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EP2530260B1 - Coupling shaft, actuator, cam shaft adjustment drive and cam shaft adjuster - Google Patents

Coupling shaft, actuator, cam shaft adjustment drive and cam shaft adjuster Download PDF

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Publication number
EP2530260B1
EP2530260B1 EP12167002.0A EP12167002A EP2530260B1 EP 2530260 B1 EP2530260 B1 EP 2530260B1 EP 12167002 A EP12167002 A EP 12167002A EP 2530260 B1 EP2530260 B1 EP 2530260B1
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EP
European Patent Office
Prior art keywords
coupling
shaft
actuator
coupling shaft
component
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.)
Not-in-force
Application number
EP12167002.0A
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German (de)
French (fr)
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EP2530260A1 (en
Inventor
Michael Schober
Felix KUFFNER
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.)
Magna Powertrain GmbH and Co KG
Original Assignee
Magna Powertrain GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by Magna Powertrain GmbH and Co KG filed Critical Magna Powertrain GmbH and Co KG
Publication of EP2530260A1 publication Critical patent/EP2530260A1/en
Application granted granted Critical
Publication of EP2530260B1 publication Critical patent/EP2530260B1/en
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Anticipated expiration legal-status Critical

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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
    • F01L1/352—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 a coupling shaft for a camshaft actuator.
  • the invention relates to an actuator for setting a camshaft variable speed gear.
  • the invention relates to a camshaft adjusting, which is also referred to below as 'variable speed'.
  • the invention relates to a camshaft adjuster for an internal combustion engine.
  • Couplings for compensating an eccentricity (axial offset) between an axis of a control shaft of an actuator and an axis of a variable speed known. These couplings exercise with appropriate radial axial offset of the corresponding waves inertial forces on these waves and their bearings. In Oldham couplings and the large axial space requirement is disadvantageous.
  • the coupling shaft for a camshaft actuator is further developed in that the coupling shaft has at each of its two ends a respective coupling component for each one achschwinkelausrete rotary coupling.
  • the fact that the coupling shaft according to the invention has a coupling component at each of its two ends it is possible to compensate for an axial offset, without causing by this measure a cause or enlargement of an axis angle between the actuator and the adjustment must be accepted.
  • the developer receives an additional degree of freedom, which he can use to reduce the axial angle for the introduction of force into the actuator or into the adjusting mechanism.
  • the clutch shaft may, but need not, be integral.
  • An (entire) axial length of the coupling shaft may be greater than w% of a maximum diameter of the larger coupling component, where w% is at least 130%, in particular at least 150%.
  • the coupling shaft may be tapered between its two ends over more than w% of its (total) axial length, w% being at least 30%, in particular at least 60%.
  • the coupling shaft may comprise on at least one of its two end faces a cylindrically symmetrical, convex formation which is arranged concentrically to the main longitudinal axis of the coupling shaft.
  • the coupling shaft may include a flange for a bearing.
  • the first axis-compensating rotary joint may include a safety pin or a component of a toothed clutch, a dog clutch, a plug-in clutch, a dog clutch, a spur gear, a Teller leopardradkupplung, a flexible disc, a Belgkupplung, an elastomeric coupling, a helical clutch, a spring clutch, a spring disc clutch, a ridge clutch, a Compensating clutch, a Kardangetriebes or a constant velocity joint comprises.
  • the second angle-compensating rotary joint may comprise a safety bolt or a component of a toothed clutch, a dog clutch, a plug-in clutch, a driving clutch, a spur gear clutch, a Teller leopardradkupplung, a flexible disc, a Belgkupplung, an elastomeric coupling, a helical clutch, a spring clutch, a spring disc clutch, a bridge coupling , a compensating coupling, a Kardangetriebes or a constant velocity joint.
  • the toothed coupling component may comprise a curved tooth coupling.
  • the toothed coupling component may have a spherical or ball-shaped basic shape on which the teeth of the toothed coupling component are arranged.
  • the actuator is further developed in that a coupling shaft for providing the Nockenwellenverstellgetriebes is coupled to the actuator by means of a first achswinkelausrete Sammlunge in a region of the actuator, which faces away from the adjusting mechanism.
  • a coupling shaft for providing the Nockenwellenverstellgetriebes is coupled to the actuator by means of a first achswinkelausrete Sammlunge in a region of the actuator, which faces away from the adjusting mechanism.
  • the clutch shaft may extend over more than 50% of a (total) axial length of a rotor of the actuator.
  • the coupling shaft may be rotatably arranged in the actuator at any circumferential angle in the pitch direction, wherein a pitch angle of the coupling shaft with respect to an axis of the actuator to at least 1 °, in particular to at least 2 °, more preferably to at least 3 °.
  • the coupling shaft may be arranged axially displaceable in the rotor.
  • the actuator may include a thrust bearing component for biasing the clutch shaft in the direction of the main longitudinal axis of the clutch shaft.
  • the first axle-compensating rotary coupling for coupling to the rotor may include a safety pin or a component of a toothed clutch, a dog clutch, a plug-in clutch, a dog clutch, a spur gear, a Teller leopardradkupplung, a flexible disc, a Belgkupplung, an elastomer coupling, a helical clutch, a spring clutch, a spring disc clutch , a bridge coupling, a compensating coupling, a Kardangetriebes or a constant velocity joint.
  • the actuator may comprise a coupling shaft according to the invention.
  • the camshaft adjusting mechanism is further developed in that an inner or outer toothing of a gear drive gear of the camshaft adjusting gear for the engagement of the toothed coupling component of a coupling shaft according to the invention is formed or suitable or that the camshaft adjusting a clutch shaft according to the invention comprises.
  • the gear coupling component of the clutch shaft may form a flying gear drive gear of the camshaft variable speed gear.
  • the camshaft adjuster is further developed in that it comprises an actuator according to the invention and / or an inventive camshaft transmission.
  • camshaft actuator 10 includes a servomotor 12 and an adjusting 32.
  • the servomotor 12 may be for example an electric machine (electric motor), a hydraulic drive or a pneumatic drive.
  • the servomotor 12 comprises a rotor 14, which is mounted in two rotor bearings 16.
  • the rotor 14 includes a hollow shaft 18.
  • the hollow shaft 18 is surrounded by a radial shaft seal 20, which helps to seal the oil-filled camshaft space 22 against parts of the servomotor 12.
  • Cam shaft-side parts 26, 32 of the camshaft actuator 10 are typically located under engine oil 24.
  • a clutch shaft 26 is passed through the hollow shaft 18 and fixed on that side of the rotor 14 to the rotor 14, which faces away from the adjusting 32.
  • the coupling shaft 26 may extend over more than 50% of a (total) axial length of a rotor 14.
  • the coupling shaft 26 is articulated to the rotor 14 for torque transmission to the adjusting mechanism 32 by means of a securing bolt 34.
  • the clutch shaft 26 has at its Stellmotor principleen end 30 a passage 25 for a safety pin 34.
  • the securing bolt 34 is mounted in opposite holes 36 in the wall of the hollow shaft 18.
  • the coupling shaft 26 may have a spindle-shaped or spherical thickening 38 whose outer diameter is only slightly smaller than the inner diameter 40 of the hollow shaft 18.
  • the securing bolt 34 is rotatably mounted in the hollow shaft 18 about its main longitudinal axis 35. Such a rotation is a rolling motion 44 of the securing bolt 34 (see Fig. 2 ).
  • the securing bolt 34 is mounted in the hollow shaft 18 with so much play that it can be tilted with respect to an axis 37 of the holes 36.
  • Such a tilting 48 is a pitching movement of the securing bolt 34.
  • the coupling shaft 26 (based on the intersection 42 of the main longitudinal axes 19, 27) in every radial direction can be tilted, so tumble.
  • the coupling shaft 26 on at least one of its two end faces 30, 31 comprises a cylindrically symmetrical, convex formation 28 which is arranged concentrically to the main longitudinal axis 27 of the coupling shaft 26.
  • a (plate-shaped) securing flange 50 may be clamped between elastomeric disks 52, which are arranged concentrically on the rotor side 54.
  • the coupling shaft 26 can execute a uniform wobbling motion during rotation of the rotor 14.
  • a plurality of extensions it is also possible for a plurality of extensions to be fastened or integrally formed on the coupling shaft 26, which have circumferential directions, for example in 3, 4 or 5.
  • On the other side 31 of the coupling shaft 26 engages a bevel gear 60 of the clutch shaft 26 in a bevel gear 72 of the adjusting 32 a.
  • the teeth of the two bevel gears 60, 72 remain despite the Achswinkels 64 between the clutch shaft 26 and adjusting 32 in loose engagement.
  • the dashed lines indicate ridges of the meshing teeth of the bevel gears 60, 72.
  • the sketch also shows that sufficient clearance 66 can be provided between the coupling shaft 26 and the hollow shaft 18, so that the coupling shaft 26 remains sufficient space for the required wobbling motion.
  • the coupling shaft 26 between its two ends 30, 31 is tapered over more than w% of its axial length 39, wherein w% is at least 30%, in particular at least 60%.
  • the illustrated angle arrangement can not only result in a side view, but also from the viewpoint of every other circumferential angle of the main longitudinal axis of the rotor 14.
  • the coupling device of FIG. 4 is not part of the invention.
  • the coupling shaft 26 may also be rigidly secured to the rotor 14, if it has a sufficient bending ability while maintaining sufficient torsional strength.
  • a circular or annular cross-section of the coupling shaft 26 an increase in the bending ability is typically accompanied equally by an increase in the torsional capability.
  • a material with a suitable poisson's ratio by choosing an anisotropic material, or by anisotropic design of the coupling shaft, it is possible to adapt the ratio of flexural rigidity to torsional rigidity to specific application requirements.
  • the illustrated angle arrangement can not only result in a side view, but also from the viewpoint of every other circumferential angle of the main longitudinal axis of the rotor 14.
  • clutch shaft 26 has a servo-motor side a gear coupling component 58.
  • the curved toothing allows an angle of the coupling shaft 26 relative to a main longitudinal axis 15 of the rotor 14 and the hollow shaft 18. Independent of which allows the internal teeth 59 of the hollow shaft 18 is an axial positional adjustment of the coupling shaft 26 along the main longitudinal axis 19 of the hollow shaft 18.
  • the clutch shaft 26 of Fig. 5 and 6 also includes on the side of the adjusting gear 32, a gear coupling component 60 which engages in an internal gear of a gear drive gear 72 of the adjusting gear 32.
  • the gear coupling component 60 here has a larger diameter 69, because the gear drive gear 72 is located at a location at which a mounting screw for the adjusting gear 32 with the sprocket 74 is to be passed to the camshaft 76 during assembly.
  • the clutch shaft 26 can be pressed by means of spring force in the direction of adjusting 32.
  • the end 31 of the clutch shaft 26 facing the camshaft 76 may be supported by a self-aligning bearing in the variator 32 (for example on an intermediate gear) or alternatively against the camshaft 76.
  • the end 31 of the coupling shaft 26 may be mounted on a ball bearing 78, which has a convex outer ring 80 so that it can be slightly angled at axial offset 79 relative to the main axis 33 of the adjusting mechanism 32.
  • the coupling shaft 26 may have a flange 81 on which the ball bearing 78 is mounted.
  • the ball bearing 78 may be within a sprocket 72. It can be supported on a journal of the camshaft 76.
  • the Fig. 7 shows a perspective view of an open Verstellgetriebes 32 with the gear drive gear 72.
  • the gear drive gear 72 is designed here as a flying gear and has an internal toothing and an external toothing.
  • the gear drive gear 72 serves to drive via an (not shown in the figure) reduction gear with intermediate gears 84 an adjusting of the adjusting 32.
  • Flanges 82 on the gear drive gear 72 and on the idler gears 84 hold the gear drive gear 72 at the axis position between the idler gears 84.
  • the gear drive gear 72 is held by guide wheels 86.
  • the gear drive gear 72 should also be sufficiently fixed or supported in the axial direction. This can be achieved for example by sliding bearing surfaces or by a (not shown in the figure) ball bearings.
  • the invention provides a clutch shaft 26, an actuator 12, a camshaft variator 32 and a camshaft actuator 10 with which radial forces between the clutch and the transmission input shaft can be reduced or avoided. This is especially true in combination with a cantilevered transmission input shaft (Gear drive gear 72).
  • the space-saving design allows a reduction in the axial space requirement for the camshaft adjuster 10. Space that can be saved for the clutch of servo motor 12 with adjusting 32, allows the use of a cheaper Verstellgetriebes 32 or a more cost-effective servomotor 12th

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gear Transmission (AREA)

Description

Die Erfindung betrifft eine Kupplungswelle für einen Nockenwellensteller.The invention relates to a coupling shaft for a camshaft actuator.

Außerdem betrifft die Erfindung einen Aktor zum Stellen eines Nockenwellenverstellgetriebes.Moreover, the invention relates to an actuator for setting a camshaft variable speed gear.

Des Weiteren betrifft die Erfindung ein Nockenwellenverstellgetriebe, das im Folgenden auch mit 'Verstellgetriebe' bezeichnet wird.Furthermore, the invention relates to a camshaft adjusting, which is also referred to below as 'variable speed'.

Darüber hinaus betrifft die Erfindung einen Nockenwellenversteller für eine Brennkraftmaschine.Moreover, the invention relates to a camshaft adjuster for an internal combustion engine.

Aus DE10 2004 041 751 A1 , DE 10 2007 049 072 A1 , DE 10 2004 061 711 A1 und DE 102 48 351 A1 sind diverseOut DE10 2004 041 751 A1 . DE 10 2007 049 072 A1 . DE 10 2004 061 711 A1 and DE 102 48 351 A1 are diverse

Kupplungen zum Ausgleich einer Exzentrizität (Achsversatzes) zwischen einer Achse einer Stellwelle eines Aktors und einer Achse eines Verstellgetriebes bekannt. Diese Kupplungen üben bei entsprechendem radialem Achsversatz der entsprechenden Wellen Massenkräfte auf diese Wellen und deren Lagerungen aus. Bei Oldham-Kupplungen ist auch der große axiale Bauraumbedarf nachteilig.Couplings for compensating an eccentricity (axial offset) between an axis of a control shaft of an actuator and an axis of a variable speed known. These couplings exercise with appropriate radial axial offset of the corresponding waves inertial forces on these waves and their bearings. In Oldham couplings and the large axial space requirement is disadvantageous.

Es ist eine Aufgabe der Erfindung, eine Kupplungswelle für einen Nockenwellensteller bereitzustellen, mit der Massenkräfte auf diese Wellen und deren Lagerungen verringert werden können. Außerdem ist es eine Aufgabe der Erfindung, einen Aktor, ein Nockenwellenverstellgetriebe und einen Nockenwellenversteller mit diesem Vorteil bereitzustellen.It is an object of the invention to provide a clutch shaft for a camshaft actuator, with the mass forces can be reduced to these waves and their bearings. In addition, it is an object of the invention to provide an actuator, a camshaft variable speed and a phaser with this advantage.

Diese Aufgabe wird mit einer Kupplungswelle gelöst, welche die Merkmale des Patentanspruchs 1 umfasst. Vorteilhafte Weiterbildungen des Erfindungsgedankens sind Gegenstand der Unteransprüche.This object is achieved with a coupling shaft comprising the features of claim 1. Advantageous developments of the inventive concept are the subject of the dependent claims.

Erfindungsgemäß ist die Kupplungswelle für einen Nockenwellensteller dadurch weitergebildet, dass die Kupplungswelle an jedem ihrer beiden Enden je eine Kupplungskomponente für je eine achswinkelausgleichende Drehkupplung aufweist. Dadurch, dass die erfindungsgemäße Kupplungswelle an jedem ihrer beiden Enden eine Kupplungskomponente aufweist, ist es möglich, einen Achsversatz auszugleichen, ohne dass durch diese Maßnahme eine Herbeiführung oder Vergrößerung eines Achswinkels zwischen dem Aktor und dem Verstellgetriebe in Kauf genommen werden muss. Durch Aufteilung der Achsversatzanpassung auf zwei Kupplungen erhält der Entwickler einen zusätzlichen Freiheitsgrad, den er nutzen kann, den Achswinkel für die Krafteinleitung in den Aktor beziehungsweise in das Verstellgetriebe zu verringern. Durch Verringerung des Achswinkels für die Krafteinleitung in den Aktor beziehungsweise in das Verstellgetriebe wird eine Rotationssymmetrie der Kraftübertragung verbessert und eine Stärke der nachteiligen Massenkräfte verringert. Die Kupplungswelle kann, aber muss nicht, einstückig sein.According to the invention, the coupling shaft for a camshaft actuator is further developed in that the coupling shaft has at each of its two ends a respective coupling component for each one achschwinkelausgleichende rotary coupling. The fact that the coupling shaft according to the invention has a coupling component at each of its two ends, it is possible to compensate for an axial offset, without causing by this measure a cause or enlargement of an axis angle between the actuator and the adjustment must be accepted. By dividing the axial offset adjustment to two clutches, the developer receives an additional degree of freedom, which he can use to reduce the axial angle for the introduction of force into the actuator or into the adjusting mechanism. By reducing the axial angle for the introduction of force into the actuator or into the adjusting mechanism, a rotational symmetry of the power transmission is improved and a strength of the disadvantageous inertial forces is reduced. The clutch shaft may, but need not, be integral.

Eine (gesamte) Axiallänge der Kupplungswelle kann größer sein als w % eines maximalen Durchmessers der größeren Kupplungskomponente, wobei w % mindestens 130 %, insbesondere mindestens 150 %, beträgt.An (entire) axial length of the coupling shaft may be greater than w% of a maximum diameter of the larger coupling component, where w% is at least 130%, in particular at least 150%.

Die Kupplungswelle kann zwischen ihren beiden Enden über mehr als w % ihrer (gesamten) Axiallänge verjüngt sein, wobei w % mindestens 30 %, insbesondere mindestens 60 %, beträgt.The coupling shaft may be tapered between its two ends over more than w% of its (total) axial length, w% being at least 30%, in particular at least 60%.

Die Kupplungswelle kann auf mindestens einer ihrer beiden Stirnseiten eine zylindersymmetrische, konvexe Ausformung umfassen, die konzentrisch zur Hauptlängsachse der Kupplungswelle angeordnet ist.The coupling shaft may comprise on at least one of its two end faces a cylindrically symmetrical, convex formation which is arranged concentrically to the main longitudinal axis of the coupling shaft.

Die Kupplungswelle kann einen Flansch für ein Lager umfassen.The coupling shaft may include a flange for a bearing.

Die erste achswinkelausgleichende Drehkupplung kann einen Sicherungsbolzen oder eine Komponente einer Zahnkupplung, einer Klauenkupplung, einer Steckkupplung, einer Mitnehmerkupplung, einer Stirnzahnradkupplung, einer Tellerzahnradkupplung, einer Gelenkscheibe, einer Balgkupplung, einer Elastomerkupplung, einer Wendelkupplung, einer Federkupplung, einer Federscheibenkupplung, einer Stegkupplung, einer Ausgleichskupplung, eines Kardangetriebes oder eines Gleichlaufgelenks umfasst. Unabhängig davon kann die zweite achswinkelausgleichende Drehkupplung einen Sicherungsbolzen oder eine Komponente einer Zahnkupplung, einer Klauenkupplung, einer Steckkupplung, einer Mitnehmerkupplung, einer Stirnzahnradkupplung, einer Tellerzahnradkupplung, einer Gelenkscheibe, einer Balgkupplung, einer Elastomerkupplung, einer Wendelkupplung, einer Federkupplung, einer Federscheibenkupplung, einer Stegkupplung, einer Ausgleichskupplung, eines Kardangetriebes oder eines Gleichlaufgelenks umfassen. Die Zahnkupplungskomponente kann eine Bogenzahnkupplung umfassen. Die Zahnkupplungskomponente kann eine kugel- oder kugelabschnittförmige Grundform aufweist, auf der die Zähne der Zahnkupplungskomponente angeordnet sind.The first axis-compensating rotary joint may include a safety pin or a component of a toothed clutch, a dog clutch, a plug-in clutch, a dog clutch, a spur gear, a Tellerzahnradkupplung, a flexible disc, a Belgkupplung, an elastomeric coupling, a helical clutch, a spring clutch, a spring disc clutch, a ridge clutch, a Compensating clutch, a Kardangetriebes or a constant velocity joint comprises. Independently of this, the second angle-compensating rotary joint may comprise a safety bolt or a component of a toothed clutch, a dog clutch, a plug-in clutch, a driving clutch, a spur gear clutch, a Tellerzahnradkupplung, a flexible disc, a Belgkupplung, an elastomeric coupling, a helical clutch, a spring clutch, a spring disc clutch, a bridge coupling , a compensating coupling, a Kardangetriebes or a constant velocity joint. The toothed coupling component may comprise a curved tooth coupling. The toothed coupling component may have a spherical or ball-shaped basic shape on which the teeth of the toothed coupling component are arranged.

Erfindungsgemäß ist der Aktor dadurch weitergebildet, dass eine Kupplungswelle zum Stellen des Nockenwellenverstellgetriebes mit dem Aktor mittels einer ersten achswinkelausgleichenden Drehkupplung in einem Bereich des Aktors gekuppelt ist, der von dem Verstellgetriebe abgewandt ist. Hierdurch kann bei unverändertem Abstand zwischen Aktor und Nockwellenverstellgetriebe der Abstand zwischen dem Ort der abwinkelbaren Verbindung mit dem Rotor und dem Nockenwellenverstellgetriebe vergrößert werden, wodurch eine Verringerung des Achswinkels für die Krafteinleitung in das Verstellgetriebe erzielt, eine Rotationssymmetrie der Kraftübertragung verbessert und eine Stärke der nachteiligen Massenkräfte verringert wird.According to the invention, the actuator is further developed in that a coupling shaft for providing the Nockenwellenverstellgetriebes is coupled to the actuator by means of a first achswinkelausgleichenden rotary coupling in a region of the actuator, which faces away from the adjusting mechanism. In this way, with an unchanged distance between the actuator and Nockwellenverstellgetriebe the distance between the location of the bendable connection to the rotor and the camshaft Verstellgetriebe be increased, thereby achieving a reduction of the axis angle for the introduction of force in the variator, a rotational symmetry of the transmission improves and a strength of the adverse mass forces is reduced.

Die Kupplungswelle kann sich über mehr als 50% einer (gesamten) Axiallänge eines Rotors des Aktors erstrecken.The clutch shaft may extend over more than 50% of a (total) axial length of a rotor of the actuator.

Die Kupplungswelle kann in dem Aktor auf jedem Umfangswinkel in Nickrichtung drehbar angeordnet sein, wobei ein Nickwinkel der Kupplungswelle gegenüber einer Achse des Aktors bis mindestens 1°, insbesondere bis mindestens 2°, insbesondere bevorzugt bis mindestens 3°, betragen kann.The coupling shaft may be rotatably arranged in the actuator at any circumferential angle in the pitch direction, wherein a pitch angle of the coupling shaft with respect to an axis of the actuator to at least 1 °, in particular to at least 2 °, more preferably to at least 3 °.

Die Kupplungswelle kann in dem Rotor axial verschiebbar angeordnet sein.The coupling shaft may be arranged axially displaceable in the rotor.

Der Aktor kann eine Axiallagerkomponente zum Vorspannen der Kupplungswelle in Richtung der Hauptlängsachse der Kupplungswelle umfassen.The actuator may include a thrust bearing component for biasing the clutch shaft in the direction of the main longitudinal axis of the clutch shaft.

Die erste achswinkelausgleichende Drehkupplung zur Kopplung mit dem Rotor kann einen Sicherungsbolzen oder eine Komponente einer Zahnkupplung, einer Klauenkupplung, einer Steckkupplung, einer Mitnehmerkupplung, einer Stirnzahnradkupplung, einer Tellerzahnradkupplung, einer Gelenkscheibe, einer Balgkupplung, einer Elastomerkupplung, einer Wendelkupplung, einer Federkupplung, einer Federscheibenkupplung, einer Stegkupplung, einer Ausgleichskupplung, eines Kardangetriebes oder eines Gleichlaufgelenks umfassen.The first axle-compensating rotary coupling for coupling to the rotor may include a safety pin or a component of a toothed clutch, a dog clutch, a plug-in clutch, a dog clutch, a spur gear, a Tellerzahnradkupplung, a flexible disc, a Belgkupplung, an elastomer coupling, a helical clutch, a spring clutch, a spring disc clutch , a bridge coupling, a compensating coupling, a Kardangetriebes or a constant velocity joint.

Der Aktor kann eine erfindungsgemäße Kupplungswelle umfassen.The actuator may comprise a coupling shaft according to the invention.

Erfindungsgemäß ist das Nockenwellenverstellgetriebe dadurch weitergebildet, dass eine Innen oder Außenverzahnung eines Getriebeantriebszahnrads des Nockenwellenverstellgetriebes für den Eingriff der Zahnkupplungskomponente einer erfindungsgemäßen Kupplungswelle ausgebildet oder geeignet ist oder dass das Nockenwellenverstellgetriebe eine erfindungsgemäße Kupplungswelle umfasst.According to the invention, the camshaft adjusting mechanism is further developed in that an inner or outer toothing of a gear drive gear of the camshaft adjusting gear for the engagement of the toothed coupling component of a coupling shaft according to the invention is formed or suitable or that the camshaft adjusting a clutch shaft according to the invention comprises.

Die Zahnkupplungskomponente der Kupplungswelle kann ein fliegendes Getriebeantriebszahnrad des Nockenwellenverstellgetriebes bilden.The gear coupling component of the clutch shaft may form a flying gear drive gear of the camshaft variable speed gear.

Erfindungsgemäß ist der Nockenwellenversteller dadurch weitergebildet, dass er einen erfindungsgemäßen Aktor und/oder ein erfindungsgemäßes Nockenverstellgetriebe umfasst.According to the invention, the camshaft adjuster is further developed in that it comprises an actuator according to the invention and / or an inventive camshaft transmission.

Die Erfindung wird nachfolgend anhand eines in den schematischen Zeichnungen dargestellten Ausführungsbeispiels näher erläutert. Es zeigen:

Fig. 1
schematisch eine teilweise angeschnittene Seitenansicht einer ersten Ausführungsform eines erfindungsgemäßen Nockenwellenstellers;
Fig. 2
schematisch einen perspektivischen Seitenquerschnitt der ersten Ausführungsform des erfindungsgemäßen Nockenwellenstellers;
Fig. 3
schematisch in Seitenansicht ein Grundkonzept des erfindungsgemäßen Achsversatzausgleichs der ersten Ausführungsform;
Fig. 4
schematisch in Seitenansicht ein Grundkonzept eines Achsversatzausgleichs einer Ausführungsform, welche kein Bestandteil der Erfindung ist;
Fig. 5
schematisch eine teilweise angeschnittenen Seitenansicht eines Nockenwellenstellers mit einer zweiten Ausführungsform der erfindungsgemäßen Kupplungswelle;
Fig. 6
schematisch eine Detailansicht eines Seitenquerschnitts der zweiten Ausführungsform des erfindungsgemäßen Nockenwellenstellers; und
Fig. 7
schematisch eine perspektivische Ansicht eines geöffneten Nockenwellenverstellgetriebes mit einem fliegenden Getriebeantriebszahnrad.
The invention will be explained in more detail with reference to an embodiment shown in the schematic drawings. Show it:
Fig. 1
schematically a partially sectioned side view of a first embodiment of a camshaft actuator according to the invention;
Fig. 2
schematically a perspective side cross-section of the first embodiment of the camshaft actuator according to the invention;
Fig. 3
schematically a side view of a basic concept of the invention Achsversatzausgleichs the first embodiment;
Fig. 4
schematically in side view a basic concept of an axial offset compensation of an embodiment which is not part of the invention;
Fig. 5
schematically a partially sectioned side view of a camshaft adjuster with a second embodiment of the coupling shaft according to the invention;
Fig. 6
schematically a detailed view of a side cross section of the second embodiment of the camshaft actuator according to the invention; and
Fig. 7
schematically a perspective view of an open Nockenwellenverstellgetriebes with a flying Getriebeantriebszahnrad.

In den Figuren werden für entsprechende Komponenten jeweils dieselben Bezugszeichen verwendet. Bezugszeichenbezogene Erläuterungen gelten daher auch figurenübergreifend, sofern sich aus dem Zusammenhang nichts anderes ergibt.In the figures, the same reference numerals are used for respective components. Reference numerals related explanations therefore also apply across figures, unless otherwise stated in the context.

Der in Fig. 1 und 2 gezeigte Nockenwellensteller 10 umfasst einen Stellmotor 12 und ein Verstellgetriebe 32. Der Stellmotor 12 kann beispielsweise eine elektrische Maschine (Elektromotor), ein Hydraulikantrieb oder ein Pneumatikantrieb sein. Der Stellmotor 12 umfasst einen Rotor 14, der in zwei Rotorlagern 16 gelagert ist. Der Rotor 14 umfasst eine Hohlwelle 18. Die Hohlwelle 18 ist von einem Radialwellendichtring 20 umgeben, der dazu beiträgt, den ölgefüllten Nockenwellenraum 22 gegenüber Teilen des Stellmotors 12 abzudichten. Nockenwellenseitige Teile 26, 32 des Nockenwellenstellers 10 befindet sich typischerweise unter Motoröl 24. Eine Kupplungswelle 26 ist durch die Hohlwelle 18 hindurchgeführt und auf derjenigen Seite des Rotors 14 an dem Rotor 14 befestigt, die von dem Verstellgetriebe 32 abgewandt ist. Die Kupplungswelle 26 kann sich über mehr als 50% einer (gesamten) Axiallänge eines Rotors 14 erstrecken.The in Fig. 1 and 2 shown camshaft actuator 10 includes a servomotor 12 and an adjusting 32. The servomotor 12 may be for example an electric machine (electric motor), a hydraulic drive or a pneumatic drive. The servomotor 12 comprises a rotor 14, which is mounted in two rotor bearings 16. The rotor 14 includes a hollow shaft 18. The hollow shaft 18 is surrounded by a radial shaft seal 20, which helps to seal the oil-filled camshaft space 22 against parts of the servomotor 12. Cam shaft-side parts 26, 32 of the camshaft actuator 10 are typically located under engine oil 24. A clutch shaft 26 is passed through the hollow shaft 18 and fixed on that side of the rotor 14 to the rotor 14, which faces away from the adjusting 32. The coupling shaft 26 may extend over more than 50% of a (total) axial length of a rotor 14.

An diesem stellmotorseitigen Ende 30 ist die Kupplungswelle 26 für eine Drehmomentübertragung zu dem Verstellgetriebe 32 mittels eines Sicherungsbolzens 34 an dem Rotor 14 angelenkt. Die Kupplungswelle 26 weist an ihrem stellmotorseitigen Ende 30 eine Durchführung 25 für einen Sicherungsbolzen 34 auf. Der Sicherungsbolzen 34 ist in gegenüberliegenden Löchern 36 in der Wandung der Hohlwelle 18 gelagert. Im Bereich der Durchführung 25 für den Sicherungsbolzen 34 kann die Kupplungswelle 26 eine spindel- oder kugelförmige Verdickung 38 aufweisen, deren Außendurchmesser nur geringfügig kleiner ist als der Innendurchmesser 40 der Hohlwelle 18. Dadurch wird erreicht, dass die Kupplungswelle 26 (unabhängig von ihrer Taumelbewegung) in der Hohlwelle 18 so befestigt ist, dass am Ort des Sicherungsbolzens 34 eine Hauptlängsachse 27 der Kupplungswelle 26 einen gemeinsamen Schnittpunkt 42 mit der Hauptlängsachse 19 der Hohlwelle 18 hat.At this actuating motor end 30, the coupling shaft 26 is articulated to the rotor 14 for torque transmission to the adjusting mechanism 32 by means of a securing bolt 34. The clutch shaft 26 has at its Stellmotorseitigen end 30 a passage 25 for a safety pin 34. The securing bolt 34 is mounted in opposite holes 36 in the wall of the hollow shaft 18. In the region of the passage 25 for the securing bolt 34, the coupling shaft 26 may have a spindle-shaped or spherical thickening 38 whose outer diameter is only slightly smaller than the inner diameter 40 of the hollow shaft 18. This ensures that the coupling shaft 26 (regardless of its tumbling motion) is fixed in the hollow shaft 18 so that at the location of the securing bolt 34, a main longitudinal axis 27 of the coupling shaft 26 has a common point of intersection 42 with the main longitudinal axis 19 of the hollow shaft 18.

Der Sicherungsbolzen 34 ist in der Hohlwelle 18 um seine Hauptlängsachse 35 drehbar gelagert. Eine solche Drehung ist eine Rollbewegung 44 des Sicherungsbolzens 34 (siehe Fig. 2). Außerdem ist der Sicherungsbolzen 34 in der Hohlwelle 18 mit so viel Spiel gelagert, dass er gegenüber einer Achse 37 der Löcher 36 gekippt werden kann. Ein solches Kippen 48 ist eine Nickbewegung des Sicherungsbolzens 34. Dadurch, dass der Sicherungsbolzen 34 in der Hohlwelle 18 sowohl eine Rollbewegung 44 als auch eine Nickbewegung 48 ausführen kann, kann die Kupplungswelle 26 (bezogen auf den Schnittpunkt 42 der Hauptlängsachsen 19, 27) in jede Radialrichtung gekippt werden, also taumeln. Um die Kupplungswelle 26 in Axialrichtung zu stützen oder gegen das Verstellgetriebe 32 vorzuspannen, kann die Kupplungswelle 26 auf mindestens einer ihrer beiden Stirnseiten 30, 31 eine zylindersymmetrische, konvexe Ausformung 28 umfasst, die konzentrisch zur Hauptlängsachse 27 der Kupplungswelle 26 angeordnet ist.The securing bolt 34 is rotatably mounted in the hollow shaft 18 about its main longitudinal axis 35. Such a rotation is a rolling motion 44 of the securing bolt 34 (see Fig. 2 ). In addition, the securing bolt 34 is mounted in the hollow shaft 18 with so much play that it can be tilted with respect to an axis 37 of the holes 36. Such a tilting 48 is a pitching movement of the securing bolt 34. The fact that the securing bolt 34 in the hollow shaft 18 can perform both a rolling movement 44 and a pitching motion 48, the coupling shaft 26 (based on the intersection 42 of the main longitudinal axes 19, 27) in every radial direction can be tilted, so tumble. In order to support the coupling shaft 26 in the axial direction or to bias it against the adjusting mechanism 32, the coupling shaft 26 on at least one of its two end faces 30, 31 comprises a cylindrically symmetrical, convex formation 28 which is arranged concentrically to the main longitudinal axis 27 of the coupling shaft 26.

Wie Fig. 3 zeigt, kann ein (tellerförmiger) Sicherungsflansch 50 zwischen Elastomerscheiben 52 eingeklemmt sein, die auf der Rotorseite 54 konzentrisch angeordnet sind. Dadurch kann die Kupplungswelle 26 beim Rotieren des Rotors 14 eine gleichmäßige Taumelbewegung ausführen. Statt eines Sicherungsflansches 50 können an der Kupplungswelle 26 auch mehrere Fortsätze befestigt oder angeformt sein, die beispielsweise in 3, 4 oder 5 Umfangsrichtungen weisen. Auf der anderen Seite 31 der Kupplungswelle 26 greift ein Kegelzahnrad 60 der Kupplungswelle 26 in ein Kegelzahnrad 72 des Verstellgetriebes 32 ein. Durch die gegenseitige Selbstzentrierung der Kegelzahnräder 60, 72 und den Andruck des federgestützten Kugelauflagers 62 bleiben die Zähne der beiden Kegelzahnräder 60, 72 trotz des Achswinkels 64 zwischen Kupplungswelle 26 und Verstellgetriebe 32 in losefreiem Eingriff. Die gestrichelten Linien deuten Grate der ineinandergreifenden Zähne der Kegelzahnräder 60, 72 an. Die Skizze zeigt auch, dass zwischen der Kupplungswelle 26 und der Hohlwelle 18 ein ausreichender Spielraum 66 vorgesehen werden kann, damit der Kupplungswelle 26 genügend Freiraum für die erforderliche Taumelbewegung bleibt. Dazu kann die Kupplungswelle 26 zwischen ihren beiden Enden 30, 31 über mehr als w % ihrer Axiallänge 39 verjüngt ist, wobei w % mindestens 30 %, insbesondere mindestens 60 %, beträgt. Bei entsprechendem Achsversatz 79 kann sich die dargestellte Winkelanordnung nicht nur in Seitenansicht, sondern auch aus Sicht jedes anderen Umfangswinkels der Hauptlängsachse des Rotors 14 ergeben.As Fig. 3 shows, a (plate-shaped) securing flange 50 may be clamped between elastomeric disks 52, which are arranged concentrically on the rotor side 54. As a result, the coupling shaft 26 can execute a uniform wobbling motion during rotation of the rotor 14. Instead of a securing flange 50, it is also possible for a plurality of extensions to be fastened or integrally formed on the coupling shaft 26, which have circumferential directions, for example in 3, 4 or 5. On the other side 31 of the coupling shaft 26 engages a bevel gear 60 of the clutch shaft 26 in a bevel gear 72 of the adjusting 32 a. Due to the mutual self-centering of the bevel gears 60, 72 and the pressure of the spring-supported ball bearing 62, the teeth of the two bevel gears 60, 72 remain despite the Achswinkels 64 between the clutch shaft 26 and adjusting 32 in loose engagement. The dashed lines indicate ridges of the meshing teeth of the bevel gears 60, 72. The sketch also shows that sufficient clearance 66 can be provided between the coupling shaft 26 and the hollow shaft 18, so that the coupling shaft 26 remains sufficient space for the required wobbling motion. For this purpose, the coupling shaft 26 between its two ends 30, 31 is tapered over more than w% of its axial length 39, wherein w% is at least 30%, in particular at least 60%. With a corresponding axial offset 79, the illustrated angle arrangement can not only result in a side view, but also from the viewpoint of every other circumferential angle of the main longitudinal axis of the rotor 14.

Die Kupplungsvorrichtung der Figur 4 ist kein Teil der Erfindung. Wie Fig. 4 zeigt, kann die Kupplungswelle 26 auch starr an dem Rotor 14 befestigt sein, wenn sie eine ausreichende Biegefähigkeit bei gleichzeitig ausreichender Torsionsfestigkeit aufweist. Bei einem kreis- oder ringförmigen Querschnitt der Kupplungswelle 26 geht eine Erhöhung der Biegefähigkeit typischerweise gleichermaßen mit einer Erhöhung der Torsionsfähigkeit einher. Je nach Anwendung kann es auch sein, dass (beispielsweise aufgrund einer Untersetzung) eine Verdrillung der biegsamen Kupplungswelle 26 nicht stört. Oder es kann durch Wahl eines Materials mit einer geeigneten Querkontraktionszahl (poisson's ratio), durch Wahl eines anisotropen Materials, oder durch einen anisotropischen Aufbau der Kupplungswelle versucht werden, das Verhältnis von Biegesteifigkeit zu Torsionssteifigkeit an konkrete Anwendungsanforderungen anzupassen. Bei entsprechendem Achsversatz 79 kann sich die dargestellte Winkelanordnung nicht nur in Seitenansicht, sondern auch aus Sicht jedes anderen Umfangswinkels der Hauptlängsachse des Rotors 14 ergeben.The coupling device of FIG. 4 is not part of the invention. As Fig. 4 shows, the coupling shaft 26 may also be rigidly secured to the rotor 14, if it has a sufficient bending ability while maintaining sufficient torsional strength. With a circular or annular cross-section of the coupling shaft 26, an increase in the bending ability is typically accompanied equally by an increase in the torsional capability. Depending on the application, it may also be that (for example, due to a reduction), a twist of the flexible coupling shaft 26 does not interfere. Or, by choosing a material with a suitable poisson's ratio, by choosing an anisotropic material, or by anisotropic design of the coupling shaft, it is possible to adapt the ratio of flexural rigidity to torsional rigidity to specific application requirements. With a corresponding axial offset 79, the illustrated angle arrangement can not only result in a side view, but also from the viewpoint of every other circumferential angle of the main longitudinal axis of the rotor 14.

Die in Fig. 5 und 6 gezeigte Kupplungswelle 26 weist stellmotorseitig eine Bogenzahnkupplungskomponente 58 auf. Die Bogenverzahnung erlaubt ein Anwinkeln der Kupplungswelle 26 gegenüber einer Hauptlängsachse 15 des Rotors 14 und der Hohlwelle 18. Unabhängig davon erlaubt die Innenverzahnung 59 der Hohlwelle 18 eine axiale Positionsanpassung der Kupplungswelle 26 entlang der Hauptlängsachse 19 der Hohlwelle 18. Die Kupplungswelle 26 der Fig. 5 und 6 umfasst auch auf der Seite des Verstellgetriebes 32 eine Bogenzahnkupplungskomponente 60, die in einen Innenzahnkranz eines Getriebenantriebszahnrads 72 des Verstellgetriebes 32 eingreift. Die Bogenzahnkupplungskomponente 60 hat hier einen größeren Durchmesser 69, weil sich das Getriebenantriebszahnrad 72 an einer Stelle befindet, an der bei der Montage eine Befestigungsschraube für das Verstellgetriebe 32 mit dem Kettenrad 74 an der Nockenwelle 76 hindurchzuführen ist.In the Fig. 5 and 6 shown clutch shaft 26 has a servo-motor side a gear coupling component 58. The curved toothing allows an angle of the coupling shaft 26 relative to a main longitudinal axis 15 of the rotor 14 and the hollow shaft 18. Independent of which allows the internal teeth 59 of the hollow shaft 18 is an axial positional adjustment of the coupling shaft 26 along the main longitudinal axis 19 of the hollow shaft 18. The clutch shaft 26 of Fig. 5 and 6 Also includes on the side of the adjusting gear 32, a gear coupling component 60 which engages in an internal gear of a gear drive gear 72 of the adjusting gear 32. The gear coupling component 60 here has a larger diameter 69, because the gear drive gear 72 is located at a location at which a mounting screw for the adjusting gear 32 with the sprocket 74 is to be passed to the camshaft 76 during assembly.

Wie schon zu Figur 3 erläutert, kann auch bei der zweiten Ausführungsform die Kupplungswelle 26 mittels Federkraft in Richtung Verstellgetriebe 32 gedrückt werden. Das zur Nockenwelle 76 zeigende Ende 31 der Kupplungswelle 26 kann durch eine Pendellagerung in dem Verstellgetriebe 32 (beispielsweise auf einem Zwischenzahnrad) oder alternativ gegen die Nockenwelle 76 abgestützt sein. Das Ende 31 der Kupplungswelle 26 kann auf einem Kugellager 78 gelagert sein, das einen balligen Außenring 80 aufweist, damit es bei Achsversatz 79 gegenüber der Hauptachse 33 des Verstellgetriebes 32 etwas angewinkelt werden kann. Die Kupplungswelle 26 kann einen Flansch 81 aufweisen, auf dem das Kugellager 78 befestigt ist. Das Kugellager 78 kann innerhalb eines Zahnkranzes 72 liegen. Es kann sich auf einem Zapfen der Nockenwelle 76 abstützen.As already too FIG. 3 explained, also in the second embodiment, the clutch shaft 26 can be pressed by means of spring force in the direction of adjusting 32. The end 31 of the clutch shaft 26 facing the camshaft 76 may be supported by a self-aligning bearing in the variator 32 (for example on an intermediate gear) or alternatively against the camshaft 76. The end 31 of the coupling shaft 26 may be mounted on a ball bearing 78, which has a convex outer ring 80 so that it can be slightly angled at axial offset 79 relative to the main axis 33 of the adjusting mechanism 32. The coupling shaft 26 may have a flange 81 on which the ball bearing 78 is mounted. The ball bearing 78 may be within a sprocket 72. It can be supported on a journal of the camshaft 76.

Die Fig. 7 zeigt eine perspektivische Ansicht eines geöffneten Verstellgetriebes 32 mit dem Getriebenantriebszahnrad 72. Das Getriebenantriebszahnrad 72 ist hier als fliegendes Zahnrad ausgeführt und weist eine Innenverzahnung und eine Außenverzahnung auf. Das Getriebenantriebszahnrad 72 dient dazu, über eine (in der Figur nicht dargestellte) Untersetzung mit Zwischenzahnrädern 84 eine Verstellwelle des Verstellgetriebes 32 anzutreiben. Spurkränze 82 am Getriebeantriebszahnrad 72 und an den Zwischenzahnrädern 84 halten das Getriebeantriebszahnrad 72 auf Achsposition zwischen den Zwischenzahnrädern 84. Bezüglich der zur Achsverbindung der Zwischenzahnräder 84 senkrechten Richtung wird das Getriebeantriebszahnrad 72 durch Führungsräder 86 gehalten. Unabhängig davon sollte das Getriebeantriebszahnrad 72 auch in axialer Richtung ausreichend fixiert oder gelagert sein. Dies kann beispielsweise durch Gleitlagerflächen oder durch ein (in der Figur nicht dargestelltes) Kugellager erreicht werden.The Fig. 7 shows a perspective view of an open Verstellgetriebes 32 with the gear drive gear 72. The gear drive gear 72 is designed here as a flying gear and has an internal toothing and an external toothing. The gear drive gear 72 serves to drive via an (not shown in the figure) reduction gear with intermediate gears 84 an adjusting of the adjusting 32. Flanges 82 on the gear drive gear 72 and on the idler gears 84 hold the gear drive gear 72 at the axis position between the idler gears 84. Regarding the direction perpendicular to the axle connection of the idler gear 84, the gear drive gear 72 is held by guide wheels 86. Regardless, the gear drive gear 72 should also be sufficiently fixed or supported in the axial direction. This can be achieved for example by sliding bearing surfaces or by a (not shown in the figure) ball bearings.

Zusammengefasst wird mit der Erfindung eine Kupplungswelle 26, ein Aktor 12, ein Nockenwellenverstellgetriebe 32 und ein Nockenwellensteller 10 bereitgestellt, mit der bzw. mit dem radiale Kräfte zwischen der Kupplung und der Getriebeeingangswelle verringert oder vermieden werden können. Dies gilt insbesondere in Kombination mit einer fliegend gelagerten Getriebeeingangswelle (Getriebeantriebszahnrad 72). Unabhängig davon ermöglicht die platzsparende Bauweise eine Verringerung des axialen Bauraumbedarfs für den Nockenwellensteller 10. Bauraum, der für die Kupplung von Stellmotor 12 mit Verstellgetriebe 32 eingespart werden kann, erlaubt die Verwendung eines kostengünstigeren Verstellgetriebes 32 oder eines kostengünstigeren Stellmotors 12.In summary, the invention provides a clutch shaft 26, an actuator 12, a camshaft variator 32 and a camshaft actuator 10 with which radial forces between the clutch and the transmission input shaft can be reduced or avoided. This is especially true in combination with a cantilevered transmission input shaft (Gear drive gear 72). Regardless, the space-saving design allows a reduction in the axial space requirement for the camshaft adjuster 10. Space that can be saved for the clutch of servo motor 12 with adjusting 32, allows the use of a cheaper Verstellgetriebes 32 or a more cost-effective servomotor 12th

Bezugszeichen:Reference numerals:

1010
Nockenwellenstellercamshaft actuator
1212
Stellmotorservomotor
1414
Rotorrotor
1515
Hauptlängsachse des Rotors 14Main longitudinal axis of the rotor 14
1616
Rotorlagerrotor bearing
1818
Hohlwellehollow shaft
1919
Hauptlängsachse der Hohlwelle 18Main longitudinal axis of the hollow shaft 18th
2020
RadialwellendichtungRadial shaft seal
2222
Nockenwellenraumcamshaft chamber
2323
Axiallänge des Rotors 14Axial length of the rotor 14
2424
MotorölEngine oil
2525
Durchführung für SicherungsbolzenBushing for safety bolts
2626
Kupplungswelleclutch shaft
2727
Hauptlängsachse der Kupplungswelle 26Main longitudinal axis of the coupling shaft 26
2828
konvexe Ausformung der Kupplungswelle 26convex shape of the coupling shaft 26
3030
stellmotorseitiges Ende der Kupplungswelle 26Stellmotorseitiges end of the clutch shaft 26th
3131
verstellgetriebeseitiges Ende der Kupplungswelle 26Verstellgetriebeseitiges end of the coupling shaft 26th
3232
Verstellgetriebevariator
3333
Hauptachse des Verstellgetriebes 32Main axis of the adjusting 32th
3434
Sicherungsbolzensafety bolt
3535
Hauptlängsachse des Sicherungsbolzens 34Main longitudinal axis of the securing bolt 34
3636
Löcher in der Wandung der Hohlwelle 18Holes in the wall of the hollow shaft 18th
3737
Achse der Löcher 36Axis of the holes 36
3838
spindel- oder kugelförmige Verdickung der Kupplungswelle 26Spindle or spherical thickening of the coupling shaft 26th
3939
Axiallänge der Kupplungswelle 26Axial length of the coupling shaft 26
4040
Innendurchmesser der Hohlwelle 18Inner diameter of the hollow shaft 18th
4242
Schnittpunkt der Hauptlängsachsen 19 und 27Intersection of the main longitudinal axes 19 and 27
4444
Rollbewegung des Sicherungsbolzens 34Rolling movement of the securing bolt 34
4848
Nickbewegung des Sicherungsbolzens 34Nick movement of the locking bolt 34th
5050
Sicherungsflanschsecuring flange
5252
Elastomerscheibenelastomer discs
5454
Rotorseiterotor side
5656
Sicherungsflanschsecuring flange
5858
stellmotorseitige Bogenzahnkupplungskomponente der Kupplungswelle 26Engine-side gear coupling component of the clutch shaft 26th
5959
Innenverzahnung der Hohlwelle 18Internal toothing of the hollow shaft 18th
6060
verstellgetriebeseitige Bogenzahnkupplungskomponente der Kupplungswelle 26Verstellgetriebeseitige gear coupling component of the coupling shaft 26th
6262
federgestütztes Kugelauflagerspring-supported ball bearing
6464
AchswinkelAxis angle
6666
Spielraum zwischen Kupplungswelle 26 und Wandung der Hohlwelle 18Clearance between coupling shaft 26 and wall of the hollow shaft 18th
6969
Durchmesser der Bogenzahnkupplungskomponente 60Diameter of the gear coupling component 60
7272
Getriebeantriebszahnrad des Verstellgetriebes 32Gear drive gear of the variable speed gear 32
7474
KettenradSprocket
7676
Nockenwellecamshaft
7878
Kugellagerball-bearing
7979
Achsversatzaxial offset
8080
Außenring des Kugellagers 78Outer ring of the ball bearing 78
8181
Flansch der Kupplungswelle 26Flange of the coupling shaft 26
8282
Spurkränze am Getriebeantriebszahnrad 72Flanges on the gear drive gear 72nd
8484
Zwischenzahnradintermediate gear
8686
Führungsräderguide wheels

Claims (14)

  1. Coupling shaft (26) for a camshaft adjuster (10) which comprises an actuating motor (12), with a hollow shaft (18) which is contained in its rotor (14), and an adjusting mechanism (32), the said coupling shaft (26) being rigid, and the said coupling shaft (26) which is guided through the hollow shaft (18) having in each case one coupling component (58, 60) at each of its two ends (30, 31) and performing a uniform tumbling movement in the hollow shaft (14), characterized in that each coupling component (58, 60) is configured as a rotary coupling (18, 58, 60, 72) for axis angle compensation with respect to both the rotor (14) and the adjuster (32).
  2. Coupling shaft (26) according to the preceding claim, characterized in that an axial length (39) of the coupling shaft (26) is greater than w % of a maximum diameter (69) of the larger coupling component (58, 60), w % being at least 130%, in particular at least 150%.
  3. Coupling shaft (26) according to either of the preceding claims, characterized in that the coupling shaft (26) is tapered between its two ends (30, 31) over more than w % of its axial length (39), w % being at least 30%, in particular at least 60%.
  4. Coupling shaft (26) according to one of the preceding claims, characterized in that the coupling shaft (26) comprises, on at least one of its two end sides, a cylindrically symmetrical, convex shaped-out formation (28) which is arranged concentrically with respect to the main longitudinal axis (27) of the coupling shaft (26).
  5. Coupling shaft (26) according to one of the preceding claims, characterized in that the coupling shaft (26) comprises a flange for a bearing (78).
  6. Coupling shaft (26) according to Claim 1, characterized in that the first axis angle-compensating rotary coupling (18, 58) is an embodiment from the following list: a securing pin (34) or a component of a tooth coupling, a claw coupling, a plug-in coupling, a driver coupling, a spur gear coupling, a ring gearwheel coupling, a flexible disc, a bellow coupling, an elastomer coupling, a helical coupling, a spring coupling, a disc spring coupling, a web coupling, a compensating coupling, a cardan mechanism or a constant velocity joint, and/or in that the second axis angle-compensating rotary coupling is an embodiment from the following list: a securing pin or a component of a tooth coupling, a claw coupling, a plug-in coupling, a driver coupling, a spur gear coupling, a ring gearwheel coupling, a flexible disc, a bellow coupling, an elastomer coupling, a helical coupling, a spring coupling, a disc spring coupling, a web coupling, a compensating coupling, a cardan mechanism or a constant velocity joint.
  7. Actuator (12) for actuating an adjusting mechanism (32) of a camshaft adjuster with a coupling shaft (26) according to Claims 1 to 6, characterized in that a coupling shaft (26) for actuating the camshaft adjusting mechanism (32) is coupled to the actuator (12) by means of a first axis angle-compensating rotary coupling (18, 58) in a region of the actuator (12) which is remote from the adjusting mechanism (32).
  8. Actuator (12) according to Claim 7, characterized in that the coupling shaft (26) extends over more than 50% of an axial length (23) of a rotor (14) of the actuator (12).
  9. Actuator (12) according to either of Claims 7 and 8, characterized in that the coupling shaft (26) is arranged in the actuator (12) such that it can be rotated in the tilting direction at every circumferential angle, it being possible for a tilting angle (44) of the coupling shaft (26) with respect to an axis (19) of the actuator (12) to be up to 1°, in particular up to at least 2°, in particular preferably up to at least 3°.
  10. Actuator (12) according to one of Claims 7 to 9, characterized in that the coupling shaft (26) is arranged axially displaceably in the rotor (14).
  11. Actuator (12) according to one of Claims 7 to 10, characterized in that the actuator (12) comprises an axial bearing component (62) for prestressing the coupling shaft (26) in the direction of a main longitudinal axis (27) of the coupling shaft (26).
  12. Actuator (12) according to one of Claims 7 to 11, characterized in that, for coupling to the rotor (14), the first axis angle-compensating rotary coupling (18, 58) comprises a securing pin (26) or a component (58) of a tooth coupling (58, 18), a claw coupling, a plug-in coupling, a driver coupling, a spur gear coupling, a ring gearwheel coupling, a flexible disc, a bellow coupling, an elastomer coupling, a helical coupling, a spring coupling, a disc spring coupling, a web coupling, a compensating coupling, a cardan mechanism or a constant velocity joint.
  13. Adjusting mechanism (32) for a camshaft adjuster with a coupling shaft (26) according to Claims 1 to 6, characterized in that an internal or external toothing system of a mechanism drive gearwheel (72) of the adjusting mechanism (32) is configured or suitable for the engagement of the tooth coupling component (60) of a coupling shaft (26).
  14. Adjusting mechanism (32) according to Claim 13, characterized in that the tooth coupling component (60) of the coupling shaft (26) forms a floating mechanism drive gearwheel (72) of the adjusting mechanism (32).
EP12167002.0A 2011-06-03 2012-05-07 Coupling shaft, actuator, cam shaft adjustment drive and cam shaft adjuster Not-in-force EP2530260B1 (en)

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DE102011103495A DE102011103495A1 (en) 2011-06-03 2011-06-03 Clutch shaft, actuator, camshaft variable speed gearbox and camshaft positioner

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EP2530260B1 true EP2530260B1 (en) 2016-01-13

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DE102016205742A1 (en) 2016-04-07 2017-10-12 Schaeffler Technologies AG & Co. KG Electric adjusting device

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DE102014217155B3 (en) 2014-08-28 2015-12-03 Schaeffler Technologies AG & Co. KG Camshaft adjuster with two ball joints
EP3578769B1 (en) * 2018-06-01 2024-06-12 Ovalo GmbH Adjusting device, in particular camshaft adjuster
DE102019118779A1 (en) * 2019-07-11 2021-01-14 Schaeffler Technologies AG & Co. KG Adjusting device

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US3959987A (en) * 1974-05-08 1976-06-01 Subsea Equipment Associates Limited Self-engaging and aligning shaft coupling
US3955378A (en) * 1974-07-16 1976-05-11 Allonca Manuel J Non-friction coupling system
JPH0788858B2 (en) * 1989-08-22 1995-09-27 新日本ツール株式会社 Constant velocity universal shaft coupling
ATE210243T1 (en) * 1997-09-19 2001-12-15 Tcg Unitech Ag DEVICE FOR ADJUSTING THE CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE
ATE241093T1 (en) * 1999-03-24 2003-06-15 Fev Motorentech Gmbh COUPLING ELEMENT FOR CONNECTING TWO AXIS-PARALLEL SHAFTS ARRANGED ON THE SAME AXIS, BEHIND EACH OTHER AND AT A TRANSVERSAL DISTANCE FROM EACH OTHER
DE10248351A1 (en) 2002-10-17 2004-04-29 Ina-Schaeffler Kg Electrically driven camshaft adjuster
DE102004041751B4 (en) 2004-08-28 2020-01-16 Schaeffler Technologies AG & Co. KG Camshaft adjuster with a coupling between an actuating shaft and an adjusting gear
DE102004061711A1 (en) * 2004-12-22 2006-07-06 Daimlerchrysler Ag Adjuster for relative rotating position of camshaft opposite to crankshaft of internal combustion engine has compensating element, which is formed as single piece or is firmly connected with inlet of adjustable mechanism
DE102005018956A1 (en) * 2005-04-23 2006-11-23 Schaeffler Kg Device for adjusting the camshaft of an internal combustion engine
DE102007049072B4 (en) 2007-10-12 2020-06-18 Schaeffler Technologies AG & Co. KG Phase adjuster for an internal combustion engine with an Oldham clutch

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016205742A1 (en) 2016-04-07 2017-10-12 Schaeffler Technologies AG & Co. KG Electric adjusting device

Also Published As

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US20120309571A1 (en) 2012-12-06
EP2530260A1 (en) 2012-12-05
JP2012251660A (en) 2012-12-20
JP5419050B2 (en) 2014-02-19
US8919308B2 (en) 2014-12-30
DE102011103495A1 (en) 2012-12-06

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