EP1506345B1 - Antriebs- und verstellsystem für variable ventilsteuerungen - Google Patents
Antriebs- und verstellsystem für variable ventilsteuerungen Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive
- valve
- lever
- roller
- cam
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
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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
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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
- 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
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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
- 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
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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
- 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 .
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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)
- Means For Warming Up And Starting Carburetors (AREA)
Description
Claims (12)
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen, die einen auf einer Achse drehbar gelagerten Schwenkhebel aufweisen, der für ein ständiges Geschlossenhalten des Venbles eine kreisförmige Kontaktfläche und für die Betätigung des Ventiles eine sich anschließende, nasenförmige Kontaktfläche für den Eingriff einer Rolle oder Kontaktfläche eines das Ventil betätigenden Schwinghebels besitzt, wobei in Abhängigkeit von der Weite des Eingriffs der Rolle oder Kontaktfläche des Schwinghebels das Ventil sowohl mit einem stufenlos variablen Ventilhub als auch mit einer hiervon abhängigen Ventilöffnungsdauer betätigt werden kann, dadurch gekennzeichnet, dass der Schwenkhebel (2) mittels eines aus einem Antriebshebels (4) gebildeten Antriebs- und Verstellsystem über ein Drehgelenk (5) des Antriebshebels (4) mit einer stufenlos einstellbaren Weite der Schwenkbewegung angetrieben wird, wobei der Antriebshebel (4) selbst über eine Nockenrolle (13) oder Kontaktfläche von einem Nocken (14) angetrieben wird und die Schwenkbewegung des Schwenkhebels (2) durch den Eingriff des Antriebshebels (4) in den Stelinocken (11) einer Stellnockenwelle (3) verändert werden kann.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, dadurch gekennzeichnet, dass der Antriebshebel (4) etwa mittig von einem Nocken (14) über eine Nockenrolle (13) oder über seine Kontaktfläche angetrieben wird, wobei der Antriebshebel (4) an seinem oberen Ende mit einer Rolle (12) oder seiner Kontaktfläche in einen Stellnocken (11) einer Stellnockenwelle (3) eingreift und mit seinem unteren Ende über ein Drehgelenk (5) den Schwenkhebel (2) antreibt.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, dadurch gekennzeichnet dass der Antriebshebel (23) an seinem oberen Ende von einem Nocken (31) über eine Nockenrolle (30) oder über seine Kontaktfläche angetrieben wird, wobei der Antriebshebel (23) etwa mittig mit einer Rolle (32) oder seiner Kontaktfläche in einen Stellnocken (33) einer Stellnockenwelle (22) eingreift und mit seinem unteren Ende über ein Drehgelenk (24) den Schwenkhebel (21) antreibt.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, 2 und 3, dadurch gekennzeichnet, dass der Schwenkhebel (2) oder (21) auf der Stellnockenwelle (3) oder (22) drehbar gelagert ist, wobei der Stellnocken (11) oder (33) über eine Stift- Niet- oder Schraubverbindung drehfest mit der Stellnockenwelle (3) oder (22) verbunden ist, um geteilte Lagerungen bei den Schwenkhebeln (2) oder (21) zu vermeiden.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, 2 und 3, dadurch gekennzeichnet, dass auf der Stellnockenwelle (3) oder (22) drehfest ein mehrere Kontaktflächen aufweisender Stellnocken (11) oder (33) angeordnet ist, wodurch die Rolle (12) oder (32) des Antriebshebels (4) oder (23) durch eine entsprechende Drehung der Stellnockenwelle (3) oder (22) auf einander unterschiedliche Kontaktflächen des Stellnockens (11) oder (33) gestellt werden kann.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 5, dadurch gekennzeichnet, dass die Erhebungskurven der Kontaktflächen des Stellnockens (11) oder (33) nach innen gewölbt, nach außen gewölbt, geradlinig oder s-förmig gestaltet sind, wodurch für jede eingestellte Ventilhublänge einander unterschiedliche Ventilöffnungszeiten bei unterschiedlichen Ventilerhebungskurven vorgesehen werden können
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 5, dadurch gekennzeichnet, dass die für den größten Ventilhub vorgesehene Kontaktfläche des Stellnockens (11) oder (33) mittels eines sich anschließenden Kreisbogens verlängert ist, der als Mittelpunkt die Drehachse der Stellnockenwelle (3) oder (22) aufweist, wodurch mittels einer Drehung der Stellnockenwelle (3) oder (22) durch die hierbei veränderte Weite des Eingriffs der Rolle (12) oder (32) des Antriebshebels (4) oder (23) in den Kreisbogen der Kontaktfläche des Stellnockens (11) oder (33) bei dem größten Ventilhub die Ventilerhebungskurve verändert werden kann.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 5, dadurch gekennzeichnet, dass die Kontaktflächen der Stellnocken (11) oder (33) zweier für einen Arbeitsraum vorgesehener Einlassventile (1) oder (20) derart gestaltet sind, dass nach einem ständigen Geschlossenhalten beider Einlassventile (1) oder (20) für den Betrieb des Arbeitsraumes nur über einen Einlasskanal durch eine Drehung der Stellnockenwelle (3) oder (22) für den unteren Leistungsbereich der Kraftmaschine zuerst ein Einlassventil (1) oder (20) betätigt wird und für den oberen Leistungsbereiche auch das zweite Einlassventil (1) oder (20) betätigt wird.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 5, dadurch gekennzeichnet, dass die Kontaktflächen der Stelinocken (11) oder (33) zweier für einen Arbeitsraum vorgesehener, verschiedene Tellerdurchmesser aufweisender Einlassventile (1) oder (20), die jeweils einen eigenen Einlasskanal besitzen können, derart gestaltet sind, dass nach einem ständigen Geschlossenhalten beider Einlassventile (1) oder (20) für den Betrieb des Arbeitsraumes in dem unteren Leistungsbereich durch eine Drehung der Stellnockenwelle (3) oder (22) zuerst das Einlassventil (1) oder (20) mit dem kleinen Tellerdurchmesser betätigt wird, für den Betrieb in dem mittleren Leistungsbereich das Ventil (1) oder (20) mit dem kleinen Tellerdurchmesser in ein ständiges Geschlossenhalten geschaltet wird, wonach das Ventil (1) oder (20) mit dem großen Tellerdurchmesser betätigt wird und für den Betrieb in dem oberen Leistungsbereich beide Ventile (1) und (20) betätigt werden, wodurch in allen Leistungsbereichen ein vorteilhafter Drall der Ansaugluft in dem Arbeitsraum entsteht.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, 2 und 3, dadurch gekennzeichnet, dass drehfest auf der Stellnockenwelle (3) oder (22) Stellarme (17) oder (36) angeordnet sind, die als Widerlager für Druckfedern (16) oder Drehfedern (35) vorgesehen sind, wobei die Anordnung der Druckfedern (26) oder Drehfedern (35) derart angeordnet sind, dass mit der Drehung der Stellnockenwelle (3) oder (22) auf einen kleineren Ventilhub und auf eine kürzere Vertilöffnungsdauer sich die auf den Schwenkhebel (2) oder (21) einwirkende Rückstellkraft durch die Verkürzung der Länge der Druckfeder (16) oder durch die Verkleinerung des Drehwinkels der Drehfeder (35) vergrößert.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 10, dadurch gekennzeichnet, dass der Stellarm (17) oder (36) mit dem Stellnocken (11) oder (33) eine Einheit bilden.
- Antriebs- und Verstellsystem für mechanisch variable Ventilsteuerungen nach Anspruch 1, 2 und 3, dadurch gekennzeichnet, dass mittels einer beiderseitigen Verlängerung der Achse des Drehgelenkes (5) oder (24) der Antriebshebel (4) oder (23) beiderseitig einen Schwenkhebel (2) oder (21) antreibt, der jeweils ein Ventil (1) oder (20) über einen Schwinghebel (28) betätigt.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10221133A DE10221133A1 (de) | 2002-05-13 | 2002-05-13 | Antriebs- und Verstellsystem für variable Ventilsteuerungen |
DE10221133 | 2002-05-13 | ||
PCT/EP2003/004627 WO2003095805A1 (de) | 2002-05-13 | 2003-05-02 | Antriebs und verstellsystem für variable ventilsteuerungen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1506345A1 EP1506345A1 (de) | 2005-02-16 |
EP1506345B1 true EP1506345B1 (de) | 2005-11-30 |
Family
ID=29285321
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03725134A Expired - Lifetime EP1506345B1 (de) | 2002-05-13 | 2003-05-02 | Antriebs- und verstellsystem für variable ventilsteuerungen |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1506345B1 (de) |
AT (1) | ATE311526T1 (de) |
AU (1) | AU2003227706A1 (de) |
DE (2) | DE10221133A1 (de) |
WO (1) | WO2003095805A1 (de) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB0325278D0 (en) * | 2003-10-29 | 2003-12-03 | Ricardo Uk Ltd | Engine valvegear |
WO2005090758A1 (ja) * | 2004-03-23 | 2005-09-29 | Mitsubishi Fuso Truck And Bus Corporation | 内燃機関の可変動弁装置 |
US6994063B2 (en) * | 2004-04-13 | 2006-02-07 | Mitsubishi Fuso Truck And Bus Corporation | Variable valve unit for internal combustion engine |
JP4221327B2 (ja) * | 2004-04-13 | 2009-02-12 | 三菱ふそうトラック・バス株式会社 | 内燃機関の可変動弁装置 |
JP4342372B2 (ja) * | 2004-04-28 | 2009-10-14 | 本田技研工業株式会社 | 内燃機関の動弁装置 |
JP4507997B2 (ja) * | 2005-06-15 | 2010-07-21 | 三菱自動車工業株式会社 | 内燃機関の可変動弁装置 |
DE102005035315B4 (de) * | 2005-07-28 | 2007-05-10 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Variabler Ventiltrieb für Verbrennungskraftmaschinen |
JP5028952B2 (ja) * | 2006-10-24 | 2012-09-19 | トヨタ自動車株式会社 | 内燃機関の動弁機構 |
JP4380695B2 (ja) * | 2006-12-18 | 2009-12-09 | トヨタ自動車株式会社 | 可変動弁機構付き内燃機関 |
ITMI20070443A1 (it) * | 2007-03-05 | 2008-09-06 | Piaggio & C Spa | Sistema per la variazione continua dell'alzata e della fase delle valvole in un motore a combustione interna |
DE102008034092A1 (de) * | 2008-07-21 | 2010-01-28 | Fev Motorentechnik Gmbh | Schaltbarer Ventilhebel für Ventiltriebe mit Ventilschaltfunktion mit einer gebogenen Schraubenfeder |
DE102011016384A1 (de) | 2011-04-07 | 2012-10-11 | Kurt Imren Yapici | Vollvariabler Ventiltrieb |
DE102017009326A1 (de) | 2017-10-09 | 2019-04-11 | Kurt Imren Yapici | Ventiltrieb |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19532334A1 (de) * | 1995-09-01 | 1997-03-06 | Bayerische Motoren Werke Ag | Variabler Ventiltrieb, insbesondere für Brennkraftmaschinen |
DE19640520A1 (de) * | 1996-07-20 | 1998-04-09 | Dieter Dipl Ing Reitz | Ventiltrieb und Zylinderkopf einer Brennkraftmaschine |
US6019076A (en) * | 1998-08-05 | 2000-02-01 | General Motors Corporation | Variable valve timing mechanism |
DE19913742A1 (de) * | 1999-03-26 | 2000-09-28 | Bayerische Motoren Werke Ag | Vorrichtung zur Hubverstellung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine |
DE10006018B4 (de) * | 2000-02-11 | 2009-09-17 | Schaeffler Kg | Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine |
DE10052811A1 (de) * | 2000-10-25 | 2002-05-08 | Ina Schaeffler Kg | Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine |
-
2002
- 2002-05-13 DE DE10221133A patent/DE10221133A1/de not_active Withdrawn
-
2003
- 2003-05-02 AU AU2003227706A patent/AU2003227706A1/en not_active Abandoned
- 2003-05-02 AT AT03725134T patent/ATE311526T1/de not_active IP Right Cessation
- 2003-05-02 WO PCT/EP2003/004627 patent/WO2003095805A1/de not_active Application Discontinuation
- 2003-05-02 DE DE50301810T patent/DE50301810D1/de not_active Expired - Lifetime
- 2003-05-02 EP EP03725134A patent/EP1506345B1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
ATE311526T1 (de) | 2005-12-15 |
DE50301810D1 (de) | 2006-01-05 |
AU2003227706A1 (en) | 2003-11-11 |
WO2003095805A1 (de) | 2003-11-20 |
EP1506345A1 (de) | 2005-02-16 |
DE10221133A1 (de) | 2003-11-27 |
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