EP2300693A1 - Dephaseur hydraulique d'arbre a cames - Google Patents

Dephaseur hydraulique d'arbre a cames

Info

Publication number
EP2300693A1
EP2300693A1 EP09765567A EP09765567A EP2300693A1 EP 2300693 A1 EP2300693 A1 EP 2300693A1 EP 09765567 A EP09765567 A EP 09765567A EP 09765567 A EP09765567 A EP 09765567A EP 2300693 A1 EP2300693 A1 EP 2300693A1
Authority
EP
European Patent Office
Prior art keywords
camshaft adjuster
inner body
elements
camshaft
oil inlet
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.)
Granted
Application number
EP09765567A
Other languages
German (de)
English (en)
Other versions
EP2300693B1 (fr
Inventor
Bernhard Terfloth
Antonio Casellas
Rainer Schmitt
Eberhard Ernst
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.)
GKN Sinter Metals Holding GmbH
Original Assignee
GKN Sinter Metals Holding GmbH
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 GKN Sinter Metals Holding GmbH filed Critical GKN Sinter Metals Holding GmbH
Publication of EP2300693A1 publication Critical patent/EP2300693A1/fr
Application granted granted Critical
Publication of EP2300693B1 publication Critical patent/EP2300693B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01L1/02—Valve drive
    • F01L1/022—Chain drive
    • 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
    • F01L1/02—Valve drive
    • F01L1/024—Belt drive
    • 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
    • F01L1/02—Valve drive
    • F01L1/026—Gear drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34459—Locking in multiple positions
    • 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
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices
    • 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
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • 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
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a hydraulic camshaft adjuster for a camshaft of an internal combustion engine.
  • a camshaft adjuster By means of a camshaft adjuster, it is possible to change a phase angle of a camshaft of an internal combustion engine relative to a crankshaft of the internal combustion engine driving the camshaft. As a result, a fuel consumption and raw emissions of the internal combustion engine can be lowered and improve a performance and torque characteristics of the internal combustion engine.
  • a rempligelzellenversteller of the generic type is known for example from the document DE 10 2004 022 097 A1.
  • the wellgelzellenversteller thereby comprises an outer body which is drivable via a crankshaft, and an inner lying to the outer body arranged inner body, which is fixedly connected to a camshaft.
  • a controlled supply of oil from an oil circuit of an internal combustion engine to individual hydraulic or working chambers of the camshaft adjuster formed in the inner body ⁇ lzulauf- and oil drain lines and a associated with the oil supply pressure build-up in the oil inlet and oil drain lines and the chambers of the inner body the outer body adjusted and thus changed the phase angle of the camshaft relative to the crankshaft.
  • Both the outer body and the inner body of such a rempligelzellenverstellers can be known sintered technology.
  • metal powders are pressed into workpieces or pressings, also known as green compacts, and the workpieces are subsequently sintered.
  • the workpieces are given their final strength by the metal powders forming a coherent crystal structure as they pass through a sintering furnace through diffusion and recrystallization processes.
  • a height dimension of the workpieces obtained during pressing of the metal powder can deviate from a desired height dimension.
  • a hydraulic camshaft adjuster for a camshaft of an internal combustion engine is proposed, which is designed in the manner of a vane-type adjuster.
  • the camshaft adjuster includes an externally drivable by means of a crankshaft of the internal combustion engine outer body with at least one hydraulic chamber, and a preferably coaxially disposed inside the inner body to the inner body, which is firmly connected to the camshaft. Under a fixed connection is a positive and / or non-positive connection between the inner body and the camshaft to understand.
  • the inner body comprises at least one pivoting wing, which extends in the radial direction into the hydraulic chamber and thereby divides the hydraulic chamber into a first working chamber and a second working chamber.
  • the inner body further comprises at least an oil inlet and outlet line extending from an inside of the shell to a shell outside of the inner body and up to one of the two working chambers, the inner body being exposed to the outside to produce a controlled hydraulic pressure in the oil inlet and outlet conduit and in one of the working chambers.
  • body is pivotable for adjusting the camshaft.
  • the inner body is further joined together at least from a first element and a second element, wherein the two elements each have at least one geometry on mutually facing end sides, which together with the respective other element forms the oil inlet and oil drain line of the inner part.
  • the two elements have a substantially radial extent over the circumference.
  • the two elements have a substantially axial extent over the circumference.
  • a geometry is to be understood as meaning a recess in the respective element which extends from the shell inner side to the outer shell side of the inner body and which does not penetrate the element in its longitudinal direction.
  • An advantage of the proposed camshaft adjuster is that there is no further machining required in connection with the above-described sintering production of such inner bodies in order to produce the oil feed and oil drain line.
  • the further machining can also include a deburring of the oil inlet and outlet line. Rather, this ⁇ lzulauf- and ⁇ lablauftechnisch created by the joining of the two elements, which together form the inner body. The parting line formed by the two elements closes hydraulically tight.
  • the inner body preferably has at least two pivoting wings which each extend into a hydraulic chamber of the outer body.
  • the inner body has four pivoting wings which extend each extending into a hydraulic chamber of the outer body.
  • the inner body has five pivoting vanes which each extend into a hydraulic chamber of the outer body.
  • At least one of the two elements has at least one projection on the front side, which engages in a form-fitting manner for connecting the two elements into a corresponding recess of the other element and forms an interference fit with the recess.
  • the projection may be formed in the manner of a claw or a web, wherein a web is a similar to a feather trained projection to understand.
  • at least one of the two elements on the front side a plurality of projections which engage positively in the joining of the two elements in corresponding recesses of the other element, wherein under the projections both claw-like and web-like projections may be.
  • the two joined elements are identical and each have at least one extending from the shell inside to the shell outside projection which positively engages the connection of the two elements in a corresponding recess of the other element and thereby with the recess forms an interference fit, wherein the two projections together with the associated recesses each form a ⁇ lzulauf- and oil drain line of the inner part.
  • An advantage of this embodiment is that in connection with the above-described sintering production of such inner body only a pressing tool is needed to produce workpieces of the same configuration.
  • the oil inlet and outlet pipe preferably extends in the radial direction from the shell inside to the outer shell side of the inner body.
  • the oil inlet and outlet pipe preferably has a quadrangular cross-sectional shape, which is due to the frontal geometries of the two elements joined together.
  • the frontal geometries can also form other cross-sectional shapes, such as a circular or a triangular shape.
  • a spring is arranged in the other working chamber between the outer body and the pivoting wing, which acts in a restoring manner in relation to the pivoting of the inner body.
  • At least a first oil inlet and oil drain line and a second oil inlet and ⁇ lab- are provided, wherein the first oil inlet and drain line extends to one of the two working chambers, while the second ⁇ lzulauf- and Oil drain line extends to the other working chamber.
  • the pivoting wing may be formed integrally with the inner body. Alternatively, the pivoting wing may be inserted into the inner body on the outside of the jacket.
  • a receptacle for the swing-wing is provided on the outer shell side of at least one of the two elements.
  • the recording can also be performed in two parts and be provided on both elements depending on a receptacle for the swing-wing.
  • the receptacle is preferably formed on the projection. Further, the receptacle is preferably formed in the manner of a slot and aligned with the longitudinal direction of the inner body.
  • the pivoting wing is preferably guided movably in the receptacle.
  • a planetary gear is arranged between the pivoting wing and the outer body, wherein on the outer body a corresponding to the planetary gear segment is formed, which cooperates with the planetary gear, and wherein on the pivoting wing a pocket is formed in the the planetary gear is inserted.
  • a planetary gear is disposed on both sides of the hydraulic chamber between a hollow cylindrical core of the inner body and the outer body, wherein on both sides of the hydraulic chamber on the hollow cylinder core corresponding to the associated planet gear segment is formed, which cooperates with the planetary gear, and wherein to both Side of the hydraulic chamber on the outer body, a pocket is formed, in which the associated planetary gear is used.
  • both the outer body and the two joined elements of the inner body are formed as sintered parts.
  • the two elements are already as compacts or green compacts joined together, which receive as workpieces their final strength during sintering.
  • FIG. 1 is a front view of a unit of a vane cell
  • FIG. 2 is a perspective view of the unit shown in FIG. 1; FIG.
  • FIG. 3 is a side view of the unit shown in FIG. 1,
  • FIG. 4 shows a sectional view along the section line A - A in the direction of the arrows shown in FIG. 3
  • FIG. 5 shows a further sectional view along the section line A - A shown in FIG. 3, in the direction opposite to the direction of the arrows,
  • FIG. 7 shows an exploded view of a first embodiment of an inner body in a first perspective view
  • FIG. 88 shows an exploded view of the first embodiment of the inner body in a second perspective view
  • FIG. 9 is a perspective view of the first embodiment of the inner body in an assembled state
  • 10 is a perspective view of a first element of the first embodiment of the inner body
  • 11 is a perspective view of a second element of the first embodiment of the inner body
  • FIG. 12 is an exploded view of a second embodiment of the inner body
  • FIG. 13 is a perspective view of the second embodiment of the inner body in an assembled state
  • FIG. 14 is a perspective view of a first element of the second embodiment of the inner body
  • FIG. 15 is a perspective view of a second element of the second embodiment of the inner body
  • Fig. 16 is a perspective view of a known in the prior art
  • FIG. 18 is a perspective view of a third embodiment of the inner body in an assembled state
  • FIG. 19 is a perspective view of an element of the third embodiment of the FIG inside the body
  • FIG. 20 shows a perspective view of a fourth embodiment of the inner body in an assembled state
  • FIG. 21 is a perspective view of an element of the fourth embodiment of the inner body
  • FIG. 22 is a front view of another unit of a vane-type adjuster
  • the assembly 2 forms a unit of a hydraulic camshaft adjuster in the form of a so-called rempligelzellenverstellers.
  • the outer body 4 is drivable by means of a crankshaft of an internal combustion engine, such as a gear drive, wherein a toothed belt drive or a chain drive is possible.
  • the inner body 6, however, is firmly connected to a camshaft of the internal combustion engine, which is insertable into the circular recess 26. Under a solid compound is a positive and / or non-positive connection to understand.
  • the outer body 4 comprises Preferably, five hydraulic chambers 18, which are formed by five radially inwardly projecting body portions 20 of the outer body 4.
  • a pivot wing 8 of the inner body 6 extends in the radial direction.
  • the individual swing vanes 8 divide the individual hydraulic chambers 18 into a first working chamber 22 and a second working chamber 24.
  • a drive torque of the crankshaft is transmitted to the camshaft adjuster by means of the outer body 4 introduced and transmitted via the working chambers 22, 24 on the inner body 6, which is fixedly connected to the camshaft.
  • the inner body 6 preferably comprises ten oil inlet and oil drain lines 14, 16, each extending preferably in the radial direction from an inner shell side 10 to a shell outer side 12 of the inner body 6 to one of the ten working chambers 22, 24, so that each of the five Hydraulikkammem 18th two of the ten oil inlet and ⁇ lablauftechnischen 14, 16 are assigned.
  • the inner body 6 is pivoted relative to the outer body 4 for adjusting the camshaft in one direction. Such pivoting in the clockwise direction is illustrated in FIG. 6 by means of arrows, in which the lines 14 and the associated working chambers 22 are subjected to the controlled hydraulic pressure.
  • the lines 14 in this illustration act as oil feed lines, while the lines 16 function as oil drain lines.
  • the arrows shown in Fig. 6 further illustrate the flow direction of the oil.
  • the individual hydraulic chambers 18 are designed to be concave in accordance with the circular movement described by the vanes 8, so that a pivoting movement of the inner body 6 relative to the outer body 4 can be initiated via the pivot vanes 8.
  • the pivoting vanes 8, which are movably guided in the individual receptacles 36 are pressed against the outer body 4 by the action of a centrifugal force, the individual working chambers 22, 24 being sealed against one another.
  • the outer wing 4 facing pivot wing sides 8a are preferably flat, so that the sealing of the working chambers 22, 24 via a pressure of the respective longitudinal edges of the swing wing sides 8a takes place.
  • the swing wing sides 8a may also be designed convex.
  • Sealing strip can also be arranged on the individual radial projections 21 of the outer body 4 in a groove provided for this purpose, so that the individual hydraulic chambers 18 are sealed against each other.
  • a spring between the outer body and the associated pivoting wing is arranged in the individual hydraulic chambers in one of two working chambers, which acts with respect to a pivoting of the inner body restoring.
  • the inner body 6 illustrated in Figs. 7-9, 12 and 13 is preferably assembled from a first element 28 and a second element 30 which describe a substantially hollow cylindrical core.
  • FIGS. 7 to 9 illustrate a first embodiment of the inner body 6, while FIGS. 12 and 13 illustrate a second embodiment of the inner body 6.
  • Both the outer body 4 and the two joined elements 28, 30 are preferably formed as sintered parts.
  • the two elements 28, 30 have on facing end faces 38, 40 in each case five geometries 39, 41, 50, 52, which together with the respective other element 28, 30 form the oil inlet and oil drain lines 14, 16 of the inner body 6.
  • the two elements 28, 30 have a substantially radial extent over the circumference.
  • the two elements 28, 30 have a substantially axial extent over the circumference.
  • a geometry 39, 41, 50, 52 means a recess in the respective element 28, 30 extending from the shell inner side 10 to the outer shell 12 of the inner body 6, which does not penetrate the element 28, 30 in its longitudinal direction.
  • the oil inlet and outlet lines 14, 16 preferably have a quadrangular cross-sectional shape, which is variable in terms of their dimensions in the first embodiment of the inner body 6 and initially increases in the radial direction from the inner shell side 10 and then up to the outer shell side 12th reduced.
  • the geometries 39, 41 each have a curvature 39a, 41a, which, however, are irrelevant with regard to the mode of operation of the vane cell adjuster. Rather, such a configuration of the two elements 28, 30 is based in a design of a pressing tool, which aims to reinforce the pressing tool.
  • the quadrangular cross-sectional shape of the second embodiment is consistently constant with respect to its dimensions.
  • the element 28 comprises, on the front side or on the end faces 40 facing the element 30, five projections 34 which are each designed in the manner of a claw and which respectively correspond to one another Recess 32 of the element 30 engage positively.
  • the projections 34 in each case form an interference fit with the associated recesses 32.
  • the parting line formed by the two elements 28, 30 also closes hydraulically tight.
  • the individual preferably integrally formed pivoting vanes 8 are inserted into the inner body 6 on the outer side 12 of the casing.
  • five preferably designed in the manner of a slot receptacles 36 are provided for the swing vanes 8, which are each formed on one of the projections 34 on the outer shell side 29 of the element 28.
  • the receiving slots 36 are preferably aligned to the longitudinal direction of the inner body (6).
  • the element 28 comprises, on the front side or on the end face 40 facing the element 30, five projections 42 and five projections 44 which are each designed in the manner of a web or a feather key and which respectively engage in a corresponding recess or groove 46, 48 of the element 30 positively.
  • the individual webs 42, 44 and recesses 46, 48 extend in the radial direction of the inner body 6.
  • the projections 42, 44 in each case with the associated recesses 46, 48 each have a press fit.
  • the parting line formed by the two elements 28, 30 also closes hydraulically tight.
  • the two elements 28, 30 each comprise, on the front side, five grooves 50, each of which is assigned to one of them.
  • Neten casing inside 33, 35 extend to an associated outer shell side 29, 31 and in the assembled state of the two elements 28, 30 form a quadrangular cross-sectional shape, which is invariable in terms of their dimensions in contrast to the first embodiment.
  • the individual slot receptacles 36 are designed in two parts.
  • five receptacles 36a are provided on the outer shell side 29 of the element 28, while on the outer shell side 31 of the element 30 five receptacles 36b are provided, which terminate flush with the receptacles 36a.
  • Figures 16 and 17 illustrate a prior art embodiment of a one-piece inner body 6 sintered from a metal powder mixture.
  • the oil inlet and outlet lines 14, 16 have been drilled into the inner body 6 following a sintering process.
  • the bores 54, 56, 58 are provided for so-called spring-loaded and hydraulically unlockable locking pins, which engage in the bores 54, 56, 58 in order to prevent unwanted pivoting of the inner body 6 relative to an outer body, not shown.
  • Fig. 18 illustrates a third embodiment of the inner body 6, in which the two assembled elements 29b - one of which is illustrated in Fig. 19 - are formed identically, and each preferably five from the shell inside 10 to the outer shell side 12 of the inner body 6 extending projections 64 which engage positively for connection of the two elements 29b in a corresponding recess 62 of the other element 29b and thereby form an interference fit with the associated recesses 62.
  • the projections 64, together with the associated recesses 62 respectively form an oil inlet and oil discharge line 14, 16 of the inner part 6.
  • An advantage of this embodiment is that, in connection with the above-described sintered production of such internal bodies only a pressing tool is required to produce workpieces of the same configuration.
  • FIG. 20 illustrates a fourth embodiment of the inner body 6, after which also the two joined elements 29b are formed identically.
  • FIG. 21 illustrates one of the two elements 29b.
  • swing vanes 8 formed integrally with the hollow cylindrical core of the respective element 29b are provided (FIG. 21).
  • one of the pivoting vanes 8 extends radially outward from the hollow cylindrical core of the inner body 6.
  • the projections 64 and recesses 62 are configured analogously to the third embodiment of the inner body 6 (FIGS. 18 and 19).
  • FIG. 22 shows an alternative arrangement 2 of a preferably integrally formed outer body 4 and a preferably two-part inner body 6, which is preferably arranged coaxially inwardly to the outer body 4.
  • the arrangement 2 preferably forms four hydraulic chambers 18, in each of which a pivoting wing 8 of the inner body 6 extends.
  • the individual pivoting vanes 8 are preferably formed integrally with the hollow cylindrical core of the inner body 6. Zwi see the individual swing wings 8 and the outer body 4 is a planetary gear 68 a arranged, which is inserted into a pocket 70 a, which is formed on the pivoting wing 8.
  • a corresponding to the planetary gear 68a gear segment 66 is formed at the respective individual planetary gears 68a associated body portions of the outer body 4, which cooperates with the planetary gear 68a.
  • the individual planet gears 68a thereby seal the working chambers 22, 24 from each other hydraulically.
  • a planetary gear 68b is arranged on both sides of the respective hydraulic chambers 18 between the hollow cylindrical core of the inner body 6 and the outer body 4.
  • the individual planet gears 68b are inserted into a pocket 70b which is formed on the respective radially inwardly projecting body portion 20 of the outer body 4.
  • a gear segment 72 is further formed on the hollow cylindrical core of the inner body 6, which is formed according to the associated planetary gear 68b and cooperates with this.
  • the individual planet gears 68b each seal two adjacent hydraulic chambers 18 against each other hydraulically.

Landscapes

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

Abstract

L'invention concerne un déphaseur hydraulique d'arbre à cames (2) avec un corps extérieur (4) pouvant être entraîné et comportant au moins une chambre hydraulique (18) et un corps intérieur (6), monté à l'intérieur et reposant contre le corps extérieur (4), pouvant être solidarisé avec un arbre à cames et possédant au moins une palette (8) qui s'étend dans la chambre hydraulique dans la direction radiale et qui subdivise ainsi la chambre hydraulique en une première chambre de travail (22) et une deuxième chambre de travail (24). Le corps intérieur (6) possède en outre au moins une conduite d'admission d'huile et d'évacuation d'huile (14, 16) qui s'étend entre une face interne de l'enveloppe (10) et une face externe de l'enveloppe (12) du corps intérieur (6) pour déboucher dans l'une des deux chambres de travail (22). Le corps intérieur (6) est composé d'au moins un premier élément (28) et un deuxième élément (30) assemblés l'un avec l'autre. Les deux éléments possèdent sur les faces frontales (38, 40) tournées l'une vers l'autre au moins une géométrie (39, 41, 50, 52) qui, avec l'autre élément considéré, forme la conduite d'admission et d'évacuation d'huile de la partie intérieure.
EP09765567A 2008-06-18 2009-06-10 Dephaseur hydraulique d'arbre a cames Active EP2300693B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008028640A DE102008028640A1 (de) 2008-06-18 2008-06-18 Hydraulischer Nockenwellenversteller
PCT/EP2009/004172 WO2009152987A1 (fr) 2008-06-18 2009-06-10 Déphaseur hydraulique d'arbre à cames

Publications (2)

Publication Number Publication Date
EP2300693A1 true EP2300693A1 (fr) 2011-03-30
EP2300693B1 EP2300693B1 (fr) 2012-08-15

Family

ID=41056926

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09765567A Active EP2300693B1 (fr) 2008-06-18 2009-06-10 Dephaseur hydraulique d'arbre a cames

Country Status (7)

Country Link
US (1) US8550046B2 (fr)
EP (1) EP2300693B1 (fr)
JP (1) JP5313342B2 (fr)
CN (1) CN102124188B (fr)
DE (1) DE102008028640A1 (fr)
ES (1) ES2393085T3 (fr)
WO (1) WO2009152987A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018010714A2 (fr) 2016-07-14 2018-01-18 Schaeffler Technologies AG & Co. KG Rotor en plusieurs parties d'un déphaseur d'arbre à cames, le rotor présentant au moins un trou de réception cylindrique s'étendant à travers toutes les parties du rotor
US10267188B2 (en) 2014-08-25 2019-04-23 Schaeffler Technologies AG & Co. KG Rotor for a hydraulic camshaft adjuster and manufacturing method for a rotor for a camshaft adjuster

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009038664B4 (de) * 2009-08-24 2018-02-01 Audi Ag Stelleinrichtung für eine Brennkraftmaschine sowie Ventiltrieb einer Brennkraftmaschine und entsprechende Brennkraftmaschine
DE102009053600B4 (de) * 2009-11-17 2021-07-22 Schaeffler Technologies AG & Co. KG Rotor eines Nockenwellenverstellers, Verfahren zum Herstellen eines Rotors sowie Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle eines Motors
DE102010008006A1 (de) * 2010-02-15 2011-08-18 Schaeffler Technologies GmbH & Co. KG, 91074 Flügelrad einer Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010034014B4 (de) 2010-08-11 2015-06-25 Schwäbische Hüttenwerke Automotive GmbH Sinterverbund und Verfahren zu seiner Herstellung
DE102010050606A1 (de) * 2010-11-05 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Rotor für einen Nockenwellenversteller sowie Nockenwellenversteller
DE102011117856A1 (de) * 2011-11-08 2013-05-08 Gkn Sinter Metals Holding Gmbh Mehrteilige, gefügte Rotoren in hydraulischen Nockenwellenverstellern mit Fügedichtprofilen und Verfahren zur Herstellung der Rotoren
DE102012212858A1 (de) * 2012-07-23 2014-01-23 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012219949A1 (de) * 2012-10-31 2014-04-30 Schaeffler Technologies Gmbh & Co. Kg Rotor eines Nockenwellenverstellers, Nockenwellenversteller mit einem solchen Rotor und Verfahren zum Herstellen eines Rotors
DE102013009729A1 (de) 2013-06-11 2014-12-11 Daimler Ag Nockenwellenversteller
DE102013217017A1 (de) 2013-08-27 2015-03-05 Schaeffler Technologies Gmbh & Co. Kg Mehrteiliger Rotor für einen hydraulischen Nockenwellenversteller mit Ölversorgung der Druckkammern durch die Flügel
DE102013217015A1 (de) 2013-08-27 2015-03-05 Schaeffler Technologies Gmbh & Co. Kg Durch den Rotor gehende direkte Ölversorgungsleitung einer Verriegelungspinbetätigungstasche
DE102013015676A1 (de) * 2013-09-23 2015-03-26 Gkn Sinter Metals Holding Gmbh Verfahren zur Herstellung eines Sinterteils mit höhenpräziser Formteilhöhe sowie Teilesatz aus Sinterfügeteilen
DE102013015675A1 (de) 2013-09-23 2015-03-26 Gkn Sinter Metals Holding Gmbh Rotor für einen Nockenwellenversteller, Teileset zur Herstellung eines Rotors für einen Nockenwellenversteller sowie Verfahren zur Herstellung eines gefügten Bauteils, bevorzugt eines Rotors für einen Nockenwellenversteller
DE102013219139B4 (de) * 2013-09-24 2020-09-24 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102013222620A1 (de) 2013-11-07 2014-11-13 Schaeffler Technologies Gmbh & Co. Kg Gebauter Rotor eines hydraulischen Nockenwellenverstellers mit zwei Hälf-ten zur Federeinhängung
DE102013226445B4 (de) 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Nockenwellenzentrierung im geteilten Rotor eines hydraulischen Nockenwellenverstellers und zugehöriges Herstellungsverfahren
DE102013226449B4 (de) 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Spanlos gefertigte Ölkanäle in einem geteilten Rotor für einen hydraulischen Nockenwellenversteller
DE102013226466A1 (de) * 2013-12-18 2015-06-18 Schaeffler Technologies AG & Co. KG Aufbauprinzip eines geteilten Rotors für einen hydraulischen Nockenwellenversteller
DE102013226454B4 (de) 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Verbindungsprinzip eines mehrteiligen Rotors für einen hydraulischen Nockenwellenversteller
DE102013226460B4 (de) * 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Verdrehsicherung des Innenteils eines geteilten Rotors für einen hydraulischen Nockenwellenversteller
DE102014209178B4 (de) 2014-03-20 2020-12-03 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller, zumindest zweiteiliger Rotor des hydraulischen Nockenwellenverstellers sowie Verfahren zur Herstellung des Rotors des hydraulischen Nockenwellenverstellers
DE102014209181A1 (de) 2014-05-15 2015-11-19 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller, Verwendung eines zumindest zweiteiligen Rotors sowie Verfahren zum Betrieb eines hydraulischen Nockenwellenverstellers
JP5987868B2 (ja) * 2014-07-22 2016-09-07 株式会社デンソー バルブタイミング調整装置
DE102014215286B4 (de) 2014-08-04 2017-10-26 Schaeffler Technologies AG & Co. KG Zweiteiliger Rotor eines hydraulischen Nockenwellenverstellers
DE102014216850A1 (de) 2014-08-25 2015-06-25 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller sowie Herstellungsverfahren eines hydraulischen Nockenwellenverstellers
DE102014112377A1 (de) * 2014-08-28 2016-03-03 Robert Bosch Automotive Steering Gmbh Herstellverfahren für komponenten eines schwenkmotors für ein lenksystem
DE102015201873A1 (de) * 2015-02-03 2016-08-18 Gkn Sinter Metals Engineering Gmbh Leises Zahnrad
DE102016210932A1 (de) 2016-06-20 2017-12-21 Schaeffler Technologies AG & Co. KG Verfahren zur Herstellung eines Rotors für einen Nockenwellenversteller
DE102016220830A1 (de) 2016-10-24 2018-04-26 Schaeffler Technologies AG & Co. KG Rotor mit durch je zwei Platten ausgeformten Fluidleitkanal für einen Nockenwellenversteller und Nockenwellenversteller
DE102017114995B4 (de) 2017-07-05 2020-11-26 Schaeffler Technologies AG & Co. KG Rotor für Nockenwellenversteller
DE102017128731B4 (de) * 2017-12-04 2021-12-09 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller zur variablen Ventilsteuerung in einer Brennkraftmaschine
DE102018117950A1 (de) * 2018-07-25 2020-01-30 Schaeffler Technologies AG & Co. KG Wellgetriebe

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19756015A1 (de) * 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
JP2000240414A (ja) * 1999-02-16 2000-09-05 Mitsubishi Electric Corp ベーン式油圧アクチュエータ
US6311655B1 (en) * 2000-01-21 2001-11-06 Borgwarner Inc. Multi-position variable cam timing system having a vane-mounted locking-piston device
US6412462B1 (en) * 2000-01-18 2002-07-02 Delphi Technologies, Inc. Cam phaser apparatus having a stator integral with a back plate or a front cover plate
DE102004024221A1 (de) * 2003-08-15 2005-03-10 Ina Schaeffler Kg Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung ihrer Nockenwelle gegenüber ihrer Kurbelwelle
DE102004024222A1 (de) * 2003-08-15 2005-03-10 Ina Schaeffler Kg Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE102004022097A1 (de) 2004-05-05 2005-12-08 Daimlerchrysler Ag Hydraulischer Nockenwellenversteller und Verfahren zur Montage desselben
JP4110479B2 (ja) * 2004-09-28 2008-07-02 アイシン精機株式会社 弁開閉時期制御装置
DE102004047817B3 (de) * 2004-09-29 2005-12-08 Gkn Sinter Metals Gmbh Nockenwellenversteller für eine Verbrennungskraftmaschine
DE102005026553B3 (de) * 2005-06-08 2006-09-07 Hydraulik-Ring Gmbh Schwenkmotor mit verringerter Leckage
DE102005037525A1 (de) * 2005-08-09 2007-02-15 Schaeffler Kg Verfahren zur Serienherstellung eines Bauteils für ein Kraftfahrzeug
JP4640616B2 (ja) * 2006-08-23 2011-03-02 アイシン精機株式会社 弁開閉時期制御装置
JP2008057397A (ja) * 2006-08-30 2008-03-13 Aisin Seiki Co Ltd 弁開閉時期制御装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009152987A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10267188B2 (en) 2014-08-25 2019-04-23 Schaeffler Technologies AG & Co. KG Rotor for a hydraulic camshaft adjuster and manufacturing method for a rotor for a camshaft adjuster
WO2018010714A2 (fr) 2016-07-14 2018-01-18 Schaeffler Technologies AG & Co. KG Rotor en plusieurs parties d'un déphaseur d'arbre à cames, le rotor présentant au moins un trou de réception cylindrique s'étendant à travers toutes les parties du rotor
DE102016212861A1 (de) 2016-07-14 2018-01-18 Schaeffler Technologies AG & Co. KG Mehrteiliger Rotor eines Nockenwellenverstellers, wobei der Rotor zumindest eine sich durch alle Rotorteile erstreckende zylindrische Aufnahmebohrung hat

Also Published As

Publication number Publication date
JP2011524495A (ja) 2011-09-01
ES2393085T3 (es) 2012-12-18
DE102008028640A1 (de) 2009-12-24
WO2009152987A1 (fr) 2009-12-23
US20110126785A1 (en) 2011-06-02
EP2300693B1 (fr) 2012-08-15
JP5313342B2 (ja) 2013-10-09
US8550046B2 (en) 2013-10-08
CN102124188A (zh) 2011-07-13
CN102124188B (zh) 2014-10-29

Similar Documents

Publication Publication Date Title
EP2300693B1 (fr) Dephaseur hydraulique d'arbre a cames
EP1752691B1 (fr) Vanne de commande et son procédé de fabrication
DE10358888B4 (de) Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
EP2470756B1 (fr) Vanne de commande
DE102010050606A1 (de) Rotor für einen Nockenwellenversteller sowie Nockenwellenversteller
DE102013226445B4 (de) Nockenwellenzentrierung im geteilten Rotor eines hydraulischen Nockenwellenverstellers und zugehöriges Herstellungsverfahren
DE102016125659B4 (de) Grünling einer Stator-Deckel-Einheit
DE102005052346A1 (de) Ölpumpe
WO1999043928A1 (fr) Unite de blocage pour un dispositif servant a modifier le calage de soupapes de changement des gaz d'un moteur a combustion interne, notamment pour une unite de reglage de cellules en ailettes
DE102012200099A1 (de) Nockenwellenversteller
WO2015090296A1 (fr) Principe de construction d'un rotor divisé pour un dispositif de déphasage d'arbre à cames hydraulique
EP1811139B1 (fr) Rotor d'un dispositif de réglage d'arbre à cames
DE102006019607A1 (de) Nockenwellenversteller
WO2001031174A1 (fr) Dispositif d'ajustement hydraulique d'angle de rotation d'un arbre par rapport a un pignon d'entree
DE102012203114A1 (de) Einlegeteil für Nockenwellenversteller mit Mittenverriegelung
DE10082316B4 (de) Vorrichtung zum Variieren der Ventilsteuerzeiten einer Brennkraftmaschine, insbesondere Nockenwellen-Verstelleinrichtung mit Schwenkflügelrad
DE102013226454A1 (de) Verbindungsprinzip eines mehrteiligen Rotors für einen hydraulischen Nockenwellenversteller
DE102013226449B4 (de) Spanlos gefertigte Ölkanäle in einem geteilten Rotor für einen hydraulischen Nockenwellenversteller
DE102005033679B4 (de) Ölpumpe
DE19781754C1 (de) Flügelzellen-Verstelleinrichtung für eine Nockenwelle in einer Brennkraftmaschine
WO2005061860A1 (fr) Dispositif pour modifier les temps de commande de soupapes d'echange gazeux d'un moteur a combustion interne, en particulier un dispositif d'ajustement de pistons de rotation permettant un ajustage de l'angle de rotation entre un arbre a cames et un vilebrequin
DE102011000591A1 (de) Zentralventil
EP3276127B1 (fr) Machine hydraulique à roue dentée
DE4417959C2 (de) Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine
EP1783331A1 (fr) Système comprenant un arbre à cames d'admission, un arbre à cames d'échappement et un variateur de phase, et utilisation de ce système

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: 20101202

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

17Q First examination report despatched

Effective date: 20120202

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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 570964

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120815

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502009004430

Country of ref document: DE

Effective date: 20121011

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2393085

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20121218

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120815

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

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121115

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121215

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121217

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121116

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

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

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

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

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

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: 20130516

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

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20121115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502009004430

Country of ref document: DE

Effective date: 20130516

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

BERE Be: lapsed

Owner name: GKN SINTER METALS HOLDING G.M.B.H.

Effective date: 20130630

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: BE

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

Effective date: 20130630

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

Ref country code: CH

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

Effective date: 20130630

Ref country code: LI

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

Effective date: 20130630

Ref country code: IE

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

Effective date: 20130610

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: VON KREISLER SELTING WERNER - PARTNERSCHAFT VO, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KNH PATENTANWAELTE KAHLHOEFER NEUMANN ROESSLER, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KAHLHOEFER ROESSLER KREUELS PATENTANWAELTE PAR, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: VON KREISLER SELTING WERNER - PARTNERSCHAFT VO, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KNH PATENTANWAELTE KAHLHOEFER NEUMANN ROESSLER, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KAHLHOEFER ROESSLER KREUELS PATENTANWAELTE PAR, DE

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

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

Ref country code: LU

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

Effective date: 20130610

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20090610

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20120815

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 570964

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140610

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

Ref country code: AT

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

Effective date: 20140610

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KARO IP PATENTANWAELTE KAHLHOEFER ROESSLER KRE, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KNH PATENTANWAELTE KAHLHOEFER NEUMANN ROESSLER, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KAHLHOEFER ROESSLER KREUELS PATENTANWAELTE PAR, DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

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

Ref country code: FR

Payment date: 20170621

Year of fee payment: 9

Ref country code: GB

Payment date: 20170626

Year of fee payment: 9

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

Ref country code: IT

Payment date: 20170622

Year of fee payment: 9

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

Ref country code: ES

Payment date: 20170703

Year of fee payment: 9

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KARO IP PATENTANWAELTE KAHLHOEFER ROESSLER KRE, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502009004430

Country of ref document: DE

Representative=s name: KAHLHOEFER ROESSLER KREUELS PATENTANWAELTE PAR, DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180610

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: 20180630

Ref country code: GB

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

Effective date: 20180610

Ref country code: IT

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

Effective date: 20180610

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20190916

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

Ref country code: ES

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

Effective date: 20180611

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

Effective date: 20230527

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

Ref country code: DE

Payment date: 20230620

Year of fee payment: 15