EP2643581B1 - Fuel injector - Google Patents

Fuel injector Download PDF

Info

Publication number
EP2643581B1
EP2643581B1 EP11788109.4A EP11788109A EP2643581B1 EP 2643581 B1 EP2643581 B1 EP 2643581B1 EP 11788109 A EP11788109 A EP 11788109A EP 2643581 B1 EP2643581 B1 EP 2643581B1
Authority
EP
European Patent Office
Prior art keywords
injection valve
hydraulic
valve element
fuel injector
valve member
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
EP11788109.4A
Other languages
German (de)
French (fr)
Other versions
EP2643581A1 (en
Inventor
Armin Schuelke
Olaf Ohlhafer
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 EP2643581A1 publication Critical patent/EP2643581A1/en
Application granted granted Critical
Publication of EP2643581B1 publication Critical patent/EP2643581B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/066—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having the features of the preamble of claim 1.
  • the fuel injector comprises a magnetic actuator for direct activation of a preferably needle-shaped injection valve member, via the lifting movement of which at least one injection port of the fuel injector is releasable or closable.
  • the control of an injection valve member of a fuel injector with a solenoid actuator as the actuating means is usually indirect.
  • the magnetic actuator comprises a solenoid valve, by means of which a control pressure acting on the injection valve member in a control chamber is variable, so that opening or closing of the injection valve member is effected with change of the control pressure.
  • the indirect control proves to be disadvantageous because the required to reduce the control pressure control amount must be fed to a return and then again promoted to high pressure.
  • indirectly actuated injection valve members have a delayed response as compared to directly actuated principles. In order to realize a direct control of the injection valve member but so far almost exclusively injector concepts are known which provide for the use of piezoelectric actuators. Because the use of a magnetic actuator would require a too large magnetic actuator at system pressures of over 2000 bar in order to realize the necessary force to open the injection valve member.
  • a fuel injector with a direct-controlled injection valve member and a magnetic actuator in the form of a solenoid valve known.
  • a flow channel of a first control chamber can be opened or closed, which is acted upon by an inlet throttle system pressure.
  • the injector concept disclosed herein also requires the discharge of a certain amount of purge through a low pressure side drain.
  • the object of the present invention is to provide a fuel injector with a solenoid actuator that allows direct control of the injection valve member and thus can be operated without backflow.
  • the proposed fuel injector should be simple and inexpensive to produce.
  • the proposed fuel injector has a magnetic actuator with a liftable anchor element for direct control of a preferably needle-shaped injection valve member.
  • the injection valve member is mechanically coupled during a first phase of its opening stroke with a hydraulic translator having a hydraulic effective area A 1 defining a control volume which, in sum with a hydraulic effective area A 2 formed on the injection valve member, is larger than an armature element defining the control volume Hydraulic effective area A 3 , so that due to the area ratio of the relevant in relation to the control volume hydraulic effective area A 1 , A 2 and A 3, a force gain is effected.
  • the injection valve member is mechanically coupled during its closing stroke with the anchor element, is acted upon in the closing direction of the injection valve member by an armature spring, so that the closing stroke of the injection valve member by means of the armature spring is effected.
  • a separate closing spring which acts on the injection valve member in the closing direction with a closing force, is thus unnecessary.
  • the elimination of a separate closing spring has the advantage of a reduced manufacturing and voting effort.
  • the control volume can be minimized, which has a favorable effect on the response of the injection valve member.
  • the force amplification makes it possible to realize a direct actuation of the injection valve member using a magnetic actuator. The control is therefore carried out without backflow.
  • the hydraulic effective area A 2 formed on the injection valve member is selected smaller than the hydraulic effective area A 3 formed on the anchor element.
  • the mechanical coupling of the injection valve member with the hydraulic booster is canceled, so that the area ratio of the relevant in terms of the control volume hydraulic active surfaces now A 2 / A 3 ⁇ 1.
  • a stop surface is formed on the injection valve member for mechanical coupling of the injection valve member with the hydraulic booster.
  • the stop surface causes the injection valve member to be entrained during a lifting movement of the hydraulic booster.
  • the lifting movement of the hydraulic translator is in turn realized by a lifting movement of the armature element in the direction of the magnetic actuator and a concomitant lowering of the control pressure in the control volume. Since during this phase of the opening stroke of the injection valve member, the hydraulic active surfaces A 1 and A 2 add up and in total are greater than the hydraulic active surface A 3 of the anchor element, a force amplification is effected by means of which the initially high closing force can be overcome.
  • a stop is preferably formed on a housing part of the fuel injector.
  • the stop serves to unilaterally limit the stroke of the hydraulic translator. This means that the opening stroke of the hydraulic booster is limited in contrast to the opening stroke of the injection valve member.
  • the hydraulic booster rests against the stop of the housing part, so that not only the mechanical coupling of the hydraulic booster with the injection valve member but also the hydraulic coupling of the hydraulic booster with the anchor member is released. Only the hydraulic coupling of the injection valve member remains, so that over a surface ratio A 2 / A 3 ⁇ 1, a path gain can be effected.
  • the hydraulic booster is disc-shaped or piston-shaped and has a central bore in which the injection valve member is received.
  • the stop formed on the injection valve member may be formed, for example, as a radial shoulder in the region of an increase in diameter of the injection valve member.
  • the hydraulic booster, the injection valve member and the anchor element is arranged coaxially, wherein the hydraulic active surface A 3 formed on the anchor element lies opposite the active surfaces A 1 and A 2 .
  • the hydraulic booster is acted upon by the pressure force of a spring, by means of which it is ensured that the hydraulic booster rests in the closed position of the injector against the stop of the injection valve member. Therefore, the spring has only to ensure that the hydraulic translator resumes its initial position after an injection process. As a result, a relatively soft spring can be used. At least the spring force is less than that of the armature spring chosen to effect the complete closing stroke of the injection valve member.
  • the illustrated fuel injector has a magnetic actuator 1 for actuating an injection valve member 2.
  • the injection valve member 2 is guided for releasing and closing at least one injection opening 3 in a liftable manner in a nozzle body 13.
  • the solenoid actuator 1 has a likewise liftable anchor element 4, which limits a control volume 5 with a hydraulic active surface A 3 in the axial direction.
  • the magnetic actuator 1 is energized, the armature element 4 moves in the direction of the actuator and thus causes a pressure drop in the control volume 5. Since the control volume 5 is further formed by a hydraulic active surface A 1 formed on a hydraulic booster 6 and by an injection valve member 2 Hydraulic active surface A 2 is limited, a hydraulic coupling takes place with the anchor element 4.
  • the hydraulic booster 6 and the injection valve member 2 follow the movement of the anchor member 4. Since the sum of the hydraulic active surfaces A 1 and A 2 is greater than the area A 3 is selected, a force gain is effected via the area ratio during this first phase of the opening stroke of the injection valve member 2. To ensure that both the hydraulic translator 6 and the injection valve member 2 follow the movement of the armature element 4, the hydraulic booster 6 and the injection valve member 2 are mechanically coupled via a stop surface 8 formed on the injection valve member 2. During the first phase of the opening stroke of the hydraulic booster 6 abuts against this stop surface 8 of the injection valve member 2. A part of the opening stroke of the injection valve member 2, the hydraulic translator 6 and the injection valve member 2 thus master together.
  • a stop 10 is formed on a housing part 9. If the hydraulic booster 6 comes into abutment with the stopper 10, the mechanical coupling with the injection valve member 2 is released and the injection valve member 2 continues the movement alone.
  • the mechanical coupling takes place in the present case in a simple manner, namely by the injection valve member 2 is received in a central bore 11 of the hydraulic booster 6 and to form the stop surface 8 has a region with increased outer diameter, wherein the outer diameter greater than the inner diameter of the central bore 11 is selected is.
  • a spring 12 which acts on the hydraulic actuator 6 in the direction of the stop surface 8 with a compressive force, ensures the installation of the hydraulic booster 6 to the stop surface 8 during the first phase of the opening stroke of the injection valve member 2 and in the closed position of the injector.
  • the energization of the magnetic actuator 1 is terminated.
  • An anchor element 4 in the closing direction with a compressive force acting anchor spring 7 ensures the return of the anchor element 4.
  • the return of the injection valve member 2 is also effected via the pressure force of the armature spring 7.
  • the spring force of the armature spring 7 is therefore chosen to be relatively high. In any case, the spring force of the armature spring 7 is selected higher than the spring force of the spring 12, which acts on the hydraulic booster in the opening direction of the injection valve member 2.
  • a separate closing spring for returning the injection valve member 2 is dispensable, whereby the manufacturing and tuning effort is reduced.

Description

Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1. Der Kraftstoffinjektor umfasst einen Magnetaktor zur direkten Ansteuerung eines vorzugsweise nadelförmigen Einspritzventilgliedes, über dessen Hubbewegung wenigstens eine Einspritzöffnung des Kraftstoffinjektors freigebbar oder verschließbar ist.The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having the features of the preamble of claim 1. The fuel injector comprises a magnetic actuator for direct activation of a preferably needle-shaped injection valve member, via the lifting movement of which at least one injection port of the fuel injector is releasable or closable.

Stand der TechnikState of the art

Die Ansteuerung eines Einspritzventilgliedes eines Kraftstoffinjektors mit einem Magnetaktor als Betätigungsmittel erfolgt in der Regel indirekt. Hierzu umfasst der Magnetaktor ein Magnetventil, mittels dessen ein das Einspritzventilglied beaufschlagender Steuerdruck in einem Steuerraum veränderbar ist, so dass mit Veränderung des Steuerdrucks ein Öffnen oder Schließen des Einspritzventilgliedes bewirkt wird. Die indirekte Ansteuerung erweist sich jedoch als nachteilig, da die zur Absenkung des Steuerdrucks erforderliche Steuermenge einem Rücklauf zugeführt und danach erneut auf Hochdruck gefördert werden muss. Außerdem weisen indirekt angesteuerte Einspritzventilglieder gegenüber direkt angesteuerten prinzipbedingt ein verzögertes Ansprechverhalten auf. Um eine direkte Ansteuerung des Einspritzventilgliedes zu realisieren sind bislang jedoch fast ausschließlich Injektorkonzepte bekannt, die den Einsatz von Piezoaktoren vorsehen. Denn der Einsatz eines Magnetaktors würde bei Systemdrücken von über 2000 bar einen zu großen Magnetaktor erfordern, um die zum Öffnen des Einspritzventilgliedes notwendige Kraft zu realisieren.The control of an injection valve member of a fuel injector with a solenoid actuator as the actuating means is usually indirect. For this purpose, the magnetic actuator comprises a solenoid valve, by means of which a control pressure acting on the injection valve member in a control chamber is variable, so that opening or closing of the injection valve member is effected with change of the control pressure. However, the indirect control proves to be disadvantageous because the required to reduce the control pressure control amount must be fed to a return and then again promoted to high pressure. In addition, indirectly actuated injection valve members have a delayed response as compared to directly actuated principles. In order to realize a direct control of the injection valve member but so far almost exclusively injector concepts are known which provide for the use of piezoelectric actuators. Because the use of a magnetic actuator would require a too large magnetic actuator at system pressures of over 2000 bar in order to realize the necessary force to open the injection valve member.

Darüber hinaus ist aus der DE 10 2006 015 745 A1 ein Kraftstoffinjektor mit einem direktgesteuerten Einspritzventilglied und einem magnetischen Steller in Form eines Magnetventils bekannt. Über das Magnetventil kann ein Ablaufkanal eines ersten Steuerraumes geöffnet oder geschlossen werden, der über eine Zulaufdrossel mit Systemdruck beaufschlagt ist. Um die prinzipbedingten langen Öffnungs- und Schließzyklen in Bezug auf das Einspritzventilglied zu verkürzen, wird vorgeschlagen, das Magnetventil durch einen zusätzlichen Bypass, der den Ablaufkanal mit einem Hochdruckanschluss verbindet, zu umgehen. Dennoch bedingt auch das hierin offenbarte Injektorkonzept das Abführen einer bestimmten Absteuermenge über einen niederdruckseitigen Ablauf.In addition, from the DE 10 2006 015 745 A1 a fuel injector with a direct-controlled injection valve member and a magnetic actuator in the form of a solenoid valve known. About the solenoid valve, a flow channel of a first control chamber can be opened or closed, which is acted upon by an inlet throttle system pressure. In order to shorten the inherent long opening and closing cycles with respect to the injection valve member, it is proposed to bypass the solenoid valve by means of an additional bypass which connects the discharge channel to a high-pressure connection. Nevertheless, the injector concept disclosed herein also requires the discharge of a certain amount of purge through a low pressure side drain.

Weiterhin sind aus WO 2007/115853 A1 , DE 10 2008 042 227 A1 und EP 2 386 746 A2 Einspritzventile bekannt, bei denen die kolbenförmigen Düsennadeln mittels eines elektrischen Aktuators und eines hydraulischen Kopplers bewegt werden.Furthermore are out WO 2007/115853 A1 . DE 10 2008 042 227 A1 and EP 2 386 746 A2 Injectors known in which the piston-shaped nozzle needles are moved by means of an electric actuator and a hydraulic coupler.

Ausgehend von dem vorstehend genannten Stand der Technik besteht die Aufgabe der vorliegenden Erfindung darin, einen Kraftstoffinjektor mit einem Magnetaktor bereit zu stellen, der eine direkte Ansteuerung des Einspritzventilgliedes ermöglicht und somit rücklaufmengenfrei betrieben werden kann. Zugleich soll der vorgeschlagene Kraft-stoffinjektor einfach und kostengünstig herstellbar sein.Based on the above-mentioned prior art, the object of the present invention is to provide a fuel injector with a solenoid actuator that allows direct control of the injection valve member and thus can be operated without backflow. At the same time, the proposed fuel injector should be simple and inexpensive to produce.

Die Aufgabe wird gelöst durch einen Kraftstoffinjektor mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.The object is achieved by a fuel injector with the features of claim 1. Advantageous developments of the invention are specified in the subclaims.

Offenbarung der ErfindungDisclosure of the invention

Der vorgeschlagene Kraftstoffinjektor weist einen Magnetaktor mit einem hubbeweglichen Ankerelement zur direkten Ansteuerung eines vorzugsweise nadelförmigen Einspritzventilgliedes auf. Erfingdungsgemäß ist das Einspritzventilglied während einer ersten Phase seines Öffnungshubes mit einem hydraulischen Übersetzer mechanisch koppelbar, der eine ein Steuervolumen begrenzende hydraulische Wirkfläche A1 besitzt, welche in Summe mit einer am Einspritzventilglied ausgebildeten hydraulischen Wirkfläche A2 größer als eine am Ankerelement ausgebildete, das Steuervolumen begrenzende hydraulische Wirkfläche A3 ist, so dass aufgrund des Flächenverhältnisses der in Bezug auf das Steuervolumen relevanten hydraulischen Wirkfläche A1, A2 und A3 eine Kraftverstärkung bewirkt wird. Ferner erfindungsgemäß ist das Einspritzventilglied während seines Schließhubes mit dem Ankerelement mechanisch koppelbar, in Schließrichtung des Einspritzventilgliedes von einer Ankerfeder beaufschlagt wird, so dass der Schließhub des Einspritzventilgliedes mittels der Ankerfeder bewirkbar ist. Eine separate Schließfeder, welche das Einspritzventilglied in Schließrichtung mit einer Schließkraft beaufschlagt, ist somit entbehrlich. Der Entfall einer separaten Schließfeder weist den Vorteil eines verminderten Fertigungs- und Abstimmungsaufwands auf. Ferner kann das Steuervolumen minimiert werden, was sich günstig auf das Ansprechverhalten des Einspritzventilgliedes auswirkt. Darüber hinaus ermöglicht die Kraftverstärkung während der ersten Phase des Öffnungshubes des Einspritzventilgliedes eine direkte Ansteuerung des Einspritzventilgliedes unter Verwendung eines Magnetaktors zu realisieren. Die Ansteuerung erfolgt demnach rücklaufmengenfrei.The proposed fuel injector has a magnetic actuator with a liftable anchor element for direct control of a preferably needle-shaped injection valve member. According to the invention, the injection valve member is mechanically coupled during a first phase of its opening stroke with a hydraulic translator having a hydraulic effective area A 1 defining a control volume which, in sum with a hydraulic effective area A 2 formed on the injection valve member, is larger than an armature element defining the control volume Hydraulic effective area A 3 , so that due to the area ratio of the relevant in relation to the control volume hydraulic effective area A 1 , A 2 and A 3, a force gain is effected. Furthermore, according to the invention, the injection valve member is mechanically coupled during its closing stroke with the anchor element, is acted upon in the closing direction of the injection valve member by an armature spring, so that the closing stroke of the injection valve member by means of the armature spring is effected. A separate closing spring, which acts on the injection valve member in the closing direction with a closing force, is thus unnecessary. The elimination of a separate closing spring has the advantage of a reduced manufacturing and voting effort. Furthermore, the control volume can be minimized, which has a favorable effect on the response of the injection valve member. In addition, during the first phase of the opening stroke of the injection valve member, the force amplification makes it possible to realize a direct actuation of the injection valve member using a magnetic actuator. The control is therefore carried out without backflow.

Während der ersten Phase des Öffnungshubes gilt es den Druckunterschied am geschlossenen Einspritzventilglied zu überwinden, der anfänglich sehr groß ist. Um das Einspritzventilglied aus seinem Sitz zu heben, bedarf es daher der Kraftverstärkung. Die mit der Kraftverstärkung einhergehende Wegminderung ist in dieser Phase des Öffnungshubes des Einspritzventilgliedes unerheblich. Zur vollständigen Sitzentdrosselung wird daher während einer zweiten Phase von einer Kraftverstärkung auf eine Wegverstärkung umgeschaltet. Die mit der Wegverstärkung einhergehende Kraftminderung ist wiederum unerheblich, da sich mit fortschreitendem Hub des Einspritzventilgliedes unterhalb des Einspritzventilgliedes ein dem Systemdruck angleichender Druck aufbaut, so dass die zum weiteren Anheben des Einspritzventilgliedes erforderliche Kraft sinkt. Die Umschaltung von einer Kraftverstärkung auf eine Wergverstärkung erfolgt durch eine Änderung des Flächenverhältnisses der jeweils in Bezug auf das Steuervolumen relevanten hydraulischen Wirkflächen.During the first phase of the opening stroke, it is necessary to overcome the pressure difference at the closed injection valve member, which is initially very large. In order to lift the injection valve member from its seat, it therefore requires the power boost. The associated with the power amplification Wegminderung is irrelevant in this phase of the opening stroke of the injection valve member. For complete seat throttling is therefore switched over during a second phase of a power gain to a path gain. The power reduction associated with the path gain is in turn irrelevant, since with increasing stroke of the injection valve member below the injection valve member a pressure equalizing the system pressure builds up, so that the force required to further increase the injection valve member decreases. The changeover from a force boost to a drag gain is effected by a change in the area ratio of the relevant in each case with respect to the control volume hydraulic active surfaces.

Vorzugsweise ist zur Realisierung einer Wegverstärkung während der zweiten Phase des Öffnungshubes des Einspritzventilgliedes die am Einspritzventilglied ausgebildete hydraulische Wirkfläche A2 kleiner als die am Ankerelement ausgebildete hydraulische Wirkfläche A3 gewählt. Zudem wird während der zweiten Phase des Öffnungshubes die mechanische Kopplung des Einspritzventilgliedes mit dem hydraulischen Übersetzer aufgehoben, so dass das Flächenverhältnis der in Bezug auf das Steuervolumen relevanten hydraulischen Wirkflächen nunmehr A2/ A3 < 1 beträgt.Preferably, in order to realize a travel gain during the second phase of the opening stroke of the injection valve member, the hydraulic effective area A 2 formed on the injection valve member is selected smaller than the hydraulic effective area A 3 formed on the anchor element. In addition, during the second phase of the opening stroke, the mechanical coupling of the injection valve member with the hydraulic booster is canceled, so that the area ratio of the relevant in terms of the control volume hydraulic active surfaces now A 2 / A 3 <1.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist zur mechanischen Kopplung des Einspritzventilgliedes mit dem hydraulischen Übersetzer eine Anschlagfläche am Einspritzventilglied ausgebildet. Die Anschlagfläche bewirkt, dass bei einer Hubbewegung des hydraulischen Übersetzers das Einspritzventilglied mitgenommen wird. Die Hubbewegung des hydraulischen Übersetzers wird wiederum durch eine Hubbewegung des Ankerelementes in Richtung des Magnetaktors und einer damit einhergehenden Absenkung des Steuerdrucks im Steuervolumen realisiert. Da sich während dieser Phase des Öffnungshubes des Einspritzventilgliedes die hydraulischen Wirkflächen A1 und A2 addieren und in der Summe größer als die hydraulische Wirkfläche A3 des Ankerelements sind, wird eine Kraftverstärkung bewirkt, mittels welcher die anfänglich hohe Schließkraft überwunden werden kann.According to a preferred embodiment of the invention, a stop surface is formed on the injection valve member for mechanical coupling of the injection valve member with the hydraulic booster. The stop surface causes the injection valve member to be entrained during a lifting movement of the hydraulic booster. The lifting movement of the hydraulic translator is in turn realized by a lifting movement of the armature element in the direction of the magnetic actuator and a concomitant lowering of the control pressure in the control volume. Since during this phase of the opening stroke of the injection valve member, the hydraulic active surfaces A 1 and A 2 add up and in total are greater than the hydraulic active surface A 3 of the anchor element, a force amplification is effected by means of which the initially high closing force can be overcome.

Um die Entkopplung des Einspritzventilgliedes vom hydraulischen Übersetzer und damit ein Umschalten von einer Kraftverstärkung auf eine Wegverstärkung zu bewirken, ist vorzugsweise an einem Gehäuseteil des Kraftstoffinjektors ein Anschlag ausgebildet. Der Anschlag dient der einseitig wirksamen Hubbegrenzung des hydraulischen Übersetzers. Das heißt, dass der Öffnungshub des hydraulischen Übersetzers im Unterschied zum Öffnungshub des Einspritzventilgliedes begrenzt ist. Während der zweiten Phase des Öffnungshubes des Einspritzventilgliedes liegt der hydraulische Übersetzer am Anschlag des Gehäuseteils an, so dass nicht nur die mechanische Kopplung des hydraulischen Übersetzers mit dem Einspritzventilglied sondern auch die hydraulische Kopplung des hydraulischen Übersetzers mit dem Ankerelement aufgehoben wird. Lediglich die hydraulische Kopplung des Einspritzventilgliedes bleibt bestehen, so dass über ein Flächenverhältnis A2/ A3 < 1 eine Wegverstärkung bewirkbar ist.In order to effect the decoupling of the injection valve member from the hydraulic booster and thus switching from a power gain to a path gain, a stop is preferably formed on a housing part of the fuel injector. The stop serves to unilaterally limit the stroke of the hydraulic translator. This means that the opening stroke of the hydraulic booster is limited in contrast to the opening stroke of the injection valve member. During the second phase of the opening stroke of the injection valve member, the hydraulic booster rests against the stop of the housing part, so that not only the mechanical coupling of the hydraulic booster with the injection valve member but also the hydraulic coupling of the hydraulic booster with the anchor member is released. Only the hydraulic coupling of the injection valve member remains, so that over a surface ratio A 2 / A 3 <1, a path gain can be effected.

Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist der hydraulische Übersetzer scheiben- oder kolbenförmig ausgebildet und besitzt eine zentrale Bohrung, in welcher das Einspritzventilglied aufgenommen ist. Auf diese Weise lassen sich am einfachsten die vorstehend beschriebenen Flächenverhältnisse während der ersten und der zweiten Phase des Öffnungshubes des Einspritzventilgliedes realisieren. Der am Einspritzventilglied ausgebildete Anschlag kann beispielsweise als radialer Absatz im Bereich einer Durchmesservergrößerung des Einspritzventilgliedes ausgebildet sein. Weiterhin bevorzugt sind der hydraulische Übersetzer, das Einspritzventilglied und das Ankerelement koaxial angeordnet, wobei die am Ankerelement ausgebildete hydraulische Wirkfläche A3 den Wirkflächen A1 und A2 gegenüber liegt.According to a further preferred embodiment of the invention, the hydraulic booster is disc-shaped or piston-shaped and has a central bore in which the injection valve member is received. In this way, the above-described surface ratios during the first and the second phase of the opening stroke of the injection valve member can be realized most simply. The stop formed on the injection valve member may be formed, for example, as a radial shoulder in the region of an increase in diameter of the injection valve member. Further preferred are the hydraulic booster, the injection valve member and the anchor element is arranged coaxially, wherein the hydraulic active surface A 3 formed on the anchor element lies opposite the active surfaces A 1 and A 2 .

Vorteilhafterweise wird der hydraulische Übersetzer von der Druckkraft einer Feder beaufschlagt, mittels welcher sichergestellt ist, dass der hydraulische Übersetzer in Schließstellung des Injektors am Anschlag des Einspritzventilgliedes anliegt. Die Feder hat demnach lediglich zu gewährleisten, dass der hydraulische Übersetzer nach einem Einspritzvorgang wieder seine Ausgangsposition einnimmt. Demzufolge kann eine relativ weiche Feder eingesetzt werden. Zumindest ist die Federkraft geringer als die der Ankerfeder gewählt, um den vollständigen Schließhub des Einspritzventilgliedes zu bewirken.Advantageously, the hydraulic booster is acted upon by the pressure force of a spring, by means of which it is ensured that the hydraulic booster rests in the closed position of the injector against the stop of the injection valve member. Therefore, the spring has only to ensure that the hydraulic translator resumes its initial position after an injection process. As a result, a relatively soft spring can be used. At least the spring force is less than that of the armature spring chosen to effect the complete closing stroke of the injection valve member.

Eine bevorzugte Ausführungsform der Erfindung wird nachfolgend anhand der einzigen Zeichnung näher beschrieben. Diese zeigt einen schematischen Längsschnitt durch einen erfindungsgemäßen Kraftstoffinjektor.A preferred embodiment of the invention will be described below with reference to the single drawing. This shows a schematic longitudinal section through a fuel injector according to the invention.

Ausführliche Beschreibung der ZeichnungDetailed description of the drawing

Der dargestellte erfindungsgemäße Kraftstoffinjektor weist einen Magnetaktor 1 zur Betätigung eines Einspritzventilgliedes 2 auf. Das Einspritzventilglied 2 ist zum Freigeben und Verschließen wenigstens einer Einspritzöffnung 3 hubbeweglich in einem Düsenkörper 13 geführt. Zur Betätigung des Einspritzventilgliedes 2 weist der Magnetaktor 1 ein ebenfalls hubbewegliches Ankerelement 4 auf, das in axialer Richtung ein Steuervolumen 5 mit einer hydraulischen Wirkfläche A3 begrenzt. Bei einer Bestromung des Magnetaktors 1 bewegt sich das Ankerelement 4 in Richtung des Aktors und bewirkt auf diese Weise einen Druckabfall im Steuervolumen 5. Da das Steuervolumen 5 ferner von einer an einem hydraulischen Übersetzer 6 ausgebildeten hydraulischen Wirkfläche A1 und von einer am Einspritzventilglied 2 ausgebildeten hydraulischen Wirkfläche A2 begrenzt wird, erfolgt eine hydraulische Kopplung dieser mit dem Ankerelement 4. Das heißt, dass der hydraulische Übersetzer 6 und das Einspritzventilglied 2 der Bewegung des Ankerelementes 4 folgen. Da die Summe der hydraulischen Wirkflächen A1 und A2 größer als die Fläche A3 gewählt ist, wird über das Flächenverhältnis während dieser ersten Phase des Öffnungshubes des Einspritzventilgliedes 2 eine Kraftverstärkung bewirkt. Um sicherzustellen, dass sowohl der hydraulische Übersetzer 6 als auch das Einspritzventilglied 2 der Bewegung des Ankerelementes 4 folgen, sind der hydraulische Übersetzer 6 und das Einspritzventilglied 2 über eine am Einspritzventilglied 2 ausgebildete Anschlagfläche 8 mechanisch koppelbar. Während der ersten Phase des Öffnungshubes liegt der hydraulische Übersetzer 6 an dieser Anschlagfläche 8 des Einspritzventilgliedes 2 an. Einen Teil des Öffnungshubes des Einspritzventilgliedes 2 bewältigen der hydraulische Übersetzer 6 und das Einspritzventilglied 2 demnach gemeinsam. Strömt nach anfänglichem Öffnen der Kraftstoff unter das Einspritzventilglied 2 sinken die Kraftanforderungen zum weiteren Anheben des Einspritzventilgliedes. Demnach kann nunmehr von einer Kraftverstärkung auf eine Wegverstärkung umgeschaltet werden. Das Umschalten erfolgt, indem der hydraulische Übersetzer 6 an einer weiteren Bewegung gehindert wird. Das heißt, dass die mechanische Kopplung des hydraulischen Übersetzers 6 mit dem Einspritzventilglied 2 während dieser zweiten Phase des Öffnungshubes des Einspritzventilgliedes 2 gelöst wird. Als wirksame hydraulische Flächen liegen sich demnach nur noch die Wirkflächen A2 und A3 gegenüber. Da die am Einspritzventilglied 2 ausgebildete hydraulische Wirkfläche A2 kleiner als die am Ankerelement 4 ausgebildete hydraulische Wirkfläche A3 gewählt ist, wird nunmehr eine Wegverstärkung erzielt.The illustrated fuel injector according to the invention has a magnetic actuator 1 for actuating an injection valve member 2. The injection valve member 2 is guided for releasing and closing at least one injection opening 3 in a liftable manner in a nozzle body 13. For actuation of the injection valve member 2, the solenoid actuator 1 has a likewise liftable anchor element 4, which limits a control volume 5 with a hydraulic active surface A 3 in the axial direction. When the magnetic actuator 1 is energized, the armature element 4 moves in the direction of the actuator and thus causes a pressure drop in the control volume 5. Since the control volume 5 is further formed by a hydraulic active surface A 1 formed on a hydraulic booster 6 and by an injection valve member 2 Hydraulic active surface A 2 is limited, a hydraulic coupling takes place with the anchor element 4. That is, the hydraulic booster 6 and the injection valve member 2 follow the movement of the anchor member 4. Since the sum of the hydraulic active surfaces A 1 and A 2 is greater than the area A 3 is selected, a force gain is effected via the area ratio during this first phase of the opening stroke of the injection valve member 2. To ensure that both the hydraulic translator 6 and the injection valve member 2 follow the movement of the armature element 4, the hydraulic booster 6 and the injection valve member 2 are mechanically coupled via a stop surface 8 formed on the injection valve member 2. During the first phase of the opening stroke of the hydraulic booster 6 abuts against this stop surface 8 of the injection valve member 2. A part of the opening stroke of the injection valve member 2, the hydraulic translator 6 and the injection valve member 2 thus master together. After initially opening the fuel flows under the injection valve member 2, the force requirements for further raising the injection valve member decrease. Accordingly, it is now possible to switch from a power amplification to a path gain. The switching occurs by preventing the hydraulic booster 6 from further movement. That is, the mechanical coupling of the hydraulic booster 6 with the injection valve member 2 is released during this second phase of the opening stroke of the injection valve member 2. As effective hydraulic surfaces are therefore only the active surfaces A 2 and A 3 against. Since the formed on the injection valve member 2 hydraulic effective area A 2 is selected to be smaller than that formed on the anchor member 4 hydraulic effective area A 3, a path gain will now be achieved.

Zur Hubbegrenzung des hydraulischen Übersetzers 6 ist an einem Gehäuseteil 9 ein Anschlag 10 ausgebildet. Gelangt der hydraulische Übersetzer 6 in Anlage mit dem Anschlag 10, wird die mechanische Kopplung mit dem Einspritzventilglied 2 gelöst und das Einspritzventilglied 2 setzt die Bewegung alleine fort. Die mechanische Kopplung erfolgt vorliegend in einfacher Weise, nämlich indem das Einspritzventilglied 2 in einer zentralen Bohrung 11 des hydraulischen Übersetzers 6 aufgenommen ist und zur Ausbildung der Anschlagfläche 8 einen Bereich mit vergrößertem Außendurchmesser besitzt, wobei der Außendurchmesser größer als der Innendurchmesser der zentralen Bohrung 11 gewählt ist. Eine Feder 12, welche den hydraulischen Übersetzer 6 in Richtung der Anschlagfläche 8 mit einer Druckkraft beaufschlagt, stellt die Anlage des hydraulischen Übersetzers 6 an der Anschlagfläche 8 während der ersten Phase des Öffnungshubes des Einspritzventilgliedes 2 bzw. in Schließstellung des Injektors sicher.To limit the stroke of the hydraulic booster 6, a stop 10 is formed on a housing part 9. If the hydraulic booster 6 comes into abutment with the stopper 10, the mechanical coupling with the injection valve member 2 is released and the injection valve member 2 continues the movement alone. The mechanical coupling takes place in the present case in a simple manner, namely by the injection valve member 2 is received in a central bore 11 of the hydraulic booster 6 and to form the stop surface 8 has a region with increased outer diameter, wherein the outer diameter greater than the inner diameter of the central bore 11 is selected is. A spring 12, which acts on the hydraulic actuator 6 in the direction of the stop surface 8 with a compressive force, ensures the installation of the hydraulic booster 6 to the stop surface 8 during the first phase of the opening stroke of the injection valve member 2 and in the closed position of the injector.

Zum Schließen der wenigstens einen Einspritzöffnung 3 wird die Bestromung des Magnetaktors 1 beendet. Eine das Ankerelement 4 in Schließrichtung mit einer Druckkraft beaufschlagende Ankerfeder 7 stellt die Rückstellung des Ankerelementes 4 sicher. Bei der Rückstellung gelangt das Ankerelement 4 in Anlage mit dem Einspritzventilglied 2 und drückt dieses in seinen Sitz zurück. Aufgrund der mechanischen Kopplung des Einspritzventilgliedes 2 mit dem Ankerelement 4 während der Schließphase wird die Rückstellung des Einspritzventilgliedes 2 ebenfalls über die Druckkraft der Ankerfeder 7 bewirkt. Die Federkraft der Ankerfeder 7 ist dementsprechend relativ hoch gewählt. In jedem Fall ist die Federkraft der Ankerfeder 7 höher als die Federkraft der Feder 12 gewählt, welche den hydraulischen Übersetzer in Öffnungsrichtung des Einspritzventilgliedes 2 beaufschlagt. Eine separate Schließfeder zur Rückstellung des Einspritzventilgliedes 2 ist verzichtbar, wodurch der Fertigungs- und Abstimmungsaufwand verringert wird.For closing the at least one injection opening 3, the energization of the magnetic actuator 1 is terminated. An anchor element 4 in the closing direction with a compressive force acting anchor spring 7 ensures the return of the anchor element 4. When returning the anchor element 4 comes into contact with the injection valve member 2 and pushes this back into its seat. Due to the mechanical coupling of the injection valve member 2 with the anchor member 4 during the closing phase, the return of the injection valve member 2 is also effected via the pressure force of the armature spring 7. The spring force of the armature spring 7 is therefore chosen to be relatively high. In any case, the spring force of the armature spring 7 is selected higher than the spring force of the spring 12, which acts on the hydraulic booster in the opening direction of the injection valve member 2. A separate closing spring for returning the injection valve member 2 is dispensable, whereby the manufacturing and tuning effort is reduced.

Die Erfindung ist nicht auf das dargestellte Ausführungsbeispiel begrenzt. Darüber hinaus sind Abwandlungen, insbesondere im Hinblick auf die Ausführung des Ankerelementes 4, des hydraulischen Übersetzers 6 und/oder des Einspritzventilgliedes 2, realisierbar. The invention is not limited to the illustrated embodiment. In addition, modifications, in particular with regard to the execution of the anchor element 4, the hydraulic booster 6 and / or the injection valve member 2, can be realized.

Claims (6)

  1. Fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having a magnetic actuator (1) for direct actuation of a preferably needle-shaped injection valve element (2), by means of whose stroke movement at least one injection opening (3) of the fuel injector can be opened up or closed, wherein the magnetic actuator (1) comprises an armature element (4), which can perform stroke movements, for controlling the control pressure in a control volume (5),
    characterized in that the injection valve element (2) is, during a first phase of its opening stroke, mechanically coupled to a hydraulic transmitter (6) which has an active hydraulic area A1 which delimits the control volume (5) and which, combined with an active hydraulic area A2 formed on the injection valve element (2), is larger than an active hydraulic area A3 which is formed on the armature element (4) and which delimits the control volume (5), such that force boosting is effected owing to the area ratio of the active hydraulic areas A1, A2 and A3 that are relevant with regard to the control volume (5),
    furthermore in that the mechanical coupling of the hydraulic transmitter (6) to the injection valve element (2) is, during a second phase of the opening stroke, eliminated such that, as active hydraulic areas, only the active areas A2 and A3 oppose one another, wherein the active hydraulic area A2 is smaller than the active area A3 and travel boosting is thus achieved,
    furthermore in that the injection valve element (2) is, during its closing stroke, mechanically coupled to the armature element (4), which is forced in the closing direction of the injection valve element (2) by the pressure force of an armature spring (7), such that the closing stroke of the injection valve element (2) can be effected by way of the armature spring (7).
  2. Fuel injector according to Claim 1,
    characterized in that a stop face (8) for mechanically coupling to the hydraulic transmitter (6) is formed on the injection valve element (2).
  3. Fuel injector according to Claim 2,
    characterized in that the stop face (8) which is formed on the injection valve element (2) causes the injection valve element (2) to be entrained during a stroke movement of the hydraulic transmitter (6) in order to implement power boosting during the first phase of the stroke movement of the injection valve element (2).
  4. Fuel injector according to one of the preceding claims,
    characterized in that a stop (10) for limiting the stroke of the hydraulic transmitter (6) on one side is formed on a housing part (9) of the fuel injector.
  5. Fuel injector according to one of the preceding claims,
    characterized in that the hydraulic transmitter (6) is formed in the shape of a disc or piston and has a central drilled hole (11) for accommodating the injection valve element (2).
  6. Fuel injector according to one of the preceding claims,
    characterized in that the hydraulic transmitter (6) is acted on by the pressure force of a spring (12).
EP11788109.4A 2010-11-22 2011-11-21 Fuel injector Not-in-force EP2643581B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010044205 DE102010044205A1 (en) 2010-11-22 2010-11-22 fuel injector
PCT/EP2011/070513 WO2012069393A1 (en) 2010-11-22 2011-11-21 Fuel injector

Publications (2)

Publication Number Publication Date
EP2643581A1 EP2643581A1 (en) 2013-10-02
EP2643581B1 true EP2643581B1 (en) 2016-07-06

Family

ID=45044561

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11788109.4A Not-in-force EP2643581B1 (en) 2010-11-22 2011-11-21 Fuel injector

Country Status (4)

Country Link
EP (1) EP2643581B1 (en)
CN (1) CN103221677B (en)
DE (1) DE102010044205A1 (en)
WO (1) WO2012069393A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014205910A1 (en) * 2014-03-31 2015-10-01 Robert Bosch Gmbh Fuel injector
EP3455498A4 (en) * 2016-05-12 2020-01-01 Briggs & Stratton Corporation Fuel delivery injector

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20010031761A (en) * 1997-11-03 2001-04-16 디이젤 엔진 리타더스, 인코포레이티드 Cascading electromagnetic armature
DE102004035280A1 (en) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Fuel injector with direct multi-stage injection valve element control
DE102006015745A1 (en) 2006-04-04 2007-10-11 Robert Bosch Gmbh Fuel injector especially for diesel engine has a solenoid operated valve with a bypass for enhanced switching speed
DE102007002758A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh fuel injector
DE102007028490A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Hydraulic coupler for injector, has coupler element which is connected with stationary component, where another coupler element is provided
DE102008042227A1 (en) * 2008-09-19 2010-04-01 Robert Bosch Gmbh Fuel injector, particularly common rail injector for injecting fuel into combustion chamber of internal-combustion engine, comprises injection valve element, which is adjustable between closing position and opening position
DE102009047559A1 (en) * 2009-12-07 2011-06-09 Robert Bosch Gmbh fuel injector
DE102010028835A1 (en) * 2010-05-11 2011-11-17 Robert Bosch Gmbh fuel injector

Also Published As

Publication number Publication date
CN103221677B (en) 2016-03-09
WO2012069393A1 (en) 2012-05-31
CN103221677A (en) 2013-07-24
EP2643581A1 (en) 2013-10-02
DE102010044205A1 (en) 2012-05-24

Similar Documents

Publication Publication Date Title
EP2079922B1 (en) Injector for injecting fuel
EP2386746B1 (en) Fuel injector
EP2510215B1 (en) Fuel injector
EP1865192B1 (en) Fuel injector with servo assistance
EP2100026A1 (en) Fuel injector having a solenoid valve with a spherical seat
DE102012222043A1 (en) Fuel injector for injecting fuel into combustion chamber of internal combustion engine, has coupler piston whose active faces limit hydraulic coupler in axial direction
EP2454467B1 (en) Valve arrangement
EP2643581B1 (en) Fuel injector
WO2012034749A1 (en) Fuel injector
DE102012220027A1 (en) Switching valve for common-rail fuel injector for injecting diesel into combustion chamber of internal combustion engine, has control space filled with fuel via hole, and closing element closing hole in position for pressure relief of space
DE102013226776A1 (en) fuel injector
EP2510220B1 (en) Fuel injector
EP2147206B1 (en) Fuel injector with a magnetic valve
DE102008040170A1 (en) Fuel injection valve, particularly injector for fuel injection system of air-compression, self-igniting internal combustion engine, has actuator and nozzle needle, where nozzle needle is actuated by control valve of actuator
DE102012221157A1 (en) Pressure control valve for a high-pressure accumulator of an internal combustion engine
DE102010042251A1 (en) Fuel injector for use as common-rail injector in internal combustion engine, has injector housing, which encloses high pressure chamber that stays in connection with high pressure source
EP2426348B1 (en) Fuel injector valve
DE102015223445A1 (en) Fuel injection valve for injecting a gaseous and / or liquid fuel
EP2138709B1 (en) Directly actuated fuel injector
DE102007009167A1 (en) Multi-way valve
EP1980742A1 (en) Fuel injector with integrated pressure intensifier
DE102010030385A1 (en) Injection valve for injecting fuel into combustion chamber of combustion engine, has axially movable pressure equalization piston included within hollow needle such that combustion and pressure chambers are axially limited
DE102014225347A1 (en) fuel injector
DE102008002438A1 (en) Injector for injection of fuel into combustion chamber of internal combustion engine, has actuator connected with control piston
DE102013224960A1 (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: 20130624

AK Designated contracting states

Kind code of ref document: A1

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

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20150518

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20160401

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM 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: AT

Ref legal event code: REF

Ref document number: 810914

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160715

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: 502011010128

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160706

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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: 20161106

Ref country code: RS

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: 20160706

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: 20160706

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: 20160706

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: 20160706

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: 20161006

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: 20160706

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: 20161130

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: 20161007

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: 20160706

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: 20160706

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: 20160706

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: 20160706

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: 20161107

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011010128

Country of ref document: DE

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

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: 20160706

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: 20160706

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: 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: 20160706

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: 20161006

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: 20160706

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: 20160706

Ref country code: SM

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: 20160706

26N No opposition filed

Effective date: 20170407

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: 20161121

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: 20161130

Ref country code: CH

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

Effective date: 20161130

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: 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: 20160706

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: 20161130

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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: 20161121

Ref country code: GB

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

Effective date: 20161121

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 810914

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161121

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: 20161121

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20161130

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: 20160706

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: 20111121

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160706

Ref country code: MK

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: 20160706

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: 20160706

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

Ref country code: AL

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: 20160706

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: 20160706

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: 8

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

Ref country code: IT

Payment date: 20191120

Year of fee payment: 9

Ref country code: FR

Payment date: 20191121

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011010128

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: IT

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

Effective date: 20201121

Ref country code: FR

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

Effective date: 20201130