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EP1748160A1 - Variable valve driving gear for internal combustion engines - Google Patents

Variable valve driving gear for internal combustion engines Download PDF

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Publication number
EP1748160A1
EP1748160A1 EP06013565A EP06013565A EP1748160A1 EP 1748160 A1 EP1748160 A1 EP 1748160A1 EP 06013565 A EP06013565 A EP 06013565A EP 06013565 A EP06013565 A EP 06013565A EP 1748160 A1 EP1748160 A1 EP 1748160A1
Authority
EP
European Patent Office
Prior art keywords
intermediate member
support body
variable valve
rocker
cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06013565A
Other languages
German (de)
French (fr)
Other versions
EP1748160B1 (en
Inventor
Markus Meyer
Andreas Werler
Jörg Wutzler
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.)
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Original Assignee
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
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 IAV GmbH Ingenieurgesellschaft Auto und Verkehr filed Critical IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Publication of EP1748160A1 publication Critical patent/EP1748160A1/en
Application granted granted Critical
Publication of EP1748160B1 publication Critical patent/EP1748160B1/en
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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
    • F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
    • F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the invention relates to a variable valve train for internal combustion engines with the features mentioned in the preamble of claim 1.
  • the intermediate member is in engagement with one of the cams of the camshaft and a Hubübertragungsan Ich for a valve.
  • the cam determines depending on the pivotal position of the variable element during the stroke of the cam, the trajectory of the intermediate member and thus the size of the Hubübertragungsan himself caused by the valve stroke.
  • the structural design of this embodiment is limited because the support curve and the cam are arranged successively extending on the variable in its position element and thereby a certain distance between the two prismatic engagement lines on the support curve and the control cam and the intermediate member is necessary.
  • a variable valve train for internal combustion engines with a indirectly from a cam via a cylinder head directly or indirectly pivotally mounted rocker or rocker arm moving valve assembly having one or more under the action of a spring closing valves.
  • the rocker arm or rocker arm engages with a swingably guided intermediate lever, this intermediate lever continuing on the one hand with the cam of a camshaft and on the other hand with a control cam of a directly or indirectly rotatably mounted on the cylinder head support body slidably engaged or rolling.
  • the support body determines with its position and the thus effective range of a control cam, the size of the valve, wherein by means of a suitable control and a corresponding actuator, the angular position of the support body can be adjusted.
  • variable valve train with adjustable valve lift in which automatically takes place in an adjustment in the direction of lower stroke, a forward displacement of the valve opening area.
  • an intermediate lever via a roller arranged on the intermediate lever with a valve-actuating pivot lever and arranged on a pivotable support body supporting curve and on the other hand via a roller arranged on the intermediate lever with the cam contour of the camshaft in operative connection.
  • a guide rocker is pivotally arranged, which is articulated to a coupled to the support body actuating arm.
  • the invention has for its object to provide a variable valve train for an internal combustion engine in which an adjustment of the valve opening and / or valve closing angle takes place in the direction of early or late in reducing the forces and the required installation space, at the same time carried out adjusting the valve lift can.
  • a variable valve train for internal combustion engines consisting of at least one camshaft, which is operatively connected via transmission members with a pivot lever for actuating the valves and a support body for valve lift
  • the intermediate member is firstly arranged on the intermediate member on a.
  • the intermediate member is indirectly connected via an arranged on a rocker roller with the cam of the camshaft in operative connection, wherein the pivotable rocker is pivotally connected thereto via a lever connected to the intermediate member.
  • valve lift adjustment and / or for adjusting the valve opening and / or closing angle the rocker is articulated to the pivotable support body.
  • a variant of the valve lift adjustment and / or adjustment of Ventilötechnischs- and / or -sch spawinkels provides to arrange the support body fixed to the cylinder head and to provide the now no longer connected to the support body rocker with an adjustment for pivoting the rocker.
  • the advantage of the device according to the invention consists in a compact design, which makes it possible to concentrate the components such as camshaft, support body, pivot lever and transmission elements in the narrowest space.
  • Another significant advantage of the solution according to the invention is that the force transmission point of the intermediate member on the support body is always between the contact point of the support curve of the intermediate member on the pin of the support body and the contact point of the arranged on the intermediate member and the control cam of the support body. This ensures that the intermediate member is constantly pressed against the support body. A possible swing out the intermediate member of the device is thereby avoided. At the same time, the forces to be transmitted are minimized by this arrangement.
  • valve opening angle can be kept almost constant by the design of the control cam and the support curve and the outer contour surface of the intermediate member in conjunction with the adjustment of the intermediate member by the pivotable rocker, while the closing angle between early and late is adjustable ,
  • the lifting height of the valve lift curve is also variable, wherein the minimization of the valve lift can be kept low.
  • This is advantageous in particular for the application of the valve drive according to the invention for an inlet valve.
  • it is advantageous to leave the closing angle of the exhaust valve almost constant, while the opening angle of the exhaust valve is adjusted to early or late. This can also be done a variation of the valve.
  • variable valve drive for internal combustion engines is explained using the example of an intake valve.
  • the solution according to the invention can also be used for the exhaust valves of an internal combustion engine.
  • the valve train has a camshaft 1 with a cam 2 which, with the interposition of a transmission mechanism, moves a pivoting lever 14 and thus a valve 17 which can be closed by means of spring force and is kept closed.
  • a valve 17 which can be closed by means of spring force and is kept closed.
  • the pivot lever 14 is mounted on a guided in the cylinder head axis with the interposition of an eccentric bushing 19.
  • the pivotable eccentric bushing 19 serves for additional adaptation of the pivot lever position in cooperation with the clearance compensation element 16.
  • the displaceable transmission mechanism consists essentially of an intermediate member 9 and an articulated on the intermediate member 9 lever 10, which is articulated about a pivotally mounted rocker 3.
  • a roller 4 is arranged, in operative connection with the contour of the cam 2 of Camshaft 1 is stationary.
  • a supporting body 5 pivotally mounted about the pivot axis 18 on the cylinder head and, as shown in Figure 1 to 3, connected to the rocker 3.
  • the rocker 3 is simultaneously pivoted, whereby a displacement of the intermediate member 9 on the support body 5 for valve lift adjustment and / or for adjusting the valve opening and / or closing angle.
  • a variant of the solution according to the invention provides to arrange the support body 5, as shown in Figure 4 and 5, fixed to the cylinder head.
  • the rocker 3 is no longer connected to the support body.
  • the adjusting device 20 is preferably an eccentric adjustment.
  • the intermediate member 9 is supported on the one hand on the support body 5 and on the other hand on the pivot lever 14.
  • the support of the intermediate member 9 on the support body 5 is effected on the one hand on a support body 5 arranged support surface and the other on a support body 5 arranged on the control cam 11.
  • the supporting body 5 arranged support surface is preferably the outer surface of a support body 5 arranged on the pin 6, at which the arranged on the intermediate member 9 support curve 13 is supported.
  • the pin 6 is arranged about the pivot axis 18 of the support body 5.
  • a roller 8 is arranged, which is in communication with the support body 5 arranged on the control cam 11.
  • the intermediate member 9 is supported on a arranged on the pivot lever 14 roller 15 from.
  • the valve spring not shown, the pivot lever 14 is pivoted counterclockwise and thus pressed the intermediate member 9 via the roller 15 against the support body 5.
  • the intermediate member 9 is secure between the support body 5 and the pivot lever fourteenth mounted and is displaced according to the engagement of the contour of the cam 2 along the control cam 11 of the support body 5.
  • the mode of action of the solution according to the invention is the following:
  • the illustrated in Figure 1 first variant of the solution according to the invention shows a closed valve 17 at a maximum set valve lift.
  • the eccentric adjustment 7 the support body 5 has pivoted about the pivot axis 18 counterclockwise in the position shown and the roller 4 of the rocker 3 is connected to the base circle of the cam 2 in engagement.
  • the cam 2 shown in Figure 1 is rotated in the clockwise direction.
  • the roller 4 is displaced by the cam 2, whereby the rocker 3 is pivoted about its point of articulation on the support body 5 in a clockwise direction.
  • the rocker 3 By pivoting the rocker 3, the articulated via the lever 10 to the rocker arm 3 intermediate member 9 is moved over the roller 8 along the control cam 11 of the support body 5.
  • FIG. 2 shows a fully opened valve 17 at a maximum stroke setting.
  • an open valve 17 is shown at a minimum set valve lift.
  • the support body 5 shown in Figures 1 and 2 is pivoted in the clockwise direction about the pivot axis 18. This also changes the position of the control cam 11 and the position of the intermediate member 9 engaged therewith so that upon complete engagement of the cam 2 with the roller 4, the pivoting lever 14 is pivoted only by a minimum amount.
  • the intermediate member 9 is also displaced during pivoting of the support body 5, that at a variably adjusted valve lift height at the same time the valve opening and / or closing angle can be adjusted.
  • FIGS. 4 and 5 as described above, a variant of the solution according to the invention is shown.
  • the same components are provided with the same reference numerals.
  • opening and closing the valve 17 the intermediate member 9 along the control cam 11 of the support body 5 is displaced by the cam 2 and the rocker 3 and the lever 10, analogously as described to Figures 1 to 3.
  • the support body 5 is firmly connected to the cylinder head.
  • the adjustment of different valve lifts and / or the adjustment of the Ventilötechnischs- and / or - closing angle is done by the Exzenterver ein arranged on the rocker 3 adjusting 20.
  • the eccentric adjustment of the adjusting 20, the rocker 3 is displaced and thus on the on the rocker. 3 hinged lever 10, the position of the intermediate member 9 on the control cam 11 of the support body 5 changed.
  • the valve 17 is closed, while according to Figure 5, the valve 17 is opened.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The variable valve drive has at least one camshaft, a pivoting lever (14) in the cylinder head that interacts with a valve (17) closed under spring force, a supporting body (5) with a control cam for valve lift adjustment and an intermediate element (9) guided between the supporting body and pivoting lever. The intermediate element engages the lever first via a supporting surface on the supporting body, second via the control cam and third via an outer contour surface on the intermediate element and can be displaced by a cam (2) on the camshaft (1).

Description

Die Erfindung betrifft einen variablen Ventiltrieb für Verbrennungskraftmaschinen mit den im Oberbegriff des Patentanspruches 1 genannten Merkmalen.The invention relates to a variable valve train for internal combustion engines with the features mentioned in the preamble of claim 1.

Vorbekannt ist aus der Schrift DE 100 61 618 B4 eine Einrichtung zur variablen Betätigung von Ventilen mittels Nocken. Diese ist in einem Zylinderkopf mit einer ortsfest gelagerten Nockenwelle, mit durch Federkraft schließenden Ventilen und zusammen mit jeweils einer jedem der Ventile zugeordneten, lagefest im Zylinderkopf geführten Hubübertragungsanordnung angeordnet. Ein zur Ventilhubeinstellung verstellbares Element ist im Zylinderkopf ortsfest, jedoch schwenkbar gelagert angeordnet. Es weist in einer axialen Ebene nacheinander verlaufend je eine Stützkurve und eine Steuerkurve auf. Ein Zwischenglied ist an dem in seiner Stellung veränderlichen Element sowohl an dessen Stütz- als auch an dessen Steuerkurve unter Kraftschluss prismatisch abgestützt und während der Hubbewegung schwenkend und dabei auf den beiden Kurven gleitend geführt. Weiterhin steht das Zwischenglied mit einem der Nocken der Nockenwelle sowie einer Hubübertragungsanordnung für ein Ventil im Eingriff. Die Steuerkurve bestimmt in Abhängigkeit von der Schwenkstellung des veränderlichen Elementes während des Hubes des Nockens die Bewegungsbahn des Zwischengliedes und damit die Größe des von der Hubübertragungsanordnung am Ventil bewirkten Hubes.Previously known from the Scriptures DE 100 61 618 B4 a device for the variable actuation of valves by means of cams. This is arranged in a cylinder head with a stationary mounted camshaft, with valves closing by spring force and together with each associated with each of the valves, positionally guided in the cylinder head Hubübertragungsanordnung. An adjustable for Ventilhubeinstellung element is fixed in the cylinder head, but pivotally mounted. It has one support curve and one control curve in succession in an axial plane. An intermediate member is prismatically supported on the element which is variable in its position, both at the support and at the control cam, under frictional connection, and is guided in a sliding manner during the lifting movement while sliding on the two curves. Furthermore, the intermediate member is in engagement with one of the cams of the camshaft and a Hubübertragungsanordnung for a valve. The cam determines depending on the pivotal position of the variable element during the stroke of the cam, the trajectory of the intermediate member and thus the size of the Hubübertragungsanordnung caused by the valve stroke.

Die konstruktive Gestaltung dieser Ausführung ist eingeschränkt, weil die Stützkurve und die Steuerkurve an dem in seiner Stellung veränderlichen Element nacheinander verlaufend angeordnet sind und dadurch ein bestimmter Abstand der beiden prismatischen Eingriffslinien an der Stützkurve und der Steuerkurve sowie dem Zwischenglied notwendig ist.The structural design of this embodiment is limited because the support curve and the cam are arranged successively extending on the variable in its position element and thereby a certain distance between the two prismatic engagement lines on the support curve and the control cam and the intermediate member is necessary.

Weiterhin vorbekannt aus der DE 100 31 783 A1 ist ein variabler Ventiltrieb für Verbrennungsmotoren mit einer indirekt von einem Nocken über einen am Zylinderkopf direkt oder indirekt schwenkbar gelagerten Schwing- oder Kipphebel bewegten Ventilanordnung, die ein oder mehrere unter Einwirkung einer Feder schließende Ventile aufweist. Der Schwing- oder Kipphebel steht mit einem schwingbeweglich geführten Zwischenhebel im Eingriff, wobei dieser Zwischenhebel weiterhin einerseits mit dem Nocken einer Nockenwelle und andererseits mit einer Steuerkurve eines am Zylinderkopf direkt oder indirekt drehbar gelagerten Stützkörpers gleitend oder wälzend im Eingriff steht. Der Stützkörper bestimmt mit seiner Stellung und dem damit wirksamen Bereich einer Steuerkurve die Größe des Ventilhubes, wobei mittels einer geeigneten Steuerung und eines entsprechenden Aktuators die Winkelstellung des Stützkörpers eingestellt werden kann.Furthermore, previously known from the DE 100 31 783 A1 is a variable valve train for internal combustion engines with a indirectly from a cam via a cylinder head directly or indirectly pivotally mounted rocker or rocker arm moving valve assembly having one or more under the action of a spring closing valves. The rocker arm or rocker arm engages with a swingably guided intermediate lever, this intermediate lever continuing on the one hand with the cam of a camshaft and on the other hand with a control cam of a directly or indirectly rotatably mounted on the cylinder head support body slidably engaged or rolling. The support body determines with its position and the thus effective range of a control cam, the size of the valve, wherein by means of a suitable control and a corresponding actuator, the angular position of the support body can be adjusted.

Nachteilig hierbei ist der komplizierte und aufwendige Aufbau des Verstellmechanismus zur Hubveränderung des Ventilöffnungsbereiches. Außerdem kann mit dem beschriebenen Stand der Technik keine gleichzeitige Verstellung des Ventilhubs und des Ventilöffnungsbereiches durchgeführt werden.The disadvantage here is the complicated and expensive construction of the adjusting mechanism for Hubveränderung the valve opening area. In addition, with the described prior art no simultaneous adjustment of the valve lift and the valve opening area can be performed.

In der nicht vorveröffentlichten Anmeldung DE 10 2004 010 418.2 ist ein variabler Ventiltrieb mit einstellbarem Ventilhub beschrieben, bei dem bei einer Verstellung in Richtung zu geringerem Hub automatisch eine Vorverlagerung des Ventilöffnungsbereiches erfolgt. Dabei steht einerseits ein Zwischenhebel über eine am Zwischenhebel angeordnete Rolle mit einem ein Ventil betätigenden Schwenkhebel und einer an einem schwenkbaren Stützkörper angeordneten Stützkurve und andererseits über eine am Zwischenhebel angeordnete Rolle mit der Nockenkontur der Nockenwelle in Wirkverbindung. An dem Zwischenhebel ist schwenkbar eine Führungsschwinge angeordnet, die an einem mit dem Stützkörper gekoppelten Stellarm gelenkig angeordnet ist.In the not previously published application DE 10 2004 010 418.2 is described a variable valve train with adjustable valve lift, in which automatically takes place in an adjustment in the direction of lower stroke, a forward displacement of the valve opening area. In this case, on the one hand an intermediate lever via a roller arranged on the intermediate lever with a valve-actuating pivot lever and arranged on a pivotable support body supporting curve and on the other hand via a roller arranged on the intermediate lever with the cam contour of the camshaft in operative connection. At the intermediate lever, a guide rocker is pivotally arranged, which is articulated to a coupled to the support body actuating arm.

Nachteilig hierbei ist ein ungünstiger Krafteintrag in den Ventiltrieb, der durch das Verschieben des Zwischenhebels durch die Nockenkontur verursacht wird. Außerdem benötigt diese Lösung einen verhältnismäßig großen Bauraum.The disadvantage here is an unfavorable force input into the valve train, which is caused by the displacement of the intermediate lever by the cam contour. In addition, this solution requires a relatively large amount of space.

Der Erfindung liegt die Aufgabe zugrunde, einen variablen Ventiltrieb für eine Brennkraftmaschine zu schaffen, bei dem bei Reduzierung der auftretenden Kräfte und des benötigten Bauraumes ein Verstellen des Ventilöffnungs- und/oder Ventilschließwinkels in Richtung früh oder spät erfolgt, wobei gleichzeitig ein Verstellen der Ventilhubhöhe erfolgen kann.The invention has for its object to provide a variable valve train for an internal combustion engine in which an adjustment of the valve opening and / or valve closing angle takes place in the direction of early or late in reducing the forces and the required installation space, at the same time carried out adjusting the valve lift can.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Patentanspruches 1 gelöst.This object is achieved by the characterizing features of claim 1.

Bei einem variablen Ventiltrieb für Verbrennungskraftmaschinen, bestehend aus wenigstens einer Nockenwelle, die über Übertragungsglieder mit einem Schwenkhebel zur Betätigung der Ventile und mit einem Stützkörper zur Ventilhubverstellung in Wirkverbindung steht, ist ein Zwischenglied eines Übertragungsgliedes einerseits zweifach an dem Stützkörper und andererseits an dem Schwenkhebel abstützend verschiebbar gelagert. Dabei steht das Zwischenglied erstens über eine an dem Zwischenglied angeordnete. Stützkurve mit einer am Stützkörper angeordneten Stützfläche und zweitens mit der Steuerkurve des Stützkörpers und drittens über eine an dem Zwischenglied angeordnete Außenkonturfläche mit dem Schwenkhebel in Eingriff. Weiterhin steht das Zwischenglied indirekt über eine an einer Schwinge angeordneten Rolle mit dem Nocken der Nockenwelle in Wirkverbindung, wobei die schwenkbare Schwinge über einen daran angeordneten Hebel gelenkig mit dem Zwischenglied verbunden ist.In a variable valve train for internal combustion engines, consisting of at least one camshaft, which is operatively connected via transmission members with a pivot lever for actuating the valves and a support body for valve lift, an intermediate member of a transmission member on the one hand twice on the support body and on the other hand on the pivot lever supporting displaced stored. In this case, the intermediate member is firstly arranged on the intermediate member on a. Support curve with a support surface arranged on the support surface and secondly with the control cam of the support body and thirdly via an arranged on the intermediate member outer contour surface with the pivot lever into engagement. Furthermore, the intermediate member is indirectly connected via an arranged on a rocker roller with the cam of the camshaft in operative connection, wherein the pivotable rocker is pivotally connected thereto via a lever connected to the intermediate member.

Zur Ventilhubverstellung und/oder zur Verstellung des Ventilöffnungs- und/oder -schließwinkels ist die Schwinge gelenkig an dem verschwenkbaren Stützkörper angeordnet. Eine Variante zur Ventilhubverstellung und/oder zur Verstellung des Ventilöffnungs- und/oder -schließwinkels sieht vor, den Stützkörper fest am Zylinderkopf anzuordnen und die nunmehr nicht mehr mit dem Stützkörper verbundene Schwinge mit einer Verstelleinrichtung zum Verschwenken der Schwinge zu versehen.For valve lift adjustment and / or for adjusting the valve opening and / or closing angle, the rocker is articulated to the pivotable support body. A variant of the valve lift adjustment and / or adjustment of Ventilöffnungs- and / or -schließwinkels provides to arrange the support body fixed to the cylinder head and to provide the now no longer connected to the support body rocker with an adjustment for pivoting the rocker.

Der Vorteil der erfindungsgemäßen Vorrichtung besteht in einer kompakten Bauweise, die es ermöglicht, die Bauteile wie Nockenwelle, Stützkörper, Schwenkhebel und Übertragungsglieder auf engsten Raum zu konzentrieren.The advantage of the device according to the invention consists in a compact design, which makes it possible to concentrate the components such as camshaft, support body, pivot lever and transmission elements in the narrowest space.

Ein weiterer wesentlicher Vorteil der erfindungsgemäßen Lösung besteht darin, dass der Kraftübertragungspunkt von dem Zwischenglied auf den Stützkörper immer zwischen dem Anlagepunkt der Stützkurve des Zwischengliedes an dem Zapfen des Stützkörpers und dem Anlagepunkt der an dem Zwischenglied angeordneten Rolle und der Steuerkurve des Stützkörpers liegt. Dadurch wird erreicht, dass das Zwischenglied ständig an den Stützkörper gepresst wird. Ein mögliches Herausschwenken des Zwischengliedes aus der Vorrichtung wird dadurch vermieden. Gleichzeitig werden durch diese Anordnung die zu übertragenden Kräfte minimiert.Another significant advantage of the solution according to the invention is that the force transmission point of the intermediate member on the support body is always between the contact point of the support curve of the intermediate member on the pin of the support body and the contact point of the arranged on the intermediate member and the control cam of the support body. This ensures that the intermediate member is constantly pressed against the support body. A possible swing out the intermediate member of the device is thereby avoided. At the same time, the forces to be transmitted are minimized by this arrangement.

Durch die Kopplung des Zwischengliedes mit dem verschwenkbaren Stützkörper über eine Schwinge bzw. durch Anordnung einer Verstelleinrichtung an der Schwinge bei einem fest am Zylinderkopf angeordneten Stützkörper in Verbindung mit einem an der Schwinge gelenkig daran angeordneten Hebel erfolgt bei einer Hubverstellung des Ventils eine automatische Verlagerung des Ventilschließwinkels. Die Steuerkurve am Stützkörper, welche die Ventilöffnung mitbestimmt, kann dabei so ausgelegt sein, dass durch das Verlagern der Steuerkurve und des mit dem Stützkörper gekoppelten Zwischengliedes gleichzeitig eine Veränderung der Hubhöhe und der Lage des Ventilöffnungs- und/oder -schließwinkels erfolgt.By coupling the intermediate member with the pivotable support body via a rocker or by arranging an adjustment of the rocker in a fixedly arranged on the cylinder head support body in conjunction with a hinged thereto on the rocker arm is carried out at a stroke adjustment of the valve, an automatic displacement of the valve closing angle , The cam on the support body, which co-determines the valve opening, can be designed so that at the same time a change in the lifting height and the position of the Ventilöffnungs- and / or -schließwinkels done by moving the control cam and coupled to the support member intermediate member.

Ein weiterer Vorteil der erfindungsgemäßen Lösung ist, dass durch die Gestaltung der Steuerkurve und der Stützkurve und der Außenkonturfläche des Zwischengliedes in Verbindung mit der Verstellung des Zwischengliedes durch die verschwenkbare Schwinge der Ventilöffnungswinkel nahezu konstant gehalten werden kann, während der Schließwinkel zwischen früh und spät verstellbar ist. Die Hubhöhe der Ventilerhebungskurve ist dabei ebenfalls veränderbar, wobei die Minimierung des Ventilhubes gering gehalten werden kann. Dies ist insbesondere für die Anwendung des erfindungsgemäßen Ventiltriebs für ein Einlassventil vorteilhaft. In einer Anwendung als Trieb für ein Auslassventil ist es beispielsweise vorteilhaft, den Schließwinkel des Auslassventils nahezu konstant zu lassen, während der Öffnungswinkel des Auslassventils nach früh oder spät verstellt wird. Hierbei kann ebenfalls eine Variation des Ventilhubs erfolgen.Another advantage of the inventive solution is that the valve opening angle can be kept almost constant by the design of the control cam and the support curve and the outer contour surface of the intermediate member in conjunction with the adjustment of the intermediate member by the pivotable rocker, while the closing angle between early and late is adjustable , The lifting height of the valve lift curve is also variable, wherein the minimization of the valve lift can be kept low. This is advantageous in particular for the application of the valve drive according to the invention for an inlet valve. In an application as a drive for an exhaust valve, for example, it is advantageous to leave the closing angle of the exhaust valve almost constant, while the opening angle of the exhaust valve is adjusted to early or late. This can also be done a variation of the valve.

Weitere vorteilhafte Ausgestaltungen sind in den Unteransprüchen beschrieben, sie werden in der Beschreibung zusammen mit ihren Wirkungen erläutert.Further advantageous embodiments are described in the subclaims, they are explained in the description together with their effects.

Anhand von Zeichnungen wird die Erfindung nachfolgend an Ausführungsbeispielen näher beschrieben. In den dazugehörigen Zeichnungen zeigen:

Fig. 1:
eine schematische Darstellung des erfindungsgemäßen Ventiltriebes bei einer maximalen Hubeinstellung und bei einem geschlossenen Ventil,
Fig. 2:
eine schematische Darstellung des erfindungsgemäßen Ventiltriebes bei einer maximalen Hubeinstellung und bei einem vollständig geöffneten Ventil und
Fig. 3:
eine schematische Darstellung des erfindungsgemäßen Ventiltriebes bei einer minimalen Hubeinstellung und bei einem geöffneten Ventil,
Fig. 4:
eine Variante des erfindungsgemäßen Ventiltriebes bei einer maximalen Hubeinstellung und bei einem geschlossenen Ventil und
Fig. 5:
eine schematische Darstellung des erfindungsgemäßen Ventiltriebes bei einer maximalen Hubeinstellung und bei einem vollständig geöffneten Ventil gemäß Figur 4.
The invention will be described in more detail below with reference to exemplary embodiments with reference to drawings. In the accompanying drawings show:
Fig. 1:
a schematic representation of the valve gear according to the invention at a maximum stroke and a closed valve,
Fig. 2:
a schematic representation of the valve gear according to the invention at a maximum stroke setting and a fully open valve and
3:
a schematic representation of the valve gear according to the invention with a minimum stroke and an open valve,
4:
a variant of the valve gear according to the invention at a maximum stroke and a closed valve and
Fig. 5:
a schematic representation of the valve gear according to the invention at a maximum stroke setting and a fully open valve according to Figure 4.

Der erfindungsgemäße variable Ventiltrieb für Verbrennungskraftmaschinen wird erläutert am Beispiel eines Einlassventils. Die erfindungsgemäße Lösung ist auch einsetzbar für die Auslassventile einer Brennkraftmaschine. Der Ventiltrieb weist eine Nockenwelle 1 mit einem Nocken 2 auf, der unter Zwischenschaltung eines Übertragungsmechanismus einen Schwenkhebel 14 und damit ein Ventil 17 bewegt, welches mittels Federkraft verschließbar ist und geschlossen gehalten wird. Von dem Ventil 17 ist nur das Schaftende dargestellt, welches an einem im Schwenkhebel 14 angeordneten Spielausgleichselement 16 anliegt. Der Schwenkhebel 14 ist auf einer im Zylinderkopf geführten Achse unter Zwischenschaltung einer Exzenterbüchse 19 gelagert. Die schwenkbare Exzenterbüchse 19 dient zur zusätzlichen Anpassung der Schwenkhebelposition im Zusammenwirken mit dem Spielausgleichselement 16.The variable valve drive for internal combustion engines according to the invention is explained using the example of an intake valve. The solution according to the invention can also be used for the exhaust valves of an internal combustion engine. The valve train has a camshaft 1 with a cam 2 which, with the interposition of a transmission mechanism, moves a pivoting lever 14 and thus a valve 17 which can be closed by means of spring force and is kept closed. Of the valve 17, only the shaft end is shown, which rests against a arranged in the pivot lever 14 clearance compensation element 16. The pivot lever 14 is mounted on a guided in the cylinder head axis with the interposition of an eccentric bushing 19. The pivotable eccentric bushing 19 serves for additional adaptation of the pivot lever position in cooperation with the clearance compensation element 16.

Der verlagerbare Übertragungsmechanismus besteht im Wesentlichen aus einem Zwischenglied 9 und einem am Zwischenglied 9 gelenkig angeordneten Hebel 10, der über eine daran gelenkig angeordnete verschwenkbare Schwinge 3. An der Schwinge 3 ist eine Rolle 4 angeordnet, die in Wirkverbindung mit der Kontur des Nockens 2 der Nockenwelle 1 steht.The displaceable transmission mechanism consists essentially of an intermediate member 9 and an articulated on the intermediate member 9 lever 10, which is articulated about a pivotally mounted rocker 3. On the rocker 3, a roller 4 is arranged, in operative connection with the contour of the cam 2 of Camshaft 1 is stationary.

Das Verschwenken der Schwinge 3 erfolgt erfindungsgemäß auf zwei verschiedene Arten. Entsprechend einer ersten Ausführungsvariante ist ein Stützkörper 5 schwenkbar um die Schwenkachse 18 an dem Zylinderkopf angeordnet und, wie in Figur 1 bis 3 dargestellt, mit der Schwinge 3 verbunden. Beim Verschwenken des Stützkörpers 5 durch eine Exzenterverstellung 7 wird gleichzeitig die Schwinge 3 verschwenkt, wodurch eine Verlagerung des Zwischengliedes 9 am Stützkörper 5 zur Ventilhubverstellung und/oder zur Verstellung des Ventilöffnungs- und/oder -schließwinkels erfolgt.The pivoting of the rocker 3 is carried out according to the invention in two different ways. According to a first embodiment variant, a supporting body 5 pivotally mounted about the pivot axis 18 on the cylinder head and, as shown in Figure 1 to 3, connected to the rocker 3. When pivoting the support body 5 by an eccentric adjustment 7, the rocker 3 is simultaneously pivoted, whereby a displacement of the intermediate member 9 on the support body 5 for valve lift adjustment and / or for adjusting the valve opening and / or closing angle.

Eine Variante der erfindungsgemäßen Lösung sieht vor, den Stützkörper 5, wie in Figur 4 und 5 dargestellt, fest am Zylinderkopf anzuordnen. Die Schwinge 3 ist dabei nicht mehr mit dem Stützkörper verbunden. Das Verschwenken der Schwinge 3 und damit eine Verlagerung des Zwischengliedes 9 am Stützkörper 5 zur Ventilhubverstellung und/oder zur Verstellung des Ventilöffnungs- und/oder -schließwinkels erfolgt durch eine Verstelleinrichtung 20, die an der Schwinge 3 angeordnet ist. Die Verstellvorrichtung 20 ist dabei vorzugsweise eine Exzenterverstellung.A variant of the solution according to the invention provides to arrange the support body 5, as shown in Figure 4 and 5, fixed to the cylinder head. The rocker 3 is no longer connected to the support body. The pivoting of the rocker 3 and thus a displacement of the intermediate member 9 on the support body 5 for valve lift and / or for adjusting the Ventilöffnungs- and / or -schließwinkels carried by an adjusting device 20 which is arranged on the rocker 3. The adjusting device 20 is preferably an eccentric adjustment.

Bei beiden Varianten ist das Zwischenglied 9 einerseits an den Stützkörper 5 und andererseits am Schwenkhebel 14 abstützend gelagert. Die Lagerung des Zwischengliedes 9 am Stützkörper 5 erfolgt dabei zum einen an einer am Stützkörper 5 angeordneten Stützfläche und zum anderen an einer am Stützkörper 5 angeordneten Steuerkurve 11. Die am Stützkörper 5 angeordnete Stützfläche ist dabei vorzugsweise die Außenfläche eines am Stützkörpers 5 angeordneten Zapfens 6, an der sich die am Zwischenglied 9 angeordnete Stützkurve 13 abstützt. Gemäß der Variante eins, bei der der Stützkörper 5 verschwenkbar ist und die Schwinge 3 am Stützkörper 5 angeordnet ist, ist der Zapfen 6 um die Schwenkachse 18 des Stützkörpers 5 angeordnet.In both variants, the intermediate member 9 is supported on the one hand on the support body 5 and on the other hand on the pivot lever 14. The support of the intermediate member 9 on the support body 5 is effected on the one hand on a support body 5 arranged support surface and the other on a support body 5 arranged on the control cam 11. The supporting body 5 arranged support surface is preferably the outer surface of a support body 5 arranged on the pin 6, at which the arranged on the intermediate member 9 support curve 13 is supported. According to the variant one, in which the support body 5 is pivotable and the rocker 3 is arranged on the support body 5, the pin 6 is arranged about the pivot axis 18 of the support body 5.

Am Zwischenglied 9 ist eine Rolle 8 angeordnet, die mit der am Stützkörper 5 angeordneten Steuerkurve 11 in Verbindung steht. Über eine am Zwischenglied 9 angeordnete Außenkonturfläche 12 stützt sich das Zwischenglied 9 auf einer am Schwenkhebel 14 angeordneten Rolle 15 ab. Durch die nicht dargestellte Ventilfeder wird der Schwenkhebel 14 entgegen der Uhrzeigerrichtung verschwenkt und damit das Zwischenglied 9 über die Rolle 15 gegen den Stützkörper 5 gedrückt. Damit ist das Zwischenglied 9 sicher zwischen dem Stützkörper 5 und dem Schwenkhebel 14 gelagert und wird entsprechend dem Eingriff der Kontur des Nockens 2 entlang der Steuerkurve 11 des Stützkörpers 5 verlagert.At the intermediate member 9, a roller 8 is arranged, which is in communication with the support body 5 arranged on the control cam 11. About an intermediate member 9 arranged on the outer contour surface 12, the intermediate member 9 is supported on a arranged on the pivot lever 14 roller 15 from. By the valve spring, not shown, the pivot lever 14 is pivoted counterclockwise and thus pressed the intermediate member 9 via the roller 15 against the support body 5. Thus, the intermediate member 9 is secure between the support body 5 and the pivot lever fourteenth mounted and is displaced according to the engagement of the contour of the cam 2 along the control cam 11 of the support body 5.

Die Wirkungsweise der erfindungsgemäßen Lösung ist folgende:The mode of action of the solution according to the invention is the following:

Die in Figur 1 dargestellte erste Variante der erfindungsgemäßen Lösung zeigt ein geschlossenes Ventil 17 bei einem maximal eingestellten Ventilhub. Dabei hat die Exzenterverstellung 7 den Stützkörper 5 um die Schwenkachse 18 entgegen der Uhrzeigerrichtung in die dargestellte Lage verschwenkt und die Rolle 4 der Schwinge 3 steht mit dem Grundkreis des Nockens 2 im Eingriff. Zum Öffnen des Ventils wird der in Figur 1 dargestellte Nocken 2 in Uhrzeigerrichtung gedreht. Durch Drehen der Nockenwelle 1, wie in Figur 2 dargestellt, wird die Rolle 4 durch den Nocken 2 verdrängt, wodurch die Schwinge 3 um ihren Anlenkpunkt am Stützkörper 5 im Uhrzeigersinn verschwenkt wird. Durch das Verschwenken der Schwinge 3 wird das über den Hebel 10 mit der Schwinge 3 gelenkig verbundene Zwischenglied 9 über die Rolle 8 entlang der Steuerkurve 11 des Stützkörpers 5 verlagert. Bei dieser Verlagerung gleitet die Stützkurve 13 des Zwischengliedes an der Oberfläche des Zapfens 6 entlang. Gleichzeitig drückt die Außenkonturfläche 12 des Zwischengliedes 9 beim Gleiten über die Rolle 15 den Schwenkhebel 14 nach unten, wobei das Ventil 17 verlagert wird und den Einlasskanal freigibt. Aufgrund der Stellung und der Gestaltung der am Stützkörper 5 angeordneten Steuerkurve 11 werden beim Gleiten der Rolle 8 des Zwischengliedes 9 an der Steuerkurve 11 unterschiedliche Hubverstellungen des Ventils 17 erzielt. In Figur 2 ist ein vollständig geöffnetes Ventil 17 bei einer maximalen Hubeinstellung dargestellt.The illustrated in Figure 1 first variant of the solution according to the invention shows a closed valve 17 at a maximum set valve lift. In this case, the eccentric adjustment 7, the support body 5 has pivoted about the pivot axis 18 counterclockwise in the position shown and the roller 4 of the rocker 3 is connected to the base circle of the cam 2 in engagement. To open the valve, the cam 2 shown in Figure 1 is rotated in the clockwise direction. By rotating the camshaft 1, as shown in Figure 2, the roller 4 is displaced by the cam 2, whereby the rocker 3 is pivoted about its point of articulation on the support body 5 in a clockwise direction. By pivoting the rocker 3, the articulated via the lever 10 to the rocker arm 3 intermediate member 9 is moved over the roller 8 along the control cam 11 of the support body 5. During this displacement, the support curve 13 of the intermediate member slides along the surface of the pin 6. At the same time the outer contour surface 12 of the intermediate member 9 presses when sliding over the roller 15, the pivot lever 14 down, wherein the valve 17 is displaced and releases the inlet channel. Due to the position and the design of the supporting body 5 arranged on the control cam 11 11 different stroke adjustments of the valve 17 are achieved when sliding the roller 8 of the intermediate member 9 on the control cam. FIG. 2 shows a fully opened valve 17 at a maximum stroke setting.

In Figur 3 ist ein geöffnetes Ventil 17 bei einem minimalen eingestellten Ventilhub dargestellt. Durch Verstellen der Exzenterverstellung 7 wird der in Figur 1 und 2 dargestellte Stützkörper 5 in Uhrzeigerrichtung um die Schwenkachse 18 verschwenkt. Damit ändert sich auch die Lage der Steuerkurve 11 und die Lage des daran in Eingriff stehenden Zwischengliedes 9, so dass bei einem vollständigen Eingriff des Nockens 2 auf die Rolle 4 der Schwenkhebel 14 nur um einen minimalen Betrag verschwenkt wird. Durch die Kopplung des Zwischengliedes 9 mit dem Stützkörper 5 über die Schwinge 3 und dem Hebel 10 wird beim Verschwenken des Stützkörpers 5 das Zwischenglied 9 ebenfalls so verlagert, dass bei einer variabel eingestellten Ventilhubhöhe gleichzeitig der Ventilöffnungs- und/oder -schließwinkel verstellt werden können.In Figure 3, an open valve 17 is shown at a minimum set valve lift. By adjusting the eccentric adjustment 7, the support body 5 shown in Figures 1 and 2 is pivoted in the clockwise direction about the pivot axis 18. This also changes the position of the control cam 11 and the position of the intermediate member 9 engaged therewith so that upon complete engagement of the cam 2 with the roller 4, the pivoting lever 14 is pivoted only by a minimum amount. By the coupling of the intermediate member 9 with the support body 5 via the rocker 3 and the lever 10, the intermediate member 9 is also displaced during pivoting of the support body 5, that at a variably adjusted valve lift height at the same time the valve opening and / or closing angle can be adjusted.

In Figur 4 und 5 ist, wie oben beschrieben, eine Variante der erfindungsgemäßen Lösung dargestellt. Dabei sind gleiche Bauteile mit den selben Bezugszeichen versehen. Beim Öffnen und Schließen des Ventils 17 wird, analog wie zu den Figuren 1 bis 3 beschrieben, durch den Nocken 2 und über die Schwinge 3 und den Hebel 10 das Zwischenglied 9 entlang der Steuerkurve 11 des Stützkörpers 5 verlagert. Der Stützkörper 5 ist aber fest mit dem Zylinderkopf verbunden. Die Einstellung von unterschiedlichen Ventilhüben und/oder die Verstellung des Ventilöffnungs- und/oder - schließwinkels erfolgt durch die Exzenterverstellung der an der Schwinge 3 angeordneten Verstelleinrichtung 20. Durch die Exzenterverstellung der Verstelleinrichtung 20 wird die Schwinge 3 verlagert und somit über den an der Schwinge 3 angelenkten Hebel 10 die Lage des Zwischenglied 9 an der Steuerkurve 11 des Stützkörpers 5 verändert. Entsprechend Figur 4 ist das Ventil 17 geschlossen, während gemäß Figur 5 das Ventil 17 geöffnet ist.In FIGS. 4 and 5, as described above, a variant of the solution according to the invention is shown. The same components are provided with the same reference numerals. When opening and closing the valve 17, the intermediate member 9 along the control cam 11 of the support body 5 is displaced by the cam 2 and the rocker 3 and the lever 10, analogously as described to Figures 1 to 3. The support body 5 is firmly connected to the cylinder head. The adjustment of different valve lifts and / or the adjustment of the Ventilöffnungs- and / or - closing angle is done by the Exzenterverstellung arranged on the rocker 3 adjusting 20. The eccentric adjustment of the adjusting 20, the rocker 3 is displaced and thus on the on the rocker. 3 hinged lever 10, the position of the intermediate member 9 on the control cam 11 of the support body 5 changed. According to Figure 4, the valve 17 is closed, while according to Figure 5, the valve 17 is opened.

Aufstellung der verwendeten BezugszeichenList of used reference numbers

11
Nockenwellecamshaft
22
Nockencam
33
Schwingewing
44
Rollerole
55
Stützkörpersupport body
66
Zapfenspigot
77
Exzenterverstellungeccentric
88th
Rollerole
99
Zwischengliedintermediary
1010
Hebellever
1111
Steuerkurvecam
1212
AußenkonturflächeOuter contour surface
1313
Stützkurvesupport curve
1414
Schwenkhebelpivoting lever
1515
Rollerole
1616
SpielausgleichselementLash adjuster
1717
VentilValve
1818
Schwenkachseswivel axis
1919
Exzenterbüchseeccentric
2020
Verstelleinrichtungadjustment

Claims (10)

Variabler Ventiltrieb für Verbrennungskraftmaschinen mit wenigstens einer Nockenwelle (1) und im Zylinderkopf angeordnetem Schwenkhebel (14), der in Wirkverbindung mit einem durch Federkraft schließenden Ventil (17) steht, mit folgender Bauart: - ein am Zylinderkopf angeordneter Stützkörper (5) weist eine Steuerkurve (11) zur Ventilhubeinstellung auf, - ein Zwischenglied (9) ist zwischen dem Stützkörper (5) und dem Schwenkhebel (14) geführt angeordnet, dadurch gekennzeichnet, dass
das Zwischenglied (9) erstens über eine an dem Zwischenglied (9) angeordnete Stützkurve (13) mit einer am Stützkörper (5) angeordneten Stützfläche, zweitens mit der Steuerkurve (11) des Stützkörpers (5) und drittens über eine an dem Zwischenglied (9) angeordnete Außenkonturfläche (12) mit dem Schwenkhebel (14) in Eingriff steht und über einen Nocken (2) der Nockenwelle (1) verlagerbar ist, wobei der Nocken (2) über eine verschwenkbare Schwinge (3) und über einen gelenkig zwischen dem Zwischenglied (9) und der Schwinge (3) angeordneten Hebel (10) in Wirkverbindung mit dem Zwischenglied (9) steht.Variable valve train for internal combustion engines with at least one camshaft (1) and pivoting lever (14) arranged in the cylinder head and in operative connection with a spring-closing valve (17) of the following type: a support body (5) arranged on the cylinder head has a control cam (11) for the valve stroke adjustment, - An intermediate member (9) is arranged guided between the support body (5) and the pivot lever (14), characterized in that
the intermediate member (9) firstly via a supporting cam (13) arranged on the intermediate member (9) with a support surface arranged on the supporting body (5), secondly with the control cam (11) of the supporting body (5) and thirdly via a support member (9) ) arranged outer surface (12) with the pivot lever (14) is engaged and via a cam (2) of the camshaft (1) is displaceable, wherein the cam (2) via a pivotable rocker (3) and via a hinged between the intermediate member (9) and the rocker (3) arranged lever (10) is in operative connection with the intermediate member (9). Variabler Ventiltrieb nach Anspruch 1,
dadurch gekennzeichnet, dass
die am Stützkörper (5) angeordnete Stützfläche durch einen am Stützkörper (5) angeordneten Zapfen (6) gebildet wird, an dem das Zwischenglied (9) über die Stützkurve (13) abstützend gelagert ist.Variable valve train according to claim 1,
characterized in that
the support surface arranged on the support body (5) is formed by a pin (6) arranged on the support body (5), on which the intermediate member (9) is supported so as to support the support curve (13). Variabler Ventiltrieb nach Anspruch 1 und 2,
dadurch gekennzeichnet, dass
das Zwischenglied (9) über eine am Zwischenglied (9) angeordnete Rolle (8) mit der Steuerkurve (11) des Stützkörpers (5) in Eingriff steht.Variable valve drive according to claim 1 and 2,
characterized in that
the intermediate member (9) via a on the intermediate member (9) arranged roller (8) with the control cam (11) of the support body (5) is engaged. Variabler Ventiltrieb nach Anspruch 1 bis 3,
dadurch gekennzeichnet, dass
an der Schwinge (3) eine Rolle (4) angeordnet ist, die in Wirkverbindung mit der Kontur des Nockens (2) steht.Variable valve train according to claim 1 to 3,
characterized in that
on the rocker (3) a roller (4) is arranged, which is in operative connection with the contour of the cam (2). Variabler Ventiltrieb nach Anspruch 1 bis 4,
dadurch gekennzeichnet, dass
die Außenkonturfläche (12) des Zwischengliedes (9) über eine am Schwenkhebel (14) angeordnete Rolle (15) mit dem Schwenkhebel (14) in Wirkverbindung steht.Variable valve train according to claim 1 to 4,
characterized in that
the outer contour surface (12) of the intermediate member (9) is operatively connected to the pivot lever (14) via a roller (15) arranged on the pivot lever (14). Variabler Ventiltrieb nach Anspruch 1 bis 5,
dadurch gekennzeichnet, dass
die Schwinge (3) gelenkig an dem um die Schwenkachse (18) schwenkbar am Zylinderkopf angeordneten Stützkörper (5) angeordnet ist.Variable valve train according to claim 1 to 5,
characterized in that
the rocker (3) is arranged articulated on the support body (5) arranged pivotably about the pivot axis (18) on the cylinder head. Variabler Ventiltrieb nach Anspruch 1 bis 6,
dadurch gekennzeichnet, dass
der Zapfen (6) in der Schwenkachse (18) am Stützkörper (5) angeordnet ist.Variable valve train according to claim 1 to 6,
characterized in that
the pin (6) in the pivot axis (18) on the support body (5) is arranged. Variabler Ventiltrieb nach Anspruch 1 bis 7,
dadurch gekennzeichnet, dass
zum Verschwenken des Stützkörpers (5) um die Schwenkachse (18) eine auf den Stützkörper (5) wirkende Exzenterverstellung (7) angeordnet ist.Variable valve train according to claim 1 to 7,
characterized in that
for pivoting the support body (5) about the pivot axis (18) acting on the supporting body (5) eccentric adjustment (7) is arranged. Variabler Ventiltrieb nach Anspruch 1 bis 5,
dadurch gekennzeichnet, dass
der Stützkörper (5) fest am Zylinderkopf angeordnet ist und die Schwinge (3) zur Ventilhubverstellung und/oder zur Verstellung des Ventilöffnungs- und/oder -schließwinkels mit einer Verstelleinrichtung (20) zum Verschwenken der Schwinge (3) versehen ist.Variable valve train according to claim 1 to 5,
characterized in that
the support body (5) is fixedly arranged on the cylinder head and the rocker (3) for valve lift adjustment and / or for adjusting the Ventilöffnungs- and / or -schließwinkels with an adjusting device (20) for pivoting the rocker (3) is provided. Variabler Ventiltrieb nach Anspruch 9,
dadurch gekennzeichnet, dass
die Verstelleinrichtung (20) eine Exzenterverstellung ist.Variable valve train according to claim 9,
characterized in that
the adjusting device (20) is an eccentric adjustment.
EP06013565A 2005-07-28 2006-06-30 Variable valve driving gear for internal combustion engines Not-in-force EP1748160B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005035315A DE102005035315B4 (en) 2005-07-28 2005-07-28 Variable valve train for internal combustion engines

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EP1748160A1 true EP1748160A1 (en) 2007-01-31
EP1748160B1 EP1748160B1 (en) 2008-01-23

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Country Link
US (1) US7367298B2 (en)
EP (1) EP1748160B1 (en)
AT (1) ATE384858T1 (en)
DE (2) DE102005035315B4 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
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CN106640256A (en) * 2016-12-05 2017-05-10 广州汽车集团股份有限公司 Valve-stroke-continuous-variable system and automobile with the same
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ATE384858T1 (en) 2008-02-15
DE102005035315A1 (en) 2007-02-01
US7367298B2 (en) 2008-05-06
DE502006000309D1 (en) 2008-03-13
EP1748160B1 (en) 2008-01-23
US20070022989A1 (en) 2007-02-01

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