EP2603675B1 - Camshaft adjusting apparatus - Google Patents

Camshaft adjusting apparatus Download PDF

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Publication number
EP2603675B1
EP2603675B1 EP11735792.1A EP11735792A EP2603675B1 EP 2603675 B1 EP2603675 B1 EP 2603675B1 EP 11735792 A EP11735792 A EP 11735792A EP 2603675 B1 EP2603675 B1 EP 2603675B1
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EP
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Prior art keywords
eccentric
central axis
adjustment apparatus
camshaft
gear
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EP11735792.1A
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German (de)
French (fr)
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EP2603675A1 (en
Inventor
Michael Schober
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Magna Powertrain GmbH and Co KG
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Magna Powertrain GmbH and Co KG
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Publication of EP2603675A1 publication Critical patent/EP2603675A1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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

Definitions

  • the invention relates to an adjusting device for Relatiwer ein a camshaft with respect to a camshaft coaxially driving drive wheel, wherein the drive wheel and the camshaft are arranged coaxially with respect to a central axis of the adjusting device.
  • the crankshaft is coupled via a chain drive, a toothed belt drive or a toothed drive with a drive wheel which drives the camshaft substantially synchronously with the crankshaft.
  • the valve opening times of the internal combustion engine are controlled via the camshaft.
  • a control gear can be effective between the drive wheel and the camshaft, which can be driven by means of an electric motor to adjust the camshaft relative to the drive wheel.
  • an electric motor allows a particularly accurate control.
  • the actuating mechanism in such an arrangement forms a summing gear in which the drive wheel is associated with a first input, an output element of the electric motor (eg a motor pinion) is associated with a second input and the camshaft or camshaft section (eg a camshaft flange) is associated with an output of the summing gear is.
  • the drive wheel, the Output member of the electric motor and the camshaft are rotatable coaxially with each other, so that the entire unit of drive wheel, electric motor, control gear and camshaft about a common axis, the so-called central axis, can rotate.
  • the control gear In order to adjust the camshaft relative to the drive wheel, comparatively high torques must be applied. For this function can be met by a small-sized, fast-running electric motor, the control gear must cause a high ratio of the speed of the electric motor to slow (based on a fixed drive wheel).
  • the actuating gear having an internally toothed gear and an externally toothed gear meshing therewith, wherein the internally toothed gear is rotatable about said central axis and the externally toothed gear is eccentric with respect to the central axis and is driven in this eccentric arrangement to a circular movement about the central axis ,
  • the said circular movement is here - as the externally toothed gear rolls on the internally toothed gear - a relatively slow rotation of the externally toothed gear (relative to the internally toothed gear) superimposed.
  • a problem with such a control gear is, however, that the meshing with the internal gear external gear is arranged eccentrically with respect to the central axis of the adjusting device.
  • the circular motion of the externally toothed gear can not readily be applied to an input element or output element of the adjusting gear (eg on the camshaft) transmitted, which - as explained above - all should be arranged coaxially to the central axis.
  • An object of the invention is to provide a camshaft adjusting device of the type mentioned, in which the actuating mechanism causes a high gear ratio with a compact design and high efficiency in the slow.
  • an adjusting device with the features of claim 1, and in particular in that the externally toothed gear is eccentrically mounted on at least two eccentric shafts, each eccentric shaft is drivable for rotational movement about a respective eccentric axis, wherein the eccentric axes eccentric with respect to the central axis arranged and rotatable about the central axis.
  • At least two eccentric axes are provided, which are arranged eccentrically with respect to the genanten central axis of the adjusting device and in particular are arranged parallel to each other.
  • the arrangement of the fixed relative to each other eccentric axes can be rotated about the central axis, i. the arrangement of at least two eccentric axes is rotatable coaxially to the drive wheel, the electric motor and the camshaft, wherein the respective position of the eccentric axes is defined for example by a common carrier device.
  • Each eccentric axis is assigned a respective eccentric shaft.
  • Each eccentric shaft includes an eccentric portion (ie, a cam) and is drivable for rotational movement about the respective eccentric axis.
  • Said external gear which with said internal toothed Gear is engaged, is mounted on the at least two eccentric shafts, so that by the rotational movement of the eccentric shafts about the respective eccentric axis, the externally toothed gear can be driven to said (eccentric) circular motion about the central axis.
  • the required eccentricity of the externally toothed gear can be represented by the respective eccentric portion of the eccentric shafts, wherein the eccentric shafts associated with the eccentric shafts can jointly perform a rotational movement coaxial with the central axis.
  • the eccentric shafts which are rotatable about the eccentrically arranged eccentric axes, thus make it possible for the eccentric circular movement (with superimposed rotation) of the externally toothed toothed wheel to be attributed to a rotational movement about the central axis of the adjusting device, namely in the form of a rotation of said eccentric axes about the central axis , Therefore, the two inputs and the output of the adjusting gear can all be arranged coaxially to the central axis.
  • the externally toothed gear is mounted by means of a respective rolling bearing on the eccentric shafts.
  • the eccentric circular movement of the externally toothed gear and the torque transmission caused thereby can be represented with a particularly good efficiency.
  • the externally toothed gear can be supported by means of a respective sliding bearing on the eccentric shafts.
  • each eccentric shaft is rotatably mounted on a respective bearing journal - the so-called eccentric pin -, wherein the eccentric pins define said eccentric axes and are fastened to a common carrier device.
  • the eccentric shafts are designed in particular as hollow shafts, which are mounted on the inside of the eccentric pin.
  • the eccentric shafts may, for example, engage directly in the manner of a pin in a common carrier device and be rotatably mounted on the latter on the outside.
  • the eccentric shafts are in turn mounted on the eccentric pin by means of a respective further rolling bearing.
  • the efficiency of the adjusting gear is further increased, since thus for the movement of the externally toothed gear a rolling bearing can be provided.
  • the internally toothed gear is rotatably connected to the drive wheel and the arrangement of the plurality of eccentric axes (in particular the arrangement of the plurality of eccentric pins) is rotatably connected to the camshaft.
  • the internal gear forms a Input and the arrangement of the multiple eccentric axes forms the output of the actuating gear.
  • said eccentric shafts are drivable by means of the electric motor to a rotational movement about the respective eccentric axis.
  • the eccentric shafts carrying the externally toothed gear are assigned to an input of the adjusting gear.
  • the eccentric shafts are drivable to a mutually synchronous rotational movement about the respective eccentric axis in order to effect the desired circular movement of the externally toothed gear.
  • each eccentric shaft with a respective coupling gear rotatably connected (in particular integrally formed).
  • the electric motor can drive a motor pinion, which is arranged coaxially to the central axis of the adjusting device and meshes with the coupling gears directly or via at least one common intermediate gear.
  • the eccentric bearing of the eccentric shafts can thus be attributed to a drive coaxial with the central axis.
  • the coupling gears and the intermediate gear (if present) in each position of the adjusting gear are arranged radially completely within the toothing of the externally toothed gear.
  • the coupling gears and possibly the intermediate gear are arranged completely within an imaginary to the central axis concentric cylinder jacket, wherein the cylinder shell is in each gear position completely within the teeth of the external gear, so that the tooth width of the external gear and also the tooth width of the internally toothed Gear can continue axially via the coupling gears and the intermediate gear.
  • the coupling gears or the intermediate gear can thus be arranged axially completely or partially within the externally toothed gear and the internally toothed gear. This shortens the axial length of the adjusting gear.
  • two, three or four eccentric shafts are provided, which are rotatably driven about a respective eccentric axis to drive the externally toothed gear, wherein the eccentric axes are preferably distributed in a uniform angular pitch about the central axis.
  • adjusting device is used to Relatiwer too a camshaft 11 of an internal combustion engine, not shown with respect to a camshaft 11 coaxially driving drive wheel 13, which is drivingly coupled for example via a chain drive, not shown, with a crankshaft of the internal combustion engine.
  • the drive wheel 13 and the camshaft 11 are arranged coaxially with respect to a central axis A of the adjusting device.
  • the drive wheel 13 is coupled to the camshaft 11 via a control gear 15, which can be driven by means of an electric motor 17 in order to adjust the phase position of the camshaft 11 relative to the drive wheel 13.
  • the adjusting gear 15 comprises an internally toothed gear 19 which is rotatably supported via a rolling bearing 21 on a support means 23 of the adjusting gear 15 coaxial with the central axis A.
  • the internal gear 19 is in engagement with an externally toothed gear 25.
  • the externally toothed gear 25 is arranged slightly eccentric with respect to the central axis A, and it is in this slightly eccentric arrangement to a circular motion about the central axis A drivable.
  • the number of teeth difference between the internal gear 19 and the external gear 25 is very small.
  • the externally toothed gear 25 has only one, two, three, four or five teeth less than the internally toothed Gear 19. Accordingly - as in particular from Fig. 3 it can be seen - the eccentricity of the externally toothed gear 25 with respect to the central axis A very low. In the upper area of Fig. 3 the externally toothed gear 25 is engaged with the internal gear 19, while in the lower region of Fig. 3 the externally toothed gear 25 is just out of engagement with the internal gear 19.
  • Fig. 3 shows that the externally toothed gear 25 is mounted on a respective rolling bearing 27 on two eccentric shafts 29.
  • Each of the two eccentric shafts 29 is in turn supported by a rolling bearing 31 on a respective eccentric pin 33 and rotatable about a respective eccentric axis B.
  • the two eccentric pins 33 and thus the two eccentric axes B are arranged eccentrically with respect to the central axis A.
  • the two eccentric pins 33 extend parallel to each other, and they are attached to the support means 23, so that the two eccentric pins 33 and thus the two eccentric axes B are rotatable about the central axis A in a fixed relative position.
  • the eccentricity of the respective outer periphery of the eccentric shafts 29 with respect to the respective eccentric axis B corresponds to the eccentricity of the externally toothed gear 25 with respect to the central axis A.
  • the eccentricity of the eccentric axes B with respect to the central axis A is significantly greater than the eccentricity of the externally toothed gear 25 with respect to the central axis A.
  • the central axis A and the eccentric axes B are within the pitch circle of the externally toothed gear 25th
  • each eccentric shaft 29 rotatably connected to a respective coupling gear 34, that is formed in one piece.
  • Fig. 2 It is shown that the two coupling gears 34 via a common intermediate gear 35 with a motor pinion 37 are engaged.
  • the intermediate gear 35 is rotatably mounted on a bearing journal 36, which is aligned parallel to the eccentric 33 and also secured to the support means 23 ( Fig. 5 ).
  • Screw 39 shown by the actuating gear 15, by means of the support means 23, fixedly connected to a flange 24 of the camshaft 11.
  • One of the screws 39 passes coaxially through the bearing pin 36 and screwed this bearing pin 36 via the support means 23 with the camshaft flange 24th
  • the motor pinion 37 is driven by the electric motor 17 via a motor shaft 41 ( Fig. 4 and 5 ).
  • the intermediate gear 35 is not mandatory; instead, the motor pinion 37 may also drive the two coupling gears 34 directly. In both cases, a synchronous drive of the two eccentric shafts 29 takes place through the motor pinion 37.
  • the actuating mechanism 15 forms a summing gear in order to be able to vary the phase position of the camshaft 11 relative to the drive wheel 13 by means of the electric motor 17.
  • the drive wheel 13 associated with internally toothed gear 19 forms a first input.
  • the motor gear 17 associated with the electric motor 17 forms a second input.
  • the eccentric 33 carrying and firmly connected to the camshaft flange 24 support means 23 forms an output of the adjusting gear 15th
  • the coupling gears 34 and the intermediate gear 35 may be made smaller such that they are disposed radially completely within the teeth of the external gear 25. In this way, a shortened axial length of the adjusting gear 15 can be achieved, namely when the externally toothed gear 25 and accordingly the internally toothed gear 19, the coupling gears 34 and the intermediate gear 35 axially partially or completely overlap.

Description

Die Erfindung betrifft eine Verstellvorrichtung zur Relatiwerstellung einer Nockenwelle bezüglich eines die Nockenwelle koaxial antreibenden Antriebsrads, wobei das Antriebsrad und die Nockenwelle bezüglich einer Zentralachse der Verstellvorrichtung koaxial angeordnet sind.The invention relates to an adjusting device for Relatiwerstellung a camshaft with respect to a camshaft coaxially driving drive wheel, wherein the drive wheel and the camshaft are arranged coaxially with respect to a central axis of the adjusting device.

Bei einer Verbrennungskraftmaschine eines Kraftfahrzeugs ist die Kurbelwelle über einen Kettentrieb, einen Zahnriementrieb oder einen Zahntrieb mit einem Antriebsrad gekoppelt, das die Nockenwelle im Wesentlichen synchron zu der Kurbelwelle antreibt. Ober die Nockenwelle werden die Ventilöffnungszeiten der Verbrennungskraftmaschine gesteuert. Durch eine Verstellvorrichtung der genannten Art kann die Phasenlage der Nockenwelle relativ zu dem Antriebsrad (und somit relativ zu der Kurbelwelle) gezielt verändert werden, um Einfluss auf die in der Verbrennungskraftmaschine stattfindenden Brennvorgänge zu nehmen. Hierfür kann zwischen dem Antriebsrad und der Nockenwelle ein Stellgetriebe wirksam sein, das mittels eines Elektromotors antreibbar ist, um die Nockenwelle relativ zu dem Antriebsrad zu verstellen. Die Verwendung eines Elektromotors gestattet eine besonders genaue Steuerung.In an internal combustion engine of a motor vehicle, the crankshaft is coupled via a chain drive, a toothed belt drive or a toothed drive with a drive wheel which drives the camshaft substantially synchronously with the crankshaft. The valve opening times of the internal combustion engine are controlled via the camshaft. By an adjusting device of the type mentioned, the phase position of the camshaft relative to the drive wheel (and thus relative to the crankshaft) can be selectively changed to influence the combustion processes taking place in the internal combustion engine. For this purpose, a control gear can be effective between the drive wheel and the camshaft, which can be driven by means of an electric motor to adjust the camshaft relative to the drive wheel. The use of an electric motor allows a particularly accurate control.

Das Stellgetriebe bildet in einer derartigen Anordnung ein Summiergetriebe, bei dem das Antriebsrad einem ersten Eingang zugeordnet ist, ein Ausgangselement des Elektromotors (z.B. ein Motorritzel) einem zweiten Eingang zugeordnet ist und die Nockenwelle oder ein Nockenwellenabschnitt (z.B. ein Nockenwellenflansch) einem Ausgang des Summiergetriebes zugeordnet ist. Hierbei ist es von Vorteil, wenn das Antriebsrad, das Ausgangselement des Elektromotors und die Nockenwelle koaxial zueinander drehbar sind, damit die gesamte Einheit aus Antriebsrad, Elektromotor, Stellgetriebe und Nockenwelle um eine gemeinsame Achse, die so genannte Zentralachse, rotieren kann.The actuating mechanism in such an arrangement forms a summing gear in which the drive wheel is associated with a first input, an output element of the electric motor (eg a motor pinion) is associated with a second input and the camshaft or camshaft section (eg a camshaft flange) is associated with an output of the summing gear is. It is advantageous if the drive wheel, the Output member of the electric motor and the camshaft are rotatable coaxially with each other, so that the entire unit of drive wheel, electric motor, control gear and camshaft about a common axis, the so-called central axis, can rotate.

Um die Nockenwelle relativ zu dem Antriebsrad verstellen zu können, müssen vergleichsweise hohe Drehmomente aufgebracht werden. Damit diese Funktion von einem klein bauenden, schnell laufenden Elektromotor erfüllt werden kann, muss das Stellgetriebe eine hohe Übersetzung der Drehzahl des Elektromotors ins Langsame bewirken (bezogen auf ein festgehaltenes Antriebsrad). Hierfür kann das Stellgetriebe ein innenverzahntes Zahnrad und ein hiermit in Eingriff stehendes außenverzahntes Zahnrad aufweisen, wobei das innenverzahnte Zahnrad um die genannte Zentralachse drehbar ist und das außenverzahnte Zahnrad bezüglich der Zentralachse exzentrisch angeordnet ist und in dieser exzentrischen Anordnung zu einer Kreisbewegung um die Zentralachse antreibbar ist. Der genannten Kreisbewegung ist hierbei - da das außenverzahnte Zahnrad an dem innenverzahnten Zahnrad abwälzt - eine vergleichsweise langsame Rotation des außenverzahnten Zahnrads (relativ zu dem innenverzahnten Zahnrad) überlagert. Falls bei einer derartigen Anordnung das außenverzahnte Zahnrad nur geringfügig weniger Zähne besitzt als das hiermit kämmende innenverzahnte Zahnrad (z.B. Unterschied von 1 bis 5 Zähnen), lassen sich hierdurch vorteilhaft hohe Übersetzungen darstellen (z.B. 60 bis 300).In order to adjust the camshaft relative to the drive wheel, comparatively high torques must be applied. For this function can be met by a small-sized, fast-running electric motor, the control gear must cause a high ratio of the speed of the electric motor to slow (based on a fixed drive wheel). For this purpose, the actuating gear having an internally toothed gear and an externally toothed gear meshing therewith, wherein the internally toothed gear is rotatable about said central axis and the externally toothed gear is eccentric with respect to the central axis and is driven in this eccentric arrangement to a circular movement about the central axis , The said circular movement is here - as the externally toothed gear rolls on the internally toothed gear - a relatively slow rotation of the externally toothed gear (relative to the internally toothed gear) superimposed. With such an arrangement, if the externally toothed gear has only slightly fewer teeth than the internally toothed gear meshing therewith (e.g., 1 to 5 teeth difference), advantageously high ratios can be achieved (e.g., 60 to 300).

Ein Problem bei einem derartigen Stellgetriebe besteht jedoch darin, dass das mit dem innenverzahnten Zahnrad kämmende außenverzahnte Zahnrad bezüglich der Zentralachse der Verstellvorrichtung exzentrisch angeordnet ist. Somit lässt sich die Kreisbewegung des außenverzahnten Zahnrads nicht ohne weiteres auf ein Eingangselement oder Ausgangselement des Stellgetriebes (z.B. auf die Nockenwelle) übertragen, die - wie vorstehend erläutert - allesamt koaxial zu der Zentralachse angeordnet sein sollen.A problem with such a control gear is, however, that the meshing with the internal gear external gear is arranged eccentrically with respect to the central axis of the adjusting device. Thus, the circular motion of the externally toothed gear can not readily be applied to an input element or output element of the adjusting gear (eg on the camshaft) transmitted, which - as explained above - all should be arranged coaxially to the central axis.

Eine Aufgabe der Erfindung besteht darin, eine Nockenwellen-Verstellvorrichtung der eingangs genannten Art zu schaffen, bei der das Stellgetriebe bei kompaktem Aufbau und hohem Wirkungsgrad eine hohe Übersetzung ins Langsame bewirkt.An object of the invention is to provide a camshaft adjusting device of the type mentioned, in which the actuating mechanism causes a high gear ratio with a compact design and high efficiency in the slow.

Diese Aufgabe wird durch eine Verstellvorrichtung mit den Merkmalen des Anspruchs 1 gelöst, und insbesondere dadurch, dass das außenverzahnte Zahnrad an wenigstens zwei Exzenterwellen exzentrisch gelagert ist, wobei jede Exzenterwelle zu einer Drehbewegung um eine jeweilige Exzenterachse antreibbar ist, wobei die Exzenterachsen bezüglich der Zentralachse exzentrisch angeordnet und um die Zentralachse drehbar sind.This object is achieved by an adjusting device with the features of claim 1, and in particular in that the externally toothed gear is eccentrically mounted on at least two eccentric shafts, each eccentric shaft is drivable for rotational movement about a respective eccentric axis, wherein the eccentric axes eccentric with respect to the central axis arranged and rotatable about the central axis.

Bei der erfindungsgemäßen Verstellvorrichtung sind also wenigstens zwei Exzenterachsen vorgesehen, die bezüglich der genanten Zentralachse der Verstellvorrichtung außermittig angeordnet und insbesondere parallel zueinander angeordnet sind. Die Anordnung der in fester Relativlage zueinander stehenden Exzenterachsen kann um die Zentralachse gedreht werden, d.h. die Anordnung aus wenigstens zwei Exzenterachsen ist koaxial zu dem Antriebsrad, dem Elektromotor und der Nockenwelle drehbar, wobei die jeweilige Lage der Exzenterachsen beispielsweise durch eine gemeinsame Trägereinrichtung definiert ist.In the adjusting device according to the invention therefore at least two eccentric axes are provided, which are arranged eccentrically with respect to the genanten central axis of the adjusting device and in particular are arranged parallel to each other. The arrangement of the fixed relative to each other eccentric axes can be rotated about the central axis, i. the arrangement of at least two eccentric axes is rotatable coaxially to the drive wheel, the electric motor and the camshaft, wherein the respective position of the eccentric axes is defined for example by a common carrier device.

Jeder Exzenterachse ist eine jeweilige Exzenterwelle zugeordnet. Jede Exzenterwelle umfasst einen Exzenterabschnitt (d.h. einen Nocken) und ist zu einer Drehbewegung um die jeweilige Exzenterachse antreibbar. Das genannte außenverzahnte Zahnrad, welches mit dem genannten innenverzahnten Zahnrad in Eingriff steht, ist an den wenigstens zwei Exzenterwellen gelagert, so dass durch die Drehbewegung der Exzenterwellen um die jeweilige Exzenterachse das außenverzahnte Zahnrad zu der genannten (exzentrischen) Kreisbewegung um die Zentralachse angetrieben werden kann.Each eccentric axis is assigned a respective eccentric shaft. Each eccentric shaft includes an eccentric portion (ie, a cam) and is drivable for rotational movement about the respective eccentric axis. Said external gear, which with said internal toothed Gear is engaged, is mounted on the at least two eccentric shafts, so that by the rotational movement of the eccentric shafts about the respective eccentric axis, the externally toothed gear can be driven to said (eccentric) circular motion about the central axis.

Somit kann die erforderliche Exzentrizität des außenverzahnten Zahnrads durch den jeweiligen Exzenterabschnitt der Exzenterwellen dargestellt werden, wobei die den Exzenterwellen zugeordneten Exzenterachsen gemeinsam eine zu der Zentralachse koaxiale Drehbewegung ausführen können. Die Exzenterwellen, die um die exzentrisch angeordneten Exzenterachsen drehbar sind, ermöglichen also, dass die exzentrische Kreisbewegung (mit überlagerter Rotation) des außenverzahnten Zahnrads auf eine Drehbewegung um die Zentralachse der Verstellvorrichtung zurückgeführt werden kann, nämlich in Form einer Rotation der genannten Exzenterachsen um die Zentralachse. Daher können die beiden Eingänge und der Ausgang des Stellgetriebes allesamt koaxial zu der Zentralachse angeordnet sein.Thus, the required eccentricity of the externally toothed gear can be represented by the respective eccentric portion of the eccentric shafts, wherein the eccentric shafts associated with the eccentric shafts can jointly perform a rotational movement coaxial with the central axis. The eccentric shafts, which are rotatable about the eccentrically arranged eccentric axes, thus make it possible for the eccentric circular movement (with superimposed rotation) of the externally toothed toothed wheel to be attributed to a rotational movement about the central axis of the adjusting device, namely in the form of a rotation of said eccentric axes about the central axis , Therefore, the two inputs and the output of the adjusting gear can all be arranged coaxially to the central axis.

Im Ergebnis kann durch die Verwendung eines koaxialen innenverzahnten Zahnrades und eines hiermit kämmenden, exzentrischen außenverzahnten Zahnrades bei geringem Bauraum ein Stellgetriebe mit einer hohen Übersetzung ins Langsame realisiert werden, wobei durch die koaxiale Ausführung der beiden Eingangselemente und des Ausgangselements des Stellgetriebes ein einfacher Aufbau möglich ist und ein hoher Wirkungsgrad erreicht werden kann.As a result, by means of the use of a coaxial internal gear and a meshing, eccentric external gear with a small space a control gear with a high gear ratio can be realized slowly, with a simple structure is possible by the coaxial design of the two input elements and the output element of the actuating gear and high efficiency can be achieved.

Vorteilhafte Ausführungsformen der Erfindung sind nachfolgend erläutert und in den abhängigen Ansprüchen genannt.Advantageous embodiments of the invention are explained below and referred to in the dependent claims.

Gemäß einer bevorzugten Ausführungsform ist das außenverzahnte Zahnrad mittels eines jeweiligen Wälzlagers an den Exzenterwellen gelagert. Hierdurch können die exzentrische Kreisbewegung des außenverzahnten Zahnrades und die hierdurch bewirkte Drehmomentübertragung mit einem besonders guten Wirkungsgrad dargestellt werden. Nach einer weiteren Ausführungsform kann das außenverzahnte Zahnrad mittels eines jeweiligen Gleitlagers an den Exzenter wellen gelagert werden.According to a preferred embodiment, the externally toothed gear is mounted by means of a respective rolling bearing on the eccentric shafts. As a result, the eccentric circular movement of the externally toothed gear and the torque transmission caused thereby can be represented with a particularly good efficiency. According to a further embodiment, the externally toothed gear can be supported by means of a respective sliding bearing on the eccentric shafts.

Ferner ist es bevorzugt, wenn jede Exzenterwelle an einem jeweiligen Lagerzapfen - dem so genannten Exzenterzapfen - drehbar gelagert ist, wobei die Exzenterzapfen die genannten Exzenterachsen definieren und an einer gemeinsamen Trägereinrichtung befestigt sind. Hierdurch ist eine besonders einfache Lagerung der drehbar antreibbaren Exzenterwellen möglich. Bei dieser Ausführungsform sind die Exzenterwellen insbesondere als Hohlwellen ausgeführt, die innenseitig an den Exzenterzapfen gelagert sind. Alternativ können die Exzenterwellen jedoch beispielsweise unmittelbar zapfenartig in eine gemeinsame Trägereinrichtung eingreifen und an diesen außenseitig drehbar gelagert sein.Furthermore, it is preferred if each eccentric shaft is rotatably mounted on a respective bearing journal - the so-called eccentric pin -, wherein the eccentric pins define said eccentric axes and are fastened to a common carrier device. As a result, a particularly simple mounting of the rotatably driven eccentric shafts is possible. In this embodiment, the eccentric shafts are designed in particular as hollow shafts, which are mounted on the inside of the eccentric pin. Alternatively, however, the eccentric shafts may, for example, engage directly in the manner of a pin in a common carrier device and be rotatably mounted on the latter on the outside.

Hierbei ist es ferner bevorzugt, wenn die Exzenterwellen wiederum mittels eines jeweiligen weiteren Wälzlagers an den Exzenterzapfen gelagert sind. Hierdurch wird der Wirkungsgrad des Stellgetriebes noch weiter erhöht, da für die Bewegung des außenverzahnten Zahnrades somit durchgehend eine Wälzlagerung vorgesehen sein kann.In this case, it is further preferred if the eccentric shafts are in turn mounted on the eccentric pin by means of a respective further rolling bearing. As a result, the efficiency of the adjusting gear is further increased, since thus for the movement of the externally toothed gear a rolling bearing can be provided.

Gemäß einer weiteren bevorzugten Ausführungsform ist das innenverzahnte Zahnrad mit dem Antriebsrad drehfest verbunden und die Anordnung der mehreren Exzenterachsen (insbesondere die Anordnung der mehreren Exzenterzapfen) ist mit der Nockenwelle drehfest verbunden. Mit anderen Worten bildet in diesem Fall das innenverzahnte Zahnrad einen Eingang und die Anordnung der mehreren Exzenterachsen bildet den Ausgang des Stellgetriebes. Hierdurch lässt sich ein besonders kompakter Aufbau des Stellgetriebes realisieren, wobei insbesondere auch eine einteilige Ausbildung des innenverzahnten Zahnrads mit dem Antriebsrad möglich ist. Grundsätzlich ist jedoch auch eine umgekehrte Anordnung möglich.According to a further preferred embodiment, the internally toothed gear is rotatably connected to the drive wheel and the arrangement of the plurality of eccentric axes (in particular the arrangement of the plurality of eccentric pins) is rotatably connected to the camshaft. In other words, in this case, the internal gear forms a Input and the arrangement of the multiple eccentric axes forms the output of the actuating gear. This makes it possible to realize a particularly compact design of the adjusting gear, wherein in particular a one-piece design of the internally toothed gear with the drive wheel is possible. In principle, however, a reverse arrangement is possible.

Weiterhin ist es bevorzugt, wenn die genannten Exzenterwellen mittels des Elektromotors zu einer Drehbewegung um die jeweilige Exzenterachse antreibbar sind. Mit anderen Worten sind in diesem Fall die das außenverzahnte Zahnrad tragenden Exzenterwellen einem Eingang des Stellgetriebes zugeordnet.Furthermore, it is preferred if said eccentric shafts are drivable by means of the electric motor to a rotational movement about the respective eccentric axis. In other words, in this case the eccentric shafts carrying the externally toothed gear are assigned to an input of the adjusting gear.

Vorzugsweise sind die Exzenterwellen zu einer zueinander synchronen Drehbewegung um die jeweilige Exzenterachse antreibbar, um die erwünschte Kreisbewegung des außenverzahnten Zahnrades zu bewirken.Preferably, the eccentric shafts are drivable to a mutually synchronous rotational movement about the respective eccentric axis in order to effect the desired circular movement of the externally toothed gear.

Gemäß einer bevorzugten Ausführungsform ist jede Exzenterwelle mit einem jeweiligen Kopplungszahnrad drehfest verbunden (insbesondere einteilig ausgebildet). In diesem Fall kann der Elektromotor ein Motorritzel antreiben, das koaxial zu der Zentralachse der Verstellvorrichtung angeordnet ist und mit den Kopplungszahnrädern direkt oder über wenigstens ein gemeinsames Zwischenzahnrad kämmt. Hierdurch kann also zusätzlich zu dem Synchronantrieb die exzentrische Lagerung der Exzenterwellen auf einen zu der Zentralachse koaxialen Antrieb zurückgeführt werden.According to a preferred embodiment, each eccentric shaft with a respective coupling gear rotatably connected (in particular integrally formed). In this case, the electric motor can drive a motor pinion, which is arranged coaxially to the central axis of the adjusting device and meshes with the coupling gears directly or via at least one common intermediate gear. As a result, in addition to the synchronous drive, the eccentric bearing of the eccentric shafts can thus be attributed to a drive coaxial with the central axis.

Vorzugsweise sind die Kopplungszahnräder und das Zwischenzahnrad (falls vorhanden) in jeder Stellung des Stellgetriebes radial vollständig innerhalb der Verzahnung des außenverzahnten Zahnrads angeordnet.Preferably, the coupling gears and the intermediate gear (if present) in each position of the adjusting gear are arranged radially completely within the toothing of the externally toothed gear.

Mit anderen Worten sind die Kopplungszahnräder und gegebenenfalls das Zwischenzahnrad vollständig innerhalb eines gedachten zur Zentralachse konzentrischen Zylindermantels angeordnet, wobei sich der Zylindermantel in jeder Getriebestellung vollständig innerhalb der Verzahnung des außenverzahnten Zahnrads befindet, so dass sich die Zahnbreite des außenverzahnten Zahnrads und ebenso die Zahnbreite des innenverzahnten Zahnrades axial über die Kopplungszahnräder bzw. das Zwischenzahnrad fortsetzen kann. Die Kopplungszahnräder bzw. das Zwischenzahnrad können somit axial vollständig oder teilweise innerhalb des außenverzahnten Zahnrads und des innenverzahnten Zahnrades angeordnet sein. Hierdurch verkürzt sich die axiale Baulänge des Stellgetriebes.In other words, the coupling gears and possibly the intermediate gear are arranged completely within an imaginary to the central axis concentric cylinder jacket, wherein the cylinder shell is in each gear position completely within the teeth of the external gear, so that the tooth width of the external gear and also the tooth width of the internally toothed Gear can continue axially via the coupling gears and the intermediate gear. The coupling gears or the intermediate gear can thus be arranged axially completely or partially within the externally toothed gear and the internally toothed gear. This shortens the axial length of the adjusting gear.

Gemäß einer weiteren Ausführungsform sind zwei, drei oder vier Exzenterwellen vorgesehen, die um eine jeweilige Exzenterachse drehbar antreibbar sind, um das außenverzahnte Zahnrad anzutreiben, wobei die Exzenterachsen vorzugsweise in einer gleichmäßigen Winkelteilung um die Zentralachse verteilt angeordnet sind.According to a further embodiment, two, three or four eccentric shafts are provided, which are rotatably driven about a respective eccentric axis to drive the externally toothed gear, wherein the eccentric axes are preferably distributed in a uniform angular pitch about the central axis.

Die Erfindung wird nachfolgend lediglich beispielhaft unter Bezugnahme auf die Zeichnungen erläutert.

Fig. 1
zeigt eine Seitenansicht einer erfindungsgemäßen Verstellvorrichtung.
Fig. 2
zeigt einen Querschnitt entlang der Ebene II-II gemäß Fig. 1.
Fig. 3
zeigt einen Querschnitt entlang der Ebene III-III gemäß Fig. 1.
Fig. 4
zeigt einen Längsschnitt entlang der Ebene IV-IV gemäß Fig. 2.
Fig. 5
zeigt einen Längsschnitt entlang der Ebene V-V gemäß Fig. 1, die bezüglich der Schnittebene gemäß Fig. 4 um 90° gedreht ist.
The invention will now be described by way of example only with reference to the drawings.
Fig. 1
shows a side view of an adjusting device according to the invention.
Fig. 2
shows a cross section along the plane II-II according to Fig. 1 ,
Fig. 3
shows a cross section along the plane III-III according to Fig. 1 ,
Fig. 4
shows a longitudinal section along the plane IV-IV according to Fig. 2 ,
Fig. 5
shows a longitudinal section along the plane VV according to Fig. 1 in accordance with the sectional plane according to Fig. 4 rotated by 90 °.

Die in Fig. 1 bis 5 gezeigte Verstellvorrichtung dient zur Relatiwerstellung einer Nockenwelle 11 einer nicht dargestellten Verbrennungskraftmaschine bezüglich eines die Nockenwelle 11 koaxial antreibenden Antriebsrads 13, das beispielsweise über einen nicht dargestellten Kettentrieb mit einer Kurbelwelle der Verbrennungskraftmaschine antriebswirksam gekoppelt ist. Das Antriebsrad 13 und die Nockenwelle 11 sind bezüglich einer Zentralachse A der Verstellvorrichtung koaxial angeordnet. Das Antriebsrad 13 ist mit der Nockenwelle 11 über ein Stellgetriebe 15 gekoppelt, das mittels eines Elektromotors 17 angetrieben werden kann, um die Phasenlage der Nockenwelle 11 relativ zu dem Antriebsrad 13 zu verstellen.In the Fig. 1 to 5 shown adjusting device is used to Relatiwerstellung a camshaft 11 of an internal combustion engine, not shown with respect to a camshaft 11 coaxially driving drive wheel 13, which is drivingly coupled for example via a chain drive, not shown, with a crankshaft of the internal combustion engine. The drive wheel 13 and the camshaft 11 are arranged coaxially with respect to a central axis A of the adjusting device. The drive wheel 13 is coupled to the camshaft 11 via a control gear 15, which can be driven by means of an electric motor 17 in order to adjust the phase position of the camshaft 11 relative to the drive wheel 13.

Wie insbesondere in den Fig. 4 und 5 gezeigt ist, umfasst das Stellgetriebe 15 ein innenverzahntes Zahnrad 19, das über ein Wälzlager 21 an einer Trägereinrichtung 23 des Stellgetriebes 15 koaxial zu der Zentralachse A drehbar gelagert ist. Wie aus den Fig. 2 und 3 ersichtlich ist, steht das innenverzahnte Zahnrad 19 mit einem außenverzahnten Zahnrad 25 in Eingriff. Das außenverzahnte Zahnrad 25 ist bezüglich der Zentralachse A geringfügig exzentrisch angeordnet, und es ist in dieser leicht exzentrischen Anordnung zu einer Kreisbewegung um die Zentralachse A antreibbar. Die Zähnezahldifferenz zwischen dem innenverzahnten Zahnrad 19 und dem außenverzahnten Zahnrad 25 ist sehr gering. Beispielsweise kann vorgesehen sein, dass das außenverzahnte Zahnrad 25 lediglich einen, zwei, drei, vier oder fünf Zähne weniger besitzt als das innenverzahnte Zahnrad 19. Dementsprechend ist - wie insbesondere aus Fig. 3 ersichtlich ist - die Exzentrizität des außenverzahnten Zahnrads 25 bezüglich der Zentralachse A sehr gering. Im oberen Bereich von Fig. 3 steht das außenverzahnte Zahnrad 25 in Eingriff mit dem innenverzahnten Zahnrad 19, während im unteren Bereich von Fig. 3 das außenverzahnte Zahnrad 25 knapp außer Eingriff mit dem innenverzahnten Zahnrad 19 steht.As in particular in the Fig. 4 and 5 is shown, the adjusting gear 15 comprises an internally toothed gear 19 which is rotatably supported via a rolling bearing 21 on a support means 23 of the adjusting gear 15 coaxial with the central axis A. Like from the Fig. 2 and 3 it can be seen, the internal gear 19 is in engagement with an externally toothed gear 25. The externally toothed gear 25 is arranged slightly eccentric with respect to the central axis A, and it is in this slightly eccentric arrangement to a circular motion about the central axis A drivable. The number of teeth difference between the internal gear 19 and the external gear 25 is very small. For example, it may be provided that the externally toothed gear 25 has only one, two, three, four or five teeth less than the internally toothed Gear 19. Accordingly - as in particular from Fig. 3 it can be seen - the eccentricity of the externally toothed gear 25 with respect to the central axis A very low. In the upper area of Fig. 3 the externally toothed gear 25 is engaged with the internal gear 19, while in the lower region of Fig. 3 the externally toothed gear 25 is just out of engagement with the internal gear 19.

Fig. 3 zeigt, dass das außenverzahnte Zahnrad 25 über ein jeweiliges Wälzlager 27 an zwei Exzenterwellen 29 gelagert ist. Jede der beiden Exzenterwellen 29 ist wiederum über ein Wälzlager 31 an einem jeweiligen Exzenterzapfen 33 gelagert und um eine jeweilige Exzenterachse B drehbar. Die beiden Exzenterzapfen 33 und somit die beiden Exzenterachsen B sind bezüglich der Zentralachse A exzentrisch angeordnet. Wie in Fig. 4 gezeigt ist, erstrecken sich die beiden Exzenterzapfen 33 parallel zueinander, und sie sind an der Trägereinrichtung 23 befestigt, so dass die beiden Exzenterzapfen 33 und somit die beiden Exzenterachsen B in fester Relativlage um die Zentralachse A drehbar sind. Aus Fig. 3 ist ersichtlich, dass die Exzentrizität des jeweiligen Außenumfangs der Exzenterwellen 29 bezüglich der jeweiligen Exzenterachse B der Exzentrizität des außenverzahnten Zahnrads 25 bezüglich der Zentralachse A entspricht. Die Exzentrizität der Exzenterachsen B bezüglich der Zentralachse A ist hingegen deutlich größer als die Exzentrizität des außenverzahnten Zahnrads 25 bezüglich der Zentralachse A. Die Zentralachse A und die Exzenterachsen B befinden sich innerhalb des Wälzkreises des außenverzahnten Zahnrads 25. Fig. 3 shows that the externally toothed gear 25 is mounted on a respective rolling bearing 27 on two eccentric shafts 29. Each of the two eccentric shafts 29 is in turn supported by a rolling bearing 31 on a respective eccentric pin 33 and rotatable about a respective eccentric axis B. The two eccentric pins 33 and thus the two eccentric axes B are arranged eccentrically with respect to the central axis A. As in Fig. 4 is shown, the two eccentric pins 33 extend parallel to each other, and they are attached to the support means 23, so that the two eccentric pins 33 and thus the two eccentric axes B are rotatable about the central axis A in a fixed relative position. Out Fig. 3 It can be seen that the eccentricity of the respective outer periphery of the eccentric shafts 29 with respect to the respective eccentric axis B corresponds to the eccentricity of the externally toothed gear 25 with respect to the central axis A. The eccentricity of the eccentric axes B with respect to the central axis A, however, is significantly greater than the eccentricity of the externally toothed gear 25 with respect to the central axis A. The central axis A and the eccentric axes B are within the pitch circle of the externally toothed gear 25th

Aus Fig. 4 ist ersichtlich, dass jede Exzenterwelle 29 mit einem jeweiligen Kopplungszahnrad 34 drehfest verbunden, nämlich einteilig ausgebildet ist. In Fig. 2 ist gezeigt, dass die beiden Kopplungszahnräder 34 über ein gemeinsames Zwischenzahnrad 35 mit einem Motorritzel 37 in Eingriff stehen. Das Zwischenzahnrad 35 ist an einem Lagerzapfen 36 drehbar gelagert, der parallel zu den Exzenterzapfen 33 ausgerichtet und ebenfalls an der Trägereinrichtung 23 befestigt ist (Fig. 5). Weiter sind in Fig. 2, 3 und 5 Schrauben 39 gezeigt, durch die das Stellgetriebe 15, mittels der Trägereinrichtung 23, fest mit einem Flansch 24 der Nockenwelle 11 verbunden ist. Eine der Schrauben 39 durchsetzt dabei koaxial den Lagerzapfen 36 und verschraubt diesen Lagerzapfen 36 über die Trägereinrichtung 23 mit dem Nockenwellenflansch 24.Out Fig. 4 It can be seen that each eccentric shaft 29 rotatably connected to a respective coupling gear 34, that is formed in one piece. In Fig. 2 It is shown that the two coupling gears 34 via a common intermediate gear 35 with a motor pinion 37 are engaged. The intermediate gear 35 is rotatably mounted on a bearing journal 36, which is aligned parallel to the eccentric 33 and also secured to the support means 23 ( Fig. 5 ). Next are in Fig. 2 . 3 and 5 Screw 39 shown by the actuating gear 15, by means of the support means 23, fixedly connected to a flange 24 of the camshaft 11. One of the screws 39 passes coaxially through the bearing pin 36 and screwed this bearing pin 36 via the support means 23 with the camshaft flange 24th

Das Motorritzel 37 wird von dem Elektromotor 17 über eine Motorwelle 41 angetrieben (Fig. 4 und 5). Das Zwischenzahnrad 35 ist jedoch nicht zwingend erforderlich; stattdessen kann das Motorritzel 37 die beiden Kopplungszahnräder 34 auch direkt antreiben. In beiden Fällen erfolgt ein synchroner Antrieb der beiden Exzenterwellen 29 durch das Motorritzel 37.The motor pinion 37 is driven by the electric motor 17 via a motor shaft 41 ( Fig. 4 and 5 ). However, the intermediate gear 35 is not mandatory; instead, the motor pinion 37 may also drive the two coupling gears 34 directly. In both cases, a synchronous drive of the two eccentric shafts 29 takes place through the motor pinion 37.

Das Stellgetriebe 15 bildet ein Summiergetriebe, um mittels des Elektromotors 17 die Phasenlage der Nockenwelle 11 relativ zu dem Antriebsrad 13 variieren zu können. Hierbei bildet das dem Antriebsrad 13 zugeordnete innenverzahnte Zahnrad 19 einen ersten Eingang. Das dem Elektromotor 17 zugeordnete Motorritzel 37 bildet einen zweiten Eingang. Die die Exzenterzapfen 33 tragende und mit dem Nockenwellenflansch 24 fest verbundene Trägereinrichtung 23 bildet einen Ausgang des Stellgetriebes 15.The actuating mechanism 15 forms a summing gear in order to be able to vary the phase position of the camshaft 11 relative to the drive wheel 13 by means of the electric motor 17. Here, the drive wheel 13 associated with internally toothed gear 19 forms a first input. The motor gear 17 associated with the electric motor 17 forms a second input. The eccentric 33 carrying and firmly connected to the camshaft flange 24 support means 23 forms an output of the adjusting gear 15th

Sofern die Drehzahl des Elektromotors 17 und somit des Motorritzels 37 auf die Drehzahl des Antriebsrads 13 eingestellt ist, dreht sich das Stellgetriebe 15 im Block um die Zentralachse A, und die Drehzahl der Nockenwelle 11 entspricht somit jener des Antriebsrads 13. Durch kurzzeitiges Schneller- oder Langsamerlaufen des Elektromotors 17 kann jedoch ein Verstellen der Phasenlage der Nockenwelle 11 bewirkt werden, wobei das von dem Elektromotor 17 aufzubringende Drehmoment gering ist. Bezogen auf ein festgehaltenes Antriebsrad 13 bewirkt eine Drehbewegung des Motorritzels 37 nämlich eine lediglich geringfügige Verdrehung der Nockenwelle 11, d.h. das Stellgetriebe 15 bewirkt eine starke Übersetzung ins Langsame. Dies ist im Wesentlichen darauf zurückzuführen, dass bei einer vollständigen Kreisbewegung des exzentrisch angeordneten außenverzahnten Zahnrads 25 um die Zentralachse A das außenverzahnte Zahnrad 25 an dem innenverzahnten Zahnrad 19 abwälzt. Aufgrund der geringen Zähnezahldifferenz zwischen den beiden Zahnrädern 19, 25 bewirkt eine vollständige Kreisbewegung des außenverzahnten Zahnrades 25 relativ zu dem innenverzahnten Zahnrad 19 nur eine geringe überlagerte Rotation des außenverzahnten Zahnrads 25, nämlich genau entsprechend der geringen Zähnezahldifferenz.If the rotational speed of the electric motor 17 and thus of the motor pinion 37 is set to the rotational speed of the drive wheel 13, the actuating gear 15 rotates in the block about the central axis A, and the rotational speed of the camshaft 11 thus corresponds to that of the drive wheel 13. Durch kurzzeitiges Schneller- Slower running of the electric motor 17, however, a Adjusting the phase position of the camshaft 11 can be effected, wherein the torque to be applied by the electric motor 17 is low. Relative to a retained drive wheel 13 causes a rotational movement of the motor pinion 37 namely only a slight rotation of the camshaft 11, that is, the actuating gear 15 causes a strong translation into slow. This is essentially due to the fact that in a complete circular movement of the eccentrically arranged externally toothed gear 25 about the central axis A, the externally toothed gear 25 rolls on the internally toothed gear 19. Due to the small number of teeth difference between the two gears 19, 25 causes a complete circular movement of the externally toothed gear 25 relative to the internal gear 19 only a small superimposed rotation of the externally toothed gear 25, namely exactly the small number of teeth difference.

Um das außenverzahnte Zahnrad 25 trotz seiner exzentrischen Anord-nung mittels des zu der Zentralachse A koaxial angeordneten Elektromotors 17 antreiben zu können, treibt das Motorritzel 37 über das Zwischenzahnrad 35 und die Kopplungszahnräder 34 die beiden Exzenterwellen 29 synchron zueinander zu einer jeweiligen Drehbewegung um die Exzenterachsen B an. Anhand von Fig. 3 ist erkennbar, dass das außenverzahnte Zahnrad 25 hierdurch zu einer Kreisbewegung relativ zu der Anordnung der Exzenterzapfen 33 angetrieben wird, wobei der Mittelpunkt des außenverzahnten Zahnrads 25 sich auf einer Kreisbahn um die Zentralachse A bewegt.In order to drive the externally toothed gear 25 despite its eccentric arrangement by means of the coaxial to the central axis A arranged electric motor 17, the motor pinion 37 drives via the intermediate gear 35 and the coupling gears 34, the two eccentric shafts 29 synchronously to each other to a respective rotational movement about the eccentric axes B on. Based on Fig. 3 It can be seen that the externally toothed gear 25 is thereby driven to a circular movement relative to the arrangement of the eccentric pins 33, wherein the center of the externally toothed gear 25 moves in a circular orbit about the central axis A.

Um die hierdurch bewirkte überlagerte Drehbewegung des außenverzahnten Zahnrads 25 relativ zu dem innenverzahnten Zahnrad 19 trotz der exzentrischen Anordnung des außenverzahnten Zahnrads 25 auf die koaxial zu der Zentralachse A angeordnete Nockenwelle 11 übertragen zu können, sitzen die der Drehbewegung des außenverzahnten Zahnrads 25 folgenden Exzenterwellen 29 auf den Exzenterzapfen 33, die über die Trägereinrichtung 23 mittels Schrauben 39 mit dem Nockenwellenflansch 24 und somit mit der Nockenwelle 11 fest verbunden sind.In spite of the eccentric arrangement of the externally toothed gear 25, the superimposed rotational movement of the externally toothed gear 25 caused thereby is transmitted to the camshaft 11 arranged coaxially with the central axis A, relative to the internally toothed gear 19 can sit the rotational movement of the externally toothed gear 25 following eccentric shafts 29 on the eccentric pin 33 which are fixedly connected via the support means 23 by means of screws 39 with the Nockenwellenflansch 24 and thus with the camshaft 11.

Somit ist es im Ergebnis möglich, die beiden Eingänge (Antriebsrad 13 mit innenverzahntem Zahnrad 19 und Motorwelle 41 mit Motorritzel 37) und den Ausgang (Exzenterzapfen 33 mit Nockenwelle 11) des Stellgetriebes 15 koaxial zu der Zentralachse A anzuordnen und gleichwohl für sämtliche drehbeweglichen Elemente des Stellgetriebes 15 eine Wälzlagerung zu ermöglichen. Die gezeigte Verstellvorrichtung zeichnet sich deshalb trotz hoher Untersetzungswirkung des Stellgetriebes 15 bei geringer Baugröße durch einen hohen Wirkungsgrad aus.Thus, it is possible as a result to arrange the two inputs (drive wheel 13 with internal gear 19 and motor shaft 41 with motor pinion 37) and the output (eccentric cam 33 with camshaft 11) of the actuating gear 15 coaxial with the central axis A and nonetheless for all rotatable elements of the Actuator 15 to allow a rolling bearing. The adjusting device shown is therefore characterized despite high reduction effect of the actuating gear 15 with a small size by a high efficiency.

Abweichend von der Darstellung in den Fig. 1 bis 5 können die Kopplungszahnräder 34 und das Zwischenzahnrad 35 derart kleiner ausgebildet sein, dass sie radial vollständig innerhalb der Verzahnung des außenverzahnten Zahnrads 25 angeordnet sind. Hierdurch lässt sich eine verkürzte axiale Baulänge des Stellgetriebes 15 erreichen, nämlich wenn das außenverzahnte Zahnrad 25 und dementsprechend das innenverzahnte Zahnrad 19 die Kopplungszahnräder 34 und das Zwischenzahnrad 35 axial teilweise oder vollständig übergreifen.Deviating from the representation in the Fig. 1 to 5 For example, the coupling gears 34 and the intermediate gear 35 may be made smaller such that they are disposed radially completely within the teeth of the external gear 25. In this way, a shortened axial length of the adjusting gear 15 can be achieved, namely when the externally toothed gear 25 and accordingly the internally toothed gear 19, the coupling gears 34 and the intermediate gear 35 axially partially or completely overlap.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1111
Nockenwellecamshaft
1313
Antriebsraddrive wheel
1515
Stellgetriebeactuating mechanism
1717
Elektromotorelectric motor
1919
innenverzahntes Zahnradinternal gear
2121
Wälzlagerroller bearing
2323
Trägereinrichtungsupport means
2424
NockenwellenflanschNockenwellenflansch
2525
außenverzahntes Zahnradexternally toothed gear
2727
Wälzlagerroller bearing
2929
Exzenterwelleeccentric shaft
3131
Wälzlagerroller bearing
3333
Exzenterzapfeneccentric
3434
Kopplungszahnradcoupling gear
3535
Zwischenzahnradintermediate gear
3636
Lagerzapfenpivot
3737
Motorritzelpinion
3939
Schraubescrew
4141
Motorwellemotor shaft
AA
Zentralachsecentral axis
BB
Exzenterachseeccentric

Claims (11)

  1. Adjustment apparatus for the relative adjustment of a camshaft (11) with respect to a drive wheel (13) that coaxially drives the camshaft, wherein the drive wheel and the camshaft are arranged coaxially with respect to a central axis (A) of the adjustment apparatus, having a control gearing (15) which acts between the drive wheel and the camshaft and which can be driven by means of an electric motor (17) for the purpose of adjusting the camshaft,
    wherein the control gearing has an internally toothed gearwheel (19) and, meshing therewith, an externally toothed gearwheel (25), wherein the internally toothed gearwheel (19) is rotatable about the central axis (A) and the externally toothed gearwheel (25) is arranged eccentrically with respect to the central axis (A) and can be driven in circulating fashion about the central axis,
    characterized
    in that the externally toothed gearwheel (25) is mounted eccentrically on at least two eccentric shafts (29), wherein each eccentric shaft can be driven so as to perform a rotational movement about a respective eccentric axis (B), wherein the eccentric axes (B) are arranged eccentrically with respect to the central axis (A) and are rotatable about the central axis.
  2. Adjustment apparatus according to Claim 1,
    wherein the externally toothed gearwheel (25) is mounted on the eccentric shafts (29) by means of a respective rolling bearing (27).
  3. Adjustment apparatus according to Claim 1 or 2,
    wherein each eccentric shaft (29) is rotatably mounted on a respective eccentric journal (33), wherein the eccentric journals (33) are fastened to a common carrier device (23).
  4. Adjustment apparatus according to Claim 3,
    wherein the eccentric shafts (29) are mounted on the eccentric journals (33) by way of a respective rolling bearing (31).
  5. Adjustment apparatus according to one of the preceding claims,
    wherein the internally toothed gearwheel (25) is connected rotationally conjointly to the drive wheel (13) and the eccentric axes (B) are assigned rotationally conjointly to the camshaft (11).
  6. Adjustment apparatus according to one of the preceding claims,
    wherein the eccentric shafts (29) can be driven by means of the electric motor (17) so as to perform a rotational movement about the respective eccentric axis (B).
  7. Adjustment apparatus according to one of the preceding claims,
    wherein the eccentric shafts (29) can be driven so as to perform a synchronous rotational movement about the respective eccentric axis (B).
  8. Adjustment apparatus according to one of the preceding claims,
    wherein each eccentric shaft (29) is connected rotationally conjointly to a respective coupling gearwheel (34), wherein the electric motor (17) drives a motor pinion (37) which is arranged coaxially with respect to the central axis (A) and which is coupled in terms of drive to the coupling gearwheels (34) directly or via an intermediate gearwheel (35).
  9. Adjustment apparatus according to Claim 8,
    wherein the coupling gearwheels (34) and, if provided, the intermediate gearwheel (35) are arranged radially entirely within the toothing of the externally toothed gearwheel (25) in all positions of the control gearing (15).
  10. Adjustment apparatus according to one of the preceding claims,
    wherein the eccentricity of the eccentric shafts (29) with respect to the respective eccentric axis (B) corresponds to the eccentricity of the externally toothed gearwheel (25) with respect to the central axis (A).
  11. Adjustment apparatus according to one of the preceding claims,
    wherein the eccentric axes (B) are arranged so as to be distributed with uniform angular separation about the central axis (A).
EP11735792.1A 2010-08-10 2011-07-06 Camshaft adjusting apparatus Active EP2603675B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010033897.4A DE102010033897B4 (en) 2010-08-10 2010-08-10 Camshaft adjustment
PCT/EP2011/003363 WO2012019680A1 (en) 2010-08-10 2011-07-06 Camshaft adjusting apparatus

Publications (2)

Publication Number Publication Date
EP2603675A1 EP2603675A1 (en) 2013-06-19
EP2603675B1 true EP2603675B1 (en) 2014-11-26

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ID=44628961

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Application Number Title Priority Date Filing Date
EP11735792.1A Active EP2603675B1 (en) 2010-08-10 2011-07-06 Camshaft adjusting apparatus

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US (1) US8881701B2 (en)
EP (1) EP2603675B1 (en)
JP (1) JP5646058B2 (en)
KR (1) KR101510971B1 (en)
CN (1) CN103080486B (en)
DE (1) DE102010033897B4 (en)
WO (1) WO2012019680A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016210710A1 (en) 2015-08-14 2017-02-16 Magna Powertrain Bad Homburg GmbH Adjustment device for adjusting a camshaft

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04105906U (en) * 1991-02-27 1992-09-11 株式会社アツギユニシア Internal combustion engine valve timing control device
US7086309B2 (en) * 2002-09-19 2006-08-08 The Johns Hopkins University Planetary-harmonic motor
DE102004007052A1 (en) 2004-02-13 2005-09-08 Daimlerchrysler Ag Phase angle adjustment system for camshaft in internal combustion engine has eccentric drive with external toothed pinion engaging gear ring driven by timing chain
JP2007198376A (en) * 2006-01-26 2007-08-09 Delphi Technologies Inc Variable cam phase device
JP4438768B2 (en) * 2006-04-27 2010-03-24 株式会社デンソー Valve timing adjustment device
JP4360426B2 (en) * 2007-07-09 2009-11-11 株式会社デンソー Valve timing adjustment device
JP5047356B2 (en) * 2008-04-23 2012-10-10 日鍛バルブ株式会社 Phase variable device for automobile engine
KR20110074753A (en) * 2008-10-22 2011-07-01 니탄 밸브 가부시키가이샤 Cam shaft phase variable device in engine for automobile
US8245679B2 (en) * 2008-10-22 2012-08-21 Denso Corporation Variable valve timing apparatus
JP4605292B2 (en) * 2008-10-22 2011-01-05 株式会社デンソー Valve timing adjustment device

Also Published As

Publication number Publication date
KR101510971B1 (en) 2015-04-10
US20130291815A1 (en) 2013-11-07
CN103080486B (en) 2015-05-06
CN103080486A (en) 2013-05-01
WO2012019680A1 (en) 2012-02-16
JP5646058B2 (en) 2014-12-24
KR20130038365A (en) 2013-04-17
EP2603675A1 (en) 2013-06-19
DE102010033897A1 (en) 2012-02-16
US8881701B2 (en) 2014-11-11
DE102010033897B4 (en) 2017-03-16
JP2013533431A (en) 2013-08-22

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