EP2565402B1 - Camshaft adjuster - Google Patents

Camshaft adjuster Download PDF

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Publication number
EP2565402B1
EP2565402B1 EP12168785.9A EP12168785A EP2565402B1 EP 2565402 B1 EP2565402 B1 EP 2565402B1 EP 12168785 A EP12168785 A EP 12168785A EP 2565402 B1 EP2565402 B1 EP 2565402B1
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EP
European Patent Office
Prior art keywords
spring
spacer element
camshaft adjuster
spring cover
spacer
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
EP12168785.9A
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German (de)
French (fr)
Other versions
EP2565402A1 (en
Inventor
Sven Weisser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2565402A1 publication Critical patent/EP2565402A1/en
Application granted granted Critical
Publication of EP2565402B1 publication Critical patent/EP2565402B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/06—Camshaft drives characterised by their transmission means the camshaft being driven by gear wheels

Definitions

  • the invention relates to a camshaft adjuster.
  • Camshaft adjusters are used in internal combustion engines for varying the timing of the combustion chamber valves in order to make the phase relation between crankshaft and camshaft in a defined angular range, between a maximum early and a maximum late position, variable. Adjusting the timing to the current load and speed reduces fuel consumption and emissions.
  • camshaft adjuster are integrated into a drive train, via which a torque is transmitted from the crankshaft to the camshaft.
  • This drive train can be realized for example as a belt, chain or gear drive.
  • the output element and the drive element form one or more pairs of mutually acting pressure chambers, which can be acted upon by oil pressure.
  • Drive element and output element are arranged coaxially. By filling and emptying individual pressure chambers, a relative movement between the drive element and output element is generated.
  • the rotationally acting on between the drive element and the output element spring urges the drive element relative to the output element in an advantageous direction. This advantage direction can be the same or opposite to the direction of rotation.
  • a common type of hydraulic phaser is the vane phaser.
  • Vane adjusters comprise a stator, a rotor and a drive element. The rotor is usually rotatably connected to the camshaft and forms the output element.
  • stator and the drive element are also rotatably connected to each other and are possibly also integrally formed.
  • the rotor is coaxial to the stator and inside the stator.
  • the vane cell adjusters have various sealing lids. Stator, drive element and sealing cover are secured by several screw connections.
  • a displacement element is axially displaced via oil pressure, which generates a helical gear teeth relative rotation between a drive element and an output element.
  • camshaft adjuster Another design of a camshaft adjuster is the electromechanical camshaft adjuster having a three-shaft gear (for example, a planetary gear). One of the shafts forms the drive element and a second shaft forms the output element. About the third wave, the system by means of an adjusting device, such as an electric motor or a brake, rotational energy supplied or removed from the system. In this case, a spring can likewise be arranged such that the drive element and the driven element assist or guide back their relative rotation.
  • an adjusting device such as an electric motor or a brake
  • the DE 10 2006 002 993 A1 discloses a camshaft adjuster, wherein the spring element is arranged on the camshaft-facing side of the camshaft adjuster.
  • the spring element is covered by a spring cover. The cover secures the spring element in the axial direction and protects against external influences.
  • the DE 10 2008 051 755 A1 discloses a phaser having a spring element with one end of the spring element mounted on a pin which is bolted to a disk.
  • a cup-shaped spring lid encapsulates the spring element with this disc and protects against external influences.
  • the object of the invention is to provide a camshaft adjuster, which has a low-friction and reliable spring safety.
  • the reduction of the axial play of the spring is effected by a spacer element of the spring cover in the region of the spring end of the spring.
  • there remains enough axial space for the windings of the spring which have a deviation from their ideal extent in the radial direction during operation of the camshaft adjuster and due to manufacturing tolerances.
  • a collision of the windings of the spring is avoided with a peripheral member, which increases the life of the spring and the friction is reduced during operation.
  • the invention provides the advantage that manufacturing tolerances with respect to the radial extension direction of the turns can be coarser and thus more economical. This advantage of coarse tolerance can also be achieved in the peripheral components, e.g. at the spring cover.
  • the spacer element is formed as a local collection in one piece with the spring cover.
  • a survey can be produced by embossing, deep drawing or milling.
  • a local education is advantageous so that targeted the areas of the spring are secured in the axial direction of the spring cover, which are subject to a minimum relative movement between the spring and a peripheral component during operation. This minimizes friction and wear and increases the life of the spring.
  • the spacer element is formed separately from the spring cover.
  • the component separation between the spring cover and the spacer element as an insert advantageously allows the targeted use of materials for certain functions.
  • the spring cover may be made of a material that specifically withstands environmental influences and the spacer element made of a wear-resistant and / or higher quality material.
  • the spring cover with the spacer element material form and / or non-positively connected.
  • a cohesive connection is provided, alternatively also in combination with a positive or non-positive connection, wherein the spacer element is embedded in the spring cover, glued, welded or soldered.
  • Positive and non-positive connections equally position the spacer reliably with the spring cover at the designated function point of the axial abutment of the spring end with the spacer element.
  • the spring cover is formed of sheet metal or plastic.
  • Forming a spring cover made of sheet metal in a thin-walled pot shape is advantageous because of the low weight and the nevertheless high rigidity.
  • a design of the spring cover made of plastic is preferably used when the economy is given to sheet metal and no high temperature differences in operation at the location of the spring cover are to be expected or the thermal shock resistance of the plastic is sufficiently given.
  • the spacer element has a coating.
  • a coating reduces the wear and the weight in the formation of the spacer element as a basic carrier with an economical material, e.g. Plastic.
  • a plurality of distributed in the circumferential direction spacer elements are provided.
  • a distribution of several spacer elements is advantageous if the load of a single spacer element is too high and this would lead to failure.
  • the distribution in the circumferential direction is preferably to be arranged outside the resilient windings. Distributed in the circumferential direction spacers may be arranged on different pitch circles and / or in different angular positions.
  • the spacer element is arranged in the region of the bearing of the spring end. A fixation of the spring ends in the axial direction on the bearing avoids compulsion in the axial direction in the region of the resilient turns.
  • the spacer extends around the storage.
  • This transfer can be partial or complete.
  • the storage is usually given by a pin or other cylindrical element.
  • the Umragung also star-shaped, be designed with the storage as a center.
  • the Umragung has an exemption in the form of the cross section of the storage, so that longer trained bearing pin can partially protrude into the spring cover. A protrusion of the spring cover by the bearing pin is conceivable.
  • the inventive arrangement of the spacer element, the friction between the spring and the spring cover, or other peripheral components is avoided. This reduces wear and increases service life.
  • the resilient in operation turns of the spring have enough axial space to avoid contact with peripheral components.
  • the bearing surface of the spring ends of the spring remains on the bearing obtained at the same time, or can be advantageously increased by the invention.
  • Fig. 1 shows a section of a camshaft adjuster 1.
  • the camshaft adjuster 1 has a drive element 2, an output element 3, a spring 4 and a spring cover 5 on.
  • the drive element 2 and the output element 3 are arranged rotatable relative to each other.
  • the relative rotation in the circumferential direction 10 of the camshaft adjuster 1 can be done, for example, by filling pressure chambers with hydraulic fluid, wherein the pressure chambers between the drive element 2 and output element 3 are formed.
  • the spring 4 braces the drive element 2 and driven element 3 relative to each other in a circumferential direction 10.
  • the bias provides for a relative rotation between the drive element 2 and driven element 3. So that the spring 4 is protected from external influences, this is at least partially covered by a spring cover 5 or encapsulated. Further ensures the operation of the spring cover 5, the spring 4 in the axial direction 8 and prevents slippage of their spring ends 7 of the bearing 11.
  • the spring 4 is formed as a spiral spring whose resilient turns extend predominantly perpen
  • the drive element 2 has in one piece or separately a not shown toothing for a timing chain or a belt.
  • the output element 3 is rotatably connected to a camshaft, not shown.
  • the spring cover 5 has a spacer element 6 which is in contact with the spring end 7 of the spring 4.
  • the spacer element 6 is formed integrally with the spring cover 5 and rises in the axial direction 8 from the end face 12 of the spring cover 5 out.
  • the bearing 11 is designed as a bearing journal 13 of a screw 14 of the camshaft adjuster 1.
  • the outer diameter of the lateral surface 15 of the bearing journal 13 is constant in the axial direction 8.
  • the spacer element 6 has a material recess 16, wherein a lateral surface 17 of the material recess 16 is larger than the diameter of the lateral surface 15 of the bearing journal 13.
  • the spacer element 6 and its material recess 16 may be formed circumferentially 10 of the camshaft adjuster 1 partially or completely circumferentially.
  • Fig. 2 shows a first embodiment of a spacer element 6.
  • the spacer element 6 is formed as a circular disk-shaped, local elevation 9 of the spring cover 5. This local survey 9 is largely aligned with the storage 11 oriented. The local elevation 9 minimizes the contact with the spring end 7 to the area around the bearing 11.
  • Fig. 3 shows a second embodiment of a spacer element 6.
  • the spacer element 6 is formed as a pattern of a plurality of individual elevations 19.
  • the individual elevations 19 are arranged in a star shape around an imaginary axial extension of the lateral surface 15 of the bearing journal 13. The distribution of the individual elevations 19 are largely evenly spaced from each other.
  • Fig. 4 shows a third embodiment of a spacer element 6.
  • the spacer element 6 is formed as a pattern of a plurality of individual elevations 19.
  • the individual elevations 19 are oriented to each other rectified. A distance between the individual elevations 19 leaves room for an imaginary extension of the lateral surface 15 of the bearing journal thirteenth
  • Fig. 5 shows a section of a spring cover 5 with a spacer element 6.
  • the spacer element 6 is formed integrally from the spring cover 5.
  • the spring cover 5 and the spacer element 6 have largely the same wall thickness.
  • the spacer element 6 has a material recess 16 with a lateral surface 17, which extends over the entire wall thickness. This space can be penetrated by a storage 11.
  • An offset A of the spacer element 6 from the spring cover 5 in the axial direction 8 limits the axial spring space 20.

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Nockenwellenversteller.The invention relates to a camshaft adjuster.

Hintergrund der ErfindungBackground of the invention

Nockenwellenversteller werden in Verbrennungsmotoren zur Variation der Steuerzeiten der Brennraumventile eingesetzt, um die Phasenrelation zwischen Kurbelwelle und Nockenwelle in einem definierten Winkelbereich, zwischen einer maximalen Früh- und einer maximalen Spätposition, variabel gestalten zu können. Die Anpassung der Steuerzeiten an die aktuelle Last und Drehzahl senkt den Verbrauch und die Emissionen. Zu diesem Zweck sind Nockenwellenversteller in einen Antriebsstrang integriert, über welche ein Drehmoment von der Kurbelwelle auf die Nockenwelle übertragen wird. Dieser Antriebsstrang kann beispielsweise als Riemen-, Ketten- oder Zahnradtrieb realisiert sein.Camshaft adjusters are used in internal combustion engines for varying the timing of the combustion chamber valves in order to make the phase relation between crankshaft and camshaft in a defined angular range, between a maximum early and a maximum late position, variable. Adjusting the timing to the current load and speed reduces fuel consumption and emissions. For this purpose, camshaft adjuster are integrated into a drive train, via which a torque is transmitted from the crankshaft to the camshaft. This drive train can be realized for example as a belt, chain or gear drive.

Bei einem hydraulischen Nockenwellenversteller bilden das Abtriebselement und das Antriebselement ein oder mehrere Paare gegeneinander wirkende Druckkammern aus, welche mit Öldruck beaufschlagbar sind. Antriebselement und Abtriebselement sind hierbei koaxial angeordnet. Durch die Befüllung und Entleerung einzelner Druckkammern wird eine Relativbewegung zwischen Antriebselement und Abtriebselement erzeugt. Die auf zwischen dem Antriebselement und dem Abtriebselement rotativ wirkende Feder drängt das Antriebselement gegenüber dem Abtriebselement in eine Vorteilsrichtung. Diese Vorteilsrichtung kann gleichläufig oder gegenläufig zu der Verdrehrichtung sein. Eine verbreitete Bauart der hydraulischen Nockenwellenversteller ist der Flügelzellenversteller. Flügelzellenversteller weisen einen Stator, einen Rotor und ein Antriebselement auf. Der Rotor ist meist mit der Nockenwelle drehfest verbunden und bildet das Abtriebselement. Der Stator und das Antriebselement werden ebenfalls untereinander drehfest verbunden und sind ggf. auch einteilig ausgebildet. Dabei befindet sich der Rotor koaxial zum Stator und innerhalb des Stators. Rotor und Stator prägen mit deren, sich radial erstreckenden Flügeln, gegensätzlich wirkende Ölkammern aus, welche durch Öldruck beaufschlagbar sind und eine Relativbewegung zwischen Stator und Rotor ermöglichen. Weiterhin weisen die Flügelzellenversteller diverse Abdichtdeckel auf. Stator, Antriebselement und Abdichtdeckel werden über mehrere Schraubenverbindungen gesichert.In a hydraulic camshaft adjuster, the output element and the drive element form one or more pairs of mutually acting pressure chambers, which can be acted upon by oil pressure. Drive element and output element are arranged coaxially. By filling and emptying individual pressure chambers, a relative movement between the drive element and output element is generated. The rotationally acting on between the drive element and the output element spring urges the drive element relative to the output element in an advantageous direction. This advantage direction can be the same or opposite to the direction of rotation. A common type of hydraulic phaser is the vane phaser. Vane adjusters comprise a stator, a rotor and a drive element. The rotor is usually rotatably connected to the camshaft and forms the output element. The stator and the drive element are also rotatably connected to each other and are possibly also integrally formed. The rotor is coaxial to the stator and inside the stator. Rotor and stator shape with their radially extending wings, oppositely acting oil chambers, which can be acted upon by oil pressure and allow relative movement between the stator and rotor. Furthermore, the vane cell adjusters have various sealing lids. Stator, drive element and sealing cover are secured by several screw connections.

Eine andere bekannte Bauart von hydraulischen Nockenwellenverstellern ist der Axialkolbenversteller. Hierbei wird über Öldruck ein Verschiebeelement axial verschoben, welches über Schrägverzahnungen eine Relativverdrehung zwischen einem Antriebselement und einem Abtriebselement erzeugt.Another known type of hydraulic phaser is the axial piston phaser. Here, a displacement element is axially displaced via oil pressure, which generates a helical gear teeth relative rotation between a drive element and an output element.

Eine weitere Bauform eines Nockenwellenverstellers ist der elektromechanische Nockenwellenversteller, der ein Dreiwellengetriebe (beispielsweise ein Planetengetriebe) aufweist. Dabei bildet eine der Wellen das Antriebselement und eine zweite Welle das Abtriebselement. Über die dritte Welle kann dem System mittels einer Stelleinrichtung, beispielsweise einem Elektromotor oder einer Bremse, Rotationsenergie zugeführt oder aus dem System abgeführt werden. Hierbei kann gleichfalls eine Feder derart angeordnet werden, dass das Antriebselement und das Abtriebselement bei deren relativen Verdrehung unterstützt oder zurückführt.Another design of a camshaft adjuster is the electromechanical camshaft adjuster having a three-shaft gear (for example, a planetary gear). One of the shafts forms the drive element and a second shaft forms the output element. About the third wave, the system by means of an adjusting device, such as an electric motor or a brake, rotational energy supplied or removed from the system. In this case, a spring can likewise be arranged such that the drive element and the driven element assist or guide back their relative rotation.

Die DE 10 2006 002 993 A1 offenbart einen Nockenwellenversteller, bei dem das Federelement auf der nockenwellenzugewandten Seite des Nockenwellenverstellers angeordnet ist. Das Federelement wird von einem Federdeckel abgedeckt. Die Abdeckung sichert das Federelement in axialer Richtung und schützt gegen äußere Einwirkungen.The DE 10 2006 002 993 A1 discloses a camshaft adjuster, wherein the spring element is arranged on the camshaft-facing side of the camshaft adjuster. The spring element is covered by a spring cover. The cover secures the spring element in the axial direction and protects against external influences.

Die DE 10 2008 051 755 A1 offenbart einen Nockenwellenversteller mit einem Federelement, wobei ein Ende des Federelements auf einem Stift gelagert ist, welcher mit einer Scheibe verschraubt ist. Ein topfförmiger Federdeckel kapselt mit dieser Scheibe das Federelement ein und schützt gegen äußere Einwirkungen.The DE 10 2008 051 755 A1 discloses a phaser having a spring element with one end of the spring element mounted on a pin which is bolted to a disk. A cup-shaped spring lid encapsulates the spring element with this disc and protects against external influences.

Zusammenfassung der ErfindungSummary of the invention

Aufgabe der Erfindung ist es, einen Nockenwellenversteller anzugeben, der eine reibungsarme und zuverlässige Federsicherung aufweist.The object of the invention is to provide a camshaft adjuster, which has a low-friction and reliable spring safety.

Erfindungsgemäß wird diese Aufgabe durch die Merkmale des Anspruchs 1 gelöst.According to the invention, this object is solved by the features of claim 1.

Die Reduzierung des axialen Spiels der Feder erfolgt durch ein Distanzelement des Federdeckels im Bereich des Federendes der Feder. Zugleich verbleibt genug axialer Raum für die Windungen der Feder, welche im Betrieb des Nockenwellenverstellers und aufgrund von Fertigungstoleranzen eine Abweichung von ihrer idealen Erstreckung in radialer Richtung aufweisen. Somit wird eine Kollision der Windungen der Feder mit einem peripherem Bauteil vermieden, wodurch sich die Lebensdauer der Feder erhöht und die Reibung im Betrieb vermindert wird. Weiterhin entsteht durch die Erfindung der Vorteil, dass Fertigungstoleranzen bezüglich der radialen Erstreckungsrichtung der Windungen gröber und somit wirtschaftlicher ausfallen können. Dieser Vorteil der Grobtolerierung kann auch bei den peripheren Bauteilen erzielt werden, z.B. bei dem Federdeckel.The reduction of the axial play of the spring is effected by a spacer element of the spring cover in the region of the spring end of the spring. At the same time there remains enough axial space for the windings of the spring, which have a deviation from their ideal extent in the radial direction during operation of the camshaft adjuster and due to manufacturing tolerances. Thus, a collision of the windings of the spring is avoided with a peripheral member, which increases the life of the spring and the friction is reduced during operation. Furthermore, the invention provides the advantage that manufacturing tolerances with respect to the radial extension direction of the turns can be coarser and thus more economical. This advantage of coarse tolerance can also be achieved in the peripheral components, e.g. at the spring cover.

In einer Ausgestaltung der Erfindung ist das Distanzelement als lokale Erhebung einteilig mit dem Federdeckel ausgebildet. Eine solche Erhebung lässt sich durch Prägen, Tiefziehen oder Fräsen herstellen. Eine lokale Ausbildung ist vorteilhaft, damit gezielt die Bereiche der Feder in axialer Richtung von dem Federdeckel gesichert werden, welche im Betrieb einer minimalen Relativbewegung zwischen der Feder und einem peripheren Bauteil unterliegen. Dadurch wird Reibung und Verschleiß minimiert und die Lebensdauer der Feder erhöht.In one embodiment of the invention, the spacer element is formed as a local collection in one piece with the spring cover. Such a survey can be produced by embossing, deep drawing or milling. A local education is advantageous so that targeted the areas of the spring are secured in the axial direction of the spring cover, which are subject to a minimum relative movement between the spring and a peripheral component during operation. This minimizes friction and wear and increases the life of the spring.

In einer optionalen Ausgestaltung der Erfindung ist das Distanzelement vom Federdeckel separat ausgebildet. Die Bauteiltrennung zwischen Federdeckel und dem Distanzelement als Einlegeteil ermöglicht vorteilhafterweise den gezielten Einsatz von Werkstoffen für bestimmte Funktionen. Beispielsweise kann der Federdeckel aus einem Werkstoff sein, der gezielt Umwelteinflüsse standhält und das Distanzelement aus einem verschleißfesten und/oder höherwertigem Werkstoff.In an optional embodiment of the invention, the spacer element is formed separately from the spring cover. The component separation between the spring cover and the spacer element as an insert advantageously allows the targeted use of materials for certain functions. For example, the spring cover may be made of a material that specifically withstands environmental influences and the spacer element made of a wear-resistant and / or higher quality material.

In einer vorteilhaften Ausgestaltung ist der Federdeckel mit dem Distanzelement stoff-, form- und/oder kraftschlüssig verbunden. Bevorzugterweise ist eine stoffschlüssige Verbindung vorzusehen, alternativ auch in Kombination mit einem Form- oder Kraftschluss, wobei das Distanzelement in den Federdeckel eingelassen, verklebt, verschweißt oder verlötet ist. Form- und kraftschlüssige Verbindungen positionieren gleichermaßen das Distanzstück zuverlässig mit dem Federdeckel an der dafür vorgesehenen Funktionsstelle der axialen Anlage des Federendes mit dem Distanzelement.In an advantageous embodiment, the spring cover with the spacer element material, form and / or non-positively connected. Preferably, a cohesive connection is provided, alternatively also in combination with a positive or non-positive connection, wherein the spacer element is embedded in the spring cover, glued, welded or soldered. Positive and non-positive connections equally position the spacer reliably with the spring cover at the designated function point of the axial abutment of the spring end with the spacer element.

In einer besonders bevorzugten Ausgestaltung ist der Federdeckel aus Blech oder Kunststoff ausgebildet. Einen Federdeckel aus Blech in dünnwandiger Topfform auszubilden ist aufgrund des geringen Gewichtes und der dennoch hohen Steifigkeit vorteilhaft. Eine Ausbildung des Federdeckels aus Kunststoff ist bevorzugt einzusetzen, wenn die Wirtschaftlichkeit gegenüber Blech gegeben ist und keine hohen Temperaturunterschiede im Betrieb an der Stelle des Federdeckels zu erwarten sind bzw. die Temperaturwechselbeständigkeit des Kunststoffes ausreichend gegeben ist.In a particularly preferred embodiment, the spring cover is formed of sheet metal or plastic. Forming a spring cover made of sheet metal in a thin-walled pot shape is advantageous because of the low weight and the nevertheless high rigidity. A design of the spring cover made of plastic is preferably used when the economy is given to sheet metal and no high temperature differences in operation at the location of the spring cover are to be expected or the thermal shock resistance of the plastic is sufficiently given.

In einer bevorzugten Ausbildung weist das Distanzelement eine Beschichtung auf. Eine Beschichtung verringert den Verschleiß und das Gewicht bei der Ausbildung des Distanzelementes als Grundträger mit einem wirtschaftlichen Werkstoff, z.B. Kunststoff.In a preferred embodiment, the spacer element has a coating. A coating reduces the wear and the weight in the formation of the spacer element as a basic carrier with an economical material, e.g. Plastic.

In einer Ausbildung der Erfindung sind mehrere, in Umfangsrichtung verteilte Distanzelemente vorgesehen. Eine Verteilung mehrerer Distanzelemente ist vorteilhaft, wenn die Belastung eines einzelnen Distanzelementes zu hoch ist und es dadurch zum Ausfall kommen würde. Die Verteilung in Umfangsrichtung ist bevorzugt außerhalb der federnden Windungen anzuordnen. In Umfangsrichtung verteilte Distanzelemente können auf verschiedenen Teilkreisen und/oder in verschiedenen Winkelpositionen angeordnet sein.In one embodiment of the invention a plurality of distributed in the circumferential direction spacer elements are provided. A distribution of several spacer elements is advantageous if the load of a single spacer element is too high and this would lead to failure. The distribution in the circumferential direction is preferably to be arranged outside the resilient windings. Distributed in the circumferential direction spacers may be arranged on different pitch circles and / or in different angular positions.

In einer vorteilhaften Ausbildung ist das Distanzelement im Bereich der Lagerung des Federendes angeordnet. Eine Fixierung der Federenden in axialer Richtung auf der Lagerung vermeidet Zwang in axialer Richtung im Bereich der federnden Windungen.In an advantageous embodiment, the spacer element is arranged in the region of the bearing of the spring end. A fixation of the spring ends in the axial direction on the bearing avoids compulsion in the axial direction in the region of the resilient turns.

In einer besonders vorteilhaften Ausbildung umragt das Distanzelement die Lagerung. Diese Umragung kann teilweise oder vollständig erfolgen. Die Lagerung ist meist durch einen Stift oder ein anderes zylindrisches Element gegeben. Somit kann die Umragung auch sternförmig, mit der Lagerung als Zentrum ausgebildet sein. Die Umragung besitzt allerdings eine Freistellung in Form des Querschnittes der Lagerung, damit länger ausgebildete Lagerzapfen teilweise in den Federdeckel hineinragen können. Ein Durchragen des Federdeckels durch den Lagerzapfen ist denkbar.In a particularly advantageous embodiment, the spacer extends around the storage. This transfer can be partial or complete. The storage is usually given by a pin or other cylindrical element. Thus, the Umragung also star-shaped, be designed with the storage as a center. However, the Umragung has an exemption in the form of the cross section of the storage, so that longer trained bearing pin can partially protrude into the spring cover. A protrusion of the spring cover by the bearing pin is conceivable.

Durch die erfindungsgemäße Anordnung des Distanzelementes wird die Reibung zwischen der Feder und dem Federdeckel, oder anderen peripheren Bauteilen, vermieden. Dadurch wird der Verschleiß vermindert und die Lebensdauer erhöht. Zudem haben die im Betrieb federnden Windungen der Feder genügend axialen Raum, um eine Kontaktierung mit peripheren Bauteilen zu vermeiden. Die Auflagefläche der Federenden der Feder auf der Lagerung bleibt zugleich erhalten, bzw. kann vorteilhafterweise durch die Erfindung erhöht werden.The inventive arrangement of the spacer element, the friction between the spring and the spring cover, or other peripheral components is avoided. This reduces wear and increases service life. In addition, the resilient in operation turns of the spring have enough axial space to avoid contact with peripheral components. The bearing surface of the spring ends of the spring remains on the bearing obtained at the same time, or can be advantageously increased by the invention.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ausführungsbeispiele der Erfindung sind in den Figuren dargestellt.Embodiments of the invention are illustrated in the figures.

Es zeigen:

  • Fig. 1 einen Ausschnitt eines Nockenwellenverstellers,
  • Fig. 2 eine erste Ausführungsform eines Distanzelementes,
  • Fig. 3 eine zweite Ausführungsform eines Distanzelementes,
  • Fig. 4 eine dritte Ausführungsform eines Distanzelementes und
  • Fig. 5 einen Ausschnitt eines Federdeckels mit einem Distanzelement.
Show it:
  • Fig. 1 a section of a camshaft adjuster,
  • Fig. 2 a first embodiment of a spacer element,
  • Fig. 3 a second embodiment of a spacer element,
  • Fig. 4 a third embodiment of a spacer element and
  • Fig. 5 a section of a spring cover with a spacer element.

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

Fig. 1 zeigt einen Ausschnitt eines Nockenwellenverstellers 1. Der Nockenwellenversteller 1 weist ein Antriebselement 2, ein Abtriebselement 3, eine Feder 4 und einen Federdeckel 5 auf. Das Antriebselement 2 und das Abtriebselement 3 sind relativ zueinander verdrehbar angeordnet. Die Relativverdrehung in Umfangsrichtung 10 des Nockenwellenverstellers 1 kann bspw. durch Befüllung von Druckkammern mit Hydraulikmittel erfolgen, wobei die Druckkammern zwischen Antriebselement 2 und Abtriebselement 3 ausgebildet sind. Die Feder 4 verspannt Antriebselement 2 und Abtriebselement 3 relativ zueinander in einer Umfangsrichtung 10. Die Vorspannung sorgt für eine Relativdrehung zwischen Antriebselement 2 und Abtriebselement 3. Damit die Feder 4 vor äußeren Einwirkungen geschützt ist, ist diese durch einen Federdeckel 5 zumindest teilweise abgedeckt bzw. abgekapselt. Weiter sichert im Betrieb der Federdeckel 5 die Feder 4 in axialer Richtung 8 und verhindert ein Abrutschen ihrer Federenden 7 von der Lagerung 11. Die Feder 4 ist als Spiralfeder ausgebildet, deren federnde Windungen sich überwiegend senkrecht zur axialen Richtung 8 erstrecken. Fig. 1 shows a section of a camshaft adjuster 1. The camshaft adjuster 1 has a drive element 2, an output element 3, a spring 4 and a spring cover 5 on. The drive element 2 and the output element 3 are arranged rotatable relative to each other. The relative rotation in the circumferential direction 10 of the camshaft adjuster 1 can be done, for example, by filling pressure chambers with hydraulic fluid, wherein the pressure chambers between the drive element 2 and output element 3 are formed. The spring 4 braces the drive element 2 and driven element 3 relative to each other in a circumferential direction 10. The bias provides for a relative rotation between the drive element 2 and driven element 3. So that the spring 4 is protected from external influences, this is at least partially covered by a spring cover 5 or encapsulated. Further ensures the operation of the spring cover 5, the spring 4 in the axial direction 8 and prevents slippage of their spring ends 7 of the bearing 11. The spring 4 is formed as a spiral spring whose resilient turns extend predominantly perpendicular to the axial direction 8.

Das Antriebselement 2 weist einteilig oder separat eine nicht weiter dargestellte Verzahnung für eine Steuerkette oder einen Riemen auf. Das Abtriebselement 3 ist drehfest mit einer nicht weiter dargestellten Nockenwelle verbindbar.The drive element 2 has in one piece or separately a not shown toothing for a timing chain or a belt. The output element 3 is rotatably connected to a camshaft, not shown.

Der Federdeckel 5 weist ein Distanzelement 6 auf, welches in Kontakt mit dem Federende 7 der Feder 4 steht. Das Distanzelement 6 ist einteilig mit dem Federdeckel 5 ausgebildet und erhebt sich in axialer Richtung 8 aus der Stirnseite 12 des Federdeckels 5 heraus. Die Lagerung 11 ist als Lagerzapfen 13 einer Schraube 14 des Nockenwellenverstellers 1 ausgebildet. Der Außendurchmesser der Mantelfläche 15 des Lagerzapfens 13 ist in axialer Richtung 8 konstant. Das Distanzelement 6 weist eine Materialausnehmung 16 auf, wobei eine Mantelfläche 17 der Materialausnehmung 16 größer ist, als der Durchmesser der Mantelfläche 15 des Lagerzapfens 13. Das Distanzelement 6 und seine Materialausnehmung 16 können in Umfangsrichtung 10 des Nockenwellenverstellers 1 teilweise oder vollständig umlaufend ausgebildet sein. In axialer Richtung 8 findet keine Überlappung der Mantelfläche 15 des Lagerzapfens 13 mit der Mantelfläche 17 Materialausnehmung 16 statt. Die Stirnseite 18 des Distanzelementes 6 ist weitestgehend parallel zur Stirnseite 12 des Federdeckels 5. Die Stirnseite 18 des Distanzelementes 6 steht in Kontakt mit dem Federende 7 und begrenzt somit den axialen Federraum 20.The spring cover 5 has a spacer element 6 which is in contact with the spring end 7 of the spring 4. The spacer element 6 is formed integrally with the spring cover 5 and rises in the axial direction 8 from the end face 12 of the spring cover 5 out. The bearing 11 is designed as a bearing journal 13 of a screw 14 of the camshaft adjuster 1. The outer diameter of the lateral surface 15 of the bearing journal 13 is constant in the axial direction 8. The spacer element 6 has a material recess 16, wherein a lateral surface 17 of the material recess 16 is larger than the diameter of the lateral surface 15 of the bearing journal 13. The spacer element 6 and its material recess 16 may be formed circumferentially 10 of the camshaft adjuster 1 partially or completely circumferentially. In the axial direction 8 there is no overlap of the lateral surface 15 of the bearing pin 13 with the lateral surface 17 Materialausnehmung 16 instead. The end face 18 of the spacer element 6 is largely parallel to the end face 12 of the spring cover 5. The end face 18 of the spacer element 6 is in contact with the spring end 7 and thus limits the axial spring chamber 20th

Fig. 2 zeigt eine erste Ausführungsform eines Distanzelementes 6. Das Distanzelement 6 ist als kreisscheibenförmige, lokale Erhebung 9 des Federdeckels 5 ausgebildet. Diese lokale Erhebung 9 ist weitestgehend fluchtend zur Lagerung 11 orientiert. Die lokale Erhebung 9 minimiert den Kontakt mit dem Federende 7 auf den Bereich um die Lagerung 11. Fig. 2 shows a first embodiment of a spacer element 6. The spacer element 6 is formed as a circular disk-shaped, local elevation 9 of the spring cover 5. This local survey 9 is largely aligned with the storage 11 oriented. The local elevation 9 minimizes the contact with the spring end 7 to the area around the bearing 11.

Fig. 3 zeigt eine zweite Ausführungsform eines Distanzelementes 6. Das Distanzelement 6 ist als Muster aus einer Vielzahl von Einzelerhebungen 19 ausgebildet. Die Einzelerhebungen 19 sind sternförmig um eine gedachte axiale Verlängerung der Mantelfläche 15 des Lagerzapfens 13 angeordnet sind. Die Verteilung der Einzelerhebungen 19 sind zueinander weitestgehend gleichmäßig beabstandet. Fig. 3 shows a second embodiment of a spacer element 6. The spacer element 6 is formed as a pattern of a plurality of individual elevations 19. The individual elevations 19 are arranged in a star shape around an imaginary axial extension of the lateral surface 15 of the bearing journal 13. The distribution of the individual elevations 19 are largely evenly spaced from each other.

Fig. 4 zeigt eine dritte Ausführungsform eines Distanzelementes 6. Das Distanzelement 6 ist als Muster aus einer Vielzahl von Einzelerhebungen 19 ausgebildet. Die Einzelerhebungen 19 sind zueinander gleichgerichtet orientiert. Ein Abstand zwischen den Einzelerhebungen 19 lässt Freiraum für eine gedachte Verlängerung der Mantelfläche 15 des Lagerzapfens 13. Fig. 4 shows a third embodiment of a spacer element 6. The spacer element 6 is formed as a pattern of a plurality of individual elevations 19. The individual elevations 19 are oriented to each other rectified. A distance between the individual elevations 19 leaves room for an imaginary extension of the lateral surface 15 of the bearing journal thirteenth

Fig. 5 zeigt einen Ausschnitt eines Federdeckels 5 mit einem Distanzelement 6. Das Distanzelement 6 ist aus dem Federdeckel 5 einteilig ausgebildet. Der Federdeckel 5 und das Distanzelement 6 haben weitestgehend dieselbe Wandstärke. Das Distanzelement 6 besitzt eine Materialausnehmung 16 mit einer Mantelfläche 17, welche sich über die gesamte Wandstärke erstreckt. Dieser Freiraum kann von einer Lagerung 11 durchdrungen werden. Ein Versatz A des Distanzelementes 6 von dem Federdeckel 5 in axialer Richtung 8 begrenzt den axialen Federraum 20. Fig. 5 shows a section of a spring cover 5 with a spacer element 6. The spacer element 6 is formed integrally from the spring cover 5. The spring cover 5 and the spacer element 6 have largely the same wall thickness. The spacer element 6 has a material recess 16 with a lateral surface 17, which extends over the entire wall thickness. This space can be penetrated by a storage 11. An offset A of the spacer element 6 from the spring cover 5 in the axial direction 8 limits the axial spring space 20.

Liste der BezugszahlenList of reference numbers

  • 1) Nockenwellenversteller1) Camshaft adjuster
  • 2) Antriebselement2) drive element
  • 3) Abtriebselement3) output element
  • 4) Feder4) spring
  • 5) Federdeckel5) Spring cover
  • 6) Distanzelement6) Spacer element
  • 7) Federende7) spring end
  • 8) Axiale Richtung8) Axial direction
  • 9) Erhebung9) Survey
  • 10)Umfangsrichtung10) circumferentially
  • 11)Lagerung11) Storage
  • 12)Stirnseite12) end face
  • 13)Lagerzapfen13) bearing journal
  • 14)Schraube14) screw
  • 15)Mantelfläche15) generated surface
  • 16)Materialausnehmung16) material recess
  • 17)Mantelfläche17) generated surface
  • 18)Stirnseite18) end face
  • 19)Einzelerhebungen19) individual surveys
  • 20)Axialer Federraum20) Axial spring space
  • A) VersatzA) Offset

Claims (8)

  1. Camshaft adjuster (1) having
    - a drive element (2), an output element (3), a spring (4) and a spring cover (5),
    - the drive element (2) and the output element (3) being arranged such that they can be rotated relative to one another,
    - the spring (4) bracing the drive element (2) and the output element (3) in the circumferential direction (10),
    - the spring cover (5) being connected to the drive element (2) or the output element (3), and
    - the spring cover (5) covering the spring (4) in the axial direction (8),
    characterized in that
    the spring cover (5) has a spacer element (6), and the spacer element (6) delimits a degree of freedom of the spring (4) in the axial direction (8), in which degree of freedom the spacer element (6) can be brought into contact with one spring end (7) of the spring (4), the spacer element (6) being arranged in the region of the mounting (11) of the spring end (7), as a result of which contact of the peripheral components with the resilient windings of the spring (4) in the axial direction (8) is avoided, the spacer element (6) being configured as a local elevation (9) in one piece with the spring cover (5).
  2. Camshaft adjuster (1) according to Claim 1, characterized in that the spacer element (6) and the spring cover (5) are configured separately.
  3. Camshaft adjuster (1) according to Claim 2, characterized in that the spring cover (5) is connected to the spacer element (6) in a material-to-material, positively locking and/or non-positive manner.
  4. Camshaft adjuster (1) according to one of the preceding claims, characterized in that the spring cover (5) is configured from sheet metal or from plastic.
  5. Camshaft adjuster (1) according to one of the preceding claims, characterized in that the spacer element (6) has a coating.
  6. Camshaft adjuster (1) according to one of the preceding claims, characterized in that a plurality of spacer elements (6) which are distributed in the circumferential direction (10) of the spring cover (5) are provided.
  7. Camshaft adjuster (1) according to Claim 1, characterized in that the spacer element (6) projects around the mounting (11).
  8. Spring cover (5) of a camshaft adjuster (1) according to one of Claims 1 to 8.
EP12168785.9A 2011-09-01 2012-05-22 Camshaft adjuster Not-in-force EP2565402B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011081971A DE102011081971A1 (en) 2011-09-01 2011-09-01 Phaser

Publications (2)

Publication Number Publication Date
EP2565402A1 EP2565402A1 (en) 2013-03-06
EP2565402B1 true EP2565402B1 (en) 2014-07-16

Family

ID=46168167

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12168785.9A Not-in-force EP2565402B1 (en) 2011-09-01 2012-05-22 Camshaft adjuster

Country Status (4)

Country Link
US (1) US8863707B2 (en)
EP (1) EP2565402B1 (en)
CN (1) CN102966392B (en)
DE (1) DE102011081971A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013206672A1 (en) * 2013-04-15 2014-10-16 Schaeffler Technologies Gmbh & Co. Kg Phaser
JP6217763B2 (en) * 2014-02-14 2017-10-25 アイシン精機株式会社 Valve timing control device
US9334763B1 (en) 2014-11-21 2016-05-10 Schaeffler Technologies AG & Co. KG Support pin for spring guidance in a camshaft phaser
US11542843B2 (en) 2018-09-25 2023-01-03 Schaeffler Technologies AG & Co. KG Insertion piece for camshaft phaser and camshaft phaser
DE102019113643B4 (en) * 2019-05-22 2021-04-22 Pierburg Gmbh Valve device

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Publication number Priority date Publication date Assignee Title
DE102006002993A1 (en) 2006-01-21 2007-08-09 Schaeffler Kg Camshaft adjuster for an internal combustion engine
DE102007039282B4 (en) * 2007-08-20 2017-06-01 Hilite Germany Gmbh Hydraulically sealed camshaft adjuster
DE102009005114A1 (en) * 2008-01-30 2009-08-06 Schaeffler Kg Camshaft adjusting device
DE102009042168A1 (en) * 2008-10-14 2010-04-15 Schaeffler Kg Camshaft adjuster and output adapter for a concentric camshaft
DE102008051732A1 (en) * 2008-10-15 2010-04-22 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102008051755A1 (en) 2008-10-15 2010-04-22 Schaeffler Kg Control time adjusting device for gas exchange valve of internal-combustion engine, has spring element resting against separately at pin formed to output and input elements, where pin is bolted with output or input element by thread section
JP4725655B2 (en) * 2009-02-09 2011-07-13 株式会社デンソー Valve timing adjustment device
DE102009015882A1 (en) * 2009-04-01 2010-10-07 Schaeffler Technologies Gmbh & Co. Kg Camshaft adjuster and method for adjusting the angular position of a camshaft relative to a crankshaft
US8424500B2 (en) * 2009-08-06 2013-04-23 Delphi Technologies, Inc. Harmonic drive camshaft phaser with improved radial stability
DE102010009394A1 (en) * 2010-02-26 2011-09-01 Schaeffler Technologies Gmbh & Co. Kg Device for variably setting the control times of gas exchange valves of an internal combustion engine
DE102011088295A1 (en) * 2011-12-12 2013-06-13 Schaeffler Technologies AG & Co. KG Phaser

Also Published As

Publication number Publication date
US8863707B2 (en) 2014-10-21
EP2565402A1 (en) 2013-03-06
DE102011081971A1 (en) 2013-03-07
CN102966392B (en) 2016-12-21
CN102966392A (en) 2013-03-13
US20130055978A1 (en) 2013-03-07

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