EP1753941B1 - Vane-type camshaft adjuster - Google Patents

Vane-type camshaft adjuster Download PDF

Info

Publication number
EP1753941B1
EP1753941B1 EP05739591A EP05739591A EP1753941B1 EP 1753941 B1 EP1753941 B1 EP 1753941B1 EP 05739591 A EP05739591 A EP 05739591A EP 05739591 A EP05739591 A EP 05739591A EP 1753941 B1 EP1753941 B1 EP 1753941B1
Authority
EP
European Patent Office
Prior art keywords
section
vane
cross
slot
enlarged
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP05739591A
Other languages
German (de)
French (fr)
Other versions
EP1753941A1 (en
Inventor
Mike Kohrs
Hermann Golbach
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler 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.)
Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP1753941A1 publication Critical patent/EP1753941A1/en
Application granted granted Critical
Publication of EP1753941B1 publication Critical patent/EP1753941B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F01L2001/34479—Sealing of phaser devices
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a vane-type camshaft adjuster with a stator and a rotor which can be hydraulically rotated relative to the stator and can be connected to a camshaft with radially projecting vanes inserted in vane grooves.
  • Camshaft adjusters are used to change the timing for opening or closing the valves. The fixed angular relationship between the camshaft and the crankshaft driving it is thereby canceled and the timing can be optimally adjusted depending on the speed and other parameters. Camshaft adjusters allow a relative rotation of the camshaft to the crankshaft.
  • Known vane-type camshaft adjuster as in the document US 2002/0038637 A1 describe a rotor having a plurality of radially projecting wings, which are pressed by the force of a spring radially outward against a stator housing. On the stator a plurality of radially inwardly projecting stops are formed, which limit the adjustment movement of the rotor in both directions of rotation when the wings run against the stops.
  • the wings bear with their end edges on the stator, so that between each one wing side and the adjacent side of a stop of the stator, a chamber is formed, in which a fluid, usually the engine oil, is conveyed via a valve associated with the camshaft adjuster.
  • the stator serves on the one hand for separating and sealing the fluid chambers, on the other hand, to set the adjustment angle between the camshaft and the crankshaft.
  • the rotor of the camshaft adjuster is frictionally connected during assembly via a screw with the camshaft.
  • To generate the frictional connection of the rotor (rotary piston) of the adjuster is pressed by the biasing force of the central screw with its lateral flange on the corresponding side surface of the camshaft.
  • the traction must transmit the drive torque and any axial or radial forces from the drive. Therefore, a relatively high biasing force must be initiated.
  • the invention is therefore based on the problem of specifying a vane-type camshaft adjuster, in which the camshaft-side stress concentration is reduced.
  • the invention is based on the finding that the stresses in the region of the groove bottom of the vane groove, which arise due to the pretensioning force of the central screw, are limited locally in the axial direction of the rotor to the region of the flange surface which adjoins the camshaft in the installed state. According to the invention, only this limited area is provided with a stress-optimized contour, while the remaining area of the vane groove retains the conventional functionally correct contour for optimal guidance of the vane and the wing spring.
  • the enlarged cross-section in the region of the camshaft-side end section of the vane groove reduces the notch effect and results in a more uniform distribution of stress across the width with considerably reduced stress peaks.
  • a particularly effective reduction of the voltage peaks can be achieved if the wing groove is undercut in the region of the groove base with respect to the groove side surfaces and has an enlarged cross section at this point.
  • the invention therefore, especially the most vulnerable area, which is located at the undercut, relieved by the choice of an enlarged cross-section.
  • the enlarged area can on the one hand be in the region of the groove base, but it can also be provided in the area of the undercut, and the area of increased cross-section can be provided both in the area of the groove bottom and in the area of the undercut or in both areas.
  • a particularly favorable voltage curve results when the transition between the non-enlarged and the enlarged groove cross-section arcuate is trained.
  • the formed as a bow transition between the two cross-sections with different diameters causes a gradual increase in voltage, so that local voltage spikes are avoided.
  • the wing groove in the region of the undercut and the groove bottom has a radially outwardly extending portion with an enlarged cross-section.
  • the region is optimized that extends radially outward from the groove bottom.
  • the original groove base and the groove bottom in the end portion may have a common baseline.
  • the cross section of the enlarged area may be approximately oval and have a straight section in the area of the groove bottom. It is also possible that the enlarged portion has at least approximately a constant diameter. Such a structure is particularly favorable production.
  • the portion of the vane groove whose cross-section is not enlarged merges into a section with a continuously enlarging cross-section.
  • the wing groove can be left unchanged while expanding outwards in the radial direction towards the outside in the form of a dome.
  • an oval cross section of the enlarged area is preferred.
  • the continuous transition between the normal cross-section vane groove and the enlarged cross-section portion avoids increased stress concentrations on the side surface against which the camshaft abuts. Accordingly, it is not necessary to resort to a material with a higher strength and the subject invention can be produced inexpensively.
  • the wing groove in the region of the groove bottom a radially inwardly extending portion having an enlarged cross section.
  • This area with the enlarged cross-section is preferably present in addition to the section with the enlarged cross-section, which is located in the region of the undercut and in the groove base and extending radially outward.
  • the entire area surrounding the undercut, the groove bottom and the beginning of Nutrich vin have the enlarged diameter. Since there are no sharp-edged transitions at any point, no local voltage peaks occur.
  • the area with the enlarged cross-section has an oval basic shape and is cone-shaped.
  • Fig. 1 shows cross section through a vane-phaser
  • Fig. 2a a perspective view of a rotor 1 of a vane-cam Verstellers 0.
  • the rotor 1 has a disc-shaped basic shape and has five evenly distributed over the circumference of the vane grooves 2, in the wings 2a can be used to seal the oil-filled chambers 2b between the rotor 1 and a stator 2c.
  • the vane groove 2 extends in the axial direction and has an enlarged cross section at its end section 5.
  • Fig. 2b shows a sectional side view of the in Fig. 1
  • the vane groove 2 has a constant cross-section in the axial direction almost over the entire thickness of the rotor 1 and only has an enlarged cross-section in the region of the end section 5.
  • This cross-sectional enlargement leads to a reduction of the notch effect and thus to lower stress peaks in the region of the end section 5.
  • FIGS. 3a-c are enlarged views of the end portion of the wing groove 9 of a rotor according to the prior art.
  • Fig. 3a is a perspective view
  • Fig. 3b is a side view analogous to Fig. 2 .
  • Fig. 3c is a front view of the wing groove 9.
  • the wing groove 9 indicates the free end 10 of the same constant diameter as in the remaining area, so that there is a relatively large jump in the cross section, which causes the increased voltages at this point.
  • FIGS. 4a-c show a first embodiment of the invention.
  • the transition 11 between the non-enlarged and the enlarged groove cross section is arcuate.
  • the transition 11 extends both from the groove base 12 and from the undercuts 13 to the outside.
  • the arcuate transition 11 causes a comparatively gentle force deflection, which leads in addition to the enlarged cross-section on the outside to lower stress concentrations.
  • FIGS. 5a-c show a second embodiment of the invention.
  • the wing groove has in the region of the undercut 13 a radially outward, that is to the opening of the wing groove, extending portion 14 with an enlarged diameter.
  • the diameter of the section 14 is constant.
  • the area with the enlarged cross section does not extend radially inward from the groove base 12. The desired voltage reduction is achieved in this variant, especially by the increased diameter.
  • FIGS. 6a-c show a third embodiment of the invention.
  • Fig. 6b It can be seen that the non-enlarged cross-section of the section 15 of the wing groove merges into a section 16 with continuously increasing cross-section.
  • This variant is also characterized by a particularly low level of local peak voltages.
  • the portion extending radially inward from the groove bottom 12 does not have an enlarged cross section.
  • the Fig. 7a - c show a fourth embodiment of the invention.
  • the basic structure of this end portion of the rotor 1 is similar to that in the FIGS. 6a - C shown, in addition, the wing groove in the region of the groove base 12 has a radially inwardly extending portion 17 with an enlarged cross-section.
  • the enlarged portion 18 extending on either side of the undercuts 13 is as in Figs FIGS. 6a-c illustrated, it corresponds to the section 16 of Fig. 6 ,
  • the opening formed on the side surface of the rotor 1, which consists of the boundaries of the sections 17, 18, is approximately oval, except for the flat groove bottom.
  • the marginal lines of the section 18 are arcuate sections of a circle whose center is approximately in the region of the lower end 19 of the Nutrich inhabit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft einen Flügelzellen-Nockenwellenversteller mit einem Stator und einem relativ zum Stator hydraulisch verdrehbaren, mit einer Nockenwelle verbindbaren Rotor mit radial abstehenden, in Flügelnuten eingesetzten Flügeln.The invention relates to a vane-type camshaft adjuster with a stator and a rotor which can be hydraulically rotated relative to the stator and can be connected to a camshaft with radially projecting vanes inserted in vane grooves.

Hintergrund der ErfindungBackground of the invention

Nockenwellenversteller werden eingesetzt, um die Steuerzeiten für das Öffnen oder Schließen der Ventile zu verändern. Die feste Winkelbeziehung zwischen der Nockenwelle und der sie antreibenden Kurbelwelle wird dadurch aufgehoben und die Steuerzeiten können in Abhängigkeit der Drehzahl und weiterer Parameter optimal eingestellt werden. Nockenwellenversteller ermöglichen eine relative Verdrehung der Nockenwelle zur Kurbelwelle.Camshaft adjusters are used to change the timing for opening or closing the valves. The fixed angular relationship between the camshaft and the crankshaft driving it is thereby canceled and the timing can be optimally adjusted depending on the speed and other parameters. Camshaft adjusters allow a relative rotation of the camshaft to the crankshaft.

Bekannte Flügelzellen-Nockenwellenversteller wie im dokument US 2002/0038637 A1 beschreiben weisen einen Rotor mit mehreren radial abstehenden Flügeln auf, die durch die Kraft einer Feder radial nach außen gegen ein Statorgehäuse gedrückt werden. An dem Stator sind mehrere radial nach innen vorspringende Anschläge ausgebildet, die die Verstellbewegung des Rotors in beide Drehrichtungen begrenzen, wenn die Flügel gegen die Anschläge laufen. Die Flügel liegen mit ihren Stirnkanten am Stator an, so dass zwischen jeweils einer Flügelseite und der benachbarten Seite eines Anschlags des Stators eine Kammer gebildet wird, in die ein Fluid, in der Regel das Motoröl, über ein dem Nockenwellenversteller zugeordnetes Ventil gefördert wird. Der Stator dient einerseits zum Trennen und Abdichten der Fluidkammern, andererseits zur Festlegung des Verstellwinkels zwischen der Nockenwelle und der Kurbelwelle.Known vane-type camshaft adjuster as in the document US 2002/0038637 A1 describe a rotor having a plurality of radially projecting wings, which are pressed by the force of a spring radially outward against a stator housing. On the stator a plurality of radially inwardly projecting stops are formed, which limit the adjustment movement of the rotor in both directions of rotation when the wings run against the stops. The wings bear with their end edges on the stator, so that between each one wing side and the adjacent side of a stop of the stator, a chamber is formed, in which a fluid, usually the engine oil, is conveyed via a valve associated with the camshaft adjuster. The stator serves on the one hand for separating and sealing the fluid chambers, on the other hand, to set the adjustment angle between the camshaft and the crankshaft.

Der Rotor des Nockenwellenverstellers wird beim Zusammenbau kraftschlüssig über eine Schraube mit der Nockenwelle verbunden. Zur Erzeugung des Kraftschlusses wird der Rotor (Drehkolben) des Verstellers durch die Vorspannkraft der Zentralschraube mit seiner seitlichen Flanschfläche an die entsprechende Seitenfläche der Nockenwelle gedrückt. Der Kraftschluss muss das Antriebsdrehmoment und eventuelle axiale oder radiale Kräfte aus dem Antrieb übertragen. Daher muss eine relativ hohe Vorspannkraft eingeleitet werden. Allerdings hat es sich herausgestellt, dass im Rotor an der der Nockenwelle zugewandten Seite im Nutgrund der Flügelnuten relativ hohe Zugspannungen erzeugt werden. Zusätzlich werden durch die Übertragung des Nockenwellenantriebsmomentes vom Antrieb zum Abtrieb des Verstellers durch die Abstützung der Flügel in der Flügelnut hohe Zugspannungen in die Flügelnut eingeleitet. Es kommt daher zur Überlagerung der Kräfte und Spannungen und in der Folge zu einer hohen Beanspruchung des Werkstoffs.The rotor of the camshaft adjuster is frictionally connected during assembly via a screw with the camshaft. To generate the frictional connection of the rotor (rotary piston) of the adjuster is pressed by the biasing force of the central screw with its lateral flange on the corresponding side surface of the camshaft. The traction must transmit the drive torque and any axial or radial forces from the drive. Therefore, a relatively high biasing force must be initiated. However, it has been found that in the rotor on the side facing the camshaft in the groove bottom of the vane grooves relatively high tensile stresses are generated. In addition, high tensile stresses are introduced into the wing groove by the transfer of the camshaft drive torque from the drive to the output of the adjuster by the support of the wings in the wing groove. It therefore comes to the superposition of forces and stresses and as a result to a high stress of the material.

Die Verwendung von Materialien mit einer höheren Festigkeit soll jedoch vermieden werden, da höherfeste Materialien in den meisten Fällen teure und aufwendige Fertigungstechnologien erfordern. Auch die Vergrößerung der Breite und/oder des Durchmessers des Rotors ist keine praktikable Lösung, da diese Maßnahmen zu einem erhöhten Gewicht und zu erhöhter Massenträgheit führen. Die bloße Vergrößerung des Radius im Nutgrund über die Breite des Rotors ist nicht möglich, da die sichere Führung des Flügels dann möglicherweise nicht mehr gewährleistet ist. Außerdem besteht die Gefahr, dass die am Nutgrund der Flügelnut angeordnete Flügelfeder ihre Lage ändert.However, the use of higher strength materials should be avoided because higher strength materials in most cases require expensive and expensive manufacturing technologies. The increase in the width and / or the diameter of the rotor is not a viable solution, since these measures lead to increased weight and increased inertia. The mere enlargement of the radius in the groove bottom across the width of the rotor is not possible because the safe guidance of the wing may then no longer be guaranteed. In addition, there is a risk that the arranged on the groove bottom of the wing groove wing spring changes its position.

Zusammenfassung der ErfindungSummary of the invention

Der Erfindung liegt daher das Problem zugrunde, einen Flügelzellen-Nockenwellenversteller anzugeben, bei dem die nockenwellenseitige Spannungskonzentration verringert ist.The invention is therefore based on the problem of specifying a vane-type camshaft adjuster, in which the camshaft-side stress concentration is reduced.

Zur Lösung dieses Problems ist bei einem Flügelzellen-Nockenwellenversteller der eingangs genannten Art erfindungsgemäß vorgesehen, dass der nockenwellenseitige Endabschnitt der Flügelnut einen vergrößerten Querschnitt aufweist.To solve this problem is provided according to the invention in a vane-type camshaft adjuster of the type mentioned that the camshaft-side end portion of the vane groove has an enlarged cross-section.

Der Erfindung liegt die Erkenntnis zugrunde, dass die Spannungen im Bereich des Nutgrunds der Flügelnut, die durch die Vorspannkraft der Zentralschraube entstehen, in Axialrichtung des Rotors lokal auf den Bereich der Flanschfläche begrenzt sind, die im eingebauten Zustand an die Nockenwelle angrenzt. Gemäß der Erfindung wird nur dieser begrenzte Bereich mit einer spannungsoptimierten Kontur ausgestattet, während der übrige Bereich der Flügelnut die herkömmliche funktionsgerechte Kontur zur optimalen Führung des Flügels und der Flügelfeder beibehält. Durch den vergrößerten Querschnitt im Bereich des nockenwellenseitigen Endabschnitts der Flügelnut wird die Kerbwirkung reduziert und es entsteht eine über die Breite gleichmäßigere Spannungsverteilung mit beträchtlich verringerten Spannungsspitzen.The invention is based on the finding that the stresses in the region of the groove bottom of the vane groove, which arise due to the pretensioning force of the central screw, are limited locally in the axial direction of the rotor to the region of the flange surface which adjoins the camshaft in the installed state. According to the invention, only this limited area is provided with a stress-optimized contour, while the remaining area of the vane groove retains the conventional functionally correct contour for optimal guidance of the vane and the wing spring. The enlarged cross-section in the region of the camshaft-side end section of the vane groove reduces the notch effect and results in a more uniform distribution of stress across the width with considerably reduced stress peaks.

Eine besonders wirksame Verringerung der Spannungsspitzen lässt sich erzielen, wenn die Flügelnut im Bereich des Nutgrunds bezüglich der Nutseitenflächen hinterschnitten ist und an dieser Stelle einen vergrößerten Querschnitt aufweist. Erfindungsgemäß wird somit speziell der am meisten gefährdete Bereich, der sich an der Hinterschneidung befindet, durch die Wahl eines vergrößerten Querschnitts entlastet. Der übrige Bereich, der von der nockenwellenseitigen Anlagefläche des Rotors beabstandet ist, bleibt unverändert. Der vergrößerte Bereich kann sich einerseits im Bereich des Nutgrunds befinden, er kann jedoch auch im Bereich der Hinterschneidung vorgesehen sein, ferner kann der Bereich mit vergrößertem Querschnitt sowohl im Bereich des Nutgrunds als auch im Bereich der Hinterschneidung oder in beiden Bereichen vorgesehen sein.A particularly effective reduction of the voltage peaks can be achieved if the wing groove is undercut in the region of the groove base with respect to the groove side surfaces and has an enlarged cross section at this point. According to the invention, therefore, especially the most vulnerable area, which is located at the undercut, relieved by the choice of an enlarged cross-section. The remaining area, which is spaced from the camshaft side bearing surface of the rotor, remains unchanged. The enlarged area can on the one hand be in the region of the groove base, but it can also be provided in the area of the undercut, and the area of increased cross-section can be provided both in the area of the groove bottom and in the area of the undercut or in both areas.

Ein besonders günstiger Spannungsverlauf ergibt sich, wenn der Übergang zwischen dem nicht vergrößerten und dem vergrößerten Nutquerschnitt bogenförmig ausgebildet ist. Der als Bogen ausgebildete Übergang zwischen den beiden Querschnitten mit unterschiedlichem Durchmesser bewirkt einen allmählichen Spannungsanstieg, so dass lokale Spannungsspitzen vermieden werden.A particularly favorable voltage curve results when the transition between the non-enlarged and the enlarged groove cross-section arcuate is trained. The formed as a bow transition between the two cross-sections with different diameters causes a gradual increase in voltage, so that local voltage spikes are avoided.

Gemäß einer alternativen Ausgestaltung der Erfindung kann es vorgesehen sein, dass die Flügelnut im Bereich der Hinterschneidung und des Nutgrunds einen radial nach außen verlaufenden Abschnitt mit einem vergrößerten Querschnitt aufweist. Bei dieser Variante wird derjenige Bereich optimiert, der sich vom Nutgrund radial nach außen erstreckt. Der ursprüngliche Nutgrund und der Nutgrund in dem Endabschnitt können dabei eine gemeinsame Grundlinie besitzen. Der Querschnitt des vergrößerten Bereichs kann näherungsweise oval ausgebildet sein und im Bereich des Nutgrunds einen geraden Abschnitt aufweisen. Es ist auch möglich, dass der vergrößerte Abschnitt zumindest näherungsweise einen konstanten Durchmesser aufweist. Ein derartiger Aufbau ist besonders fertigungsgünstig.According to an alternative embodiment of the invention, it may be provided that the wing groove in the region of the undercut and the groove bottom has a radially outwardly extending portion with an enlarged cross-section. In this variant, the region is optimized that extends radially outward from the groove bottom. The original groove base and the groove bottom in the end portion may have a common baseline. The cross section of the enlarged area may be approximately oval and have a straight section in the area of the groove bottom. It is also possible that the enlarged portion has at least approximately a constant diameter. Such a structure is particularly favorable production.

Gemäß einer weiteren alternativen Ausgestaltung der Erfindung kann es vorgesehen sein, dass der Abschnitt der Flügelnut, dessen Querschnitt nicht vergrößert ist, in einen Abschnitt mit sich kontinuierlich vergrößerndem Querschnitt übergeht. In dem Bereich des Nutgrunds kann die Flügelnut dabei unverändert belassen sein, während sie sich von dort in Radialrichtung nach außen kelchartig erweitert. Auch bei dieser Ausführung wird ein ovaler Querschnitt des vergrößerten Bereichs bevorzugt. Durch den kontinuierlichen Übergang zwischen der Flügelnut mit dem normalen Querschnitt und dem Abschnitt mit dem vergrößerten Querschnitt werden erhöhte Spannungskonzentrationen an der Seitenfläche, an der die Nockenwelle anliegt, vermieden. Dementsprechend ist es nicht erforderlich, auf einen Werkstoff mit einer höheren Festigkeit zurückzugreifen und der Erfindungsgegenstand kann kostengünstig hergestellt werden.According to a further alternative embodiment of the invention, it may be provided that the portion of the vane groove whose cross-section is not enlarged, merges into a section with a continuously enlarging cross-section. In the area of the groove bottom, the wing groove can be left unchanged while expanding outwards in the radial direction towards the outside in the form of a dome. Also in this embodiment, an oval cross section of the enlarged area is preferred. The continuous transition between the normal cross-section vane groove and the enlarged cross-section portion avoids increased stress concentrations on the side surface against which the camshaft abuts. Accordingly, it is not necessary to resort to a material with a higher strength and the subject invention can be produced inexpensively.

Gemäß einer weiteren, ebenfalls besonders vorteilhaften Weiterbildung der Erfindung kann es vorgesehen sein, dass die Flügelnut im Bereich des Nutgrunds einen radial nach innen verlaufenden Abschnitt mit einem vergrößerten Querschnitt aufweist. Dieser Bereich mit dem vergrößerten Querschnitt ist vorzugsweise zusätzlich zu dem Abschnitt mit dem vergrößerten Querschnitt vorhanden, der sich im Bereich der Hinterschneidung und in dem Nutgrund befindet und sich radial nach außen erstreckt. Insgesamt kann der gesamte Bereich, der die Hinterschneidung, den Nutgrund und den Anfang der Nutseitenflächen umgibt, den vergrößerten Durchmesser aufweisen. Da an keiner Stelle scharfkantige Übergänge entstehen, treten keine lokalen Spannungsspitzen auf. Der Bereich mit dem vergrößerten Querschnitt besitzt eine ovale Grundform und ist konusartig ausgebildet.According to another, likewise particularly advantageous embodiment of the invention, it can be provided that the wing groove in the region of the groove bottom a radially inwardly extending portion having an enlarged cross section. This area with the enlarged cross-section is preferably present in addition to the section with the enlarged cross-section, which is located in the region of the undercut and in the groove base and extending radially outward. Overall, the entire area surrounding the undercut, the groove bottom and the beginning of Nutseitenflächen, have the enlarged diameter. Since there are no sharp-edged transitions at any point, no local voltage peaks occur. The area with the enlarged cross-section has an oval basic shape and is cone-shaped.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile und Einzelheiten der Erfindung werden anhand von bevorzugten Ausführungsbeispielen unter Bezugnahme auf die Figuren erläutert. Die Figuren sind schematische Darstellungen und zeigen:

Fig. 1
einen Querschnitt durch einen Flügelzellen-Nockenwellenversteller;
Fig. 2a
eine perspektivische Ansicht des Rotors eines erfindungsgemäßen Flügelzellen-Nockenwellenverstellers;
Fig. 2b
eine Seitenansicht des in Fig. 1 gezeigten Rotors;
Fig. 3a - c
Darstellungen des Endabschnitts der Flügelnut eines Rotors gemäß dem Stand der Technik;
Fig. 4a - c
ein erstes Ausführungsbeispiel der Erfindung;
Fig. 5a - c
ein zweites Ausführungsbeispiel der Erfindung;
Fig. 6a - c
ein drittes Ausführungsbeispiel der Erfindung und
Fig. 7a - c
ein viertes Ausführungsbeispiel der Erfindung.
Further advantages and details of the invention will be explained with reference to preferred embodiments with reference to the figures. The figures are schematic representations and show:
Fig. 1
a cross section through a vane-phaser;
Fig. 2a
a perspective view of the rotor of a vane-type camshaft adjuster according to the invention;
Fig. 2b
a side view of the in Fig. 1 shown rotor;
Fig. 3a - c
Representations of the end portion of the wing groove of a rotor according to the prior art;
Fig. 4a - c
a first embodiment of the invention;
Fig. 5a - c
a second embodiment of the invention;
Fig. 6a - c
A third embodiment of the invention and
Fig. 7a - c
A fourth embodiment of the invention.

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

Fig. 1 zeigt Querschnitt durch einen Flügelzellen-Nockenwellenversteller 0, Fig. 2a eine perspektivische Ansicht eines Rotors 1 eines Flügelzellen-Nockenwellenverstellers 0. Fig. 1 shows cross section through a vane-phaser 0, Fig. 2a a perspective view of a rotor 1 of a vane-cam Verstellers 0.

Der Rotor 1 weist eine scheibenförmige Grundform auf und besitzt fünf gleichmäßig über den Umfang verteilte Flügelnuten 2, in die Flügel 2a einsetzbar sind, die mit Öl befüllbare Kammern 2b zwischen dem Rotor 1 und einem Stator 2c abdichten. Auf der linken und rechten Seite jeder Flügelnut 2 sind Bohrungen 3, 4 angeordnet, durch die das Öl in die erwähnten Kammern 2b ein- und wieder ausfließen kann.The rotor 1 has a disc-shaped basic shape and has five evenly distributed over the circumference of the vane grooves 2, in the wings 2a can be used to seal the oil-filled chambers 2b between the rotor 1 and a stator 2c. On the left and right side of each wing groove 2 holes 3, 4 are arranged, through which the oil in the mentioned chambers 2b and can flow out again.

Die Flügelnut 2 verläuft in Axialrichtung und weist an ihrem Endabschnitt 5 einen vergrößerten Querschnitt auf.The vane groove 2 extends in the axial direction and has an enlarged cross section at its end section 5.

Fig. 2b zeigt eine geschnittene Seitenansicht des in Fig. 1 gezeigten Rotors 1. In dieser Darstellung ist besonders gut zu sehen, dass die Flügelnut 2 in Axialrichtung nahezu über die gesamte Dicke des Rotors 1 einen konstanten Querschnitt aufweist und lediglich im Bereich des Endabschnitts 5 einen vergrößerten Querschnitt besitzt. Diese Querschnittsvergrößerung führt zu einer Verringerung der Kerbwirkung und damit zu niedrigeren Spannungsspitzen im Bereich des Endabschnitts 5. Fig. 2b shows a sectional side view of the in Fig. 1 In this illustration, it is particularly easy to see that the vane groove 2 has a constant cross-section in the axial direction almost over the entire thickness of the rotor 1 and only has an enlarged cross-section in the region of the end section 5. This cross-sectional enlargement leads to a reduction of the notch effect and thus to lower stress peaks in the region of the end section 5.

Die Figuren 3a - c sind vergrößerte Darstellungen des Endabschnitts der Flügelnut 9 eines Rotors gemäß dem Stand der Technik. Fig. 3a ist eine perspektivische Ansicht, Fig. 3b ist eine Seitenansicht analog zu Fig. 2, Fig. 3c ist eine Vorderansicht der Flügelnut 9. Wie in Fig. 3c zu erkennen ist, weisen die Nutseitenflächen 6 in der Nähe des Nutgrunds 8 eine Hinterschneidung 7 auf, die aus Bogenabschnitten und geraden Stücken besteht. Die Flügelnut 9 weist an dem freien Ende 10 denselben konstanten Durchmesser wie in dem übrigen Bereich auf, so dass an dieser Stelle ein relativ starker Querschnittssprung vorliegt, der die erhöhten Spannungen hervorruft.The FIGS. 3a-c are enlarged views of the end portion of the wing groove 9 of a rotor according to the prior art. Fig. 3a is a perspective view Fig. 3b is a side view analogous to Fig. 2 . Fig. 3c is a front view of the wing groove 9. As in Fig. 3c can be seen, the groove side surfaces 6 in the vicinity of the groove bottom 8 on an undercut 7, which consists of bow sections and straight pieces. The wing groove 9 indicates the free end 10 of the same constant diameter as in the remaining area, so that there is a relatively large jump in the cross section, which causes the increased voltages at this point.

Die Figuren 4a - c zeigen ein erstes Ausführungsbeispiel der Erfindung.The FIGS. 4a-c show a first embodiment of the invention.

Anders als bei der in den Figuren 3a - c gezeigten Flügelnut ist der Übergang 11 zwischen dem nicht vergrößerten und dem vergrößerten Nutquerschnitt bogenförmig ausgebildet. Der Übergang 11 erstreckt sich dabei sowohl vom Nutgrund 12 als auch von den Hinterschneidungen 13 nach außen. Der bogenförmige Übergang 11 bewirkt eine vergleichsweise sanfte Kraftumlenkung, die neben dem vergrößerten Querschnitt an der Außenseite zu geringeren Spannungskonzentrationen führt.Unlike the one in the FIGS. 3a-c shown vane groove, the transition 11 between the non-enlarged and the enlarged groove cross section is arcuate. The transition 11 extends both from the groove base 12 and from the undercuts 13 to the outside. The arcuate transition 11 causes a comparatively gentle force deflection, which leads in addition to the enlarged cross-section on the outside to lower stress concentrations.

Die Figuren 5a - c zeigen ein zweites Ausführungsbeispiel der Erfindung. Die Flügelnut weist im Bereich der Hinterschneidung 13 einen radial nach außen, das heißt zur Öffnung der Flügelnut, verlaufenden Abschnitt 14 mit einem vergrößerten Durchmesser auf. Wie am besten in Fig. 5b zu erkennen ist, ist der Durchmesser des Abschnitts 14 konstant. Andererseits erstreckt sich der Bereich mit dem vergrößerten Querschnitt nicht vom Nutgrund 12 radial nach innen. Die erwünschte Spannungsreduzierung wird bei dieser Variante vor allem durch den vergrößerten Durchmesser erzielt.The FIGS. 5a-c show a second embodiment of the invention. The wing groove has in the region of the undercut 13 a radially outward, that is to the opening of the wing groove, extending portion 14 with an enlarged diameter. How best in Fig. 5b can be seen, the diameter of the section 14 is constant. On the other hand, the area with the enlarged cross section does not extend radially inward from the groove base 12. The desired voltage reduction is achieved in this variant, especially by the increased diameter.

Die Figuren 6a - c zeigen ein drittes Ausführungsbeispiel der Erfindung.The FIGS. 6a-c show a third embodiment of the invention.

In Fig. 6b ist erkennbar, dass der nicht vergrößerte Querschnitt des Abschnitts 15 der Flügelnut in einen Abschnitt 16 mit sich kontinuierlich vergrößerndem Querschnitt übergeht. Diese Variante zeichnet sich ebenfalls durch ein besonders niedriges Niveau der lokalen Spitzenspannungen aus. In Übereinstimmung mit der Variante gemäß den Figuren 5a - c weist der Bereich, der sich von dem Nutgrund 12 radial nach innen erstreckt, keinen vergrößerten Querschnitt auf.In Fig. 6b It can be seen that the non-enlarged cross-section of the section 15 of the wing groove merges into a section 16 with continuously increasing cross-section. This variant is also characterized by a particularly low level of local peak voltages. In accordance with the variant according to the FIGS. 5a-c For example, the portion extending radially inward from the groove bottom 12 does not have an enlarged cross section.

Die Fig. 7a - c zeigen ein viertes Ausführungsbeispiel der Erfindung. Der Grundaufbau dieses Endabschnitts des Rotors 1 gleicht dem in den Figuren 6a - c dargestellten, zusätzlich weist die Flügelnut im Bereich des Nutgrunds 12 einen radial nach innen verlaufenden Abschnitt 17 mit einem vergrößerten Querschnitt auf. Der vergrößerte Abschnitt 18, der sich beiderseits der Hinterschneidungen 13 erstreckt, ist wie in den Figuren 6a - c dargestellt aufgebaut, er entspricht somit dem Abschnitt 16 von Fig. 6. Die an der Seitenfläche des Rotors 1 gebildete Öffnung, die aus den Begrenzungen der Abschnitte 17, 18 besteht, ist näherungsweise oval ausgebildet, abgesehen von dem ebenen Nutgrund. Die Randlinien des Abschnitts 18 sind Bogenabschnitte eines Kreises, dessen Mittelpunkt sich näherungsweise im Bereich des unteren Endes 19 der Nutseitenflächen befindet.The Fig. 7a - c show a fourth embodiment of the invention. The basic structure of this end portion of the rotor 1 is similar to that in the FIGS. 6a - C shown, in addition, the wing groove in the region of the groove base 12 has a radially inwardly extending portion 17 with an enlarged cross-section. The enlarged portion 18 extending on either side of the undercuts 13 is as in Figs FIGS. 6a-c illustrated, it corresponds to the section 16 of Fig. 6 , The opening formed on the side surface of the rotor 1, which consists of the boundaries of the sections 17, 18, is approximately oval, except for the flat groove bottom. The marginal lines of the section 18 are arcuate sections of a circle whose center is approximately in the region of the lower end 19 of the Nutseitenflächen.

Bezugszahlenreference numerals

00
Flügelzellen-NockenwellenverstellerVane-type camshaft adjuster
11
Rotorrotor
22
Flügelnutvane
2a2a
Flügelwing
2b2 B
Kammerchamber
2c2c
Statorstator
33
Bohrungdrilling
44
Bohrungdrilling
55
Endabschnittend
66
Nutseitenflächegroove side
77
Hinterschneidungundercut
88th
Nutgrundgroove base
99
Flügelnutvane
1010
EndeThe End
1111
Übergangcrossing
1212
Nutgrundgroove base
1313
Hinterschneidungundercut
1414
Abschnittsection
1515
Abschnittsection
1616
Abschnittsection
1717
Abschnittsection
1818
Abschnittsection
1919
EndeThe End

Claims (10)

  1. Vane-cell camshaft adjuster (0) with a stator (2c) and a rotor which is hydraulically rotatable relative to the stator (2c), is connectable to a camshaft, and is provided with radially projecting vanes (2a) which are inserted in vane slots, characterized in that the end section (5) of the vane slot (2) on the camshaft side has an enlarged cross section.
  2. Vane-cell camshaft adjuster (0) according to Claim 1, characterized in that the vane slot (2), in the region of the slot base (12), has an undercut (13) with regard to the side faces of the slot.
  3. Vane-cell camshaft adjuster (0) according to Claim 2, characterized in that the vane slot, in the region of the slot base (12), has an enlarged cross section.
  4. Vane-cell camshaft adjuster (0) according to Claim 2 or 3, characterized in that the vane slot in the region of the undercut (13) has an enlarged cross section.
  5. Vane-cell camshaft adjuster (0) according to one of the preceding claims, characterized in that the transition (11) between the cross section of the slot which is not enlarged and the cross section which is enlarged, is formed arc-shaped.
  6. Vane-cell camshaft adjuster (0) according to Claim 2 or 3, characterized in that the vane slot in the region of the undercut (13) and the slot base (12) has a section (14, 16, 18) with an enlarged cross section, which extends radially outwards.
  7. Vane-cell camshaft adjuster (0) according to Claim 6, characterized in that the section (14) with the enlarged cross section has at least approximately a constant cross section.
  8. Vane-cell camshaft adjuster (0) according to Claim 6, characterized in that the section (15) of the vane slot, the cross section of which is not enlarged, merges into a section (16) with continuously increasing cross section.
  9. Vane-cell camshaft adjuster (0) according to Claim 6, characterized in that the vane slot in the region of the slot base (12) has a section (17) with an enlarged cross section, which extends radially inwards.
  10. Vane-cell camshaft adjuster (0) according to Claim 9, characterized in that the section of the vane slot, the cross section of which is not enlarged, merges into a section with a continuously increasing cross section.
EP05739591A 2004-06-08 2005-05-10 Vane-type camshaft adjuster Expired - Fee Related EP1753941B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004027951A DE102004027951A1 (en) 2004-06-08 2004-06-08 Vane-type camshaft adjuster
PCT/EP2005/005039 WO2005121511A1 (en) 2004-06-08 2005-05-10 Vane-type camshaft adjuster

Publications (2)

Publication Number Publication Date
EP1753941A1 EP1753941A1 (en) 2007-02-21
EP1753941B1 true EP1753941B1 (en) 2008-11-26

Family

ID=34966652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05739591A Expired - Fee Related EP1753941B1 (en) 2004-06-08 2005-05-10 Vane-type camshaft adjuster

Country Status (7)

Country Link
US (1) US7588004B2 (en)
EP (1) EP1753941B1 (en)
JP (1) JP2008501886A (en)
KR (1) KR101179289B1 (en)
CN (1) CN1965149B (en)
DE (2) DE102004027951A1 (en)
WO (1) WO2005121511A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004027950A1 (en) * 2004-06-08 2006-02-16 Ina-Schaeffler Kg Vane-type camshaft adjuster
DE102007039852A1 (en) 2007-08-23 2009-02-26 Schaeffler Kg Timing adjustment device
US8449271B2 (en) * 2010-05-17 2013-05-28 GM Global Technology Operations LLC Engine assembly including camshaft with integrated pump
CN102284963A (en) * 2011-07-15 2011-12-21 海宁市新艺机电有限公司 Rotary shaver blade and shaver head with same
DE102011084944A1 (en) * 2011-10-21 2013-04-25 Schaeffler Technologies AG & Co. KG Integration of an axial bearing in a rotor
US9341089B2 (en) 2014-04-04 2016-05-17 RB Distribution, Inc. Camshaft phaser
CN103953408B (en) * 2014-04-30 2016-08-17 桂林电子科技大学 Electrodeless variable valve timing mechanism
CN105736083A (en) * 2014-12-12 2016-07-06 舍弗勒技术股份两合公司 camshaft phase adjuster
CN104863656B (en) * 2015-06-09 2017-10-17 吕元之 Changeable air valve high-density powder metallurgy VVT rotors and preparation method thereof

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3627340B2 (en) * 1996-01-30 2005-03-09 アイシン精機株式会社 Valve timing control device
JPH10184322A (en) 1996-12-24 1998-07-14 Aisin Seiki Co Ltd Valve timing control device
DE19844646C2 (en) * 1997-09-29 2003-04-10 Aisin Seiki Valve timing control device
DE19860418B4 (en) * 1998-12-28 2008-09-11 Schaeffler Kg Device for changing the timing of gas exchange valves of an internal combustion engine, in particular camshaft adjusting device with impeller
DE19962981A1 (en) * 1999-12-24 2001-07-05 Schaeffler Waelzlager Ohg Timing adjustment device for gas exchange valves, pref. hydraulic camshaft adjusting device IC engines with slotted steel sealing rings to seal gaps against pressure medium leakage
US6247434B1 (en) * 1999-12-28 2001-06-19 Borgwarner Inc. Multi-position variable camshaft timing system actuated by engine oil
JP2002097911A (en) * 2000-09-22 2002-04-05 Aisin Seiki Co Ltd Valve opening and closing timing control device
JP4487449B2 (en) * 2001-06-28 2010-06-23 アイシン精機株式会社 Valve timing control device
JP4595263B2 (en) * 2001-07-31 2010-12-08 アイシン精機株式会社 Valve timing control device
JP2003328709A (en) * 2002-03-08 2003-11-19 Aisin Seiki Co Ltd Valve timing control device
JP3906763B2 (en) 2002-08-28 2007-04-18 アイシン精機株式会社 Valve timing control device
JP2004346788A (en) 2003-05-21 2004-12-09 Aisin Seiki Co Ltd Vane, valve timing control device and sliding material

Also Published As

Publication number Publication date
US20080047390A1 (en) 2008-02-28
KR20070022719A (en) 2007-02-27
CN1965149B (en) 2011-06-01
CN1965149A (en) 2007-05-16
DE102004027951A1 (en) 2006-02-16
WO2005121511A1 (en) 2005-12-22
JP2008501886A (en) 2008-01-24
US7588004B2 (en) 2009-09-15
KR101179289B1 (en) 2012-09-03
DE502005006071D1 (en) 2009-01-08
EP1753941A1 (en) 2007-02-21

Similar Documents

Publication Publication Date Title
EP1753941B1 (en) Vane-type camshaft adjuster
EP2386731B1 (en) Hydraulic valve
DE3717190C2 (en)
DE102009054049B4 (en) Camshaft timing arrangement
EP1738081B1 (en) Radial oscillating motor, and method for the production thereof
DE102006004760A1 (en) Hydraulic camshaft adjuster
EP1752691A1 (en) Control spool valve and its manufacturing process
WO2008135420A1 (en) Camshaft adjuster for an internal combustion engine with improved design of the pressure chambers
DE102010046619A1 (en) Rotor for a camshaft adjuster and camshaft adjusting system
DE19708661B4 (en) Device for varying the valve timing of an internal combustion engine, in particular camshaft adjusting device according to the vane cell principle
DE19828817A1 (en) Turbine rotor with releasably connected blade disks
DE19808619A1 (en) Locking device for a device for changing the control times of gas exchange valves of an internal combustion engine, in particular for a vane cell adjustment device
WO2013087620A1 (en) Hydraulic valve
DE10082316B4 (en) Device for varying the valve timing of an internal combustion engine, in particular camshaft adjusting device with swivel impeller
DE10083949B4 (en) Rotary piston adjuster
EP2486249B1 (en) Camshaft arrangement
EP1370749B1 (en) Device for adjusting the angle of rotation of a camshaft of an internal combustion engine with regard to a drive gear
DE102004032141A1 (en) Phaser
EP1605141B1 (en) Vane type camshaft phaser
DE19932299A1 (en) Turning angle adjustment device for camshaft relative to crankshaft in IC engines has swivel vanes charged with hydraulic oil on underside when engine is running, to press vanes against inner face of outer rotor
WO2011157542A1 (en) Rotor for a camshaft adjuster and camshaft adjuster
DE102005007942B4 (en) Camshaft adjusting device for internal combustion engines of motor vehicles
EP1339953A1 (en) Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel
EP3517743A1 (en) Pivoting motor adjuster for a camshaft and camshaft assembly having a camshaft and a pivoting motor adjuster
DE2627973A1 (en) BEARING RING FOR THE BLADES OF A variable-pitch propeller

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20061110

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR HU IT

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR HU IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR HU IT

REF Corresponds to:

Ref document number: 502005006071

Country of ref document: DE

Date of ref document: 20090108

Kind code of ref document: P

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E005107

Country of ref document: HU

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090827

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005006071

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005006071

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005006071

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140214

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005006071

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140214

REG Reference to a national code

Ref country code: HU

Ref legal event code: GB9C

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER(S): SCHAEFFLER KG, DE

Ref country code: HU

Ref legal event code: FH1C

Free format text: FORMER REPRESENTATIVE(S): MESZAROSNE DONUSZ KATALIN, S.B.G. & K. SZABADALMI UEGYVIVOEI IRODA, HU

Representative=s name: SBGK SZABADALMI UEGYVIVOEI IRODA, HU

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005006071

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150213

REG Reference to a national code

Ref country code: HU

Ref legal event code: FH1C

Free format text: FORMER REPRESENTATIVE(S): SBGK SZABADALMI UEGYVIVOEI IRODA, HU

Representative=s name: SBGK SZABADALMI UEGYVIVOEI IRODA, HU

Ref country code: HU

Ref legal event code: GB9C

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER(S): SCHAEFFLER KG, DE; SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180525

Year of fee payment: 14

Ref country code: IT

Payment date: 20180524

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: HU

Payment date: 20180620

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180731

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005006071

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190511

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191203

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190531

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522