016-12-20 2018-06-21 Robert Bosch Gmbh Device for metering a gaseous fuel to an injector
DE102016225946A1 (en) * 2016-12-22 2018-06-28 Robert Bosch Gmbh Fuel injector and its use
US11466652B2 (en) * 2017-06-14 2022-10-11 Cummins Inc. Fuel injector having a self-contained replaceable pilot valve assembly
CN109488772B (en) * 2018-11-30 2019-12-03 北京理工大学 A kind of double sealing structure of injection electromagnetic valve

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES487024A1 (en) * 1979-01-25 1980-06-16 Bendix Corp Fuel injector with electronically operated control.
SU909263A1 (en) * 1980-05-26 1982-02-28 Коломенский Филиал Всесоюзного Заочного Политехнического Института Injection nozzle
US4482094A (en) * 1983-09-06 1984-11-13 General Motors Corporation Electromagnetic unit fuel injector
JPS6220980A (en) * 1985-07-18 1987-01-29 Diesel Kiki Co Ltd Solenoid-controlled valve
JPH0338540Y2 (en) * 1987-03-30 1991-08-14
DE3727342A1 (en) * 1987-08-17 1989-03-02 Bosch Gmbh Robert ELECTROMAGNETICALLY ACTUABLE FUEL INJECTION VALVE
IT212429Z2 (en) * 1987-08-25 1989-07-04 Weber Srl FAST SOLENOID VALVE PARTICULARLY FUEL INJECTION PILOT VALVE FOR DIESEL CYCLE ENGINES
DE3802648A1 (en) * 1988-01-29 1989-08-10 Mainz Gmbh Feinmech Werke Electromagnetically actuated hydraulic quick-action switching valve
SU1719703A1 (en) * 1989-06-14 1992-03-15 Коломенский Филиал Всесоюзного Заочного Политехнического Института Electrically controllable pump-injector of diesel
DE3936619A1 (en) * 1989-11-03 1991-05-08 Man Nutzfahrzeuge Ag METHOD FOR INJECTING A FUEL INTO THE COMBUSTION CHAMBER OF AN AIR COMPRESSING, SELF-IGNITION ENGINE, AND APPARATUS FOR CARRYING OUT THIS METHOD
US5381965A (en) * 1993-02-16 1995-01-17 Siemens Automotive L.P. Fuel injector
EP0748417B1 (en) * 1994-02-15 2001-11-21 Invent Engineering Pty. Ltd. Hydraulically actuated electronic fuel injection system
JPH0861152A (en) * 1994-08-12 1996-03-05 Honda Motor Co Ltd Fuel injection device
JPH0979104A (en) * 1995-09-12 1997-03-25 Nippon Soken Inc Pressure accumulating type fuel injection device
US5947380A (en) * 1997-11-03 1999-09-07 Caterpillar Inc. Fuel injector utilizing flat-seat poppet valves
DE19833461A1 (en) * 1998-07-24 2000-01-27 Bosch Gmbh Robert Electromagnetically operated valve for fuel injection compressed mixtures and external fuel ignition has specially designed impact area acting as core or relay armature
RU2150019C1 (en) * 1999-03-16 2000-05-27 Пинский Феликс Ильич Electrohydraulic injector
DE10039039A1 (en) * 2000-08-10 2002-02-21 Bosch Gmbh Robert Solenoid valve for controlling an injection valve for internal combustion engines and electromagnet therefor
CN1133808C (en) * 2000-10-20 2004-01-07 昆腾燃料***技术环球公司 Gas fuel injector
DE10124747A1 (en) * 2001-05-21 2002-11-28 Bosch Gmbh Robert Fuel injection valve for internal combustion engines comprises an armature buffer surface and/or a counter-buffer surface having in a recess an elastic damping element protruding over the armature buffer surface/ counter-buffer surface
DE10131199A1 (en) 2001-06-28 2003-01-16 Bosch Gmbh Robert Solenoid valve for controlling an injection valve of an internal combustion engine
DE10161002A1 (en) * 2001-12-12 2003-07-03 Bosch Gmbh Robert Solenoid valve for controlling an injection valve of an internal combustion engine
JP3757261B2 (en) * 2002-08-05 2006-03-22 ボッシュ株式会社 Fuel injection valve
RU2247855C1 (en) * 2003-07-21 2005-03-10 Открытое акционерное общество "Ярославский завод топливной аппаратуры" (ОАО "ЯЗТА") Nozzle for internal combustion engine
DE102004010759A1 (en) * 2004-03-05 2005-09-22 Robert Bosch Gmbh Common rail injector
ES2277229T3 (en) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE.
DE602004002686T8 (en) * 2004-06-30 2008-01-03 C.R.F. Società Consortile per Azioni, Orbassano Fuel injector with force balanced control valve
JP3928162B2 (en) * 2004-10-08 2007-06-13 ボッシュ株式会社 Fuel injection valve
ATE468482T1 (en) * 2005-03-14 2010-06-15 Fiat Ricerche ADJUSTABLE DOSING SERVO VALVE OF AN INJECTION VALVE AND ITS ADJUSTMENT METHOD
EP1707797B1 (en) * 2005-03-14 2007-08-22 C.R.F. Società Consortile per Azioni Adjustable metering servovalve for a fuel injector

Also Published As

Publication number Publication date
RU2451821C2 (en) 2012-05-27
WO2007128612A1 (en) 2007-11-15
RU2008148287A (en) 2010-06-20
JP5054762B2 (en) 2012-10-24
CN101490405B (en) 2012-04-18
JP2012137097A (en) 2012-07-19
JP5783947B2 (en) 2015-09-24
ATE534815T1 (en) 2011-12-15
JP2009536288A (en) 2009-10-08
US8371516B2 (en) 2013-02-12
US20090159727A1 (en) 2009-06-25
CN101490405A (en) 2009-07-22
EP2021617A1 (en) 2009-02-11
DE102006021736A1 (en) 2007-11-15

Similar Documents

Publication Publication Date Title
EP2021617B1 (en) Fuel injector comprising a pressure-compensated control valve
EP1266135B1 (en) Electrovalve for controlling an injection valve in an internal combustion engine
EP2021618B1 (en) Fuel injector comprising a pressure-compensated control valve
DE10131201A1 (en) Solenoid valve for controlling an injection valve of an internal combustion engine
EP1259729B1 (en) Electromagnetic valve for controlling an injection valve of an internal combustion engine
EP2092187B1 (en) Injector for injecting fuel
EP2531715A1 (en) Control valve assembly of a fuel injector
WO2003002868A1 (en) Magnetic valve for controlling an injection valve in an internal combustion engine
WO2008049671A1 (en) Fuel injector
DE102007011047A1 (en) Magnetventilinjektor
DE102009027727A1 (en) valve assembly
WO2007065752A1 (en) Deformation-optimized armature guide for solenoid valves
EP3384149B1 (en) Fuel injector having a control valve
WO2010009925A1 (en) Armature pin for solenoid valve
DE10122168A1 (en) Solenoid valve for controlling an injection valve of an internal combustion engine
EP3387247B1 (en) Electromagnetically actuatable inlet valve and high-pressure pump having an inlet valve
EP3095998B1 (en) Fuel injector
EP1179675A2 (en) Solenoid valve controlling the injection valve of an internal combustion engine and electromagnet for it
EP3775527B1 (en) Injector for injecting fuel
DE3841010A1 (en) ELECTROMAGNETICALLY ACTUABLE VALVE
DE102013225376A1 (en) Solenoid valve for a fuel injector
DE102008001843A1 (en) Magnetic valve for fuel injector, particularly fuel injector at high pressure storage injection system, has armature assembly and magnetic core in which magnetic coil is embedded and armature plate is axially relocatable at armature bolt
WO2016206850A1 (en) Fuel injector with control valve
WO2017089032A1 (en) Electromagnetically actuatable suction valve for a high-pressure pump, and high-pressure pump
EP3098433A1 (en) Fuel injector

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: 20081210

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 HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17Q First examination report despatched

Effective date: 20091126

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 HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
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

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: 502007008723

Country of ref document: DE

Effective date: 20120202

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20111123

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20111123

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

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: 20120323

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: 20111123

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

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: 20120224

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: 20120323

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: 20111123

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: 20111123

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: 20111123

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: 20111123

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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: 20111123

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

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: 20111123

Ref country code: IE

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: 20111123

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: 20111123

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: 20120223

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: 20111123

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: 20111123

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

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: 20111123

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: 20111123

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

BERE Be: lapsed

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

Effective date: 20120331

26N No opposition filed

Effective date: 20120824

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

Ref country code: MC

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

Effective date: 20120331

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007008723

Country of ref document: DE

Effective date: 20120824

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

Ref country code: LI

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

Effective date: 20120331

Ref country code: CH

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

Effective date: 20120331

Ref country code: BE

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

Effective date: 20120331

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

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: 20120305

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 534815

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120319

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

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: 20111123

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: 20111123

Ref country code: AT

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

Effective date: 20120319

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: 20111123

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: 20120319

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

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

Effective date: 20070319

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

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

Ref country code: DE

Payment date: 20230524

Year of fee payment: 17

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

Ref country code: GB

Payment date: 20240322

Year of fee payment: 18

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

Ref country code: IT

Payment date: 20240329

Year of fee payment: 18

Ref country code: FR

Payment date: 20240320

Year of fee payment: 18