EP2867518A1 - Fuel-injection valve for internal combustion engines - Google Patents

Fuel-injection valve for internal combustion engines

Info

Publication number
EP2867518A1
EP2867518A1 EP13724791.2A EP13724791A EP2867518A1 EP 2867518 A1 EP2867518 A1 EP 2867518A1 EP 13724791 A EP13724791 A EP 13724791A EP 2867518 A1 EP2867518 A1 EP 2867518A1
Authority
EP
European Patent Office
Prior art keywords
fuel
pressure chamber
valve needle
valve
fuel injection
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.)
Granted
Application number
EP13724791.2A
Other languages
German (de)
French (fr)
Other versions
EP2867518B1 (en
Inventor
Hans-Peter ZEITLHOFER
Roland Mitter
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 EP2867518A1 publication Critical patent/EP2867518A1/en
Application granted granted Critical
Publication of EP2867518B1 publication Critical patent/EP2867518B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement

Definitions

  • the invention relates to a fuel injection valve, as it is preferably used for the injection of fuel directly into combustion chambers of internal combustion engines use, preferably of those that operate on the principle of auto-ignition.
  • Injection valves are known for injecting fuel, which introduce the fuel under high pressure into combustion chambers.
  • the injection of the fuel is done by one or more injection ports under very high pressure, which may be up to 2500 bar, to achieve a fine atomization of the fuel.
  • the fuel together with the compressed air in the combustion chamber forms an ignitable mixture which burns spontaneously or externally ignited.
  • the injectors usually have a valve needle, which is arranged longitudinally displaceable in the housing of a fuel injection valve.
  • the valve needle is mounted longitudinally movable in a pressure chamber and surrounded by fuel under high pressure.
  • the valve needle opens or closes one or more injection openings through which the fuel finally reaches the combustion chamber of the internal combustion engine.
  • This movement of the valve needle must be performed very quickly and precisely to bring exactly the required amount of fuel at the desired time in the combustion chamber.
  • a fuel injection valve is known for example from the published patent application DE 36 24 476 AI.
  • this In order to guide the valve needle in the pressure chamber, this has at least one guide section, with which the valve needle is guided in the radial direction.
  • Object of the present invention is to pass the fuel flow on the one hand to the leadership of the valve needle and on the other hand to achieve a defined throttling of the fuel flow to a pressure difference between the upstream and downstream of the guide portion to arranged Part of the pressure chamber to reach.
  • the valve needle of the fuel injection valve is arranged in a pressure chamber and closes and opens by its longitudinal movement at least one injection port through which fuel can be introduced into a combustion chamber of an internal combustion engine.
  • an annular space can flow through the fuel at high pressure in the direction of the injection openings.
  • a guide portion is formed by the valve needle is guided.
  • the valve needle has a longitudinal bore through which fuel can flow from the part of the pressure chamber formed upstream of the guide section into the part of the pressure chamber formed downstream of the guide section, the longitudinal bore being connected to the pressure chamber via a plurality of throttle bores formed in the valve needle is.
  • These bores can both form the inlet into the longitudinal bore, that is to say be arranged upstream of the guide section within the valve needle, and also form the outflow of the fuel from the longitudinal bore into the pressure chamber, ie be formed downstream of the guide section.
  • the respective other connection which forms the inlet and outlet into the longitudinal bore, is ensured by a further connection which is formed between the longitudinal bore and the pressure chamber.
  • the further connection is formed by a plurality of filter bores formed in the valve needle. These filter bores, which are formed as holes extending in the radial direction within the valve needle, provide a filter for dirt particles that can enter the fuel flow in the injector and cause malfunction.
  • the filter holes are formed in such a number and with such a diameter that on the one hand they have a good filtering effect, but on the other hand, the fuel flow into the longitudinal bore or from the longitudinal bore in the pressure chamber or only insignificantly throttle, so that the throttling of the fuel flow and thus the pressure difference is caused exclusively by the throttle bores.
  • the filter bores form the further connection upstream of the guide section is formed, so that the throttle bores form the flow path formed downstream of the guide portion of the longitudinal bore in the pressure chamber. Dirt particles entering the injector are thus already retained by the filter bores prior to entry into the longitudinal bore, so that they are not added to the throttle bores by dirt particles and thus lose their effect to cause a well-defined pressure drop.
  • the throttle bores are preferably formed as a radially extending bores having a diameter of preferably 50 to 250 ⁇ . This diameter range allows to achieve the desired effect with a manageable number of throttle bores.
  • the valve needle consists of at least two partial valve needles, which are connected to each other in the region of the longitudinal bore.
  • the longitudinal bore can be formed by two blind bores formed in the respective partial valve needles, from which the longitudinal bore results through the joining together of the partial valve needles.
  • Figure 1 is a schematic representation of a longitudinal section through an inventive fuel injection valve with the essential components connected and
  • Figure 2 is an enlarged view of the valve body arranged therein
  • the fuel injection valve 1 shows a fuel injection valve 1 according to the invention is shown schematically in longitudinal section.
  • the fuel injection valve 1 comprises a housing 2, which comprises a holding body 4 and a valve body 5, which bear against each other with their respective end faces.
  • the holding body 4 and the valve body 5 are pressed against each other by a device, not shown in the drawing, so that fuel from the interior of the housing 2 can not escape to the outside, so there is a liquid-tight connection between the two parts of the housing 2.
  • a pressure chamber 6 is formed which can be filled with fuel under high pressure.
  • a valve needle 10 is arranged longitudinally displaceable, which has a sealing surface 11 at its end facing the combustion chamber, which has a substantially conical shape and cooperates with a formed in the valve body 5 valve seat 12. If the valve needle 10 with the sealing surface 11 on the valve seat 12, so one or more injection ports 8, which are formed in the valve body 5, sealed against the pressure chamber 6. On the other hand, if the valve needle 10 is lifted off the valve seat 12, a connection between the sealing surface 11 and the valve seat 12 is opened, through which fuel can flow from the pressure chamber 6 to the injection openings 8. When the fuel injection valve is installed in an internal combustion engine, the fuel passes through the injection openings 8 into a combustion chamber of the internal combustion engine.
  • the valve needle 10 extends into the holding body 4 and is at the valve seat facing away from the end of the valve needle 10 is guided in a sleeve 22 which defines a control chamber 26 together with the valve seat facing away from the end of the valve needle 10 and a throttle plate 30.
  • the sleeve 22 is pressed by a spring 25 against the throttle plate 30, wherein the spring 25 is arranged under pressure bias and is supported at its other end to a shoulder 24 which is formed on the valve needle 10.
  • the remaining between the valve needle 10 and the wall of the pressure chamber 6 space serves as a fuel line, through the fuel through the pressure chamber 6 up to the injection openings 8 can flow.
  • a guide portion 14 is formed in the valve body 5, in which the valve needle 10 is guided.
  • the remaining between the valve needle 10 and the guide portion 14 gap is so small that on the one hand a lubricating film between the valve needle 10 and the wall of the pressure chamber 6 remains to allow movement of the valve needle 10, but on the other hand is so tight that Fuel can flow through this residual gap in the direction of the injection openings 8 only to a very small extent, so only a leakage flow is possible.
  • a longitudinal bore 15 is formed in the valve needle 10 and runs at the level of the guide section 14.
  • the longitudinal bore 15 can be formed, for example, in that the valve needle 10 consists of two valve needle parts 110, 210.
  • the first valve needle part 110 is arranged in the valve body 5, while the second valve needle part 210 is arranged in the holding body 4.
  • the two valve needle parts 110, 210 abut each other and are fixedly connected to each other, for example by a welded or soldered connection.
  • the longitudinal bore 15 can then be formed by blind bores, which are introduced in the first valve needle part 110 and in the second valve needle part 210.
  • a plurality of throttle bores 20 are formed in the second valve needle part 210, which is arranged in the holding body 4.
  • the throttle bores 20 are formed as radial bores which have a diameter such that the fuel Ström flows with the fuel injection valve open from the pressure chamber 6 through the throttle bores 20 in the longitudinal bore 15.
  • the fuel experiences at the throttle bores 20 a pressure drop, whereby within the longitudinal bore 15, a lower pressure prevails than in the pressure chamber 6 upstream of the guide portion 14.
  • the fuel then flows through the longitudinal bore 15 further direction injection ports 8 and passes through a connection 17, here as Inclined bore is formed in the valve needle 10, in the downstream of the The fuel finally flows through this until it is introduced via the injection openings 8 in a combustion chamber.
  • the control of the longitudinal movement of the valve needle 10 in the pressure chamber 6 is effected by an alternating pressure in the control chamber 26.
  • a flow restrictor 41 is formed in the throttle plate 30, which can be connected via a control valve 32 and a drain line 34 to a fuel tank 40 in which only a low pressure, preferably ambient pressure, prevails.
  • the control valve 32 is preferably an electromagnetic valve that can be opened or closed by applying a control current.
  • the high-pressure accumulator 36 contains fuel under high pressure, with which the fuel is ultimately to be introduced into the combustion chamber, and in turn is supplied from the fuel tank 40 via a high-pressure pump 37 with compressed fuel. With the high-pressure accumulator 36 a plurality of injectors 1 may be connected, which are each connected via high-pressure lines 35 to the high-pressure accumulator 36.
  • valve needle 10 In the closed state of the fuel injection valve 1, the valve needle 10 is pressed by the pressure in the control chamber 26 and the consequent hydraulic force in the direction of the valve seat 12. Although the spring 25 presses the valve needle 10 also in the direction of the valve seat 12, but this force plays only a minor role in relation to the large hydraulic forces. Since the valve needle 10 rests with its sealing surface 11 on the valve seat 12, parts of the valve sealing surface are not acted upon by the pressure of the pressure chamber 6, so that there is an excess of force in the direction of the valve seat 12, which is due to the hydraulic forces. The control valve 32 is in its closed position, so that the drain line 34 is interrupted.
  • the control valve 32 is opened, so that the control chamber 26 via the outlet throttle 41 and the Leakage oil line 34 is connected to the fuel tank 40.
  • the pressure in the control chamber 26 decreases, wherein the outlet throttle 41 and the inlet throttle 42 are dimensioned so that when the control valve 32 is open, more fuel flows out of the control chamber 26 than flows through the inlet throttle 42 in the same period. Due to the hydraulic forces on the valve needle 10, in particular within the valve body 5, now results in a resultant force on the valve needle 10, which is directed away from the valve seat 12 and the valve needle 10 spends in its open position.
  • valve needle 10 lifts off from the valve seat 12 and releases the injection openings 8, so that fuel is ejected from the pressure chamber 6 via the injection openings 8.
  • control valve 32 is closed again, and it turns in the control chamber 26 again a high fuel pressure, which urges the valve needle 10 with a closing force in the direction of the valve seat 12 and pushes back into its closed position.
  • the valve needle 10 is configured to be substantially force balanced in the open state and when the control space 26 is again flooded with fuel at high pressure, i. H.
  • the hydraulic forces cancel each other in the longitudinal direction largely against each other. Since the closing force exerted by the spring 25 on the valve needle 10 is not sufficient for a quick closing alone, the closing of the valve needle 10 must be hydraulically assisted, as too slow needle closing leads to increased pollutant emissions. For this purpose, a pressure difference between the areas of the pressure chamber upstream and downstream of the guide portion 14 must be achieved because then the opening force on the valve needle 10 by the fuel pressure in the valve body 5 is lower than the closing force, by the hydraulic force within the control chamber 26 on the valve needle 10 is exercised.
  • the fuel flows to the injection openings 8 through the longitudinal bore 15 within the valve needle 10 by entering through the throttle bores 20 from the pressure chamber 6 in the longitudinal bore 15.
  • the throttle bores 20 whose number and diameter is so dimensioned that with the fuel injection valve open a pressure reduction takes place at these throttle bores 20, such a pressure difference is achieved.
  • connection of the longitudinal bore 15 with the pressure chamber 6 takes place upstream of the guide portion 14 via the throttle bores 20, as shown in Figure 1.
  • the connection 17 located downstream of the guide section 14 takes place, for example, through an oblique bore within the valve needle 10. It is also possible to provide a plurality of inclined bores which ensure the connection.
  • valve needle 10 here also has a longitudinal bore 15, wherein the connection with the pressure chamber 6 upstream of the guide section 14 is achieved by filter bores 21, which are introduced into the valve needle 10 in the radial direction.
  • the filter bores 21 are dimensioned in number and diameter so that no or only a slight pressure reduction takes place at these filter bores 21 compared with the pressure reduction at the throttle bores 20 '.
  • the filter bores 21 serve at this point the filtering of the fuel, d. H. in that through the filter bores 21 particles in the fuel which have entered the fuel injection valve 1 are filtered out so that they do not reach the injection openings 8.
  • Another advantage is that the throttle bores 20 'are not added with particles. As a result, the effect of the throttle bores 20 'is maintained throughout the life of the fuel injection valve.
  • connection of the longitudinal bore 15 with the downstream of the guide portion 14 located part of the pressure chamber 6 takes place, as in the embodiment shown in Figure 1, via orifices 20 ', which produce the desired pressure difference between the longitudinal bore 15 and the pressure chamber 6.
  • this pressure reduction takes place only when the fuel flow is actually in motion, ie only when the fuel injection valve is open. When the fuel injection valve is in the closed state, a fuel pressure which is the same within the entire pressure chamber 6 returns very quickly.
  • the throttle bores 20, 20 ' are designed as radial bores and can be produced in various ways, for example by electroerosion or by a laser drilling process.
  • the diameter of the throttle bores 20, 20 ' is preferably 50 to 250 ⁇ , depending on the viscosity of the fuel and depending on the number of throttle bores 20, 20'.
  • the diameter of the filter bores 21 is dimensioned such that, taking into account the number of filter bores 21, there is no or only a slight pressure reduction with respect to the pressure reduction at the throttle bores 20.
  • the diameter of the filter bores 21 depends on the size of the expected particles and is in the order of 100 to 300 ⁇ .

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)

Abstract

The invention concerns a fuel-injection valve (1) for internal combustion engines, with a housing (2), in which is formed a pressure chamber (6) from which at least one injection opening (8) proceeds. Disposed in the pressure chamber (6) is a valve needle (10), of which the longitudinal movement opens and closes the at least one injection opening (8), there remaining at least in sections between the valve needle (10) and the wall of the pressure chamber (6) an annular space which can be filled with fuel at high pressure and through which fuel can flow in the direction of the injection openings (8). The valve needle (10) is guided by a guide section (14) in the pressure chamber (6) and comprises, in the region of the guide section (14), an elongate bore (15), through which fuel can flow from the part of the pressure chamber (6) formed upstream of the guide section (14) into the part of the pressure chamber (6) formed downstream of the guide section (14), the elongate bore (15) being connected to the pressure chamber (6) by means of a plurality of throttle bores (20, 20') formed in the valve needle (10).

Description

Beschreibung Titel  Description title
Kraftstoffeinspritzventil für Brennkraftmaschinen  Fuel injection valve for internal combustion engines
Die Erfindung betrifft ein Kraftstoffeinspritzventil, wie es vorzugsweise zur Einspritzung von Kraftstoff direkt in Brennräume von Brennkraftmaschinen Verwendung findet, vorzugsweise von solchen, die nach dem Prinzip der Selbstzündung arbeiten. The invention relates to a fuel injection valve, as it is preferably used for the injection of fuel directly into combustion chambers of internal combustion engines use, preferably of those that operate on the principle of auto-ignition.
Stand der Technik State of the art
Zur Einspritzung von Kraftstoff sind Einspritzventile bekannt, die den Kraftstoff unter hohem Druck in Brennräume einbringen. Die Einspritzung des Kraftstoffs geschieht dabei durch eine oder mehrere Einspritzöffnungen unter sehr hohem Druck, der bis zu 2500 bar betragen kann, um ein feines Zerstäuben des Kraftstoffs zu erreichen. Der Kraftstoff bildet zusammen mit der verdichteten Luft im Brennraum ein zündfähiges Gemisch, das selbst- oder fremdgezündet verbrennt. Injection valves are known for injecting fuel, which introduce the fuel under high pressure into combustion chambers. The injection of the fuel is done by one or more injection ports under very high pressure, which may be up to 2500 bar, to achieve a fine atomization of the fuel. The fuel together with the compressed air in the combustion chamber forms an ignitable mixture which burns spontaneously or externally ignited.
Zur Steuerung der Einspritzung weisen die Einspritzventile in aller Regel eine Ventilnadel auf, die längsverschiebbar im Gehäuse eines Kraftstoffeinspritzventils angeordnet ist. Die Ventilnadel ist dabei in einem Druckraum längsbewegbar gelagert und von Kraftstoff unter hohem Druck umgeben. Durch ihre Längsbewegung öffnet oder schließt die Ventilnadel eine oder mehrere Einspritzöffnungen, durch die der Kraftstoff letztendlich in den Brennraum der Brennkraftmaschine gelangt. Diese Bewegung der Ventilnadel muss sehr rasch und präzise durchgeführt werden, um genau die benötigte Kraftstoffmenge zum gewünschten Zeitpunkt in den Brennraum einzubringen. Ein solches Kraftstoffeinspritzventil ist beispielweise aus der Offenlegungsschrift DE 36 24 476 AI bekannt. Um die Ventilnadel im Druckraum zu führen, weist diese wenigstens einen Führungsabschnitt auf, mit dem die Ventilnadel in radialer Richtung geführt ist. Es können aber auch mehrere Führungsabschnitte vorgesehen sein. Um den Kraftstoff zwischen der Wand des Druckraums und der Ventilnadel hindurch zu den Einspritzöffnungen zu bringen, ist zwischen der Ventilnadel und der Wand des Druckraums ein Ringraum vorgesehen, durch den der Kraftstoff den Einspritzöffnungen zufließt. Im Bereich des Führungsabschnitts, also dort, wo die Ventilnadel im Druckraum geführt ist, müssen besondere Vorkehrungen getroffen werden, um einen drosselfreien Fluss des Kraftstoffs zu ermöglichen. Hier sind vor allem Anschliffe an der Ventilnadel bekannt, die trotz der Führung der Ventilnadel innerhalb der Bohrung einen Fluss des Kraftstoffs ermöglichen. Darüber hinaus ist beispielsweise aus der DE 36 24 476 AI bekannt, den Kraftstoff durch eine Schrägbohrung zu leiten, die in der Ventilnadel ausgebildet ist und im Bereich des Führungsabschnitts verläuft. To control the injection, the injectors usually have a valve needle, which is arranged longitudinally displaceable in the housing of a fuel injection valve. The valve needle is mounted longitudinally movable in a pressure chamber and surrounded by fuel under high pressure. As a result of its longitudinal movement, the valve needle opens or closes one or more injection openings through which the fuel finally reaches the combustion chamber of the internal combustion engine. This movement of the valve needle must be performed very quickly and precisely to bring exactly the required amount of fuel at the desired time in the combustion chamber. Such a fuel injection valve is known for example from the published patent application DE 36 24 476 AI. In order to guide the valve needle in the pressure chamber, this has at least one guide section, with which the valve needle is guided in the radial direction. But it can also be provided several guide sections. In order to bring the fuel between the wall of the pressure chamber and the valve needle through to the injection openings, an annular space is provided between the valve needle and the wall of the pressure chamber, through which the fuel flows to the injection openings. In the area of the guide section, ie where the valve needle is guided in the pressure chamber, special precautions must be taken to allow a throttle-free flow of the fuel. Here, above all, polished sections on the valve needle are known, which allow a flow of the fuel despite the leadership of the valve needle within the bore. In addition, for example, from DE 36 24 476 AI known to direct the fuel through an oblique bore which is formed in the valve needle and extends in the region of the guide portion.
In der Regel soll vermieden werden, dass der Kraftstoffdruck bei seinem Weg durch den Druckraum nennenswert an Druck verliert, indem er Engstellen passiert, da der volle Einspritzdruck an den Einspritzöffnungen zur Verfügung stehen soll, um eine bestmögliche Zerstäubung zu gewährleisten. Bei manchen Einspritzventilen ist jedoch auch eine gezielte Minderung des Kraftstoffdrucks erwünscht und für die Funktion notwendig. So ist beispielsweise aus der Schrift DE 10 2007 032 741 AI ein Kraftstoffeinspritzventil bekannt, bei dem ein Drosselbund an der Ventilnadel ausgebildet ist, so dass der Kraftstoff bei seinem Fluss durch den Druckraum in Richtung der Einspritzöffnungen an dieser Stelle gedrosselt wird und somit etwas an Druck verliert. Dies ist notwendig, um ein sicheres Schließen der Ventilnadel zu ermöglichen, die ansonsten weitgehend in Längsrichtung druckausgeglichen ist. As a rule, it should be avoided that the fuel pressure on its way through the pressure chamber significantly loses pressure by passing bottlenecks, since the full injection pressure at the injection ports should be available to ensure the best possible atomization. In some injectors, however, a targeted reduction of the fuel pressure is desired and necessary for the function. For example, from DE 10 2007 032 741 AI a fuel injection valve is known in which a throttle collar is formed on the valve needle, so that the fuel is throttled at its flow through the pressure chamber in the direction of the injection openings at this point and thus some pressure loses. This is necessary to allow a safe closing of the valve needle, which is otherwise largely pressure balanced in the longitudinal direction.
Offenbarung der Erfindung Disclosure of the invention
Aufgabe der vorliegenden Erfindung ist es, den Kraftstoffstrom einerseits an der Führung der Ventilnadel vorbeizuleiten und andererseits eine definierte Drosselung des Kraftstoffstroms zu erreichen, um eine Druckdifferenz zwischen dem stromaufwärts und dem stromabwärts des Führungsabschnitts zu angeordneten Teil des Druckraums zu erreichen. Hierzu ist die Ventilnadel des Kraftstoffeinspritzventils in einem Druckraum angeordnet und schließt und öffnet durch ihre Längsbewegung wenigstens eine Einspritzöffnung, durch die Kraftstoff in einen Brennraum einer Brennkraftmaschine eingebracht werden kann. Hierbei verbleibt zwischen der Ventilnadel und der Wand des Druckraums zumindest abschnittsweise ein Ringraum, über den Kraftstoff unter hohem Druck in Richtung der Einspritzöffnungen fließen kann. Innerhalb des Druckraums ist ein Führungsabschnitt ausgebildet, indem die Ventilnadel geführt ist. Die Ventilnadel weist auf Höhe des Führungsabschnitts 14 eine Längsbohrung auf, durch die Kraftstoff von dem stromaufwärts des Führungsabschnitts ausgebildeten Teil des Druckraums in den stromabwärts des Führungsabschnitts ausgebildeten Teil des Druckraums fließen kann, wobei die Längsbohrung über mehrere in der Ventilnadel ausgebildete Drosselbohrungen mit dem Druckraum verbunden ist. Diese Bohrungen können sowohl den Zulauf in die Längsbohrung bilden, also stromaufwärts des Führungsabschnitts innerhalb der Ventilnadel angeordnet sein, als auch den Ab- fluss des Kraftstoffs aus der Längsbohrung in den Druckraum bilden, also stromabwärts des Führungsabschnitts ausgebildet sein. Object of the present invention is to pass the fuel flow on the one hand to the leadership of the valve needle and on the other hand to achieve a defined throttling of the fuel flow to a pressure difference between the upstream and downstream of the guide portion to arranged Part of the pressure chamber to reach. For this purpose, the valve needle of the fuel injection valve is arranged in a pressure chamber and closes and opens by its longitudinal movement at least one injection port through which fuel can be introduced into a combustion chamber of an internal combustion engine. In this case, at least in sections remains between the valve needle and the wall of the pressure chamber, an annular space, can flow through the fuel at high pressure in the direction of the injection openings. Within the pressure chamber, a guide portion is formed by the valve needle is guided. At the level of the guide section 14, the valve needle has a longitudinal bore through which fuel can flow from the part of the pressure chamber formed upstream of the guide section into the part of the pressure chamber formed downstream of the guide section, the longitudinal bore being connected to the pressure chamber via a plurality of throttle bores formed in the valve needle is. These bores can both form the inlet into the longitudinal bore, that is to say be arranged upstream of the guide section within the valve needle, and also form the outflow of the fuel from the longitudinal bore into the pressure chamber, ie be formed downstream of the guide section.
Je nachdem, ob die Drosselbohrungen stromaufwärts oder stromabwärts des Führungsabschnitts ausgebildet sind, wird die jeweils andere Verbindung, die den Zu- bzw. Ablauf in die Längsbohrung bildet, durch eine weitere Verbindung sichergestellt, die zwischen der Längsbohrung und dem Druckraum ausgebildet ist. In einer vorteilhaften Ausgestaltung der Erfindung ist die weitere Verbindung durch mehrere in der Ventilnadel ausgebildete Filterbohrungen gebildet. Diese Filterbohrungen, die als in radialer Richtung verlaufende Bohrungen innerhalb der Ventilnadel ausgebildet sind, stellen einen Filter für Schmutzpartikel dar, die im Kraftstoffstrom in den Injektor gelangen und dort Fehlfunktionen verursachen können. Die Filterbohrungen werden in einer solchen Anzahl und mit einem solchen Durchmesser ausgebildet, dass sie einerseits eine gute Filterwirkung haben, andererseits jedoch den Kraftstoff ström in die Längsbohrung bzw. von der Längsbohrung in den Druckraum nicht oder nur unwesentlich drosseln, so dass die Drosselung des Kraftstoffstroms und damit die Druckdifferenz ausschließlich durch die Drosselbohrungen hervorgerufen wird. Vorzugsweise bilden die Filterbohrungen die weitere Verbindung, die stromaufwärts des Führungsabschnitts ausgebildet ist, so dass die Drosselbohrungen den stromabwärts des Führungsabschnitts ausgebildeten Strömungspfad von der Längsbohrung in den Druckraum bilden. Schmutzpartikel, die in den Injektor gelangen, werden so bereits vor dem Eintritt in die Längsbohrung durch die Filterbohrungen zurückgehalten, so dass sie die Drosselbohrungen nicht durch Schmutzpartikel zugesetzt werden und so ihre Wirkung, einen genau definierten Druckabfall zu bewirken, verlieren. Depending on whether the throttle bores are formed upstream or downstream of the guide section, the respective other connection, which forms the inlet and outlet into the longitudinal bore, is ensured by a further connection which is formed between the longitudinal bore and the pressure chamber. In an advantageous embodiment of the invention, the further connection is formed by a plurality of filter bores formed in the valve needle. These filter bores, which are formed as holes extending in the radial direction within the valve needle, provide a filter for dirt particles that can enter the fuel flow in the injector and cause malfunction. The filter holes are formed in such a number and with such a diameter that on the one hand they have a good filtering effect, but on the other hand, the fuel flow into the longitudinal bore or from the longitudinal bore in the pressure chamber or only insignificantly throttle, so that the throttling of the fuel flow and thus the pressure difference is caused exclusively by the throttle bores. Preferably, the filter bores form the further connection upstream of the guide section is formed, so that the throttle bores form the flow path formed downstream of the guide portion of the longitudinal bore in the pressure chamber. Dirt particles entering the injector are thus already retained by the filter bores prior to entry into the longitudinal bore, so that they are not added to the throttle bores by dirt particles and thus lose their effect to cause a well-defined pressure drop.
Die Drosselbohrungen sind vorzugsweise als radial verlaufende Bohrungen ausgebildet mit einem Durchmesser von vorzugsweise 50 bis 250 μηη. Dieser Durchmesserbereich erlaubt, die gewünschte Wirkung mit einer überschaubaren Zahl von Drosselbohrungen zu erreichen. The throttle bores are preferably formed as a radially extending bores having a diameter of preferably 50 to 250 μηη. This diameter range allows to achieve the desired effect with a manageable number of throttle bores.
In einer weiteren vorteilhaften Ausgestaltung der Erfindung besteht die Ventilnadel aus wenigstens zwei Teilventilnadeln, die im Bereich der Längsbohrung miteinander verbunden sind. Dadurch lässt sich die Längsbohrung durch zwei in den jeweiligen Teilventilnadeln ausgebildete Sackbohrungen bilden, aus denen sich durch das Zusammenfügen der Teilventilnadeln die Längsbohrung ergibt. In a further advantageous embodiment of the invention, the valve needle consists of at least two partial valve needles, which are connected to each other in the region of the longitudinal bore. As a result, the longitudinal bore can be formed by two blind bores formed in the respective partial valve needles, from which the longitudinal bore results through the joining together of the partial valve needles.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der Beschreibung und der Zeichnung entnehmbar. Further advantages and advantageous embodiments of the invention are the description and the drawings can be removed.
Zeichnungen drawings
In der Zeichnung sind Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt In the drawings, embodiments of the fuel injection valve according to the invention are shown. It shows
Figur 1 in schematischer Darstellung einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil mit den wesentlichen angeschlossenen Komponenten und  Figure 1 is a schematic representation of a longitudinal section through an inventive fuel injection valve with the essential components connected and
Figur 2 eine vergrößerte Darstellung des Ventilkörpers mit darin angeordneter  Figure 2 is an enlarged view of the valve body arranged therein
Ventilnadel eines weiteren Ausführungsbeispiels. Beschreibung der Ausführungsbeispiele Valve needle of another embodiment. Description of the embodiments
In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil 1 schematisch im Längsschnitt dargestellt. Das Kraftstoffeinspritzventil 1 umfasst ein Gehäuse 2, das einen Haltekörper 4 und einen Ventilkörper 5 umfasst, die mit ihren jeweiligen Stirnseiten aneinander anliegen. Der Haltekörper 4 und der Ventilkörper 5 werden dabei von einer in der Zeichnung nicht dargestellten Vorrichtung gegeneinander verpresst, so dass Kraftstoff vom Inneren des Gehäuses 2 nicht nach außen gelangen kann, also eine flüssigkeitsdichte Verbindung zwischen den beiden Teilen des Gehäuses 2 besteht. Im Haltekörper 4 und im Ventilkörper 5 ist ein Druckraum 6 ausgebildet, der mit Kraftstoff unter hohem Druck befüllbar ist. Im Druckraum 6 ist eine Ventilnadel 10 längsverschiebbar angeordnet, die an ihrem dem Brennraum zugewandten Ende eine Dichtfläche 11 aufweist, die im Wesentlichen eine konische Form aufweist und mit einem im Ventilkörper 5 ausgebildeten Ventilsitz 12 zusammenwirkt. Liegt die Ventilnadel 10 mit der Dichtfläche 11 auf dem Ventilsitz 12 auf, so werden eine oder mehrere Einspritzöffnungen 8, die im Ventilkörper 5 ausgebildet sind, gegen den Druckraum 6 abgedichtet. Hebt die Ventilnadel 10 hingegen vom Ventilsitz 12 ab, so wird eine Verbindung zwischen der Dichtfläche 11 und dem Ventilsitz 12 aufgesteuert, durch die Kraftstoff aus dem Druckraum 6 zu den Einspritzöffnungen 8 strömen kann. Der Kraftstoff gelangt dann, wenn das Kraftstoffeinspritzventil in einer Brennkraftma- schine verbaut ist, durch die Einspritzöffnungen 8 in einen Brennraum der Brenn- kraftmaschine. 1 shows a fuel injection valve 1 according to the invention is shown schematically in longitudinal section. The fuel injection valve 1 comprises a housing 2, which comprises a holding body 4 and a valve body 5, which bear against each other with their respective end faces. The holding body 4 and the valve body 5 are pressed against each other by a device, not shown in the drawing, so that fuel from the interior of the housing 2 can not escape to the outside, so there is a liquid-tight connection between the two parts of the housing 2. In the holding body 4 and in the valve body 5, a pressure chamber 6 is formed which can be filled with fuel under high pressure. In the pressure chamber 6, a valve needle 10 is arranged longitudinally displaceable, which has a sealing surface 11 at its end facing the combustion chamber, which has a substantially conical shape and cooperates with a formed in the valve body 5 valve seat 12. If the valve needle 10 with the sealing surface 11 on the valve seat 12, so one or more injection ports 8, which are formed in the valve body 5, sealed against the pressure chamber 6. On the other hand, if the valve needle 10 is lifted off the valve seat 12, a connection between the sealing surface 11 and the valve seat 12 is opened, through which fuel can flow from the pressure chamber 6 to the injection openings 8. When the fuel injection valve is installed in an internal combustion engine, the fuel passes through the injection openings 8 into a combustion chamber of the internal combustion engine.
Die Ventilnadel 10 erstreckt sich bis in den Haltekörper 4 und ist am ventilsitzabgewandten Ende ist die Ventilnadel 10 in einer Hülse 22 geführt, die zusammen mit der ventilsitzabgewandten Stirnseite der Ventilnadel 10 und einer Drosselplatte 30 einen Steuerraum 26 begrenzt. Die Hülse 22 wird durch eine Feder 25 entgegen die Drosselplatte 30 gedrückt, wobei die Feder 25 unter Druckvorspannung angeordnet ist und sich mit ihrem anderen Ende an einem Absatz 24 abstützt, der an der Ventilnadel 10 ausgebildet ist. The valve needle 10 extends into the holding body 4 and is at the valve seat facing away from the end of the valve needle 10 is guided in a sleeve 22 which defines a control chamber 26 together with the valve seat facing away from the end of the valve needle 10 and a throttle plate 30. The sleeve 22 is pressed by a spring 25 against the throttle plate 30, wherein the spring 25 is arranged under pressure bias and is supported at its other end to a shoulder 24 which is formed on the valve needle 10.
Der zwischen der Ventilnadel 10 und der Wand des Druckraums 6 verbleibende Raum dient als Kraftstoff leitung, über die Kraftstoff durch den Druckraum 6 bis zu den Einspritzöffnungen 8 fließen kann. Zur Anordnung der Ventilnadel 10 genau mittig im Druckraum 6 ist ein Führungsabschnitt 14 im Ventilkörper 5 ausgebildet, in dem die Ventilnadel 10 geführt ist. Der zwischen der Ventilnadel 10 und dem Führungsabschnitt 14 verbleibende Zwischenraum ist dabei so gering, dass zwar einerseits ein Schmierfilm zwischen der Ventilnadel 10 und der Wand des Druckraums 6 verbleibt, um eine Bewegung der Ventilnadel 10 zu ermöglichen, der jedoch andererseits so eng ist, dass Kraftstoff nur in sehr geringem Ausmaß durch diesen Restspalt in Richtung der Einspritzöffnungen 8 fließen kann, also nur eine Leckageströmung möglich ist. The remaining between the valve needle 10 and the wall of the pressure chamber 6 space serves as a fuel line, through the fuel through the pressure chamber 6 up to the injection openings 8 can flow. For the arrangement of the valve needle 10 exactly in the middle of the pressure chamber 6, a guide portion 14 is formed in the valve body 5, in which the valve needle 10 is guided. The remaining between the valve needle 10 and the guide portion 14 gap is so small that on the one hand a lubricating film between the valve needle 10 and the wall of the pressure chamber 6 remains to allow movement of the valve needle 10, but on the other hand is so tight that Fuel can flow through this residual gap in the direction of the injection openings 8 only to a very small extent, so only a leakage flow is possible.
Damit Kraftstoff aus dem stromaufwärts des Führungsabschnitts 14 gelegenen Bereich des Druckraums 6 in den stromabwärts gelegenen Teil des Druckraums 6 fließen kann, ist in der Ventilnadel 10 eine Längsbohrung 15 ausgebildet, die auf Höhe des Führungsabschnitts 14 verläuft. Die Längsbohrung 15 kann beispielsweise dadurch ausgebildet werden, dass die Ventilnadel 10 aus zwei Ventilnadelteilen 110, 210 besteht. Das erste Ventilnadelteil 110 ist dabei im Ventilkörper 5 angeordnet, während das zweite Ventilnadelteil 210 im Haltekörper 4 angeordnet ist. An der Grenzfläche 28 liegen die beiden Ventilnadelteile 110, 210 aneinander und sind miteinander fest verbunden, beispielweise durch eine Schweiß- oder Lötverbindung. Die Längsbohrung 15 kann dann durch Sackbohrungen gebildet werden, die im ersten Ventilnadelteil 110 bzw. im zweiten Ventilnadelteil 210 eingebracht sind. In order for fuel to flow from the region of the pressure chamber 6 located upstream of the guide section 14 into the downstream part of the pressure chamber 6, a longitudinal bore 15 is formed in the valve needle 10 and runs at the level of the guide section 14. The longitudinal bore 15 can be formed, for example, in that the valve needle 10 consists of two valve needle parts 110, 210. The first valve needle part 110 is arranged in the valve body 5, while the second valve needle part 210 is arranged in the holding body 4. At the interface 28, the two valve needle parts 110, 210 abut each other and are fixedly connected to each other, for example by a welded or soldered connection. The longitudinal bore 15 can then be formed by blind bores, which are introduced in the first valve needle part 110 and in the second valve needle part 210.
Zur Ermöglichung des Kraftstoff Stroms durch die Längsbohrung 15 sind im zweiten Ventilnadelteil 210, der im Haltekörper 4 angeordnet ist, mehrere Drosselbohrungen 20 ausgebildet. Die Drosselbohrungen 20 sind als radiale Bohrungen ausgebildet, die einen solchen Durchmesser aufweisen, dass der Kraftstoff ström bei geöffnetem Kraftstoffeinspritzventil aus dem Druckraum 6 durch die Drosselbohrungen 20 in die Längsbohrung 15 strömt. Der Kraftstoff erfährt an den Drosselbohrungen 20 einen Druckabfall, wodurch innerhalb der Längsbohrung 15 ein geringerer Druck herrscht als im Druckraum 6 stromaufwärts des Führungsabschnitts 14. Der Kraftstoff strömt sodann durch die Längsbohrung 15 weiter Richtung Einspritzöffnungen 8 und gelangt über eine Verbindung 17, die hier als Schrägbohrung in der Ventilnadel 10 ausgebildet ist, in den stromabwärts des Führungsabschnitts 14 gelegenen Teil des Druckraums 6. Durch diesen fließt der Kraftstoff schließlich weiter, bis er über die Einspritzöffnungen 8 in einen Brennraum eingebracht wird. To allow the fuel flow through the longitudinal bore 15, a plurality of throttle bores 20 are formed in the second valve needle part 210, which is arranged in the holding body 4. The throttle bores 20 are formed as radial bores which have a diameter such that the fuel Ström flows with the fuel injection valve open from the pressure chamber 6 through the throttle bores 20 in the longitudinal bore 15. The fuel experiences at the throttle bores 20 a pressure drop, whereby within the longitudinal bore 15, a lower pressure prevails than in the pressure chamber 6 upstream of the guide portion 14. The fuel then flows through the longitudinal bore 15 further direction injection ports 8 and passes through a connection 17, here as Inclined bore is formed in the valve needle 10, in the downstream of the The fuel finally flows through this until it is introduced via the injection openings 8 in a combustion chamber.
Die Steuerung der Längsbewegung der Ventilnadel 10 im Druckraum 6 erfolgt durch einen wechselnden Druck im Steuerraum 26. Dazu ist in der Drosselplatte 30 eine Ablaufdrossel 41 ausgebildet, die über ein Steuerventil 32 und eine Leckölleitung 34 mit einem Kraftstoffbehälter 40 verbunden werden kann, in dem nur ein geringer Druck, vorzugsweise Umgebungsdruck, herrscht. Das Steuerventil 32 ist dabei vorzugsweise ein elektromagnetisches Ventil, das über das Anlegen eines Steuerstroms geöffnet oder geschlossen werden kann. Die Befüllung des Steuerraums 26 erfolgt über eine ebenfalls in der Drosselplatte 30 ausgebildete Zulaufdrossel 42, die über eine Hochdruckleitung 35 mit einem Hochdruckspeicher 36 verbunden ist. Der Hochdruckspeicher 36 beinhaltet Kraftstoff unter hohem Druck, mit dem der Kraftstoff letztendlich in den Brennraum eingebracht werden soll, und wird seinerseits aus dem Kraftstoffbehälter 40 über eine Hochdruckpumpe 37 mit verdichtetem Kraftstoff versorgt. Mit dem Hochdruckspeicher 36 können mehrere Einspritzventile 1 verbunden sein, die jeweils über Hochdruckleitungen 35 mit dem Hochdruckspeicher 36 verbunden sind. The control of the longitudinal movement of the valve needle 10 in the pressure chamber 6 is effected by an alternating pressure in the control chamber 26. For this purpose, a flow restrictor 41 is formed in the throttle plate 30, which can be connected via a control valve 32 and a drain line 34 to a fuel tank 40 in which only a low pressure, preferably ambient pressure, prevails. The control valve 32 is preferably an electromagnetic valve that can be opened or closed by applying a control current. The filling of the control chamber 26 via a likewise formed in the throttle plate 30 inlet throttle 42, which is connected via a high pressure line 35 to a high pressure accumulator 36. The high-pressure accumulator 36 contains fuel under high pressure, with which the fuel is ultimately to be introduced into the combustion chamber, and in turn is supplied from the fuel tank 40 via a high-pressure pump 37 with compressed fuel. With the high-pressure accumulator 36 a plurality of injectors 1 may be connected, which are each connected via high-pressure lines 35 to the high-pressure accumulator 36.
In geschlossenem Zustand des Kraftstoffeinspritzventils 1 wird die Ventilnadel 10 durch den Druck im Steuerraum 26 und die dadurch bedingte hydraulische Kraft in Richtung des Ventilsitzes 12 gedrückt. Die Feder 25 drückt zwar die Ventilnadel 10 ebenfalls in Richtung des Ventilsitzes 12, jedoch spielt diese Kraft im Verhältnis zu den großen hydraulischen Kräften nur eine untergeordnete Rolle. Da die Ventilnadel 10 mit ihrer Dichtfläche 11 auf dem Ventilsitz 12 aufliegt, werden Teile der Ventildichtfläche nicht vom Druck des Druckraums 6 beaufschlagt, so dass sich ein Kraftüberschuss in Richtung des Ventilsitzes 12 ergibt, der durch die hydraulischen Kräfte bedingt ist. Das Steuerventil 32 befindet sich dabei in seiner Schließstellung, so dass die Leckölleitung 34 unterbrochen ist. In the closed state of the fuel injection valve 1, the valve needle 10 is pressed by the pressure in the control chamber 26 and the consequent hydraulic force in the direction of the valve seat 12. Although the spring 25 presses the valve needle 10 also in the direction of the valve seat 12, but this force plays only a minor role in relation to the large hydraulic forces. Since the valve needle 10 rests with its sealing surface 11 on the valve seat 12, parts of the valve sealing surface are not acted upon by the pressure of the pressure chamber 6, so that there is an excess of force in the direction of the valve seat 12, which is due to the hydraulic forces. The control valve 32 is in its closed position, so that the drain line 34 is interrupted.
Um die Ventilnadel 10 im Druckraum 6 zu bewegen, wird das Steuerventil 32 geöffnet, so dass der Steuerraum 26 über die Ablaufdrossel 41 und die Leckölleitung 34 mit dem Kraftstoffbehälter 40 verbunden wird. Dadurch sinkt der Druck im Steuerraum 26 ab, wobei die Ablaufdrossel 41 und die Zulaufdrossel 42 so dimensioniert sind, dass bei geöffnetem Steuerventil 32 mehr Kraftstoff aus dem Steuerraum 26 abfließt, als über die Zulaufdrossel 42 im selben Zeitraum zufließt. Durch die hydraulischen Kräfte auf der Ventilnadel 10, insbesondere innerhalb des Ventilkörpers 5, ergibt sich jetzt eine resultierende Kraft auf die Ventilnadel 10, die vom Ventilsitz 12 weggerichtet ist und die Ventilnadel 10 in ihre Öffnungsstellung verbringt. Die Ventilnadel 10 hebt vom Ventilsitz 12 ab und gibt die Einspritzöffnungen 8 frei, so dass Kraftstoff aus dem Druckraum 6 über die Einspritzöffnungen 8 ausgespritzt wird. Zur Beendigung der Einspritzung wird das Steuerventil 32 wieder geschlossen, und es stellt sich im Steuerraum 26 erneut ein hoher Kraftstoffdruck ein, der die Ventilnadel 10 mit einer Schließkraft in Richtung des Ventilsitzes 12 beaufschlagt und zurück in ihre Schließstellung drückt. To move the valve needle 10 in the pressure chamber 6, the control valve 32 is opened, so that the control chamber 26 via the outlet throttle 41 and the Leakage oil line 34 is connected to the fuel tank 40. As a result, the pressure in the control chamber 26 decreases, wherein the outlet throttle 41 and the inlet throttle 42 are dimensioned so that when the control valve 32 is open, more fuel flows out of the control chamber 26 than flows through the inlet throttle 42 in the same period. Due to the hydraulic forces on the valve needle 10, in particular within the valve body 5, now results in a resultant force on the valve needle 10, which is directed away from the valve seat 12 and the valve needle 10 spends in its open position. The valve needle 10 lifts off from the valve seat 12 and releases the injection openings 8, so that fuel is ejected from the pressure chamber 6 via the injection openings 8. To end the injection, the control valve 32 is closed again, and it turns in the control chamber 26 again a high fuel pressure, which urges the valve needle 10 with a closing force in the direction of the valve seat 12 and pushes back into its closed position.
Die Ventilnadel 10 ist so ausgebildet, dass sie im geöffneten Zustand und dann, wenn der Steuerraum 26 wieder mit Kraftstoff unter hohem Druck geflutet wird, im Wesentlichen kraftausgeglichen ist, d. h. die hydraulischen Kräfte heben sich in Längsrichtung weitgehend gegeneinander auf. Da die Schließkraft, die die Feder 25 auf die Ventilnadel 10 ausübt, allein zu einem schnellen Schließen nicht ausreicht, muss das Schließen der Ventilnadel 10 hydraulisch unterstützt werden, da ein zu langsames Nadelschließen zu erhöhten Schadstoffemissionen führt. Dazu muss eine Druckdifferenz zwischen den Bereichen des Druckraums stromaufwärts und stromabwärts des Führungsabschnitts 14 erreicht werden, da dann die Öffnungskraft auf die Ventilnadel 10 durch den Kraftstoffdruck im Ventilkörper 5 geringer ist als die Schließkraft, die durch die hydraulische Kraft innerhalb des Steuerraums 26 auf der Ventilnadel 10 ausgeübt wird. The valve needle 10 is configured to be substantially force balanced in the open state and when the control space 26 is again flooded with fuel at high pressure, i. H. The hydraulic forces cancel each other in the longitudinal direction largely against each other. Since the closing force exerted by the spring 25 on the valve needle 10 is not sufficient for a quick closing alone, the closing of the valve needle 10 must be hydraulically assisted, as too slow needle closing leads to increased pollutant emissions. For this purpose, a pressure difference between the areas of the pressure chamber upstream and downstream of the guide portion 14 must be achieved because then the opening force on the valve needle 10 by the fuel pressure in the valve body 5 is lower than the closing force, by the hydraulic force within the control chamber 26 on the valve needle 10 is exercised.
Der Kraftstoff fließt zu den Einspritzöffnungen 8 durch die Längsbohrung 15 innerhalb der Ventilnadel 10, indem er durch Drosselbohrungen 20 aus dem Druckraum 6 in die Längsbohrung 15 eintritt. Durch die Drosselbohrungen 20, deren Anzahl und Durchmesser so bemessen ist, dass bei geöffnetem Kraftstoffeinspritzventil eine Druckminderungen an diesen Drosselbohrungen 20 stattfindet, wird eine solche Druckdifferenz erreicht. Dadurch ist der Druck in der Längs- bohrung und in der Folge über die Verbindung 17 auch im stromabwärtigen Teil des Druckraums 16 geringer als im stromaufwärts des Führungsabschnitts 14 gelegenen Bereich des Druckraums 6. The fuel flows to the injection openings 8 through the longitudinal bore 15 within the valve needle 10 by entering through the throttle bores 20 from the pressure chamber 6 in the longitudinal bore 15. Through the throttle bores 20, whose number and diameter is so dimensioned that with the fuel injection valve open a pressure reduction takes place at these throttle bores 20, such a pressure difference is achieved. As a result, the pressure in the longitudinal bore and subsequently via the connection 17 in the downstream part of the pressure chamber 16 less than in the upstream of the guide portion 14 located region of the pressure chamber 6th
Die Verbindung der Längsbohrung 15 mit dem Druckraum 6 erfolgt stromaufwärts des Führungsabschnitts 14 über die Drosselbohrungen 20, wie in Figur 1 dargestellt. Die stromabwärts des Führungsabschnitts 14 gelegene Verbindung 17 erfolgt beispielsweise durch eine Schrägbohrung innerhalb der Ventilnadel 10. Es können auch mehrere Schrägbohrungen vorgesehen sein, die die Verbindung sicherstellen. The connection of the longitudinal bore 15 with the pressure chamber 6 takes place upstream of the guide portion 14 via the throttle bores 20, as shown in Figure 1. The connection 17 located downstream of the guide section 14 takes place, for example, through an oblique bore within the valve needle 10. It is also possible to provide a plurality of inclined bores which ensure the connection.
In Figur 2 ist ein weiteres Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt, wobei hier nur der Ventilkörper 5 zusammen mit der Ventilnadel 10 dargestellt ist. Die Ventilnadel 10 weist auch hier eine Längsbohrung 15 auf, wobei die Verbindung mit dem Druckraum 6 stromaufwärts des Führungsabschnitts 14 durch Filterbohrungen 21 erreicht wird, die in radialer Richtung in die Ventilnadel 10 eingebracht sind. Die Filterbohrungen 21 sind dabei in Anzahl und Durchmesser so bemessen, dass an diesen Filterbohrungen 21 keine oder nur eine geringe Druckminderung stattfindet verglichen mit der Druckminderung an den Drosselbohrungen 20'. Die Filterbohrungen 21 dienen an dieser Stelle der Filterung des Kraftstoffs, d. h. dass durch die Filterbohrungen 21 Partikel im Kraftstoff, die in das Kraftstoffeinspritzventil 1 gelangt sind, herausgefiltert werden, damit diese nicht bis zu den Einspritzöffnungen 8 gelangen. Ein weiterer Vorteil besteht darin, dass die Drosselbohrungen 20' nicht mit Partikeln zugesetzt werden. Dadurch bleibt die Wirkung der Drosselbohrungen 20' während der gesamten Lebensdauer des Kraftstoffeinspritzventils erhalten. 2 shows a further embodiment of the fuel injection valve according to the invention is shown, in which case only the valve body 5 is shown together with the valve needle 10. The valve needle 10 here also has a longitudinal bore 15, wherein the connection with the pressure chamber 6 upstream of the guide section 14 is achieved by filter bores 21, which are introduced into the valve needle 10 in the radial direction. The filter bores 21 are dimensioned in number and diameter so that no or only a slight pressure reduction takes place at these filter bores 21 compared with the pressure reduction at the throttle bores 20 '. The filter bores 21 serve at this point the filtering of the fuel, d. H. in that through the filter bores 21 particles in the fuel which have entered the fuel injection valve 1 are filtered out so that they do not reach the injection openings 8. Another advantage is that the throttle bores 20 'are not added with particles. As a result, the effect of the throttle bores 20 'is maintained throughout the life of the fuel injection valve.
Die Verbindung der Längsbohrung 15 mit dem stromabwärts des Führungsabschnitts 14 gelegenen Teil des Druckraums 6 erfolgt, wie bei dem in Figur 1 gezeigten Ausführungsbeispiel, über Drosselbohrungen 20', die die gewünschte Druckdifferenz zwischen der Längsbohrung 15 und den Druckraum 6 herstellen. Bei diesem Ausführungsbeispiel herrscht also innerhalb der Längsbohrung 15 ein höherer Druck als im stromabwärts des Führungsabschnitts 14 gelegenen Teil des Druckraums 6, während bei dem in Figur 1 gezeigten Ausführungsbeispiel die Druckminderung bereits bei Eintritt des Kraftstoffs in die Längsbohrung 15 erfolgt. Es sei noch einmal darauf hingewiesen, dass diese Druckminderung nur dann stattfindet, wenn der Kraftstoffstrom tatsächlich in Bewegung ist, d.h. nur, wenn das Kraftstoffeinspritzventil geöffnet ist. In geschlossenem Zustand des Kraftstoffeinspritzventils stellt sich sehr rasch wieder ein Kraftstoffdruck ein, der innerhalb des gesamten Druckraums 6 gleich ist. The connection of the longitudinal bore 15 with the downstream of the guide portion 14 located part of the pressure chamber 6 takes place, as in the embodiment shown in Figure 1, via orifices 20 ', which produce the desired pressure difference between the longitudinal bore 15 and the pressure chamber 6. In this embodiment, therefore, there is a higher pressure within the longitudinal bore 15 than in the downstream of the guide portion 14 located part of the pressure chamber 6, while in the embodiment shown in Figure 1 the pressure reduction already takes place when the fuel enters the longitudinal bore 15. It should again be noted that this pressure reduction takes place only when the fuel flow is actually in motion, ie only when the fuel injection valve is open. When the fuel injection valve is in the closed state, a fuel pressure which is the same within the entire pressure chamber 6 returns very quickly.
Die Drosselbohrungen 20, 20' sind als radiale Bohrungen ausgeführt und können auf verschiedene Art und Weise hergestellt werden, beispielsweise durch Elektroerosion oder durch einen Laser- Bohrprozess. Der Durchmesser der Drosselbohrungen 20, 20' beträgt dabei vorzugsweise 50 bis 250 μηη, je nach Viskosität des Kraftstoffs und je nach Anzahl der Drosselbohrungen 20, 20'. Der Durchmesser der Filterbohrungen 21 ist so bemessen, dass unter Berücksichtigung der Anzahl der Filterbohrungen 21 keine oder nur eine gegenüber der Druckminderung an den Drosselbohrungen 20 geringe Druckminderung stattfindet. Der Durchmesser der Filterbohrungen 21 richtet sich nach der Größe der zu erwartenden Partikel und ist in der Größenordnung von 100 bis 300 μηη. The throttle bores 20, 20 'are designed as radial bores and can be produced in various ways, for example by electroerosion or by a laser drilling process. The diameter of the throttle bores 20, 20 'is preferably 50 to 250 μηη, depending on the viscosity of the fuel and depending on the number of throttle bores 20, 20'. The diameter of the filter bores 21 is dimensioned such that, taking into account the number of filter bores 21, there is no or only a slight pressure reduction with respect to the pressure reduction at the throttle bores 20. The diameter of the filter bores 21 depends on the size of the expected particles and is in the order of 100 to 300 μηη.

Claims

Ansprüche claims
1. Kraftstoffeinspritzventil (1) für Brennkraftmaschinen mit einem Gehäuse (2), in dem ein Druckraum (6) ausgebildet ist, von dem wenigstens eine Einspritzöffnung (8) ausgeht, und mit einer im Druckraum (6) angeordneten Ventilnadel (10), die durch ihre Längsbewegung die wenigstens eine Einspritzöffnung (8) öffnet und schließt, wobei zwischen der Ventilnadel (10) und der Wand des Druckraums (6) zumindest abschnittsweise ein Ringraum verbleibt, der mit Kraftstoff unter hohem Druck befüllbar ist und durch den Kraftstoff in Richtung der Einspritzöffnungen (8) fließen kann, und mit einem im Druckraum (6) ausgebildeten Führungsabschnitt (14), in dem die Ventilnadel (10) geführt ist, dadurch gekennzeichnet, dass die Ventilnadel (10) im Bereich des Führungsabschnitts (14) eine Längsbohrung (15) aufweist, durch die Kraftstoff von dem stromaufwärts des Führungsabschnitts (14) ausgebildeten Teil des Druckraums (6) in den stromabwärts des Führungsabschnitts (14) ausgebildeten Teil des Druckraums (6) fließen kann, wobei die Längsbohrung (15) über mehrere, in der Ventilnadel (10) ausgebildete Drosselbohrungen (20; 20') mit dem Druckraum (6) verbunden ist. 1. Fuel injection valve (1) for internal combustion engines having a housing (2) in which a pressure chamber (6) is formed, from which at least one injection opening (8) starts, and with a in the pressure chamber (6) arranged valve needle (10) by at least one injection opening (8) opens and closes by its longitudinal movement, wherein between the valve needle (10) and the wall of the pressure chamber (6) at least partially remains an annular space which can be filled with fuel under high pressure and by the fuel in the direction of Injection openings (8) can flow, and with a in the pressure chamber (6) formed guide portion (14) in which the valve needle (10) is guided, characterized in that the valve needle (10) in the region of the guide portion (14) has a longitudinal bore ( 15), formed by the fuel from the upstream of the guide portion (14) formed part of the pressure chamber (6) in the downstream of the guide portion (14) formed Tei l of the pressure chamber (6) can flow, wherein the longitudinal bore (15) via a plurality, in the valve needle (10) formed throttle bores (20; 20 ') is connected to the pressure chamber (6).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Drosselbohrungen (20') stromabwärts des Führungsabschnitts (14) ausgebildet sind und dass stromaufwärts des Führungsabschnitts (14) eine weitere Verbindung (17) zwischen der Längsbohrung (15) und dem Druckraum (6) in der Ventilnadel (10) ausgebildet ist. 2. Fuel injection valve according to claim 1, characterized in that the throttle bores (20 ') downstream of the guide portion (14) are formed and that upstream of the guide portion (14) has a further connection (17) between the longitudinal bore (15) and the pressure chamber (6 ) is formed in the valve needle (10).
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass die weitere Verbindung (17) durch mehrere, in der Ventilnadel (10) ausgebildete Filterbohrungen (21) gebildet ist. 3. Fuel injection valve according to claim 2, characterized in that the further connection (17) by a plurality, in the valve needle (10) formed filter bores (21) is formed.
4. Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, dass die Filterbohrungen (21) eine solche Anzahl und einen solchen Durchmesser aufweisen, dass der Kraftstoffstrom vom Druckraum (6) in die Längsbohrung (15) durch die Filterbohrungen (21) nicht oder nur unwesentlich gedrosselt wird. 4. Fuel injection valve according to claim 3, characterized in that the filter bores (21) such a number and such a diameter have that the fuel flow from the pressure chamber (6) in the longitudinal bore (15) through the filter bores (21) is not or only slightly throttled.
5. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Drosselbohrungen (20; 20') einen bestimmten Druckabfall zwischen der Längsbohrung (15) und dem stromabwärts des Führungsabschnitts (14) gelegenen Teil des Druckraums (6) bewirken, wenn eine Einspritzung von Kraftstoff durch das Kraftstoffeinspritzventil (1) geschieht. 5. Fuel injection valve according to claim 1, characterized in that the throttle bores (20, 20 ') cause a certain pressure drop between the longitudinal bore (15) and the downstream of the guide portion (14) located part of the pressure chamber (6), when an injection of fuel happens through the fuel injection valve (1).
6. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Drosselbohrungen (20; 20') als radial verlaufende Bohrungen ausgebildet sind. 6. Fuel injection valve according to claim 1, characterized in that the throttle bores (20; 20 ') are designed as radially extending bores.
7. Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, dass die Drosselbohrungen (20; 20') einen Durchmesser von 50 bis 250 μηη aufweisen. 7. Fuel injection valve according to claim 6, characterized in that the throttle bores (20, 20 ') have a diameter of 50 to 250 μηη.
8. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Ventilnadel (10) aus wenigstens zwei Teilventilnadeln (110; 210) besteht, die im Bereich der Längsbohrung (15) miteinander verbunden sind. 8. Fuel injection valve according to claim 1, characterized in that the valve needle (10) consists of at least two partial valve needles (110, 210), which are connected to each other in the region of the longitudinal bore (15).
9. Kraftstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, dass die Längsbohrung durch zwei in den jeweiligen Teilventilnadeln (110; 210) ausgebildete Sackbohrungen gebildet ist. 9. Fuel injection valve according to claim 8, characterized in that the longitudinal bore is formed by two in the respective part valve needles (110, 210) formed blind holes.
10. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass der den Einspritzöffnungen abgewandte Ende der Ventilnadel (10) einen Steuerraum begrenzt, in dem ein wechselnder Kraftstoffdruck einstellbar ist. 10. Fuel injection valve according to claim 1, characterized in that the injection openings facing away from the end of the valve needle (10) delimits a control space in which an alternating fuel pressure is adjustable.
11. Kraftstoffeinspritzventil nach Anspruch 9, dadurch gekennzeichnet, dass die in Längsrichtung von den Einspritzöffnungen (8) weg gerichteten hydraulischen Kräfte auf die Ventilnadel (10) 11. Fuel injection valve according to claim 9, characterized in that in the longitudinal direction of the injection openings (8) directed away from the hydraulic forces on the valve needle (10)
EP13724791.2A 2012-06-27 2013-05-16 Fuel-injection valve for internal combustion engines Not-in-force EP2867518B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210210955 DE102012210955A1 (en) 2012-06-27 2012-06-27 Fuel injection valve for internal combustion engines
PCT/EP2013/060195 WO2014000966A1 (en) 2012-06-27 2013-05-16 Fuel-injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP2867518A1 true EP2867518A1 (en) 2015-05-06
EP2867518B1 EP2867518B1 (en) 2019-05-01

Family

ID=48485155

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13724791.2A Not-in-force EP2867518B1 (en) 2012-06-27 2013-05-16 Fuel-injection valve for internal combustion engines

Country Status (3)

Country Link
EP (1) EP2867518B1 (en)
DE (1) DE102012210955A1 (en)
WO (1) WO2014000966A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016216451A1 (en) 2016-08-31 2018-03-01 Robert Bosch Gmbh Nozzle assembly for a fuel injector and fuel injector

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3624476A1 (en) 1986-07-19 1988-01-28 Bosch Gmbh Robert INJECTION VALVE
DE10259799A1 (en) * 2002-12-19 2004-07-29 Robert Bosch Gmbh Fuel injector
US7334741B2 (en) * 2005-01-28 2008-02-26 Cummins Inc. Fuel injector with injection rate control
DE102006041071A1 (en) * 2006-09-01 2008-03-06 Robert Bosch Gmbh Injector for injecting fuel into cylinder combustion chambers of internal combustion engines; in particular common rail injector
DE102007032741A1 (en) 2007-07-13 2009-01-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014000966A1 *

Also Published As

Publication number Publication date
WO2014000966A1 (en) 2014-01-03
DE102012210955A1 (en) 2014-01-02
EP2867518B1 (en) 2019-05-01

Similar Documents

Publication Publication Date Title
EP2171255B1 (en) Throttle on a valve needle of a fuel injection valve for internal combustion engines
DE60017643T2 (en) Fuel injector
EP3353413B1 (en) Device for metering fuel
EP0657643A2 (en) Fuel injection device for internal combustion engines
DE102009000181A1 (en) Fuel injector
WO2004085832A1 (en) Fuel injection valve for internal combustion engines
EP2867518B1 (en) Fuel-injection valve for internal combustion engines
EP1311755A1 (en) Fuel injection device
DE102004041172B3 (en) Fuel injection valve for internal combustion engines has servo valve, body and inner and outer nozzle needles constructed so that depending upon position of outer piston of servo valve the position of outer nozzle needle is adjustable
WO2007014734A1 (en) Fuel injection system for an internal combustion engine
EP2867519B1 (en) Fuel-injection valve for internal combustion engines
EP1658427A1 (en) Fuel injection valve for internal combustion engines
DE10019153A1 (en) Fuel injection valve for IC engines has valve bore with valve member and valve piston loaded by hydraulic closing force to engage on valve member
EP2798192B1 (en) Fuel injector for combustion engine
DE10357873A1 (en) Injector
DE102015220375A1 (en) fuel injector
DE60116173T2 (en) Fuel system
WO2007059906A1 (en) Injector
DE102006050033A1 (en) Injector, in particular common rail injector
WO2005045233A1 (en) Fuel injection valve for internal combustion engines
DE10355024A1 (en) Fuel injector for IC engine has two sets of outlet holes for a two stage injection to cover a wide range of torque requirements
DE10104618A1 (en) Valve for controlling liquids
WO2003040544A1 (en) Control module for a tank injection system injector
DE102009039609A1 (en) Injector assembly for fuel injection valve of diesel engine of motor vehicle, has throttle element located in channel at lower pressure in switching position with throttle resistance, which differs from another throttle resistance
WO2004111430A1 (en) Injector for internal combustion engines

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: 20150127

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

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20170209

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20181219

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1127252

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190515

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013012750

Country of ref document: DE

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: NL

Ref legal event code: MP

Effective date: 20190501

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: 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: 20190501

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: 20190501

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: 20190501

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: 20190801

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: 20190501

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: 20190901

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: 20190501

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: 20190501

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: 20190501

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

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: 20190801

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: 20190501

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: 20190501

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: 20190802

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20190901

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: 20190501

Ref country code: CH

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

Effective date: 20190531

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: 20190501

Ref country code: LI

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

Effective date: 20190531

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: 20190501

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: 20190501

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: 20190501

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: 20190501

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013012750

Country of ref document: DE

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190531

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

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: 20190501

Ref country code: LU

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

Effective date: 20190516

Ref country code: IT

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: 20190501

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: 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: 20190501

26N No opposition filed

Effective date: 20200204

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

Effective date: 20190801

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

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: 20190501

Ref country code: IE

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

Effective date: 20190516

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: 20190501

Ref country code: BE

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

Effective date: 20190531

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

Ref country code: FR

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

Effective date: 20190701

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1127252

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190516

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

Ref country code: GB

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

Effective date: 20190801

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

Ref country code: DE

Payment date: 20200728

Year of fee payment: 8

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: 20190516

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: 20190501

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: 20190501

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: 20130516

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502013012750

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: 20211201

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

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: 20190501