EP1506345B1 - Drive and displacement system for variable valve-controlled distribution - Google Patents

Drive and displacement system for variable valve-controlled distribution Download PDF

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Publication number
EP1506345B1
EP1506345B1 EP03725134A EP03725134A EP1506345B1 EP 1506345 B1 EP1506345 B1 EP 1506345B1 EP 03725134 A EP03725134 A EP 03725134A EP 03725134 A EP03725134 A EP 03725134A EP 1506345 B1 EP1506345 B1 EP 1506345B1
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EP
European Patent Office
Prior art keywords
drive
valve
lever
roller
cam
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Expired - Lifetime
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EP03725134A
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German (de)
French (fr)
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EP1506345A1 (en
Inventor
Herbert Naumann
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ThyssenKrupp Technologies AG
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ThyssenKrupp Automotive AG
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Publication of EP1506345A1 publication Critical patent/EP1506345A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type

Definitions

  • the present invention relates to a drive and adjustment system for mechanically variable valve controls with one on a shaft or axle rotatably mounted pivot lever, by engaging in the role or Contact surface of a rocker arm actuates the valves, wherein the shaft or axle is arranged in fixedly connected to the cylinder head bearings.
  • the Swing levers can also drive tilt or angle lever. See, for example, EP 1 039 103.
  • valve controls can be adjusted according to the invention such that the valves can be steplessly adjusted from a constant closed to the largest planned valve lift at a time coinciding with the magnification the valve lift continuously variable valve opening duration are actuated.
  • the valve controls for a throttle-free load control are suitable.
  • valve controls can in addition to the drive of a valve also simultaneously actuate several valves, and optionally only one valve of a Working space can be actuated while the other valve of the working space is always kept closed.
  • the pivot lever by a drive lever driven, with its lower end the pivot lever via a swivel joint drives, wherein the drive lever at its upper end by means of a roller or engages its contact surface in a parking cam of a parking camshaft and centered driven by a cam via a cam roller or its contact surface becomes.
  • the drive lever also drives with its lower End the pivot lever via a swivel joint, but with the drive lever at its upper end via a cam roller or its contact surface of one Cam is driven and centrally by means of a roller or its contact surface in engages an adjusting cam of an actuating camshaft.
  • Valve controls in an arrangement of a star-shaped adjusting cam on the Stellnockenwelle having different contact surfaces, through a corresponding rotational movement of the actuating camshaft, the engine of a Vehicle operated by several programs, where on the one hand an economic operation and on the other a sporty enterprise as well as a adjusted between these modes of operation of the engine can be. Due to the star-shaped arrangement of adjusting cams on the Stellnockenwelle is the production of a mechanical, largely fully variable Valve control allows, as to each set valve stroke different Valve opening times can be assigned.
  • Fig. 1 shows a valve control in the side view with a driving lever formed by a drive and adjustment, wherein the drive lever is driven approximately centrally via a cam roller; arranged with a arranged at its upper end role in a rotationally fixed manner on an actuating camshaft adjusting cam engages and drives a arranged on its lower end pivot a rotatably mounted on the actuating cam pivot lever.
  • the valve control is shown in Fig. 1 in the position of the constant closed keeping of the valves.
  • Fig. 2 shows the valve control of Fig. 1 in the side view in the position of the largest valve lift and the longest valve opening time.
  • Fig. 3 shows a valve control in the side view with a drive lever formed by a drive and adjustment, wherein the drive lever is driven at its upper end via a cam roller; engages with an approximately centrally arranged role in a rotationally fixed on an actuating camshaft adjusting cam and drives a arranged on its lower end pivot a rotatably mounted on the actuating cam pivot lever.
  • the valve control is shown in Fig. 3 in the position of the constant closed keeping of the valves.
  • Fig. 4 shows the valve control of Fig. 3 in the side view in the position of the largest valve lift and the longest valve opening time.
  • the pivot lever can also be rotatably mounted on a separate axis, which is fixedly connected to the cylinder head,
  • the valve controls on a drive lever which is supported at its upper end on an actuating cam provided only as a control shaft actuating cam shaft by means of a roller and via the arranged at its lower end pivot the pivot lever thereby drives that the drive lever itself is driven by a cam between the engaging in the adjusting cam roller and the pivot cam roller arranged.
  • the drive lever can also be driven at its upper end via a cam roller by a cam, wherein the drive lever has engaging in the adjusting cam of the actuating camshaft roller between the cam roller and arranged at the lower end of the drive lever rotary joint.
  • a cam engagement is possible here from both longitudinal sides of the drive lever, wherein the support by the adjusting cam always takes place on the side opposite to the cam engagement.
  • the control cam can be forged or cast in one piece.
  • the adjusting cams are rotatably connected via a pin rivet or screw with the actuating camshaft to avoid shared bearings in the pivoting levers.
  • axle with the pivoting levers, with the bearings can be arranged the pivot levers connected via the hinge drive levers and with the with the drive levers associated actuating camshaft as a unit in the Cylinder head used and mounted there, although the bearings of the Stellnockenwelle also run divided.
  • Fig. 1 shows a mechanically variable valve control in the setting of the constant closed keeping of the valve 1, in which a pivoting lever 2 which is rotatably mounted on a control camshaft 3 and provided by a provided for the drive and the adjustment lever 4 via a rotary joint 5 in a Pivoting movement is offset.
  • the rotary joint is arranged at the lower end of the drive lever 4 and in the vicinity of the contact surface formed of two sections 6 and 7 of the pivot lever 2 5 and serves as a bearing of the pivot lever 2 actuating cam shaft 3 is disposed in fixed to the cylinder head 8 bearings.
  • a valve 1 is actuated rocker arm 9 is driven via its roller 10 , wherein the rocker arm 9 can also be driven via a contact surface.
  • the actuating camshaft 3 has a control cam associated with its actuating cam 11 , in which the drive lever 4 engages with a roller 12 arranged at its upper end.
  • the drive lever 4 between the pivot 5 and the roller 12 has a cam roller 13 , in which a cam 14 engages.
  • the region 6 of the contact surface of the pivot lever 2 extends in a circle around the axis of rotation of the control shaft 3 and is provided for a constant closed keeping of the valve 1 .
  • the area 7 of the contact surface of the pivot lever 2 has an inwardly curved, shaped as a nose curve and is provided for the actuation of the valve 1 .
  • the roller 12 of the drive lever 4 engages here in the base circle of which is arranged on the adjusting cam shaft 3 controlling pin 11, which cam roller 13 is located on the base circle of the cam 14 and the roller 10 of the swing lever 9 is in the point A, the starting point of the region 6 the contact surface of the pivot lever 2.
  • the pivot lever 2 engages with its circular extending around its pivot axis region 6 of its contact surface to the roller 10 of the rocker arm 9 in a reciprocating motion between the point a and the point B , wherein the valve 1 is not actuated.
  • the roller 12 of the drive lever 4 is on the elevation curve of the actuating cam 11 of the actuating camshaft 3, whereby the drive lever 4 performs a rotational movement in the clockwise direction about the axis of rotation of its cam roller 13 and the pivot lever 2 via the hinge 5 is pivoted to the left.
  • the roller 10 of the rocker arm 9 is moved in the direction of the point B from the point A, in which a continuous keeping closed of the valve 1 is set.
  • the engagement of the roller 10 of the rocker arm 9 shifts in addition in the direction of the point B.
  • a compression spring 16 between the pivot lever 2 and a rotatably connected to the control shaft 3 actuating arm 17 is arranged as a return spring, wherein both the pivot lever 2 a spring plate 18 and the actuating arm 17 has a spring plate 19 .
  • the compression spring 16 is shortened in length, whereby the force acting on the pivot lever 2 restoring force of the compression spring 16 is increased.
  • the actuating arm 17 can be combined with the actuating cam 11 to form a component.
  • the drive lever 4 in addition to its pivoting movement also performs a longitudinal movement; whereby the drive lever 4 with its roller 12 on the actuating cam 11 performs a reciprocating motion. Due to the shape of the elevation curve of the actuating cam 11 , the valve lift curve generated by the cam 14 can be changed.
  • the roller 12 of the drive lever 4 by a corresponding rotation of the actuating camshaft 3 to each other different contact surfaces of the actuating cam 11 can be made.
  • the elevation curves of the contact surfaces of the actuating cam 11 may be curved inward, arched outwards, rectilinear or s-shaped, whereby for each set valve stroke different valve opening times can be provided at different valve lift curves and an engine can be operated in different work programs.
  • the provided for the largest valve lift contact surface of the actuating cam 11 can be extended by means of a subsequent arc here, which has the center of rotation of the actuating camshaft 3 , whereby by means of a rotation of the actuating camshaft 3 by the hereby changed width of the engagement of the roller 12th of the drive lever 4 in the circular arc of the contact surface of the control cam 11 at the largest valve lift the valve lift curve can be changed.
  • the contact surfaces of the parking cam 11 of two each actuate a valve 1 valve controllers be designed such that by a rotation of the adjusting cam shaft 3 by the driving lever 4 at first a pivot lever 2 for actuating a valve 1 and will hereinafter be set for the upper power range of the other pivot lever 2 for the actuation of the other valve 1, according to which both valves 1 be operated simultaneously.
  • the engine can also be operated alternately with an intake port advantageous, wherein for the operation of the engine at idle and in the lower power range, an inlet channel with a small diameter and a valve 1 with the small plate diameter and an intake duct for the medium power range after the switching of the valve 1 with the smaller disc diameter in a permanent keeping closed with the larger diameter and a valve 1 with the major plate diameter to the operation of the engine can be used.
  • a twist of the intake air in the upper power range is advantageously generated by the different diameters of the two inlet channels and the valves 1 , when both valves 1 are actuated.
  • Fig. 2 shows the valve timing in the setting of the largest valve lift and the longest valve opening time, wherein the roller 12 of the drive lever 4 is at the highest specified point of the elevation curve of the actuating cam 11 and the cam roller 13 engages in the base circle of the cam 14 .
  • the actuator arm 17 has placed with the rotation of the actuating camshaft 3 in the clockwise direction on the axis C , whereby the compression spring 16 exerts a reduced restoring force on the pivot lever 2 by the greater length thus obtained in an advantageous manner.
  • Fig. 3 shows a mechanically variable valve control in the setting of the constant closed keeping of the valve 20, in which a pivoting lever 21 which is rotatably mounted on a control camshaft 22 and provided by a provided for the drive and the adjustment lever 23 via a rotary joint 24 in a Pivoting movement is offset.
  • the rotary joint 24 is arranged at the lower end of the drive lever 23 in the vicinity of the two regions 25 and 26 contact surface formed of the pivot lever 21 and serving as a bearing of the pivot lever 21 control shaft 22 is disposed in fixed to the cylinder head 27 camps.
  • a valve 20 is actuated rocker arm 28 is driven via its roller 29 , wherein the rocker arm 28 can also be driven via a contact surface.
  • the drive lever 23 at its upper end to a cam roller 30 , in which a cam 31 engages.
  • a roller 32 is arranged, which engages in a rotatably connected to the actuating cam shaft 22 adjusting cam 33 .
  • the region 25 of the contact surface of the pivot lever 21 extends in a circle around the axis of rotation of the actuating camshaft 22 and is provided for a continuous closed keeping of the valve 20 .
  • the region 26 of the contact surface of the pivot lever 21 has an inwardly curved, shaped as a nose curvature and is provided for the actuation of the valve 20 .
  • the roller 32 of the drive lever 23 engages here in the base circle of which is arranged on the actuating camshaft 22 controlling pin 33, which cam roller 30 is located on the base circle of the cam 31 and the roller 29 of the swing lever 28 is in the point A, the starting point of the region 25 the contact surface of the pivot lever 21.
  • the pivot lever 21 of the swing lever 28 engages with its circular extending around its axis of rotation area 25 its contact surface to the roller 29 in a reciprocating motion between the point a and the point B , wherein the valve 20 is not actuated.
  • the roller 32 of the drive lever 23 is on the elevation curve of the actuating cam 33 of the actuating camshaft 22, whereby the drive lever 23 performs a counterclockwise rotation about the axis of rotation of its cam roller 30 and the pivot lever 21 via the hinge 24 is pivoted to the right.
  • the roller 29 of the rocker arm 28 is moved in the direction of the point B from the point A, in which a continuous keeping closed of the valve 20 is set.
  • the engagement of the roller 29 of the rocker arm 28 shifts in addition in the direction of the point B.
  • a torsion spring 35 are arranged as a return spring on both sides of the pivot lever 21 , of which one leg has the axis of the arranged on the pivot lever 21 and drive lever 23 pivot 24 and the other leg arranged in the actuating arm 36 dome 37 as an abutment.
  • the axis C to the axis D reduces the torsion springs 35 in their rotation angle, whereby the force acting on the pivot lever 21 restoring force of the torsion springs 35 is increased.
  • the actuating arm 36 can be combined with the adjusting cam 33 to form a component.
  • the drive lever 23 in addition to its pivotal movement also performs a longitudinal movement, whereby the drive lever 23 with its roller 32 on the actuating cam 33 performs a reciprocating motion.
  • the valve lift curve generated by the cam 31 can be changed.
  • an adjusting cam 33 can be advantageously arranged rotatably on the actuating cam shaft 22 with a plurality of contact surfaces, whereby the roller 32 of the drive lever 23 by a corresponding rotation of the actuating cam shaft 22 to each other different contact surfaces of the actuating cam 33 can be provided.
  • the elevation curves of the contact surfaces of the control cam 11 may be curved inward, arched outwards, rectilinear or s-shaped, whereby for each set valve stroke length different valve opening times at different valve lift curves can be provided and an engine can be operated in different work programs.
  • the provided for the largest valve lift contact surface of the actuating cam 33 can be extended by means of a subsequent arc here, which has the axis of rotation of the actuating camshaft 22 as a center, whereby by means of a rotation of the actuating camshaft 22 by the hereby changed width of the engagement of the roller 32nd of the drive lever 23 in the circular arc of the contact surface of the actuating cam 33 at the largest valve lift the valve lift curve can be changed.
  • Valve controls be designed such that by a rotation of the actuating camshaft 22 by the drive lever 23 first a pivot lever 21 for the operation of a valve 20 and thereafter for the upper power range of the other pivot lever 21 is set for the actuation of the other valve 20 , after which both valves 20 be operated simultaneously.
  • the engine can also be operated alternately with an intake port, wherein for the operation of the engine in idle and in the lower power range, an inlet channel with a small diameter and a valve 20 with the small plate diameter and for the medium power range by the circuit of the valve 20, an intake passage having the larger diameter and a valve 20 may be used with the larger disc diameter for the operation of the engine with the smaller disc diameter in a permanent keeping closed.
  • an intake passage having the larger diameter and a valve 20 may be used with the larger disc diameter for the operation of the engine with the smaller disc diameter in a permanent keeping closed.
  • Fig. 4 shows the valve timing in the setting of the largest valve lift and the longest valve opening time, wherein the roller 32 of the drive lever 23 is at the highest predetermined point of the elevation curve of the control cam 33 and the cam roller 30 engages in the base circle of the cam 31 .
  • the actuator arm 36 has placed with the rotation of the actuating camshaft 22 counterclockwise on the axis D , whereby the torsion spring 35 by the resulting smaller bias advantageously a reduced restoring force on the pivot lever 21 exerts.
  • the drive lever 23 on both sides drive a pivot lever 21 which actuates a valve 20 via a rocker arm 28 .

Abstract

The invention concerns a drive and displacement system for mechanically variable valve-controlled distribution. Said system comprises drive levers which drive pivoting levers, actuating valves, via oscillating levers, such that the lifting of the valves and the opening time of the valves can be constantly adjusted, up to a permanent closing position of said valves, thereby enabling the use of said valve-controlled distribution for choke-free load control. The invention is characterized in that said pivoting levers (2) are driven by a drive lever (4), which is driven more or less in its center by a cam roller (13) or a contact surface. Said drive lever is urged to be engaged, at its upper end, with a control cam (11) of a drive camshaft (3) by means of a roller (12) or a contact surface, and then drives, with its lower end, said pivoting lever (2) via a revolute joint (5), said pivoting lever (2) being mounted on the drive camshaft (3) so as to be able to perform a rotational movement thereon. The driving of the pivoting lever (2) by means of a separate drive lever (4) provides mechanically variable valve-controlled distribution with simple and compact structure, said pre-assembled valve-controlled distribution capable being readily mounted in the cylinder head.

Description

Die vorliegende Erfindung bezieht sich auf ein Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen mit einem auf einer Welle oder Achse drehbar gelagerten Schwenkhebel, der durch den Eingriff in die Rolle oder Kontaktfläche eines Schwinghebels die Ventile betätigt, wobei die Welle oder Achse in mit dem Zylinderkopf fest verbundenen Lagerungen angeordnet ist. Die Schwenkhebel können hierbei auch Kipp- oder Winkelhebel antreiben. Siehe zum Beispiel EP 1 039 103.The present invention relates to a drive and adjustment system for mechanically variable valve controls with one on a shaft or axle rotatably mounted pivot lever, by engaging in the role or Contact surface of a rocker arm actuates the valves, wherein the shaft or axle is arranged in fixedly connected to the cylinder head bearings. The Swing levers can also drive tilt or angle lever. See, for example, EP 1 039 103.

Die Ventilsteuerungen können gemäß der Erfindung derart eingestellt werden, dass die Ventile von einem ständigen Geschlossenhalten stufenlos bis zu dem größten vorgesehenen Ventilhub bei einer sich gleichzeitig mit der Vergrößerung des Ventilhubes stufenlos verlängernden Ventilöffnungsdauer betätigt werden. Hierdurch sind die Ventilsteuerungen für eine drosselfreie Laststeuerung geeignet.The valve controls can be adjusted according to the invention such that the valves can be steplessly adjusted from a constant closed to the largest planned valve lift at a time coinciding with the magnification the valve lift continuously variable valve opening duration are actuated. As a result, the valve controls for a throttle-free load control are suitable.

Die Ventilsteuerungen können neben dem Antrieb eines Ventiles auch gleichzeitig mehrere Ventile betätigen, wobei auch wahlweise nur ein Ventil eines Arbeitsraumes betätigt werden kann, während das andere Ventil des Arbeitsraumes ständig geschlossen gehalten ist.The valve controls can in addition to the drive of a valve also simultaneously actuate several valves, and optionally only one valve of a Working space can be actuated while the other valve of the working space is always kept closed.

Gemäß der Erfindung werden die Schwenkhebel durch einen Antriebshebel angetrieben, der mit seinem unteren Ende den Schwenkhebel über ein Drehgelenk antreibt, wobei der Antriebshebel an seinem oberen Ende mittels einer Rolle oder seiner Kontaktfläche in einen Stellnocken einer Stellnockenwelle eingreift und mittig über eine Nockenrolle oder seine Kontaktfläche von einem Nocken angetrieben wird.According to the invention, the pivot lever by a drive lever driven, with its lower end the pivot lever via a swivel joint drives, wherein the drive lever at its upper end by means of a roller or engages its contact surface in a parking cam of a parking camshaft and centered driven by a cam via a cam roller or its contact surface becomes.

In einer weiteren Bauweise treibt der Antriebshebel ebenfalls mit seinem unteren Ende den Schwenkhebel über ein Drehgelenk an, wobei jedoch der Antriebshebel an seinem oberen Ende über eine Nockenrolle oder seine Kontaktfläche von einem Nocken angetrieben wird und mittig mittels einer Rolle oder seiner Kontaktfläche in einen Stellnocken einer Stellnockenwelle eingreift.In another construction, the drive lever also drives with its lower End the pivot lever via a swivel joint, but with the drive lever at its upper end via a cam roller or its contact surface of one Cam is driven and centrally by means of a roller or its contact surface in engages an adjusting cam of an actuating camshaft.

Durch den Antrieb des Schwenkhebels mittels eines gesonderten Antriebshebels wird die Herstellung von mechanisch variablen Ventilsteuerungen in einer einfachen und Raum sparenden Bauweise ermöglicht, wobei die Ventilsteuerungen weitgehend vormontiert in einfacher Weise in den Zylinderkopf eingesetzt werden können.By driving the pivot lever by means of a separate drive lever The production of mechanically variable valve controls in a simple and space-saving design allows, with the valve controls largely pre-assembled in a simple manner can be used in the cylinder head can.

Durch den Eingriff des Antriebshebels in einen Stellnocken einer Stellnockenwelle und dadurch, dass der Antriebshebel neben seiner Schwenkbewegung auch eine Längsbewegung ausführt und hierdurch mit seiner Rolle oder Kontaktfläche auf der Kontaktfläche des Stellnocken eine Hin- und Herbewegung ausführt, kann durch die Ventilsteuerungen bei einer Anordnung eines sternförmigen Stellnockens auf der Stellnockenwelle, der einander unterschiedliche Kontaktflächen aufweist, durch eine entsprechende Drehbewegung der Stellnockenwelle die Kraftmaschine eines Fahrzeuges nach mehreren Programmen betrieben werden, bei denen zum einen ein wirtschaftlicher Betrieb und zum anderen ein sportlicher Betrieb sowie ein zwischen diesen Betriebsarten liegender Betrieb der Kraftmaschine eingestellt werden kann. Durch die sternförmige Anordnung von Stellnocken auf der Stellnockenwelle wird die Herstellung einer mechanischen, weitgehend vollvariablen Ventilsteuerung ermöglicht, da zu jeder eingestellten Ventilhublänge verschiedene Ventilöffnungszeiten zugeordnet werden können.By the engagement of the drive lever in a parking cam of an actuating camshaft and in that the drive lever in addition to its pivoting movement and a Performs longitudinal movement and thereby with its role or contact surface on the Contact surface of the actuating cam performs a reciprocating motion, can through the Valve controls in an arrangement of a star-shaped adjusting cam on the Stellnockenwelle having different contact surfaces, through a corresponding rotational movement of the actuating camshaft, the engine of a Vehicle operated by several programs, where on the one hand an economic operation and on the other a sporty enterprise as well as a adjusted between these modes of operation of the engine can be. Due to the star-shaped arrangement of adjusting cams on the Stellnockenwelle is the production of a mechanical, largely fully variable Valve control allows, as to each set valve stroke different Valve opening times can be assigned.

Fig. 1 zeigt eine Ventilsteuerung in der Seitenansicht mit einem durch einen Antriebshebel gebildeten Antriebs- und Verstellsystem, wobei der Antriebshebel etwa mittig über eine Nockenrolle angetrieben wird; mit einer an seinem oberen Ende angeordneten Rolle in einen auf einer Stellnockenwelle drehfest gelagerten Stellnocken eingreift und über ein an seinem unteren Ende angeordnetes Drehgelenk einen auf der Stellnockenwelle drehbar gelagerten Schwenkhebel antreibt. Die Ventilsteuerung ist in der Fig. 1 in der Stellung des ständigen Geschlossenhaltens der Ventile dargestellt. Fig. 1 shows a valve control in the side view with a driving lever formed by a drive and adjustment, wherein the drive lever is driven approximately centrally via a cam roller; arranged with a arranged at its upper end role in a rotationally fixed manner on an actuating camshaft adjusting cam engages and drives a arranged on its lower end pivot a rotatably mounted on the actuating cam pivot lever. The valve control is shown in Fig. 1 in the position of the constant closed keeping of the valves.

Fig. 2 zeigt die Ventilsteuerung der Fig. 1 in der Seitenansicht in der Stellung des größten Ventilhubes und der längsten Ventilöffnungszeit. Fig. 2 shows the valve control of Fig. 1 in the side view in the position of the largest valve lift and the longest valve opening time.

Fig. 3 zeigt eine Ventilsteuerung in der Seitenansicht mit einem durch einen Antriebshebel gebildeten Antriebs- und Verstellsystem, wobei der Antriebshebel an seinem oberen Ende über eine Nockenrolle angetriebenen wird; mit einer etwa mittig angeordneten Rolle in einen auf einer Stellnockenwelle drehfest gelagerten Stellnocken eingreift und über ein an seinem unteren Ende angeordnetes Drehgelenk einen auf der Stellnockenwelle drehbar gelagerten Schwenkhebel antreibt. Die Ventilsteuerung ist in der Fig. 3 in der Stellung des ständigen Geschlossenhaltens der Ventile dargestellt. Fig. 3 shows a valve control in the side view with a drive lever formed by a drive and adjustment, wherein the drive lever is driven at its upper end via a cam roller; engages with an approximately centrally arranged role in a rotationally fixed on an actuating camshaft adjusting cam and drives a arranged on its lower end pivot a rotatably mounted on the actuating cam pivot lever. The valve control is shown in Fig. 3 in the position of the constant closed keeping of the valves.

Fig. 4 zeigt die Ventilsteuerung der Fig. 3 in der Seitenansicht in der Stellung des größten Ventilhubes und der längsten Ventilöffnungszeit. Fig. 4 shows the valve control of Fig. 3 in the side view in the position of the largest valve lift and the longest valve opening time.

Gemäß der Erfindung können die Schwenkhebel auch auf einer gesonderten Achse drehbar gelagert werden, die mit dem Zylinderkopf fest verbunden ist, Hierbei weisen die Ventilsteuerungen einen Antriebshebel auf, der sich an seinem oberen Ende auf einem Stellnocken einer nur als Steuerwelle vorgesehenen Stellnockenwelle mittels einer Rolle abstützt und über das an seinem unteren Ende angeordnete Drehgelenk den Schwenkhebel dadurch antreibt, dass der Antriebshebel selbst über eine zwischen der in den Stellnocken eingreifenden Rolle und dem Drehgelenk angeordnete Nockenrolle von einem Nocken angetrieben wird. Der Antriebshebel kann auch an seinem oberen Ende über eine Nockenrolle von einem Nocken angetrieben werden, wobei der Antriebshebel die in den Stellnocken der Stellnockenwelle eingreifende Rolle zwischen der Nockenrolle und dem an dem unteren Ende des Antriebshebels angeordneten Drehgelenk aufweist. Ein Nockeneingriff ist hier von beiden Längsseiten des Antriebshebels möglich, wobei die Abstützung durch den Stellnocken immer auf der dem Nockeneingriff entgegengesetzten Seite erfolgt. Gegenüber den Ventilsteuerungen der Fig. 1 und 2 ist der Raumbedarf der Ventilsteuerungen mit der gesonderten Achse, auf der die Schwenkhebel gelagert sind, erheblich größer. In vorteilhafter Weise lässt sich hier die Stellnockenwelle einteilig geschmiedet oder gegossen herstellen.According to the invention, the pivot lever can also be rotatably mounted on a separate axis, which is fixedly connected to the cylinder head, Here, the valve controls on a drive lever which is supported at its upper end on an actuating cam provided only as a control shaft actuating cam shaft by means of a roller and via the arranged at its lower end pivot the pivot lever thereby drives that the drive lever itself is driven by a cam between the engaging in the adjusting cam roller and the pivot cam roller arranged. The drive lever can also be driven at its upper end via a cam roller by a cam, wherein the drive lever has engaging in the adjusting cam of the actuating camshaft roller between the cam roller and arranged at the lower end of the drive lever rotary joint. A cam engagement is possible here from both longitudinal sides of the drive lever, wherein the support by the adjusting cam always takes place on the side opposite to the cam engagement. Compared with the valve controls of FIGS. 1 and 2 , the space requirement of the valve controls with the separate axis on which the pivot lever are mounted considerably larger. Advantageously, here the control cam can be forged or cast in one piece.

Bei der Stellnockenwelle der Ventilsteuerungen gemäß Fig. 1 und 2, die auch als Lagerung der Schwenkhebel vorgesehen ist, sind die Stellnocken über eine Stift-Niet- oder Schraubverbindung drehfest mit der Stellnockenwelle verbunden, um geteilte Lagerungen bei den Schwenkhebeln zu vermeiden.In the actuating camshaft of the valve controls of FIG. 1 and 2 , which is also provided as a bearing of the pivot lever, the adjusting cams are rotatably connected via a pin rivet or screw with the actuating camshaft to avoid shared bearings in the pivoting levers.

Weist die Stellnockenwelle in dem Zylinderkopf geteilte Lagerungen auf, kann die Stellnockenwelle mit den auf ihr montierten Schwenkhebeln und mit den an den Schwenkhebeln über das Drehgelenk verbundenen Antriebshebeln als Einheit in den Zylinderkopf eingesetzt und dort montiert werden. Does the control camshaft in the cylinder head shared bearings, the Stellnockenwelle with mounted on her swivel levers and with the s.den Swing levers connected via the swivel drive levers as a unit in the cylinder head used and mounted there.

Sind die Schwenkhebel auf einer Achse in dem Zylinderkopf in geteilten Lagerungen angeordnet, kann auch die Achse mit den Schwenkhebeln, mit den an den Schwenkhebeln über das Drehgelenk verbundenen Antriebshebeln und mit der mit den Antriebshebeln verbundenen Stellnockenwelle als Einheit in den Zylinderkopf eingesetzt und dort montiert werden, wenn auch die Lagerungen der Stellnockenwelle ebenfalls geteilt ausgeführt sind.Are the pivot levers on an axle in the cylinder head in split Also, the axle with the pivoting levers, with the bearings can be arranged the pivot levers connected via the hinge drive levers and with the with the drive levers associated actuating camshaft as a unit in the Cylinder head used and mounted there, although the bearings of the Stellnockenwelle also run divided.

Fig. 1 zeigt eine mechanisch variable Ventilsteuerung in der Einstellung des ständigen Geschlossenhaltens des Ventiles 1, bei dem ein Schwenkhebel 2, der auf einer Stellnockenwelle 3 drehbar gelagert ist und von einem für den Antrieb und die Einstellung vorgesehenen Antriebshebel 4 über ein Drehgelenk 5 in eine Schwenkbewegung versetzt wird. Hierbei ist das Drehgelenk 5 an dem unteren Ende des Antriebshebels 4 und in der Nähe der aus zwei Bereichen 6 und 7 gebildeten Kontaktfläche des Schwenkhebels 2 angeordnet und die als Lagerung des Schwenkhebels 2 dienende Stellnockenwelle 3 ist in fest mit dem Zylinderkopf 8 verbundenen Lagern angeordnet. Durch die aus zwei Bereichen 6 und 7 gebildete Kontaktfläche des Schwenkhebels 2 wird ein das Ventil 1 betätigender Schwinghebel 9 über seine Rolle 10 angetrieben, wobei der Schwinghebel 9 auch über eine Kontaktfläche angetrieben werden kann. Die Stellnockenwelle 3 weist einen drehfest mit ihr verbundenen Stellnocken 11 auf, in den der Antriebshebel 4 mit einer an seinem oberen Ende angeordneten Rolle 12 eingreift. Für seinen Antrieb weist der Antriebshebel 4 zwischen dem Drehgelenk 5 und der Rolle 12 eine Nockenrolle 13 auf, in die ein Nocken 14 eingreift. Der Bereich 6 der Kontaktfläche des Schwenkhebels 2 verläuft kreisförmig um die Drehachse der Steuerwelle 3 und ist für ein ständiges Geschlossenhalten des Ventiles 1 vorgesehen. Der Bereich 7 der Kontaktfläche des Schwenkhebels 2 weist eine nach innen gewölbte, als Nase geformte Krümmung auf und ist für die Betätigung des Ventiles 1 vorgesehen. Fig. 1 shows a mechanically variable valve control in the setting of the constant closed keeping of the valve 1, in which a pivoting lever 2 which is rotatably mounted on a control camshaft 3 and provided by a provided for the drive and the adjustment lever 4 via a rotary joint 5 in a Pivoting movement is offset. Here, the rotary joint is arranged at the lower end of the drive lever 4 and in the vicinity of the contact surface formed of two sections 6 and 7 of the pivot lever 2 5 and serves as a bearing of the pivot lever 2 actuating cam shaft 3 is disposed in fixed to the cylinder head 8 bearings. By formed of two areas 6 and 7 contact surface of the pivot lever 2 , a valve 1 is actuated rocker arm 9 is driven via its roller 10 , wherein the rocker arm 9 can also be driven via a contact surface. The actuating camshaft 3 has a control cam associated with its actuating cam 11 , in which the drive lever 4 engages with a roller 12 arranged at its upper end. For its drive, the drive lever 4 between the pivot 5 and the roller 12 has a cam roller 13 , in which a cam 14 engages. The region 6 of the contact surface of the pivot lever 2 extends in a circle around the axis of rotation of the control shaft 3 and is provided for a constant closed keeping of the valve 1 . The area 7 of the contact surface of the pivot lever 2 has an inwardly curved, shaped as a nose curve and is provided for the actuation of the valve 1 .

Die Rolle 12 des Antriebshebels 4 greift hier in den Grundkreis des auf der Stellnockenwelle 3 angeordneten Stellnockens 11 ein, die Nockenrolle 13 befindet sich auf dem Grundkreis des Nockens 14 und die Rolle 10 des Schwinghebels 9 steht in dem Punkt A, dem Anfangspunkt des Bereiches 6 der Kontaktfläche des Schwenkhebels 2. Während der Antriebshebel 4 von dem Nocken 14 angetrieben wird, greift der Schwenkhebel 2 mit seinem kreisförmig um seine Drehachse verlaufenden Bereich 6 seiner Kontaktfläche in die Rolle 10 des Schwinghebels 9 in einer Hin- und Herbewegung zwischen dem Punkt A und dem Punkt B ein, wobei das Ventil 1 nicht betätigt wird.The roller 12 of the drive lever 4 engages here in the base circle of which is arranged on the adjusting cam shaft 3 controlling pin 11, which cam roller 13 is located on the base circle of the cam 14 and the roller 10 of the swing lever 9 is in the point A, the starting point of the region 6 the contact surface of the pivot lever 2. During the driving lever 4 is driven by the cam 14, the pivot lever 2 engages with its circular extending around its pivot axis region 6 of its contact surface to the roller 10 of the rocker arm 9 in a reciprocating motion between the point a and the point B , wherein the valve 1 is not actuated.

Wird die Stellnockenwelle 3 in dem Uhrzeigersinn gedreht, stellt sich die Rolle 12 des Antriebshebels 4 auf die Erhebungskurve des Stellnockens 11 der Stellnockenwelle 3, wodurch der Antriebshebel 4 eine Drehbewegung in dem Uhrzeigersinn um die Drehachse seiner Nockenrolle 13 ausführt und der Schwenkhebel 2 über das Drehgelenk 5 nach links verschwenkt wird. Hierbei wird die Rolle 10 des Schwinghebels 9 von dem Punkt A, in dem ein ständiges Geschlossenhalten des Ventiles 1 eingestellt ist, in die Richtung des Punktes B verstellt. Durch den hiernach erfolgenden Eingriff der Nockenrolle 13 in die Erhebungskurve des Nockens 14 verschiebt sich der Eingriff der Rolle 10 des Schwinghebels 9 zusätzlich in die Richtung des Punktes B. If the actuating camshaft 3 is rotated in the clockwise direction, the roller 12 of the drive lever 4 is on the elevation curve of the actuating cam 11 of the actuating camshaft 3, whereby the drive lever 4 performs a rotational movement in the clockwise direction about the axis of rotation of its cam roller 13 and the pivot lever 2 via the hinge 5 is pivoted to the left. Here, the roller 10 of the rocker arm 9 is moved in the direction of the point B from the point A, in which a continuous keeping closed of the valve 1 is set. By the subsequent engagement of the cam roller 13 in the elevation curve of the cam 14 , the engagement of the roller 10 of the rocker arm 9 shifts in addition in the direction of the point B.

Wenn die Rolle 12 des Antriebshebels 4 den höchsten festgelegten Punkt der Erhebungskurve des Stellnockens 11 erreicht hat und die Nockenrolle 13 des Antriebshebels 4 in den Grundkreis des Nockens 14 eingreift, beginnt der Eingriff der Rolle 10 des Schwinghebels 9 in dem Punkt B, wobei hier der größte Ventilhub und die längste Ventilöffnungsdauer eingestellt ist.When the roller 12 of the drive lever 4 has reached the highest defined point of the elevation curve of the actuating cam 11 and the cam roller 13 of the drive lever 4 engages in the base circle of the cam 14 , the engagement of the roller 10 of the rocker arm 9 begins in the point B, here largest valve lift and the longest valve opening duration is set.

Erfolgt der Eingriff der Rolle 10 des Schwinghebels 9 in einem kurzen Abstand zu dem Punkt A in die Richtung des Punktes B, wenn die Nockenrolle 13 sich auf dem Grundkreis des Nockens 14 befindet, und greift die Nockenrolle 13 des Antriebshebels 4 nun in die Erhebungskurve des Nockens 14 ein, beginnt die Rolle 10, den Punkt B zu überschreiten und in den vorderen, nasenförmigen Bereich 7 der Kontaktfläche des Schwenkhebels 2 einzugreifen. Hierdurch wird das Ventil 1 mit einem kurzen Ventilhub und einer kurzen Ventilöffnungszeit betätigt. Wird die Rolle 12 des Antriebshebels 4 weitergehend auf die Erhebungskurve des Stellnockens 11 der Stellnockenwelle 3 gestellt, vergrößert sich der Ventilhub und es verlängert sich die Ventilöffnungsdauer. Hierbei steht die Größe des Ventilhubes und die hiervon abhängige Länge der Ventilöffnungsdauer in Abhängigkeit von der Weite des Eingriffs der Rolle 10 des Schwinghebels 9 in den nasenförmigen Bereich 7 der Kontaktfläche des Schwenkhebels 2. If the engagement of the roller 10 of the oscillating lever 9 at a short distance to the point A in the direction of the point B, when the cam roller 13 is located on the base circle of the cam 14 , and the cam roller 13 of the drive lever 4 now engages in the elevation curve of the Cam 14 , the roller 10 begins to exceed the point B and to engage in the front, nose-shaped portion 7 of the contact surface of the pivot lever 2 . As a result, the valve 1 is actuated with a short valve lift and a short valve opening time. If the roller 12 of the drive lever 4 further set to the elevation curve of the actuating cam 11 of the actuating camshaft 3 , the valve lift increases and it extends the valve opening period. Here, the size of the valve lift and the dependent thereon length of the valve opening duration depending on the width of the engagement of the roller 10 of the rocker arm 9 in the nose-shaped portion 7 of the contact surface of the pivot lever . 2

Solange die Rolle 10 des Schwinghebels 9 in den nasenförmigen Bereich 7 der Kontaktfläche des Schwenkhebels 2 eingreift, erfolgt eine Rückstellung des Schwenkhebels 2 durch die Kraft der Ventilfeder 15, wobei sich die auf den Schwenkhebel 2 übertragene Rückstellkraft, wenn der Ventilhub verkleinert und die Ventilöffnungsdauer verkürzt wird, mit der Verstellung der Rolle 10 des Schwinghebels 9 in die Richtung des Bereiches 6 der Kontaktfläche des Schwenkhebels 2 verringert und wobei die Rückstellkraft nicht mehr vorhanden ist, wenn die Rolle 10 in den um die Drehachse des Schwenkhebels 2 kreisförmig verlaufenden Bereich 6 der Kontaktfläche des Schwenkhebels 2 eingreift. Aus diesem Grunde ist als Rückstellfeder eine Druckfeder 16 zwischen dem Schwenkhebel 2 und einem drehfest mit der Steuerwelle 3 verbundenen Stellarm 17 angeordnet, wobei sowohl der Schwenkhebel 2 einen Federteller 18 als auch der Stellarm 17 einen Federteller 19 aufweist.As long as the roller 10 of the rocking lever 9 engages in the nose-shaped portion 7 of the contact surface of the pivot lever 2 , a return of the pivot lever 2 by the force of the valve spring 15, wherein the force transmitted to the pivot lever 2 restoring force, as the valve lift decreases and shortens the valve opening duration is reduced with the adjustment of the roller 10 of the rocker arm 9 in the direction of the region 6 of the contact surface of the pivot lever 2 and wherein the restoring force is no longer present when the roller 10 in the circular axis about the axis of rotation of the pivot lever 2 extending portion 6 of the contact surface of the pivot lever 2 engages. For this reason, a compression spring 16 between the pivot lever 2 and a rotatably connected to the control shaft 3 actuating arm 17 is arranged as a return spring, wherein both the pivot lever 2 a spring plate 18 and the actuating arm 17 has a spring plate 19 .

In vorteilhafter Weise wird während der Verstellung der Ventilsteuerung auf einen geringeren Ventilhub und eine verkürzte Ventilöffnungsdauer, bei der sich die von der Ventilfeder 15 auf den Schwenkhebel 2 einwirkende Kraft vermindert, durch die hierbei mit der Steuerwelle 3 erfolgende Drehbewegung des Stellarmes 17 gegen den Uhrzeigersinn von der Achse C zu der Achse D die Druckfeder 16 in ihrer Länge verkürzt, wodurch die auf den Schwenkhebel 2 einwirkende Rückstellkraft der Druckfeder 16 vergrößert wird.Advantageously, during the adjustment of the valve control to a smaller valve lift and a shortened valve opening duration, in which the force acting on the pivot lever 2 by the valve spring 15, reduced by the case taking place with the control shaft 3 rotational movement of the actuating arm 17 in the counterclockwise direction the axis C to the axis D, the compression spring 16 is shortened in length, whereby the force acting on the pivot lever 2 restoring force of the compression spring 16 is increased.

In einfacher Weise kann der Stellarm 17 mit dem Stellnocken 11 zu einem Bauteil zusammengefasst sein.In a simple way, the actuating arm 17 can be combined with the actuating cam 11 to form a component.

Während der Schwenkbewegung des Schwenkhebels 2 führt der Antriebshebel 4 neben seiner Schwenkbewegung auch eine Längsbewegung aus; wodurch der Antriebshebel 4 mit seiner Rolle 12 auf dem Stellnocken 11 eine Hin- und Herbewegung ausführt. Durch die Formgebung der Erhebungskurve des Stellnockens 11 lässt sich die durch den Nocken 14 erzeugte Ventilerhebungskurve verändern.During the pivotal movement of the pivot lever 2 , the drive lever 4 in addition to its pivoting movement also performs a longitudinal movement; whereby the drive lever 4 with its roller 12 on the actuating cam 11 performs a reciprocating motion. Due to the shape of the elevation curve of the actuating cam 11 , the valve lift curve generated by the cam 14 can be changed.

Aus diesem Grunde kann vorteilhaft auf der Stellnockenwelle 3 ein mehrere Kontaktflächen aufweisender Stellnocken 11 drehfest angeordnet sein, wodurch die Rolle 12 des Antriebshebels 4 durch eine entsprechende Drehung der Stellnockenwelle 3 auf einander unterschiedliche Kontaktflächen des Stellnockens 11 gestellt werden kann. Hierbei können die Erhebungskurven der Kontaktflächen des Stellnockens 11 nach innen gewölbt, nach außen gewölbt, geradlinig oder s-förmig gestaltet sein, wodurch für jede eingestellte Ventilhublänge unterschiedliche Ventilöffnungszeiten bei unterschiedlichen Ventilerhebungskurven vorgesehen werden können und eine Kraftmaschine in unterschiedlichen Arbeitsprogrammen betrieben werden kann.For this reason, can advantageously be arranged rotatably on the actuating camshaft 3 a plurality of contact surfaces exhibiting actuating cam 11 , whereby the roller 12 of the drive lever 4 by a corresponding rotation of the actuating camshaft 3 to each other different contact surfaces of the actuating cam 11 can be made. Here, the elevation curves of the contact surfaces of the actuating cam 11 may be curved inward, arched outwards, rectilinear or s-shaped, whereby for each set valve stroke different valve opening times can be provided at different valve lift curves and an engine can be operated in different work programs.

In einfacher Weise kann die für den größten Ventilhub vorgesehene Kontaktfläche des Stellnockens 11 mittels eines sich hier anschließenden Kreisbogens verlängert werden, der als Mittelpunkt die Drehachse der Stellnockenwelle 3 aufweist, wodurch mittels einer Drehung der Stellnockenwelle 3 durch die hierbei veränderte Weite des Eingriffs der Rolle 12 des Antriebshebels 4 in den Kreisbogen der Kontaktfläche des Stellnockens 11 bei dem größten Ventilhub die Ventilerhebungskurve verändert werden kann.In a simple manner, the provided for the largest valve lift contact surface of the actuating cam 11 can be extended by means of a subsequent arc here, which has the center of rotation of the actuating camshaft 3 , whereby by means of a rotation of the actuating camshaft 3 by the hereby changed width of the engagement of the roller 12th of the drive lever 4 in the circular arc of the contact surface of the control cam 11 at the largest valve lift the valve lift curve can be changed.

Um eine Abschaltung eines Einlasskanals einer zwei Einlasskanäle aufweisenden Kraftmaschine zu bewirken, wodurch eine Kraftmaschine im Leerlauf und unteren Leistungsbereich für die Erzeugung eines vorteilhaften Dralls der Ansaugluft nur mit einem Einlasskanal betrieben werden kann, können die Kontaktflächen der Stellnocken 11 von zwei jeweils ein Ventil 1 betätigenden Ventilsteuerungen derart ausgebildet sein, dass durch eine Drehung der Stellnockenwelle 3 durch die Antriebshebel 4 zuerst ein Schwenkhebel 2 für die Betätigung eines Ventiles 1 und hiernach für den oberen Leistungsbereich der andere Schwenkhebel 2 für die Betätigung des anderes Ventiles 1 eingestellt wird, wonach beide Ventile 1 gleichzeitig betätigt werden.In order to effect shutdown of an intake passage of a dual intake passage type engine, whereby an idling and lower power range engine for generating favorable intake air swirl can be operated with only one intake passage, the contact surfaces of the parking cam 11 of two each actuate a valve 1 valve controllers be designed such that by a rotation of the adjusting cam shaft 3 by the driving lever 4 at first a pivot lever 2 for actuating a valve 1 and will hereinafter be set for the upper power range of the other pivot lever 2 for the actuation of the other valve 1, according to which both valves 1 be operated simultaneously.

Bei einer Anordnung von zwei Ventilen 1 mit einander unterschiedlichen Tellerdurchmessem kann die Kraftmaschine auch wechselseitig mit einem Einlasskanal vorteilhaft betrieben werden, wobei für den Betrieb der Kraftmaschine im Leerlauf und in dem unteren Leistungsbereich ein Einlasskanal mit einem kleinen Durchmesser und einem Ventil 1 mit dem kleinen Tellerdurchmesser und für den mittleren Leistungsbereich nach der Schaltung des Ventiles 1 mit dem kleineren Tellerdurchmesser in ein ständiges Geschlossenhalten ein Einlasskanal mit dem größeren Durchmesser und einem Ventil 1 mit dem größeren Tellerdurchmesser für den Betrieb der Kraftmaschine herangezogen werden können. Hierbei wird auch durch die unterschiedlichen Durchmesser der beiden Einlasskanäle und der Ventile 1 vorteilhaft ein Drall der Ansaugluft im oberen Leistungsbereich erzeugt, wenn beide Ventile 1 betätigt sind.In an arrangement of two valves 1 with different Tellerdurchmessem the engine can also be operated alternately with an intake port advantageous, wherein for the operation of the engine at idle and in the lower power range, an inlet channel with a small diameter and a valve 1 with the small plate diameter and an intake duct for the medium power range after the switching of the valve 1 with the smaller disc diameter in a permanent keeping closed with the larger diameter and a valve 1 with the major plate diameter to the operation of the engine can be used. In this case, a twist of the intake air in the upper power range is advantageously generated by the different diameters of the two inlet channels and the valves 1 , when both valves 1 are actuated.

Fig. 2 zeigt die Ventilsteuerung in der Einstellung des größten Ventilhubes und der längsten Ventilöffnungszeit, wobei sich die Rolle 12 des Antriebshebels 4 auf dem höchsten festgelegten Punkt der Erhebungskurve des Stellnockens 11 befindet und die Nockenrolle 13 in den Grundkreis des Nockens 14 eingreift. Der Stellarm 17 hat sich mit der Drehung der Stellnockenwelle 3 in dem Uhrzeigersinn auf die Achse C gestellt, wodurch die Druckfeder 16 durch die hierdurch erhaltene größere Länge in vorteilhafter Weise eine verminderte Rückstellkraft auf den Schwenkhebel 2 ausübt. Fig. 2 shows the valve timing in the setting of the largest valve lift and the longest valve opening time, wherein the roller 12 of the drive lever 4 is at the highest specified point of the elevation curve of the actuating cam 11 and the cam roller 13 engages in the base circle of the cam 14 . The actuator arm 17 has placed with the rotation of the actuating camshaft 3 in the clockwise direction on the axis C , whereby the compression spring 16 exerts a reduced restoring force on the pivot lever 2 by the greater length thus obtained in an advantageous manner.

Durch eine beiderseitige Verlängerung der Achse des Drehgelenkes 5 kann der Antriebshebel 4 beiderseitig einen Schwenkhebel 2 antreiben, der ein Ventil 1 über einen Schwinghebel 9 betätigt.By a mutual extension of the axis of the rotary joint 5 , the drive lever 4 on both sides drive a pivot lever 2 , which actuates a valve 1 via a rocker arm 9 .

Fig. 3 zeigt eine mechanisch variable Ventilsteuerung in der Einstellung des ständigen Geschlossenhaltens des Ventiles 20, bei dem ein Schwenkhebel 21, der auf einer Stellnockenwelle 22 drehbar gelagert ist und von einem für den Antrieb und die Einstellung vorgesehenen Antriebshebel 23 über ein Drehgelenk 24 in eine Schwenkbewegung versetzt wird. Hierbei ist das Drehgelenk 24 an dem unteren Ende des Antriebshebels 23 in der Nähe der aus zwei Bereichen 25 und 26 gebildeten Kontaktfläche des Schwenkhebels 21 angeordnet und die als Lagerung des Schwenkhebels 21 dienende Steuerwelle 22 ist in fest mit dem Zylinderkopf 27 verbundenen Lagern angeordnet. Durch die aus zwei Bereichen 25 und 26 gebildete Kontaktfläche des Schwenkhebels 21 wird ein das Ventil 20 betätigender Schwinghebel 28 über seine Rolle 29 angetrieben, wobei der Schwinghebel 28 auch über eine Kontaktfläche angetrieben werden kann. Für seinen Antrieb weist der Antriebshebel 23 an seinem oberen Ende eine Nockenrolle 30 auf, in die ein Nocken 31 eingreift. Zwischen der Nockenrolle 30 und dem Drehgelenk 24 des Antriebshebels 23 ist eine Rolle 32 angeordnet, die in einen drehfest mit der Stellnockenwelle 22 verbundenen Stellnocken 33 eingreift. Der Bereich 25 der Kontaktfläche des Schwenkhebels 21 verläuft kreisförmig um die Drehachse der Stellnockenwelle 22 und ist für ein ständiges Geschlossenhalten des Ventiles 20 vorgesehen. Der Bereich 26 der Kontaktfläche des Schwenkhebels 21 weist eine nach innen gewölbte, als Nase geformte Krümmung auf und ist für die Betätigung des Ventiles 20 vorgesehen. Fig. 3 shows a mechanically variable valve control in the setting of the constant closed keeping of the valve 20, in which a pivoting lever 21 which is rotatably mounted on a control camshaft 22 and provided by a provided for the drive and the adjustment lever 23 via a rotary joint 24 in a Pivoting movement is offset. Here, the rotary joint 24 is arranged at the lower end of the drive lever 23 in the vicinity of the two regions 25 and 26 contact surface formed of the pivot lever 21 and serving as a bearing of the pivot lever 21 control shaft 22 is disposed in fixed to the cylinder head 27 camps. By formed of two regions 25 and 26 contact surface of the pivot lever 21 , a valve 20 is actuated rocker arm 28 is driven via its roller 29 , wherein the rocker arm 28 can also be driven via a contact surface. For its drive, the drive lever 23 at its upper end to a cam roller 30 , in which a cam 31 engages. Between the cam roller 30 and the rotary joint 24 of the drive lever 23 , a roller 32 is arranged, which engages in a rotatably connected to the actuating cam shaft 22 adjusting cam 33 . The region 25 of the contact surface of the pivot lever 21 extends in a circle around the axis of rotation of the actuating camshaft 22 and is provided for a continuous closed keeping of the valve 20 . The region 26 of the contact surface of the pivot lever 21 has an inwardly curved, shaped as a nose curvature and is provided for the actuation of the valve 20 .

Die Rolle 32 des Antriebshebels 23 greift hier in den Grundkreis des auf der Stellnockenwelle 22 angeordneten Stellnockens 33 ein, die Nockenrolle 30 befindet sich auf dem Grundkreis des Nockens 31 und die Rolle 29 des Schwinghebels 28 steht in dem Punkt A, dem Anfangspunkt des Bereiches 25 der Kontaktfläche des Schwenkhebels 21. Während der Antriebshebel 23 von dem Nocken 31 angetrieben wird, greift der Schwenkhebel 21 mit seinem kreisförmig um seine Drehachse verlaufenden Bereich 25 seiner Kontaktfläche in die Rolle 29 des Schwinghebels 28 in einer Hin- und Herbewegung zwischen dem Punkt A und dem Punkt B ein, wobei das Ventil 20 nicht betätigt wird.The roller 32 of the drive lever 23 engages here in the base circle of which is arranged on the actuating camshaft 22 controlling pin 33, which cam roller 30 is located on the base circle of the cam 31 and the roller 29 of the swing lever 28 is in the point A, the starting point of the region 25 the contact surface of the pivot lever 21. While the drive lever 23 is driven by the cam 31, the pivot lever 21 of the swing lever 28 engages with its circular extending around its axis of rotation area 25 its contact surface to the roller 29 in a reciprocating motion between the point a and the point B , wherein the valve 20 is not actuated.

Wird die Steuerwelle 22 gegen den Uhrzeigersinn gedreht, stellt sich die Rolle 32 des Antriebshebels 23 auf die Erhebungskurve des Stellnockens 33 der Stellnockenwelle 22, wodurch der Antriebshebel 23 eine Drehbewegung gegen den Uhrzeigersinn um die Drehachse seiner Nockenrolle 30 ausführt und der Schwenkhebel 21 über das Drehgelenk 24 nach rechts verschwenkt wird. Hierbei wird die Rolle 29 des Schwinghebels 28 von dem Punkt A, in dem ein ständiges Geschlossenhalten des Ventiles 20 eingestellt ist, in die Richtung des Punktes B verstellt. Durch den hiernach erfolgenden Eingriff der Nockenrolle 30 in die Erhebungskurve des Nockens 31 verschiebt sich der Eingriff der Rolle 29 des Schwinghebels 28 zusätzlich in die Richtung des Punktes B. If the control shaft 22 is rotated counterclockwise, the roller 32 of the drive lever 23 is on the elevation curve of the actuating cam 33 of the actuating camshaft 22, whereby the drive lever 23 performs a counterclockwise rotation about the axis of rotation of its cam roller 30 and the pivot lever 21 via the hinge 24 is pivoted to the right. Here, the roller 29 of the rocker arm 28 is moved in the direction of the point B from the point A, in which a continuous keeping closed of the valve 20 is set. By the subsequent engagement of the cam roller 30 in the elevation curve of the cam 31 , the engagement of the roller 29 of the rocker arm 28 shifts in addition in the direction of the point B.

Wenn die Rolle 32 des Antriebshebels 23 den höchsten festgelegten Punkt der Erhebungskurve des Stellnockens 33 erreicht hat und die Nockenrolle 30 des Antriebshebels 23 in den Grundkreis des Nockens 31 eingreift, beginnt der Eingriff der Rolle 29 des Schwinghebels 28 in dem Punkt B, wobei hier der größte Ventilhub und die längste Ventilöffnungsdauer eingestellt ist.When the roller 32 of the drive lever 23 has reached the highest fixed point of the elevation curve of the actuating cam 33 and the cam roller 30 of the drive lever 23 engages in the base circle of the cam 31 , the engagement of the roller 29 of the rocker arm 28 begins in the point B, here largest valve lift and the longest valve opening duration is set.

Erfolgt der Eingriff der Rolle 29 des Schwinghebels 28 in einem kurzen Abstand zu dem Punkt A in die Richtung des Punktes B, wenn die Nockenrolle 30 sich auf dem Grundkreis des Nockens 31 befindet und greift die Nockenrolle 30 des Antriebshebels 23 nun in die Erhebungskurve des Nockens 31 ein, beginnt die Rolle 29, den Punkt B zu überschreiten und in den vorderen, nasenförmigen Bereich 26 der Kontaktfläche des Schwenkhebels 21 einzugreifen. Hierdurch wird das Ventil 20 mit einem kurzen Ventilhub und einer kurzen Ventilöffnungszeit betätigt. Wird die Rolle 32 des Antriebshebels 23 weitergehend auf die Erhebungskurve des Stellnockens 33 der Stellnockenwelle 22 gestellt, vergrößert sich der Ventilhub und es verlängert sich die Ventilöffnungsdauer. Hierbei steht die Größe des Ventilhubes und die hiervon abhängige Länge der Ventilöffnungsdauer in Abhängigkeit von der Weite des Eingriffs der Rolle 29 des Schwinghebels 28 in den nasenförmigen Bereich 26 der Kontaktfläche des Schwenkhebels 21.Is the engagement of the roller 29 of the rocker arm 28 at a short distance to the point A in the direction of the point B, when the cam roller 30 is located on the base circle of the cam 31 and engages the cam roller 30 of the drive lever 23 now in the elevation curve of the cam 31 , the roller 29 starts to exceed the point B and to engage in the front nose-shaped portion 26 of the contact surface of the pivot lever 21 . As a result, the valve 20 is actuated with a short valve lift and a short valve opening time. If the roller 32 of the drive lever 23 is further set to the elevation curve of the actuating cam 33 of the actuating camshaft 22 , the valve lift increases and it extends the valve opening duration. Here, the size of the valve lift and the dependent thereon length of the valve opening duration depending on the width of the engagement of the roller 29 of the rocker arm 28 in the nose-shaped portion 26 of the contact surface of the pivot lever 21st

Solange die Rolle 29 des Schwinghebels 28 in den nasenförmigen Bereich 26 der Kontaktfläche des Schwenkhebels 21 eingreift, erfolgt eine Rückstellung des Schwenkhebels 21 durch die Kraft der Ventilfeder 34, wobei sich die auf den Schwenkhebel 21 übertragene Rückstellkraft, wenn der Ventilhub verkleinert und die Ventilöffnungsdauer verkürzt wird, mit der Verstellung der Rolle 29 des Schwinghebels 28 in die Richtung des Bereiches 25 der Kontaktfläche des Schwenkhebels 21 verringert und die Rückstellkraft nicht mehr vorhanden ist, wenn die Rolle 29 in den um die Drehachse des Schwenkhebels 21 kreisförmig verlaufenden Bereich 25 der Kontaktfläche des Schwenkhebels 21 eingreift. Aus diesem Grunde sind als Rückstellfeder beiderseitig von dem Schwenkhebel 21 je eine Drehfeder 35 angeordnet, von denen ein Schenkel die Achse des auf dem Schwenkhebel 21 und Antriebshebel 23 angeordneten Drehgelenkes 24 und der andere Schenkel einen in dem Stellarm 36 angeordneten Dom 37 als Widerlager besitzt.As long as the roller 29 of the rocker arm 28 engages the nose-shaped portion 26 of the contact surface of the pivot lever 21 , a reset of the pivot lever 21 is effected by the force of the valve spring 34, wherein the force transmitted to the pivot lever 21 restoring force, as the valve lift decreases and shortens the valve opening duration is reduced with the adjustment of the roller 29 of the rocker arm 28 in the direction of the region 25 of the contact surface of the pivot lever 21 and the restoring force is no longer present when the roller 29 in the about the axis of rotation of the pivot lever 21 circular area 25 of the contact surface of the Swing lever 21 engages. For this reason, a torsion spring 35 are arranged as a return spring on both sides of the pivot lever 21 , of which one leg has the axis of the arranged on the pivot lever 21 and drive lever 23 pivot 24 and the other leg arranged in the actuating arm 36 dome 37 as an abutment.

In vorteilhafter Weise werden während der Verstellung der Ventilsteuerung auf einen geringeren Ventilhub und eine verkürzte Ventilöffnungsdauer, bei der sich die von der Ventilfeder 20 auf den Schwenkhebel 21 einwirkende Kraft vermindert, durch die hierbei mit der Stelinockenwelle 22 erfolgende Drehbewegung des Stellarmes 36 in dem Uhrzeigersinn von der Achse C zu der Achse D die Drehfedern 35 in ihrem Drehwinkel verkleinert, wodurch die auf den Schwenkhebel 21 einwirkende Rückstellkraft der Drehfedern 35 vergrößert wird.Advantageously, during the adjustment of the valve control to a lesser valve lift and a shortened valve opening duration, at which the force acting on the pivot lever 21 of the valve spring 20 decreases, thereby taking place with the Stelinockenwelle 22 rotational movement of the actuating arm 36 in the clockwise direction the axis C to the axis D reduces the torsion springs 35 in their rotation angle, whereby the force acting on the pivot lever 21 restoring force of the torsion springs 35 is increased.

In einfacher Weise kann der Stellarm 36 mit dem Stellnocken 33 zu einem Bauteil zusammengefasst sein.In a simple way, the actuating arm 36 can be combined with the adjusting cam 33 to form a component.

Während der Schwenkbewegung des Schwenkhebels 21 führt der Antriebshebel 23 neben seiner Schwenkbewegung auch eine Längsbewegung aus, wodurch der Antriebshebel 23 mit seiner Rolle 32 auf dem Stellnocken 33 eine Hin- und Herbewegung ausführt. Durch die Formgebung der Erhebungskurve des Stellnockens 33 lässt sich die durch den Nocken 31 erzeugte Ventilerhebungskurve verändern.During the pivoting movement of the pivoting lever 21 , the drive lever 23 in addition to its pivotal movement also performs a longitudinal movement, whereby the drive lever 23 with its roller 32 on the actuating cam 33 performs a reciprocating motion. By shaping the elevation curve of the adjusting cam 33 , the valve lift curve generated by the cam 31 can be changed.

Aus diesem Grunde kann vorteilhaft drehfest auf der Stellnockenwelle 22 ein Stellnocken 33 mit mehreren Kontaktflächen angeordnet werden, wodurch die Rolle 32 des Antriebshebels 23 durch eine entsprechende Drehung der Stellnockenwelle 22 auf einander unterschiedliche Kontaktflächen des Stellnockens 33 gestellt werden kann. Hierbei können die Erhebungskurven der Kontaktflächen des Stellnockens 11 nach innen gewölbt, nach außen gewölbt, geradlinig oder s-förmig gestaltet sein, wodurch für jede eingestellte Ventilhublänge einander unterschiedliche Ventilöffnungszeiten bei verschiedenen Ventilerhebungskurven vorgesehen werden können und eine Kraftmaschine in unterschiedlichen Arbeitsprogrammen betrieben werden kann. For this reason, an adjusting cam 33 can be advantageously arranged rotatably on the actuating cam shaft 22 with a plurality of contact surfaces, whereby the roller 32 of the drive lever 23 by a corresponding rotation of the actuating cam shaft 22 to each other different contact surfaces of the actuating cam 33 can be provided. In this case, the elevation curves of the contact surfaces of the control cam 11 may be curved inward, arched outwards, rectilinear or s-shaped, whereby for each set valve stroke length different valve opening times at different valve lift curves can be provided and an engine can be operated in different work programs.

In einfacher Weise kann die für den größten Ventilhub vorgesehene Kontaktfläche des Stellnockens 33 mittels eines sich hier anschließenden Kreisbogens verlängert werden, der als Mittelpunkt die Drehachse der Stellnockenwelle 22 aufweist, wodurch mittels einer Drehung der Stellnockenwelle 22 durch die hierbei veränderte Weite des Eingriffs der Rolle 32 des Antriebshebels 23 in den Kreisbogen der Kontaktfläche des Stellnockens 33 bei dem größten Ventilhub die Ventilerhebungskurve verändert werden kann.In a simple manner, the provided for the largest valve lift contact surface of the actuating cam 33 can be extended by means of a subsequent arc here, which has the axis of rotation of the actuating camshaft 22 as a center, whereby by means of a rotation of the actuating camshaft 22 by the hereby changed width of the engagement of the roller 32nd of the drive lever 23 in the circular arc of the contact surface of the actuating cam 33 at the largest valve lift the valve lift curve can be changed.

Um eine Abschaltung eines Einlasskanals einer zwei Einlasskanäle aufweisenden Kraftmaschine zu bewirken, wodurch eine Kraftmaschine im Leerlauf und unteren Leistungsbereich für die Erzeugung eines vorteilhaften Dralls der Ansaugluft nur mit einem Ansaugkanal betrieben werden kann, können die Kontaktflächen der Stellnocken 33 von zwei jeweils ein Ventil 20 betätigenden Ventilsteuerungen derart ausgebildet sein, dass durch eine Drehung der Stellnockenwelle 22 durch die Antriebshebel 23 zuerst ein Schwenkhebel 21 für die Betätigung eines Ventiles 20 und hiernach für den oberen Leistungsbereich der andere Schwenkhebel 21 für die Betätigung des anderes Ventiles 20 eingestellt wird, wonach beide Ventile 20 gleichzeitig betätigt werden.In order to effect shutdown of an intake passage of an engine having two intake passages, whereby an engine at idle and lower power range can be operated with only one intake passage for generating favorable intake air swirl, the contact surfaces of the parking cams 33 can each actuate one valve 20 Valve controls be designed such that by a rotation of the actuating camshaft 22 by the drive lever 23 first a pivot lever 21 for the operation of a valve 20 and thereafter for the upper power range of the other pivot lever 21 is set for the actuation of the other valve 20 , after which both valves 20 be operated simultaneously.

Bei einer Anordnung von zwei Ventilen 20 mit einander unterschiedlichen Tellerdurchmessern kann die Kraftmaschine auch wechselseitig mit einem Einlasskanal vorteilhaft betrieben werden, wobei für den Betrieb der Kraftmaschine im Leerlauf und in dem unteren Leistungsbereich ein Einlasskanal mit einem kleinen Durchmesser und einem Ventil 20 mit dem kleinen Tellerdurchmesser und für den mittleren Leistungsbereich nach der Schaltung des Ventiles 20 mit dem kleineren Tellerdurchmesser in ein ständiges Geschlossenhalten ein Einlasskanal mit dem größeren Durchmesser und einem Ventil 20 mit dem größeren Tellerdurchmesser für den Betrieb der Kraftmaschine herangezogen werden können. Hierbei wird auch durch die unterschiedlichen Durchmesser der beiden Einlasskanäle und der Ventile 20 vorteilhaft ein Drall der Ansaugluft im oberen Leistungsbereich erzeugt, wenn beide Ventile 20 betätigt sind.In an arrangement of two valves 20 with different diameter diameters, the engine can also be operated alternately with an intake port, wherein for the operation of the engine in idle and in the lower power range, an inlet channel with a small diameter and a valve 20 with the small plate diameter and for the medium power range by the circuit of the valve 20, an intake passage having the larger diameter and a valve 20 may be used with the larger disc diameter for the operation of the engine with the smaller disc diameter in a permanent keeping closed. In this case, due to the different diameters of the two inlet channels and the valves 20, a swirl of the intake air in the upper power range is advantageously generated when both valves 20 are actuated.

Fig. 4 zeigt die Ventilsteuerung in der Einstellung des größten Ventilhubes und der längsten Ventilöffnungszeit, wobei sich die Rolle 32 des Antriebshebels 23 auf dem höchsten festgelegten Punkt der Erhebungskurve des Steuernockens 33 befindet und die Nockenrolle 30 in den Grundkreis des Nockens 31 eingreift. Der Stellarm 36 hat sich mit der Drehung der Stellnockenwelle 22 gegen den Uhrzeigersinn auf die Achse D gestellt, wodurch die Drehfeder 35 durch die hierdurch erhaltene kleinere Vorspannung in vorteilhafter Weise eine verminderte Rückstellkraft auf den Schwenkhebel 21 ausübt. Fig. 4 shows the valve timing in the setting of the largest valve lift and the longest valve opening time, wherein the roller 32 of the drive lever 23 is at the highest predetermined point of the elevation curve of the control cam 33 and the cam roller 30 engages in the base circle of the cam 31 . The actuator arm 36 has placed with the rotation of the actuating camshaft 22 counterclockwise on the axis D , whereby the torsion spring 35 by the resulting smaller bias advantageously a reduced restoring force on the pivot lever 21 exerts.

Durch eine beiderseitige Verlängerung der Achse des Drehgelenkes 24 kann der Antriebshebel 23 beiderseitig einen Schwenkhebel 21 antreiben, der ein Ventil 20 über einen Schwinghebel 28 betätigt.By a mutual extension of the axis of the rotary joint 24 , the drive lever 23 on both sides drive a pivot lever 21 which actuates a valve 20 via a rocker arm 28 .

Claims (12)

  1. Drive and displacement system for mechanically variable valve controls which have a pivot lever which is rotatably mounted on a spindle and which, in order to keep the valve constantly closed, has a circular contact surface and, in order to actuate the valve, has an adjoining lug-like contact surface for engagement of a roller or contact surface of a rocker lever which actuates the valve, wherein, in dependence upon the extent of the engagement of the roller or contact surface of the rocker lever, the valve can be actuated both with a continuously variable valve stroke and also with a valve opening duration dependent thereon, characterised in that the pivot lever (2) is driven by means of a drive and displacement system formed from a drive lever (4) via a swivel joint (5) of the drive lever (4), the extent of the pivoting movement being continuously adjustable, wherein the drive lever (4) is itself driven by a cam (14) via a cam roller (13) or contact surface and the pivot movement of the pivot lever (2) can be changed by the engagement of the drive lever (4) into the adjusting cam (11) of an adjusting cam shaft (3).
  2. Drive and displacement system for mechanically variable valve controls as claimed in claim 1, characterised in that the drive lever (4) is driven approximately centrally by a cam (14) via a cam roller (13) or via its contact surface, wherein the drive lever (4) at its upper end engages with a roller (12) or its contact surface into an adjusting cam (11) of an adjusting cam shaft (3) and with its lower end drives the pivot lever (2) via a swivel joint (5).
  3. Drive and displacement system for mechanically variable valve controls as claimed in claim 1, characterised in that the drive lever (23) is driven at its upper end by a cam (31) via a cam roller (30) or via its contact surface, wherein the drive lever (23) engages approximately centrally with a roller (32) or its contact surface into an adjusting cam (33) of an adjusting cam shaft (22) and with its lower end drives the pivot lever (21) via a swivel joint (24).
  4. Drive and displacement system for mechanically variable valve controls as claimed in claims 1, 2 and 3, characterised in that the pivot lever (2) or (21) is rotatably mounted on the adjusting cam shaft (3) or (22), wherein the adjusting cam (11) or (33) is connected in a non-rotational manner to the adjusting cam shaft (3) or (22) via a pin, rivet or screw connection in order to avoid the division of bearings in the pivot levers (2) or (21).
  5. Drive and displacement system for mechanically variable valve controls as claimed in claims 1, 2 and 3, characterised in that an adjusting cam (11) or (33) comprising a plurality of contact surfaces is disposed in a non-rotational manner on the adjusting cam shaft (3) or (22), whereby the roller (12) or (32) of the drive lever (4) or (23) can be adjusted by a corresponding rotation of the adjusting cam shaft (3) or (22) on mutually different contact surfaces of the adjusting cam (11) or (33).
  6. Drive and displacement system for mechanically variable valve controls as claimed in claim 5, characterised in that the elevation curves of the contact surfaces of the adjusting cam (11) or (33) are inwardly curved, outwardly curved, straight or s-shaped, wherein for each set valve stroke length mutually different valve opening times can be provided in the case of different valve elevation curves.
  7. Drive and displacement system for mechanically variable valve controls as claimed in claim 5, characterised in that the contact surface of the adjusting cam (11) or (33) provided for the largest valve stroke is extended by means of an adjoining circular arc which as its middle point has the axis of rotation of the adjusting cam shaft (3) or (22), whereby the valve elevation curve can be changed by means of a rotation of the adjusting cam shaft (3) or (22) through the thus changed extent of the engagement of the roller (12) or (32) of the drive lever (4) or (23) into the circular arc of the contact surface of the adjusting cam (11) or (33) in the case of the largest valve stroke.
  8. Drive and displacement system for mechanically variable valve controls as claimed in claim 5, characterised in that the contact surfaces of the adjusting cams (11) or (33) of two inlet valves (1) or (20) provided for a working chamber are formed in such a way that after both inlet valves (1) or (20) have been kept constantly closed for operation of the working chamber via only one inlet channel by a rotation of the adjusting cam shaft (3) or (22) for the lower performance range of the power machine an inlet valve (1) or (20) is first actuated and for the upper performance ranges the second inlet valve (1) or (20) is also actuated.
  9. Drive and displacement system for mechanically variable valve controls as claimed in claim 5, characterised in that the contact surfaces of the adjusting cams (11) or (33) of two inlet valves (1) or (20), which are provided for a working chamber, have different plate diameters and can each have their own inlet channel, are formed in such a way that, after both inlet valves (1) or (20) have been kept constantly closed for operation of the working chamber in the lower performance range by a rotation of the adjusting cam shaft (3) or (22) first the inlet valve (1) or (20) with the small plate diameter is actuated, for operation in the middle performance range the valve (1) or (20) with the small plate diameter is switched into a constantly closed state, whereupon the valve (1) or (20) with the large plate diameter is actuated and for operation in the upper performance range both valves (1) and (20) are actuated, whereby in all performance ranges an advantageous twisting of the intake air in the working chamber is produced.
  10. Drive and displacement system for mechanically variable valve controls as claimed in claims 1, 2 and 3, characterised in that adjusting arms (17) or (36) are disposed in a non-rotational manner on the adjusting cam shaft (3) or (22) and are provided as counter bearings for compression springs (16) or torsion springs (35), wherein the compression springs (26) or torsion springs (35) are disposed in such a way that with the rotation of the adjusting cam shaft (3) or (22) to a smaller valve stroke and to a shorter valve opening duration the restoring force acting upon the pivot lever (2) or (21) is increased by the shortening of the length of the compression spring (16) or by the reduction in the rotary angle of the torsion spring (35).
  11. Drive and displacement system for mechanically variable valve controls as claimed in claim 10, characterised in that the adjusting arm (17) or (36) form a unit with the adjusting cam (11) or (33).
  12. Drive and displacement system for mechanically variable valve controls as claimed in claims 1, 2 and 3, characterised in that by means of the extension of the spindle of the swivel joint (5) or (24) on both sides the drive lever (4) or (23) drives a pivot lever (2) or (21) on both sides, which pivot lever actuates a respective valve (1) or (20) via a rocking lever (28).
EP03725134A 2002-05-13 2003-05-02 Drive and displacement system for variable valve-controlled distribution Expired - Lifetime EP1506345B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10221133A DE10221133A1 (en) 2002-05-13 2002-05-13 Drive and adjustment system for variable valve controls
DE10221133 2002-05-13
PCT/EP2003/004627 WO2003095805A1 (en) 2002-05-13 2003-05-02 Drive and displacement system for variable valve-controlled distribution

Publications (2)

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EP1506345A1 EP1506345A1 (en) 2005-02-16
EP1506345B1 true EP1506345B1 (en) 2005-11-30

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EP (1) EP1506345B1 (en)
AT (1) ATE311526T1 (en)
AU (1) AU2003227706A1 (en)
DE (2) DE10221133A1 (en)
WO (1) WO2003095805A1 (en)

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DE19913742A1 (en) * 1999-03-26 2000-09-28 Bayerische Motoren Werke Ag Device for stroke adjustment of a gas exchange valve in the cylinder head of an internal combustion engine
DE10006018B4 (en) * 2000-02-11 2009-09-17 Schaeffler Kg Variable valve drive for load control of a spark-ignited internal combustion engine
DE10052811A1 (en) * 2000-10-25 2002-05-08 Ina Schaeffler Kg Variable valve train for load control of a spark ignition internal combustion engine

Also Published As

Publication number Publication date
EP1506345A1 (en) 2005-02-16
ATE311526T1 (en) 2005-12-15
AU2003227706A1 (en) 2003-11-11
DE10221133A1 (en) 2003-11-27
WO2003095805A1 (en) 2003-11-20
DE50301810D1 (en) 2006-01-05

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