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EP0903471B1 - 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
EP0903471B1
EP0903471B1 EP98890262A EP98890262A EP0903471B1 EP 0903471 B1 EP0903471 B1 EP 0903471B1 EP 98890262 A EP98890262 A EP 98890262A EP 98890262 A EP98890262 A EP 98890262A EP 0903471 B1 EP0903471 B1 EP 0903471B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
electric motor
gear
planetary gear
planet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98890262A
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German (de)
French (fr)
Other versions
EP0903471A1 (en
Inventor
Siegfried Ing. Heer
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.)
TCG Unitech AG
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TCG Unitech AG
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Filing date
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
Application granted granted Critical
Publication of EP0903471B1 publication Critical patent/EP0903471B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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 an internal combustion engine with an adjustment mechanism, the one with the camshaft or with the drive wheel firmly connected electric motor is operated.
  • the camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.
  • DE 41 10 088 C and DE 39 29 619 A are adjusting devices known in which between one connected to the camshaft Component and a component connected to the drive wheel Adjustment element is provided, which has two helical gears that with corresponding toothing of the camshaft or the drive wheel in engagement stand.
  • An axial displacement of this adjustment element can Rotation of the camshaft relative to the drive wheel can be caused.
  • a The possibility of 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 necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort.
  • the oil consumption is due to the actuation of the piston relatively large, which is a load on the engine by a corresponding Oil pump represents.
  • switched the camshaft only between two end positions become.
  • an electrical adjustment device is known from DE 41 01 676A, in which an electric motor is provided, the adjusting element via a threaded spindle shifts.
  • an axial thrust bearing can be provided, which the relative movement between the torsion-resistant and the rotating component.
  • This thrust bearing is with the known solution practically during the entire engine operation because it acts between the drive wheel and the camshaft Torsional moments always exert a force acting on the adjusting element in the axial direction is exercised.
  • This thrust bearing is therefore a critical component that limits the life of the engine.
  • an adjusting mechanism is known from GB 2 221 513 A, 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 the an adjusting element is guided, which with a Camshaft and via a second group of levers with the drive wheel in Connection is established. By operating the electric motor this way rotation of the camshaft relative to the drive wheel can be brought about.
  • Such a device is very complex and requires a relatively large one Installation space.
  • DE 36 07 256 A shows an adjustment device in which the adjustment the camshaft is done by a stepper motor, which is fixed to the drive wheel connected is.
  • this stepper motor has to absorb all the torque, that is required to drive the camshaft.
  • Such a stepper motor decides due to the required size and power consumption the practical use.
  • the US 5,293,845 A shows an adjusting mechanism for a camshaft, the has a planetary gear.
  • a fixed electric motor causes one Phase shift of the camshaft.
  • the disadvantage is that the power transmission for driving the camshaft via the rotating gear wheels of the Planetary gear takes place, so that the limited efficiency of the planetary gear leads to the corresponding losses. It also shifts at one Adjustment of the axis of the drive wheel, which is due to complex clamping mechanisms is to be balanced.
  • EP 0 234 853 A shows a device for adjusting a camshaft which is adjusted via a harmonic drive gear.
  • a transmission consists of an internally toothed gear and an elliptical deformable Gear that meshes with the internally toothed gear. The resilience and life of such a transmission has certain limits that it do not appear suitable for all applications.
  • the object of the present invention is to provide a device in which the disadvantages described above can be avoided, and in particular it enables quick and reliable adjustment in a simple manner to enable the camshaft. in particular, the device should have little installation space claim, so that an independent adjustment of two Camshafts with a small axial distance is possible.
  • the adjustment mechanism Planetary gear includes.
  • a planetary gear Adjustment elements that move in the axial direction can be avoided.
  • the mechanical structure can be simplified and a small size can be achieved.
  • Another advantage of the invention is that it is relative is simple to ensure a secure oil seal, so the electric motor runs in the dry.
  • the planetary gear preferably has a large reduction ratio, which is preferably greater than 1: 8 and particularly preferably greater than 1:12. Such a reduction ratio may result in self-locking be achieved or at least approximately achieved. On in this way, the electric motor during normal operation of the internal combustion engine, where there is no adjustment, no or only minimal load. This increases the service life and reduces the amount of energy required.
  • the electric motor and an internally toothed gear of the planetary gear are firmly connected to the drive wheel.
  • the planet carrier is preferred of the planetary gear firmly connected to the camshaft.
  • the output shaft the electric motor stands in this case with the sun gear of the planetary gear in connection. This allows a relatively large 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 thereon.
  • a sun gear is not provided in such a planetary gear.
  • the number of teeth of the planetary gear is preferably only slightly smaller than the number of teeth of the internally toothed gear, 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 meshing simultaneously, so that one very favorable situation with regard to the load is given.
  • Such The device can therefore be made extremely compact, so that even close distance two camshafts can be adjusted independently can.
  • a large reduction ratio is achieved in this way, what is favorable in view of the required size of the electric motor is.
  • the electric motor is firmly connected to the camshaft is and that the planet gear via a synchronous clutch with the drive gear connected is.
  • the synchronous clutch for example as an Oldham clutch is formed, the axial offset of the planet gear and Drive wheel off.
  • the electric motor is fixed to the drive wheel is connected and that the planet gear via a synchronous clutch is connected to the camshaft.
  • the planet carrier as an output shaft of the electric motor is formed, which has a desaxed section where the planet gear is mounted.
  • Precise 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 Combustion having a device as described above.
  • FIG. 1 a first embodiment variant the present invention in longitudinal section
  • Fig. 2 another Embodiment variant of the present invention in longitudinal section
  • Fig. 3 shows the variant of Fig. 2 in a section along line III - III in Fig. 2, wherein to increase clarity, individual components are not shown
  • the Fig. 4 is an exploded view of the embodiment of Figures 2 and 3
  • 5 shows a detail of this embodiment variant.
  • a first embodiment variant of the present invention is shown in FIG. 1.
  • a bracket 30 is rotatable on a camshaft 1, but axially fixed immovably.
  • On this bracket 30 is on the outer circumference Toothed 36 is provided, which is used to hold a toothed belt, which Drives camshaft 1 and thus represents the drive wheel.
  • the bracket 30 further carries a plate 31 on which an electric motor 15 is fixedly 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 over planet gears 33, 34 with a ring gear, i.e. an internally toothed gear 35 which is integrally formed in the bracket 30.
  • a planet carrier 37, the planet gears 33, 34 rotatably carries, is fixedly connected to the camshaft 1. If the electric motor 15 is not controlled, the pinion 32 is related to the Motor 15 silent, and thus pinion 32 and planet carrier 37 rotate with the Speed of the drive wheel 36, which also causes the camshaft 1 at this speed rotates. By controlling the electric motor 15, a relative movement can of the planet carrier 37 can be effected in relation to the drive wheel 36. The relatively large translation by the planetary gear ensures that the correspondingly large torques for adjusting the camshaft 1 a relatively underpowered electric motor 15 can be made available can. The sealing of the system against the oil space in the area of Camshaft 1 takes place via radial shaft sealing rings 38 and 39. A screw 40 is used to attach the planet carrier to camshaft 1.
  • the planetary gear consisting of the gears 32, 33, 34 and 35, be carried out in a known manner without play.
  • these gears 32 to 35 can be made of high-strength Be made of plastic.
  • the camshaft 1 has its End of a flange 2.
  • a drive wheel is on the flange 2 via a slide bearing 42 6 for the camshaft 1, which has a toothing 6a on its circumference Includes a drive chain, not shown.
  • Via threaded bolts 8 a holding body 43 is connected to the flange 2.
  • the threaded bolts 8 kick thereby through openings 10 in the drive wheel 6, which are arcuate Elongated holes are formed. This is the angular range of the adjustment the camshaft 1 defined.
  • a shaft nut 44 is on the holding body 43 attached, which carries an electric motor 15 via screws 45. As with the previous one Design variant is the electric motor 15 via slip rings 19 and Sliding contacts 41 supplied with power.
  • the output shaft 29 of the electric motor 15 is on the holding body via roller bearings 46 and 47 43 and mounted on the shaft nut 44 and has on the motor 15 distal end a desaxed section 48.
  • the bearings 46 and 47 are held in the axial direction by locking rings 49.
  • On the daxed Section is mounted on a needle bearing 50, a planet gear 51, which with a internally toothed gear 52 is engaged, which is integral with the holding body 43 is formed.
  • An axial plain bearing bush 53 secures the planet gear 51 in Axial direction.
  • the planet gear 51 is a so-called Oldham clutch 54 Constant velocity joint represents, with the drive wheel 6 in rotary connection.
  • the Oldham coupling 54 has an engagement part 55 which is connected to the planet gear 51 a slide guide 56 communicates which limits movement of the Engagement part 55 relative to the planet gear 51 in the plane of FIG. 2 allows.
  • the engagement part 55 stands with an adapter 58 of the drive wheel 6 via a further sliding guide 57 in connection, which has a limited movement of the engaging part 55 with respect to the drive wheel 6 in the plane of FIG. 3 enables. In this way it is possible to get the drive torque from the drive wheel 6 to be transferred to the planet gear 51, the eccentricity s being overcome becomes. Screws 59 connect the adapter 58 to the sprocket 6 and simultaneously secure the engaging part 55.
  • a housing 60 with a radial shaft seal 61 opposite the holding part 43 is sealed, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, like the electric motor 15.
  • the structure of the planetary gear is shown in FIG. 5.
  • the internally toothed 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 51 approximately touches the tip circle of the internal gear 52. In this way, about half of all Teeth always engaged, which reduces the tooth flank load. Therefore, it can Planetary gears are designed to be very compact. It also causes one revolution the output shaft 29 of the electric motor 15 only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load of the electric motor can also be minimized.
  • the present invention makes it possible to control the valve timing Change internal combustion engine in a simple and safe way. Particularly advantageous is that any intermediate positions can also be controlled.

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

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 an internal combustion engine with an adjustment mechanism, the one with the camshaft or with the drive wheel firmly connected electric motor 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.In order to optimize consumption and consumption in various areas of the engine map To achieve exhaust gas values, it is necessary to depend on the valve timing to change various operating parameters. Such a change in Timing can be elegantly twisted in by turning the camshaft Regarding the wheel driving them. The camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.

Aus der DE 41 10 088 C und aus der DE 39 29 619 A 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.DE 41 10 088 C and DE 39 29 619 A are adjusting devices known in which between one connected to the camshaft Component and a component connected to the drive wheel Adjustment element is provided, which has two helical gears that with corresponding toothing of the camshaft or the drive wheel in engagement stand. An axial displacement of this adjustment element can Rotation of the camshaft relative to the drive wheel can be caused. A The possibility of 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 necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort. In addition, the oil consumption is due to the actuation of the piston relatively large, which is a load on the engine by a corresponding Oil pump represents. In addition, in such a known Device switched the camshaft only between two end positions become.

Weiters ist aus der DE 41 01 676A 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 Motor-betriebs 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 676A, in which an electric motor is provided, the adjusting element via a threaded spindle shifts. However, since the adjustment element essentially with Camshaft speed must rotate between the electric motor and the adjusting element an axial thrust bearing can be provided, which the relative movement between the torsion-resistant and the rotating component. This thrust bearing is with the known solution practically during the entire engine operation because it acts between the drive wheel and the camshaft Torsional moments always exert a force acting on the adjusting element in the axial direction is exercised. This thrust bearing is therefore a critical component that limits the life of the engine.

Weiters ist aus der GB 2 221 513 A 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, an adjusting mechanism is known from GB 2 221 513 A, 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 the an adjusting element is guided, which with a Camshaft and via a second group of levers with the drive wheel in Connection is established. By operating the electric motor this way rotation of the camshaft relative to the drive wheel can be brought about. Such a device is very complex and requires a relatively large one Installation space.

Ferner zeigt die DE 36 07 256 A 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 36 07 256 A shows an adjustment device in which the adjustment the camshaft is done by a stepper motor, which is fixed to the drive wheel connected is. However, this stepper motor has to absorb all the torque, that is required to drive the camshaft. Such a stepper motor decides due to the required size and power consumption the practical use.

Die US 5,293,845 A 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 5,293,845 A shows an adjusting mechanism for a camshaft, the has a planetary gear. A fixed electric motor causes one Phase shift of the camshaft. The disadvantage, however, is that the power transmission for driving the camshaft via the rotating gear wheels of the Planetary gear takes place, so that the limited efficiency of the planetary gear leads to the corresponding losses. It also shifts at one Adjustment of the axis of the drive wheel, which is due to complex clamping mechanisms is to be balanced.

Die EP 0 234 853 A zeigt eine Vorrichtung zum Verstellen einer Nockenwelle, bei der die Verstellung über ein Harmonic-Drive-Getriebe erfolgt. Ein solches Getriebe besteht aus einem innenverzahnten Zahnrad und einem eliptischen verformbaren Zahnrad, das in das innenverzahnte Zahnrad eingreift. Die Belastbarkeit und Lebensdauer eines solchen Getriebes besitzt gewisse Grenzen, die es nicht für alle Anwendungen geeignet erscheinen lassen.EP 0 234 853 A shows a device for adjusting a camshaft which is adjusted via a harmonic drive gear. Such a transmission consists of an internally toothed gear and an elliptical deformable Gear that meshes with the internally toothed gear. The resilience and life of such a transmission has certain limits that it do not appear suitable for all applications.

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 disadvantages described above can be avoided, and in particular it enables quick and reliable adjustment in a simple manner to enable the camshaft. in particular, the device should have little installation space claim, so that an independent adjustment of two Camshafts with a small axial distance is possible.

Diese Aufgaben werden erfindungsgemäß durch die Ausführungsvarianten mit den Merkmalen der Ansprüche 1 bzw. 2 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.These tasks are achieved according to the invention by the design variants the features of claims 1 and 2 solved that the adjustment mechanism Planetary gear includes. By using a planetary gear Adjustment elements that move in the axial direction can be avoided. Thereby the mechanical structure can be simplified and a small size can be achieved. Another advantage of the invention is that it is relative is simple to ensure a secure oil seal, so the electric motor runs in the dry. In order to also ensure emergency operation in the event of adjustment failure to be able, it is generally provided that by the drive torque the camshaft reaches 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 is preferably greater than 1: 8 and particularly preferably greater than 1:12. Such a reduction ratio may result in self-locking be achieved or at least approximately achieved. On in this way, the electric motor during normal operation of the internal combustion engine, where there is no adjustment, no or only minimal load. 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 variant of the invention, that the electric motor and an internally toothed gear of the planetary gear are firmly connected to the drive wheel. The planet carrier is preferred of the planetary gear firmly connected to the camshaft. The output shaft the electric motor stands in this case with the sun gear of the planetary gear in connection. This allows a relatively large 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 preferred embodiment variant of the invention provided that the planetary gear consists only of an internally toothed gear and a planet carrier with a single planet gear mounted thereon. A sun gear is not provided in such a planetary gear. The number of teeth of the planetary gear is preferably only slightly smaller than the number of teeth of the internally toothed gear, 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 meshing simultaneously, so that one very favorable situation with regard to the load is given. Such The device can therefore be made extremely compact, so that even close distance two camshafts can be adjusted independently can. In addition, a large reduction ratio is achieved in this way, what is favorable in view of the required size of the electric motor is.

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 is and that the planet gear via a synchronous clutch with the drive gear connected is. The synchronous clutch, for example as an Oldham clutch is formed, the axial offset of the planet gear and Drive wheel off.

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 fixed to the drive wheel is connected and that the planet gear via a synchronous clutch is connected to the camshaft.

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 as an output shaft of the electric motor is formed, which has a desaxed section where the planet gear is mounted.

Eine exakte Steuerung des Verstellwinkels kann dadurch erreicht werden, dass der Elektromotor als Schrittmotor ausgebildet ist.Precise 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 Combustion having 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 the present invention in longitudinal section Fig. 2 another Embodiment variant of the present invention in longitudinal section; Fig. 3 shows the variant of Fig. 2 in a section along line III - III in Fig. 2, wherein to increase clarity, individual components are not shown; the Fig. 4 is an exploded view of the embodiment of Figures 2 and 3; and 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. A bracket 30 is rotatable on a camshaft 1, but axially fixed immovably. On this bracket 30 is on the outer circumference Toothed 36 is provided, which is used to hold a toothed belt, which Drives camshaft 1 and thus represents the drive wheel. The bracket 30 further carries a plate 31 on which an electric motor 15 is fixedly 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 over planet gears 33, 34 with a ring gear, i.e. an internally toothed gear 35 which is integrally formed in the bracket 30. A planet carrier 37, the planet gears 33, 34 rotatably carries, is fixedly connected to the camshaft 1. If the electric motor 15 is not controlled, the pinion 32 is related to the Motor 15 silent, and thus pinion 32 and planet carrier 37 rotate with the Speed of the drive wheel 36, which also causes the camshaft 1 at this speed rotates. By controlling the electric motor 15, a relative movement can of the planet carrier 37 can be effected in relation to the drive wheel 36. The relatively large translation by the planetary gear ensures that the correspondingly large torques for adjusting the camshaft 1 a relatively underpowered electric motor 15 can be made available can. The sealing of the system against the oil space in the area of Camshaft 1 takes place via radial shaft sealing rings 38 and 39. A screw 40 is used to attach the planet carrier to 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, can the planetary gear, consisting of the gears 32, 33, 34 and 35, be carried out in a known manner without play. To the noise level To minimize as much as possible, these gears 32 to 35 can be made of high-strength Be made of 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.2 to 5, the camshaft 1 has its End of a flange 2. A drive wheel is on the flange 2 via a slide bearing 42 6 for the camshaft 1, which has a toothing 6a on its circumference Includes a drive chain, not shown. Via threaded bolts 8 a holding body 43 is connected to the flange 2. The threaded bolts 8 kick thereby through openings 10 in the drive wheel 6, which are arcuate Elongated holes are formed. This is the angular range of the adjustment the camshaft 1 defined. A shaft nut 44 is on the holding body 43 attached, which carries an electric motor 15 via screws 45. As with the previous one Design variant is the electric motor 15 via slip rings 19 and Sliding contacts 41 supplied with power.

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 via roller bearings 46 and 47 43 and mounted on the shaft nut 44 and has on the motor 15 distal end a desaxed section 48. The bearings 46 and 47 are held in the axial direction by locking rings 49. On the daxed Section is mounted on a needle bearing 50, a planet gear 51, which with a internally toothed gear 52 is engaged, which is integral with the holding body 43 is formed. An axial plain bearing bush 53 secures the planet gear 51 in 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 s überwunden wird. Schrauben 59 verbinden den Adapter 58 mit dem Kettenrad 6 und sichern gleichzeitig den Eingriffsteil 55.The planet gear 51 is a so-called Oldham clutch 54 Constant velocity joint represents, with the drive wheel 6 in rotary connection. The Oldham coupling 54 has an engagement part 55 which is connected to the planet gear 51 a slide guide 56 communicates which limits movement of the Engagement part 55 relative to the planet gear 51 in the plane of FIG. 2 allows. On the other hand, the engagement part 55 stands with an adapter 58 of the drive wheel 6 via a further sliding guide 57 in connection, which has a limited movement of the engaging part 55 with respect to the drive wheel 6 in the plane of FIG. 3 enables. In this way it is possible to get the drive torque from the drive wheel 6 to be transferred to the planet gear 51, the eccentricity s being overcome becomes. Screws 59 connect the adapter 58 to the sprocket 6 and simultaneously secure the engaging 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 with a radial shaft seal 61 opposite the holding part 43 is sealed, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, like 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 internally toothed 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 intervention The tip circle of the planet gear 51 approximately touches the tip circle of the internal gear 52. In this way, about half of all Teeth always engaged, which reduces the tooth flank load. Therefore, it can Planetary gears are designed to be very compact. It also causes one revolution the output shaft 29 of the electric motor 15 only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load of 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 Change internal combustion engine in a simple and safe way. Particularly advantageous is that any intermediate positions can also be controlled.

Claims (11)

  1. Device for adjusting the phase angle of a camshaft (1) of an internal combustion engine, comprising an adjusting mechanism that is operated by an electric motor (15), which electric motor (15) is rigidly connected to the camshaft (1) and supplied with power via sliding contacts, characterized in that the adjusting mechanism comprises a planetary gear set and that the planet gear (51) is connected to a drive gear (6) for the camshaft (1) by means of a synchronizing coupling (54).
  2. Device for adjusting the phase angle of a camshaft (1) of an internal combustion engine, comprising an adjusting mechanism that is operated by an electric motor (15), which electric motor (15) is rigidly connected to a drive gear (6) for a camshaft (1) and supplied with power via slip contacts, characterized in that the adjusting mechanism comprises a planetary gear set and that the planet gear (51) is connected to the the camshaft (1) by means of a synchronizing coupling (54).
  3. Device according to claim 1 or 2, characterized in that the planetary gear set has a large reduction ratio, i.e., preferably greater than 1:8, and even more preferably, greater than 1:12.
  4. Device according to any of claims 1 to 3, characterized in that the planetary gear set is self-locking as regards adjustment of the camshaft (1) by means of the drive gear (6, 36).
  5. Device according to any of claims 1 to 4, characterized in that the electric motor (15) and an internally toothed gear (35) of the planetary gear set are rigidly connected to the drive gear (36).
  6. Device according to claim 5, characterized in that the planet carrier (37) of the planetary gear set is rigidly connected to the camshaft (1).
  7. Device according to any of claims 1 to 4, characterized in that the planetary gear set comprises only an internally toothed gear (52) and a planet carrier (48) supporting a single planet gear (51).
  8. Device according to claim 7, characterized in that the number of teeth of the planet gear (51) is only slightly - smaller than the number of teeth of the internally toothed gear (52), i.e., preferably by one.
  9. Device according to any of claims 7 or 8, characterized in that the planet carrier (48) is configured as part of the output shaft (29) of the electric motor (15), which output shaft (29) is provided with an eccentric piece (48) on which the planet gear 51 is supported.
  10. Device as claimed according to any of claims 1 to 9, characterized in that the electric motor (15) is configured as a stepping motor.
  11. Internal combustion engine, characterized in that it is provided with a device as claimed in any of claims 1 to 10.
EP98890262A 1997-09-19 1998-09-10 Device for variable camshaft timing in an internal combustion engine Expired - Lifetime EP0903471B1 (en)

Applications Claiming Priority (6)

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

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AT (1) ATE210243T1 (en)
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ES2167864T3 (en) 2002-05-16
ATE210243T1 (en) 2001-12-15
US6138622A (en) 2000-10-31
DE59802310D1 (en) 2002-01-17

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