EP2401480A1 - Valve drive of an internal combustion engine having an adjustment device - Google Patents

Valve drive of an internal combustion engine having an adjustment device

Info

Publication number
EP2401480A1
EP2401480A1 EP10703648A EP10703648A EP2401480A1 EP 2401480 A1 EP2401480 A1 EP 2401480A1 EP 10703648 A EP10703648 A EP 10703648A EP 10703648 A EP10703648 A EP 10703648A EP 2401480 A1 EP2401480 A1 EP 2401480A1
Authority
EP
European Patent Office
Prior art keywords
valve
drive
valve camshaft
camshaft
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10703648A
Other languages
German (de)
French (fr)
Other versions
EP2401480B1 (en
Inventor
Jens Schaefer
Sebastian Zwahr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2401480A1 publication Critical patent/EP2401480A1/en
Application granted granted Critical
Publication of EP2401480B1 publication Critical patent/EP2401480B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0042—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams being profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow camshafts

Definitions

  • the invention relates to a valve train for controlling charge exchange valves of an internal combustion engine, comprising at least one mounted within a cylinder head of the internal combustion engine valve camshaft, which is displaceable via a drive pulley in rotation, wherein an adjusting motor and a transmission having adjusting device is provided which upon actuation of the adjusting motor and via the intermediate gearbox specifically provides for an axial displacement and / or rotation of the at least one valve camshaft relative to the drive disk in order to selectively vary an actuation of the charge exchange valves taking place via cams of the at least one valve camshaft.
  • a valve drive for controlling charge exchange valves of an internal combustion engine in which a valve camshaft, which is mounted in a cylinder head of the internal combustion engine, can be set into rotation via a drive disk.
  • an adjusting device is provided on the front side of the valve camshaft which has an adjusting motor and a gearbox located in an additional housing outside the cylinder head, the adjusting motor communicating with the valve camshaft via the intermediate gearbox.
  • the invention comprises the technical teaching that the adjusting motor of the adjusting device is placed predominantly or completely within a common chamber with the drive pulley.
  • the adjusting motor of the adjusting device is placed predominantly or completely within a common chamber with the drive pulley.
  • the cams of the valve camshaft have a cam elevation which is variable in the axial direction.
  • Be strokes of the associated charge exchange valves in addition to a phase change can be varied. Accordingly, the control of the charge changeover valves can be adapted even more precisely to the required amount of mixture in favor of a dethrottling of the internal combustion engine.
  • the gearbox of the adjusting device comprises a nut fixedly connected to one end of the valve camshaft and a spindle connected to the adjusting motor and is supported via a thrust bearing unit on a drive assembly unit carrying the drive disk.
  • a thrust bearing unit on a drive assembly unit carrying the drive disk.
  • the axial displacement of the nut displacement in both directions by each fixed to the cylinder head related axial stops can be limited. This can be reliably prevented in a simple manner damage to the transmission due to excessive axial feed of the mother.
  • the axial displacement of the nut in both directions by each fixedly placed on the spindle radial stops can be limited, which come from a defined position with each provided on the mother projections in contact.
  • Such a limited limitation of the axial travel of the nut has the advantage that no additional forces are exerted on contact of the radial stops with the nut on the bearings of the components involved.
  • the thrust bearing unit is designed in the manner of a double-sided, preloaded roller bearing.
  • a coupling in the form of a cross slide clutch is provided between the spindle and the adjusting motor.
  • this radial and axial manufacturing and assembly tolerances between the two components can be reliably compensated.
  • other types of coupling can also be used for this purpose.
  • At least one guide body is placed in the radial direction between the valve camshaft and the drive pulley carrying the drive pulley, which is provided in mutually corresponding manner on the part of the valve camshaft and on the part of the drive pulley and helically extending guideways runs and causes an axial displacement of the valve cam whose relative rotation with respect to the Antriebsbauaji.
  • the guide body is a ball, as it also finds use as a rolling element in low-friction ball bearings.
  • the adjusting motor is designed in the manner of an electric motor. As a result, a precise control of the transmission of the adjusting device can be realized.
  • the drive pulley is designed as a chain wheel. Accordingly, a robust and accurate drive of the valve camshaft becomes possible.
  • 1 shows a detailed sectional view of the valve drive according to the invention, in the region of one end of the valve camshaft; 2 shows a detailed sectional view of the valve cam shaft together
  • FIG. 3 shows a perspective detailed view of a transmission of the adjusting device of the valve drive according to the invention according to a first embodiment
  • FIG. 1 shows a detailed sectional view of the valve drive according to the invention in the region of one end of a valve camshaft 1.
  • This valve camshaft 1 has a plurality of cams 2, which are in each case in operative connection via an actuating device 3 with two associated gas exchange valves 4a and 4b.
  • the valve camshaft 1 is further rotatably mounted in a cylinder head 5 of the internal combustion engine and has at its one end via a drive pulley 6, which is formed in this case as a chain disc and via which they by means of a chain not shown here with a crankshaft of the internal combustion engine in combination stands.
  • valve camshaft 1 When the internal combustion engine is running, the valve camshaft 1 is driven by means of this drive pulley 6 via the crankshaft and in this case actuates via its cams 2 the respective associated charge exchange valves 4a and 4b.
  • the cams 2 are so-called space cams which each have a cam elevation which is variable in the axial direction.
  • the elevation of the cam 2 transmitted via the actuating device 3 to the charge exchange valves 4a and 4b is selectively varied. This results in a change in the lift of the charge exchange valves 4a and 4b.
  • an adjusting device 7 with an adjusting motor 8 is provided in the region of the drive disk 6, which is placed with the drive disk 6 predominantly in a common chamber 9. This is defined by a lid 10 placed directly on the cylinder head 5.
  • the predominant integration of the adjusting device 7 into the chamber 9 of the drive disk 6 represents a particularly compact construction in favor of a small overall length of the internal combustion engine.
  • FIG. 2 shows a sectional view of the valve camshaft 1 on the side of the adjusting device 7 without the surrounding cylinder head 5.
  • the valve camshaft 1 is designed as a hollow shaft and is at its end with a nut 11 of a transmission 12 of the adjusting device 7 firmly in communication.
  • the nut 11 is placed at its inner diameter with a thread on a corresponding thereto thread of a spindle 13, wherein a relative rotation of the spindle 13 to the nut 11 causes an axial movement of the nut 11 in the corresponding direction.
  • the spindle 13 is at its side facing away from the valve camshaft 1 side with the inner ring of a thrust bearing unit 14 in conjunction, which is designed as a double-sided, biased rolling bearing.
  • the inner ring of this thrust bearing unit 14 can in this case perform a rotation with respect to the outer ring and is further connected via a cross slide coupling 15 with the adjusting motor 8 in operative connection.
  • the adjustment motor 8 is designed as an electric motor and has, in a known manner, a rotor which is connected to the cross slide coupling 15 and a stator part connected to the cover 10.
  • the adjusting motor 8 can also be realized in the form of an alternative actuator, for example in US Pat Shape of a hysteresis brake.
  • the outer ring of the thrust bearing unit 14 is fixedly attached to a drive assembly 16 which carries the drive disk 6, not shown here between a first part 17 and a second part 18 and also by means of the first part 17, the inner ring 19 of a sliding bearing for supporting the valve camshaft 1 in the cylinder head 5 trains.
  • first part 17 and the valve cam 1 guide body 20 are placed in the radial direction in the form of balls, which run in the valve camshaft 1 and part of the second part 17 of the drive assembly 16 provided, mutually corresponding guideways 21 and 22. These are each formed helically and thus on the one hand enable the transmission of torque from the drive pulley 6 by means of the drive assembly 16 on the valve camshaft 1 and on the other cause an axial displacement of the Ventilno- ckenwelle 1 via the guide body 20, a relative rotation of the valve camshaft 1 with respect to the Drive assembly 16.
  • the gear 12 and the drive assembly 16 are arranged radially nested with each other, wherein the spindle 13 and the guide tracks 21, 22 axially completely overlap axially.
  • a torque is transmitted to the valve camshaft 1 via the drive pulley 6 and by means of the drive assembly 16, with the entire transmission 12 and the rotor of the adjustment motor 8 rotating at the same speed. If now the rotation of the motor is amplified or decelerated by actuation of the adjustment motor 8, this is transmitted to the spindle 13 by means of the cross slide coupling 15. The then adjusting differential speed between the spindle 13 and nut 11 causes an axial displacement of the nut 11, wherein the direction of this axial displacement corresponds to the sign of the speed difference between the spindle 13 and nut 11.
  • the radial stop 24 is formed by the inner ring of the Axialla- geriens 14.
  • the radial stops 23 and 24 each occur from a defined position of the nut 11 with protrusions extending thereon

Abstract

The invention relates to a valve drive for controlling gas exchange valves (4a, 4b) of an internal combustion engine, comprising at least one valve camshaft (1) that is supported within a cylinder head (5) of the internal combustion engine and that can be moved in rotation by means of a drive disk (6), wherein an adjustment device (7) comprising an adjustment motor (8) and a gear train (12) is provided, wherein the adjustment device provides for an axial movement and/or rotation of the at least one valve camshaft (1) relative to the drive disk (6) in a specific manner upon actuation of the adjustment motor (8) and by means of the intermediately connected gear train (12) in order to vary in a specific manner an actuation of the gas exchange valves (4a, 4b) that occurs by means of cams (2) of the at least one valve camshaft (1), wherein furthermore the adjustment motor (8) is placed predominantly or completely within a common chamber (9) with the drive disk (6).

Description

Bezeichnung der Erfindung Name of the invention
Ventiltrieb einer Brennkraftmaschine mit einer VerstelleinrichtungValve gear of an internal combustion engine with an adjusting device
Beschreibungdescription
Gebiet der ErfindungField of the invention
Die Erfindung betrifft einen Ventiltrieb zum Steuern von Ladungswechselventilen einer Brennkraftmaschine, umfassend mindestens eine innerhalb eines Zylinderkopfs der Brennkraftmaschine gelagerte Ventilnockenwelle, die über eine Antriebsscheibe in Rotation versetzbar ist, wobei eine einen Verstellmotor und ein Getriebe aufweisende Verstelleinrichtung vorgesehen ist, welche bei Betätigung des Verstellmotors und über das zwischengeschaltete Getriebe gezielt für eine axiale Verschiebung und/oder Verdrehung der mindestens ei- nen Ventilnockenwelle relativ zu der Antriebsscheibe sorgt, um eine über Nocken der mindestens einen Ventilnockenwelle stattfindende Betätigung der Ladungswechselventile gezielt zu variieren.The invention relates to a valve train for controlling charge exchange valves of an internal combustion engine, comprising at least one mounted within a cylinder head of the internal combustion engine valve camshaft, which is displaceable via a drive pulley in rotation, wherein an adjusting motor and a transmission having adjusting device is provided which upon actuation of the adjusting motor and via the intermediate gearbox specifically provides for an axial displacement and / or rotation of the at least one valve camshaft relative to the drive disk in order to selectively vary an actuation of the charge exchange valves taking place via cams of the at least one valve camshaft.
Hintergrund der ErfindungBackground of the invention
Nach dem Viertaktprinzip arbeitende Brennkraftmaschinen verfügen üblicherweise über Ladungswechselventile in Form von Einlass- und Auslassventilen, um den zum Betrieb der Brennkraftmaschine nötigen Ladungswechsel durchführen zu können. Dabei werden Öffnungs- und Schließbewegungen der jewei- ligen Ventile über Nocken einer zugeordneten Ventilnockenwelle eingeleitet.According to the four-stroke principle operating internal combustion engines usually have charge exchange valves in the form of intake and exhaust valves to perform the necessary to operate the internal combustion engine charge exchange. In this case, opening and closing movements of the respective valves are initiated via cams of an associated valve camshaft.
Im Bereich der Ottomotoren finden des Weiteren üblicherweise Verstelleinrichtungen Anwendung, über welche die Steuerzeiten der Ladungswechselventile mittels einer Verdrehung der Ventilnockenwelle verschoben und damit an verschiedene Drehzahlen und Zylinderfüllungen der Brennkraftmaschine ange- passt werden können. Hierdurch kann eine Steigerung der Qualität des Ladungswechsels erreicht werden.In the field of gasoline engines are also usually adjusting application, via which the timing of the charge exchange valves displaced by means of a rotation of the valve camshaft and thus can be adapted to different speeds and cylinder fillings of the internal combustion engine. As a result, an increase in the quality of the charge exchange can be achieved.
Stand der TechnikState of the art
Aus der DE 102 48 351 A1 ist ein Ventiltrieb zum Steuern von Ladungswechselventilen einer Brennkraftmaschine bekannt, bei welchem eine innerhalb ei- nes Zylinderkopfs der Brennkraftmaschine gelagert angeordnete Ventilnockenwelle über eine Antriebsscheibe in Rotation versetzbar ist. Stirnseitig der Ventilnockenwelle ist dabei eine Verstelleinrichtung vorgesehen, welche über einen außerhalb des Zylinderkopfs in einem zusätzlichen Gehäuse liegenden Verstellmotor und ein Getriebe verfügt, wobei der Verstellmotor über das zwi- schenliegende Getriebe mit der Ventilnockenwelle in Verbindung steht. Bei einer Betätigung des Verstellmotors kann mittels des Getriebes eine Relativverdrehung der Ventilnockenwelle bezüglich der Antriebsscheibe erreicht werden, was zu einer Verschiebung der über Nocken der Ventilnockenwelle stattfindenden Betätigung der Ladungswechselventile führt.From DE 102 48 351 A1, a valve drive for controlling charge exchange valves of an internal combustion engine is known, in which a valve camshaft, which is mounted in a cylinder head of the internal combustion engine, can be set into rotation via a drive disk. In this case, an adjusting device is provided on the front side of the valve camshaft which has an adjusting motor and a gearbox located in an additional housing outside the cylinder head, the adjusting motor communicating with the valve camshaft via the intermediate gearbox. Upon actuation of the adjusting motor, a relative rotation of the valve camshaft with respect to the drive disk can be achieved by means of the transmission, which leads to a displacement of the actuation of the charge exchange valves taking place via cams of the valve camshaft.
Eine derartige Anordnung weist allerdings den Nachteil auf, dass die Brennkraftmaschine durch den im zusätzlichen Gehäuse am Zylinderkopf vorgesehenen Verstellmotor einen größeren Platzbedarf aufweist.However, such an arrangement has the disadvantage that the internal combustion engine has a larger footprint due to the adjustment motor provided in the additional housing on the cylinder head.
Es ist daher die Aufgabe der vorliegenden Erfindung, einen Ventiltrieb zum Steuern von Ladungswechselventilen einer Brennkraftmaschine zur Verfügung zu stellen, welcher eine möglichst kompakt angeordnete Verstelleinrichtung zu Gunsten einer reduzierten Baulänge der Brennkraftmaschine aufweist.It is therefore an object of the present invention to provide a valve train for controlling charge exchange valves of an internal combustion engine is available, which has a compact as possible adjustment in favor of a reduced overall length of the internal combustion engine.
Offenbarung der ErfindungDisclosure of the invention
Diese Aufgabe wird ausgehend vom Oberbegriff des Anspruchs 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die darauffolgenden, abhängigen Ansprüche geben jeweils vorteilhafte Weiterbildungen der Erfindung wieder.This object is achieved on the basis of the preamble of claim 1 in conjunction with its characterizing features. The following, dependent claims give each advantageous embodiments of the invention again.
Die Erfindung umfasst die technische Lehre, dass der Verstellmotor der Ver- Stelleinrichtung überwiegend oder vollständig innerhalb einer gemeinsamen Kammer mit der Antriebsscheibe platziert ist. Durch die Integration des Verstellmotors in die Kammer der Antriebsscheibe können die Baulänge der Brennkraftmaschine reduziert werden und zudem zusätzliche Gehäuseteile zur Einkapselung des Verstellmotors eingespart werden. Dem Fachmann wird hierbei klar sein, dass es sich bei der Kammer der Antriebsscheibe je nach Ausgestaltung der Brennkraftmaschine um den Zylinderkopf oder einen Kettenbzw. Riemenkasten handeln kann.The invention comprises the technical teaching that the adjusting motor of the adjusting device is placed predominantly or completely within a common chamber with the drive pulley. By integrating the adjusting motor in the chamber of the drive pulley, the overall length of the internal combustion engine can be reduced and also additional housing parts for encapsulation of the adjustment can be saved. The expert will be clear in this case that it is in the chamber of the drive pulley depending on the configuration of the internal combustion engine to the cylinder head or a Kettenbzw. Belt box can act.
Entsprechend einer Ausgestaltung der Erfindung weisen die Nocken der Ven- tilnockenwelle eine in axialer Richtung veränderliche Nockenerhebung auf.According to one embodiment of the invention, the cams of the valve camshaft have a cam elevation which is variable in the axial direction.
Mittels dieser sogenannten Raumnocken und einer Verstelleinrichtung, die eine Axialverschiebung der Ventilnockenwelle herbeiführen kann, können dieBy means of these so-called space cam and an adjusting device, which can bring about an axial displacement of the valve cam shaft, the
Hübe der zugehörigen Ladungswechselventile zusätzlich zu einer Phasenlage- änderung variiert werden. Dementsprechend kann die Ansteuerung der La- dungswechselventile noch präziser an die benötigte Gemischmenge zugunsten einer Entdrosselung der Brennkraftmaschine angepasst werden.Be strokes of the associated charge exchange valves in addition to a phase change can be varied. Accordingly, the control of the charge changeover valves can be adapted even more precisely to the required amount of mixture in favor of a dethrottling of the internal combustion engine.
In Weiterbildung der Erfindung umfasst das Getriebe der Verstelleinrichtung eine mit einem Ende der Ventilnockenwelle fest verbundene Mutter und eine mit dem Verstellmotor in Verbindung stehende Spindel und stützt sich über eine Axiallagereinheit an einer die Antriebsscheibe tragenden Antriebsbaueinheit ab. Dabei wird eine über den Verstellmotor eingeleitete Relativrotation der Spindel bezüglich der Antriebsscheibe in eine axiale Verschiebung der Mutter umgesetzt. Eine derartige Ausgestaltung des Getriebes hat den wesentlichen Vorteil, dass die durch den Verstellmotor erzeugte Relativrotation bezüglich der Antriebsscheibe kompakt und reibungsarm in eine Axialverschiebung der Ventilnockenwelle überführt wird. Ferner können durch die Ventilnockenwelle in das Getriebe eingeleitete Axialkräfte mittels der vorgesehenen Axiallagereinheit zuverlässig aufgenommen werden.In a further development of the invention, the gearbox of the adjusting device comprises a nut fixedly connected to one end of the valve camshaft and a spindle connected to the adjusting motor and is supported via a thrust bearing unit on a drive assembly unit carrying the drive disk. In this case, initiated via the adjusting relative rotation of the spindle with respect to the drive pulley is converted into an axial displacement of the nut. Such a configuration of the transmission has the significant advantage that the relative rotation generated by the adjusting motor with respect to the drive pulley is compact and low friction transferred into an axial displacement of the valve camshaft. Furthermore, through the valve camshaft in the transmission introduced axial forces are reliably absorbed by means of the provided thrust bearing unit.
Gemäß einer vorteilhaften Ausführungsform der Erfindung ist die axiale Ver- Schiebung der Mutter in beide Richtungen durch jeweils fest mit dem Zylinderkopf in Verbindung stehende Axialanschläge begrenzbar. Dadurch kann auf einfache Art und Weise einer Beschädigung des Getriebes infolge eines übermäßigen Axialvorschubs der Mutter zuverlässig vorgebeugt werden.According to an advantageous embodiment of the invention, the axial displacement of the nut displacement in both directions by each fixed to the cylinder head related axial stops can be limited. This can be reliably prevented in a simple manner damage to the transmission due to excessive axial feed of the mother.
Es ist eine alternative Ausgestaltung der Erfindung, dass die axiale Verschiebung der Mutter in beide Richtungen durch jeweils ortsfest auf der Spindel platzierte Radialanschläge begrenzbar ist, welche ab einer definierten Position mit jeweils an der Mutter vorgesehenen Auskragungen in Kontakt treten. Eine derartig ausgebildete Begrenzung des axialen Stellweges der Mutter hat den Vor- teil, dass keine zusätzlichen Kräfte bei Kontakt der Radialanschläge mit der Mutter auf die Lagerungen der beteiligten Bauteile ausgeübt werden.It is an alternative embodiment of the invention that the axial displacement of the nut in both directions by each fixedly placed on the spindle radial stops can be limited, which come from a defined position with each provided on the mother projections in contact. Such a limited limitation of the axial travel of the nut has the advantage that no additional forces are exerted on contact of the radial stops with the nut on the bearings of the components involved.
In Weiterbildung der Erfindung ist die Axiallagereinheit nach Art eines zweiseitig wirkenden, vorgespannten Wälzlagers ausgebildet. Durch diese Maßnahme kann eine reibungsarme und robuste Axiallagerung des Getriebes erreicht werden.In a further development of the invention, the thrust bearing unit is designed in the manner of a double-sided, preloaded roller bearing. By this measure, a low-friction and robust axial bearing of the transmission can be achieved.
Entsprechend einer weiteren vorteilhaften Ausgestaltung der Erfindung ist zwischen Spindel und Verstellmotor eine Kupplung in Form einer Kreuzschieber- kupplung vorgesehen. Vorteilhafterweise können hierdurch radiale und axiale Fertigungs- und Montagetoleranzen zwischen beiden Bauteilen zuverlässig ausgeglichen werden. Dem Fachmann wird allerdings klar sein, dass zu diesem Zweck auch andere Kupplungstypen Anwendung finden können.According to a further advantageous embodiment of the invention, a coupling in the form of a cross slide clutch is provided between the spindle and the adjusting motor. Advantageously, this radial and axial manufacturing and assembly tolerances between the two components can be reliably compensated. However, it will be clear to those skilled in the art that other types of coupling can also be used for this purpose.
In Weiterbildung der Erfindung ist in radialer Richtung zwischen der Ventilnockenwelle und der die Antriebsscheibe tragenden Antriebsbaueinheit mindestens ein Führungskörper platziert, welcher in seitens der Ventilnockenwelle und seitens der Antriebsbaueinheit vorgesehenen, zueinander korrespondierenden und helixartig verlaufenden Führungsbahnen läuft und bei einer axialen Verschiebung der Ventilnockenwelle deren Relativverdrehung bezüglich der Antriebsbaueinheit bewirkt. Mittels einer derartigen Anordnung kann entsprechend der Gestaltung der Führungsbahnen bei einer axialen Verschiebung der Ventilnockenwelle zugleich eine definierte Relativverdrehung der Ventilnockenwelle bezüglich der Antriebsscheibe erreicht werden. Vorteilhafterweise handelt es sich bei dem Führungskörper um eine Kugel, wie sie auch als Wälzkörper in reibungsarmen Kugellagern Verwendung findet.In a further development of the invention, at least one guide body is placed in the radial direction between the valve camshaft and the drive pulley carrying the drive pulley, which is provided in mutually corresponding manner on the part of the valve camshaft and on the part of the drive pulley and helically extending guideways runs and causes an axial displacement of the valve cam whose relative rotation with respect to the Antriebsbaueinheit. By means of such an arrangement can be achieved with respect to the drive pulley according to the design of the guideways at an axial displacement of the valve cam shaft at the same time a defined relative rotation of the valve camshaft. Advantageously, the guide body is a ball, as it also finds use as a rolling element in low-friction ball bearings.
Im Hinblick auf den axialen Bauraumbedarf von Antriebseinheit und Getriebe ist es besonders günstig, wenn sich die Spindel und die Führungsbahnen überwiegend oder vollständig axial überlappen.With regard to the axial space requirements of the drive unit and the gearbox, it is particularly advantageous if the spindle and the guide tracks overlap mainly or completely axially.
In Weiterbildung der Erfindung ist der Verstellmotor nach Art eines Elektromo- tors ausgebildet. Dadurch kann eine präzise Steuerung des Getriebes der Verstelleinrichtung realisiert werden.In a further development of the invention, the adjusting motor is designed in the manner of an electric motor. As a result, a precise control of the transmission of the adjusting device can be realized.
Es ist eine weitere vorteilhafte Ausführungsform der Erfindung, dass die Antriebsscheibe als Kettenscheibe ausgeführt ist. Dementsprechend wird ein ro- buster und genauer Antrieb der Ventilnockenwelle möglich.It is a further advantageous embodiment of the invention that the drive pulley is designed as a chain wheel. Accordingly, a robust and accurate drive of the valve camshaft becomes possible.
Weitere, die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung bevorzugter Ausführungsformen der Erfindung anhand der Figuren näher dargestellt.Further, measures improving the invention will be described in more detail below together with the description of preferred embodiments of the invention with reference to FIGS.
Kurzbeschreibung der ZeichnungenBrief description of the drawings
Es zeigen:Show it:
Fig.1 eine detaillierte Schnittansicht des erfindungsgemäßen Ventiltriebs, im Bereich einen Endes der Ventilnockenwelle; Fig.2 eine detaillierte Schnittansicht der Ventilnockenwelle mitsamt1 shows a detailed sectional view of the valve drive according to the invention, in the region of one end of the valve camshaft; 2 shows a detailed sectional view of the valve cam shaft together
Verstelleinrichtung;adjusting device;
Fig.3 eine perspektivische Detailansicht eines Getriebes der Verstell- einrichtung des erfindungsgemäßen Ventiltriebes gemäß einer ersten Ausführungsform; und3 shows a perspective detailed view of a transmission of the adjusting device of the valve drive according to the invention according to a first embodiment; and
Fig.4 eine schematische Ansicht eines Getriebes der Verstelleinrichtung des erfindungsgemäßen Ventiltriebes gemäß einer zweiten Ausführungsform.A schematic view of a transmission of the adjusting device of the valve gear according to the invention according to a second embodiment.
Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings
In Fig.1 ist eine detaillierte Schnittansicht des erfindungsgemäßen Ventiltriebs im Bereich einen Endes einer Ventilnockenwelle 1 dargestellt. Diese Ventilnockenwelle 1 verfügt über mehrere Nocken 2, welche im Einzelnen jeweils über eine Betätigungseinrichtung 3 mit zwei zugeordneten Ladungswechselventilen 4a und 4b in Wirkverbindung stehen. Die Ventilnockenwelle 1 ist des Weiteren in einem Zylinderkopf 5 der Brennkraftmaschine rotierbar gelagert und verfügt an ihrem einen Ende über eine Antriebsscheibe 6, welche in diesem Fall als Kettenscheibe ausgebildet ist und über welche sie mittels einer hier nicht dargestellten Kette mit einer Kurbelwelle der Brennkraftmaschine in Verbindung steht. Bei laufender Brennkraftmaschine wird die Ventilnockenwelle 1 mittels dieser Antriebsscheibe 6 über die Kurbelwelle angetrieben und betätigt hierbei über ihre Nocken 2 die jeweils zugeordneten Ladungswechselventile 4a und 4b. Bei den Nocken 2 handelt es sich um sogenannte Raumnocken, die jeweils eine in axialer Richtung veränderliche Nockenerhebung aufweisen. Durch axiale Verschiebung der Ventilnockenwelle 1 relativ zur Betätigungseinrichtung 3 wird die über die Betätigungseinrichtung 3 auf die Ladungswechselventile 4a und 4b übertragene Erhebung des Nockens 2 gezielt variiert. Dies resultiert in einer Veränderung des Hubes der Ladungswechselventile 4a und 4b. Gleichzeitig wird durch eine Relativverdrehung der Ventilnockenwelle 1 bezüglich der Antriebsscheibe 6 eine Steuerzeitenänderung der Ladungswechselventile 4a und 4b erreicht, wobei die Ladungswechselventile 4a und 4b je nach Verdrehrichtung der Ventilnockenwelle 1 mit früherer oder späterer Phasenlage öffnen.FIG. 1 shows a detailed sectional view of the valve drive according to the invention in the region of one end of a valve camshaft 1. This valve camshaft 1 has a plurality of cams 2, which are in each case in operative connection via an actuating device 3 with two associated gas exchange valves 4a and 4b. The valve camshaft 1 is further rotatably mounted in a cylinder head 5 of the internal combustion engine and has at its one end via a drive pulley 6, which is formed in this case as a chain disc and via which they by means of a chain not shown here with a crankshaft of the internal combustion engine in combination stands. When the internal combustion engine is running, the valve camshaft 1 is driven by means of this drive pulley 6 via the crankshaft and in this case actuates via its cams 2 the respective associated charge exchange valves 4a and 4b. The cams 2 are so-called space cams which each have a cam elevation which is variable in the axial direction. By axial displacement of the valve camshaft 1 relative to the actuating device 3, the elevation of the cam 2 transmitted via the actuating device 3 to the charge exchange valves 4a and 4b is selectively varied. This results in a change in the lift of the charge exchange valves 4a and 4b. At the same time by a relative rotation of the valve camshaft 1 with respect to the drive pulley 6, a change in the timing of the charge exchange valves 4a and 4b achieved, wherein the charge exchange valves 4a and 4b open depending on the direction of rotation of the valve camshaft 1 with earlier or later phase position.
Um die axialen Verschiebungen und Relativverdrehungen der Ventilnockenwel- Ie 1 zu steuern, ist im Bereich der Antriebsscheibe 6 eine Verstelleinrichtung 7 mit einem Verstellmotor 8 vorgesehen, der mit der Antriebsscheibe 6 überwiegend in einer gemeinsamen Kammer 9 platziert ist. Diese ist durch einen unmittelbar auf den Zylinderkopf 5 aufgesetzten Deckel 10 definiert. Die überwiegende Integration der Verstelleinrichtung 7 in die Kammer 9 der Antriebsschei- be 6 stellt eine besonders kompakte Bauweise zugunsten einer geringen Baulängen der Brennkraftmaschine dar.In order to control the axial displacements and relative rotations of the valve camshaft 1e, an adjusting device 7 with an adjusting motor 8 is provided in the region of the drive disk 6, which is placed with the drive disk 6 predominantly in a common chamber 9. This is defined by a lid 10 placed directly on the cylinder head 5. The predominant integration of the adjusting device 7 into the chamber 9 of the drive disk 6 represents a particularly compact construction in favor of a small overall length of the internal combustion engine.
Zur besseren Verständlichkeit des Zusammenwirkens der Ventilnockenwelle 1 mit der Verstelleinrichtung 7 ist in Fig. 2 eine Schnittansicht der Ventilnocken- welle 1 auf Seiten der Verstelleinrichtung 7 ohne umliegenden Zylinderkopf 5 dargestellt. Wie zu erkennen ist, ist die Ventilnockenwelle 1 als Hohlwelle ausgeführt und steht an ihrem Ende mit einer Mutter 11 eines Getriebes 12 der Verstelleinrichtung 7 fest in Verbindung. Die Mutter 11 ist an ihrem Innendurchmesser mit einem Gewinde auf einem hierzu korrespondierenden Gewin- de einer Spindel 13 aufgesetzt, wobei eine relative Rotation der Spindel 13 zur Mutter 11 eine axiale Bewegung der Mutter 11 in die entsprechende Richtung hervorruft. Die Spindel 13 steht an ihrer der Ventilnockenwelle 1 abgewandten Seite mit dem Innenring einer Axiallagereinheit 14 in Verbindung, welche als zweiseitig wirkendes, vorgespanntes Wälzlager ausgebildet ist. Der Innenring dieser Axiallagereinheit 14 kann hierbei bezüglich des Außenrings eine Rotation ausführen und steht des Weiteren über eine Kreuzschieberkupplung 15 mit dem Verstellmotor 8 in Wirkverbindung.For better understanding of the interaction of the valve camshaft 1 with the adjusting device 7, FIG. 2 shows a sectional view of the valve camshaft 1 on the side of the adjusting device 7 without the surrounding cylinder head 5. As can be seen, the valve camshaft 1 is designed as a hollow shaft and is at its end with a nut 11 of a transmission 12 of the adjusting device 7 firmly in communication. The nut 11 is placed at its inner diameter with a thread on a corresponding thereto thread of a spindle 13, wherein a relative rotation of the spindle 13 to the nut 11 causes an axial movement of the nut 11 in the corresponding direction. The spindle 13 is at its side facing away from the valve camshaft 1 side with the inner ring of a thrust bearing unit 14 in conjunction, which is designed as a double-sided, biased rolling bearing. The inner ring of this thrust bearing unit 14 can in this case perform a rotation with respect to the outer ring and is further connected via a cross slide coupling 15 with the adjusting motor 8 in operative connection.
Der hier nicht geschnitten dargestellte Verstellmotor 8 ist als Elektromotor aus- geführt und verfügt auf bekannte Weise über einen Rotor, der mit der Kreuzschieberkupplung 15 verbunden ist, und einen mit Deckel 10 verbundenen Statorteil. Dem Fachmann wird allerdings klar sein, dass der Verstellmotor 8 auch in Form eines alternativen Aktuators verwirklicht sein kann, beispielsweise in Form einer Hysteresebremse. Der Außenring der Axiallagereinheit 14 ist fest an einer Antriebsbaueinheit 16 angegliedert, die zwischen einem ersten Teil 17 und einem zweiten Teil 18 die hier nicht dargestellte Antriebsscheibe 6 trägt und zudem mittels des ersten Teils 17 den Innenring 19 einer Gleitlagerung zur Lagerung der Ventilnockenwelle 1 im Zylinderkopf 5 ausbildet.The adjustment motor 8, not shown cut here, is designed as an electric motor and has, in a known manner, a rotor which is connected to the cross slide coupling 15 and a stator part connected to the cover 10. However, it will be clear to the person skilled in the art that the adjusting motor 8 can also be realized in the form of an alternative actuator, for example in US Pat Shape of a hysteresis brake. The outer ring of the thrust bearing unit 14 is fixedly attached to a drive assembly 16 which carries the drive disk 6, not shown here between a first part 17 and a second part 18 and also by means of the first part 17, the inner ring 19 of a sliding bearing for supporting the valve camshaft 1 in the cylinder head 5 trains.
Zwischen dem als Hohlwelle ausgeführten ersten Teil 17 und der Ventilnockenwelle 1 sind in radialer Richtung Führungskörper 20 in Form von Kugeln platziert, die in seitens der Ventilnockenwelle 1 und seitens des zweiten Teils 17 der Antriebsbaueinheit 16 vorgesehenen, zueinander korrespondierenden Führungsbahnen 21 und 22 laufen. Diese sind jeweils helixartig ausgebildet und ermöglichen so zum einen die Übertragung eines Drehmoments von der Antriebsscheibe 6 mittels der Antriebsbaueinheit 16 auf die Ventilnockenwelle 1 und bewirken zum anderen bei einer axialen Verschiebung der Ventilno- ckenwelle 1 über die Führungskörper 20 eine Relativverdrehung der Ventilnockenwelle 1 bezüglich der Antriebsbaueinheit 16.Between the designed as a hollow shaft first part 17 and the valve cam 1 guide body 20 are placed in the radial direction in the form of balls, which run in the valve camshaft 1 and part of the second part 17 of the drive assembly 16 provided, mutually corresponding guideways 21 and 22. These are each formed helically and thus on the one hand enable the transmission of torque from the drive pulley 6 by means of the drive assembly 16 on the valve camshaft 1 and on the other cause an axial displacement of the Ventilno- ckenwelle 1 via the guide body 20, a relative rotation of the valve camshaft 1 with respect to the Drive assembly 16.
Das Getriebe 12 und die Antriebsbaueinheit 16 sind radial ineinander verschachtelt angeordnet, wobei sich die Spindel 13 und die Führungsbahnen 21 , 22 axial vollständig axial überlappen.The gear 12 and the drive assembly 16 are arranged radially nested with each other, wherein the spindle 13 and the guide tracks 21, 22 axially completely overlap axially.
Im Betrieb der Brennkraftmaschine wird über die Antriebsscheibe 6 und mittels der Antriebsbaueinheit 16 ein Drehmoment auf die Ventilnockenwelle 1 übertragen, wobei das gesamte Getriebe 12 sowie der Rotor des Verstellmotors 8 mit gleicher Drehzahl mit rotieren. Wird nun durch Betätigung des Verstellmotors 8 die Rotation des Motors verstärkt oder verzögert, so wird dies mittels der Kreuzschieberkupplung 15 auf die Spindel 13 übertragen. Die sich daraufhin einstellende Differenzdrehzahl zwischen Spindel 13 und Mutter 11 bewirkt eine axiale Verschiebung der Mutter 11 , wobei die Richtung dieser axialen Ver- Schiebung dem Vorzeichen der Drehzahldifferenz zwischen Spindel 13 und Mutter 11 entspricht. Die Mutter 11 führt bei dieser Bewegung die Ventilnockenwelle 1 mit sich, die gleichzeitig aufgrund der Führungsbahnen 21 und 22 und der Führungskörper 20 eine Relativverdrehung bezüglich der Antriebsbau- einheit 16 ausführt. Um allerdings einer Beschädigung des Getriebes 12 durch eine zu weite axiale Verschiebung der Mutter 11 vorzubeugen, sind auf der Spindel 13 beidseits der Mutter 11 ortsfest platzierte Radialanschläge 23 undDuring operation of the internal combustion engine, a torque is transmitted to the valve camshaft 1 via the drive pulley 6 and by means of the drive assembly 16, with the entire transmission 12 and the rotor of the adjustment motor 8 rotating at the same speed. If now the rotation of the motor is amplified or decelerated by actuation of the adjustment motor 8, this is transmitted to the spindle 13 by means of the cross slide coupling 15. The then adjusting differential speed between the spindle 13 and nut 11 causes an axial displacement of the nut 11, wherein the direction of this axial displacement corresponds to the sign of the speed difference between the spindle 13 and nut 11. During this movement, the nut 11 carries with it the valve camshaft 1, which at the same time, due to the guide tracks 21 and 22 and the guide body 20, makes a relative rotation with respect to the drive structure. unit 16 executes. However, to prevent damage to the transmission 12 by an excessive axial displacement of the nut 11 are on the spindle 13 on both sides of the nut 11 fixedly placed radial stops 23 and
24 vorgesehen, wobei der Radialanschlag 24 durch den Innenring der Axialla- gereinheit 14 ausgebildet ist. Die Radialanschläge 23 und 24 treten jeweils ab einer definierten Position der Mutter 11 mit daran verlaufenden Auskragungen24, wherein the radial stop 24 is formed by the inner ring of the Axialla- gereinheit 14. The radial stops 23 and 24 each occur from a defined position of the nut 11 with protrusions extending thereon
25 und 26 in Kontakt. Zur besseren Nachvollziehbarkeit ist ein Zusammenwirken dieser Elemente in der perspektivischen Detailansicht in Fig.3 näher dargestellt.25 and 26 in contact. For better traceability, an interaction of these elements in the perspective detail view in Figure 3 is shown in more detail.
Aus Fig.4 ist eine alternative Möglichkeit zur Begrenzung der axialen Bewegung einer Mutter 11 ' dargestellt. Im Unterschied zu der vorher beschriebenen Variante wird hierbei eine durch die Spindel 13 hervorgerufene, axiale Verschiebung der Mutter 11 ' durch beidseitig angeordnete - hier nur auf einer Sei- te dargestellt - Axialanschläge 27 bewerkstelligt, die fest mit dem Zylinderkopf 5 verbunden sind. From Figure 4, an alternative way to limit the axial movement of a nut 11 'is shown. In contrast to the previously described variant, an axial displacement of the nut 11 'caused by the spindle 13 is effected by axial stops 27 arranged on both sides-shown here only on one side-which are fixedly connected to the cylinder head 5.
Bezu gsze ichen l isteI would like to say
1 Ventilnockenwelle1 valve camshaft
2 Nocken2 cams
3 Betätigungseinrichtung3 actuator
4a ,4b Ladungswechselventile4a, 4b charge exchange valves
5 Zylinderkopf5 cylinder head
6 Antriebsscheibe6 drive pulley
7 Verstelleinrichtung7 adjustment
8 Verstellmotor8 adjusting motor
9 Kammer9 chamber
10 Deckel10 lids
11 , 11' Mutter11, 11 'mother
12 Getriebe12 gears
13 Spindel13 spindle
14 Axiallagereinheit14 thrust bearing unit
15 Kreuzschieberkupplung15 cross slide coupling
16 Antriebsbaueinheit16 drive assembly
17 erster Teil Antriebsbaueinheit17 first part drive assembly
18 zweiter Teil Antriebsbaueinheit18 second part drive assembly
19 Innenring Gleitlagerung19 inner ring plain bearing
20 Führungskörper20 guide body
21 Führungsbahn Ventilnockenwelle21 guideway valve camshaft
22 Führungsbahn Antriebsbaueinheit22 guideway drive assembly
23 , 24 Radialanschläge23, 24 Radial stops
25 ,26 Auskragungen Mutter25, 26 overhangs nut
27 Axialanschlag 27 axial stop

Claims

Patentansprüche claims
1. Ventiltrieb zum Steuern von Ladungswechselventilen (4a, 4b) einer Brennkraftmaschine, umfassend mindestens eine innerhalb eines Zylinderkopfs (5) der Brennkraftmaschine gelagerte Ventilnockenwelle (1 ), die über eine Antriebsscheibe (6) in Rotation versetzbar ist, wobei eine einen Verstellmotor (8) und ein Getriebe (12) aufweisende Verstelleinrichtung1. Valve drive for controlling charge exchange valves (4a, 4b) of an internal combustion engine, comprising at least one inside a cylinder head (5) of the internal combustion engine mounted valve camshaft (1) which is set in rotation via a drive pulley (6), wherein an adjusting motor (8 ) and a transmission (12) having adjusting
(7) vorgesehen ist, welche bei Betätigung des Verstellmotors (8) und über das zwischengeschaltete Getriebe (12) gezielt für eine axiale Verschiebung und/oder Verdrehung der mindestens einen Ventilnockenwelle (1 ) relativ zu der Antriebsscheibe (6) sorgt, um eine über Nocken (2) der min- destens einen Ventilnockenwelle (1 ) stattfindende Betätigung der Ladungswechselventile (4a, 4b) gezielt zu variieren, dadurch gekennzeichnet, dass der Verstellmotor (8) überwiegend oder vollständig innerhalb einer gemeinsamen Kammer (9) mit der Antriebsscheibe (6) platziert ist.(7) is provided, which specifically provides for actuation of the adjusting motor (8) and the intermediate gear (12) for an axial displacement and / or rotation of the at least one valve camshaft (1) relative to the drive pulley (6) to one over Cams (2) of the at least one valve camshaft (1) occurring operation of the charge exchange valves (4a, 4b) to vary specifically, characterized in that the adjusting motor (8) predominantly or completely within a common chamber (9) with the drive pulley (6 ) is placed.
2. Ventiltrieb nach Anspruch 1 , dadurch gekennzeichnet, dass die Nocken (2) der mindestens einen Ventilnockenwelle (1 ) eine in axialer Richtung veränderliche Nockenerhebung aufweisen.2. Valve drive according to claim 1, characterized in that the cams (2) of the at least one valve camshaft (1) have a variable in the axial direction cam lobe.
3. Ventiltrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Getriebe (12) eine mit einem Ende der mindestens einen Ventilnockenwelle (1 ) fest verbundene Mutter (11 , 11 ') und eine mit dem Verstellmotor3. Valve drive according to claim 1 or 2, characterized in that the transmission (12) with one end of the at least one valve camshaft (1) fixedly connected nut (11, 11 ') and one with the adjusting motor
(8) in Verbindung stehende Spindel (13) umfasst und sich über eine Axiallagereinheit (14) an einer die Antriebsscheibe (6) tragenden Antriebsbau- einheit (16) abstützt, wobei eine über den Verstellmotor (8) eingeleitete(8) comprises associated spindle (13) and is supported via a thrust bearing unit (14) on a Antriebsbau- unit (16) carrying the drive pulley (6), one via the adjusting motor (8) introduced
Relativrotation der Spindel (13) bezüglich der Antriebsscheibe (6) in eine axiale Verschiebung der Mutter (11 , 11 ') umsetzbar ist. Relative rotation of the spindle (13) with respect to the drive pulley (6) in an axial displacement of the nut (11, 11 ') can be implemented.
4. Ventiltrieb nach Anspruch 3, dadurch gekennzeichnet, dass die axiale Verschiebung der Mutter (11 ') in beide Richtungen durch jeweils fest mit dem Zylinderkopf (5) in Verbindung stehende Axialanschläge (27) begrenzbar ist.4. Valve gear according to claim 3, characterized in that the axial displacement of the nut (11 ') in both directions by each fixed to the cylinder head (5) in conjunction axial stops (27) is limited.
5. Ventiltrieb nach Anspruch 3, dadurch gekennzeichnet, dass die axiale Verschiebung der Mutter (11 ) in beide Richtungen durch jeweils ortsfest auf der Spindel (13) platzierte Radialanschläge (23, 24) begrenzbar ist, welche ab einer definierten Position mit jeweils an der Mutter (11 ) vorge- sehenen Auskragungen (25, 26) in Kontakt treten.5. Valve gear according to claim 3, characterized in that the axial displacement of the nut (11) in both directions by each stationary on the spindle (13) placed radial stops (23, 24) can be limited, which from a defined position with each at the Mother (11) provided projections (25, 26) come into contact.
6. Ventiltrieb nach einem der Ansprüche 3-5, dadurch gekennzeichnet, dass die Axiallagereinheit (14) nach Art eines zweiseitig wirkenden, vorgespannten Wälzlagers ausgebildet ist.6. Valve drive according to one of claims 3-5, characterized in that the thrust bearing unit (14) is designed in the manner of a two-sided acting, prestressed rolling bearing.
7. Ventiltrieb nach einem der Ansprüche 3-6, dadurch gekennzeichnet, dass zwischen Spindel (13) und Verstellmotor (8) eine Kupplung in Form einer Kreuzschieberkupplung (15) vorgesehen ist.7. Valve drive according to one of claims 3-6, characterized in that between the spindle (13) and adjusting motor (8) a coupling in the form of a cross slide coupling (15) is provided.
8. Ventiltrieb nach einem der Ansprüche 2-7, dadurch gekennzeichnet, dass in radialer Richtung zwischen der mindestens einen Ventilnockenwelle (1 ) und der die Antriebsscheibe (6) tragenden Antriebsbaueinheit (16) mindestens ein Führungskörper (20) platziert ist, welcher in seitens der mindestens einen Ventilnockenwelle (1 ) und seitens der Antriebsbau- einheit (16) vorgesehenen, zueinander korrespondierenden und helixartig verlaufenden Führungsbahnen (21 , 22) läuft und bei einer axialen Verschiebung der mindestens einen Ventilnockenwelle (1 ) eine Relativverdrehung der mindestens einen Ventilnockenwelle (1 ) bezüglich der Antriebsbaueinheit (16) bewirkt.8. Valve drive according to one of claims 2-7, characterized in that in the radial direction between the at least one valve camshaft (1) and the drive pulley (6) carrying drive assembly (16) at least one guide body (20) is placed, which in part the at least one valve camshaft (1) and guide tracks (21, 22) which extend from one another and run on the drive unit (16) run, and when the at least one valve camshaft (1) is displaced axially, a relative rotation of the at least one valve camshaft (1 ) with respect to the drive assembly (16).
9. Ventiltrieb nach Anspruch 8, dadurch gekennzeichnet, dass die Spindel (13) und die Führungsbahnen (21 , 22) sich überwiegend oder vollständig axial überlappend angeordnet sind. 9. Valve drive according to claim 8, characterized in that the spindle (13) and the guide tracks (21, 22) are arranged predominantly or completely axially overlapping.
10. Ventiltrieb nach Anspruch 8, dadurch gekennzeichnet, dass der mindestens eine Führungskörper (20) kugelförmig ausgestaltet ist.10. Valve gear according to claim 8, characterized in that the at least one guide body (20) is designed spherical.
11. Ventiltrieb nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Verstellmotor (8) nach Art eines Elektromotors ausgebildet ist.11. Valve drive according to one of the preceding claims, characterized in that the adjusting motor (8) is designed in the manner of an electric motor.
12. Ventiltrieb nach einem der vorhergehenden Ansprüche, dadurch ge- kennzeichnet, dass die Antriebsscheibe (6) als Kettenscheibe ausgeführt ist.12. Valve drive according to one of the preceding claims, character- ized in that the drive disc (6) is designed as a chain disc.
13. Brennkraftmaschine zum Antrieb eines Kraftfahrzeuges, umfassend einen Ventiltrieb nach einem der Ansprüche 1 -12. 13. Internal combustion engine for driving a motor vehicle, comprising a valve train according to one of claims 1 -12.
EP10703648.5A 2009-02-26 2010-02-11 Valve drive of an internal combustion engine having an adjustment device Not-in-force EP2401480B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009010407A DE102009010407A1 (en) 2009-02-26 2009-02-26 Valve gear of an internal combustion engine with an adjusting device
PCT/EP2010/051712 WO2010097295A1 (en) 2009-02-26 2010-02-11 Valve drive of an internal combustion engine having an adjustment device

Publications (2)

Publication Number Publication Date
EP2401480A1 true EP2401480A1 (en) 2012-01-04
EP2401480B1 EP2401480B1 (en) 2014-11-19

Family

ID=42108895

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10703648.5A Not-in-force EP2401480B1 (en) 2009-02-26 2010-02-11 Valve drive of an internal combustion engine having an adjustment device

Country Status (4)

Country Link
US (1) US8757117B2 (en)
EP (1) EP2401480B1 (en)
DE (1) DE102009010407A1 (en)
WO (1) WO2010097295A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010045047A1 (en) * 2010-09-10 2012-03-15 Thyssenkrupp Presta Teccenter Ag Method for assembling a motor module

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2930266A1 (en) * 1979-07-26 1981-02-12 Volkswagenwerk Ag CAMSHAFT ARRANGEMENT, IN PARTICULAR FOR AN INTERNAL COMBUSTION ENGINE
US4601266A (en) * 1983-12-30 1986-07-22 Renold Plc Phasing device for machine applications
KR0158899B1 (en) * 1992-09-30 1998-12-15 와다 요시히로 System for controlling valve shift timing of an engine
JP3392514B2 (en) * 1993-05-10 2003-03-31 日鍛バルブ株式会社 Engine valve timing control device
GB2347987A (en) * 1999-02-18 2000-09-20 Mechadyne Int Plc Variable phase coupling
US6216654B1 (en) * 1999-08-27 2001-04-17 Daimlerchrysler Corporation Phase changing device
GB0006875D0 (en) * 2000-03-21 2000-05-10 Walters Christopher P M Valve control mechanism
JP4134587B2 (en) 2001-04-16 2008-08-20 スズキ株式会社 Valve operating device and internal combustion engine provided with the same
DE10248351A1 (en) 2002-10-17 2004-04-29 Ina-Schaeffler Kg Electrically driven camshaft adjuster
JP2008095549A (en) * 2006-10-06 2008-04-24 Denso Corp Valve timing adjusting device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010097295A1 *

Also Published As

Publication number Publication date
US8757117B2 (en) 2014-06-24
DE102009010407A1 (en) 2010-09-02
WO2010097295A1 (en) 2010-09-02
EP2401480B1 (en) 2014-11-19
US20110303172A1 (en) 2011-12-15

Similar Documents

Publication Publication Date Title
EP1715143B1 (en) Camshaft phasing device for an internal combustion engine
DE10116707B4 (en) Device for relative rotation of a camshaft relative to a crankshaft of an internal combustion engine
DE102011108728B4 (en) Valve train for internal combustion engines for actuating gas exchange valves
DE102018114793A1 (en) Valve opening / VENTILSCHLIESSZEITSTEUERVORRICHTUNG
EP2676009A1 (en) Activation module for at least one gas exchange valve of an internal combustion engine
DE102014216929A1 (en) Actuator for a coupling with a multi-part rotor and a contoured wire spring
DE102004021375B4 (en) Valve gear of an internal combustion engine with at least one camshaft
WO2006074732A1 (en) Device for modifying the control times of an internal combustion engine
EP2676010A2 (en) Three-shaft adjustment mechanism with altered mass distribution and method for producing a shaft generator
WO2014016242A1 (en) Camshaft adjuster transmission
EP2401480B1 (en) Valve drive of an internal combustion engine having an adjustment device
WO2015021984A1 (en) Camshaft adjuster
DE102008061882A1 (en) Internal combustion engine with an accessory drive
DE102004007052A1 (en) Phase angle adjustment system for camshaft in internal combustion engine has eccentric drive with external toothed pinion engaging gear ring driven by timing chain
WO2013053416A1 (en) Valve operating device for an internal combustion engine
WO2017021042A1 (en) Continuously variable transmission and vehicle comprising a cvt
EP2744987B1 (en) Camshaft for the valve train of an internal combustion engine
DE102017116732A1 (en) Camshaft adjuster for the variable adjustment of the valve timing of an internal combustion engine and arrangement for the sealing of a camshaft adjuster
EP0290864A2 (en) Internal axis rotary piston machine
DE102010018210A1 (en) Device for adjusting the angular position of a shaft
DE19501172C2 (en) Rotary drive arrangement
DE102018125582B4 (en) Valve timing adjustment device
DE102012203984A1 (en) Device i.e. camshaft adjuster, for displacing camshaft of internal combustion engine of motor car, has gearing tracks axially arranged at distance from each other by annular gap, and output ring gears rotatably inserted into annular gap
DE102018214698B4 (en) Valve train for an internal combustion engine
DE10112048A1 (en) Setting device for camshaft with variable phase angle creates phase angle by relative turn of drive shaft and camshaft

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20110926

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140717

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 697166

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141215

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010008278

Country of ref document: DE

Effective date: 20141231

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502010008278

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150123

Ref country code: DE

Ref legal event code: R081

Ref document number: 502010008278

Country of ref document: DE

Owner name: SCHAEFER, JENS, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150123

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20141119

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150319

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150319

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150219

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150220

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010008278

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150211

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20150820

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150228

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150228

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150219

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150302

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 697166

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150211

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502010008278

Country of ref document: DE

Owner name: SCHAEFER, JENS, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20100211

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 502010008278

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141119

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190228

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502010008278

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200901

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522