EP0903471A1 - Device for variable camshaft timing in an internal combustion engine - Google Patents

Device for variable camshaft timing in an internal combustion engine Download PDF

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Publication number
EP0903471A1
EP0903471A1 EP98890262A EP98890262A EP0903471A1 EP 0903471 A1 EP0903471 A1 EP 0903471A1 EP 98890262 A EP98890262 A EP 98890262A EP 98890262 A EP98890262 A EP 98890262A EP 0903471 A1 EP0903471 A1 EP 0903471A1
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EP
European Patent Office
Prior art keywords
camshaft
gear
electric motor
drive wheel
planetary gear
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
EP98890262A
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German (de)
French (fr)
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EP0903471B1 (en
Inventor
Siegfried Ing. Heer
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TCG Unitech AG
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TCG Unitech AG
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Publication date
Priority claimed from AT0158697A external-priority patent/AT407282B/en
Application filed by TCG Unitech AG filed Critical TCG Unitech AG
Publication of EP0903471A1 publication Critical patent/EP0903471A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to a device for adjusting the camshaft Internal combustion engine, with an adjustment mechanism that by an electric motor firmly connected to the camshaft or to the drive wheel is operated.
  • the camshaft of an internal combustion engine is usually driven by a sprocket is connected to the crankshaft via a drive chain, or one designed as a pulley Drive wheel, which is connected to the crankshaft via a toothed belt, driven.
  • Adjustment devices are known from DE 41 10 088 C1 and from DE 39 29 619 A1, where between a component connected to the camshaft and a an adjusting element is provided with the drive wheel in connection with the component has two helical gears with the corresponding gears of the camshaft or the drive wheel are engaged.
  • an axial displacement of this adjustment element can cause the camshaft to rotate relative to the drive wheel become.
  • One possibility of the axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is operated.
  • the disadvantage of this solution is that to achieve the required forces relatively large hydraulic piston is required, which is a great deal of construction represents.
  • the oil consumption by the operation of the piston is relatively large represents a load on the engine by an appropriate oil pump.
  • the camshaft only between two end positions be switched back and forth.
  • an electrical adjustment device is known from DE 41 01 676 A1, in which a Electric motor is provided, which moves the adjusting element via a threaded spindle.
  • a Electric motor is provided, which moves the adjusting element via a threaded spindle.
  • the adjusting element rotates essentially at the camshaft speed, it must an axial thrust bearing can be provided between the electric motor and the adjusting element, that absorbs the relative movement between the torsion-resistant and the rotating component.
  • This thrust bearing is in the known solution practically throughout Engine operation is loaded because of the torsional moments acting between the drive wheel and the camshaft always exerted a force acting in the axial direction on the adjusting element becomes. This thrust bearing is therefore a critical part of the life of the engine restricted.
  • an adjustment mechanism in which an electric motor is provided, which is fixedly connected to the drive wheel which drives the camshaft.
  • the electric motor drives a screw spindle on which an adjusting element is guided, that via a first group of levers with the camshaft and via a second group of Lever is connected to the drive wheel.
  • the operation of the electric motor can in this way a rotation of the camshaft relative to the drive wheel can be effected.
  • Such a device is very complex and requires a relatively large amount of space.
  • DE-A 36 07 256 shows an adjustment device in which the adjustment of the Camshaft is done by a stepper motor that is firmly connected to the drive wheel.
  • this stepper motor must absorb all the torque that drives the Camshaft is required.
  • Such a stepper motor decides due to the required Size and power consumption for practical use.
  • the US-A 5,293,845 shows an adjusting mechanism for a camshaft, which is a planetary gear having.
  • a stationary electric motor causes a phase shift the camshaft.
  • the disadvantage is that the power transmission for driving the Camshaft on the rotating gears of the planetary gear, so that the limited Efficiency of the planetary gear leads to the corresponding losses. Furthermore moves the axis of the drive wheel during an adjustment, which is due to complex Compensate clamping mechanisms.
  • the object of the present invention is to provide a device in which the above Disadvantages described can be avoided, and which makes it possible in particular to enable a quick and reliable adjustment of the camshaft in a simple manner. in particular, the device should take up little space, so that an independent Adjustment of two camshafts with a small axial distance is possible.
  • the adjusting mechanism Planetary gear includes.
  • a planetary gear By using a planetary gear, adjusting elements, which move in the axial direction can be avoided. This allows the mechanical Construction can be simplified and a small size can be achieved.
  • Another The advantage of the invention is that it is relatively easy to seal oil securely ensure that the electric motor runs dry. To also run an emergency run To ensure failure of the adjustment, it is generally provided that the drive torque of the camshaft is reached an end position in which a safe Operation of the internal combustion engine is possible.
  • the planetary gear preferably has a large reduction ratio, which preferably is greater than 1: 8 and particularly preferably greater than 1:12. Through one Reduction ratio can, if necessary, be achieved or at least can be approximately achieved. In this way, the electric motor during normal operation of the internal combustion engine, in which there is no adjustment, not or only minimal burden. This increases the service life and reduces the amount of energy required.
  • the Electric motor and an internally toothed gear of the planetary gear fixed to the drive wheel are connected.
  • the planet carrier of the planetary gear is preferably fixed connected to the camshaft.
  • the output shaft of the electric motor is included the sun gear of the planetary gear. This way, a relatively large one Reduction ratio can be achieved.
  • the planetary gear consists only of an internally toothed gear and a planet carrier with a single planet gear mounted on it.
  • a sun gear is one of them Planetary gear not provided.
  • the number of teeth of the planet gear is preferred only slightly smaller than the number of teeth of the internally toothed gear, and indeed preferably by one. This means that the axis of the planet gear is only slightly opposite the axis of the internally toothed gear is shifted. Stand this way always several teeth of these gears engaged at the same time, so that a very favorable situation with regard to the load is given.
  • Such a device can therefore be extremely be made compact, so that even with a small distance two camshafts independently can be adjusted from each other. It also creates a large reduction ratio achieved what in terms of the required size of the electric motor is cheap.
  • the electric motor is firmly connected to the camshaft and that the planet gear is connected to the drive gear via a synchronization clutch.
  • the Synchronous clutch which is designed as an Oldham clutch, for example, the same axial offset from the planet gear and drive gear.
  • the electric motor is firmly connected to the drive wheel and that the planet gear is connected to the camshaft via a synchronous clutch is.
  • the planet carrier acts as the output shaft of the electric motor is formed, which has a desaxed portion on which the planet gear is stored.
  • Exact control of the adjustment angle can be achieved in that the electric motor is designed as a stepper motor.
  • the present invention relates to an internal combustion engine, which has a device as described above.
  • FIG. 1 a first embodiment variant of the present Invention in longitudinal section
  • Fig. 2 shows another embodiment of the present Invention in longitudinal section
  • Fig. 3 shows the variant of Fig. 2 in a section Line III - III in Fig. 2, wherein individual components are not to increase clarity are shown
  • 4 is an exploded view of the embodiment of FIG. 2 and 3
  • FIG. 5 shows a detail of this embodiment variant.
  • FIG. 1 A first embodiment variant of the present invention is shown in FIG. 1.
  • a bracket 30 On a camshaft 1, a bracket 30 is rotatable, but axially fixed.
  • a toothing 36 is provided on the outer circumference, which for A toothed belt is used to drive the camshaft 1 and thus the drive wheel represents.
  • the holder 30 also carries a plate 31 on which an electric motor 15 is firmly attached. The electric motor 15 thus rotates together with the drive wheel 36. Slip rings 19 are provided, which are fed by fixed sliding contacts 41 become.
  • the pinion 32 of the electric motor 15 stands with a planetary gears 33, 34 Ring gear, i.e. an internally toothed gear 35 which is integral with the bracket 30 is formed.
  • a planet carrier 37 which rotatably supports the planet gears 33, 34, is fixed connected to the camshaft 1. If the electric motor 15 is not activated, it stops the pinion 32 is still with respect to the motor 15, and thus the pinions 32 and Planet carrier 37 at the speed of the drive wheel 36, whereby the camshaft 1 rotates at this speed. By controlling the electric motor 15, a Relative movement of the planet carrier 37 in relation to the drive wheel 36 can be effected. Due to the relatively large translation by the planetary gear, this is achieved accordingly large torques for adjusting the camshaft 1 by a relative underpowered electric motor 15 can be provided. The seal of the system in relation to the oil chamber in the area of camshaft 1 takes place via radial shaft seals 38 and 39. A screw 40 is used to attach the planet carrier the camshaft 1.
  • the planetary gear consisting of the gears 32, 33, 34 and 35, in a known manner and be carried out without play.
  • these gears 32 to 35 can be made of high-strength plastic.
  • the camshaft 1 has one at its end Flange 2.
  • a drive wheel 6 for the camshaft is on the flange 2 via a slide bearing 42 1, which has a toothing 6a on its circumference for receiving a not shown Has drive chain.
  • a holding body 43 is connected to the flange 2 via threaded bolts 8.
  • the threaded bolts 8 pass through openings 10 in the drive wheel 6, which are designed as arc-shaped elongated holes. This is the angular range at the same time the adjustment of the camshaft 1 defined.
  • a shaft nut 44 is fastened to the holding body 43, which carries an electric motor 15 via screws 45. As with the previous one
  • the electric motor 15 is implemented as a variant via slip rings 19 and sliding contacts 41 powered.
  • the output shaft 29 of the electric motor 15 is on the holding body 43 via roller bearings 46 and 47 and mounted on the shaft nut 44 and has one at its end remote from the motor 15 desaxed section 48.
  • the roller bearings 46 and 47 are secured by circlips 49 in Maintained axial direction.
  • At the desaxed section there is a planet gear via a needle bearing 50 51 mounted, which is in engagement with an internally toothed gear 52, which is in one piece is formed with the holding body 43.
  • An axial plain bearing bush 53 ensures that Planet gear 51 in the axial direction.
  • the planet gear 51 is via a so-called Oldham clutch 54, which is a constant velocity joint represents, with the drive wheel 6 in rotary connection.
  • the Oldham coupling 54 has one Engagement part 55, which is connected to the planet gear 51 via a sliding guide 56, which limited movement of the engaging member 55 with respect to the planet gear 51 in the Level of Fig. 2 allows.
  • the engagement part 55 is with an adapter 58 of the Drive wheel 6 via a further sliding guide 57 in connection, which is limited Movement of the engaging part 55 relative to the drive wheel 6 in the plane of FIG. 3 enables. In this way, it is possible to drive the drive torque from the drive wheel 6 to the To transfer planet gear 51, wherein the eccentricity ⁇ is overcome. Screws 59 connect the adapter 58 to the sprocket 6 and at the same time secure the engagement part 55.
  • a housing 60 which seals with a radial shaft sealing ring 61 with respect to the holding part 43 is, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, such as the electric motor 15.
  • the structure of the planetary gear is shown in FIG. 5.
  • the internal gear 52 in the holding body 43 has fourteen teeth, while the planet gear 51 has thirteen teeth.
  • the tip circle of the planet gear touches 51 approximately the tip circle of the internally toothed gear 52.
  • the planetary gear can be made very compact. It also causes one revolution of the output shaft 29 of the electric motor 15 is only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load on the Electric motor can also be minimized.
  • the present invention makes it possible to control the valve timing of an internal combustion engine easy and safe to change. It is particularly advantageous that any Intermediate positions can be controlled.

Abstract

The adjusting mechanism for the camshaft has a planetary gear with a high gear reduction ratio, preferably more than 1:8 and especially more than 1:12. The gear is self-locking relative to adjustment of the camshaft (1) by the drive pulley (36). The mechanism is operated by an electric motor, and the motor and an internally toothed gear (35) are fastened to the drive pulley. The sun wheel (37) is fastened to the camshaft.

Description

Die vorliegende Erfindung betrifft eine Vorrichtung zur Verstellung der Nockenwelle einer Brennkraftmaschine mit innerer Verbrennung, mit einem Verstellmechanismus, der durch einen fest mit der Nockenwelle oder mit dem Antriebsrad fest verbundenen Elektromotor betätigt wird.The present invention relates to a device for adjusting the camshaft Internal combustion engine, with an adjustment mechanism that by an electric motor firmly connected to the camshaft or to the drive wheel is operated.

Um in verschiedenen Bereichen des Motorkennfeldes optimale Verbrauchs- und Abgaswerte zu erzielen, ist es erforderlich, die Ventilsteuerzeiten in Abhängigkeit verschiedener Betriebsparameter zu verändern. Eine solche Veränderung der Steuerzeiten kann in eleganter Weise durch eine Verdrehung der Nockenwelle in Bezug auf das sie antreibende Rad bewirkt werden. Die Nockenwelle einer Brennkraftmaschine wird üblicherweise durch ein Kettenrad, das mit der Kurbelwelle über eine Antriebskette verbunden ist, oder ein als Riemenscheibe ausgebildetes Antriebsrad, das über einen Zahnriemen mit der Kurbelwelle in Verbindung steht, angetrieben.To ensure optimum consumption and exhaust gas values in various areas of the engine map To achieve this, it is necessary to adjust the valve timing depending on various operating parameters to change. Such a change in tax times can be done in an elegant way caused by a rotation of the camshaft in relation to the wheel driving it. The camshaft of an internal combustion engine is usually driven by a sprocket is connected to the crankshaft via a drive chain, or one designed as a pulley Drive wheel, which is connected to the crankshaft via a toothed belt, driven.

Aus der DE 41 10 088 C1 und aus der DE 39 29 619 A1 sind Verstelleinrichtungen bekannt, bei denen zwischen einem mit der Nockenwelle in Verbindung stehenden Bauteil und einem mit dem Antriebsrad in Verbindung stehenden Bauteil ein Verstellelement vorgesehen ist, das zwei Schrägverzahnungen aufweist, die mit entsprechenden Verzahnungen der Nockenwelle bzw. des Antriebsrades in Eingriff stehen. Durch eine Axialverschiebung dieses Verstellelements kann eine Verdrehung der Nockenwelle gegenüber dem Antriebsrad bewirkt werden. Eine Möglichkeit der Axialverschiebung des Verstellelements ist dabei die Betätigung durch einen Hydraulikkolben, der in Abhängigkeit von der erforderlichen Verstellung betätigt wird. Nachteilig bei dieser Lösung ist, daß zur Erzielung der erforderlichen Kräfte ein relativ großer Hydraulikkolben erforderlich ist, was einen großen baulichen Aufwand darstellt. Außerdem ist der Ölverbrauch durch die Betätigung des Kolbens relativ groß, das eine Belastung des Motors durch ein entsprechende Ölpumpe darstellt. Darüber hinaus kann bei einer solchen bekannten Vorrichtung die Nockenwelle nur zwischen zwei Endstellungen hin- und her geschaltet werden.Adjustment devices are known from DE 41 10 088 C1 and from DE 39 29 619 A1, where between a component connected to the camshaft and a an adjusting element is provided with the drive wheel in connection with the component has two helical gears with the corresponding gears of the camshaft or the drive wheel are engaged. By an axial displacement of this adjustment element can cause the camshaft to rotate relative to the drive wheel become. One possibility of the axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is operated. The disadvantage of this solution is that to achieve the required forces relatively large hydraulic piston is required, which is a great deal of construction represents. In addition, the oil consumption by the operation of the piston is relatively large represents a load on the engine by an appropriate oil pump. Furthermore, can in such a known device, the camshaft only between two end positions be switched back and forth.

Weiters ist aus der DE 41 01 676 A1 eine elektrische Verstellvorrichtung bekannt, bei der ein Elektromotor vorgesehen ist, der über eine Gewindespindel das Verstellelement verschiebt. Da sich jedoch das Verstellelement im wesentlichen mit Nockenwellendrehzahl dreht, muß zwischen dem Elektromotor und dem Verstellelement ein Axialdrucklager vorgesehen sein, das die Relativbewegung zwischen dem verdrehfesten und dem sich drehenden Bauteil aufnimmt. Dieses Axialdrucklager ist bei der bekannten Lösung praktisch während des gesamten Motorbetriebs belastet, da durch die zwischen Antriebsrad und Nockenwelle wirkenden Torsionsmomente stets eine in Axialrichtung wirkende Kraft auf das Verstellelement ausgeübt wird. Dieses Axialdrucklager ist daher ein kritischer Bauteil, der die Lebensdauer des Motors einschränkt.Furthermore, an electrical adjustment device is known from DE 41 01 676 A1, in which a Electric motor is provided, which moves the adjusting element via a threaded spindle. However, since the adjusting element rotates essentially at the camshaft speed, it must an axial thrust bearing can be provided between the electric motor and the adjusting element, that absorbs the relative movement between the torsion-resistant and the rotating component. This thrust bearing is in the known solution practically throughout Engine operation is loaded because of the torsional moments acting between the drive wheel and the camshaft always exerted a force acting in the axial direction on the adjusting element becomes. This thrust bearing is therefore a critical part of the life of the engine restricted.

Weiters ist aus der GB-A 2 221 513 ein Verstellmechanismus bekannt, bei dem ein Elektromotor vorgesehen ist, der fest mit dem Antriebsrad verbunden ist, das die Nockenwelle antreibt. Der Elektromotor treibt eine Schraubspindel an, auf der ein Verstellelement geführt ist, das über eine erste Gruppe von Hebeln mit der Nockenwelle und über eine zweite Gruppe von Hebeln mit dem Antriebsrad in Verbindung steht. Durch den Betrieb des Elektromotors kann auf diese Weise eine Verdrehung der Nockenwelle gegenüber dem Antriebsrad bewirkt werden. Eine solche Vorrichtung ist sehr aufwendig und benötigt einen relativ großen Bauraum.Furthermore, from GB-A 2 221 513 an adjustment mechanism is known in which an electric motor is provided, which is fixedly connected to the drive wheel which drives the camshaft. The electric motor drives a screw spindle on which an adjusting element is guided, that via a first group of levers with the camshaft and via a second group of Lever is connected to the drive wheel. The operation of the electric motor can in this way a rotation of the camshaft relative to the drive wheel can be effected. Such a device is very complex and requires a relatively large amount of space.

Ferner zeigt die DE-A 36 07 256 eine Verstellvorrichtung, bei der die Verstellung der Nockenwelle durch einen Schrittmotor erfolgt, der fest mit dem Antriebsrad verbunden ist. Dieser Schrittmotor muß jedoch das gesamte Drehmoment aufnehmen, das zum Antrieb der Nockenwelle erforderlich ist. Ein solcher Schrittmotor scheidet aufgrund der erforderlichen Größe und Leistungsaufnahme für den praktischen Einsatz aus.Furthermore, DE-A 36 07 256 shows an adjustment device in which the adjustment of the Camshaft is done by a stepper motor that is firmly connected to the drive wheel. However, this stepper motor must absorb all the torque that drives the Camshaft is required. Such a stepper motor decides due to the required Size and power consumption for practical use.

Die US-A 5,293,845 zeigt einen Verstellmechanismus für eine Nockenwelle, der ein Planetengetriebe aufweist. Ein feststehender Elektromotor bewirkt dabei eine Phasenverschiebung der Nockenwelle. Nachteilig dabei ist jedoch, daß die Kraftübertragung für den Antrieb der Nockenwelle über die rotierenden Zahnräder des Planetengetriebes erfolgt, so das der beschränkte Wirkungsgrad des Planetengetriebes zu den entsprechenden Verlusten führt. Außerdem verschiebt sich bei einer Verstellung die Achse des Antriebsrades, was durch aufwendige Spannmechanismen auszugleichen ist.The US-A 5,293,845 shows an adjusting mechanism for a camshaft, which is a planetary gear having. A stationary electric motor causes a phase shift the camshaft. The disadvantage, however, is that the power transmission for driving the Camshaft on the rotating gears of the planetary gear, so that the limited Efficiency of the planetary gear leads to the corresponding losses. Furthermore moves the axis of the drive wheel during an adjustment, which is due to complex Compensate clamping mechanisms.

Aufgabe der vorliegenden Erfindung ist es, eine Vorrichtung zu schaffen, bei der die oben beschriebenen Nachteile vermieden werden können, und die es insbesonders ermöglicht, in einfacher Weise eine schnelle und zuverlässige Verstellung der Nockenwelle zu ermöglichen. insbesonders soll die Vorrichtung wenig Bauraum beanspruchen, so daß auch eine unabhängige Verstellung von zwei Nockenwellen mit geringem Axialabstand möglich ist.The object of the present invention is to provide a device in which the above Disadvantages described can be avoided, and which makes it possible in particular to enable a quick and reliable adjustment of the camshaft in a simple manner. in particular, the device should take up little space, so that an independent Adjustment of two camshafts with a small axial distance is possible.

Diese Aufgaben werden erfindungsgemäß dadurch gelöst, daß der Verstellmechanismus ein Planetengetriebe umfaßt. Durch die Verwendung eines Planetengetriebes können Verstellelemente, die sich in Axialrichtung bewegen, vermieden werden. Dadurch kann der mechanische Aufbau vereinfacht werden und eine geringe Baugröße erreicht werden. Ein weiterer Vorteil der Erfindung besteht darin, daß es relativ einfach ist, eine sichere Ölabdichtung zu gewährleisten, so daß der Elektromotor im Trockenen läuft. Um auch einen Notlaufbetrieb bei Ausfall der Verstellung gewährleisten zu können, ist im allgemeinen vorgesehen, daß durch das Antriebsmoment der Nockenwelle eine Endstellung erreicht wird, bei der ein gefahrloser Betrieb der Brennkraftmaschine möglich ist.According to the invention, these objects are achieved in that the adjusting mechanism Planetary gear includes. By using a planetary gear, adjusting elements, which move in the axial direction can be avoided. This allows the mechanical Construction can be simplified and a small size can be achieved. Another The advantage of the invention is that it is relatively easy to seal oil securely ensure that the electric motor runs dry. To also run an emergency run To ensure failure of the adjustment, it is generally provided that the drive torque of the camshaft is reached an end position in which a safe Operation of the internal combustion engine is possible.

Vorzugsweise weist das Planetengetriebe ein großes Untersetzungsverhältnis auf, das vorzugsweise größer als 1:8 und besonders vorzugsweise größer als 1:12 ist. Durch ein solches Untersetzungsverhältnis kann gegebenenfalls eine Selbsthemmung erreicht werden oder zumindest näherungsweise erreicht werden. Auf diese Weise wird der Elektromotor während des normalen Betriebs der Brennkraftmaschine, bei dem keine Verstellung erfolgt, nicht oder nur minimal belastet. Dies erhöht die Lebensdauer und verringert den erforderlichen Energieaufwand. The planetary gear preferably has a large reduction ratio, which preferably is greater than 1: 8 and particularly preferably greater than 1:12. Through one Reduction ratio can, if necessary, be achieved or at least can be approximately achieved. In this way, the electric motor during normal operation of the internal combustion engine, in which there is no adjustment, not or only minimal burden. This increases the service life and reduces the amount of energy required.

In einer besonders vorteilhaften Ausführungsvariante der Erfindung ist vorgesehen, daß der Elektromotor und ein innenverzahntes Zahnrad des Planetengetriebes fest mit dem Antriebsrad verbunden sind. Dabei ist vorzugsweise der Planetenträger des Planetengetriebes fest mit der Nockenwelle verbunden. Die Abtriebswelle des Elektromotors steht in diesem Fall mit dem Sonnenrad des Planetengetriebes in Verbindung. Auf diese Weise kann ein relativ großes Untersetzungsverhältnis erreicht werden.In a particularly advantageous embodiment of the invention it is provided that the Electric motor and an internally toothed gear of the planetary gear fixed to the drive wheel are connected. The planet carrier of the planetary gear is preferably fixed connected to the camshaft. In this case, the output shaft of the electric motor is included the sun gear of the planetary gear. This way, a relatively large one Reduction ratio can be achieved.

In einer weiteren besonders begünstigten Ausführungsvariante der Erfindung ist vorgesehen, daß das Planetengetriebe nur aus einem innenverzahntes Zahnrad und einem Planetenträger mit einem einzigen darauf gelagerten Planetenrad besteht. Ein Sonnenrad ist bei einem solchen Planetengetriebe nicht vorgesehen. Vorzugsweise ist dabei die Zähnezahl des Planetenrades nur geringfügig kleiner als die Zähnezahl des innenverzahnten Zahnrades, und zwar vorzugsweise um eins. Dies bedeutet, daß die Achse des Planetenrades nur geringfügig gegenüber der Achse des innenverzahnten Zahnrades verschoben ist. Auf diese Weise stehen stets mehrere Zähne dieser Zahnräder gleichzeitig in Eingriff, so daß eine sehr günstige Situation in Hinblick auf die Belastung gegeben ist. Eine solche Vorrichtung kann daher äußerst kompakt ausgeführt werden, so daß auch bei geringem Abstand zwei Nockenwellen unabhängig voneinander verstellt werden können. Außerdem wird auf diese weise ein großes Untersetzungsverhältnis erreicht, was im Hinblick auf die erforderliche Baugröße des Elektromotors günstig ist.In a further particularly advantageous embodiment variant of the invention, that the planetary gear consists only of an internally toothed gear and a planet carrier with a single planet gear mounted on it. A sun gear is one of them Planetary gear not provided. The number of teeth of the planet gear is preferred only slightly smaller than the number of teeth of the internally toothed gear, and indeed preferably by one. This means that the axis of the planet gear is only slightly opposite the axis of the internally toothed gear is shifted. Stand this way always several teeth of these gears engaged at the same time, so that a very favorable situation with regard to the load is given. Such a device can therefore be extremely be made compact, so that even with a small distance two camshafts independently can be adjusted from each other. It also creates a large reduction ratio achieved what in terms of the required size of the electric motor is cheap.

Es ist dabei vorteilhaft, wenn der Elektromotor fest mit der Nockenwelle verbunden ist und daß das Planetenrad über eine Gleichlaufkupplung mit dem Antriebsrad verbunden ist. Die Gleichlaufkupplung, die beispielsweise als Oldhamkupplung ausgebildet ist, gleich dabei den axialen Versatz von Planetenrad und Antriebsrad aus.It is advantageous if the electric motor is firmly connected to the camshaft and that the planet gear is connected to the drive gear via a synchronization clutch. The Synchronous clutch, which is designed as an Oldham clutch, for example, the same axial offset from the planet gear and drive gear.

Alternativ dazu kann vorgesehen sein, daß der Elektromotor fest mit dem Antriebsrad verbunden ist und daß das Planetenrad über eine Gleichlaufkupplung mit der Nockenwelle verbunden ist.Alternatively, it can be provided that the electric motor is firmly connected to the drive wheel and that the planet gear is connected to the camshaft via a synchronous clutch is.

Konstruktiv besonders günstig ist es, wenn der Planetenträger als Abtriebswelle des Elektromotors ausgebildet ist, die einen desaxierten Abschnitt aufweist, auf dem das Planetenrad gelagert ist.It is structurally particularly favorable if the planet carrier acts as the output shaft of the electric motor is formed, which has a desaxed portion on which the planet gear is stored.

Eine exakte Steuerung des Verstellwinkels kann dadurch erreicht werden, daß der Elektromotor als Schrittmotor ausgebildet ist.Exact control of the adjustment angle can be achieved in that the electric motor is designed as a stepper motor.

Weiters betrifft die vorliegende Erfindung eine Brennkraftmaschine mit innerer Verbrennung, die eine Vorrichtung, wie sie oben beschrieben ist, aufweist.Furthermore, the present invention relates to an internal combustion engine, which has a device as described above.

In der Folge wird die Erfindung anhand der in den Figuren dargestellten Ausführungsbeispiele näher erläutert. Die Figuren zeigen: Fig. 1, eine erste Ausführungsvariante der vorliegenden Erfindung im Längsschnitt Fig. 2 eine weitere Ausführungsvariante der vorliegenden Erfindung im Längsschnitt; Fig. 3 die Ausführungsvariante von Fig. 2 in einem Schnitt nach Linie III - III in Fig. 2, wobei zur Erhöhung der Übersichtlichkeit einzelne Bauteile nicht dargestellt sind; die Fig. 4 eine Explosionsdarstellung der Ausführungsvariante von Fig. 2 und 3; und die Fig. 5 ein Detail dieser Ausführungsvariante.In the following, the invention is based on the exemplary embodiments shown in the figures explained in more detail. The figures show: FIG. 1, a first embodiment variant of the present Invention in longitudinal section Fig. 2 shows another embodiment of the present Invention in longitudinal section; Fig. 3 shows the variant of Fig. 2 in a section Line III - III in Fig. 2, wherein individual components are not to increase clarity are shown; 4 is an exploded view of the embodiment of FIG. 2 and 3; and FIG. 5 shows a detail of this embodiment variant.

Eine erste Ausführungsvariante der vorliegenden Erfindung ist in der Fig. 1 dargestellt. Auf einer Nockenwelle 1 ist eine Halterung 30 verdrehbar, jedoch axial unverschieblich befestigt. Auf dieser Halterung 30 ist am äußeren Umfang eine Verzahnung 36 vorgesehen, die zur Aufnahmen eine Zahnriemens dient, der die Nockenwelle 1 antreibt und die somit das Antriebsrad darstellt. Die Halterung 30 trägt weiters eine Platte 31, an der ein Elektromotor 15 fest angebracht ist. Der Elektromotor 15 dreht sich somit gemeinsam mit dem Antriebsrad 36. Es sind Schleifringe 19 vorgesehen, die von feststehenden Schleifkontakten 41 angespeist werden. Das Ritzel 32 des Elektromotors 15 steht über Planetenräder 33, 34 mit einem Hohlrad, d.h. einem innenverzahnten Zahnrad 35 in Eingriff, das einstückig in der Halterung 30 ausgebildet ist. Ein Planetenträger 37, der die Planetenräder 33, 34 drehbar trägt, ist fest mit der Nockenwelle 1 verbunden. Wenn der Elektromotor 15 nicht angesteuert wird, steht das Ritzel 32 in Bezug auf den Motor 15 still, und somit drehen sich Ritzel 32 und Planetenträger 37 mit der Drehzahl des Antriebsrades 36, wodurch auch die Nockenwelle 1 mit dieser Drehzahl rotiert. Durch die Ansteuerung des Elektromotors 15 kann eine Relativbewegung des Planetenträgers 37 in Bezug auf das Antriebsrad 36 bewirkt werden. Durch die relativ große Übersetzung durch das Planetengetriebe wird erreicht, das entsprechend große Drehmomente zur Verstellung der Nockenwelle 1 durch einen relativ leistungsschwachen Elektromotor 15 zur Verfügung gestellt werden können. Die Abdichtung des Systems gegenüber dem Ölraum im Bereich der Nockenwelle 1 erfolgt über Radialwellendichtringe 38 und 39. Eine Schraube 40 dient zur Befestigung des Planetenträgers an der Nockenwelle 1.A first embodiment variant of the present invention is shown in FIG. 1. On a camshaft 1, a bracket 30 is rotatable, but axially fixed. On this bracket 30, a toothing 36 is provided on the outer circumference, which for A toothed belt is used to drive the camshaft 1 and thus the drive wheel represents. The holder 30 also carries a plate 31 on which an electric motor 15 is firmly attached. The electric motor 15 thus rotates together with the drive wheel 36. Slip rings 19 are provided, which are fed by fixed sliding contacts 41 become. The pinion 32 of the electric motor 15 stands with a planetary gears 33, 34 Ring gear, i.e. an internally toothed gear 35 which is integral with the bracket 30 is formed. A planet carrier 37, which rotatably supports the planet gears 33, 34, is fixed connected to the camshaft 1. If the electric motor 15 is not activated, it stops the pinion 32 is still with respect to the motor 15, and thus the pinions 32 and Planet carrier 37 at the speed of the drive wheel 36, whereby the camshaft 1 rotates at this speed. By controlling the electric motor 15, a Relative movement of the planet carrier 37 in relation to the drive wheel 36 can be effected. Due to the relatively large translation by the planetary gear, this is achieved accordingly large torques for adjusting the camshaft 1 by a relative underpowered electric motor 15 can be provided. The seal of the system in relation to the oil chamber in the area of camshaft 1 takes place via radial shaft seals 38 and 39. A screw 40 is used to attach the planet carrier the camshaft 1.

Um eine möglichst große Genauigkeit zur Verstellung der Nockenwelle 1 zu erzielen, kann das Planetengetriebe, bestehend aus den Zahnrädern 32, 33, 34 und 35, in einer bekannten Art und Weise spielfrei ausgeführt sein. Um die Geräuschbelastung möglichst zu minimieren, können diese Zahnräder 32 bis 35 aus hochfestem Kunststoff ausgeführt sein.In order to achieve the greatest possible accuracy for adjusting the camshaft 1, the planetary gear, consisting of the gears 32, 33, 34 and 35, in a known manner and be carried out without play. In order to minimize noise pollution as much as possible, these gears 32 to 35 can be made of high-strength plastic.

Bei der Ausführungsvariante der Fig. 2 bis 5 besitzt die Nockenwelle 1 an ihrem Ende einen Flansch 2. Über ein Gleitlager 42 ist an dem Flansch 2 ein Antriebsrad 6 für die Nockenwelle 1 gelagert, das an seinem Umfang eine Verzahnung 6a zur Aufnahme einer nicht dargestellten Antriebskette aufweist. Über Gewindebolzen 8 ist mit dem Flansch 2 ein Haltekörper 43 verbunden. Die Gewindebolzen 8 treten dabei durch Öffnungen 10 im Antriebsrad 6 hindurch, die als bogenförmige Langlöcher ausgebildet sind. Dadurch ist gleichzeitig der Winkelbereich der Verstellung der Nockenwelle 1 definiert. Am Haltekörper 43 ist eine Wellenmutter 44 befestigt, die über Schrauben 45 einen Elektromotor 15 trägt. Wie bei der vorigen Ausführungsvariante wird der Elektromotor 15 über Schleifringe 19 und Schleifkontakte 41 mit Strom versorgt.In the embodiment variant of FIGS. 2 to 5, the camshaft 1 has one at its end Flange 2. A drive wheel 6 for the camshaft is on the flange 2 via a slide bearing 42 1, which has a toothing 6a on its circumference for receiving a not shown Has drive chain. A holding body 43 is connected to the flange 2 via threaded bolts 8. The threaded bolts 8 pass through openings 10 in the drive wheel 6, which are designed as arc-shaped elongated holes. This is the angular range at the same time the adjustment of the camshaft 1 defined. A shaft nut 44 is fastened to the holding body 43, which carries an electric motor 15 via screws 45. As with the previous one The electric motor 15 is implemented as a variant via slip rings 19 and sliding contacts 41 powered.

Die Abtriebswelle 29 des Elektromotors 15 ist über Wälzlager 46 und 47 am Haltekörper 43 und an der Wellenmutter 44 gelagert und besitzt an ihrem vom Motor 15 entfernten Ende einen desaxierten Abschnitt 48. Die Wälzlager 46 und 47 werden durch Sicherungsringe 49 in Axialrichtung gehalten. An dem desaxierten Abschnitt ist über ein Nadellager 50 ein Planetenrad 51 gelagert, das mit einem innenverzahnten Zahnrad 52 in Eingriff steht, das einstückig mit dem Haltekörper 43 ausgebildet ist. Eine Axialgleitlagerbuchse 53 sichert das Planetenrad 51 in Axialrichtung.The output shaft 29 of the electric motor 15 is on the holding body 43 via roller bearings 46 and 47 and mounted on the shaft nut 44 and has one at its end remote from the motor 15 desaxed section 48. The roller bearings 46 and 47 are secured by circlips 49 in Maintained axial direction. At the desaxed section there is a planet gear via a needle bearing 50 51 mounted, which is in engagement with an internally toothed gear 52, which is in one piece is formed with the holding body 43. An axial plain bearing bush 53 ensures that Planet gear 51 in the axial direction.

Das Planetenrad 51 ist über eine sogenannte Oldhamkupplung 54, die ein Gleichlaufgelenk darstellt, mit dem Antriebsrad 6 in Drehverbindung. Die Oldhamkupplung 54 besitzt einen Eingriffsteil 55, der mit dem Planetenrad 51 über eine Gleitführung 56 in Verbindung steht, die eine beschränkte Bewegung des Eingriffsteils 55 gegenüber dem Planetenrad 51 in der Ebene der Fig. 2 ermöglicht. Andererseits steht der Eingriffsteil 55 mit einem Adapter 58 des Antriebsrades 6 über eine weitere Gleitführung 57 in Verbindung, die eine beschränkte Bewegung des Eingriffsteils 55 gegenüber dem Antriebsrad 6 in der Ebene der Fig. 3 ermöglicht. Auf diese Weise ist es möglich, das Antriebsmoment von dem Antriebsrad 6 auf das Planetenrad 51 zu übertragen, wobei die Exzentrizität ε überwunden wird. Schrauben 59 verbinden den Adapter 58 mit dem Kettenrad 6 und sichern gleichzeitig den Eingriffsteil 55.The planet gear 51 is via a so-called Oldham clutch 54, which is a constant velocity joint represents, with the drive wheel 6 in rotary connection. The Oldham coupling 54 has one Engagement part 55, which is connected to the planet gear 51 via a sliding guide 56, which limited movement of the engaging member 55 with respect to the planet gear 51 in the Level of Fig. 2 allows. On the other hand, the engagement part 55 is with an adapter 58 of the Drive wheel 6 via a further sliding guide 57 in connection, which is limited Movement of the engaging part 55 relative to the drive wheel 6 in the plane of FIG. 3 enables. In this way, it is possible to drive the drive torque from the drive wheel 6 to the To transfer planet gear 51, wherein the eccentricity ε is overcome. Screws 59 connect the adapter 58 to the sprocket 6 and at the same time secure the engagement part 55.

Ein Gehäuse 60, das mit einem Radialwellendichtring 61 gegenüber dem Halteteil 43 abgedichtet ist, trennt die motorseitigen Bauteile, wie Nockenwelle 1, Oldhamkupplung 54 und das Planetengetriebe von den nicht ölbenetzten Bauteilen, wie den Elektromotor 15.A housing 60, which seals with a radial shaft sealing ring 61 with respect to the holding part 43 is, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, such as the electric motor 15.

Aus der Fig. 5 ist der Aufbau des Planetengetriebes ersichtlich. Das innenverzahnte Zahnrad 52 im Haltekörper 43 besitzt vierzehn Zähne, während das Planetenrad 51 dreizehn Zähne besitzt. An der dem Eingriffspunkt gegenüberliegenden Stelle berührt der Kopfkreis des Planetenrades 51 näherungsweise den Kopfkreis des innenverzahnten Zahnrades 52. Auf diese Weise ist etwa die Hälfte aller Zähne stets in Eingriff, was die Zahnflankenbelastung verringert. Daher kann das Planetengetriebe sehr kompakt ausgeführt werden. Außerdem bewirkt eine Umdrehung der Abtriebswelle 29 des Elektromotors 15 nur eine dreizehntel Umdrehung des Planetenrades 51 in Bezug auf den Elektromotor 15, so daß die Belastung des Elektromotors ebenfalls minimiert werden kann.The structure of the planetary gear is shown in FIG. 5. The internal gear 52 in the holding body 43 has fourteen teeth, while the planet gear 51 has thirteen teeth. At the point opposite the point of engagement, the tip circle of the planet gear touches 51 approximately the tip circle of the internally toothed gear 52. On this About half of all teeth are always in mesh, which reduces the tooth flank load. Therefore, the planetary gear can be made very compact. It also causes one revolution of the output shaft 29 of the electric motor 15 is only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load on the Electric motor can also be minimized.

Die vorliegende Erfindung ermöglicht es, die Steuerzeiten der Ventile einer Brennkraftmaschine in einfacher Weise und sicher zu verändern. Besonders vorteilhaft ist, daß auch beliebige Zwischenstellungen angesteuert werden können.The present invention makes it possible to control the valve timing of an internal combustion engine easy and safe to change. It is particularly advantageous that any Intermediate positions can be controlled.

Claims (12)

Vorrichtung zur Verstellung der Nockenwelle (1) einer Brennkraftmaschine mit innerer Verbrennung, mit einem Verstellmechanismus, der durch einen fest mit der Nockenwelle (1) oder mit einem Antriebsrad (6, 36) der Nockenwelle (1) fest verbundenen Elektromotor (15) betätigt wird, der über Schleifkontakte mit Strom versorgt wird, dadurch gekennzeichnet, daß der Verstellmechanismus ein Planetengetriebe umfaßt.Device for adjusting the camshaft (1) of an internal combustion engine, with an adjusting mechanism which is actuated by an electric motor (15) which is firmly connected to the camshaft (1) or to a drive wheel (6, 36) of the camshaft (1) , which is supplied with power via sliding contacts, characterized in that the adjusting mechanism comprises a planetary gear. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Planetengetriebe ein großes Untersetzungsverhältnis aufweist, das vorzugsweise größer als 1:8 und besonders vorzugsweise größer als 1:12 ist.Apparatus according to claim 1, characterized in that the planetary gear has a large reduction ratio, which is preferably greater than 1: 8 and particularly is preferably greater than 1:12. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Planetengetriebe in Bezug auf die Verstellung der Nockenwelle (1) durch das Antriebsrad (6, 36) selbsthemmend ist.Device according to claim 1 or 2, characterized in that the planetary gear in relation to the adjustment of the camshaft (1) by the drive wheel (6, 36) is self-locking. Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Elektromotor (15) und ein innenverzahntes Zahnrad (35) des Planetengetriebes fest mit dem Antriebsrad (36) verbunden sind.Device according to one of claims 1 to 3, characterized in that the electric motor (15) and an internally toothed gear (35) of the planetary gear with the Drive wheel (36) are connected. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß der Planetenträger (37) des Planetengetriebes fest mit der Nockenwelle (1) verbunden ist.Apparatus according to claim 4, characterized in that the planet carrier (37) of the Planetary gear is firmly connected to the camshaft (1). Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Planetengetriebe nur aus einem innenverzahnten Zahnrad (52) und einem Planetenträger (48) mit einem einzigen darauf gelagerten Planetenrad (51) besteht.Device according to one of claims 1 to 3, characterized in that the planetary gear only from an internally toothed gear (52) and a planet carrier (48) with a single planet gear (51) mounted thereon. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die Zähnezahl des Planetenrades (51) nur geringfügig kleiner ist als die Zähnezahl des innenverzahnten Zahnrades (52), und zwar vorzugsweise um eins.Apparatus according to claim 6, characterized in that the number of teeth on the planet gear (51) is only slightly smaller than the number of teeth on the internally toothed gear (52), preferably by one. Vorrichtung nach einem der Ansprüche 6 oder 7, dadurch gekennzeichnet, daß der Elektromotor (15) fest mit der Nockenwelle (1) verbunden ist und daß das Planetenrad (51) über eine Gleichlaufkupplung (54) mit dem Antriebsrad (6) verbunden ist.Device according to one of claims 6 or 7, characterized in that the electric motor (15) is firmly connected to the camshaft (1) and that the planet gear (51) is connected to the drive wheel (6) via a synchronous clutch (54). Vorrichtung nach einem der Ansprüche 6 oder 7, dadurch gekennzeichnet, daß der Elektromotor (15) fest mit dem Antriebsrad (6) verbunden ist und daß das Planetenrad (51) über eine Gleichlaufkupplung (54) mit der Nockenwelle (1) verbunden ist.Device according to one of claims 6 or 7, characterized in that the electric motor (15) is firmly connected to the drive gear (6) and that the planet gear (51) is connected to the camshaft (1) via a synchronous clutch (54). Vorrichtung nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, daß der Planetenträger (48) als Teil der Abtriebswelle (29) des Elektromotors (15) ausgebildet ist, die einen desaxierten Abschnitt (48) aufweist, auf dem das Planetenrad (51) gelagert ist.Device according to one of claims 6 to 9, characterized in that the planet carrier (48) as part of the output shaft (29) of the electric motor (15), which has a desaxed section (48) on which the planet gear (51) is mounted. Vorrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß der Elektromotor (15) als Schrittmotor ausgebildet ist. Device according to one of claims 1 to 10, characterized in that the electric motor (15) is designed as a stepper motor. Brennkraftmaschine mit innerer Verbrennung, dadurch gekennzeichnet, daß sie eine Vorrichtung nach einem der Ansprüche 1 bis 11 aufweist.Internal combustion engine, characterized in that it has a Device according to one of claims 1 to 11.
EP98890262A 1997-09-19 1998-09-10 Device for variable camshaft timing in an internal combustion engine Expired - Lifetime EP0903471B1 (en)

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AT158697 1997-09-19
AT1586/97 1997-09-19
AT0158697A AT407282B (en) 1997-09-19 1997-09-19 DEVICE FOR ADJUSTING A CAMSHAFT
AT135898 1998-08-06
AT135898 1998-08-06
AT1358/98 1998-08-06

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GB2221513A (en) 1988-08-05 1990-02-07 Ford Motor Co Variable phase drive mechanism
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DE4040486A1 (en) * 1990-06-22 1992-01-02 Schrick Gmbh Dr Camshaft adjuster - has opposing meshing gear tooth systems for controlled rotation of camshaft w.r.t. camshaft timing gear
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Cited By (18)

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Publication number Priority date Publication date Assignee Title
EP1039101A2 (en) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Camshaft phaser for an internal combustion engine
EP1039100A2 (en) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Camshaft phaser for an internal combustion engine
US6257186B1 (en) 1999-03-23 2001-07-10 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
AT410825B (en) * 1999-03-23 2003-08-25 Tcg Unitech Ag Adjusting device for camshaft for IC engines has electric motor with disc armature rotor for high torque
AT409786B (en) * 1999-03-23 2002-11-25 Tcg Unitech Ag Arrangement for displacing an internal combustion engine camshaft has electric motor housing mounting elements fed into drive wheel via apertures that limit camshaft adjustment range
US6302073B1 (en) 1999-03-23 2001-10-16 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6328006B1 (en) 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
EP1052379A2 (en) 1999-05-12 2000-11-15 TCG UNITECH Aktiengesellschaft Camshaft phaser for an internal combustion engine
EP1136658A3 (en) * 2000-03-09 2001-12-19 TCG UNITECH Aktiengesellschaft Camshaft phasing device
AT408897B (en) * 2000-03-09 2002-03-25 Tcg Unitech Ag DEVICE FOR ADJUSTING A CAMSHAFT
AT409030B (en) * 2000-03-09 2002-05-27 Tcg Unitech Ag DEVICE FOR ADJUSTING A CAMSHAFT
EP1136657A2 (en) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Camshaft phasing device
US6543399B2 (en) 2000-03-09 2003-04-08 Tcg Unitech Aktiengesellschaft Apparatus for adjusting a camshaft
EP1136658A2 (en) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Camshaft phasing device
DE102008006199A1 (en) 2008-01-26 2009-07-30 Schaeffler Kg Actuating drive i.e. phase adjuster, for e.g. adjusting element at camshaft of internal combustion engine, has power transformer with primary coil and secondary coil, whose number of turns is greater than number of turns of primary coil
DE102008006199B4 (en) 2008-01-26 2022-04-21 Schaeffler Technologies AG & Co. KG Actuating drive for an adjustment element
EP2530260A1 (en) * 2011-06-03 2012-12-05 Magna Powertrain AG & Co. KG Coupling shaft, actuator, cam shaft adjustment drive and cam shaft adjuster
WO2013075933A1 (en) * 2011-11-24 2013-05-30 Magna Powertrain Ag & Co. Kg Adjustment drive having an oldham coupling

Also Published As

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US6138622A (en) 2000-10-31
EP0903471B1 (en) 2001-12-05
ATE210243T1 (en) 2001-12-15
DE59802310D1 (en) 2002-01-17
ES2167864T3 (en) 2002-05-16

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