EP1590554A1 - Fully variable mechanical valve drive mechanism for a piston-type internal combustion engine comprising adjustable valve play compensation - Google Patents

Fully variable mechanical valve drive mechanism for a piston-type internal combustion engine comprising adjustable valve play compensation

Info

Publication number
EP1590554A1
EP1590554A1 EP04701291A EP04701291A EP1590554A1 EP 1590554 A1 EP1590554 A1 EP 1590554A1 EP 04701291 A EP04701291 A EP 04701291A EP 04701291 A EP04701291 A EP 04701291A EP 1590554 A1 EP1590554 A1 EP 1590554A1
Authority
EP
European Patent Office
Prior art keywords
play compensation
eccentric sleeve
valve
cylinder head
valve train
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
EP04701291A
Other languages
German (de)
French (fr)
Other versions
EP1590554B1 (en
Inventor
Thomas Koch
Markus Duesmann
Sven Lauer
Helge Djie
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.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and Co KG
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 FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Publication of EP1590554A1 publication Critical patent/EP1590554A1/en
Application granted granted Critical
Publication of EP1590554B1 publication Critical patent/EP1590554B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—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

  • Mechanical valve drives have a camshaft, a stroke predetermined by the geometry of a cam being transmitted to the gas exchange valve to be actuated via a rocker arm.
  • the arrangement of adjustable stroke transmission means between the cam and rocker arm makes it possible to make a mechanical valve train fully variable.
  • Fully variable mechanical valve train for a piston combustion. Engine are known for example from DE 100 06 018A or WO 02 / 053881A.
  • a stroke transmission means formed from a plurality of interacting partial elements is arranged between a drive means, for example in the form of a cam of a camshaft, and the gas exchange valve to be actuated, which enables the full stroke predetermined by the cam contour to be set between a zero and a correspondingly arranged adjustable control element. Stroke and the full stroke according to the operational requirements.
  • the stroke transmission means acts on a rocker arm, which is supported with its free end on the shaft of the gas exchange valve to be actuated and with its other end is mounted on a, preferably hydraulically actuated, play compensation element arranged on the cylinder head, forming a pivot bearing.
  • the invention has for its object to improve such multiple sub-elements valve trains in that unavoidable, proper function disadvantageously influencing manufacturing tolerances can be compensated.
  • the object is achieved according to the invention with a variably adjustable valve train which has the features specified in claim 1. Characterized in that the play compensation element is connected to an adjusting means, there is the possibility of changing the geometric assignment of the rocker arm to the stroke transmission means by shifting the pivot bearing of the rocker arm and thus achieving perfect kinematics.
  • the means for the adjustment is formed by an eccentric sleeve connected to the cylinder head as a receptacle for the play compensation element.
  • the eccentric sleeve is rotatably arranged.
  • an eccentric sleeve with an eccentricity is provided, which corresponds to the expected maximum manufacturing-related dimensional deviation.
  • a stepless adjustment of the pivot axis of the pivot element can then be effected with respect to the fixed axis of rotation of the guide element.
  • means are provided for fixing the eccentric sleeve to the cylinder head. These can be formed, for example, by a corresponding tab on the eccentric sleeve, which engages in the cylinder head. It is also possible to provide the eccentric sleeve with an axially extending groove into which a steel ball is pressed after adjustment, so that the eccentric sleeve is fixed while deforming the base material of the cylinder head.
  • Fig. 3 is a plan view of the arrangement acc. Fig. 2,
  • FIG. 4 shows a perspective view of a play compensation element with an eccentric sleeve.
  • the valve train shown schematically in Fig. 1 consists essentially of a gas exchange valve 1, which is held in the closed position via a valve spring 2. Associated with the free end 3 of the valve stem of the gas exchange valve 1 is a stroke transmission means 4, which is made up of a plurality of interacting partial elements which can be partially adjusted in relation to one another and which acts on a rocker arm 5.
  • stroke transmission means in the sense of the invention, all are between the drive means 14 (camshaft of a camshaft or also electrical or hydraulic actuators) and one the rocker arm 5 acting directly on the gas exchange valve 1 and interacting with each other are sub-elements. By adjusting sub-elements relative to one another, their mechanical-geometric interaction can be changed, so that with a stroke that is fixed, for example, by a cam, the actual stroke that acts on the gas exchange valve 1 via the rocker arm 5 is variable between “zero” and “full stroke” can be adjusted.
  • a guide element 11 with a control cam 12 and a pivot element 8 are essentially provided as sub-elements of the stroke transmission means 4.
  • the rocker arm 5 is supported by a lash adjuster 6 to compensate for the valve lash on the cylinder head or engine block and rests with its free end 7 on the shaft end 3 of the gas exchange valve 1.
  • the rocker arm 5 is supported on the play compensation element 6 at the same time forms a pivot bearing 6.1 for the rocker arm 5.
  • the pivot element 8 is mounted on the rocker arm 5 between the pivot bearing 6.1 and the support on the shaft end 3 of the gas exchange valve 1 so that it can pivot back and forth about a pivot axis 9.
  • the pivot element 8 has on its
  • Pivot axis 9 facing away from the free end of a guide roller 10.
  • the guide element 11 with its cam 12 for the guide roller 10 is also assigned to the pivot element 8.
  • the guide element 11 is adjustable on the cylinder head or engine block about a fixed axis of rotation in the direction of the double arrow 13 with the aid of an actuator relative to the gas exchange valve 1, so that, as will be explained in more detail below, 10 different rolling areas can be specified for the rolling of the guide roller ,
  • the pivot element 8 is further provided between the guide roller 10 and the pivot axis 9 with a pressure roller 8.1, on which a drive means in the form of a cam 14 of a camshaft acts with its control contour 15.
  • the pivoting element 8 is pressed against the control contour 15 of the cam 14 via a return spring 16, for example in the form of the winding or spiral spring shown here.
  • the gas exchange valve is shown in the closed position.
  • the pivot element 8 is pivoted about its axis of rotation 9. Since the guide roller 10 rolls on the control contour 12, the guide roller 10 can only follow the control contour 12 if the guide element 11 is positioned accordingly, so that the rocker arm 5 supported on the swivel bearing 6.1 is also supported by the force between cam 14 and pressure roller 8.1 is articulated downwards in the same direction as arrow 17 and this
  • Gas exchange valve 1 is opened against the force of the valve spring 2.
  • the control contour 12 of the guide element 11 now has a first contour region I, which is shaped as a circular path, the center of which coincides with the axis of rotation of the guide element 11 and the pivot axis of the pivot element 8 when the gas exchange valve is closed. This has the effect that when the cam 14 rotates the pivoting element can pivot back and forth, but no force effect on the
  • the axis of rotation of the guide element 11 and the pivot axis 9 of the pivot element 8 must ideally coincide when the gas exchange valve is closed. Since the axis of rotation of the guide element 11 is stationary on the cylinder head, but the position of the pivot axis 9 of the pivot element 8 can deviate from the ideal position due to a chaining of manufacturing tolerances, as shown in FIG. 2, the play compensation element 6 is provided with means for adjusting the Swivel bearing 6.1 and thus provided for adjusting the swivel axis 9 of the swivel element 8 with respect to the axis of rotation of the guide element 11.
  • a bore 18 is provided in the cylinder head Z, into which a cylindrical sleeve with an eccentric bore 19, a so-called eccentric sleeve 20, is inserted.
  • the play compensation element 6 is inserted into the eccentric bore 19 of the eccentric sleeve 20.
  • the arrangement is gem.
  • Fig. 2 shown in a top view and the eccentricity e of the axis 6.2 of the play compensation element 6 to the axis 20.1 of the eccentric sleeve 20 can be seen.
  • the rocker arm 5 rests with a dome-shaped recess 5.1 on the correspondingly spherically shaped end of the play compensation element 6 which forms the pivot bearing 6.1.
  • FIG. 2 is shown in the same drawing plane as FIG. 1.
  • the play compensation element 6 and thus also the eccentric sleeve 20 are aligned in this embodiment in the pivot bearing 6.1 with its axis 6.2 inclined at an angle to the axis of movement 1.1 of the gas exchange valve 1 for reasons of favorable force introduction in this embodiment.
  • the eccentric sleeve 20 in the direction of arrow 21 from the in
  • FIG. 4 shows a perspective view of the eccentric sleeve 20 with the play compensation element 6 inserted.
  • the eccentric sleeve 20 has a radial bore 21, to which an oil distribution groove 22 is assigned on the outer surface.
  • a pressure oil channel 23 is cut through the receiving bore 18 in the cylinder head, so that with appropriate positioning of the bore 21 and the oil distribution groove 22 there is a connection to the play compensation elements 6 and thus through the movable part of the play compensation element a corresponding pressurization via the rocker arm 5, the stroke transmission means 4 can be kept free of play.
  • the play compensation element 6 and the eccentric sleeve 20 are used here in each case pressure-tight and liquid-tight.
  • eccentric sleeves which are kept for example in classes with eccentricities of 0.02 mm, 0.04 mm and 0.06 mm.
  • an appropriately selected eccentric sleeve is then used. This can be done, for example, in the form shown in FIG. 3, namely that the eccentricities in the gradation are used in a plane defined by the axis 6.2 of the play compensation element 6 and the movement axis 1.1 of the gas exchange valve 1.
  • Intermediate stages can then be set, for example, by inserting these classified eccentric sleeves at an angle to the plane mentioned above.
  • Both the rotatable version and the fixed version are then fixed in each case in the receiving bore 18, be it by frictional engagement, clamping action, a corresponding tab or by a pressed-in locking ball 24. as shown in Fig. 3.

Landscapes

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

Abstract

Variable valve drive for at least one gas shuttle valve (1) provided with a closing spring (2) comprises a drive device (14) acting on a stroke transfer device (4) consisting of interacting partial elements and acting against the force of the closing spring on the gas shuttle valve. The stroke transfer device has an adjustable control element (12) and interacts with a lever (5) supported with its free end on the shaft end (3) of the gas shuttle valve and having another end mounted on a play-compensation element (6) arranged on a cylinder head and forming a pivot bearing (6.1) and connected to a device for adjusting the pivot axis (9) relative to the stroke transfer device.

Description

Bezeichnung: Vollvariabler mechanischer Ventiltrieb für eine Kolbenbrennkraftmaschine mit justierbarem VentilspielausgleichDescription: Fully variable mechanical valve train for a piston internal combustion engine with adjustable valve clearance compensation
Beschreibungdescription
Mechanische Ventiltriebe weisen eine Nockenwelle auf, wobei jeweils ein durch die Geometrie eines Nockens vorgegebener Hub über einen Schlepphebel auf das zu betätigende Gaswechselventil übertragen wird. Durch die Anordnung verstellbarer Hubübertragungsmittel zwischen Nocken und Schlepphebel ist es möglich, einen mechanischen Ventiltrieb voll variabel zu gestalten.Mechanical valve drives have a camshaft, a stroke predetermined by the geometry of a cam being transmitted to the gas exchange valve to be actuated via a rocker arm. The arrangement of adjustable stroke transmission means between the cam and rocker arm makes it possible to make a mechanical valve train fully variable.
Voll variable mechanische Ventiltriebe für eine Kolbenbrenn- . kraftmaschine sind beispielsweise aus DE 100 06 018A oder WO 02/053881A bekannt. Bei diesen ist jeweils zwischen einem Antriebsmittel, beispielsweise in Form eines Nockens einer Nockenwelle, und dem zu betätigenden Gaswechselventil ein aus mehreren zusammenwirkenden Teilelementen gebildetes Hubübertragungsmittel angeordnet, das es ermöglicht, den durch die Nockenkontur vorgegebenen Vollhub über ein entsprechend angeordnetes verstellbares Steuerelement zwischen einem Null-Hub und dem Voll-Hub entsprechend den betriebsbedingten Vorgaben zu verändern.Fully variable mechanical valve train for a piston combustion. Engine are known for example from DE 100 06 018A or WO 02 / 053881A. In each of these, a stroke transmission means formed from a plurality of interacting partial elements is arranged between a drive means, for example in the form of a cam of a camshaft, and the gas exchange valve to be actuated, which enables the full stroke predetermined by the cam contour to be set between a zero and a correspondingly arranged adjustable control element. Stroke and the full stroke according to the operational requirements.
Das Hubübertragungsmittel wirkt auf einen Schlepphebel ein, der sich mit seinem freien Ende auf dem Schaft des zu betätigenden Gaswechselventils abstützt und mit seinem anderen Ende auf einem ein Schwenklager bildenden,, am Zylinderkopf angeordneten, vorzugsweise hydraulisch betätigbaren Spielausgleichselement gelagert ist.The stroke transmission means acts on a rocker arm, which is supported with its free end on the shaft of the gas exchange valve to be actuated and with its other end is mounted on a, preferably hydraulically actuated, play compensation element arranged on the cylinder head, forming a pivot bearing.
Der Erfindung liegt die Aufgabe zugrunde, derartige mehrere Teilelemente aufweisende Ventiltriebe dadurch zu verbessern, daß nicht zu vermeidende, eine ordnungsgemäße Funktion nachteilig beeinflussende Fertigungstoleranzen ausgeglichen werden können.The invention has for its object to improve such multiple sub-elements valve trains in that unavoidable, proper function disadvantageously influencing manufacturing tolerances can be compensated.
Die Aufgabe wird gemäß der Erfindung mit einem variabel ein- stellbaren Ventiltrieb gelöst, der die im Anspruch 1 angegebenen Merkmale aufweist. Dadurch, daß das Spielausgleichselement mit einem Justiermittel verbunden ist, ergibt sich die Möglichkeit, durch eine Verschiebung des Schwenklagers des Schlepphebels die geometrische Zuordnung des Schlepphebels zum Hubübertragungsmittel zu verändern und so eine einwandfreie Kinematik zu erzielen.The object is achieved according to the invention with a variably adjustable valve train which has the features specified in claim 1. Characterized in that the play compensation element is connected to an adjusting means, there is the possibility of changing the geometric assignment of the rocker arm to the stroke transmission means by shifting the pivot bearing of the rocker arm and thus achieving perfect kinematics.
In vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, daß das Mittel für die Justierung durch eine mit dem Zylin- derkopf verbundene Exzenterhülse als Aufnahme für das Spielausgleichselement gebildet wird. Bei dieser Lösung wird mit Vorteil ausgenutzt, daß das Spielausgleichselement üblicherweise in eine entsprechende Aufnahmebohrung im Zylinderkopf eingesetzt ist.In an advantageous embodiment of the invention it is provided that the means for the adjustment is formed by an eccentric sleeve connected to the cylinder head as a receptacle for the play compensation element. This solution takes advantage of the fact that the play compensation element is usually inserted into a corresponding receiving bore in the cylinder head.
Das Einjustieren zum Ausgleich fertigungsbedingter Maßabweichungen kann nun gemäß einer Ausführungs orm der Erfindung dadurch geschehen, daß Exzenterhülsen mit unterschiedlicher Exzentrizität ihrer Aufnahme für das Spielausgleichselement vorgehalten werden, so daß entsprechend der erfaßten Maßabweichung eine Exzenterhülse mit "passender" Exzentrizität eingesetzt wird.The adjustment to compensate for manufacturing-related dimensional deviations can now be done according to an embodiment orm of the invention in that eccentric sleeves with different eccentricity of their receptacle are kept for the play compensation element, so that an eccentric sleeve with a "suitable" eccentricity is used in accordance with the detected dimensional deviation.
In einer anderen Ausgestaltung der Erfindung ist vorgesehen, daß die Exzenterhülse verdrehbar angeordnet ist. In diesem Falle wird eine Exzenterhülse mit einer Exzentrizität vorgesehen, die der zu erwartenden maximalen fertigungsbedingten Maßabweichung entspricht. Durch Verdrehen der Exzenterhülse im Zylinderkopf läßt sich dann eine stufenlose Justierung der Schwenkachse des Schwenkelementes in bezug auf die ortsfeste Drehachse des Führungselementes bewirken. In beiden Fällen sind Mittel zur Fixierung der Exzenterhülse am Zylinderkopf vorgesehen. Diese können beispielsweise durch eine entsprechende Lasche an der Exzenterhülse gebildet werden, die in den Zylinderkopf eingreift. Es ist auch möglich, die Exzenterhülse mit einer axial verlaufenden Nut zu versehen, in die nach erfolgter Justierung eine Stahlkugel eingepreßt wird, so daß unter Verformung des Grundwerkstoffs des Zylinderkopfs die Exzenterhülse fixiert ist.In another embodiment of the invention it is provided that the eccentric sleeve is rotatably arranged. In this case, an eccentric sleeve with an eccentricity is provided, which corresponds to the expected maximum manufacturing-related dimensional deviation. By rotating the eccentric sleeve in the cylinder head, a stepless adjustment of the pivot axis of the pivot element can then be effected with respect to the fixed axis of rotation of the guide element. In both cases, means are provided for fixing the eccentric sleeve to the cylinder head. These can be formed, for example, by a corresponding tab on the eccentric sleeve, which engages in the cylinder head. It is also possible to provide the eccentric sleeve with an axially extending groove into which a steel ball is pressed after adjustment, so that the eccentric sleeve is fixed while deforming the base material of the cylinder head.
Weitere Merkmale uns Ausgestaltungen der Erfindung sind in der nachfolgenden Beschreibung und in den Unteransprüchen angegeben.Further features and refinements of the invention are specified in the following description and in the subclaims.
Die Erfindung wird anhand schematischer Zeichnungen eines Ausführungsbeispiels näher erläutert. Es zeigen:The invention is explained in more detail with reference to schematic drawings of an embodiment. Show it:
Fig. 1 einen mechanischen Ventiltrieb,1 shows a mechanical valve train,
Fig. 2 in einem Teilschnitt die Anordnung eines Spielausgleichselementes,2 shows a partial section of the arrangement of a play compensation element,
Fig. 3 eine Aufsicht auf die Anordnung gem. Fig. 2,Fig. 3 is a plan view of the arrangement acc. Fig. 2,
Fig. 4 eine perspektivische Ansicht eines Spiel- ausgleichselementes mit Exzenterhülse.4 shows a perspective view of a play compensation element with an eccentric sleeve.
Der in Fig. 1 schematisch dargestellte Ventiltrieb besteht im wesentlichen aus einem Gaswechselventil 1, das über eine Ventilfeder 2 in Schließstellung gehalten wird. Dem freien Ende 3 des Ventilschaftes des Gaswechselventils 1 ist ein aus mehreren zusammenwirkenden, in ihrer Position zueinander teilweise verstellbaren Teilelementen gebildetes Hubübertragungs- mittel 4 zugeordnet, das auf einen Schlepphebel 5 einwirkt.The valve train shown schematically in Fig. 1 consists essentially of a gas exchange valve 1, which is held in the closed position via a valve spring 2. Associated with the free end 3 of the valve stem of the gas exchange valve 1 is a stroke transmission means 4, which is made up of a plurality of interacting partial elements which can be partially adjusted in relation to one another and which acts on a rocker arm 5.
Als "Hubübertragungsmittel" im Sinne der Erfindung sind alle zwischen dem Antriebsmittel 14 (Nocken einer Nockenwelle oder auch elektrische oder hydraulische Aktuatoren) und einem auf das Gaswechselventil 1 unmittelbar einwirkenden Schlepphebel 5 einwirkende und miteinander in Wirkverbindung stehende Teilelemente anzusehen. Durch ein Verstellen von Teilelementen zueinander kann ihr mechanisch-geometrisches Zusammenwir- ken verändert werden, so daß bei einem beispielsweise durch einen Nocken fest vorgegebenen Hub der tatsächliche, über den Schlepphebel 5 auf das Gaswechselventil 1 wirkende Hub zwischen "Null" und "Vollhub" variabel eingestellt werden kann.As “stroke transmission means” in the sense of the invention, all are between the drive means 14 (camshaft of a camshaft or also electrical or hydraulic actuators) and one the rocker arm 5 acting directly on the gas exchange valve 1 and interacting with each other are sub-elements. By adjusting sub-elements relative to one another, their mechanical-geometric interaction can be changed, so that with a stroke that is fixed, for example, by a cam, the actual stroke that acts on the gas exchange valve 1 via the rocker arm 5 is variable between “zero” and “full stroke” can be adjusted.
Bei dem hier dargestellten Ausführungsbeispiel sind als Teilelemente des Hubübertragungsmittels 4 im wesentlichen ein Führungselement 11 mit Steuerkurve 12 und ein Schwenkelement 8 vorgesehen.In the exemplary embodiment shown here, a guide element 11 with a control cam 12 and a pivot element 8 are essentially provided as sub-elements of the stroke transmission means 4.
Der Schlepphebel 5 ist über ein Spielausgleichselement 6 zum Ausgleich des Ventilspiels am Zylinderkopf bzw. Motorblock gelagert und liegt mit seinem freien Ende 7 auf dem Schaftende 3 des Gaswechselventils 1 auf. Die Abstützung des Schlepphebels 5 auf dem Spielausgleichselement 6 bildet zu- gleich ein Schwenklager 6.1 für den Schlepphebel 5.The rocker arm 5 is supported by a lash adjuster 6 to compensate for the valve lash on the cylinder head or engine block and rests with its free end 7 on the shaft end 3 of the gas exchange valve 1. The rocker arm 5 is supported on the play compensation element 6 at the same time forms a pivot bearing 6.1 for the rocker arm 5.
Am Schlepphebel 5 ist zwischen dem Schwenklager 6.1 und der Auflage auf dem Schaftende 3 des Gaswechselventils 1 das Schwenkelement 8 um eine Schwenkachse 9 hin und her schwenk- bar gelagert. Das Schwenkelement 8 weist an seinem derThe pivot element 8 is mounted on the rocker arm 5 between the pivot bearing 6.1 and the support on the shaft end 3 of the gas exchange valve 1 so that it can pivot back and forth about a pivot axis 9. The pivot element 8 has on its
Schwenkachse 9 abgekehrten freien Ende eine Führungsrolle 10 auf.Pivot axis 9 facing away from the free end of a guide roller 10.
Dem Schwenkelement 8 ist ferner das Führungselement 11 mit seiner Steuerkurve 12 für die Führungsrolle 10 zugeordnet.The guide element 11 with its cam 12 for the guide roller 10 is also assigned to the pivot element 8.
Das Führungselement 11 ist am Zylinderkopf bzw. Motorblock um eine ortsfeste Drehachse in Richtung des Doppelpfeiles 13 mit Hilfe eines Stellantriebes relativ zum Gaswechselventil 1 verstellbar, so daß, wie nachstehend noch näher angegeben werden wird, für das Abrollen der Führungsrolle 10 unterschiedliche Abrollbereiche vorgegeben werden können. Das Schwenkelement 8 ist ferner zwischen der Führungsrolle 10 und der Schwenkachse 9 mit einer Druckrolle 8.1 versehen, auf die ein Antriebsmittel in Form eines Nockens 14 einer Nockenwelle mit seiner Steuerkontur 15 einwirkt. Über eine Rück- stellfeder 16, beispielsweise in Form der hier dargestellten Wickel- oder Biegefeder, wird das Schwenkelement 8, gegen die Steuerkontur 15 des Nockens 14 angedrückt.The guide element 11 is adjustable on the cylinder head or engine block about a fixed axis of rotation in the direction of the double arrow 13 with the aid of an actuator relative to the gas exchange valve 1, so that, as will be explained in more detail below, 10 different rolling areas can be specified for the rolling of the guide roller , The pivot element 8 is further provided between the guide roller 10 and the pivot axis 9 with a pressure roller 8.1, on which a drive means in the form of a cam 14 of a camshaft acts with its control contour 15. The pivoting element 8 is pressed against the control contour 15 of the cam 14 via a return spring 16, for example in the form of the winding or spiral spring shown here.
Der Vorteil dieser Form der Rückstellfeder besteht darin, daß in dem sehr begrenzten Bauraum im Bereich zwischen Nockenwelle und Gaswechselventil ein Federelement raumsparend angeordnet werden kann, das den verhältnismäßig großen Hub des Schwenkelementes 8 bei annähernd konstanter Rückstellfederkraft aufzunehmen vermag.The advantage of this form of the return spring is that in the very limited space in the area between the camshaft and gas exchange valve, a spring element can be arranged in a space-saving manner, which is able to absorb the relatively large stroke of the pivot element 8 with an approximately constant return spring force.
In der Zeichnung ist das Gaswechselventil in Schließstellung dargestellt. Bei einer Drehung des Nockens 14 in Richtung des Pfeils 17 wird das Schwenkelement 8 um seine Drehachse 9 verschwenkt. Da die Führungsrolle 10 auf der Steuerkontur 12 ab- rollt, kann bei entsprechender Positionierung des Führungselementes 11 die Führungsrolle 10 nur der Steuerkontur 12 folgen, so daß dementsprechend durch die Kraftwirkung zwischen Nocken 14 und Druckrolle 8.1 der sich auf dem Schwenklager 6.1 abstützende Schlepphebel 5 ebenfalls gleichsinnig zum Pfeil 17 nach unten angelenkt wird und hierbei dasIn the drawing, the gas exchange valve is shown in the closed position. When the cam 14 rotates in the direction of the arrow 17, the pivot element 8 is pivoted about its axis of rotation 9. Since the guide roller 10 rolls on the control contour 12, the guide roller 10 can only follow the control contour 12 if the guide element 11 is positioned accordingly, so that the rocker arm 5 supported on the swivel bearing 6.1 is also supported by the force between cam 14 and pressure roller 8.1 is articulated downwards in the same direction as arrow 17 and this
Gaswechselventil 1 gegen die Kraft der Ventilfeder 2 geöffnet wird.Gas exchange valve 1 is opened against the force of the valve spring 2.
Die Steuerkontur 12 des Führungselementes 11 weist nun einen ersten Konturenbereich I auf, der als Kreisbahn geformt ist, deren Mittelpunkt mit der Drehachse des Führungselementes 11 und der Schwenkachse des Schwenkelementes 8 bei geschlossenem Gaswechselventil zusammenfällt. Hierdurch wird bewirkt, daß bei Drehung des Nockens 14 das Schwenkelement zwar hin und her schwenken kann, jedoch keine Kraftwirkung auf denThe control contour 12 of the guide element 11 now has a first contour region I, which is shaped as a circular path, the center of which coincides with the axis of rotation of the guide element 11 and the pivot axis of the pivot element 8 when the gas exchange valve is closed. This has the effect that when the cam 14 rotates the pivoting element can pivot back and forth, but no force effect on the
Schlepphebel 5 und damit kein Öffnungshub des Ventils 1 erfolgt. Erst bei einem Verschwenken des Führungselementes 11 in Richtung auf den Nocken 14 rollt die Führungsrolle 10 über einen Bereich II der Steuerkontur, der einen geringeren Krümmungsradius und damit auch einen anderen Bahnmittelpunkt aufweist, so daß dementsprechend über das Schwenkelement 8 der Schlepphebel 5 in Öffnungsstellung gedrückt wird. Dieser Bereich II der Steuerkontur 12 ist entsprechend den Anforderungen an die Hubkinematik für das Gaswechselventil 1 geformt. Je nach der Positionierung des Führungselementes 11 kann nun ausgehend von einem Null-Hub über beliebige reduzierte Hub- weiten der Betrieb bis zum Voll-Hub eingestellt werden.Rocker arm 5 and thus no opening stroke of valve 1 takes place. Only when the guide element 11 is pivoted In the direction of the cam 14, the guide roller 10 rolls over an area II of the control contour, which has a smaller radius of curvature and thus also a different center of the path, so that the rocker arm 5 is accordingly pressed into the open position via the pivot element 8. This area II of the control contour 12 is shaped in accordance with the requirements for the lifting kinematics for the gas exchange valve 1. Depending on the positioning of the guide element 11, the operation can now be set to a full stroke starting from a zero stroke over any reduced stroke lengths.
Über das hydraulische Spielausgleichselement 6, das in üblicher Weise ausgebildet ist, wird im Betrieb ein durch temperaturbedingte Längenänderungen und/oder Verschleiß bewirktes Spiel zwischen den einzelnen Teilen des Hubübertragungsmittels 4 ausgeglichen, so daß im Zusammenwirken von Ventilfeder 2 und Rückholfeder 16 sowohl die Druckrolle 8.1 als auch die Führungsrolle 10 jeweils spielfrei auf ihrer Steuerkontur abrollen.About the hydraulic lash adjuster 6, which is designed in a conventional manner, a game caused by temperature-related changes in length and / or wear is compensated for play between the individual parts of the stroke transmission means 4, so that in the interaction of valve spring 2 and return spring 16 both the pressure roller 8.1 and also roll the guide roller 10 without play on its control contour.
Die Drehachse des Führungselementes 11 und die Schwenkachse 9 des Schwenkelementes 8 müssen bei geschlossenem Gaswechselventil im Idealfall zusammenfallen. Da die Drehachse des Führungselementes 11 ortsfest am Zylinderkopf liegt, die Positi- on der Schwenkachse 9 des Schwenkelementes 8 infolge einer Verkettung von Fertigungstoleranzen jedoch von der Ideallage abweichen kann, ist, wie in Fig. 2 dargestellt, das Spielausgleichselement 6 mit Mitteln zur Justierung des Schwenklagers 6.1 und damit zur Justierung der Schwenkachse 9 des Schwenk- elementes 8 in bezug auf die Drehachse des Führungselementes 11 versehen. Bei dem hier dargestellten Ausführungsbeispiel ist im Zylinderkopf Z eine Bohrung 18 vorgesehen, in die eine zylindrische Hülse mit einer exzentrischen Bohrung 19, eine sogenannte Exzenterhülse 20 eingesetzt ist. In die exzentri- sehe Bohrung 19 der Exzenterhülse 20 ist das Spielausgleichselement 6 eingesetzt. In Fig. 3 ist die Anordnung gem. Fig. 2 in einer Aufsicht dargestellt und die Exzentrizität e der Achse 6.2 des Spielausgleichselementes 6 zur Achse 20.1 der Exzenterhülse 20 zu erkennen. Der Schlepphebel 5 liegt mit einer kalottenförmigen Ausnehmung 5.1 auf dem entsprechend kugelförmig geformten, das Schwenklager 6.1 bildenden Ende des Spielausgleichselementes 6 auf. Fig. 2 in der gleichen Zeichenebene dargestellt wie Fig. 1.The axis of rotation of the guide element 11 and the pivot axis 9 of the pivot element 8 must ideally coincide when the gas exchange valve is closed. Since the axis of rotation of the guide element 11 is stationary on the cylinder head, but the position of the pivot axis 9 of the pivot element 8 can deviate from the ideal position due to a chaining of manufacturing tolerances, as shown in FIG. 2, the play compensation element 6 is provided with means for adjusting the Swivel bearing 6.1 and thus provided for adjusting the swivel axis 9 of the swivel element 8 with respect to the axis of rotation of the guide element 11. In the exemplary embodiment shown here, a bore 18 is provided in the cylinder head Z, into which a cylindrical sleeve with an eccentric bore 19, a so-called eccentric sleeve 20, is inserted. The play compensation element 6 is inserted into the eccentric bore 19 of the eccentric sleeve 20. In Fig. 3 the arrangement is gem. Fig. 2 shown in a top view and the eccentricity e of the axis 6.2 of the play compensation element 6 to the axis 20.1 of the eccentric sleeve 20 can be seen. The rocker arm 5 rests with a dome-shaped recess 5.1 on the correspondingly spherically shaped end of the play compensation element 6 which forms the pivot bearing 6.1. FIG. 2 is shown in the same drawing plane as FIG. 1.
Das Spielausgleichselement 6 und damit auch die Exzenterhülse 20 sind aus Gründen einer günstigen Krafteinleitung in dieser Ausführung im Schwenklager 6.1 mit seiner Achse 6.2 unter einem Winkel gegen die Bewegungsachse 1.1 des Gaswechselventils 1 geneigt ausgerichtet. Wird nun, wie in Fig. 3 angedeutet, die Exzenterhülse 20 in Richtung des Pfeils 21 aus der inThe play compensation element 6 and thus also the eccentric sleeve 20 are aligned in this embodiment in the pivot bearing 6.1 with its axis 6.2 inclined at an angle to the axis of movement 1.1 of the gas exchange valve 1 for reasons of favorable force introduction in this embodiment. Now, as indicated in Fig. 3, the eccentric sleeve 20 in the direction of arrow 21 from the in
Fig. 3 dargestellten Grundstellung verdreht, dann bewegt sich der durch die Achse 6.2 definierte Lagermittelpunkt 6.3 (Fig. 2) des Schwenklagers 6.1 zwischen Spielausgleichselement 6 und Schlepphebel 5 auf einer entsprechend geneigt ausgerich- teten Kreisbahn, so daß der Lagermittelpunkt 6.3, bezogen auf die Darstellung in Fig. 1, nicht nur quer in die X-Richtung des in Fig. 1 dargestellten Koordinatensystems sondern auch in Y-Richtung, d. h. in Richtung der Bewegungsachse 1.1 des Gaswechselventils 1. Für die Justierung der Schwenkachse 9 in Bezug auf die Drehachse des Führungselementes 11 kommt es hierbei nur darauf an, daß beide Achsen praktisch den gleichen Querabstand zur Bewegungsachse 1.1 des Gaswechselventils 1 aufweisen. Unterschiedliche Höhenlagen in der ϊ-Richtung sind ohne Belang. Ebenso ist ohne Belang, daß sich bei einem Verdrehen der Lagermittelpunkt 6.3 auch in Z-Richtung (vgl. Fig. 3) verschiebt. Hierdurch ergibt sich nur eine Parallelverschiebung des Hubübertragungsmittels 4 insgesamt gegenüber dem Gaswechselventil 1 und dem Nocken 14 sowie dem Führungselement 11. Fig. 4 zeigt in einer perspektivischen Ansicht die Exzenterhülse 20 mit eingesetztem Spielausgleichselement 6. Wie aus der Ansicht zu erkennen ist, weist die Exzenterhülse 20 eine radiale Bohrung 21, der auf der Außenfläche eine Ölver- teilungsnut 22 zugeordnet ist.3 rotated, then the bearing center point 6.3 (FIG. 2) of the pivot bearing 6.1 defined by the axis 6.2 moves between the play compensation element 6 and the rocker arm 5 on a correspondingly inclined circular path, so that the bearing center point 6.3, relative to the 1, not only transversely in the X direction of the coordinate system shown in FIG. 1 but also in the Y direction, ie in the direction of the movement axis 1.1 of the gas exchange valve 1. For the adjustment of the pivot axis 9 with respect to the axis of rotation of the Guide element 11 is only important that both axes have practically the same transverse distance to the axis of movement 1.1 of the gas exchange valve 1. Different altitudes in the ϊ direction are irrelevant. It is also irrelevant that when the bearing center point 6.3 is rotated, it also shifts in the Z direction (see FIG. 3). As a result, there is only a total parallel displacement of the stroke transmission means 4 with respect to the gas exchange valve 1 and the cam 14 and the guide element 11. FIG. 4 shows a perspective view of the eccentric sleeve 20 with the play compensation element 6 inserted. As can be seen from the view, the eccentric sleeve 20 has a radial bore 21, to which an oil distribution groove 22 is assigned on the outer surface.
Wie die Schnittdarstellung in Fig. 2 erkennen läßt, wird durch die Aufnahmebohrung 18 ein Druckölkanal 23 im Zylinderkopf angeschnitten, so daß bei entsprechender Positionierung der Bohrung 21 und der Olverteilungsnut 22 eine Verbindung zum Spielausgleichselemente 6 gegeben ist und so über den beweglichen Teil des Spielausgleichselementes durch eine entsprechende Druckbeaufschlagung über den Schlepphebel 5 das Hubübertragungsmittel 4 spielfrei gehalten werden kann. Das Spielausgleichselement 6 und die Exzenterhülse 20 sind hier jeweils druck- und flüssigkeitsdicht eingesetzt.As can be seen from the sectional view in FIG. 2, a pressure oil channel 23 is cut through the receiving bore 18 in the cylinder head, so that with appropriate positioning of the bore 21 and the oil distribution groove 22 there is a connection to the play compensation elements 6 and thus through the movable part of the play compensation element a corresponding pressurization via the rocker arm 5, the stroke transmission means 4 can be kept free of play. The play compensation element 6 and the eccentric sleeve 20 are used here in each case pressure-tight and liquid-tight.
Statt der vorstehend beschriebenen verdrehbaren Anordnung nur einer Exzenterhülse ist es auch möglich, verschiedene, klas- sifizierte Exzenterhülsen vorzusehen, die beispielsweise in Klassen mit Exzentrizitäten von 0,02 mm, 0,04 mm und 0,06 mm vorgehalten werden. Je nach den festgestellten Maßabweichungen wird dann eine entsprechend ausgewählte Exzenterhülse eingesetzt. Dies kann beispielsweise in der in Fig. 3 darge- stellten Form erfolgen, nämlich daß die Exzentrizitäten in der Abstufung in eine durch die Achse 6.2 des Spielausgleichselementes 6 und der Bewegungsachse 1.1 des Gaswechselventils 1 definierten Ebene eingesetzt werden. Zwischenstufen können dann beispielsweise durch Einsetzen dieser klassifi- zierten Exzenterhülsen unter einem Winkel zu der vorstehend genannten Ebene eingestellt werden.Instead of the rotatable arrangement of only one eccentric sleeve described above, it is also possible to provide different, classified eccentric sleeves, which are kept for example in classes with eccentricities of 0.02 mm, 0.04 mm and 0.06 mm. Depending on the determined dimensional deviations, an appropriately selected eccentric sleeve is then used. This can be done, for example, in the form shown in FIG. 3, namely that the eccentricities in the gradation are used in a plane defined by the axis 6.2 of the play compensation element 6 and the movement axis 1.1 of the gas exchange valve 1. Intermediate stages can then be set, for example, by inserting these classified eccentric sleeves at an angle to the plane mentioned above.
Sowohl die verdrehbare Ausführung wie auch die fest einzusetzende Ausführung wird dann jeweils in der Aufnahmebohrung 18 fixiert, sei es durch Reibschluß, Klemmwirkung, eine entsprechende Lasche oder sei es durch eine eingepreßte Arretierungskugel 24,. wie in Fig. 3 dargestellt. Both the rotatable version and the fixed version are then fixed in each case in the receiving bore 18, be it by frictional engagement, clamping action, a corresponding tab or by a pressed-in locking ball 24. as shown in Fig. 3.

Claims

Ansprüche Expectations
1. Variabel einstellbarer Ventiltrieb für wenigstens ein mit einer Schließfeder (2) versehenes Gaswechselventil (1) an einer Hubkolbenmaschine, insbesondere einer Hubkolbenbrenn- kraftmaschine-, mit einem Antriebsmittel (14), das auf ein gegen die Kraft der Schließfeder (2) auf das Gaswechselventil (1) einwirkendes, aus mehreren zusammenwirkenden Teilelementen gebildetes Hubübertragungsmittel (4) wirkt, das ein ver- stellbares Steuerelement (12) aufweist und das mit einem1. A variably adjustable valve train for at least one gas exchange valve (1) provided with a closing spring (2) on a reciprocating piston engine, in particular a reciprocating internal combustion engine, with a drive means (14) acting on the against the force of the closing spring (2) Stroke transmission means (4), which acts on the gas exchange valve (1) and consists of a plurality of interacting sub-elements, has an adjustable control element (12) and one
Schlepphebel (5) in Wirkverbindung steht, der sich mit seinem freien Ende auf dem Schaftende (3) des Gaswechselventils (1) abstützt und dessen anderes Ende auf einem ein Schwenklager (6.1) bildendes, am Zylinderkopf angeordneten Spielaus- gleichselement (6) gelagert ist und das mit einem Mittel (20) für eine Justierung des Schwenklagers ( 9 ) relativ zum Hubübertragungsmittel (4) verbunden ist.The rocker arm (5) is in operative connection, the free end of which is supported on the shaft end (3) of the gas exchange valve (1) and the other end of which is mounted on a play compensation element (6) which forms a swivel bearing (6.1) and is arranged on the cylinder head and which is connected to a means (20) for adjusting the pivot bearing (9) relative to the stroke transmission means (4).
2. Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß das Spielausgleichselement (6) in einer Aufnahmebohrung (18) im Zylinderkopf angeordnet ist.2. Valve train according to claim 1, characterized in that the play compensation element (6) is arranged in a receiving bore (18) in the cylinder head.
3. Ventiltrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Mittel für die Justierung durch eine mit dem Zylinderkopf verbundene Exzenterhülse (20) als Aufnahme für das Spielausgleichselement (6) gebildet wird.3. Valve train according to claim 1 or 2, characterized in that the means for adjustment by an eccentric sleeve (20) connected to the cylinder head is formed as a receptacle for the play compensation element (6).
4. Ventiltrieb nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Exzenterhülse (20) mit einer vorgegebe- nen Exzentrizität (e) gegen eine Exzenterhülse mit einer anderen vorgegebenen Exzentrizität (e) austauschbar ausgebildet4. Valve train according to one of claims 1 to 3, characterized in that the eccentric sleeve (20) with a predetermined eccentricity (e) against an eccentric sleeve with another predetermined eccentricity (e) designed to be interchangeable
5. Ventiltrieb nach einem der Ansprüche 1 bis 3, dadurch ge- kennzeichnet, daß die Exzenterhülse (20) verdrehbar angeordnet ist. 5. Valve train according to one of claims 1 to 3, characterized in that the eccentric sleeve (20) is rotatably arranged.
6. Ventiltrieb nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß Mittel (24) zur Fixierung der Exzenterhülse (20) am Zylinderkopf vorgesehen sind.6. Valve train according to one of claims 1 to 5, characterized in that means (24) for fixing the eccentric sleeve (20) are provided on the cylinder head.
7. Ventiltrieb' nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Stellachse (6.2) des Spielausgleichselementes (6) in der Bewegungsebene des Schlepphebels (5) gegenüber der Bewegungsachse (1.1) des Gaswechselventils (1) geneigt angeordnet ist.7. Valve train ' according to one of claims 1 to 6, characterized in that the adjusting axis (6.2) of the play compensation element (6) in the plane of motion of the rocker arm (5) relative to the movement axis (1.1) of the gas exchange valve (1) is arranged inclined.
8. Ventiltrieb nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Exzenterhülse (20) eine radiale Verbindungsbohrung (21) für den Durchtritt von Drucköl aus einem Druckölkanal (23) im Zylinderkopf in das Spielausgleichsele- ment (6) aufweist. 8. Valve train according to one of claims 1 to 7, characterized in that the eccentric sleeve (20) has a radial connecting bore (21) for the passage of pressure oil from a pressure oil channel (23) in the cylinder head into the play compensation element (6).
EP04701291A 2003-01-28 2004-01-10 Fully variable mechanical valve drive mechanism for a piston-type internal combustion engine comprising adjustable valve play compensation Expired - Lifetime EP1590554B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10303128A DE10303128A1 (en) 2003-01-28 2003-01-28 Variable valve drive for a gas shuttle valve in a reciprocating piston engine, especially a reciprocating internal combustion engine, comprises a drive device acting on a stroke transfer device having an adjustable control element
DE10303128 2003-01-28
PCT/EP2004/000124 WO2004067924A1 (en) 2003-01-28 2004-01-10 Fully variable mechanical valve drive mechanism for a piston-type internal combustion engine comprising adjustable valve play compensation

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EP1590554B1 EP1590554B1 (en) 2009-01-14

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ITTO20050326A1 (en) 2005-05-12 2006-11-13 Luigi Conti INTERNAL COMBUSTION ENGINE WITH VARIABLE LIFTED VALVES
US10001035B2 (en) * 2016-03-18 2018-06-19 Cummins Inc. Hydraulic lash adjuster
EP3296531A1 (en) * 2016-09-14 2018-03-21 Mechadyne International Limited Engine valve system
US10697332B2 (en) * 2016-09-28 2020-06-30 Cummins Inc. Eccentric hydraulic lash adjuster for use with compression release brake

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JPS63297713A (en) * 1987-05-29 1988-12-05 Suzuki Motor Co Ltd Variable valve lift device of four-cycle engine
DE4105194A1 (en) * 1991-02-20 1992-08-27 Bayerische Motoren Werke Ag Actuator for IC engine valve - involves supporting rocker arm between two points with swivelling adjustment
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CN1742152A (en) 2006-03-01
CN100460633C (en) 2009-02-11
WO2004067924A1 (en) 2004-08-12

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