EP2668376B1 - Variable valve drive - Google Patents

Variable valve drive Download PDF

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Publication number
EP2668376B1
EP2668376B1 EP12700959.5A EP12700959A EP2668376B1 EP 2668376 B1 EP2668376 B1 EP 2668376B1 EP 12700959 A EP12700959 A EP 12700959A EP 2668376 B1 EP2668376 B1 EP 2668376B1
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EP
European Patent Office
Prior art keywords
eccentric shaft
valve
controllable valve
train assembly
mechanically controllable
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.)
Active
Application number
EP12700959.5A
Other languages
German (de)
French (fr)
Other versions
EP2668376B8 (en
EP2668376A1 (en
Inventor
Rudolf Flierl
Manfred Kloft
Paul Gnegel
Karsten Grimm
Martin Nowak
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.)
Volkswagen AG
Kolbenschmidt Pierburg Innovations GmbH
Original Assignee
Volkswagen AG
Kolbenschmidt Pierburg Innovations GmbH
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Publication date
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Publication of EP2668376A1 publication Critical patent/EP2668376A1/en
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Publication of EP2668376B1 publication Critical patent/EP2668376B1/en
Publication of EP2668376B8 publication Critical patent/EP2668376B8/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
    • F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0478—Torque pulse compensated camshafts
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/12—Fail safe operation

Definitions

  • FIG. 1 shows an embodiment of a valve train assembly 10 according to the invention with a plurality of gas exchange valves arranged in series 12, 14, 16, 18, 20, 22, 24 and 26.
  • two inlet gas exchange valves are assigned to a cylinder of the internal combustion engine.
  • the mechanically controllable valve drive arrangement 10 has four transmission arrangements 28, 29; 30, 31; 32, 33 and 34, 35, which in each case two gas exchange valves 12, 14; 16, 18; 20, 22; 24, 26 are assigned.
  • the transmission arrangements 28, 29; 30, 31; 32, 33; and 34, 35 stored in a known manner in the cylinder head by means of bearings.
  • the bearing means 36, 38 are in the present FIG.
  • each transmission arrangement 28, 29; 30, 31; 32, 33 and 34, 35 in known manner with a camshaft 40 in operative connection.
  • each transmission arrangement 28, 29; 30, 31; 32, 33 and 34, 35 by control peripheral surfaces 42, 43; 44, 45 (not visible here); 46, 47 and 48, 49 with corresponding adjusting a Ventilhubverstell sensible 41 such controlled that a lesser or higher valve lift of the intake valves 12, 14; 16, 18; 20, 22; 24, 26 is adjustable, this being accomplished by eccentric organs, which are provided on an eccentric shaft 50.
  • the eccentric shaft 50 is driven by a drive device 52 in the present case via a gear 53 designed as a gear 53.
  • eccentric shaft 50 It is designed in this embodiment as a push-through eccentric shaft, in which all possible contours of the eccentric organs are within a circle, which is formed by the outer diameter of an eccentric shaft bearing.
  • drive means 52 can be used both a forward and reverse rotary drive.
  • the eccentric shaft 50 can thus be driven in such a way that, depending on the present position, the valve stroke corresponding to the next operating state can be selected quickly and precisely by the use of the corresponding eccentric members (not shown). Even angles of rotation of> 360 ° can be realized.
  • a mechanically actuable valve drive 54 has the transmission arrangement 35 and the gas exchange valve 26.
  • the transfer assembly 35 consists of the pivot lever 56 and a rocker arm 58, wherein the pivot lever 56 engages with a working curve on the gas exchange valve 26 and the rocker arm 58 is in operative connection with the Ventilhubverstell noticed 41 and the camshaft 40.
  • the control circumferential surface 48 engages with an adjusting member of the valve lift adjusting device 41 against a biasing force of a spring 55 on a not further shown attack member (for example, a roller) of the rocker arm 58.
  • the rocker arm 58 engages with a working contour not shown on the pivot lever 56.
  • the respective rocker arm an off-center attacking Force exert on the eccentric shaft 50, which generates a torque that rotates the eccentric shaft 50 in a stable position in case of failure of the drive means 50, which causes a zero lift of the gas exchange valves and thus causes the failure of the internal combustion engine.
  • the eccentric shaft 50 at least one cam member 62 (see FIG.
  • cam member 62 may also be disposed over the eccentric shaft 50 via a single cam lobe. It may also be advantageous if the contour of the cam member 62 is within the circle formed by the outer diameter of the Exzenterwellenlagerung. This makes it possible to save the mounting step of attaching the cam member 62.
  • the plunger member 64 acts on the peripheral surface of the eccentric shaft 50 via a smooth contour or, for example, a roller.
  • a stable equilibrium position of the eccentric shaft 50 is set as a result of the interaction of cam member 62 and plunger member 64, wherein in each case a lift of the inlet valves is not equal to zero when actuated by the camshaft 40 is provided.
  • the cam member 62 is formed on the extension piece 63. It should be understood that the cam member 62 may also be formed on a single cam lobe. In this way, a position at one of the ends of the eccentric shaft 50 could be selected.
  • the cam member 62 is formed integrally with the eccentric shaft 50 and that the contour of the cam member 62 is within the circle formed by the outer diameter of an eccentric shaft bearing.
  • FIG. 3 shows an example of a schematic representation of the different position potentials of the eccentric shaft due to the acting moments at different eccentric shaft positions.
  • the curve 74 shows the positional potential of the eccentric shaft 50 due to the torque applied by the rocker arms.
  • the stable equilibrium position (characterized by the lowest position potential, here at the curve 74 it is equal to 0) is taken with a valve lift of 0, which leads to the mentioned problems.
  • the curve 78 shows the position potential due to the torque of the plunger member 64 in cooperation with the cam member 62.

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

Description

Die Erfindung betrifft eine mechanisch steuerbare Ventiltriebanordnung mit mehreren in Reihe angeordneten Gaswechselventilen, denen mindestens zwei in Reihe angeordnete Zylinder zugeordnet sind, wobei mindestens einem Gaswechselventil eine Übertragungsanordnung zugordnet ist, wobei jede Übertragungsanordnung im Zylinderkopf mittels Lagermittel beweglich gelagert ist und wobei jede Übertragungsanordnung mit jeweils einer Ventilhubversteileinrichtung und einer Nockenwelle in Wirkverbindung steht, wobei jede Ventilhubverstelleinrichtung eine drehbare Exzenterwelle mit Steuerumfangsflächen mit mindestens einem Exzenterorgan aufweist, die durch eine Antriebseinrichtung antreibbar ist, derart, dass verschiedene Ventilhubpositionen einstellbar sind.The invention relates to a mechanically controllable valve train arrangement having a plurality of gas exchange valves arranged in series, which are assigned at least two cylinders arranged in series, wherein at least one gas exchange valve is assigns a transfer arrangement, each transfer arrangement is movably mounted in the cylinder head by means of bearing means and wherein each transfer arrangement with one Ventilhubversteileinrichtung and a camshaft is in operative connection, each Ventilhubverstelleinrichtung having a rotatable eccentric shaft with control peripheral surfaces having at least one eccentric member which is driven by a drive means, such that different valve lift positions are adjustable.

Eine derartige mechanisch steuerbare Ventiltriebanordnung ist aus der DE 10 2004 003 327 A1 bekannt. Dabei offenbart diese Patentanmeldung eine Anordnung, die eine Exzenterwelle aufweist, die Steuerumfangsflächen mit Exzenterorganen besitzt, um Hubverstellungen von Gaswechselventilen zwischen Nullhub und Maximalhub zu gewährleisten. Diese Ausführungsform bietet bei einer hohen Variabilität einen großen Fertigung- und Montagevorteil. Ein Nachteil dieser bekannten Ausführungsform ist jedoch, dass dadurch, dass sich die Übertragungsanordnung, insbesondere ein Zwischenhebel der Übertragungsanordnung bei ihrer Bewegung an der Exzenterwelle abstützen und auf diese Weise eine Kraft bewirken, die außermittig an der Exzenterwelle angreift. Hierdurch entsteht ein über den Umfang der Exzenterwelle nicht konstantes mittleres Drehmoment, das von der Antriebeinrichtung abgefangen werden muss. Abhängig vom Drehwinkel der Exzenterwelle mit einem Exzenterorgan gibt es zwei Positionen, an denen dieses Moment Null ist: Die Position mit der größten und die Position mit der geringsten Hubverstellung, wobei lediglich die Position mit der geringsten Hubverstellung ein stabiles Gleichgewicht gewährleistet. Dies hat jedoch zur Folge, dass bei einem Defekt der Antriebseinrichtung, die Exzenterwelle in die Position des stabilen Gleichgewichts überführt wird, was bei einer Ausführung, in der die geringste Hubverstellung einen Nullhub beschreibt, einen Ausfall der gesamten Brennkraftmaschine zur Folge hat.Such a mechanically controllable valve train arrangement is known from DE 10 2004 003 327 A1 known. In this case, this patent application discloses an arrangement having an eccentric shaft having control peripheral surfaces with Exzenterorganen to ensure stroke adjustments of gas exchange valves between zero stroke and maximum stroke. This embodiment offers a large manufacturing and assembly advantage with high variability. A disadvantage of this known embodiment, however, is that the fact that the transmission arrangement, in particular an intermediate lever of the transmission arrangement is supported during its movement on the eccentric shaft and in this way cause a force which acts eccentrically on the eccentric shaft. This creates a non-constant over the circumference of the eccentric shaft mean torque, which of the Drive device must be intercepted. Depending on the rotation angle of the eccentric shaft with an eccentric member, there are two positions where this moment is zero: the position with the largest and the position with the smallest stroke adjustment, with only the position with the lowest stroke ensures a stable balance. However, this has the consequence that in case of a defect of the drive device, the eccentric shaft is converted into the position of stable equilibrium, which has a failure of the entire internal combustion engine in an embodiment in which the slightest stroke adjustment describes a zero stroke.

Aufgabe der Erfindung ist es daher, eine Ventiltriebanordnung zu schaffen, die den oben genannten Nachteil vermeidet und die Möglichkeit bietet, bei einem Defekt der Antriebseinrichtung der Exzenterwelle eine Fail-Safe-Funktion vorzusehen.The object of the invention is therefore to provide a valve train arrangement which avoids the above-mentioned disadvantage and offers the possibility to provide a fail-safe function in case of a defect of the drive means of the eccentric shaft.

Diese Aufgabe wird dadurch gelöst, dass die Exzenterwelle mindestens ein Nockenelement aufweist, das in Längsrichtung der Exzenterwelle gesehen außerhalb der Steuerumfangsflächen angeordnet ist und das in Wirkverbindung mit einem federbelasteten Stößelorgan steht, wobei das mindestens eine Nockenelement in Umfangsrichtung gesehen in Höhe der Nullhubeinstellungen der Steuerumfangsflächen angeordnet ist. Auf diese Weise wird gewährleistet, dass die Exzenterwelle im Falle eines Defektes der Antriebseinrichtung eine Position einnimmt, die eine bestimmte Hubverstellung der Einlassventile bewirkt.This object is achieved in that the eccentric shaft has at least one cam element, which is arranged in the longitudinal direction of the eccentric shaft outside the control peripheral surfaces and which is in operative connection with a spring-loaded plunger member, wherein the at least one cam member arranged in the circumferential direction in the amount of zero stroke settings of the control peripheral surfaces is. In this way it is ensured that the eccentric shaft assumes a position in the event of a defect of the drive device, which causes a certain stroke adjustment of the intake valves.

Hierbei ist es denkbar, dass das Stößelorgan über eine Rolle auf die Umfangsfläche der Exzenterwelle einwirkt. Eine besonders vorteilhafte und reibungsfreie Ausführungsform ist jedoch dadurch gegeben, dass das Stößelorgan über ein Wälzlager auf die Umfangsfläche der Exzenterwelle einwirkt. Hierbei soll noch einmal deutlich angemerkt werden, dass dies lediglich eine besonders vorteilhafte Ausführungsform darstellt. Es ist natürlich auch möglich, dass das Stößelorgan über eine glatte Kontur auf die Umfangsfläche der Exzenterwelle einwirkt. Auch ist es besonders vorteilhaft wenn das Stößelorgan einen Käfig aufweist, in dem ein Federorgan, vorzugsweise eine Schraubenfeder, gelagert ist. Hierbei kann das Nockenelement auf einem Nockenansatzstück ausgebildet sein, das form- und/oder kraftschlüssig an einem der beiden Enden der Exzenterwelle angeordnet ist.It is conceivable that the plunger member acts via a roller on the peripheral surface of the eccentric shaft. However, a particularly advantageous and friction-free embodiment is provided by the fact that the plunger member acts via a roller bearing on the peripheral surface of the eccentric shaft. It should again be clearly noted that this represents only a particularly advantageous embodiment. It is Of course, also possible that the plunger member acts on a smooth contour on the peripheral surface of the eccentric shaft. It is also particularly advantageous if the plunger member has a cage in which a spring member, preferably a coil spring, is mounted. In this case, the cam element may be formed on a cam attachment piece which is arranged in a positive and / or non-positive fit on one of the two ends of the eccentric shaft.

In einer Ausführungsform, bei der alle möglichen Konturen der Exzenterorgane innerhalb eines Kreises liegen, der durch die Außendurchmesser einer Exzenterwellenlagerung gebildet ist, wobei die Exzenterwelle entsprechende Lagerflächen aufweist, kann die Exzenterwelle als sogenannte durchsteckbare Exzenterwelle ausgebildet sein, was wesentliche Fertigungs- und Montagevorteile bietet. Hierbei kann es vorteilhaft sein, wenn die Antriebseinrichtung die Exzenterwelle über ein Zahnradorgan antreibt, wobei das Zahnradorgan eine Durchstecköffnung für die Exzenterwelle aufweist und form- und/oder kraftschlüssig mit der Lagerfläche verbunden ist. In einer besonders einfachen Ausführungsform kann dabei das Zahnradorgan ein Ansatzstück aufweisen, auf dem das Nockenelement ausgebildet ist. Hierbei können im Zylinderkopf Anschlagflächen vorgesehen sein, an denen das Getriebeorgan beidseits in axialer Richtung anliegt.In an embodiment in which all possible contours of the eccentric organs are within a circle formed by the outer diameter of an eccentric shaft bearing, wherein the eccentric shaft has corresponding bearing surfaces, the eccentric shaft may be formed as a so-called push-through eccentric shaft, which offers substantial manufacturing and assembly advantages. It may be advantageous if the drive means drives the eccentric shaft via a gear member, wherein the gear member has a through opening for the eccentric shaft and is positively and / or non-positively connected to the bearing surface. In a particularly simple embodiment, the gear member may have an extension on which the cam member is formed. In this case, stop surfaces may be provided in the cylinder head, against which the gear member bears on both sides in the axial direction.

Darüber hinaus hat es sich besonders vorteilhaft erwiesen, wenn jede Übertragungsanordnung mindestens einen Schwenkhebel und mindestens einen Kipphebel aufweist, wobei der Schwenkhebel mit einer Arbeitskurve auf das Gaswechselventil angreift und der Kipphebel in Wirkverbindung mit der Ventilhubverstelleinrichtung und der Nockenwelle steht und über eine Arbeitskontur auf den Schwenkhebel angreift.In addition, it has proven particularly advantageous if each transmission arrangement has at least one pivot lever and at least one rocker arm, wherein the pivot lever engages with a working curve on the gas exchange valve and the rocker arm is in operative connection with the Ventilhubverstelleinrichtung and the camshaft and a working contour on the pivot lever attacks.

Die Erfindung wird nachfolgend anhand der Zeichnungen näher erläutert, hierin zeigen:

  • Figur 1 eine perspektivische Darstellung einer Ausführungsform einer erfinderischen Ventiltriebanordnung,
  • Figur 2 eine Querschnittansicht der im Zylinderkopf gelagerten Exzenterwelle aus Figur 1 in Höhe des Nockenelementes, und
  • Figur 3 eine schematische Darstellung der unterschiedlichen Lagepotentiale der Exzenterwelle aufgrund der wirkenden Momente.
The invention will be explained in more detail below with reference to the drawings, in which:
  • FIG. 1 a perspective view of an embodiment of an inventive valve train assembly,
  • FIG. 2 a cross-sectional view of the cylinder head mounted in the eccentric shaft FIG. 1 in height of the cam element, and
  • FIG. 3 a schematic representation of the different position potentials of the eccentric shaft due to the acting moments.

Figur 1 zeigt eine Ausführungsform einer erfindungsgemäßen Ventiltriebanordnung 10 mit mehreren in Reihe angeordneten Gaswechselventilen 12, 14, 16, 18, 20, 22, 24 und 26. Im vorliegenden Fall sind jeweils zwei Einlass-Gaswechselventile einem Zylinder der Brennkraftmaschine zugeordnet. Die mechanisch steuerbare Ventiltriebanordnung 10 weist im vorliegenden Fall vier Übertragungsanordnungen 28, 29; 30, 31; 32, 33 und 34, 35 auf, denen jeweils zwei Gaswechselventile 12, 14; 16, 18; 20, 22; 24, 26 zugeordnet sind. Dabei sind die Übertragungsanordnungen 28, 29; 30, 31; 32, 33; und 34, 35 auf bekannte Weise im Zylinderkopf mittels Lagermitteln gelagert. Die Lagermittel 36, 38 werden in der vorliegenden Figur 1 lediglich exemplarisch für die Lagerung eines Schwenkhebels 56 der Übertragungsanordnung 35 dargestellt. Darüber hinaus stehen die Übertragungsanordnungen 28, 29; 30, 31; 32, 33 und 34, 35 auf bekannte Weise mit einer Nockenwelle 40 in Wirkverbindung. Außerdem ist jede Übertragungsanordnung 28, 29; 30, 31; 32, 33 und 34, 35 durch Steuerumfangsflächen 42, 43; 44, 45 (hier nicht erkennbar); 46, 47 und 48, 49 mit entsprechenden Verstellorgane einer Ventilhubverstelleinrichtung 41 derart ansteuerbar, dass ein geringerer oder höherer Ventilhub der Einlassventile 12, 14; 16, 18; 20, 22; 24, 26 einstellbar ist, wobei dies durch Exzenterorgane, die auf einer Exzenterwelle 50 vorgesehen sind, bewerkstelligt wird. Die Exzenterwelle 50 wird im vorliegenden Fall über ein als Zahnrad 53 ausgebildetes Getriebeorgan 53 durch eine Antriebseinrichtung 52 angetrieben. Sie ist in diesem Ausführungsbeispiel als durchsteckbare Exzenterwelle ausgebildet, bei der alle möglichen Konturen der Exzenterorgane innerhalb eines Kreises liegen, der durch die Außendurchmesser einer Exzenterwellenlagerung gebildet ist. Als Antriebseinrichtung 52 kann ein sowohl vorwärts wie rückwärts laufender Drehantrieb genutzt werden. Die Exzenterwelle 50 kann damit derart angetrieben werden, dass in Anhängigkeit von der vorliegenden Position schnell und präzise der dem nächsten Betriebszustand entsprechende Ventilhub durch den Einsatz der entsprechenden, nicht weiter dargestellten Exzenterorgane gewählt werden kann. Auch Drehwinkel von > 360° sind damit realisierbar. FIG. 1 shows an embodiment of a valve train assembly 10 according to the invention with a plurality of gas exchange valves arranged in series 12, 14, 16, 18, 20, 22, 24 and 26. In the present case, two inlet gas exchange valves are assigned to a cylinder of the internal combustion engine. In the present case, the mechanically controllable valve drive arrangement 10 has four transmission arrangements 28, 29; 30, 31; 32, 33 and 34, 35, which in each case two gas exchange valves 12, 14; 16, 18; 20, 22; 24, 26 are assigned. In this case, the transmission arrangements 28, 29; 30, 31; 32, 33; and 34, 35 stored in a known manner in the cylinder head by means of bearings. The bearing means 36, 38 are in the present FIG. 1 merely exemplified for the storage of a pivot lever 56 of the transfer assembly 35. In addition, the transmission arrangements 28, 29; 30, 31; 32, 33 and 34, 35 in known manner with a camshaft 40 in operative connection. In addition, each transmission arrangement 28, 29; 30, 31; 32, 33 and 34, 35 by control peripheral surfaces 42, 43; 44, 45 (not visible here); 46, 47 and 48, 49 with corresponding adjusting a Ventilhubverstelleinrichtung 41 such controlled that a lesser or higher valve lift of the intake valves 12, 14; 16, 18; 20, 22; 24, 26 is adjustable, this being accomplished by eccentric organs, which are provided on an eccentric shaft 50. The eccentric shaft 50 is driven by a drive device 52 in the present case via a gear 53 designed as a gear 53. It is designed in this embodiment as a push-through eccentric shaft, in which all possible contours of the eccentric organs are within a circle, which is formed by the outer diameter of an eccentric shaft bearing. As drive means 52 can be used both a forward and reverse rotary drive. The eccentric shaft 50 can thus be driven in such a way that, depending on the present position, the valve stroke corresponding to the next operating state can be selected quickly and precisely by the use of the corresponding eccentric members (not shown). Even angles of rotation of> 360 ° can be realized.

Im vorliegenden Ausführungsbeispiel weist ein mechanisch ansteuerbarer Ventiltrieb 54 die Übertragungsanordnung 35 sowie das Gaswechselventil 26 auf. Die Übertragungsanordnung 35 besteht dabei aus dem Schwenkhebel 56 sowie einem Kipphebel 58, wobei der Schwenkhebel 56 mit einer Arbeitskurve auf das Gaswechselventil 26 angreift und der Kipphebel 58 in Wirkverbindung mit der Ventilhubverstelleinrichtung 41 und der Nockenwelle 40 steht. Dabei greift die Steuerumgangsfläche 48 mit einem Verstellorgan der Ventilhubverstelleinrichtung 41 entgegen einer Vorspannkraft einer Feder 55 auf ein nicht weiter dargestelltes Angriffsorgan (beispielsweise eine Rolle) des Kipphebels 58 an. Der Kipphebel 58 greift mit einer nicht weiter dargestellten Arbeitskontur auf den Schwenkhebel 56 an. Auf der gegenüber gelegenen Seite sind Führungsrollen angeordnet, mit denen der Kipphebel 58 in einer Kulisse geführt ist. Die Führungsrollen sind wiederum auf einer Welle gelagert, die zwei benachbarte Kipphebel miteinander verbindet, wobei zwischen den Führungsrollen noch eine Rolle auf der Welle angeordnet ist, die wiederum mit der Nockenwelle in Wirkverbindung steht. Ein Nocken der Nockenwelle steht also mit zwei Übertragungsanordnungen in Wirkverbindung. Hinsichtlich der Funktion und Arbeitsweise einer derartigen Übertragungsanordnung wird explizit auf die deutsche Offenlegungsschrift DE 101 40 635 A1 verwiesen. Es sollte deutlich sein, dass im vorliegenden Ausführungsbeispiel die jeweiligen Kipphebel eine außermittig angreifende Kraft auf die Exzenterwelle 50 ausüben können, die ein Drehmoment erzeugt, das bei Ausfall der Antriebseinrichtung 52 die Exzenterwelle 50 in eine stabile Position verdreht, die einen Nullhub der Gaswechselventile verursacht und damit den Ausfall der Brennkraftmaschine bewirkt. Um dies zu verhindern und eine Fail-Safe-Position zu gewährleisten, die eine bestimmte Hubverstellung garantiert, weist erfindungsgemäß die Exzenterwelle 50 mindestens ein Nockenelement 62 (siehe Figur 2) auf, das in Längsrichtung der Exzenterwelle 50 gesehen außerhalb der Steuerumfangsflächen (42, 43; 44, 45; 46, 47; 48, 49) angeordnet ist und das in Wirkverbindung mit einem federbelasteten Stößelorgan 64 steht, wobei das Nockenelement 62 in Umfangsrichtung gesehen in Höhe der Nullhubeinstellungen der Steuerumfangsflächen (42, 43; 44, 45; 46, 47; 48, 49) angeordnet ist. Das Stößelorgan 64 ist im vorliegenden Ausführungsbeispiel durch eine Schraubenfeder 66 federbelastet, die in einem Käfig 68 gelagert ist. Durch diese besondere Anordnung wird den Drehmömenten der Kipphebel ein Drehmoment entgegengesetzt, was zu einer stabilen Gleichgewichtslage der Exzenterwelle 50 führt, bei der ein Ventilhub von ungleich Null vorliegt (siehe hierzu Figur 3). Es sollte jedoch deutlich sein, dass das Nockenelement 62 auch über ein einzelnes Nockenansatzstück auf der Exzenterwelle 50 angeordnet sein kann. Auch kann es durchaus vorteilhaft sein, wenn auch die Kontur des Nockenelementes 62 innerhalb des Kreises liegt, der durch die Außendurchmesser der Exzenterwellenlagerung gebildet ist. Hierdurch ist es möglich, den Montageschritt der Anbringung des Nockenelementes 62 einzusparen.In the present exemplary embodiment, a mechanically actuable valve drive 54 has the transmission arrangement 35 and the gas exchange valve 26. The transfer assembly 35 consists of the pivot lever 56 and a rocker arm 58, wherein the pivot lever 56 engages with a working curve on the gas exchange valve 26 and the rocker arm 58 is in operative connection with the Ventilhubverstelleinrichtung 41 and the camshaft 40. In this case, the control circumferential surface 48 engages with an adjusting member of the valve lift adjusting device 41 against a biasing force of a spring 55 on a not further shown attack member (for example, a roller) of the rocker arm 58. The rocker arm 58 engages with a working contour not shown on the pivot lever 56. On the opposite side guide rollers are arranged, with which the rocker arm 58 is guided in a backdrop. The guide rollers are in turn mounted on a shaft which connects two adjacent rocker arms with each other, wherein between the guide rollers still a roller is arranged on the shaft, which in turn is in operative connection with the camshaft. A cam of the camshaft is thus in operative connection with two transmission arrangements. With regard to the function and operation of such a transfer arrangement is explicitly to the German patent application DE 101 40 635 A1 directed. It should be clear that in the present embodiment, the respective rocker arm an off-center attacking Force exert on the eccentric shaft 50, which generates a torque that rotates the eccentric shaft 50 in a stable position in case of failure of the drive means 50, which causes a zero lift of the gas exchange valves and thus causes the failure of the internal combustion engine. To prevent this and to ensure a fail-safe position, which guarantees a certain stroke adjustment, according to the invention, the eccentric shaft 50 at least one cam member 62 (see FIG. 2 ) disposed longitudinally of the eccentric shaft 50, outside the control peripheral surfaces (42, 43; 44, 45; 46, 47; 48, 49), and being operatively connected to a spring loaded ram member 64, the cam member 62 being circumferentially seen in the amount of Nullhubeinstellungen the control peripheral surfaces (42, 43, 44, 45, 46, 47, 48, 49) is arranged. The plunger member 64 is spring-loaded in the present embodiment by a coil spring 66 which is mounted in a cage 68. By this particular arrangement, the torque of the rocker arm is opposed by a torque, resulting in a stable equilibrium position of the eccentric shaft 50, in which a non-zero valve lift is present (see FIG. 3 ). It should be understood, however, that the cam member 62 may also be disposed over the eccentric shaft 50 via a single cam lobe. It may also be advantageous if the contour of the cam member 62 is within the circle formed by the outer diameter of the Exzenterwellenlagerung. This makes it possible to save the mounting step of attaching the cam member 62.

Figur 2 zeigt eine Querschnittansicht der im Zylinderkopf gelagerten Exzenterwelle aus Figur 1 in Höhe des Nockenelementes 62. Das Nockenelement 62 ist im vorliegenden Ausführungsbeispiel auf einem Ansatzstück 63 des Zahnradorgans 53 ausgebildet. Das Zahnradorgan 53 ist über eine nicht weiter dargestellte Schraubverbindung lösbar mit der Exzenterwelle 50 verbunden. Das Stößelorgan 64 weist im Wesentlichen eine Schraubenfeder 66 auf, die sich auf bekannte Weise an einem Ansatzstück im Zylinderkopf abstützt und in dem Käfig 68 derart gelagert ist, dass sie über einen mit dem Käfig 68 verbundenen Stift 70 und einem darauf gelagerten Wälzlager 72 in Wirkverbindung mit der Umfangsfläche der Exzenterwelle 50 steht. Es ist natürlich auch möglich, dass das Stößelorgan 64 über eine glatte Kontur oder beispielsweise eine Rolle auf die Umfangsfläche der Exzenterwelle 50 einwirkt. Bei Ausfall der Antriebseinrichtung 52 wird in Folge des Zusammenwirkens von Nockenelement 62 und Stößelorgan 64 eine stabile Gleichgewichtslage der Exzenterwelle 50 eingestellt, bei der in jedem Fall ein Hub der Einlassventile ungleich Null bei Betätigung durch die Nockenwelle 40 vorgesehen ist. Im vorliegenden Fall ist das Nockenelement 62 auf dem Ansatzstück 63 ausgebildet. Es sollte deutlich sein, dass das Nockenelement 62 auch auf einem einzelnen Nockenansatzstück ausgebildet sein kann. Auf diese Art und Weise könnte auch eine Position an einem der Enden der Exzenterwelle 50 gewählt werden. Auch ist es natürlich möglich, dass das Nockenelement 62 einstückig mit der Exzenterwelle 50 ausgebildet ist und dass die Kontur des Nockenelementes 62 innerhalb des Kreises liegt, der durch die Außendurchmesser einer Exzenterwellenlagerung gebildet ist. FIG. 2 shows a cross-sectional view of the cylinder head mounted in the eccentric shaft FIG. 1 in the amount of the cam member 62. The cam member 62 is formed in the present embodiment on an extension piece 63 of the gear member 53. The gear member 53 is connected via a screw not shown releasably connected to the eccentric shaft 50. The plunger 64 is substantially a coil spring 66, which is supported in a known manner on an extension piece in the cylinder head and is mounted in the cage 68 such that it via a connected to the cage 68 pin 70 and a bearing mounted thereon bearing 72 in operative connection with the peripheral surface of the eccentric shaft 50th stands. It is of course also possible that the plunger member 64 acts on the peripheral surface of the eccentric shaft 50 via a smooth contour or, for example, a roller. In case of failure of the drive means 52, a stable equilibrium position of the eccentric shaft 50 is set as a result of the interaction of cam member 62 and plunger member 64, wherein in each case a lift of the inlet valves is not equal to zero when actuated by the camshaft 40 is provided. In the present case, the cam member 62 is formed on the extension piece 63. It should be understood that the cam member 62 may also be formed on a single cam lobe. In this way, a position at one of the ends of the eccentric shaft 50 could be selected. Also, it is of course possible that the cam member 62 is formed integrally with the eccentric shaft 50 and that the contour of the cam member 62 is within the circle formed by the outer diameter of an eccentric shaft bearing.

Figur 3 zeigt exemplarisch eine schematische Darstellung der unterschiedlichen Lagepotentiale der Exzenterwelle aufgrund der wirkenden Momente bei unterschiedlichen Exzenterwellenstellungen. Das Lagepotential ist hierbei wie folgt definiert: U(φ) = ∫ M dφ (J). Die Kurve 74 zeigt das Lagepotential der Exzenterwelle 50 aufgrund des durch die Kipphebel aufgebrachten Drehmomentes. Die stabile Gleichgewichtslage (ist gekennzeichnet durch das niedrigste Lagepotential, hier bei der Kurve 74 ist es gleich 0) wird bei einem Ventilhub von 0 eingenommen, was zu den angesprochenen Problemen führt. Die Kurve 78 zeigt das Lagepotential aufgrund des Drehmomentes des Stößelorgans 64 im Zusammenwirken mit dem Nockenelement 62. Die Kurve 76 zeigt nun das resultierende Lagepotential der Exzenterwelle 50, bei der zwei stabile Gleichgewichtslagen (hier Lagepotential = -4) einen Ventilhub von ca. maximal 3mm ermöglichen. Je nachdem, in welcher Stellung der Exzenterwelle im Betrieb die Fail-Safe-Position eingenommen werden muss, wird sich eine der beiden Fail-Safe-Positionen einstellen. FIG. 3 shows an example of a schematic representation of the different position potentials of the eccentric shaft due to the acting moments at different eccentric shaft positions. The position potential is defined as follows: U (φ) = ∫ M dφ (J). The curve 74 shows the positional potential of the eccentric shaft 50 due to the torque applied by the rocker arms. The stable equilibrium position (characterized by the lowest position potential, here at the curve 74 it is equal to 0) is taken with a valve lift of 0, which leads to the mentioned problems. The curve 78 shows the position potential due to the torque of the plunger member 64 in cooperation with the cam member 62. The curve 76 now shows the resulting position potential of the eccentric shaft 50, in which two stable equilibrium positions (here position potential = -4) allow a valve lift of approximately 3 mm maximum. Depending on the position of the eccentric shaft in operation, the fail-safe position must be taken, one of the two fail-safe positions will stop.

Claims (11)

  1. A mechanically controllable valve-train assembly (10) comprising a plurality of serially arranged gas exchange valves (12, 14, 16, 18, 20, 22, 24, 26) having assigned thereto at least two serially arranged cylinders, wherein at least one gas exchange valve (12, 14, 16, 18, 20, 22, 24, 26) has a transmission assembly (28, 29; 30, 31; 32, 33; 34, 35) assigned thereto, wherein each transmission assembly (28, 29; 30, 31; 32, 33; 34, 35) is mounted movably in the cylinder head with the aid of bearing means (36, 38), and wherein each transmission assembly (28, 29; 30, 31; 32, 33; 34, 35) is operatively connected to a respective valve-lift adjusting device (41) and a camshaft (40), wherein each valve-lift adjusting device (41) comprises a rotatable eccentric shaft (50) having circumferential control surfaces (42, 43; 44, 45; 46, 47; 48, 49) with at least one eccentric member, which eccentric shaft can be driven by a drive means (52) in such a way that various valve-lift positions can be set,
    characterized in that
    the eccentric shaft (50) comprises at least one cam element (62) which is arranged outside the circumferential control surfaces (42, 43; 44, 45; 46, 47; 48, 49) in the longitudinal direction of the eccentric shaft (50) and which is operatively connected to a spring-loaded tappet element (64), said at least one cam element (62) in the circumferential direction being arranged at the level of the zero-lift positions of the circumferential control surfaces (42, 43; 44, 45; 46, 47; 48, 49).
  2. The mechanically controllable valve-train assembly (10) according to claim 1, characterized in that the tappet element (64) acts on the circumferential surface of the eccentric shaft (50) via a roller.
  3. The mechanically controllable valve-train assembly (10) according to claim 1, characterized in that the tappet element (64) acts on the circumferential surface of the eccentric shaft (50) via a rolling bearing (72).
  4. The mechanically controllable valve-train assembly (10) according to any one of claims 1-3, characterized in that the cam element (62) is formed on a cam-holding projection portion which is fastened to one of the two ends of the eccentric shaft (50) by form- and/or force-locked engagement.
  5. The mechanically controllable valve-train assembly (10) according to any one of claims 1-4, characterized in that the tappet element (64) comprises a cage (68) in which a spring member (66), preferably a coil spring, is supported.
  6. The mechanically controllable valve-train assembly (10) according to any one of preceding claims, characterized in that all possible contours of the eccentric members are located within a circle formed by the outer diameters of an eccentric shaft bearing, wherein the eccentric shaft (50) comprises corresponding bearing surfaces.
  7. The mechanically controllable valve-train assembly (10) according to claim 6, characterized in that the drive means (52) is arranged to drive the eccentric shaft (50) via a gear member (53), the gear member (53) comprising a pass-through opening for the eccentric shaft (50) and being connected to the bearing surface by form- and/or force-locked engagement.
  8. The mechanically controllable valve-train assembly (10) according to claim 7, characterized in that said gear member (53) comprises a projection portion (63) on which the cam element (62) is formed.
  9. The mechanically controllable valve-train assembly (10) according to claim 7 or 8, characterized in that the cylinder head is provided with abutment faces internally thereof, which are abutted by the gear member (53) on both sides in the axial direction.
  10. The mechanically controllable valve-train assembly (10) according to claim 6, characterized in that also the contour of the cam element (62) is located within the circle formed by the outer diameters of an eccentric shaft bearing.
  11. The mechanically controllable valve-train assembly (10) according to any one of preceding claims, characterized in that each transmission assembly (28, 29; 30, 31; 32, 33; 34, 35) comprises at least one pivot lever (56) and at least one tilt lever (58), wherein the pivot lever (56) engages the gas exchange valve (12, 14, 16, 18, 20, 22, 24, 26) with a work curve and said tilt lever (58) is operatively connected to the valve-lift adjusting device (41) and the camshaft (40) and engages the pivot lever (56) via a work contour.
EP12700959.5A 2011-01-25 2012-01-13 Variable valve drive Active EP2668376B8 (en)

Applications Claiming Priority (2)

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DE102011009417A DE102011009417A1 (en) 2011-01-25 2011-01-25 Mechanically controllable valve train arrangement
PCT/EP2012/050473 WO2012100993A1 (en) 2011-01-25 2012-01-13 Mechanically controllable valve-train assembly

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EP2668376B1 true EP2668376B1 (en) 2014-12-31
EP2668376B8 EP2668376B8 (en) 2015-02-25

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JP (1) JP2014503750A (en)
CN (1) CN103354860B (en)
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CN109973168B (en) * 2019-03-27 2020-11-10 大连理工大学 Multi-mode fully-variable mechanism

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EP2668376B8 (en) 2015-02-25
CN103354860A (en) 2013-10-16
DE102011009417A1 (en) 2012-07-26
ES2532714T3 (en) 2015-03-31
CN103354860B (en) 2016-08-10
WO2012100993A1 (en) 2012-08-02
US20130306010A1 (en) 2013-11-21
EP2668376A1 (en) 2013-12-04
US9074495B2 (en) 2015-07-07
JP2014503750A (en) 2014-02-13

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