EP0780547A1 - Internal combustion engine valve lift varying device - Google Patents

Internal combustion engine valve lift varying device Download PDF

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Publication number
EP0780547A1
EP0780547A1 EP96119721A EP96119721A EP0780547A1 EP 0780547 A1 EP0780547 A1 EP 0780547A1 EP 96119721 A EP96119721 A EP 96119721A EP 96119721 A EP96119721 A EP 96119721A EP 0780547 A1 EP0780547 A1 EP 0780547A1
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EP
European Patent Office
Prior art keywords
eccentric shaft
rocker arm
shaft
electric motor
motor
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.)
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Application number
EP96119721A
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German (de)
French (fr)
Inventor
Achim Dipl.-Ing. Koch
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Siemens AG
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Siemens AG
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Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0780547A1 publication Critical patent/EP0780547A1/en
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    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • 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 an adjusting device according to the preamble of claim 1.
  • An adjusting device known from EP 0 638 706 A1 comprises an eccentric shaft on which a rocker arm is supported.
  • a camshaft rolls on a roller that is assigned to the rocker arm.
  • the cam stroke of the camshaft is thus transmitted to the rocker arm, which acts on a gas exchange valve via a rocker arm.
  • the cam stroke is transmitted differently to the rocker arm, which enables different valve stroke profiles.
  • phase shifts between the crankshaft and camshaft that are adjustable by an electric motor and controllable via control units are known in principle; the mutual adjustment takes place via translatory spindle movements, which are associated with the disadvantage of a large installation space and a relatively slow adjustment possibility.
  • the object of the invention is to provide a compact, quickly adjustable and simple adjustment device.
  • FIG. 1 shows a valve train 1 with an adjusting device according to the invention.
  • a cylinder head 2 extends across several cylinders perpendicular to the plane of the drawing.
  • At least one inlet channel 4 to the combustion chamber 5 is provided per cylinder, a gas exchange valve (hereinafter referred to as a lift valve 6) being provided for each inlet channel 4.
  • the lift valve 6 is actuated by a cam 7 of a camshaft 8, the cam 7 acting on the rocker arm 10 via a roller 9 which is rotatably mounted on a rocker arm 10.
  • the rocker arm 10 in turn acts on a rocker arm 11 via a second roller 11a mounted there.
  • the rocker arm 11 is provided with a hydraulic play compensation element 12, on which a shaft 13 of the lift valve 6 is ultimately supported.
  • the adjusting device for the lift valve 6 comprises the rocker arm 10, an eccentric shaft 15 with an eccentric 16, a gear, an electric motor 17 with a motor shaft 18, a rotation angle sensor 19 and a control unit 20.
  • the rocker arm 10 is supported on an eccentric 16, which is machined out of the eccentric shaft 15. If the eccentric shaft 15 is rotated about its longitudinal axis, ie its rotational position is changed, the support point of the rocker arm 10 is shifted. Such a change in the support point of the rocker arm 10 results in different valve lift profiles for the same cam stroke, since due to the changed support of the rocker arm 10, when the cam 7 rotates with respect to the rocker arm 11, a different trajectory is traversed, so that the rocker arm 11 is deflected differently. In particular, it is hereby In addition to a maximum valve lift, it is also possible to achieve a valve lift of almost zero in which the lift valve 6 is opened only minimally.
  • the rocker arm 10 is guided by a bolt-hole guide 21, which comprises an elongated hole 21a in the rocker arm, via which the rocker arm 10 is suspended with a bolt 21b, which is fastened to the cylinder head 2 in a bearing point 22. Because of this bolt-hole guide 21, the rocker arm 10 can thus assume different positions.
  • the electric motor 17 is arranged on the cylinder head 2 such that its motor shaft 18 is positively connected to the eccentric shaft 15 via a gear.
  • the gear is designed as a worm gear.
  • the electric motor 17 is arranged on the cylinder head 2 so that its motor shaft 18 is supported at one free end in a bearing 23 and the longitudinal axis of the motor shaft 18 is perpendicular to the longitudinal axis of the eccentric shaft 15.
  • the worm gear comprises a worm 24 and a worm wheel 25.
  • the worm 24 is arranged on the motor shaft 18 and engages in the worm wheel 25, which is arranged on the eccentric shaft 15.
  • the worm gear mechanism is designed to be self-locking in order to make it impossible to drive the worm 24 from the worm wheel 25. As a result, torque fluctuations of the eccentric shaft 15 are not transmitted directly to the electric motor 17.
  • the angle encoder 19 is arranged on the motor shaft 18 and generates a rotational position signal.
  • An actual value of the rotational position of the eccentric shaft 15 is determined in the control unit 20 from the rotational position signal, taking into account the gear ratio.
  • a setpoint for the rotational position of the eccentric shaft 15 is specified by an engine control of a motor vehicle, not shown here.
  • the electric motor 17 is controlled by the control unit 20.
  • the electric motor 17 can also be arranged such that the longitudinal axis of the motor shaft 18 runs parallel to the eccentric shaft 15.
  • the gear is then designed as a spur gear, which has a first spur gear and a second spur gear.
  • the first spur gear is arranged on the motor shaft 15 and positively connected to the second spur gear, which is arranged on the eccentric shaft 15.
  • the angle encoder 19 can also be arranged directly on the eccentric shaft 15. Then the position signal directly represents the actual value.
  • the rotational position of the eccentric shaft 15 can be changed quickly in any operating state of the internal combustion engine. This is an important advantage in particular if a very large torque is required when starting the internal combustion engine.
  • the rotational position of the eccentric shaft 15 can then be adjusted immediately so that the stroke course of the globe valve 6 becomes maximum. In contrast to an electrohydraulic drive, in which the necessary pressure must first be built up, this is possible without delay.
  • a reset mandrel 26 which always presses the rocker arm 10 against both the cam 7 and the eccentric 16.
  • the reset mandrel 26 is acted upon in a corresponding manner by a compression spring 27 which is supported on a guide element 28 screwed into the cylinder head 2.

Abstract

An adjustment or positioning device for the stroke excursion of a gas exchange valve, includes an eccentric shaft (15) rotatably mounted in a cylinder head (2), a follower lever (10) supported on the eccentric shaft (15) and a roller wheel (9)on which rolls a cam shaft (8) whereby the follower (10) acts on a rocker arm (11) which actuates the gas-exchange valve. The adjustment or positioning device is provided with an electric motor (17) equipped with a motor shaft (18) which is tightly coupled via gears to the eccentric shaft (15). Also included is a control unit (20) for controlling the electric motor (17).

Description

Die Erfindung betrifft eine Verstellvorrichtung gemäß dem Oberbegriff von Patentanspruch 1.The invention relates to an adjusting device according to the preamble of claim 1.

Eine durch die EP 0 638 706 A1 bekannte Verstellvorrichtung umfaßt eine Exzenterwelle, auf der sich ein Schlepphebel abstützt. Eine Nockenwelle rollt sich auf einer Rolle ab, die dem Schlepphebel zugeordnet ist. Somit wird der Nockenhub der Nockenwelle auf den Schlepphebel übertragen, der über einen Schwinghebel auf ein Gaswechselventil einwirkt. Je nach Drehlage der Exzenterwelle wird der Nockenhub unterschiedlich auf den Schlepphebel übertragen, wodurch verschiedenartige Ventilhubverläufe ermöglicht werden.An adjusting device known from EP 0 638 706 A1 comprises an eccentric shaft on which a rocker arm is supported. A camshaft rolls on a roller that is assigned to the rocker arm. The cam stroke of the camshaft is thus transmitted to the rocker arm, which acts on a gas exchange valve via a rocker arm. Depending on the rotational position of the eccentric shaft, the cam stroke is transmitted differently to the rocker arm, which enables different valve stroke profiles.

Es ist bekannt, die Exzenterwelle mit einem elektrohydraulischen Antrieb zu verstellen, der jedoch den Nachteil hat, daß er aufwendig ist und nicht in allen Betriebszuständen der Brennkraftmaschine die Exzenterwelle schnell genug verstellen kann.It is known to adjust the eccentric shaft with an electro-hydraulic drive, which, however, has the disadvantage that it is complex and cannot adjust the eccentric shaft quickly enough in all operating states of the internal combustion engine.

Durch die WO 83/01 483 A1 bzw. die DE 92 17 241 U1 sind elektromotorisch verstellbare, über Steuereinheiten steuerbare Phasenverschiebungen zwischen Kurbelwelle und Nockenwelle grundsätzlich bekannt; die gegenseitige Verstellung erfolgt über translatorische Spindelbewegungen, die mit dem Nachteil eines großen Einbauraums und einer nur relativ langsamen Verstellmöglichkeit verbunden sind.From WO 83/01 483 A1 and DE 92 17 241 U1, phase shifts between the crankshaft and camshaft that are adjustable by an electric motor and controllable via control units are known in principle; the mutual adjustment takes place via translatory spindle movements, which are associated with the disadvantage of a large installation space and a relatively slow adjustment possibility.

Die Aufgabe der Erfindung ist es, eine kompakte, schnell verstellbare und einfache Verstellvorrichtung zu schaffen.The object of the invention is to provide a compact, quickly adjustable and simple adjustment device.

Diese Aufgabe wird erfindungsgemäß durch die Lehre des Patentanspruch 1 gelöst.Vorteilhafte Ausgestaltungen der Erfindung sind jeweils Gegenstand der Unteransprüchen.This object is achieved according to the invention by the teaching of claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.

Ausführungsbeispiele der Erfindung sind im folgenden unter Bezugnahme auf die schematische Zeichnung näher erläutert. Die Figur zeigt einen Ventiltrieb 1 mit einer erfindungsgemäßen Verstellvorrichtung. Ein Zylinderkopf 2 erstreckt sich in der Darstellung senkrecht zur Zeichenebene über mehrere Zylinder. Je Zylinder ist zumindest ein Einlaßkanal 4 zum Brennraum 5 vorhanden, wobei je Einlaßkanal 4 ein Gaswechselventil ( im folgenden als Hubventil 6 bezeichnet) vorgesehen ist. Betätigt wird das Hubventil 6 durch einen Nocken 7 einer Nockenwelle 8, wobei der Nocken 7 über eine Rolle 9, die drehbar auf einem Schlepphebel 10 gelagert ist, auf diesen einwirkt. Der Schlepphebel 10 wirkt seinerseits auf einen Schwinghebel 11 über eine dort gelagerte zweite Rolle 11a ein. Der Schwinghebel 11 ist mit einem hydraulischen Spielausgleichselement 12 versehen, auf dem sich letztendlich ein Schaft 13 des Hubventils 6 abstützt.Exemplary embodiments of the invention are explained in more detail below with reference to the schematic drawing. The figure shows a valve train 1 with an adjusting device according to the invention. A cylinder head 2 extends across several cylinders perpendicular to the plane of the drawing. At least one inlet channel 4 to the combustion chamber 5 is provided per cylinder, a gas exchange valve (hereinafter referred to as a lift valve 6) being provided for each inlet channel 4. The lift valve 6 is actuated by a cam 7 of a camshaft 8, the cam 7 acting on the rocker arm 10 via a roller 9 which is rotatably mounted on a rocker arm 10. The rocker arm 10 in turn acts on a rocker arm 11 via a second roller 11a mounted there. The rocker arm 11 is provided with a hydraulic play compensation element 12, on which a shaft 13 of the lift valve 6 is ultimately supported.

Die Verstellvorrichtung für das Hubventil 6 umfaßt den Schlepphebel 10 eine Exzenterwelle 15 mit einem Exzenter 16, ein Getriebe, einen Elektromotor 17 mit einer Motorwelle 18, einen Drehwinkelgeber 19 und eine Steuereinheit 20.The adjusting device for the lift valve 6 comprises the rocker arm 10, an eccentric shaft 15 with an eccentric 16, a gear, an electric motor 17 with a motor shaft 18, a rotation angle sensor 19 and a control unit 20.

Der Schlepphebel 10 stützt sich an einem Exzenter 16 ab, der aus der Exzenterwelle 15 herausgearbeitet ist. Wird die Exzenterwelle 15 um ihre Längsachse verdreht, d.h. ihre Drehlage verändert, so wird der Abstützpunkt des Schlepphebels 10 verschoben. Mit einer derartigen Veränderung des Abstützpunktes des Schlepphebels 10 ergeben sich bei gleichem Nockenhub unterschiedliche Ventilhubverläufe, da aufgrund der geänderten Abstützung der Schlepphebel 10 bei einer Rotation des Nockens 7 gegenüber dem Schwinghebel 11 eine unterschiedliche Bewegungsbahn durchläuft, so daß auch der Schwinghebel 11 unterschiedlich ausgelenkt wird. Insbesondere ist es hiermit möglich neben einem maximalen Ventilhub auch einen Ventilhub nahezu vom Betrag Null zu erreichen, bei dem das Hubventil 6 lediglich minimal geöffnet wird.The rocker arm 10 is supported on an eccentric 16, which is machined out of the eccentric shaft 15. If the eccentric shaft 15 is rotated about its longitudinal axis, ie its rotational position is changed, the support point of the rocker arm 10 is shifted. Such a change in the support point of the rocker arm 10 results in different valve lift profiles for the same cam stroke, since due to the changed support of the rocker arm 10, when the cam 7 rotates with respect to the rocker arm 11, a different trajectory is traversed, so that the rocker arm 11 is deflected differently. In particular, it is hereby In addition to a maximum valve lift, it is also possible to achieve a valve lift of almost zero in which the lift valve 6 is opened only minimally.

Geführt wird der Schlepphebel 10 durch eine Bolzen-Loch-Führung 21, die ein Langloch 21a in dem Schlepphebel umfaßt, über das der Schlepphebel 10 mit einem Bolzen 21b eingehängt ist, der am Zylinderkopf 2 in einer Lagerstelle 22 befestigt ist. Aufgrund dieser Bolzen-Loch-Führung 21 kann somit der Schlepphebel 10 unterschiedliche Positionen einnehmen.The rocker arm 10 is guided by a bolt-hole guide 21, which comprises an elongated hole 21a in the rocker arm, via which the rocker arm 10 is suspended with a bolt 21b, which is fastened to the cylinder head 2 in a bearing point 22. Because of this bolt-hole guide 21, the rocker arm 10 can thus assume different positions.

Der Elektromotor 17 ist derart am Zylinderkopf 2 angeordnet, daß seine Motorwelle 18 über ein Getriebe formschlüssig mit der Exzenterwelle 15 verbunden ist. Das Getriebe ist als Schneckenradgetriebe ausgebildet. Der Elektromotor 17 ist am Zylinderkopf 2 so angeordnet, daß seine Motorwelle 18 an ihrem einen freien Ende in einem Lager 23 gelagert ist und die Längsachse der Motorwelle 18 rechtwinklig zur Längsachse der Exzenterwelle 15 liegt. Das Schneckenradgetriebe umfaßt eine Schnecke 24 und ein Schneckenrad 25. Die Schnecke 24 ist auf der Motorwelle 18 angeordnet und greift in das Schneckenrad 25 ein, das auf der Exzenterwelle 15 angeordnet ist. Das Schneckenradgetriebe ist selbsthemmend ausgebildet, um einen Antrieb der Schnecke 24 vom Schneckenrad 25 unmöglich zu machen. Dadurch werden Momentenschwankungen der Exzenterwelle 15 nicht direkt auf den Elektromotor 17 übertragen.The electric motor 17 is arranged on the cylinder head 2 such that its motor shaft 18 is positively connected to the eccentric shaft 15 via a gear. The gear is designed as a worm gear. The electric motor 17 is arranged on the cylinder head 2 so that its motor shaft 18 is supported at one free end in a bearing 23 and the longitudinal axis of the motor shaft 18 is perpendicular to the longitudinal axis of the eccentric shaft 15. The worm gear comprises a worm 24 and a worm wheel 25. The worm 24 is arranged on the motor shaft 18 and engages in the worm wheel 25, which is arranged on the eccentric shaft 15. The worm gear mechanism is designed to be self-locking in order to make it impossible to drive the worm 24 from the worm wheel 25. As a result, torque fluctuations of the eccentric shaft 15 are not transmitted directly to the electric motor 17.

Der Drehwinkelgeber 19 ist auf der Motorwelle 18 angeordnet und erzeugt ein Drehlagensignal. Aus dem Drehlagensignal wird in der Steuereinheit 20 unter Berücksichtigung der Getriebeübersetzung ein Istwert der Drehlage der Exzenterwelle 15 ermittelt. Ein Sollwert für die Drehlage der Exzenterwelle 15 wird von einer hier nicht dargestellten Motorsteuerung eines Kraftfahrzeugs vorgegeben. In Abängigkeit von dem Istwert und dem Sollwert wird der Elektromotor 17 von der Steuereinheit 20 angesteuert.The angle encoder 19 is arranged on the motor shaft 18 and generates a rotational position signal. An actual value of the rotational position of the eccentric shaft 15 is determined in the control unit 20 from the rotational position signal, taking into account the gear ratio. A setpoint for the rotational position of the eccentric shaft 15 is specified by an engine control of a motor vehicle, not shown here. Depending on the actual value and the desired value, the electric motor 17 is controlled by the control unit 20.

Der Elektromotor 17 kann auch derart angeordnet sein, daß die Längsachse der Motorwelle 18 parallel zu der Exzenterwelle 15 verläuft. Das Getriebe ist dann als Stirnradgetriebe ausgebildet, das ein erstes Stirnrad und zweites Stirnrad aufweist. Das erste Stirnrad ist auf der Motorwelle 15 angeordnet und formschlüssig mit dem zweiten Stirnrad verbunden, das auf der Exzenterwelle 15 angeordnet ist.The electric motor 17 can also be arranged such that the longitudinal axis of the motor shaft 18 runs parallel to the eccentric shaft 15. The gear is then designed as a spur gear, which has a first spur gear and a second spur gear. The first spur gear is arranged on the motor shaft 15 and positively connected to the second spur gear, which is arranged on the eccentric shaft 15.

Der Drehwinkelgeber 19 kann auch direkt auf der Exzenterwelle 15 angeordnet sein. Dann stellt das Drehlagensignal direkt den Istwert dar.The angle encoder 19 can also be arranged directly on the eccentric shaft 15. Then the position signal directly represents the actual value.

Mit der erfindungsgemäßen Verstellvorrichtung ist ein schnelles Verändern der Drehlage der Exzenterwelle 15 in jedem Betriebszustand der Brennkraftmaschine möglich. Dies ist insbesondere dann ein gewichtiger Vorteil, wenn beim Start der Brennkraftmaschine ein sehr großes Drehmoment benötigt wird. Die Drehlage der Exzenterwelle 15 kann dann sofort so eingestellt werden, daß der Hubverlauf des Hubventils 6 maximal wird. Dies ist im Gegensatz zu einem elektrohydraulischen Antrieb, bei dem erst der nötige Druck aufgebaut werden muß, ohne Zeitverzug möglich.With the adjusting device according to the invention, the rotational position of the eccentric shaft 15 can be changed quickly in any operating state of the internal combustion engine. This is an important advantage in particular if a very large torque is required when starting the internal combustion engine. The rotational position of the eccentric shaft 15 can then be adjusted immediately so that the stroke course of the globe valve 6 becomes maximum. In contrast to an electrohydraulic drive, in which the necessary pressure must first be built up, this is possible without delay.

Zur Sicherstellung der beschriebenen Verstellfunktion greift ferner an einem Absatz des Schlepphebels ein Rückstelldorn 26 an, der den Schlepphebel 10 stets sowohl gegen den Nocken 7 als auch gegen den Exzenter 16 preßt. Hierzu wird der Rückstelldorn 26 in entsprechender Weise von einer Druckfeder 27 beaufschlagt, die sich an einem in den Zylinderkopf 2 eingeschraubten Führungselement 28 abstützt.To ensure the adjustment function described also acts on a shoulder of the rocker arm, a reset mandrel 26, which always presses the rocker arm 10 against both the cam 7 and the eccentric 16. For this purpose, the reset mandrel 26 is acted upon in a corresponding manner by a compression spring 27 which is supported on a guide element 28 screwed into the cylinder head 2.

Es ist vorteilhaft eine Rückstellfeder vorzusehen, die derart angeordnet ist, daß sie bei Ausfall des Elektromotors 17 die Motorwelle 18 in eine Notlaufposition verstellt. Dadurch kann die Funktion der Brennkraftmaschine auch in diesem Fall sichergestellt werden und eine mechanische Beschädigung des Ventiltriebs verhindert werden.It is advantageous to provide a return spring which is arranged such that it moves the motor shaft 18 into an emergency running position in the event of failure of the electric motor 17. As a result, the function of the internal combustion engine can also be ensured in this case and mechanical damage to the valve train can be prevented.

Claims (4)

Verstellvorrichtung für den Hubverlauf eines Gaswechselventils einer Brennkraftmaschine - mit einer Exzenterwelle (15), die drehbar in einem Zylinderkopf (2) gelagert ist, - mit einem Schlepphebel (10), der auf die Exzenterwelle (15) abgestützt ist und eine Rolle (9) aufweist, auf der eine Nockenwelle (8) abrollt, wobei der Schlepphebel (10) auf einen Schwinghebel (11) einwirkt, der das Gaswechselventil betätigt, gekennzeichnet durch - einen Elektromotor (17), dessen rechtwinklig zu der Exzenterwelle (15) verlaufende Motorwelle (18) nach Art eines Schneckengetriebes über eine koaxial mit der Motorwelle (18) verbundene Schnecke (24) ein koaxial auf der Exzenterwelle (15) angeordnetes Schneckenrad (25) antreibt, - durch eine Steuereinheit (20), die den Elektromotor (17) steuert. Adjustment device for the stroke of a gas exchange valve of an internal combustion engine - With an eccentric shaft (15) which is rotatably mounted in a cylinder head (2), - With a rocker arm (10), which is supported on the eccentric shaft (15) and has a roller (9) on which a camshaft (8) rolls, the rocker arm (10) acting on a rocker arm (11), which Gas exchange valve actuated, characterized by - An electric motor (17), the motor shaft (18) of which runs at right angles to the eccentric shaft (15) in the manner of a worm gear via a worm gear (24) coaxially connected to the motor shaft (18) and a worm wheel (25) arranged coaxially on the eccentric shaft (15) ) drives - By a control unit (20) that controls the electric motor (17). Verstellvorrichtung für den Hubverlauf eines Gaswechselventils einer Brennkraftmaschine - mit einer Exzenterwelle (15), die drehbar in einem Zylinderkopf (2) gelagert ist, - mit einem Schlepphebel (10), der auf die Exzenterwelle (15) abgestützt ist und eine Rolle (9) aufweist, auf der eine Nockenwelle (8) abrollt, wobei der Schlepphebel (10) auf einen Schwinghebel (11) einwirkt, der das Gaswechselventil betätigt, gekennzeichnet durch - einen Elektromotor (17), dessen parallel zu der Exzenterwelle (15) verlaufende Motorwelle (18) nach Art eines Stirnradgetriebes über ein koaxial auf der Motorwelle (18) angeordnetes erstes Stirnrad ein koaxial auf der Exzenterwelle (15) angeordnetes zweites Stirnrad antreibt, - durch eine Steuereinheit (10), die den Elektromotor (17) steuert. Adjustment device for the stroke of a gas exchange valve of an internal combustion engine - With an eccentric shaft (15) which is rotatably mounted in a cylinder head (2), - With a rocker arm (10), which is supported on the eccentric shaft (15) and has a roller (9) on which a camshaft (8) rolls, the rocker arm (10) acting on a rocker arm (11), which Gas exchange valve actuated, characterized by an electric motor (17), the motor shaft (18) of which runs parallel to the eccentric shaft (15) and drives a second spur gear arranged coaxially on the eccentric shaft (15) via a first spur gear arranged coaxially on the motor shaft (18), - By a control unit (10) that controls the electric motor (17). Verstellvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß sie einen Drehwinkelgeber (19) auf der Motorwelle (18) aufweist, der ein Drehlagensignal erzeugt und an die Steuereinheit (20) weiterleitet.Adjusting device according to claim 1 or 2, characterized in that it has a rotation angle transmitter (19) on the motor shaft (18) which generates a rotation position signal and forwards it to the control unit (20). Verstellvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß sie einen Drehwinkelgeber (19) auf der Exzenterwelle (15) aufweist, der ein Drehlagensignal erzeugt und an die Steuereinheit (20) weiterleitet.Adjusting device according to claim 1 or 2, characterized in that it has a rotary angle sensor (19) on the eccentric shaft (15) which generates a rotary position signal and forwards it to the control unit (20).
EP96119721A 1995-12-22 1996-12-09 Internal combustion engine valve lift varying device Withdrawn EP0780547A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1995148389 DE19548389A1 (en) 1995-12-22 1995-12-22 Adjustment device for the stroke of a gas exchange valve of an internal combustion engine
DE19548389 1995-12-22

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EP0780547A1 true EP0780547A1 (en) 1997-06-25

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EP96119721A Withdrawn EP0780547A1 (en) 1995-12-22 1996-12-09 Internal combustion engine valve lift varying device

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DE (1) DE19548389A1 (en)

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US6425357B2 (en) 2000-03-21 2002-07-30 Toyota Jidosha Kabushiki Kaisha Variable valve drive mechanism and intake air amount control apparatus of internal combustion engine
EP1255027A1 (en) * 2001-05-03 2002-11-06 STS System Technology Services GmbH Mechanic control of variable lift of an intake valve of an internal combustion engine
EP1347154A2 (en) * 2002-03-20 2003-09-24 Hydraulik-Ring Gmbh Valve lift control for internal combustion engine
EP1387050A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Cylinder head for an internal combustion engine with variable lift valve drive
EP1387049A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Rocker arm for a variable lift valve drive
WO2004057160A1 (en) * 2002-12-21 2004-07-08 Ina-Schaeffler Kg Intermediate lever for a variable valve drive of an internal combustion engine
WO2004059133A1 (en) * 2002-12-27 2004-07-15 Boesl-Flierl Gerlinde Valve actuation device for variable valve control of gas-exchange valves of an internal combustion engine
EP1445434A1 (en) * 2003-02-04 2004-08-11 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with valve lift adjustment
US6932035B1 (en) 2005-01-28 2005-08-23 Ford Global Technologies, Llc Cylinder valve operating system for internal combustion engine
EP1619361A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve-moving device for engine
EP1801368A1 (en) * 2005-12-26 2007-06-27 Otics Corporation Variable valve operating mechanism
KR100949524B1 (en) 2002-06-20 2010-03-25 엔텍 컨설팅 게엠베하 A stroke adjusting device for valves of a combustion engine
EP1921282A3 (en) * 2006-10-31 2010-08-11 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Arrangement structure of electrically-driven actuator
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US6792903B2 (en) 2001-05-03 2004-09-21 Sts System Technology Services Gmbh Mechanical control of the intake valve lift adjustment in an internal combustion engine
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EP1387049A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Rocker arm for a variable lift valve drive
EP1387050A1 (en) * 2002-08-02 2004-02-04 Bayerische Motoren Werke Aktiengesellschaft Cylinder head for an internal combustion engine with variable lift valve drive
WO2004057160A1 (en) * 2002-12-21 2004-07-08 Ina-Schaeffler Kg Intermediate lever for a variable valve drive of an internal combustion engine
US7055478B2 (en) 2002-12-21 2006-06-06 Ina-Schaeffler Kg Intermediate lever for a variable valve train of an internal combustion engine
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US7044094B2 (en) 2002-12-27 2006-05-16 Gerlinde Bosl-Flierl Valve-lift device for the variable control of gas-exchange valves of an internal combustion engine
WO2004059133A1 (en) * 2002-12-27 2004-07-15 Boesl-Flierl Gerlinde Valve actuation device for variable valve control of gas-exchange valves of an internal combustion engine
EP1445434A1 (en) * 2003-02-04 2004-08-11 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine with valve lift adjustment
EP1619361A4 (en) * 2003-05-01 2008-11-26 Yamaha Motor Co Ltd Valve-moving device for engine
EP1619361A1 (en) * 2003-05-01 2006-01-25 Yamaha Hatsudoki Kabushiki Kaisha Valve-moving device for engine
US6932035B1 (en) 2005-01-28 2005-08-23 Ford Global Technologies, Llc Cylinder valve operating system for internal combustion engine
EP1801368A1 (en) * 2005-12-26 2007-06-27 Otics Corporation Variable valve operating mechanism
US7621242B2 (en) 2005-12-26 2009-11-24 Otics Corporation Variable valve operating mechanism
EP1921282A3 (en) * 2006-10-31 2010-08-11 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Arrangement structure of electrically-driven actuator
WO2011080076A1 (en) * 2009-12-16 2011-07-07 Iveco Motorenforschung Ag Mechanical variable valve actuation system for 2-stroke and 4-stroke engine operations
US8584635B2 (en) 2009-12-16 2013-11-19 Iveco Motorenforschung Ag Mechanical variable valve actuation system for 2-stroke and 4-stroke engine operations
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