EP1619362B1 - Valve train for an internal combustion engine - Google Patents
Valve train for an internal combustion engine Download PDFInfo
- Publication number
- EP1619362B1 EP1619362B1 EP05014341A EP05014341A EP1619362B1 EP 1619362 B1 EP1619362 B1 EP 1619362B1 EP 05014341 A EP05014341 A EP 05014341A EP 05014341 A EP05014341 A EP 05014341A EP 1619362 B1 EP1619362 B1 EP 1619362B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- transmission element
- cam
- valve
- torsion spring
- pivoted lever
- 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.)
- Expired - Fee Related
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0005—Deactivating valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
- F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
- F01L2001/467—Lost motion springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
- F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- the present invention relates to a valve train of an internal combustion engine according to the preamble of claim 1.
- valve train for an internal combustion engine has a rotatable drive shaft with at least one cam and an actuatable pivot lever, which is operatively connected to a, a shaft of a gas exchange valve acting second transmission element such that a displacement of the pivot lever along a cam formed between the pivot lever and the second transmission element leads to a change in the lifting height of the acted gas exchange valve.
- the displacement of the pivot lever by means of a rotation of a shaft and / or the operation of an actuator, wherein an elastic member acts on the pivot lever for contact with the cam.
- the elastic member is arranged such that the biasing force generated by the elastic member is independent of the displacement of the pivot lever relative to the second transmission member, and that the elastic member is rotatably disposed on the drive shaft relative thereto.
- the elastic member is arranged by means of a rotatable relative to the drive shaft holder on the drive shaft to which a rolling body is rotatably mounted, which is in rolling contact with the cam.
- Object of the present invention is to provide a measure that compensate depending on the position of the actuator, the induced over the eccentric displacement.
- the invention now provides a valve drive with the features in the characterizing part of claim 1 to solve this problem.
- the invention provides a valve train of an internal combustion engine, wherein the valve drive has a rotatable drive shaft having at least one cam and a first transmission element operable therewith, a pivot lever, which is in operative connection with a second transmission element such that this can act on a shaft of a gas exchange valve namely, such that a displacement of the first transmission element along a control curve formed between the first and the second transmission element leads to a change in the lift height of the gas exchange valve acted upon and the displacement of the first transmission element by means of a rotation of a shaft and / or the actuation of an actuator and takes place elastic member acts on the first transmission element for contact with the cam and this elastic member is arranged such that the biasing force generated by the elastic member of the publisher tion of the first transmission element relative to the second transmission element is independent.
- the invention thus provides a variable-stroke valve drive, in which the valve lift in a wide range between a full load position with maximum valve lift and a Leerlaufgaswolf with minimal valve lift or a Zylinderabschalt ein can be changed with Nullventilhub and thereby the first cam follower element forming the first transmission element is acted upon by an elastic member against the cam for contact therewith, that the biasing force generated by the elastic member of the for effecting the change of the stroke of Gas exchange valve necessary displacement of the first transmission element relative to the second transmission element is independent.
- the elastic member is rotatably mounted on the drive shaft relative thereto and that this can be achieved by means of a rotatably mounted on the drive shaft holder which receives and holds the elastic member.
- the first transmission element is a pivot lever, on which a rolling body is rotatably mounted, which is connected to the cam of the rotatable drive shaft is in rolling engagement.
- a displacement of the pivot lever on the rolling elements of the second transmission element along the control curve can take place by a predetermined distance, which can be superimposed additively the displacement induced by the eccentric shaft.
- the elastic member may be a torsion spring which is received by the holder rotatably mounted on the drive shaft and having a spring arm, which in a bore engages the pivot lever and thus keeps the rolling elements on the pivot lever in contact with the cam.
- the arranged between the drive shaft and the pivot lever torsion spring is tensioned, so that the torsion spring ensures that after the turning away of the cam lobe profile from the contact with the rolling elements of the rolling elements against the cam base circle is pressed and thus the rolling element remains in contact with the cam.
- control cam is formed on the pivot lever and has a Nullhubkurve and has a Hubrampenab mustard and the pivoting lever thus formed along the control cam on a second transmission element rotatably arranged rolling elements is displaced.
- this means that the pivoting lever can be displaced along the control cam on the rolling body of the second transmission element, so that the contact point between the pivoting lever or the control cam formed on the pivot lever and the rolling element is in the region between the zero-stroke curve and the lifting ramp section so that, when the contact point is in the zero-stroke curve, a cylinder-selective valve deactivation and thereby cylinder deactivation can be realized, and when the contact point is in the range of the lift ramp portion of the control cam, a change in the lift of the gas exchange valve can be realized, as appropriate the position of the contact point along the Hubrampenabites or its geometric design.
- the shaft for displacing the first transmission element relative to the second Consequentlysüngselement is an eccentric shaft and displacement of the pivot lever on the rolling elements of the second transmission element along the control cam by a predetermined distance is possible by means of a rotation of the eccentric shaft.
- a rotation of the eccentric shaft for example, a cylinder bank selective Basic tuning of the lifting height of the gas exchange valve of this cylinder bank can be achieved.
- the above-mentioned holder is made of a plastic material, on which the torsion spring can be releasably fixed, for example by means of a latching connection.
- FIG. 1 The drawing now shows a valve train 1 according to an embodiment of the present invention in a schematic view for ease of understanding in a plan view.
- the valve drive 1 has a drive shaft 2, which is rotated by the base engine, not shown, via a drive in the form of a chain or a toothed belt or the like in rotation.
- the drive shaft 2 is shown with only one cam 3, but may be the drive shaft with cams of a multi-cylinder internal combustion engine, so that it is readily apparent that the drive shaft 2 may have a plurality of cams 3.
- the valve drive 1 shown can thus serve for the inlet control of a multi-cylinder multi-valve internal combustion engine.
- the cam 3 now follows a cam follower component or first transmission element 4 in the form of a pivoting lever.
- a rolling element 5 is rotatably arranged in the form of a roller on the pivot lever 4, so that it comes between the cam 3 and the roller 5 to a rolling operation.
- the pivot lever 4 has in the region of the bearing of the roller 5 a bore or receptacle 6, in which a spring arm 7 of a torsion spring 8 engages.
- the torsion spring 8 is received in a made of a plastic material holder 9, wherein for receiving the torsion spring 8, the holder 9 is formed in two parts and by latching the two housing halves of the holder 9, the torsion spring 8 is fixed in the holder 9.
- the thus created unit of torsion spring 8 and holder 9 can now be rotatably mounted on a bearing portion of the drive shaft or camshaft 2.
- the pivot lever 4 can by means of a rotation of an eccentric shaft 10 by 180 degrees from the in Fig. 1 and 2 the drawing shown full load basic position of the valve train in an in Fig. 3 to 6 illustrated idle basic position are shifted, with the in Fig. 1 and 2 the drawing shown full load position of the in Fig. 3 and 4 illustrated idle position in particular differs in that the point of contact between a control arm formed on the pivot lever 4 and arranged on a second transmission element 12 roller 13 from the designated HR ramp portion of the control cam 11 migrates to the NH designated Nullhubabmale the cam 11.
- the second transmission element 12 in the form of a finger lever can press on a valve stem 15 for actuation of a gas exchange valve 14 and is supported at its end 16 opposite the valve stem 15 at, for example, a hydraulically operating valve clearance compensation element 17.
- the gas exchange valve 14 is axially guided with its valve stem 15 in a valve stem guide 18 which may be pressed into a cylinder head, not shown, and is kept closed in an unopened state by means of a coil spring 19, so that the valve disc 20 against a in the cylinder head of Internal combustion engine arranged valve seat presses.
- the holder 9 is rotatably mounted at a bearing point of the drive shaft or camshaft 2, so that a rotation of the camshaft 2 does not lead to a deflection of the spring arm 7 with respect to the center axis 21 of the torsion spring 8, as long as the cam 3 rolls with its base circle on the roller 5. Since the torsion spring 8 in the in Fig. 1 shown basic position exerts a biasing force, the roller 5 is pressed by this biasing force to the cam 3.
- FIG. 3 The drawing shows the valve gear 1 in the neutral position corresponding to a basic position with the torsion spring 8 in the basic position.
- the eccentric shaft 10 has been rotated by 180 degrees, which leads to a displacement of the pivot lever 4 along the control cam 11 in the designated zero NH range.
- the included between the center axis 21 and along the center axis of the spring arm 7 reference axis 23 included angle ⁇ has not changed by the displacement of the pivot lever 4 along the control cam 11 in the region of the zero stroke section of the control cam 11.
- the base of the torsion spring 8 corresponding biasing force is maintained, so that no change in the friction conditions in the valve train 1 has resulted from the displacement of the pivot lever 4.
- Fig. 4 The drawing now shows a similar presentation Fig. 3 with rotated cam, so that the gas exchange valve 14 performs a valve lift, which is sufficient for maintaining the idling speed of the internal combustion engine.
- the valve lift of the gas exchange valve in the full load position is 12 mm, for example, the valve lift in the idling position may be reduced to a value of, for example, 1.5 mm.
- the biasing force generated in the deflected by the rotation of the cam 3 and tensioned position of the torsion spring 8 corresponds to the biasing force of the torsion spring 8 in the Fig. 2 illustrated deflected position in full load operation.
- FIG. 5 shows the valve train 1 in a position to provide selective cylinder deactivation.
- This position was realized by a further displacement of the pivot lever 4 along the zero lift curve NH of the control cam 11 by means of the application of a piston / cylinder unit 24 with, for example, pressure oil from the engine lubricating oil circuit.
- the application of the piston / cylinder unit 24 now leads to a displacement caused by the displacement of the pivoting lever 4 due to the rotation of the eccentric shaft 10, which is additively superimposed on a further displacement of the pivot lever 4 brought about by the piston / cylinder unit 24 such that the point of contact between the Control cam 11 and the roller 13 has been moved to the end of the zero lift NH.
- the valve train 1 in which the biasing force of the torsion spring 8 in the unactuated initial position of the biasing force of the torsion spring 8 in the unactuated basic position in the full load position of the valve train 1 and in the idle position of the valve train 1 corresponds (the angle ⁇ has not changed) , performs a rotation of the cam 3 (see Fig. 6 the drawing) to a rolling of the contact point between the roller 13 and the cam 11 in the zero lift curve NH, so that it no longer comes to an opening of the valve stem 15 by the cam follower 12, the gas exchange valve 14 remains closed, the associated cylinder of the engine is excluded from the gas exchange process, the cylinder is selectively switched off.
- actuated by the cam 3 position and thus deflected and cocked position of the torsion spring 8 corresponds to the biasing force generated by the torsion spring 8 of those of the torsion spring 8 in the tensioned state in idle position of the valve gear 1 and in the tensioned state in full load position of the valve train. 1 is produced.
- the biasing force of the torsion spring 8 changes in each of the cam 3 not actuated basic position or actuated by the cam 3 deflected biased position not in response to the displacement of the pivot lever 4 and thus not in response to the desired or realized valve lift ,
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
Die vorliegende Erfindung betrifft einen Ventiltrieb einer Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The present invention relates to a valve train of an internal combustion engine according to the preamble of
Beispielsweise aus der
Die gleiche Kinematik für einen Ventiltrieb einer Brennkraftmaschine ist auch aus dem Dokument
Nachteilig an der bekannten Kinematik ist die je nach Stellung des Stellantriebs die über die Exzenterwelle herbeigeführte Verlagerung des Schwenkhebels.A disadvantage of the known kinematics, depending on the position of the actuator, brought about via the eccentric shaft displacement of the pivot lever.
Aufgabe der vorliegenden Erfindung ist es, eine Maßnahme aufzuzeigen, die je nach Stellung des Stellantriebs die über die Exzenterwelle herbeigeführte Verlagerung zu kompensieren.Object of the present invention is to provide a measure that compensate depending on the position of the actuator, the induced over the eccentric displacement.
Die Erfindung schafft nunmehr zur Lösung dieser Aufgabe einen Ventiltrieb mit den Merkmalen im kennzeichnenden Teil des Anspruchs 1.The invention now provides a valve drive with the features in the characterizing part of
Die Erfindung sieht einen Ventiltrieb einer Brennkraftmaschine vor, wobei der Ventiltrieb eine drehbare Antriebswelle besitzt mit wenigstens einer Nocke und ein damit betätigbares erstes Übertragungselement, einen Schwenkhebel, aufweist, welches mit einem zweiten Übertragungselement in Wirkverbindung steht derart, dass dieses einen Schaft eines Gaswechselventils beaufschlagen kann nämlich derart, dass eine Verlagerung des ersten Übertragungselements entlang einer zwischen dem ersten und dem zweiten Übertragungselement ausgebildeten Steuerkurve zu einer Veränderung der Hubhöhe des beaufschlagten Gaswechselventils führt und die Verlagerung des ersten Übertragungselements mittels einer Verdrehung einer Welle und/oder der Betätigung eines Stellantriebs erfolgt und ein elastisches Bauteil das erste Übertragungselement zum Kontakt mit der Nocke beaufschlägt und dieses elastische Bauteil derart angeordnet ist, dass die vom elastischen Bauteil erzeugte Vorspannkraft von der Verlagerung des ersten Übertragungselements relativ zu zweiten Übertragungselement unabhängig ist.The invention provides a valve train of an internal combustion engine, wherein the valve drive has a rotatable drive shaft having at least one cam and a first transmission element operable therewith, a pivot lever, which is in operative connection with a second transmission element such that this can act on a shaft of a gas exchange valve namely, such that a displacement of the first transmission element along a control curve formed between the first and the second transmission element leads to a change in the lift height of the gas exchange valve acted upon and the displacement of the first transmission element by means of a rotation of a shaft and / or the actuation of an actuator and takes place elastic member acts on the first transmission element for contact with the cam and this elastic member is arranged such that the biasing force generated by the elastic member of the publisher tion of the first transmission element relative to the second transmission element is independent.
Die Erfindung schafft damit einen hubvariablen Ventiltrieb, bei dem die Ventilhubhöhe in einem weiten Bereich zwischen einer Volllaststellung mit maximalem Ventilhub und einer Leerlaufgasstellung mit minimalem Ventilhub bzw. einer Zylinderabschaltstellung mit Nullventilhub verändert werden kann und dabei das das erste Nockenfolgeelement bildende erste Übertragungselement von einem elastischen Bauteil so gegen die Nocke zum Kontakt mit dieser beaufschlagt wird, dass die von dem elastischen Bauteil erzeugte Vorspannkraft von der zur Herbeiführung der Veränderung des Hubs des Gaswechselventils notwendigen Verlagerung des ersten Übertragungselements relativ zum zweiten Übertragungselement unabhängig ist.The invention thus provides a variable-stroke valve drive, in which the valve lift in a wide range between a full load position with maximum valve lift and a Leerlaufgasstellung with minimal valve lift or a Zylinderabschaltstellung can be changed with Nullventilhub and thereby the first cam follower element forming the first transmission element is acted upon by an elastic member against the cam for contact therewith, that the biasing force generated by the elastic member of the for effecting the change of the stroke of Gas exchange valve necessary displacement of the first transmission element relative to the second transmission element is independent.
Damit wird in vorteilhafter Weise erreicht, dass unabhängig von der Stellung des ersten Übertragungselements relativ zum zweiten Übertragungselement die vom elastischen Bauteil erzeugte Vorspannkraft aufgetragen über dem Nockenwinkel gleiche Werte einnimmt und nicht durch eine Relativbewegung des ersten bertragungselements relativ zum zweiten Übertragungselement verändert wird, so dass bei vergleichbaren Nockenwinkeln eine gleiche Vorspannkraft und damit Flächenpressung zwischen der Nocke und dem ersten Übertragungselement als Nockenfolgebauteil besteht, ohne dass hierbei durch eine Verlagerung des ersten Übertragungselements relativ zum zweiten Übertragungselement eine Abhängigkeit in den Verlauf der Vorspannkraft eingeführt wird. Da damit die Vorspannkraft nicht von der Verlagerung des ersten Übertragungselements relativ zum zweiten Übertragungselement abhängt, führt diese Verlagerung auch nicht zu einer verlagerungsabhängigen Reibleistung zwischen den Wälzpartnem Nocke und Nockenfolgebauteil, also dem ersten Übertragungselement.This is achieved in an advantageous manner that regardless of the position of the first transmission element relative to the second transmission element applied by the elastic component biasing force applied over the cam angle assumes the same values and is not changed by a relative movement of the first transmission element relative to the second transmission element, so that at Comparable cam angles a same biasing force and thus surface pressure between the cam and the first transmission element as a cam follower component, without this being introduced by a displacement of the first transmission element relative to the second transmission element, a dependence in the course of the biasing force. Since thus the biasing force does not depend on the displacement of the first transmission element relative to the second transmission element, this displacement also does not lead to a displacement-dependent friction between the Wälzpartnem cam and cam follower component, ie the first transmission element.
Weiter ist es vorgesehen, dass das elastische Bauteil an der Antriebswelle relativ zu dieser drehbar angeordnet ist und zwar kann dies mittels eines an der Antriebswelle drehbar angeordneten Halters erreicht werden, der das elastische Bauteil aufnimmt und hält.Further, it is provided that the elastic member is rotatably mounted on the drive shaft relative thereto and that this can be achieved by means of a rotatably mounted on the drive shaft holder which receives and holds the elastic member.
Weiter ist vorgesehen, dass das erste Übertragungselement ein Schwenkhebel ist, an dem ein Wälzkörper drehbar gelagert ist, der sich mit der Nocke der drehbaren Antriebswelle in Wälzeingriff befindet. Damit wird zwischen dem Wälzkörper des Schwenkhebels und der Nocke eine Rollbedingung realisiert, die positiv zum Ziel der Verringerung der Reibleistung beiträgt.It is further provided that the first transmission element is a pivot lever, on which a rolling body is rotatably mounted, which is connected to the cam of the rotatable drive shaft is in rolling engagement. Thus, a rolling condition is realized between the rolling elements of the pivot lever and the cam, which contributes positively to the goal of reducing the friction power.
Mittels einer Betätigung eines der Exzenterwelle nachgeschalteten Stellantriebs in der Form einer Kolben/Zylindereinheit kann eine Verlagerung des Schwenkhebels am Wälzkörper des zweiten Übertragungselements entlang der Steuerkurve um einen wiederum vorbestimmten Abstand erfolgen, die der mittels der Exzenterwelle herbeigeführten Verlagerung additiv überlagert werden kann. Es bedeutet dies mit anderen Worten, dass je nach Stellung des Stellantriebs die über die Exzenterwelle herbeigeführte Verlagerung beispielsweise kompensiert werden kann oder durch die Betätigung des Stellantriebs eine in Richtung der Verlagerung des Schwenkhebels am zweiten Übertragungselement mit gleichem Richtungsvorzeichen additiv überlagerte erweiterte Verlagerung des Schwenkhebels am Wälzkörper des zweiten Übertragungselements realisiert werden kann, mit der beispielsweise eine Verschiebung des Kontaktpunkt der Steuerkurve am Schwenkhebel zum Wälzkörper des zweiten Übertragungselements realisiert werden kann, bis in den Bereich der Nullhubkurve der Steuerkurve selbst und somit eine zylinderselektive Zylinderabschaltung durch den erfindungsgemäßen Ventiltrieb realisiert werden kann.By means of an actuation of an eccentric shaft downstream actuator in the form of a piston / cylinder unit, a displacement of the pivot lever on the rolling elements of the second transmission element along the control curve can take place by a predetermined distance, which can be superimposed additively the displacement induced by the eccentric shaft. In other words, this means that depending on the position of the actuator, the displacement caused by the eccentric shaft can be compensated, for example, or by the actuation of the actuator in the direction of displacement of the pivot lever on the second transmission element with the same direction additive additive superimposed extended displacement of the pivot lever on the rolling elements of the second transmission element can be realized with the example, a shift of the contact point of the control cam on the pivot lever to the rolling elements of the second transmission element can be realized in the range of Nullhubkurve the cam itself and thus a cylinder-selective cylinder shutdown by the valve gear according to the invention.
Nach einer vorteilhaften Ausgestaltung gemäss der Erfindung kann das elastische Bauteil eine Drehfeder sein, die von dem an der Antriebswelle drehbar angeordneten Halter aufgenommen ist und einen Federarm aufweist, der in eine Bohrung des Schwenkhebels eingreift und somit den Wälzkörper am Schwenkhebel in Kontakt mit der Nocke hält.According to an advantageous embodiment according to the invention, the elastic member may be a torsion spring which is received by the holder rotatably mounted on the drive shaft and having a spring arm, which in a bore engages the pivot lever and thus keeps the rolling elements on the pivot lever in contact with the cam.
Wenn nun die Nocke mit ihrem Nockenerhebungsprofil mit dem Wälzkörper in Kontakt kommt, wird die zwischen der Antriebswelle und dem Schwenkhebel angeordnete Drehfeder gespannt, so dass die Drehfeder dafür sorgt, dass nach dem Wegdrehen des Nockenerhebungsprofils aus dem Kontakt mit dem Wälzkörper der Wälzkörper gegen den Nockengrundkreis gedrückt wird und somit der Wälzkörper in Kontakt mit der Nocke verbleibt.Now, when the cam with its cam lobe profile comes into contact with the rolling element, the arranged between the drive shaft and the pivot lever torsion spring is tensioned, so that the torsion spring ensures that after the turning away of the cam lobe profile from the contact with the rolling elements of the rolling elements against the cam base circle is pressed and thus the rolling element remains in contact with the cam.
Nach einer Weiterbildung der Erfindung ist es vorgesehen, dass die vorstehend genannte Steuerkurve am Schwenkhebel ausgebildet ist und eine Nullhubkurve aufweist sowie einen Hubrampenabschnitt besitzt und der so ausgebildete Schwenkhebel entlang der Steuerkurve an einem am zweiten Übertragungselement drehbar angeordneten Wälzkörper verlagerbar ist. Es bedeutet dies mit anderen Worten, dass der Schwenkhebel entlang der Steuerkurve an dem Wälzkörper des zweiten Übertragungselements verschoben werden kann, so dass sich der Kontaktpunkt zwischen dem Schwenkhebel bzw. der am Schwenkhebel ausgebildeten Steuerkurve und dem Wälzkörper im Bereich zwischen der Nullhubkurve und dem Hubrampenabschnitt befindet, so dass dann, wenn sich der Kontaktpunkt im Bereich der Nullhubkurve befindet eine zylinderselektive Ventilabschaltung und damit Zylinderabschaltung realisiert werden kann und dann, wenn sich der Kontaktpunkt im Bereich des Hubrampenabschnitts der Steuerkurve befindet, eine Veränderung des Hubs des Gaswechselventils realisiert werden kann, je nach der Position des Kontaktpunkts entlang des Hubrampenabschnitts bzw. dessen geometrischer Ausbildung.According to a development of the invention, it is provided that the above-mentioned control cam is formed on the pivot lever and has a Nullhubkurve and has a Hubrampenabschnitt and the pivoting lever thus formed along the control cam on a second transmission element rotatably arranged rolling elements is displaced. In other words, this means that the pivoting lever can be displaced along the control cam on the rolling body of the second transmission element, so that the contact point between the pivoting lever or the control cam formed on the pivot lever and the rolling element is in the region between the zero-stroke curve and the lifting ramp section so that, when the contact point is in the zero-stroke curve, a cylinder-selective valve deactivation and thereby cylinder deactivation can be realized, and when the contact point is in the range of the lift ramp portion of the control cam, a change in the lift of the gas exchange valve can be realized, as appropriate the position of the contact point along the Hubrampenabschnitts or its geometric design.
Nach einer Weiterbildung der Erfindung ist es vorgesehen, dass die Welle zur Verlagerung des ersten Übertragungselements relativ zum zweiten Übertragüngselement eine Exzenterwelle ist und mittels einer Verdrehung der Exzenterwelle eine Verlagerung des Schwenkhebels am Wälzkörper des zweiten Übertragungselements entlang der Steuerkurve um einen vorbestimmten Abstand möglich ist. Damit kann durch eine Verdrehung der Exzenterwelle eine beispielsweise zylinderbankselektive Grundabstimmung der Hubhöhe der Gaswechselventil dieser Zylinderbank erreicht werden.According to a development of the invention, it is provided that the shaft for displacing the first transmission element relative to the second Übertragungsüngselement is an eccentric shaft and displacement of the pivot lever on the rolling elements of the second transmission element along the control cam by a predetermined distance is possible by means of a rotation of the eccentric shaft. Thus, by a rotation of the eccentric shaft, for example, a cylinder bank selective Basic tuning of the lifting height of the gas exchange valve of this cylinder bank can be achieved.
Nach einer vorteilhaften Ausführungsform ist es vorgesehen, dass der vorstehend genannte Halter aus einem Kunststoffwerkstoff gefertigt ist, an dem die Drehfeder beispielsweise mittels einer Rastverbindung lösbar festgelegt werden kann. Durch eine drehbare Anordnung des die Drehfeder haltenden Halters an der Antriebswelle wird damit erreicht, dass die Drehfeder so zwischen der Antriebswelle und dem Wälzkörper des Schwenkhebels eingespannt ist, dass die von der Drehfeder erzeugte Federkraft von einer Verlagerung des Schwenkhebels relativ zum zweiten Übertragungselement unabhängig ist.According to an advantageous embodiment, it is provided that the above-mentioned holder is made of a plastic material, on which the torsion spring can be releasably fixed, for example by means of a latching connection. By a rotatable arrangement of the torsion spring holding holder on the drive shaft is achieved so that the torsion spring is clamped between the drive shaft and the rolling elements of the pivot lever, that the spring force generated by the torsion spring is independent of a displacement of the pivot lever relative to the second transmission element.
Damit bleibt die Vorspannkraft, mit der der Wälzkörper des Schwenkhebels gegen die Nocke der Antriebswelle gedrückt wird, unabhängig von der Verlagerung des Schwenkhebels relativ zum zweiten Übertragungselement. Das geometrische Verhältnis zwischen der Mitte der Nockenwelle, einem Drehpunkt des Federarms der Drehfeder und der Mitte des Wälzkörpers des Schwenkhebels bleibt somit unabhängig von der Lage des Schwenkhebels immer gleich und damit die Vorspannkraft bzw. die zu überwindende Reibleistung.Thus, the biasing force with which the rolling elements of the pivot lever is pressed against the cam of the drive shaft, regardless of the displacement of the pivot lever relative to the second transmission element. The geometric relationship between the center of the camshaft, a pivot point of the spring arm The torsion spring and the center of the rolling element of the pivot lever thus remains independent of the position of the pivot lever always the same and thus the biasing force or to be overcome friction.
Die Erfindung wird im Folgenden anhand der Zeichnung näher erläutert. Diese zeigt in:
-
Fig. 1 einen Ventiltrieb gemäß einer Ausführungsform nach der vorliegenden Erfindung in Volllaststellung mit einer Drehfeder in Grundstellung; -
Fig. 2 eine Volllaststellung ähnlichFig. 1 mit aufgrund der Drehung der Nocke gespannter Drehfeder und betätigtem Gaswechselventil; -
Fig. 3 dem Ventiltrieb in einer Leerlaufstellung mit Drehfeder in Grundstellung und unbetätigtem Gaswechselventil; -
Fig. 4 eine Abbildung ähnlichFig. 3 mit Ventiltrieb in Leerlaufstellung mit aufgrund der Drehung der Nocke gespannter Drehfeder und betätigtem Gaswechselventil; -
Fig. 5 einen Ventiltrieb in einer Stellung zur Herbeiführung einer Zylinderabschaltung mit Drehfeder in Grundstellung; und -
Fig. 6 eine Darstellung ähnlichFig. 5 mit aufgrund der Drehung der Nocke gespannter Drehfeder und unbetätigtem Gaswechselventil.
-
Fig. 1 a valve train according to an embodiment of the present invention in full load position with a torsion spring in basic position; -
Fig. 2 a full load position similarFig. 1 with due to the rotation of the cam tensioned torsion spring and actuated gas exchange valve; -
Fig. 3 the valve gear in an idle position with torsion spring in basic position and unconfirmed gas exchange valve; -
Fig. 4 a picture similarFig. 3 with valve gear in idle position with due to the rotation of the cam tensioned torsion spring and actuated gas exchange valve; -
Fig. 5 a valvetrain in a position to bring about a cylinder deactivation with torsion spring in basic position; and -
Fig. 6 a representation similarFig. 5 with due to the rotation of the cam tensioned torsion spring and unconfirmed gas exchange valve.
Nachfolgend folgt nun zunächst eine Beschreibung des Ventiltriebs unter Bezugnahme auf
Der Ventiltrieb 1 weist eine Antriebswelle 2 auf, die vom nicht dargestellten Grundmotor über einen Antrieb in der Form einer Kette oder eines Zahnriemens oder dergleichen in Drehung versetzt wird. In den Figuren ist die Antriebswelle 2 jeweils mit nur einer Nocke 3 dargestellt, kann aber die Antriebswelle mit Nocken einer mehrzylindrigen Brennkraftmaschine sein, so dass es ohne weiteres klar ist, dass die Antriebswelle 2 eine Vielzahl von Nocken 3 besitzen kann. Der dargestellte Ventiltrieb 1 kann somit zur Einlasssteuerung einer mehrzylindrigen mehrventiligen Brennkraftmaschine dienen.The
Der Nocke 3 folgt nun ein Nockenfolgebauteil oder erstes Übertragungselement 4 in der Form eines Schwenkhebels.The
An dem der Nocke 3 zugewandten Ende des Schwenkhebels 4 ist ein Wälzkörper 5 in der Form einer Laufrolle am Schwenkhebel 4 drehbar angeordnet, so dass es zwischen der Nocke 3 und der Laufrolle 5 zu einer Rollbedienung kommt. Der Schwenkhebel 4 weist im Bereich der Lagerung der Laufrolle 5 eine Bohrung oder Aufnahme 6 auf, in die ein Federarm 7 einer Drehfeder 8 eingreift. Die Drehfeder 8 ist dabei in einem aus einem Kunststoffwerkstoff gefertigten Halter 9 aufgenommen, wobei zur Aufnahme der Drehfeder 8 der Halter 9 zweiteilig ausgebildet ist und durch miteinander Verrasten der beiden Gehäusehälften des Halters 9 die Drehfeder 8 im Halter 9 festgelegt wird. Die so geschaffene Einheit aus Drehfeder 8 und Halter 9 kann nun an einem Lagerabschnitt der Antriebswelle oder Nockenwelle 2 drehbar befestigt werden.At the
Der Schwenkhebel 4 kann mittels einer Drehung einer Exzenterwelle 10 um 180 Grad aus der in
Das zweite Übertragungselement 12 in der Form eines Schlepphebels kann zur Betätigung eines Gaswechselventils 14 auf einen Ventilschaft 15 drücken und stützt sich an seinem dem Ventilschaft 15 gegenüberliegenden Ende 16 an einem beispielsweise hydraulisch arbeitenden Ventilspielausgleichselement 17 ab.The
Das Gaswechselventil 14 wird mit seinem Ventilschaft 15 in einer Ventilschaftführung 18, die in einem nicht näher dargestellten Zylinderkopf eingepresst sein kann, axial geführt und wird in einem ungeöffneten Zustand mittels einer Schraubenfeder 19 geschlossen gehalten, so dass sich der Ventilteller 20 gegen einen im Zylinderkopf der Brennkraftmaschine angeordneten Ventilsitz drückt.The
Wie es vorstehend bereits erwähnt wurde, ist der Halter 9 an einer Lagerstelle der Antriebswelle oder Nockenwelle 2 drehbar gelagert, so dass eine Verdrehung der Nockenwelle 2 nicht zu einer Auslenkung des Federarms 7 bezogen auf die Mittenachse 21 der Drehfeder 8 führt, so lange die Nocke 3 mit ihrem Grundkreis an der Laufrolle 5 abrollt. Da die Drehfeder 8 in der in
Auch in der in
Hinsichtlich vorstehend im Einzelnen nicht näher erläuterter Merkmale der Erfindung wird im Übrigen ausdrücklich auf die Ansprüche und die Zeichnung verwiesen.With regard to features of the invention which are not explained in greater detail above, reference is expressly made to the claims and the drawings, moreover.
Bezugszeichenliste
- 1.
- Ventiltrieb
- 2.
- Antriebswelle
- 3.
- Nocke
- 4.
- Schwenkhebel
- 5.
- Laufrolle
- 6.
- Bohrung
- 7.
- Federarm
- 8.
- Drehfeder
- 9.
- Halter
- 10.
- Exzenterwelle
- 11.
- Steuerkurve
- 12.
- 2. Übertragungselement, Schlepphebel
- 13.
- Laufrolle
- 14.
- Gaswechselventil
- 15.
- Ventilschaft
- 16.
- Schlepphebelende
- 17.
- Ventilspielausgleichselement
- 18.
- Ventilschaftführung
- 19.
- Schraubenfeder
- 20.
- Ventilteller
- 21.
- Mittenachse
- 22.
- Nockenerhebungskurve
- 23.
- Bezugsachse
- 24.
- Kolben/Zylindereinheit
- 1.
- valve train
- Second
- drive shaft
- Third
- cam
- 4th
- pivoting lever
- 5th
- caster
- 6th
- drilling
- 7th
- spring arm
- 8th.
- torsion spring
- 9th
- holder
- 10th
- eccentric shaft
- 11th
- cam
- 12th
- 2. Transmission element, drag lever
- 13th
- caster
- 14th
- Gas exchange valve
- 15th
- valve stem
- 16th
- Drag lever end
- 17th
- Lash adjuster
- 18th
- Valve stem guide
- 19th
- coil spring
- 20th
- valve disc
- 21st
- mid-axis
- 22nd
- Cam elevation curve
- 23rd
- reference axis
- 24th
- Piston / cylinder unit
Claims (8)
- A valve drive of an internal combustion engine comprising a rotatable drive shaft (2) with at least one cam (3) actuating a first transmission element (4) which is in operative connection with a second transmission element acting on a shank (15) of a gas change valve (14), such that a movement of the first transmission element (4) along a radial cam (11) formed between the first (4) and the second (12) transmission element results in a change in the stroke length of the acted-upon gas change valve (14), and the first transmission element (4) is moved by rotation of a shaft (10) and/or actuation of a servomotor (24) and a resilient component (8) urges the first transmission element (4) into contact with the cam (3), wherein the resilient component (8) is disposed so that the prestress generated by the resilient component (8) is independent of the movement of the first transmission element (4) relative to the second transmission element (12), and the resilient component (8) is rotatably disposed on the drive shaft (2), wherein the resilient component (8) is disposed on the drive shaft (2) via a holder (9) rotatable relative to the drive shaft (2), and the first transmission element (4) is a pivoted lever on which a rolling member (5) is rotatably mounted and is in rolling engagement with the cam (3),
characterised in that
the servomotor (24) is a piston-cylinder unit which when actuated moves the pivoted lever (4) on the rolling member (13) of the second transmission element (12) along the radial cam (11) through a set distance, the movement being superposed on and added to the movement produced by the eccentric shaft (10). - A valve drive according to claim 1,
characterised in that the resilient component (8) is a torsion spring having an arm (7) which engages in a bore (6) in the pivoted lever (4) and holds the rolling member (5) in contact with the cam (3). - A valve drive according to claim 1 or claim 2,
characterised in that the radial cam (11) is formed on the pivoted lever (4) and has a zero-stroke cam (NH) and a stroke-slope portion (HR) and the pivoted lever (4) is movable along the radial cam (11) on a rolling member (13) rotatably disposed on the second transmission element (12). - A valve drive according to any of claims 1 to 3,
characterised in that the shaft (10) is an eccentric shaft and the rotation of the eccentric shaft (10) results in movement of the pivoted lever (4) on the rolling member (13) of the second transmission element (12) along the radial cam (11) through a set distance. - A valve drive according to any of claims 1 to 4,
characterised in that the holder (9) is preferably made of a plastics material. - A valve drive according to claim 5,
characterised in that the torsion spring (8) can be releasably fastened to the holder (9) by a catch connection. - A valve drive according to claim 5 or claim 6,
characterised in that the holder (9) and the torsion spring (8) can be rotatably and releasably fastened to the drive shaft (2). - A valve drive according to any of claims 2 to 7,
characterised in that the torsion spring (8) is clamped by the holder (9) between the drive shaft (2) and the rolling member (5) of the pivoted lever (4), such that the spring force generated by the torsion spring (8) is independent of movement of the pivoted lever (4) relative to the second transmission element (12).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004035005A DE102004035005A1 (en) | 2004-07-20 | 2004-07-20 | Valve gear of an internal combustion engine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1619362A2 EP1619362A2 (en) | 2006-01-25 |
EP1619362A3 EP1619362A3 (en) | 2010-01-27 |
EP1619362B1 true EP1619362B1 (en) | 2011-04-20 |
Family
ID=35094444
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05014341A Expired - Fee Related EP1619362B1 (en) | 2004-07-20 | 2005-07-01 | Valve train for an internal combustion engine |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1619362B1 (en) |
DE (2) | DE102004035005A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005040959A1 (en) * | 2005-08-30 | 2007-03-08 | Bayerische Motoren Werke Ag | Hubvariabler valve drive for an internal combustion engine |
DE102006013915A1 (en) * | 2006-03-25 | 2007-09-27 | Daimlerchrysler Ag | Adjustment of camshaft action on motor valves uses two setting units, in contact with control curves with two degrees of freedom with relative movements between them |
JP5436103B2 (en) * | 2009-09-03 | 2014-03-05 | 株式会社オティックス | Variable valve mechanism |
JP5294156B2 (en) * | 2009-11-12 | 2013-09-18 | スズキ株式会社 | Variable valve operating device for internal combustion engine |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2363891A1 (en) * | 1973-07-13 | 1975-06-26 | Daimler Benz Ag | Valve control system for ic engine - valve rod is controlled by action of lever on adjustable curved surface |
DE2629554A1 (en) * | 1976-07-01 | 1978-01-12 | Daimler Benz Ag | Charge regulator for mixture compression engine - has valve actuator lever moved by cam with adjustable rotation centre |
US4469056A (en) * | 1983-02-22 | 1984-09-04 | Tourtelot Jr Edward M | Dual follower variable valve timing mechanism |
DE4420064A1 (en) | 1994-06-08 | 1995-12-14 | Bayerische Motoren Werke Ag | Valve train with variable control of the valve opening angle |
US5937809A (en) | 1997-03-20 | 1999-08-17 | General Motors Corporation | Variable valve timing mechanisms |
DE19913742A1 (en) * | 1999-03-26 | 2000-09-28 | Bayerische Motoren Werke Ag | Device for stroke adjustment of a gas exchange valve in the cylinder head of an internal combustion engine |
DE10038743A1 (en) | 2000-08-09 | 2002-02-21 | Daimler Chrysler Ag | Device for igniting combustible gas mixture has frame arrangement wound with heating wire and installed in exhaust path at right angles to flow direction of exhaust gas, and has current source to supply electric current to heating wire |
DE10237104A1 (en) * | 2002-08-13 | 2004-02-26 | Bayerische Motoren Werke Ag | Valve drive for a piston combustion engine has a variable lift control with transmission and actuator elements fixed together |
US6684832B1 (en) * | 2003-04-28 | 2004-02-03 | Roberto Marcelo Codina | Oscillating camshaft controlled valve operating device |
-
2004
- 2004-07-20 DE DE102004035005A patent/DE102004035005A1/en not_active Withdrawn
-
2005
- 2005-07-01 EP EP05014341A patent/EP1619362B1/en not_active Expired - Fee Related
- 2005-07-01 DE DE502005011266T patent/DE502005011266D1/en active Active
Also Published As
Publication number | Publication date |
---|---|
DE502005011266D1 (en) | 2011-06-01 |
EP1619362A3 (en) | 2010-01-27 |
DE102004035005A1 (en) | 2006-02-16 |
EP1619362A2 (en) | 2006-01-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3170997B1 (en) | Variable valve drive with a rocker arm | |
EP2291578B1 (en) | Valve train for gas exchange valves of an internal combustion engine having double-supported cam carriers | |
DE60304621T2 (en) | Rocker arm for two-stage cam operation | |
EP0659232B1 (en) | Variable control process and device for an internal combustion engine valve | |
DE19960742B4 (en) | Variable valve train, preferably for internal combustion engines | |
DE10006018B4 (en) | Variable valve drive for load control of a spark-ignited internal combustion engine | |
DE10158703A1 (en) | rocker | |
EP0627043B1 (en) | Valve actuating mechanism for an internal combustion engine | |
DE102007051453A1 (en) | Adjustable double tappet for push rod valve gear of internal-combustion engine, has lost motion spring fixed between lower head of inner unit facing upper head and lower side of cross web of housing | |
WO2005075797A1 (en) | Drag lever for deviation switching | |
DE10228022A1 (en) | Valve lifting device for the stroke adjustment of the gas exchange valves of an internal combustion engine | |
DE102007010155A1 (en) | Camshaft for IC engine has two cam followers plus a circular cam which slides axially into the cam bearing for the non operating valve setting | |
EP0521412A1 (en) | Internal combustion engine with rocker lever valve drive | |
EP1619362B1 (en) | Valve train for an internal combustion engine | |
DE4237777A1 (en) | ||
WO1999056008A1 (en) | Support element for a cam follower of a valve gear of an internal combustion engine | |
DE102008027649A1 (en) | Valve operation for an internal combustion engine | |
EP1205643A1 (en) | Valve drive in an internal combustion engine | |
DE4411182B4 (en) | Switchable valve control for internal combustion engines | |
EP1022443B1 (en) | Variable valve drive for internal combustion engine | |
DE4334395C2 (en) | Cam switching mechanism for motors | |
WO2004067922A1 (en) | Valve control | |
DE102004040652A1 (en) | Completely-variable five-section valve gear for internal combustion engine, includes guide rocker, moving connection adjuster, control pawl and cam track | |
EP3173593B1 (en) | Variable valve drive with a rocker arm | |
DE4230809C2 (en) | Valve control 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 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA HR MK YU |
|
17P | Request for examination filed |
Effective date: 20100211 |
|
17Q | First examination report despatched |
Effective date: 20100319 |
|
AKX | Designation fees paid |
Designated state(s): DE FR GB IT |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 502005011266 Country of ref document: DE Date of ref document: 20110601 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502005011266 Country of ref document: DE Effective date: 20110601 |
|
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 |
|
26N | No opposition filed |
Effective date: 20120123 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502005011266 Country of ref document: DE Effective date: 20120123 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20170712 Year of fee payment: 13 Ref country code: GB Payment date: 20170724 Year of fee payment: 13 Ref country code: FR Payment date: 20170720 Year of fee payment: 13 Ref country code: IT Payment date: 20170721 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502005011266 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20180701 |
|
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: 20180731 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20180701 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190201 |
|
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: 20180701 |