EP1760278A2 - Lift-variable valve-operating system for internal combustion engine - Google Patents

Lift-variable valve-operating system for internal combustion engine Download PDF

Info

Publication number
EP1760278A2
EP1760278A2 EP06014987A EP06014987A EP1760278A2 EP 1760278 A2 EP1760278 A2 EP 1760278A2 EP 06014987 A EP06014987 A EP 06014987A EP 06014987 A EP06014987 A EP 06014987A EP 1760278 A2 EP1760278 A2 EP 1760278A2
Authority
EP
European Patent Office
Prior art keywords
gas exchange
curve
valve
point
adjusting device
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.)
Withdrawn
Application number
EP06014987A
Other languages
German (de)
French (fr)
Other versions
EP1760278A3 (en
Inventor
Franz Kreil
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP1760278A2 publication Critical patent/EP1760278A2/en
Publication of EP1760278A3 publication Critical patent/EP1760278A3/en
Withdrawn legal-status Critical Current

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
    • 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

Definitions

  • the invention relates to a variable-stroke valve drive for an internal combustion engine having the features of the preamble of patent claim 1.
  • valve drive device for variable stroke adjustment of a gas exchange valve of an internal combustion engine is described.
  • the gas exchange valve with the interposition of the role of a roller drag or roller rocker arm with a pivot lever in operative connection, the gas exchange valve side has a control track with a Operahubkurve and a lift curve.
  • the pivot lever On the side facing away from the gas exchange valve, the pivot lever is slidably mounted on a slide on a slide.
  • the pivoting lever is displaceable on the roller near the stage by means of an adjusting device along the slide track in order to set a valve lift.
  • the roller center of the supported on the backdrop role the backdrop is a circular path with a radius "R" to the Rotary axis of the roller of the roller drag or roller rocker arm.
  • the described valve drive device can be assigned to all cylinders (intake and / or exhaust gas changeover valves) of the same type acting all cylinders of the internal combustion engine.
  • the object is to develop a generic valve train for an internal combustion engine with a cylinder deactivation.
  • the second adjusting device may be a cam according to claim 2, wherein a previously unused curve section a Nullhubkontur having.
  • slide solutions such as linear slides, can also be realized as adjusting devices.
  • the positional shift of the intermediate lever can be represented for example hydraulically and / or electromechanically by the linear movement of a slider or actuator.
  • the embodiment according to claim 3 provides the simplest form of manufacturing a cam for a variable stroke valve drive according to the invention. Furthermore, a harmonious transition between the different operating modes, partial load full load cylinder deactivation is achieved.
  • the proposed embodiment two modes of the fully variable valve train are possible.
  • Both proposed variants each offer specific advantages. If the changeover takes place from the second curve section to the third curve section, ie at the maximum gas exchange valve lift, the internal combustion engine is temporarily throttled in this area via a separate throttle element, such as a throttle flap. This form of shutdown of individual cylinders brings particular acoustic benefits. The easier switching takes place from the first curve section to the third curve section.
  • a disadvantage of this embodiment is the short stroke transition from the partial stroke in the zero stroke, which can be realized only in a certain time window of about 300 ms. During this short period of time, the rotational speed of the internal combustion engine drops approximately to idling speed, whereby a transition to the cylinder deactivation, which is comparatively unstable for the first variant, takes place.
  • the embodiment according to claim 4 allows the optimal stroke control of the gas exchange valve.
  • the arrangement of the second adjusting devices to a common shaft according to claim 5 reduces the manufacturing cost and thus the cost of the valve gear according to the invention.
  • FIG. 1 shows a section through a variable-stroke valve drive 1 according to the invention for an internal combustion engine, with a view of a first gas exchange valve actuating unit 1 ', as can be better seen in FIG. 2, almost completely covering a second gas exchange valve actuating unit 1' according to the prior art , Structure and function are identical for both gas exchange valve actuation units 1 ', 1'bis to the inventive design.
  • Each gas exchange valve actuating unit 1 ', 1' is provided for the actuation of an equivalent gas exchange valve 6 of the internal combustion engine.
  • the arranged in a cylinder head 11 stroke variable valve train 1 consists essentially of an intermediate lever 2, which is on the one hand with a roller slidably mounted on a slide track 3 'a link 3 and on the other hand has a working curve 4, in a Sectionhubkurve 4' and a full lift curve 'split, the working curve 4 via a Intermediate element 5, a roller rocker arm, is in operative connection with a gas exchange valve 6. Furthermore, a first adjusting device 7, a cam of a camshaft, for rotating the intermediate lever 2 about a point close to the point 8, a center of rotation of the roller supported on the link, against a spring force of a spring element 9 is provided.
  • the intermediate lever 2 is displaceable with a second adjusting device 10, a cam, along the slide track 3 'via the roller supporting the intermediate lever 2 on the slide.
  • a second adjusting device 10 is a contour of a known from the prior art second adjusting device 10 'a second gas exchange valve actuator unit 1' recognizable.
  • the second adjusting device 10 has a first setpoint for a partial lift and a second setpoint for a full lift and a third setpoint for a zero lift of the gas exchange valve 6.
  • Each set point is represented by a curve point of a circular segment of the cam.
  • the cam is divided into a first curve section 12, a second curve section 13 and a third curve section 14.
  • the first set point is a first curve point 12 'on the outer circumference of the first curve section 12 and corresponds to a partial lift of the gas exchange valve 6.
  • the second set point is a second curve point 13' on the outer circumference of the second curve section 13 'and corresponds to a full lift of the gas exchange valve 6.
  • Der third set point is a third curve point 14 'on the outer circumference of the third curve section 14 and corresponds to a zero stroke or decommissioning of the gas exchange valve 6.
  • the second adjusting device 10 can also be replaced by linear adjusting devices which have different stops or latching devices, corresponding to the zero stroke, the partial stroke and the full stroke of the gas exchange valve 6.
  • the third curved section 14 merges continuously into the first curved section 12 and the second curved section 13. As described above, this allows two different modes of operation with their respective specific advantages.
  • FIG. 2 shows the top view of a stroke-variable valve drive 1 according to the invention for an internal combustion engine with two intake gas exchange valves and two exhaust gas exchange valves per cylinder. Shown is a section of the cylinder head 11, inlet side with a first gas exchange valve actuating unit 1 'with two inventively designed second adjusting devices 10, and two second adjusting devices 10' for a second not shown in detail Gas exchange valve actuating unit 1 ', as known from the prior art.
  • the second adjusting devices 10, 10 ' are arranged on a common shaft 15 and are each provided for an inlet gas exchange valve.
  • the cylinder head On the exhaust side, the cylinder head on a conventional valve train, which will not be further discussed.
  • the second adjusting devices 10 have a first curved section 12, a second curved section 13 and a third curved section 14.
  • the structural overhead for decommissioning defined gas exchange valves 6, preferably the intake gas exchange valves, is very low.
  • the outlet gas exchange valves with the proposed embodiment can be shut down.
  • other, cheaper funds for decommissioning can be used, for example, switchable hydraulic valve clearance compensation elements or shift cam followers or other switching elements.
  • Another advantage of the embodiment of the invention lies in the fact that even in the state of the cylinder deactivation, the load control can be represented by a variability of the intake gas exchange valve. This means over "black and white" methods, only full stroke or zero stroke of the gas exchange valves 6, an additional fuel saving potential.
  • the control contour on the second actuator 10 is extended according to the invention in a simple manner in the embodiment. This is done by an extension of the effective angle range of the control contour of the second control element 10.
  • the usual working range on the eccentric cam of the second actuator 10 is limited to less than or equal to 180 °.
  • the working curve range By extending the working curve range to greater than 180 °, ie up to 360 °, it is achieved that the gas exchange valves of the cylinders to be shut down can be shut down, whereas the gas exchange valves 6 of the non-shutdown cylinder maintain their full Hubvariabiltician.
  • this can be done for example by the introduction of further stops or locking devices.

Abstract

The system has two cylinders with similarly functioning charge cycle valves (6), where each cylinder is attached to a charge cycle valve operating device (1`). A control (10) has a positioning point for a partial stroke and another positioning point for a full stroke of a charge cycle valve. The control of the operating device of the cylinder includes a third positioning point for zero stroke of the charge cycle valve.

Description

Die Erfindung betrifft einen hubvariablen Ventiltrieb für eine Brennkraftmaschine mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1.The invention relates to a variable-stroke valve drive for an internal combustion engine having the features of the preamble of patent claim 1.

Sie geht von der deutschen Patentanmeldung DE 101 23 186 aus. In dieser ist eine Ventiltriebsvorrichtung zur variablen Hubverstellung eines Gaswechselventils einer Brennkraftmaschine beschrieben. Bei der Ventiltriebsvorrichtung steht das Gaswechselventil unter Zwischenschaltung der Rolle eines Rollenschlepp- oder Rollenkipphebels mit einem Schwenkhebel in Wirkverbindung, der gaswechselventilseitig eine Steuerbahn mit einer Teilhubkurve und einer Hubkurve aufweist. Auf der dem Gaswechselventil abgewandten Seite ist der Schwenkhebel über eine Rolle auf einer Kulisse schiebebeweglich gelagert. Der Schwenkhebel ist einerseits kulissennah über diese Rolle von einer Stellvorrichtung entlang der Kulissenbahn verschiebbar, um einen Ventilhub einzustellen. Auf der der Stellvorrichtung abgewandten Seite steht der Schwenkhebel kulissenfern über eine zweite Rolle mit dem Nocken einer Nockenwelle in Wirkverbindung, zur Betätigung des Gaswechselventils, wobei die Gaswechselventilbetätigung gegen die Federkraft einer Feder erfolgt. Zur Erzielung einer rein rotatorischen Bewegung des Schwenkhebels um seinen Schwingdrehpunkt, den Rollenmittelpunkt der auf der Kulisse abgestützten Rolle, ist die Kulisse eine Kreisbahn mit einem Radius "R" um die Drehachse der Rolle des Rollenschlepp- oder Rollenkipphebels. Die beschriebene Ventiltriebsvorrichtung kann allen gleich wirkenden Gaswechselventilen (Einlass- und/oder Auslassgaswechselventilen) sämtlicher Zylinder der Brennkraftmaschine zugeordnet werden.She goes from the German patent application DE 101 23 186 out. In this a valve drive device for variable stroke adjustment of a gas exchange valve of an internal combustion engine is described. In the valve drive device, the gas exchange valve with the interposition of the role of a roller drag or roller rocker arm with a pivot lever in operative connection, the gas exchange valve side has a control track with a Teilhubkurve and a lift curve. On the side facing away from the gas exchange valve, the pivot lever is slidably mounted on a slide on a slide. On the one hand, the pivoting lever is displaceable on the roller near the stage by means of an adjusting device along the slide track in order to set a valve lift. On the side facing away from the actuator side of the pivot lever is scenery remote via a second roller with the cam of a camshaft in operative connection, for actuating the gas exchange valve, wherein the gas exchange valve actuation takes place against the spring force of a spring. To achieve a purely rotational movement of the pivot lever about its swing fulcrum, the roller center of the supported on the backdrop role, the backdrop is a circular path with a radius "R" to the Rotary axis of the roller of the roller drag or roller rocker arm. The described valve drive device can be assigned to all cylinders (intake and / or exhaust gas changeover valves) of the same type acting all cylinders of the internal combustion engine.

Da der beschriebene Ventiltrieb keine Nachteile aufweist, liegt die Aufgabe darin, einen gattungsgemäßen Ventiltrieb für eine Brennkraftmaschine mit einer Zylinderabschaltung weiterzubilden.Since the valve train described has no disadvantages, the object is to develop a generic valve train for an internal combustion engine with a cylinder deactivation.

Diese Aufgabe wird durch die Merkmale im kennzeichnenden Teil des Patentanspruchs 1 dadurch gelöst, dass die zweite Stellvorrichtung einer Gaswechselventil-Betätigungseinheit eines Zylinders einen dritten Einstellpunkt für einen Nullhub des Gaswechselventils aufweist.This object is solved by the features in the characterizing part of patent claim 1, characterized in that the second adjusting device of a gas exchange valve actuating unit of a cylinder has a third set point for a zero stroke of the gas exchange valve.

Wenn ohnehin ein bereits vollvariabler, mechanischer Ventiltrieb in der Brennkraftmaschine verbaut ist, ist der vorgeschlagene Mehraufwand zur Stilllegung definierter Gaswechselventile sehr gering. Somit ergibt sich ein äußerst effizienter Weg um auf einfachste Weise eine Zylinderabschaltung, d. h. die Stilllegung der Gaswechsel-Einlassventile eines Zylinders der Brennkraftmaschine, zu realisieren, da lediglich die Gaswechsel-Auslassventile mit separaten Mitteln stillzulegen sind. Selbstverständlich kann auch auslassseitig ein erfindungsgemäßer Ventiltrieb vorgesehen werden. Ein weiterer wesentlicher Vorteil der erfindungsgemäßen Ausgestaltung liegt darin, dass auch im Zustand der Zylinderabschaltung die Laststeuerung der Brennkraftmaschine durch eine Variabilität des Einlassgaswechselventilhubes dargestellt wird. Dies bedeutet gegenüber "Schwarz/Weiß"-Methoden, wie z. B. die Verwendung einer Drosselklappe zur Laststeuerung, ein zusätzliches Kraftstoffeinsparpotential.If, in any case, an already fully variable mechanical valve drive is installed in the internal combustion engine, the proposed additional expenditure for decommissioning defined gas exchange valves is very small. This results in a very efficient way to simplify a cylinder shutdown, d. H. the decommissioning of the gas exchange intake valves of a cylinder of the internal combustion engine to realize, since only the gas exchange exhaust valves are shut down with separate means. Of course, an inventive valve train can also be provided on the outlet side. Another significant advantage of the embodiment of the invention is that even in the state of cylinder deactivation, the load control of the internal combustion engine is represented by a variability of the intake gas exchange valve. This means compared to "black and white" methods, such. As the use of a throttle valve for load control, an additional fuel economy.

Die zweite Stellvorrichtung kann gemäß Patentanspruch 2 eine Kurvenscheibe sein, wobei ein bisher nicht genutzter Kurvenabschnitt eine Nullhubkontur aufweist. In weiteren Ausführungsvarianten können als Stellvorrichtungen auch Schieberlösungen, wie Linearschieber, realisiert werden. Hierbei kann die Lageverschiebung des Zwischenhebels beispielsweise hydraulisch und/oder elektromechanisch durch die Linearbewegung eines Schiebers oder Stellelementes dargestellt werden.The second adjusting device may be a cam according to claim 2, wherein a previously unused curve section a Nullhubkontur having. In further embodiments, slide solutions, such as linear slides, can also be realized as adjusting devices. Here, the positional shift of the intermediate lever can be represented for example hydraulically and / or electromechanically by the linear movement of a slider or actuator.

Die Ausgestaltung gemäß Patentanspruch 3 bietet die einfachste Form der Fertigung einer Kurvenscheibe für einen erfindungsgemäßen hubvariablen Ventiltrieb. Ferner wird ein harmonischer Übergang zwischen den unterschiedlichen Betriebsarten, Teillast-Volllast-Zylinderabschaltung, erzielt. Durch die vorgeschlagene Ausgestaltung sind zwei Betriebsarten des vollvariablen Ventiltriebs möglich. Die Steuerung der Zylinderabschaltung über den Vollhub oder über den Teilhub des Gaswechselventils. Beide vorgeschlagenen Varianten bieten jeweils spezifische Vorteile. Findet die Umschaltung vom zweiten Kurvenabschnitt in den dritten Kurvenabschnitt statt, d. h. bei maximalem Gaswechselventilhub, so wird in diesem Bereich die Brennkraftmaschine über ein separates Drosselorgan, wie beispielsweise eine Drosselklappe, kurzfristig gedrosselt. Diese Form der Abschaltung einzelner Zylinder bringt insbesondere Akustikvorteile. Die einfachere Umschaltung erfolgt vom ersten Kurvenabschnitt in den dritten Kurvenabschnitt. Dies ist insofern von Vorteil, da die Zylinderabschaltung im Bereich einer niederen Last bzw. im Bereich der Abgabe einer niederen Leistung stattfindet, einem Betriebszustand also, bei dem ohnehin eine Zylinderabschaltung erfolgen soll. Nachteilig bei dieser Ausgestaltung ist jedoch der kurze Hubübergang vom Teilhub in den Nullhub, der nur in einem bestimmten Zeitfenster von ca. 300 ms realisiert werden kann. Während dieser kurzen Zeitspanne fällt die Drehzahl der Brennkraftmaschine in etwa auf Leerlaufdrehzahl ab, wodurch ein zur ersten Variante vergleichsweise unruhiger Übergang zu der Zylinderabschaltung erfolgt.The embodiment according to claim 3 provides the simplest form of manufacturing a cam for a variable stroke valve drive according to the invention. Furthermore, a harmonious transition between the different operating modes, partial load full load cylinder deactivation is achieved. The proposed embodiment, two modes of the fully variable valve train are possible. The control of the cylinder deactivation over the full stroke or over the partial lift of the gas exchange valve. Both proposed variants each offer specific advantages. If the changeover takes place from the second curve section to the third curve section, ie at the maximum gas exchange valve lift, the internal combustion engine is temporarily throttled in this area via a separate throttle element, such as a throttle flap. This form of shutdown of individual cylinders brings particular acoustic benefits. The easier switching takes place from the first curve section to the third curve section. This is advantageous in that the cylinder deactivation takes place in the region of a low load or in the region of the delivery of a low power, ie an operating state in which a cylinder deactivation should take place anyway. A disadvantage of this embodiment, however, is the short stroke transition from the partial stroke in the zero stroke, which can be realized only in a certain time window of about 300 ms. During this short period of time, the rotational speed of the internal combustion engine drops approximately to idling speed, whereby a transition to the cylinder deactivation, which is comparatively unstable for the first variant, takes place.

Die Ausgestaltung gemäß Patentanspruch 4 gestattet die optimale Hubsteuerung des Gaswechselventils.The embodiment according to claim 4 allows the optimal stroke control of the gas exchange valve.

Die Anordnung der zweiten Stellvorrichtungen an eine gemeinsame Welle gemäß Patentanspruch 5 reduziert den Fertigungsaufwand und somit die Kosten des erfindungsgemäßen Ventiltriebs.The arrangement of the second adjusting devices to a common shaft according to claim 5 reduces the manufacturing cost and thus the cost of the valve gear according to the invention.

Im Folgenden ist die Erfindung anhand eines bevorzugten Ausführungsbeispieles in zwei Figuren näher erläutert.

Fig. 1
zeigt einen Schnitt durch einen erfindungsgemäßen hubvariablen Ventiltrieb;
Fig. 2
zeigt die Aufsicht auf einen erfindungsgemäßen hubvariablen Ventiltrieb für zwei Zylinder einer Brennkraftmaschine.
In the following the invention with reference to a preferred embodiment is explained in more detail in two figures.
Fig. 1
shows a section through a variable-stroke valve drive according to the invention;
Fig. 2
shows the top view of a variable stroke valve train according to the invention for two cylinders of an internal combustion engine.

Fig. 1 zeigt einen Schnitt durch einen erfindungsgemäßen hubvariablen Ventiltrieb 1 für eine Brennkraftmaschine mit Blick auf eine erste Gaswechselventil-Betätigungseinheit 1'die, wie in Fig. 2 besser erkennbar, eine zweite Gaswechselventil-Betätigungseinheit 1'gemäß dem Stand der Technik fast vollständig überdeckt. Aufbau und Funktion sind für beide Gaswechselventil-Betätigungseinheiten 1', 1'bis auf die erfindungsgemäße Ausgestaltung identisch. Jede Gaswechselventil-Betätigungseinheit 1', 1' ist für die Betätigung eines gleichwirkenden Gaswechselventils 6 der Brennkraftmaschine vorgesehen.1 shows a section through a variable-stroke valve drive 1 according to the invention for an internal combustion engine, with a view of a first gas exchange valve actuating unit 1 ', as can be better seen in FIG. 2, almost completely covering a second gas exchange valve actuating unit 1' according to the prior art , Structure and function are identical for both gas exchange valve actuation units 1 ', 1'bis to the inventive design. Each gas exchange valve actuating unit 1 ', 1' is provided for the actuation of an equivalent gas exchange valve 6 of the internal combustion engine.

Der in einem Zylinderkopf 11 angeordnete hubvariable Ventiltrieb 1 besteht im wesentlichen aus einem Zwischenhebel 2, der einerseits mit einer Rolle schieberollbeweglich auf einer Kulissenbahn 3' einer Kulisse 3 gelagert ist und andererseits eine Arbeitskurve 4 aufweist, die in eine Teilhubkurve 4' und eine Vollhubkurve 4' aufgeteilt ist, wobei die Arbeitskurve 4 über ein Zwischenelement 5, einem Rollenschlepphebel, mit einem Gaswechselventil 6 in Wirkverbindung steht. Ferner ist eine erste Stellvorrichtung 7, ein Nocken einer Nockenwelle, zum Drehen des Zwischenhebels 2 um einen kulissennahen Punkt 8, ein Drehmittelpunkt der auf der Kulisse abgestützten Rolle, gegen eine Federkraft eines Federelementes 9 vorgesehen. Der Zwischenhebel 2 ist mit einer zweiten Stellvorrichtung 10, einer Kurvenscheibe, entlang der Kulissenbahn 3' über die den Zwischenhebel 2 auf der Kulisse abstützenden Rolle verschiebbar. Im Hintergrund der zweiten Stellvorrichtung 10 ist eine Kontur einer aus dem Stand der Technik bekannten zweiten Stellvorrichtung 10' einer zweiten Gaswechselventil-Betätigungseinheit 1' erkennbar. Die zweite Stellvorrichtung 10 weist erfindungsgemäß einen ersten Einstellpunkt für einen Teilhub und einen zweiten Einstellpunkt für einen Vollhub und einen dritten Einstellpunkt für einen Nullhub des Gaswechselventils 6 auf. Jeder Einstellpunkt ist durch einen Kurvenpunkt eines Kreissegmentes der Kurvenscheibe dargestellt. Die Kurvenscheibe ist in einen ersten Kurvenabschnitt 12, einen zweiten Kurvenabschnitt 13 und einen dritten Kurvenabschnitt 14 aufgeteilt. Der erste Einstellpunkt ist ein erster Kurvenpunkt 12' auf dem Außenumfang des ersten Kurvenabschnittes 12 und entspricht einem Teilhub des Gaswechselventils 6. Der zweite Einstellpunkt ist ein zweiter Kurvenpunkt 13' auf dem Außenumfang des zweiten Kurvenabschnittes 13' und entspricht einem Vollhub des Gaswechselventils 6. Der dritte Einstellpunkt ist ein dritter Kurvenpunkt 14' auf dem Außenumfang des dritten Kurvenabschnittes 14 und entspricht einem Nullhub oder einer Stilllegung des Gaswechselventils 6.The arranged in a cylinder head 11 stroke variable valve train 1 consists essentially of an intermediate lever 2, which is on the one hand with a roller slidably mounted on a slide track 3 'a link 3 and on the other hand has a working curve 4, in a Teilhubkurve 4' and a full lift curve 'split, the working curve 4 via a Intermediate element 5, a roller rocker arm, is in operative connection with a gas exchange valve 6. Furthermore, a first adjusting device 7, a cam of a camshaft, for rotating the intermediate lever 2 about a point close to the point 8, a center of rotation of the roller supported on the link, against a spring force of a spring element 9 is provided. The intermediate lever 2 is displaceable with a second adjusting device 10, a cam, along the slide track 3 'via the roller supporting the intermediate lever 2 on the slide. In the background of the second adjusting device 10 is a contour of a known from the prior art second adjusting device 10 'a second gas exchange valve actuator unit 1' recognizable. According to the invention, the second adjusting device 10 has a first setpoint for a partial lift and a second setpoint for a full lift and a third setpoint for a zero lift of the gas exchange valve 6. Each set point is represented by a curve point of a circular segment of the cam. The cam is divided into a first curve section 12, a second curve section 13 and a third curve section 14. The first set point is a first curve point 12 'on the outer circumference of the first curve section 12 and corresponds to a partial lift of the gas exchange valve 6. The second set point is a second curve point 13' on the outer circumference of the second curve section 13 'and corresponds to a full lift of the gas exchange valve 6. Der third set point is a third curve point 14 'on the outer circumference of the third curve section 14 and corresponds to a zero stroke or decommissioning of the gas exchange valve 6.

In weiteren Ausführungsbeispielen kann die zweite Stellvorrichtung 10 anstelle einer Kurvenscheibe auch durch lineare Stelleinrichtungen ersetzt werden, die unterschiedliche Anschläge bzw. Rasteinrichtungen aufweisen, entsprechend dem Nullhub, dem Teilhub und dem Vollhub des Gaswechselventils 6.In further exemplary embodiments, instead of a cam disk, the second adjusting device 10 can also be replaced by linear adjusting devices which have different stops or latching devices, corresponding to the zero stroke, the partial stroke and the full stroke of the gas exchange valve 6.

Bei der dargestellten Ausgestaltung geht der dritte Kurvenabschnitt 14 stetig in den ersten Kurvenabschnitt 12 und den zweiten Kurvenabschnitt 13 über. Wie oben beschrieben sind hierdurch zwei unterschiedliche Betriebsweisen mit ihren jeweils spezifischen Vorteilen möglich.In the illustrated embodiment, the third curved section 14 merges continuously into the first curved section 12 and the second curved section 13. As described above, this allows two different modes of operation with their respective specific advantages.

Fig. 2 zeigt die Aufsicht auf einen erfindungsgemäßen hubvariablen Ventiltrieb 1 für eine Brennkraftmaschine mit zwei Einlassgaswechselventilen und zwei Auslassgaswechselventilen je Zylinder. Für gleiche Bauelemente gelten die gleichen Bezugszeichen wie in Fig. 1. Dargestellt ist ein Abschnitt des Zylinderkopfes 11, einlassseitig mit einer ersten Gaswechselventil-Betätigungseinheit 1' mit zwei erfindungsgemäß ausgestalteten zweiten Stellvorrichtungen 10, sowie zwei zweiten Stellvorrichtungen 10' für eine zweite nicht näher dargestellte Gaswechselventil-Betätigungseinheit 1', wie sie aus dem Stand der Technik bekannt ist. Die zweiten Stellvorrichtungen 10, 10' sind auf einer gemeinsamen Welle 15 angeordnet und sind für jeweils ein Einlassgaswechselventil vorgesehen. Auslassseitig weist der Zylinderkopf einen konventionellen Ventiltrieb auf, der nicht weiter erläutet wird.2 shows the top view of a stroke-variable valve drive 1 according to the invention for an internal combustion engine with two intake gas exchange valves and two exhaust gas exchange valves per cylinder. Shown is a section of the cylinder head 11, inlet side with a first gas exchange valve actuating unit 1 'with two inventively designed second adjusting devices 10, and two second adjusting devices 10' for a second not shown in detail Gas exchange valve actuating unit 1 ', as known from the prior art. The second adjusting devices 10, 10 'are arranged on a common shaft 15 and are each provided for an inlet gas exchange valve. On the exhaust side, the cylinder head on a conventional valve train, which will not be further discussed.

Erfindungsgemäß weisen die zweiten Stellvorrichtungen 10 einen ersten Kurvenabschnitt 12, einen zweiten Kurvenabschnitt 13 sowie einen dritten Kurvenabschnitt 14 auf.According to the invention, the second adjusting devices 10 have a first curved section 12, a second curved section 13 and a third curved section 14.

Da die zweiten Stellvorrichtungen 10, 10' an die gemeinsame Welle 15 angeordnet sind, wird zum Antrieb bzw. zur Verdrehung der gemeinsamen Welle 15 zur Laststeuerung der Brennkraftmaschine nur ein einziges Antriebselement benötigt.Since the second adjusting devices 10, 10 'are arranged on the common shaft 15, only a single drive element is required for driving or for rotating the common shaft 15 for load control of the internal combustion engine.

Zusammengefasst bietet die erfindungsgemäße Weiterbildung des gattungsbildenden hubvariablen Ventiltriebs 1 folgende Vorteile:In summary, the development of the generic type variable stroke valve train 1 according to the invention offers the following advantages:

Da ohnehin bereits ein vollvariabler mechanischer Ventiltrieb vorhanden ist, ist der bauliche Mehraufwand zur Stilllegung definierter Gaswechselventile 6, vorzugsweise der Einlassgaswechselventile, sehr gering. Somit ergibt sich ein äußerst effizienter Weg, um eine Zylinderabschaltung für eine Brennkraftmaschine zu realisieren. Selbstverständlich können auch die Auslassgaswechselventile mit der vorgeschlagenen Ausgestaltung still gelegt werden. Auslassseitig können jedoch auch andere, billigere Mittel zur Stilllegung eingesetzt werden, beispielsweise schaltbare hydraulische Ventilspielausgleichselemente oder auch Schaltschlepphebel oder andere Schaltelemente. Ein weiterer Vorteil der erfindungsgemäßen Ausgestaltung liegt darin begründet, dass auch im Zustand der Zylinderabschaltung die Laststeuerung durch eine Variabilität des Einlassgaswechselventilhubes dargestellt werden kann. Dies bedeutet gegenüber"Schwarz/Weiß"-Methoden, nur Vollhub oder Nullhub der Gaswechselventile 6, ein zusätzliches Kraftstoffeinsparpotential. Um dies zu erzielen, wird im Ausführungsbeispiel in einfacher Weise die Steuerkontur auf der zweiten Stellvorrichtung 10 erfindungsgemäß erweitert. Dies geschieht durch eine Erweiterung des wirksamen Winkelbereichs der Steuerkontur des zweiten Stellelementes 10. Beim erfindungsgemäßen Ausführungsbeispiel ist der übliche Arbeitsbereich auf dem Exzenternocken der zweiten Stellvorrichtung 10 auf kleiner oder gleich 180° beschränkt. Durch die Ausweitung des Arbeitskurvenbereiches auf größer 180°, d. h. auf bis zu 360°, wird erreicht, dass die Gaswechselventile der abzuschaltenden Zylinder stillgelegt werden können, wohingegen die Gaswechselventile 6 der nicht abzuschaltenden Zylinder ihre volle Hubvariabilität beibehalten. In anderen Ausführungsbeispielen, wie z. B. bei hydraulischen und/oder elektromechanischen linearen arbeitenden zweiten Stellvorrichtungen 10, kann dies beispielsweise durch die Einbringung weiterer Anschläge bzw. Rasteinrichtungen erfolgen.Since already a fully variable mechanical valve train is already present, the structural overhead for decommissioning defined gas exchange valves 6, preferably the intake gas exchange valves, is very low. Thus, there is an extremely efficient way to realize cylinder deactivation for an internal combustion engine. Of course, the outlet gas exchange valves with the proposed embodiment can be shut down. On the outlet side, however, other, cheaper funds for decommissioning can be used, for example, switchable hydraulic valve clearance compensation elements or shift cam followers or other switching elements. Another advantage of the embodiment of the invention lies in the fact that even in the state of the cylinder deactivation, the load control can be represented by a variability of the intake gas exchange valve. This means over "black and white" methods, only full stroke or zero stroke of the gas exchange valves 6, an additional fuel saving potential. To achieve this, the control contour on the second actuator 10 is extended according to the invention in a simple manner in the embodiment. This is done by an extension of the effective angle range of the control contour of the second control element 10. In the embodiment according to the invention, the usual working range on the eccentric cam of the second actuator 10 is limited to less than or equal to 180 °. By extending the working curve range to greater than 180 °, ie up to 360 °, it is achieved that the gas exchange valves of the cylinders to be shut down can be shut down, whereas the gas exchange valves 6 of the non-shutdown cylinder maintain their full Hubvariabilität. In other embodiments, such as. B. in hydraulic and / or electromechanical linear operating second adjusting devices 10, this can be done for example by the introduction of further stops or locking devices.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1.1.
Hubvariabler VentiltriebHubvariabler valve drive
1'1'
erste Gaswechselventil-Betätigungseinheitfirst gas exchange valve actuator
1'1'
zweite Gaswechselventil-Betätigungseinheitsecond gas exchange valve actuator
2.Second
Zwischenhebelintermediate lever
3.Third
Kulissescenery
3'3 '
Kulissenbahnlink path
4.4th
Arbeitskurveworking curve
4'4 '
TeilhubkurveTeilhubkurve
4'4 '
VollhubkurveVollhubkurve
5.5th
Zwischenelementintermediate element
6.6th
GaswechselventilGas exchange valve
7.7th
erste Stellvorrichtungfirst adjusting device
8.8th.
kulissennaher Punktscene near the point
9.9th
Federelementspring element
10, 10'10, 10 '
zweite Stellvorrichtungsecond adjusting device
11.11th
Zylinderkopfcylinder head
12.12th
erster Kurvenabschnittfirst curve section
12'12 '
erster Kurvenpunktfirst curve point
13.13th
zweiter Kurvenabschnittsecond curve section
13'13 '
zweiter Kurvenpunktsecond curve point
14.14th
dritter Kurvenabschnittthird curve section
14'14 '
dritter Kurvenpunktthird curve point
15.15th
gemeinsame Wellecommon wave

Claims (5)

Hubvariabler Ventiltrieb (1) für eine Brennkraftmaschine mit zumindest zwei Zylindern mit gleichwirkenden Gaswechselventilen (6), wobei jedem Zylinder zumindest eine Gaswechselventil-Betätigungseinheit (1') zugeordnet ist, bestehend aus - einem Zwischenhebel (2), der einerseits schiebebeweglich auf einer Kulissenbahn (3') einer Kulisse (3) gelagert ist und andererseits eine Arbeitskurve (4) aufweist, wobei - die Arbeitskurve (4) über ein Zwischenelement (5) mit einem Gaswechselventil (6) in Wirkverbindung steht, wobei - eine erste Stellvorrichtung (7) zum Drehen des Zwischenhebels (2) um einen kulissennahen Punkt (8) gegen eine Federkraft eines Federelementes (9) vorgesehen ist, wobei - der Zwischenhebel (2) mit einer zweiten Stellvorrichtung (10) entlang der Kulissenbahn (3') verschiebbar ist, wobei - die zweite Stellvorrichtung (10) zumindest einen ersten Einstellpunkt für einen Teilhub und zumindest einen zweiten Einstellpunkt für einen Vollhub des Gaswechselventils (6) aufweist, dadurch gekennzeichnet, dass die zweite Stellvorrichtung (10) einer Gaswechselventil-Betätigungseinheit (1') eines Zylinders einen dritten Einstellpunkt für einen Nullhub des Gaswechselventils (6) aufweist.Hubvariabler valve drive (1) for an internal combustion engine having at least two cylinders with the same effect gas exchange valves (6), each cylinder at least one gas exchange valve actuator unit (1 ') is assigned, consisting of - An intermediate lever (2) which is on the one hand slidingly mounted on a slide track (3 ') of a link (3) and on the other hand, a working curve (4), wherein - The working curve (4) via an intermediate element (5) with a gas exchange valve (6) is in operative connection, wherein - A first adjusting device (7) for rotating the intermediate lever (2) to a near-stage point (8) against a spring force of a spring element (9) is provided, wherein - The intermediate lever (2) with a second adjusting device (10) along the slide track (3 ') is displaceable, wherein the second adjusting device (10) has at least one first setting point for a partial stroke and at least one second setting point for a full stroke of the gas exchange valve (6), characterized in that the second adjusting device (10) of a gas exchange valve actuating unit (1 ') of a cylinder has a third set point for a zero stroke of the gas exchange valve (6). Hubvariabler Ventiltrieb nach Patentanspruch 1, wobei die zweite Stellvorrichtung (10) eine Kurvenscheibe ist und der erste Einstellpunkt ein erster Kurvenpunkt (12') auf einem ersten Kurvenabschnitt (12) und der zweite Einstellpunkt ein zweiter Kurvenpunkt (13') auf einem zweiten Kurvenabschnitt (13) der Stellvorrichtung (10) ist,
dadurch gekennzeichnet, dass der dritte Einstellpunkt zumindest ein dritter Kurvenpunkt (14') auf einem dritten Kurvenabschnitt (14) der Stellvorrichtung (10) ist.A variable displacement valve train according to claim 1, wherein said second actuator (10) is a cam and said first set point is a first curve point (12 ') on a first curve section (12) and said second set point is a second curve point (13') on a second curve section (12). 13) of the adjusting device (10),
characterized in that the third set point is at least a third curve point (14 ') on a third curve section (14) of the adjusting device (10). Hubvariabler Ventiltrieb nach Patentanspruch 2,
dadurch gekennzeichnet, dass der dritte Kurvenabschnitt (14) stetig in den zweiten Kurvenabschnitt (13) und/oder in den ersten Kurvenabschnitt (12) übergeht.Hubvariabler valve drive according to claim 2,
characterized in that the third curve section (14) merges smoothly into the second curve section (13) and / or into the first curve section (12). Hubvariabler Ventiltrieb nach einem der Patentansprüche 2 oder 3,
dadurch gekennzeichnet, dass die Arbeitskurve (4) eine Teilhubkurve (4') und eine Vollhubkurve (4') aufweist.Hubvariabler valve drive according to one of the claims 2 or 3,
characterized in that the working curve (4) has a Teilhubkurve (4 ') and a Vollhubkurve (4'). Hubvariabler Ventiltrieb nach einem der Patentansprüche 2 bis 4,
dadurch gekennzeichnet, dass die zweiten Stellvorrichtungen (10) von zumindest zwei Zylindern an eine gemeinsame Welle (15) angeordnet sind.Hubvariabler valve drive according to one of the claims 2 to 4,
characterized in that the second adjusting devices (10) of at least two cylinders are arranged on a common shaft (15).
EP06014987A 2005-08-30 2006-07-19 Lift-variable valve-operating system for internal combustion engine Withdrawn EP1760278A3 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510040959 DE102005040959A1 (en) 2005-08-30 2005-08-30 Hubvariabler valve drive for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1760278A2 true EP1760278A2 (en) 2007-03-07
EP1760278A3 EP1760278A3 (en) 2010-03-10

Family

ID=37499693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06014987A Withdrawn EP1760278A3 (en) 2005-08-30 2006-07-19 Lift-variable valve-operating system for internal combustion engine

Country Status (2)

Country Link
EP (1) EP1760278A3 (en)
DE (1) DE102005040959A1 (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010048709A1 (en) 2010-10-19 2012-04-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
DE102011014744A1 (en) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
WO2013113425A1 (en) * 2012-01-30 2013-08-08 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive arrangement
WO2013149737A1 (en) * 2012-04-05 2013-10-10 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve train assembly, internal combustion engine and method for operating an internal combustion engine
DE102013113815A1 (en) 2013-12-11 2015-06-11 Pierburg Gmbh Transmission arrangement for a mechanically controllable valve train
DE102014114396A1 (en) 2014-10-02 2016-04-07 Pierburg Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
EP3073072A2 (en) 2015-03-26 2016-09-28 Pierburg GmbH Mechanically controllable valve drive and mechanically controllable valve drive assembly
US10450907B2 (en) 2014-09-03 2019-10-22 Ford Global Technologies, Llc Valve lift control device with cylinder deactivation

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008047480A1 (en) * 2008-09-17 2010-04-15 Bayerische Motoren Werke Aktiengesellschaft Variable stroke valve drive for adjusting stroke of gas shuttle valve in cylinder head of internal-combustion engine, has pivoted lever displaced by eccentric shaft, and spring whose coil is arranged radially around eccentric shaft
DE102010062319B4 (en) * 2010-12-02 2023-04-20 Bayerische Motoren Werke Aktiengesellschaft Cylinder deactivation in an internal combustion engine with variable valve lift
DE102010054520A1 (en) 2010-12-15 2012-06-21 Bayerische Motoren Werke Aktiengesellschaft Four stroke-reciprocating piston-internal combustion engine has one and another cylinder and one and another piston, which are driven in lifting motion by crank mechanism
DE102011003898B4 (en) 2011-02-10 2021-09-09 Schaeffler Technologies AG & Co. KG Intermediate lever
DE102012002026A1 (en) * 2012-02-03 2013-08-08 Volkswagen Aktiengesellschaft Variable-stroke valve drive for internal combustion engine, has eccentric shaft with eccentric cams having angular range, in which stroke of valve and of similar valve group vary differently from each other
DE102013106646A1 (en) * 2013-06-25 2015-01-08 Pierburg Gmbh Spring arrangement for a variable valve train of an internal combustion engine
DE102015219875A1 (en) 2015-10-14 2017-04-20 Bayerische Motoren Werke Aktiengesellschaft Control shaft for intake valve deactivation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4223172C1 (en) * 1992-07-15 1993-08-19 Bayerische Motoren Werke Ag, 8000 Muenchen, De Cylinder head for IC engine - bearing cover for cam shaft bearing also acts for bearing for eccentric shaft
US5373818A (en) * 1993-08-05 1994-12-20 Bayerische Motoren Werke Ag Valve gear assembly for an internal-combustion engine
EP1143118A2 (en) * 2000-04-07 2001-10-10 Bayerische Motoren Werke Aktiengesellschaft Device for varying the valve lift in an engine cylinder head
DE10123186A1 (en) * 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Valve gear device for variable lift adjustment is for gas exchange valve of internal combustion engine and has valve vai intermediary of transmission component effectively connected to roller movable around rotary axis
DE10235401A1 (en) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Lift stroke-variable valve gear for cylinder head of internal combustion engine has second pivoting lever installed stationary on first lever to form one-piece and material uniform double lever arrangement
EP1445434A1 (en) * 2003-02-04 2004-08-11 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with valve lift adjustment
WO2004088094A2 (en) * 2003-03-29 2004-10-14 Hydraulik-Ring Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19629881A1 (en) * 1996-07-24 1998-01-29 Bayerische Motoren Werke Ag Valve train of an internal combustion engine with rocker arms supported on an eccentric shaft
DE10052811A1 (en) * 2000-10-25 2002-05-08 Ina Schaeffler Kg Variable valve train for load control of a spark ignition internal combustion engine
ES2185519T3 (en) * 2001-05-03 2005-03-16 Sts System Technology Services Gmbh MECHANICAL REGULATION OF THE RUNNING VALVE OF A COMBUSTION ENGINE.
DE10205216B4 (en) * 2002-02-08 2006-04-27 Robert Bosch Gmbh Actuator with variable stroke for an oscillating component
DE10248959B4 (en) * 2002-10-21 2004-07-15 Rolf Jung Valve train of an internal combustion engine with variable valve lift
DE10312959B4 (en) * 2003-03-24 2006-10-05 Thyssenkrupp Automotive Ag Device for the variable actuation of gas exchange valves of internal combustion engines
DE10314683B4 (en) * 2003-03-29 2009-05-07 Entec Consulting Gmbh Variable valve lift control for a combustion engine with a bottom camshaft
DE10341702A1 (en) * 2003-09-10 2005-04-28 Bayerische Motoren Werke Ag Valve drive mechanism for a lifting-piston internal combustion engine has a cam device to activate a gas shuttle valve in accordance with the cam device
DE102004021646A1 (en) * 2004-05-03 2005-12-01 Bayerische Motoren Werke Ag Adjusting shaft of a variable-stroke valve drive
DE102004035005A1 (en) * 2004-07-20 2006-02-16 Bayerische Motoren Werke Ag Valve gear of an internal combustion engine
DE202004016360U1 (en) * 2004-08-20 2005-02-17 Jung, Rolf Completely-variable five-section valve gear for internal combustion engine, includes guide rocker, moving connection adjuster, control pawl and cam track
DE202004019202U1 (en) * 2004-12-01 2005-02-10 Jung, Rolf Fully variable lifting valve controller for combustion engine has intermediate element with rocker arm interacting with pawl in pivotable manner at coupling axis, acted upon by cam/camshaft at engagement surface, control block at free end

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4223172C1 (en) * 1992-07-15 1993-08-19 Bayerische Motoren Werke Ag, 8000 Muenchen, De Cylinder head for IC engine - bearing cover for cam shaft bearing also acts for bearing for eccentric shaft
US5373818A (en) * 1993-08-05 1994-12-20 Bayerische Motoren Werke Ag Valve gear assembly for an internal-combustion engine
EP1143118A2 (en) * 2000-04-07 2001-10-10 Bayerische Motoren Werke Aktiengesellschaft Device for varying the valve lift in an engine cylinder head
DE10123186A1 (en) * 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Valve gear device for variable lift adjustment is for gas exchange valve of internal combustion engine and has valve vai intermediary of transmission component effectively connected to roller movable around rotary axis
DE10235401A1 (en) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Lift stroke-variable valve gear for cylinder head of internal combustion engine has second pivoting lever installed stationary on first lever to form one-piece and material uniform double lever arrangement
EP1445434A1 (en) * 2003-02-04 2004-08-11 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with valve lift adjustment
WO2004088094A2 (en) * 2003-03-29 2004-10-14 Hydraulik-Ring Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012052216A1 (en) 2010-10-19 2012-04-26 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve operating mechanism, and mechanically controllable valve operating mechanism arrangement
DE102010048709B4 (en) * 2010-10-19 2013-01-03 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
DE102010048709A1 (en) 2010-10-19 2012-04-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
US8807104B2 (en) 2010-10-19 2014-08-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve operating mechanism, and mechanically controllable valve operating mechanism arrangement
US9133737B2 (en) 2011-03-22 2015-09-15 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve drive arrangement
DE102011014744A1 (en) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
WO2012126648A1 (en) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve drive arrangement
WO2013113425A1 (en) * 2012-01-30 2013-08-08 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive arrangement
CN104066938A (en) * 2012-01-30 2014-09-24 科尔本施密特皮尔伯格创新股份有限公司 Mechanically controllable valve drive arrangement
CN104066938B (en) * 2012-01-30 2016-09-07 科尔本施密特皮尔伯格创新股份有限公司 Can the valve device of Mechanical course
US9145798B2 (en) 2012-01-30 2015-09-29 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive arrangement
WO2013149737A1 (en) * 2012-04-05 2013-10-10 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve train assembly, internal combustion engine and method for operating an internal combustion engine
JP2015512489A (en) * 2012-04-05 2015-04-27 コルベンシュミット ピアブルク イノヴェイションズ ゲゼルシャフト ミット ベシュレンクテル ハフツングＫｏｌｂｅｎｓｃｈｍｉｄｔ Ｐｉｅｒｂｕｒｇ Ｉｎｎｏｖａｔｉｏｎｓ ＧｍｂＨ Mechanically controllable valve assembly, internal combustion engine and method of operating the internal combustion engine
US9157381B2 (en) 2012-04-05 2015-10-13 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve train assembly, internal combustion engine and method for operating an internal combustion engine
CN104271902A (en) * 2012-04-05 2015-01-07 科尔本施密特皮尔伯格创新股份有限公司 Mechanically controllable valve train assembly, internal combustion engine and method for operating an internal combustion engine
EP2834483B1 (en) * 2012-04-05 2019-03-13 Kolbenschmidt Pierburg Innovations GmbH Mechanically actuated valve drive, engine and engine driving method
EP2905437A2 (en) 2013-12-11 2015-08-12 Pierburg GmbH Transfer assembly for a mechanically controllable valve drive
DE102013113815A1 (en) 2013-12-11 2015-06-11 Pierburg Gmbh Transmission arrangement for a mechanically controllable valve train
US9464540B2 (en) 2013-12-11 2016-10-11 Pierburg Gmbh Transfer assembly for a mechanically controllable valve train
US10450907B2 (en) 2014-09-03 2019-10-22 Ford Global Technologies, Llc Valve lift control device with cylinder deactivation
DE102014114396A1 (en) 2014-10-02 2016-04-07 Pierburg Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement
EP3006684A1 (en) 2014-10-02 2016-04-13 Pierburg GmbH Mechanically controllable valve drive and mechanically controllable valve drive assembly
EP3073072A2 (en) 2015-03-26 2016-09-28 Pierburg GmbH Mechanically controllable valve drive and mechanically controllable valve drive assembly
DE102015104633A1 (en) 2015-03-26 2016-09-29 Pierburg Gmbh Mechanically controllable valve drive and mechanically controllable valve train arrangement

Also Published As

Publication number Publication date
DE102005040959A1 (en) 2007-03-08
EP1760278A3 (en) 2010-03-10

Similar Documents

Publication Publication Date Title
EP1760278A2 (en) Lift-variable valve-operating system for internal combustion engine
EP2017456B1 (en) Exhaust gas recirculation system
EP2459849B1 (en) Valve train device
EP1853797B1 (en) Variable mechanical valve control for an internal combustion engine
DE10025877C2 (en) Exhaust gas recirculation system
DE112004001450B4 (en) Device for an internal combustion engine
DE102006033559A1 (en) Valve drive unit for an internal combustion engine comprises a first adjusting unit assigned to a gas exchange valve of a first cylinder and a second adjusting unit assigned to the gas exchange valve of a second cylinder
DE10241920A1 (en) Valve control system for IC engine has at least two cams per cylinder on a camshaft with axial adjustment and with one cam with a circular outer profile to switch off the valve action
WO2002053881A1 (en) Fully variable mechanical valve gear for a piston internal combustion engine
DE102012002026A1 (en) Variable-stroke valve drive for internal combustion engine, has eccentric shaft with eccentric cams having angular range, in which stroke of valve and of similar valve group vary differently from each other
DE102004008350A1 (en) Engine valve actuation system
DE102005048951B4 (en) Diesel engine with four-valve cylinder head and method for swirl control
EP1608850B1 (en) Device for the variable actuation of the gas exchange valves of internal combustion engines
DE102008059207A1 (en) Cam follower for actuating gas exchange valve in valve gear device of internal-combustion engine, has gripping element for gripping cam outline and another gripping element for gripping another cam outline
DE102016212480A1 (en) Variable valve train of a combustion piston engine
DE69917274T2 (en) Internal combustion engine
WO2004085804A1 (en) Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device
EP1608852B1 (en) Device for the variable actuation of gas exchange valves of internal combustion engines and method for operating said device
EP1375843B1 (en) Internal combustion engine
EP1849976A2 (en) Piston engine
EP3440322A1 (en) Valve train and engine assembly
EP1722076B1 (en) Valve drive train for an internal combustion engine
DE102018130428A1 (en) Variable valve train with at least two working positions
DE10138741A1 (en) Internal combustion engine with valve lift adjustment, has second rocker lever operated by first rocker lever that opens valve in such a way that rocker levers are parallel when valve is closed
DE10352677A1 (en) Variable valve lift device for internal combustion engine, has rotatable eccentric shaft having eccentrics contours positioned within circle formed by external diameter of bearings of eccentric shaft

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 RS

17P Request for examination filed

Effective date: 20100326

17Q First examination report despatched

Effective date: 20100511

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20100621