EP2322769B1 - Camshaft drive with a camshaft and a camshaft hub - Google Patents

Camshaft drive with a camshaft and a camshaft hub Download PDF

Info

Publication number
EP2322769B1
EP2322769B1 EP10189470.7A EP10189470A EP2322769B1 EP 2322769 B1 EP2322769 B1 EP 2322769B1 EP 10189470 A EP10189470 A EP 10189470A EP 2322769 B1 EP2322769 B1 EP 2322769B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
pressure
pressure accumulator
rotor
insert
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10189470.7A
Other languages
German (de)
French (fr)
Other versions
EP2322769A1 (en
Inventor
Marc Hohmann
Dietmar Schulze
Andreas Knecht
André Selke
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.)
Hilite Germany GmbH
Original Assignee
Hilite Germany 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 Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP2322769A1 publication Critical patent/EP2322769A1/en
Application granted granted Critical
Publication of EP2322769B1 publication Critical patent/EP2322769B1/en
Not-in-force 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow camshafts
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a camshaft drive with a, camshaft with a camshaft insert which is rotatably connected to a rotor of a Schwenkmotorverstellers according to claim 1, as it is known from WO 2008/140 897 is known.
  • An electro-hydraulic valve for a Schwenkmotorversteller a camshaft is already known. This valve is inserted into a valve housing in which channels are provided with working ports A, B, which lead to the pressure chambers of the Schwenkmotorversteller. A plunger of the electro-hydraulic valve abuts a piston rod which is integrally connected to a piston. This piston is displaceable against a spring force within a pressure chamber in the valve housing.
  • the DE 10 2004 038 252 A1 shows a Schwenkmotorversteller with a so-called central valve.
  • the valve for actuating the Schwenkmotorverstellers is arranged radially inside the rotor on the rotor hub.
  • the object of the invention is to provide a Schwenkmotorversteller, in which space-saving a pressure accumulator is provided.
  • a pressure accumulator is integrated in a camshaft insert, which carries the rotor according to claim 1.
  • the camshaft insert and a threaded pin for rotationally fixed attachment of the rotor to the camshaft are made in one piece.
  • the camshaft insert can be made very thick-walled, whereby a longitudinal bore introduced into this can be.
  • This longitudinal bore can, in particular, guide the hydraulic fluid coming from the accumulator-in particular engine oil-to the central valve.
  • the central valve can be designed such that is supplied from the longitudinal bore via a small transverse bore Hyraulikfluid an annular groove in the valve piston, which is limited by annular webs. At these ring webs are the edges. If these annular webs have the same outer diameter, then the central valve is pressure-balanced.
  • a check valve may be provided that reduces leakage losses at the rotary feedthrough for the fluid, in particular engine oil.
  • the camshaft drive comprises a camshaft 5, which is mounted on both sides in non-illustrated camshaft bearings.
  • This camshaft 5 has cam, not shown, with which gas exchange valves of an internal combustion engine can be actuated.
  • the camshaft 5 is designed as a built-up camshaft.
  • the main body of the camshaft 5 is a hollow tube, are shrunk or pressed onto the cam.
  • a fit 7 is rotated in the interior of the hollow shaft, which receives an inner pin 8 of a camshaft insert 9.
  • the camshaft insert 9 is formed as a rotor carrier 10, which has a larger diameter than the inner pin 8.
  • the camshaft insert 9 has a threaded pin 11 whose thread diameter is smaller than the diameter of the rotor carrier 10.
  • a nut 12 is screwed, which rotatably clamped the rotor 6 against a shoulder 13 of the rotor carrier 10.
  • a radially projecting from a rotor hub 14 radially inwardly annular shoulder 15 is clamped axially between the nut 12 and the shoulder 13 of the camshaft insert 9.
  • This paragraph 13 delimits the rotor carrier 10 from the threaded pin 11.
  • the rotor hub 14 is placed on the rear portion of the rotor carrier 10.
  • the front region of the rotor carrier 10 protrudes through a bearing eye 16 of a cylinder head part 17, which receives this rotor carrier 10 in stock.
  • an annular groove 18 is incorporated in the cylinder head part 17, which is supplied by an oil pump, not shown engine oil, so that this annular groove 18 forms a pressure port P.
  • a band-shaped Check valve 50 is used, which prevents the engine oil can flow back into the oil pump due to camshaft alternating torques.
  • the pressurized engine oil is fed into a transverse bore 19 of the rotor carrier 10. From this continuous transverse bore 19, the flow of engine oil is divided on a pressure accumulator 20 and a longitudinal bore 21 leading to the valve in the rotor arm 10. This longitudinal bore 21 is closed at its end facing the engine compartment with a pressed ball 22.
  • the pressure accumulator 20 is aligned in a front region of the camshaft insert 9 coaxially with its central axis 23.
  • a pressure chamber 24 of the pressure accumulator 20 is formed by a blind hole 25, which is worked from the front into the camshaft insert 9.
  • a hydraulic piston 26 is guided axially displaceable, which is connected immovably with a direction away from the pressure chamber 24 direction piston rod 27.
  • This piston rod 27 protrudes with radial clearance through a ring 28 which is pressed firmly into the inner pin 8 in the entry region of the blind hole 25.
  • one end of a helical compression spring 29 is supported, the other end is supported on the hydraulic piston 26.
  • a hydraulic part 2 is arranged in the camshaft insert 9.
  • a partition wall 30 lies between the pressure accumulator 20 and the hydraulic part 2.
  • An end of a further helical compression spring 31 is supported on this partition wall 30, the other end of which is supported on a bottom 32 of a valve piston 33.
  • this other end projects into a guide recess 34 of the valve piston 33 up to the recess bottom, in which the bottom 32 lies.
  • the valve piston 33 is axially guided in a central blind hole 35.
  • the blind hole 35 is opened in the region of the threaded pin 11. In this case, the inlet region of this blind hole 35 forms the first tank outlet T1.
  • the valve piston 33 has a wide annular groove 36, so that on both sides of the annular groove 36 annular webs 37, 38 remain, each of which forms on both sides of the discharge edges 39, 40, 41, 42.
  • the mutually facing outlet edges 40, 41 serve the inlet to a working port A and B.
  • the mutually remote flow edges 39, 42 form the outlet to a tank drain T1 or T2.
  • the annular groove 36 can be supplied via a transverse bore 43 engine oil.
  • This transverse bore 43 is provided in the wall 44 of the rotor carrier 10 and thereby forms the storage port S.
  • the transverse bore 43 intersects the longitudinal bore 21.
  • the storage port S is connected via the foremost transverse bore 19 both to the pressure chamber 24 and to the pressure port P.
  • valve piston 33 On the valve piston 33 is on the outside -. coming from the inlet area - a dashed line shown plunger 47 of an electromagnetic linear actuator, which is otherwise not shown in detail.
  • the engine oil coming from the annular groove 36, is conducted via the working port A into the pressure chambers of the swivel motor adjuster 1 associated with one direction of rotation.
  • the engine oil is transferred from the pressure chambers assigned to the opposite direction of rotation the working port B to the first tank discharge T1 passed.
  • the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the one direction of rotation.
  • the plunger 47 is retracted to the maximum, the engine oil, coming from the annular groove 36, is conducted via the working port B into the pressure chambers of the swivel motor adjuster 1 assigned to the other rotational direction.
  • the engine oil from the opposite direction of rotation to this opposite direction of rotation pressure chambers is passed through the working port A to the second tank outlet T2.
  • the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the other direction of rotation.
  • valve piston 33 and the blind hole 35 are dimensioned in relation to the axial distances between the working ports A, B and the trailing edges 39 to 42 that given in a central position of the valve piston 33 pressure on the two rotational directions associated pressure chambers becomes. In the central position, therefore, the hydraulic pressure is controlled with a slight overlap.
  • the hydraulic piston 26 in the pressure accumulator 20 does not necessarily have a piston rod 27. If the guide length of the hydraulic piston 26 is sufficient, the entire diameter in the ring 28 can also be used for a large volume flow.
  • the longitudinal bore and the transverse bores in the camshaft insert may be distributed circumferentially such that the imbalance is only slight.
  • the blind hole 35 can also be closed, so that in both directions the discharge takes place against the tank only via the one tank outlet T2, which thus forms the single tank outlet.
  • the plunger protrudes through a sealed opening in the camshaft insert 9.
  • the hydraulic piston 26 can also be performed directly in the camshaft 5, if this is carried out according to the drawing with a hollow tube as the main body.
  • the ring 28 may also be axially supported directly in the camshaft 5.
  • the band-shaped check valve 50 may also be inserted into an annular groove in the camshaft insert 9. This can prevent leakage losses at the transfer point from bearing lug 16 to camshaft insert 9.
  • a possible embodiment of a band-shaped check valve is in the US 7,600,531 B2 shown.

Landscapes

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

Description

Die Erfindung betrifft gemäß dem Patentanspruch 1 einen Nockenwellentrieb mit einer, Nockenwelle mit einem Nockenwellen einsatz der drehfest mit einem Rotor eines Schwenkmotorverstellers verbunden ist, wie er aus der WO 2008/140 897 bekannt ist.The invention relates to a camshaft drive with a, camshaft with a camshaft insert which is rotatably connected to a rotor of a Schwenkmotorverstellers according to claim 1, as it is known from WO 2008/140 897 is known.

Aus der DE 100 50 225 A1 ist bereits ein elektrohydraulisches Ventil für einen Schwenkmotorversteller einer Nockenwelle bekannt. Dieses Ventil ist in ein Ventilgehäuse eingesetzt, in dem Kanäle mit Arbeitsanschlüssen A, B vorgesehen sind, die zu den Druckräumen vom Schwenkmotorversteller führen. Ein Stößel des elektrohydraulischen Ventils liegt an einer Kolbenstange an, die einteilig mit einem Kolben verbunden ist. Dieser Kolben ist dabei gegen eine Federkraft innerhalb eines Druckraumes im Ventilgehäuse verschieblich.From the DE 100 50 225 A1 An electro-hydraulic valve for a Schwenkmotorversteller a camshaft is already known. This valve is inserted into a valve housing in which channels are provided with working ports A, B, which lead to the pressure chambers of the Schwenkmotorversteller. A plunger of the electro-hydraulic valve abuts a piston rod which is integrally connected to a piston. This piston is displaceable against a spring force within a pressure chamber in the valve housing.

Die DE 10 2004 038 252 A1 zeigt ein Schwenkmotorversteller mit einem sogenannten Zentralventil. Bei einem Zentralventil ist das Ventil zur Betätigung des Schwenkmotorverstellers radial innerhalb des Rotors auf dessen Rotornabe angeordnet.The DE 10 2004 038 252 A1 shows a Schwenkmotorversteller with a so-called central valve. In a central valve, the valve for actuating the Schwenkmotorverstellers is arranged radially inside the rotor on the rotor hub.

Aufgabe der Erfindung ist es, einen Schwenkmotorversteller zu schaffen, in dem platzsparend ein Druckspeicher vorgesehen ist.The object of the invention is to provide a Schwenkmotorversteller, in which space-saving a pressure accumulator is provided.

Diese Aufgabe wird erfindungsgemäß mit den Merkmalen von Patentanspruch 1 gelöst.This object is achieved with the features of claim 1.

In besonders vorteilhafter Weise ist gemäß Patentanspruch 1 ein Druckspeicher in einem Nockenwelleneinsatz integriert, welcher den Rotor trägt.In a particularly advantageous manner, a pressure accumulator is integrated in a camshaft insert, which carries the rotor according to claim 1.

Dabei sind in einer besonders vorteilhaften Ausgestaltung der Erfindung der Nockenwelleneinsatz und ein Gewindezapfen zur drehfesten Befestigung des Rotors an der Nockenwelle einteilig ausgeführt. Damit kann der Nockenwelleneinsatz sehr dickwandig ausgeführt sein, wodurch eine Längsbohrung in diesen eingebracht werden kann. Diese Längsbohrung kann insbesondere das vom Druckspeicher kommende Hydraulikfluid - insbesondere Motoröl - zum zentralen Ventil leiten. Das zentrale Ventil kann dabei derart ausgeführt sein, dass von der Längsbohrung über ein kleine Querbohrung Hyraulikfluid einer Ringnut im Ventilkolben zugeleitet wird, welche durch Ringstege begrenzt ist. An diesen Ringstegen liegen die Ablaufkanten. Haben diese Ringstege gleichen Außendurchmesser, so ist das zentrale Ventil druckausgeglichen.In this case, in a particularly advantageous embodiment of the invention, the camshaft insert and a threaded pin for rotationally fixed attachment of the rotor to the camshaft are made in one piece. Thus, the camshaft insert can be made very thick-walled, whereby a longitudinal bore introduced into this can be. This longitudinal bore can, in particular, guide the hydraulic fluid coming from the accumulator-in particular engine oil-to the central valve. The central valve can be designed such that is supplied from the longitudinal bore via a small transverse bore Hyraulikfluid an annular groove in the valve piston, which is limited by annular webs. At these ring webs are the edges. If these annular webs have the same outer diameter, then the central valve is pressure-balanced.

In besonders vorteilhafter Weise brauchen im Kraftfluss der Verschraubung keine Querbohrungen zu liegen, so dass hohe Axialkräfte übertragbar sind.In a particularly advantageous manner need in the power flow of the screw no cross holes to lie, so that high axial forces are transferable.

Die erfindungsgemäße folgend dargestellte Konstruktion ermöglicht es, dass die Bereiche des Nockenwelleneinsatzes mit Querbohrungen für die Arbeitsanschlüsse A, B frei von Zugkräften gehalten werden, wobei diese Bereiche beim Anziehen der Mutter lediglich mit Torsionskräften belastet sind.The construction according to the invention shown below makes it possible that the areas of the camshaft insert with transverse bores for the working ports A, B are kept free of tensile forces, these areas are only loaded with torsional forces when tightening the nut.

In besonders vorteilhafter Weise kann ein Rückschlagventil vorgesehen sein, dass Leckageverluste an der Drehdurchführung für das Fluid - insbesondere Motoröl - vermindert.In a particularly advantageous manner, a check valve may be provided that reduces leakage losses at the rotary feedthrough for the fluid, in particular engine oil.

Weitere Vorteile der Erfindung gehen aus den weiteren Patentansprüchen, der Beschreibung und der Zeichnung vor.Further advantages of the invention will become apparent from the other claims, the description and the drawings.

Die Erfindung ist nachfolgend anhand von zwei Ausgestaltungsformen näher erläutert.The invention is explained in more detail below with reference to two embodiments.

Dabei zeigen

  • Fig. 1 konstruktiv einen Nockenwellentrieb in einer ersten Ausgestaltungsform und Fig. 1 zeigt einen Nockenwellentrieb mit einem Schwenkmotorversteller 1, wie ein solcher auch bereits in der DE 100 50 225 A1 dargestellt ist. Im Gegensatz zur DE 100 50 225 A1 ist ein Hydraulikteil 2 eines Ventils 3 jedoch als zentrales Ventil - d.h.
Zentralventil - ausgeführt. Der Schwenkmotorversteller 1 umfasst einen über eine Verzahnung 48 von einer Kurbelwelle bzw. einer anderen Nockenwelle angetriebenen Stator 4. Dazu greift in diese Verzahnung 48 eine Kette, ein Zahnriemen oder ein weiteres Zahnrad ein. Ferner umfasst der Schwenkmotorversteller 1 einen Rotor 6, der gegenüber dem Stator 4 verschwenkbar angeordnet ist. Dazu unterteilen Flügel 49 des Rotors 6 nicht näher dargestellte Kammern des Stators 4 in gegenläufige Druckkammern.Show
  • Fig. 1 constructively a camshaft drive in a first embodiment and Fig. 1 shows a camshaft drive with a Schwenkmotorversteller 1, such as one already in the DE 100 50 225 A1 is shown. In contrast to DE 100 50 225 A1 is a hydraulic part 2 of a valve 3, however, as a central valve - ie
Central valve - executed. The Schwenkmotorversteller 1 comprises a via a toothing 48 driven by a crankshaft or other camshaft stator 4. For this purpose engages in this toothing 48, a chain, a toothed belt or another gear. Furthermore, the Schwenkmotorversteller 1 comprises a rotor 6 which is arranged pivotably relative to the stator 4. For this purpose, subdivide wings 49 of the rotor 6 not shown chambers of the stator 4 in opposite pressure chambers.

Der Nockenwellentrieb umfasst eine Nockenwelle 5, die beidseitig in nicht näher dargestellten Nockenwellenlagern gelagert ist. Diese Nockenwelle 5 weist nicht näher dargestellte Nocken auf, mit denen Gaswechselventile eines Verbrennungsmotors betätigbar sind. Die Nockenwelle 5 ist als gebaute Nockenwelle ausgeführt. Dabei ist der Grundkörper der Nockenwelle 5 ein Hohlrohr, auf das Nocken aufgeschrumpft bzw. aufgepresst sind. In das schwenkmotorseitige Ende ist eine Passung 7 in den Innenraum der Hohlwelle gedreht, der einen Innenzapfen 8 eines Nockenwelleneinsatz 9 aufnimmt.The camshaft drive comprises a camshaft 5, which is mounted on both sides in non-illustrated camshaft bearings. This camshaft 5 has cam, not shown, with which gas exchange valves of an internal combustion engine can be actuated. The camshaft 5 is designed as a built-up camshaft. Here, the main body of the camshaft 5 is a hollow tube, are shrunk or pressed onto the cam. In the pivot motor end end a fit 7 is rotated in the interior of the hollow shaft, which receives an inner pin 8 of a camshaft insert 9.

Außerhalb der Nockenwelle 5 ist der Nockenwelleneinsatz 9 als Rotorträger 10 ausgeformt, der einen größeren Durchmesser aufweist, als der Innenzapfen 8. Am hinteren Ende weist der Nockenwelleneinsatz 9 einen Gewindezapfen 11 auf, dessen Gewindedurchmesser kleiner ist, als der Durchmesser des Rotorträgers 10. Auf diesen Gewindezapfen 11 ist eine Mutter 12 aufgeschraubt, welche den Rotor 6 drehfest gegen einen Absatz 13 des Rotorträgers 10 verspannt. Dazu ist ein radial von einer Rotornabe 14 radial nach innen ragender ringförmiger Ansatz 15 axial zwischen der Mutter 12 und dem Absatz 13 des Nockenwelleneinsatzes 9 verspannt. Dieser Absatz 13 grenzt den Rotorträger 10 vom Gewindezapfen 11 ab. Die Rotornabe 14 ist auf den hinteren Bereich des Rotorträgers 10 aufgesetzt.Outside the camshaft 5, the camshaft insert 9 is formed as a rotor carrier 10, which has a larger diameter than the inner pin 8. At the rear end, the camshaft insert 9 has a threaded pin 11 whose thread diameter is smaller than the diameter of the rotor carrier 10. On this Threaded pin 11 is a nut 12 is screwed, which rotatably clamped the rotor 6 against a shoulder 13 of the rotor carrier 10. For this purpose, a radially projecting from a rotor hub 14 radially inwardly annular shoulder 15 is clamped axially between the nut 12 and the shoulder 13 of the camshaft insert 9. This paragraph 13 delimits the rotor carrier 10 from the threaded pin 11. The rotor hub 14 is placed on the rear portion of the rotor carrier 10.

Hingegen ragt der vordere Bereich des Rotorträgers 10 durch ein Lagerauge 16 eines Zylinderkopfteils 17, welches diesen Rotorträger 10 lagernd aufnimmt. Dabei ist in das Zylinderkopfteil 17 eine Ringnut 18 eingearbeitet, welcher von einer nicht näher dargestellten Ölpumpe Motoröl zugeführt wird, so dass dieser Ringnut 18 einen Druckanschluss P bildet. In diese Ringnut 18 ist ein bandförmiges Rückschlagventil 50 eingesetzt, welches verhindert, das infolge von Nockenwellenwechselmomenten Motoröl in die Ölpumpe zurückströmen kann. Von diesem Druckanschluss P wird das unter Druck stehende Motoröl in eine Querbohrung 19 des Rotorträgers 10 einspeist. Von dieser durchgehenden Querbohrung 19 teilt sich der Fluss des Motoröls auf einen Druckspeicher 20 und eine zum Ventil 3 führende Längsbohrung 21 in dem Rotorträger 10 auf. Diese Längsbohrung 21 ist an deren zum Motorinnenraum weisenden Ende mit einer eingepressten Kugel 22 verschlossen.By contrast, the front region of the rotor carrier 10 protrudes through a bearing eye 16 of a cylinder head part 17, which receives this rotor carrier 10 in stock. In this case, an annular groove 18 is incorporated in the cylinder head part 17, which is supplied by an oil pump, not shown engine oil, so that this annular groove 18 forms a pressure port P. In this annular groove 18 is a band-shaped Check valve 50 is used, which prevents the engine oil can flow back into the oil pump due to camshaft alternating torques. From this pressure port P, the pressurized engine oil is fed into a transverse bore 19 of the rotor carrier 10. From this continuous transverse bore 19, the flow of engine oil is divided on a pressure accumulator 20 and a longitudinal bore 21 leading to the valve in the rotor arm 10. This longitudinal bore 21 is closed at its end facing the engine compartment with a pressed ball 22.

Der Druckspeicher 20 ist in einem vorderen Bereich des Nockenwelleneinsatzes 9 koaxial zu dessen Zentralachse 23 ausgerichtet. Ein Druckraum 24 des Druckspeichers 20 wird von einem Sackloch 25 gebildet, das von vorne in den Nockenwelleneinsatz 9 gearbeitet ist. In diesem Sackloch 25 ist ein Hydraulikkolben 26 axialverschiebbar geführt, der mit einer vom Druckraum 24 hinfort weisenden Richtung Kolbenstange 27 bewegungsfest verbunden ist. Diese Kolbenstange 27 ragt mit radialem Spiel durch einen Ring 28, der im Eintrittsbereich des Sackloches 25 fest in den Innenzapfen 8 eingepresst ist. An diesem Ring 28 stützt sich ein Ende einer Schraubendruckfeder 29 ab, deren anderes Ende an dem Hydraulikkolben 26 abgestützt ist. Das radiale Spiel zwischen der Kolbenstange 27 und dem Ring 28 ermöglicht den Durchtritt von Luft bzw. Motoröl, so dass der Hydraulikkolben 26 frei verschieblich ist, ohne dass das aus einem Federraum zu verdrängende Volumen zu hohen Strömungswiderständen führt. Damit bildet sich der mittels einer Federkraft belastbare Druckspeicher 20.The pressure accumulator 20 is aligned in a front region of the camshaft insert 9 coaxially with its central axis 23. A pressure chamber 24 of the pressure accumulator 20 is formed by a blind hole 25, which is worked from the front into the camshaft insert 9. In this blind hole 25, a hydraulic piston 26 is guided axially displaceable, which is connected immovably with a direction away from the pressure chamber 24 direction piston rod 27. This piston rod 27 protrudes with radial clearance through a ring 28 which is pressed firmly into the inner pin 8 in the entry region of the blind hole 25. On this ring 28, one end of a helical compression spring 29 is supported, the other end is supported on the hydraulic piston 26. The radial clearance between the piston rod 27 and the ring 28 allows the passage of air or engine oil, so that the hydraulic piston 26 is freely displaceable, without that to be displaced from a spring chamber volume leads to high flow resistance. This forms the loadable by means of a spring pressure accumulator 20th

Fluchtend zu diesem Druckspeicher 20 ist ein Hydraulikteil 2 im Nockenwelleneinsatz 9 angeordnet. Zwischen dem Druckspeicher 20 und dem Hydraulikteil 2 liegt dabei eine Trennwand 30. An dieser Trennwand 30 stützt sich ein Ende einer weiteren Schraubendruckfeder 31 ab, deren anderes Ende an einem Boden 32 eines Ventilkolbens 33 abgestützt ist. Dazu ragt dieses andere Ende in eine Führungsausnehmung 34 des Ventilkolbens 33 bis zum Ausnehmungsgrund, in dem der Boden 32 liegt.In alignment with this pressure accumulator 20, a hydraulic part 2 is arranged in the camshaft insert 9. A partition wall 30 lies between the pressure accumulator 20 and the hydraulic part 2. An end of a further helical compression spring 31 is supported on this partition wall 30, the other end of which is supported on a bottom 32 of a valve piston 33. For this purpose, this other end projects into a guide recess 34 of the valve piston 33 up to the recess bottom, in which the bottom 32 lies.

Der Ventilkolben 33 ist in einem zentralen Sackloch 35 axial geführt. Das Sackloch 35 ist im Bereich des Gewindezapfens 11 geöffnet. Dabei bildet der Eintrittsbereich dieses Sackloches 35 den ersten Tankabfluss T1.The valve piston 33 is axially guided in a central blind hole 35. The blind hole 35 is opened in the region of the threaded pin 11. In this case, the inlet region of this blind hole 35 forms the first tank outlet T1.

Der Ventilkolben 33 weist eine breite Ringnut 36 auf, so dass beiderseits der Ringnut 36 Ringstege 37, 38 verbleiben, die jeweils beiderseits Ablaufkanten 39, 40, 41, 42 bilden. Die einander zugewandten Ablaufkanten 40, 41 dienen dabei dem Zulauf zu einem Arbeitsanschluss A bzw. B. Die voneinander abgewandten Ablaufkanten 39, 42 bilden den Ablauf zu einem Tankabfluss T1 bzw. T2.The valve piston 33 has a wide annular groove 36, so that on both sides of the annular groove 36 annular webs 37, 38 remain, each of which forms on both sides of the discharge edges 39, 40, 41, 42. The mutually facing outlet edges 40, 41 serve the inlet to a working port A and B. The mutually remote flow edges 39, 42 form the outlet to a tank drain T1 or T2.

Der Ringnut 36 kann Motoröl über eine Querbohrung 43 zugeführt werden. Diese Querbohrung 43 ist in der Wand 44 des Rotorträgers 10 vorgesehen und bildet dabei den Speicheranschluss S. Die Querbohrung 43 kreuzt die Längsbohrung 21. Damit ist der Speicheranschluss S über die vorderste Querbohrung 19 sowohl mit dem Druckraum 24 als auch mit dem Druckanschluss P verbunden.The annular groove 36 can be supplied via a transverse bore 43 engine oil. This transverse bore 43 is provided in the wall 44 of the rotor carrier 10 and thereby forms the storage port S. The transverse bore 43 intersects the longitudinal bore 21. Thus, the storage port S is connected via the foremost transverse bore 19 both to the pressure chamber 24 and to the pressure port P.

Axial zwischen dem Ventilkolben 33 und der Trennwand 30 ist ein Raum 45 eingeschlossen, der über eine Querbohrung 46 zu dem zweiten Tankabfluss T2 führt. Dieser zweite Tankabfluss T2 liegt axial zwischen dem Zylinderkopfteil 17 und dem Schwenkmotorversteller 1. Ferner liegt dieser zweite Tankabfluss T2 axial

  • zwischen dem Speicheranschluss S einerseits und
  • den beiden Arbeitsanschlüssen A, B und dem Druckanschluss P andererseits.
Axially between the valve piston 33 and the partition wall 30, a space 45 is included, which leads via a transverse bore 46 to the second tank outlet T2. This second tank outlet T2 lies axially between the cylinder head part 17 and the Schwenkmotorversteller 1. Furthermore, this second tank outlet T2 is axially
  • between the memory port S on the one hand and
  • the two working ports A, B and the pressure port P on the other hand.

An dem Ventilkolben 33 liegt außen - d.h. vom dem Eintrittsbereich kommend - ein gestrichelt dargestellter Stößel 47 eines elektromagnetischen Linearstellgliedes an, welches ansonsten nicht näher dargestellt ist.On the valve piston 33 is on the outside -. coming from the inlet area - a dashed line shown plunger 47 of an electromagnetic linear actuator, which is otherwise not shown in detail.

Ist der Stößel 47 maximal ausgerückt, so wird das Motoröl von der Ringnut 36 kommend über der Arbeitsanschluss A in die der einen Drehrichtung zugeordneten Druckkammern des Schwenkmotorverstellers 1 geleitet. Hingegen wird das Motoröl aus den der entgegen gesetzten Drehrichtung zugeordneten Druckkammern über den Arbeitsanschluss B zum ersten Tankabfluss T1 geleitet. Dabei schwenkt der Rotor 6 mitsamt der Nockenwelle 5 gegenüber dem Stator 4 in die eine Drehrichtung.If the plunger 47 is disengaged to the maximum, the engine oil, coming from the annular groove 36, is conducted via the working port A into the pressure chambers of the swivel motor adjuster 1 associated with one direction of rotation. On the other hand, the engine oil is transferred from the pressure chambers assigned to the opposite direction of rotation the working port B to the first tank discharge T1 passed. In this case, the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the one direction of rotation.

Ist der Stößel 47 hingegen maximal eingefahren, so wird das Motoröl von der Ringnut 36 kommend über der Arbeitsanschluss B in die der anderen Drehrichtung zugeordneten Druckkammern des Schwenkmotorverstellers 1 geleitet. Zugleich wird das Motoröl aus den dieser anderen Drehrichtung entgegen gesetzten Drehrichtung zugeordneten Druckkammern über den Arbeitsanschluss A zum zweiten Tankabfluss T2 geleitet. Dabei schwenkt der Rotor 6 mitsamt der Nockenwelle 5 gegenüber dem Stator 4 in die andere Drehrichtung.If, however, the plunger 47 is retracted to the maximum, the engine oil, coming from the annular groove 36, is conducted via the working port B into the pressure chambers of the swivel motor adjuster 1 assigned to the other rotational direction. At the same time, the engine oil from the opposite direction of rotation to this opposite direction of rotation pressure chambers is passed through the working port A to the second tank outlet T2. In this case, the rotor 6 pivots together with the camshaft 5 relative to the stator 4 in the other direction of rotation.

Dabei ist das Spiel zwischen dem Ventilkolben 33 und dem Sackloch 35 so im Verhältnis zu den axialen Abständen zwischen den Arbeitsanschlüssen A,B und den Ablaufkanten 39 bis 42 dimensioniert, dass in einer mittigen Stellung des Ventilkolbens 33 Druck auf die den beiden Drehrichtungen zugeordneten Druckkammern gegeben wird. In der mittigen Stellung wird demzufolge der Hydraulikdruck mit einer leichten Überschneidung gesteuert.The play between the valve piston 33 and the blind hole 35 is dimensioned in relation to the axial distances between the working ports A, B and the trailing edges 39 to 42 that given in a central position of the valve piston 33 pressure on the two rotational directions associated pressure chambers becomes. In the central position, therefore, the hydraulic pressure is controlled with a slight overlap.

Der Hydraulikkolben 26 im Druckspeicher 20 muss nicht unbedingt eine Kolbenstange 27 aufweisen. Ist die Führungslänge des Hydraulikkolbens 26 ausreichend, kann auch der gesamte Durchmesser in dem Ring 28 für einen großen Volumenstrom genutzt werden.The hydraulic piston 26 in the pressure accumulator 20 does not necessarily have a piston rod 27. If the guide length of the hydraulic piston 26 is sufficient, the entire diameter in the ring 28 can also be used for a large volume flow.

Da die Nockenwelle eine relativ geringe Drehzahl aufweist, spielen Unwuchten eine untergeordnete Rolle. Jedoch können zur Reduktion der Unwucht die der Längsbohrung und die Querbohrungen im Nockenwelleneinsatz umfangsmäßig so verteilt sein, dass die Unwucht nur gering ist.Since the camshaft has a relatively low speed, imbalances play a minor role. However, in order to reduce the unbalance, the longitudinal bore and the transverse bores in the camshaft insert may be distributed circumferentially such that the imbalance is only slight.

Ist im Boden 32 des Ventilkolbens 33 eine Öffnung vorgesehen, so kann das Sackloch 35 auch geschlossen sein, so dass in beiden Drehrichtung die Entlastung gegen Tank nur über den einen Tankablauf T2 erfolgt, der damit den einzigen Tankablauf bildet. In dem Fall ragt der Stößel durch eine abgedichtete Öffnung im Nockenwelleneinsatz 9.If an opening is provided in the bottom 32 of the valve piston 33, the blind hole 35 can also be closed, so that in both directions the discharge takes place against the tank only via the one tank outlet T2, which thus forms the single tank outlet. In this case, the plunger protrudes through a sealed opening in the camshaft insert 9.

Der Hydraulikkolben 26 kann auch direkt in der Nockenwelle 5 geführt werden, wenn diese entsprechend der Zeichnung mit einem Hohlrohr als Grundkörper ausgeführt ist.The hydraulic piston 26 can also be performed directly in the camshaft 5, if this is carried out according to the drawing with a hollow tube as the main body.

Der Ring 28 kann auch direkt in der Nockenwelle 5 axial abgestützt sein.The ring 28 may also be axially supported directly in the camshaft 5.

Das bandförmige Rückschlagventil 50 kann auch in eine Ringnut im Nockenwelleneinsatz 9 eingesetzt sein. Damit kann verhindert werden, dass Leckageverluste an der Übergabestelle vom Lagerauge 16 zum Nockenwelleneinsatz 9 entstehen.The band-shaped check valve 50 may also be inserted into an annular groove in the camshaft insert 9. This can prevent leakage losses at the transfer point from bearing lug 16 to camshaft insert 9.

Eine mögliche Ausführungsform eines bandförmigen Rückschlagventils ist in der US 7,600,531 B2 dargestellt.A possible embodiment of a band-shaped check valve is in the US 7,600,531 B2 shown.

Bei den beschriebenen Ausführungsformen handelt es sich nur um beispielhafte Ausgestaltungen. Eine Kombination der beschriebenen Merkmale für unterschiedliche Ausführungsformen ist ebenfalls möglich. Weitere, insbesondere nicht beschriebene Merkmale der zur Erfindung gehörenden Vorrichtungsteile, sind den in den Zeichnungen dargestellten Geometrien der Vorrichtungsteile zu entnehmen.The described embodiments are only exemplary embodiments. A combination of the described features for different embodiments is also possible. Further, in particular not described features of the device parts belonging to the invention are to be taken from the geometries of the device parts shown in the drawings.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
SchwenkmotornockenwellenverstellerOscillating motor camshaft adjuster
22
Hydraulikteilhydraulic part
33
VentilValve
44
Statorstator
55
Nockenwellecamshaft
66
Rotorrotor
77
Passungfit
88th
Innenzapfeninner pins
99
Nockenwelleneinsatzcamshafts use
1010
Rotorträgerrotorarm
1111
Gewindezapfenthreaded pin
1212
Muttermother
1313
Absatzparagraph
1414
Rotornaberotor hub
1515
Ansatzapproach
1616
Lageraugebearing eye
1717
ZylinderkopfteilCylinder head
1818
Ringnutring groove
1919
Querbohrungcross hole
2020
Druckspeicheraccumulator
2121
Längsbohrunglongitudinal bore
2222
KugelBullet
2323
Zentralachsecentral axis
2424
Druckraumpressure chamber
2525
Sacklochblind
2626
Hydraulikkolbenhydraulic pistons
2727
Kolbenstangepiston rod
2828
Ringring
2929
SchraubendruckfederHelical compression spring
3030
Trennwandpartition wall
3131
SchraubendruckfederHelical compression spring
3232
Bodenground
3333
Ventilkolbenplunger
3434
Führungsausnehmungguide recess
3535
Sacklochblind
3636
Ringnutring groove
3737
Ringstegring land
3838
Ringstegring land
3939
Ablaufkantetrailing edge
4040
Ablaufkantetrailing edge
4141
Ablaufkantetrailing edge
4242
Ablaufkantetrailing edge
4343
Querbohrungcross hole
4444
Wandwall
4545
Raumroom
4646
Querbohrungcross hole
4747
Stößeltappet
4848
Verzahnunggearing
4949
Flügelwing
5050
Rückschlagventilcheck valve

Claims (8)

  1. A camshaft drive having a camshaft with a camshaft insert (9) which is connected in rotationally fixed manner to a rotor (6) of an oscillating motor adjuster (1), wherein a pressure accumulator (20) which can be loaded by means of a spring force is arranged within the camshaft drive,
    wherein a hydraulic part (2) of a valve (3 and 55) is arranged radially within the rotor (6),
    wherein the hydraulic part (2) is arranged flush with the pressure accumulator (20 and 58),
    wherein the pressure accumulator (20) has a pressure chamber (24) to which the fluid is supplied by a pressure connection (P),
    wherein the pressure accumulator (20) is delimited by an axially displaceable hydraulic piston (26) which, on its side facing away from the pressure chamber (24), is supported by means of a helical pressure spring (29) on a part (ring 28) fixed axially to the camshaft,
    wherein fluid is supplied to the pressure accumulator (20) by a channel (19),
    characterised in that
    the pressure accumulator (20) is arranged within the camshaft insert (9), wherein
    the channel (19) is supplied with the fluid from an annular groove (18) which is provided in a cylinder head part (17),
    wherein a tank connection (T2) is located axially between the pressure connection (P) leading into the pressure chamber (24) of the pressure accumulator (20) and the working connections (A, B).
  2. A camshaft drive according to one of the preceding claims, characterised in that the pressure accumulator (20) is separated from the hydraulic part (2) by means of a wall (30) on which a first end of a helical pressure spring (31) is supported at least indirectly, the second end of which is supported on a valve piston (33).
  3. A camshaft drive according to Claim 3, characterised in that an electromagnetic actuating element is supported on one side of the valve piston (33), on the other side of which the second end of the helical pressure spring (31) is supported, wherein the valve piston (33) is supplied with fluid by way of an accumulator connection (S) coming from the pressure accumulator (20), which fluid can be divided alternately by an overlap control between two working connections (A, B) by way of two run-off edges (40, 41), which working connections lead into opposing pressure chambers on both sides of at least one blade (49) of the rotor (6).
  4. A camshaft drive according to one of the preceding claims, characterised in that the camshaft insert (9) has an inner journal (8) which is pressed into the hollow camshaft (5).
  5. A camshaft drive according to Claim 5, characterised in that the camshaft (5) is an assembled camshaft (5).
  6. A camshaft drive according to Claim 6, characterised in that the camshaft insert (9) and a threaded journal (11) are constructed as one piece for mounting the rotor (6) in rotationally fixed manner on the camshaft (5).
  7. A camshaft drive according to one of the preceding claims, characterised in that the camshaft insert (9) has a threaded journal (11) onto which a nut is screwed which clamps the rotor (6) in rotationally fixed manner against a shoulder (13) of the camshaft insert (9).
  8. A camshaft drive according to one of the preceding claims, characterised in that a non-return valve (63) is provided in the hydraulic flow between an oil pump (60) and the pressure accumulator (20).
EP10189470.7A 2009-11-13 2010-10-29 Camshaft drive with a camshaft and a camshaft hub Not-in-force EP2322769B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009052841A DE102009052841A1 (en) 2009-11-13 2009-11-13 camshafts use

Publications (2)

Publication Number Publication Date
EP2322769A1 EP2322769A1 (en) 2011-05-18
EP2322769B1 true EP2322769B1 (en) 2013-07-24

Family

ID=43640082

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10189470.7A Not-in-force EP2322769B1 (en) 2009-11-13 2010-10-29 Camshaft drive with a camshaft and a camshaft hub

Country Status (4)

Country Link
US (1) US20110114047A1 (en)
EP (1) EP2322769B1 (en)
CN (1) CN102061953B (en)
DE (1) DE102009052841A1 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009042202A1 (en) * 2009-09-18 2011-04-14 Schaeffler Technologies Gmbh & Co. Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102009050779B4 (en) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller with a friction disc and mounting method
DE102012200685B4 (en) * 2012-01-18 2020-10-22 Schaeffler Technologies AG & Co. KG Valve arrangement for camshaft adjuster
DE102012200683B4 (en) * 2012-01-18 2017-01-26 Schaeffler Technologies AG & Co. KG Phaser
DE102012201560B4 (en) 2012-02-02 2019-02-21 Schaeffler Technologies AG & Co. KG Volume accumulator design in a camshaft adjuster
DE102012202823B4 (en) 2012-02-24 2014-03-06 Schaeffler Technologies AG & Co. KG Phaser
DE102012218802B4 (en) 2012-10-16 2018-05-17 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster system
DE102012223582A1 (en) * 2012-12-18 2014-06-18 Schaeffler Technologies Gmbh & Co. Kg Phaser system
JP6169795B2 (en) * 2013-07-15 2017-07-26 山東大学 Oil control device for fully variable hydraulic valve system of internal combustion engine
DE102015204040B4 (en) 2015-03-06 2021-07-08 Schaeffler Technologies AG & Co. KG Camshaft adjuster
DE102015213135B3 (en) * 2015-07-14 2017-01-05 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster
CN106194304A (en) * 2016-09-12 2016-12-07 奇瑞汽车股份有限公司 A kind of coupling is put the camshaft of OCV
WO2019029786A1 (en) * 2017-08-07 2019-02-14 HELLA GmbH & Co. KGaA Apparatus for camshaft timing adjustment with built in pump
DE102017011004A1 (en) * 2017-11-28 2019-05-29 Schwäbische Hüttenwerke Automotive GmbH Camshaft phaser with ring-type check valve
DE102019113638B3 (en) * 2019-05-22 2020-09-17 Schaeffler Technologies AG & Co. KG Control valve with an integrated active pressure accumulator
US11261765B1 (en) * 2020-08-25 2022-03-01 Borgwamer Inc. Control valve assembly of a variable cam timing phaser
DE102021116598A1 (en) 2021-06-28 2022-12-29 Schaeffler Technologies AG & Co. KG camshaft adjuster

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654926A1 (en) * 1996-03-22 1997-11-20 Daimler Benz Ag Device for angular adjustment of camshaft with respect to crankshaft on IC engine
DE19955507A1 (en) * 1999-11-18 2001-06-07 Daimler Chrysler Ag Camshaft adjuster for IC engines has connection screw shaft integrated in camshaft
DE102005048732A1 (en) * 2005-10-12 2007-04-19 Schaeffler Kg Hydraulic directional valve

Family Cites Families (87)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE135322C (en) * 1900-01-01
US2649105A (en) * 1953-08-18 Self-draining pipe joint
US894286A (en) * 1908-04-10 1908-07-28 Frederick C Reineking Air-intake regulator for carbureters.
US1746855A (en) * 1926-03-17 1930-02-11 Louis O French Valve
US1860163A (en) * 1930-04-21 1932-05-24 Binks Mfg Co Valve assembly for air-compressing cylinders
US2781059A (en) * 1954-01-08 1957-02-12 Gen Motors Corp Flow control device
US2918941A (en) * 1957-12-02 1959-12-29 Orenda Engines Ltd Pressure relief blow-out device
US3783590A (en) * 1970-07-09 1974-01-08 A Allen Filter-silencer for pneumatic devices
US3779669A (en) * 1972-05-22 1973-12-18 Wooster Brush Co Pump spray unit
US3882891A (en) * 1974-06-19 1975-05-13 Abex Corp Check valve
US4051864A (en) * 1975-10-21 1977-10-04 Gould Inc. Flow regulator
DE2757490C3 (en) * 1977-12-22 1980-09-11 1000 Berlin Pressure valve
JPS5578150A (en) * 1978-12-06 1980-06-12 Nissan Motor Co Ltd Exhaust gas return control device for internal conbustion engine
DE3616234A1 (en) * 1986-05-14 1987-11-19 Bayerische Motoren Werke Ag DEVICE FOR THE RELATIVE TURNING CHANGE OF TWO DRIVELY CONNECTED SHAFTS, ESPECIALLY BETWEEN A CRANKSHAFT AND CAMSHAFT BEARING IN A MACHINE HOUSING OF AN INTERNAL COMBUSTION ENGINE
FR2641832B1 (en) * 1989-01-13 1991-04-12 Melchior Jean COUPLING FOR TRANSMISSION OF ALTERNATE COUPLES
DE4024057C1 (en) * 1990-07-28 1991-09-19 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5323806A (en) * 1992-03-26 1994-06-28 Matsushita Electric Works, Ltd. Constant-speed exhaust valve device for hemadynamometer
US5657725A (en) * 1994-09-15 1997-08-19 Borg-Warner Automotive, Inc. VCT system utilizing engine oil pressure for actuation
DE19525837A1 (en) * 1995-07-15 1997-01-16 Schaeffler Waelzlager Kg Control time adjuster for internal combustion engine - has outer jacket of oil guide shell with at least one longitudinal groove to form radial web
JP3620684B2 (en) * 1997-01-31 2005-02-16 株式会社デンソー Valve timing adjusting device for internal combustion engine
DE19756016A1 (en) * 1997-12-17 1999-06-24 Porsche Ag Device for the hydraulic rotation angle adjustment of a shaft to a drive wheel
JP4147435B2 (en) * 1998-01-30 2008-09-10 アイシン精機株式会社 Valve timing control device
US6234125B1 (en) * 1998-03-30 2001-05-22 Aft Atlas Fahrzeugtechnik Gmbh Apparatus for angular adjustment of camshafts relative to crankshafts in combustion engines
JPH11280427A (en) * 1998-03-31 1999-10-12 Aisin Seiki Co Ltd Control device for valve opening/closing timing
JP3918971B2 (en) * 1998-04-27 2007-05-23 アイシン精機株式会社 Valve timing control device
DE19823619A1 (en) * 1998-05-27 1999-12-02 Porsche Ag Device for changing the relative rotational position of a shaft to the drive wheel
JP4013364B2 (en) * 1998-10-30 2007-11-28 アイシン精機株式会社 Valve timing control device
US6267041B1 (en) * 1999-12-15 2001-07-31 Caterpillar Inc. Fluid regeneration circuit for hydraulic cylinders
JP4802394B2 (en) * 2000-08-03 2011-10-26 アイシン精機株式会社 Valve timing control device
DE10050225A1 (en) * 2000-10-11 2002-04-25 Hydraulik Ring Gmbh Actuating device for fixing a camshaft of a drive engine of a vehicle, preferably a motor vehicle, in a starting position
JP4159241B2 (en) * 2000-11-30 2008-10-01 株式会社デンソー Valve timing adjusting device for internal combustion engine
US6453859B1 (en) * 2001-01-08 2002-09-24 Borgwarner Inc. Multi-mode control system for variable camshaft timing devices
US20030033998A1 (en) * 2001-08-14 2003-02-20 Marty Gardner Hybrid multi-position cam indexer having controls located in rotor
US6763791B2 (en) * 2001-08-14 2004-07-20 Borgwarner Inc. Cam phaser for engines having two check valves in rotor between chambers and spool valve
DE10143433B4 (en) * 2001-09-05 2013-09-26 Hilite Germany Gmbh proportional valve
DE10161698A1 (en) * 2001-12-15 2003-06-26 Ina Schaeffler Kg Device is for altering control times of gas exchange valves in internal combustion engine, particularly for hydraulic rotary angle adjustment of camshaft in relation to crankshaft
DE10205415A1 (en) * 2002-02-09 2003-08-28 Porsche Ag Device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel
DE10211468A1 (en) * 2002-03-15 2003-09-25 Daimler Chrysler Ag Camshaft adjuster for internal combustion engine has control piston in separate guide casing
DE10213081A1 (en) * 2002-03-20 2003-10-02 Hydraulik Ring Gmbh Valve control for adjusting the stroke of valves in motor vehicles
US6782856B2 (en) * 2002-04-09 2004-08-31 Ford Global Technologies, Llc Camshaft accumulator
DE10216352A1 (en) * 2002-04-13 2003-10-23 Hydraulik Ring Gmbh Control device for at least one consumer, such as camshaft adjusters, automatic transmissions and the like, of vehicles, preferably motor vehicles
DE10228354B4 (en) * 2002-06-25 2017-06-22 Daimler Ag Device for supplying pressure to a camshaft adjusting device
JP4126600B2 (en) * 2002-09-26 2008-07-30 アイシン精機株式会社 Control mechanism of valve timing control device
US6899199B2 (en) * 2002-10-24 2005-05-31 Barnes Group Inc. Flapper finger valve assembly
DE10314683B4 (en) * 2003-03-29 2009-05-07 Entec Consulting Gmbh Variable valve lift control for a combustion engine with a bottom camshaft
WO2004088094A2 (en) * 2003-03-29 2004-10-14 Hydraulik-Ring Gmbh Variable valve lift device for the lift adjustment of gas-exchange valves of an internal combustion engine
EP1464793B1 (en) * 2003-04-02 2007-12-05 Renault s.a.s. Camshaft arrangements for engines
DE10319831A1 (en) * 2003-05-03 2004-11-18 Hydraulik-Ring Gmbh Hydraulic valve socket
US6871621B2 (en) * 2003-05-12 2005-03-29 Hydraulik-Ring Gmbh Camshaft adjuster for internal combustion engines of motor vehicles
ITBO20030390A1 (en) * 2003-06-23 2004-12-24 Magneti Marelli Powertrain Spa METHOD AND VALVE SPEED CONTROL DEVICE
DE10330449B3 (en) * 2003-07-05 2005-02-24 Daimlerchrysler Ag Camshaft adjuster for internal combustion engine has stator and first thrust washer bounding adjuster towards cam frictionally joined to camshaft by cylindrical surface
DE10334690B4 (en) * 2003-07-30 2008-08-21 Böckmann-Hannibal, Angela, Dipl.-Ing. (FH) Device for adjusting the camshaft of internal combustion engines
DE10346443A1 (en) * 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulic camshaft adjuster for internal combustion engine, has electromagnetic operating unit for operating hydraulic control valve having valve housing with control piston for controlling supply of hydraulic fluid
DE10346448B4 (en) * 2003-10-07 2017-03-30 Daimler Ag Camshaft adjuster for an internal combustion engine
DE10352255B4 (en) * 2003-11-08 2017-03-09 Schaeffler Technologies AG & Co. KG Adjustment device for adjusting the relative angular position of a camshaft relative to a crankshaft of an internal combustion engine
DE102004038252A1 (en) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Control valve for a device for changing the timing of an internal combustion engine
DE502005010369D1 (en) * 2004-05-14 2010-11-25 Schaeffler Kg Phaser
JP4202297B2 (en) * 2004-05-20 2008-12-24 株式会社日立製作所 Valve timing control device for internal combustion engine
DE102004039800B4 (en) * 2004-08-17 2006-07-27 Hydraulik-Ring Gmbh Cam Phaser System
US7387097B2 (en) * 2004-10-08 2008-06-17 Ina-Schaeffler Jg INA-schaeffler KG, industriestrasse 1-3, 91074 herzogenaurach ANR 12 88 48 20
GB2421557B (en) * 2004-12-23 2009-10-28 Mechadyne Plc Vane-type phaser
DE102005004281B3 (en) * 2005-01-28 2006-01-05 Hydraulik-Ring Gmbh Camshaft setter with no-clearance locking for internal combustion engine is in form of slide valve with two sectors, between which power transfer takes place
DE102005013085B3 (en) 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Hydraulic valve for automobile, has check valve with band formed of closed ring, which serves as opening-free band and is made of spring steel, where steel forms ring by overlap of section of bands at about one hundred and eighty degree
DE102005034276A1 (en) * 2005-07-22 2007-01-25 Daimlerchrysler Ag Camshaft adjusting device
DE102005034275B4 (en) * 2005-07-22 2018-02-15 Daimler Ag Camshaft variable valve mechanism
DE102005060111A1 (en) * 2005-12-16 2007-07-05 Schaeffler Kg Camshaft adjuster feed line
DE102006008532A1 (en) * 2006-02-22 2007-08-30 Thyssenkrupp Automotive Ag Camshaft e.g. eccentric shaft, manufacturing method for internal combustion engine, involves shielding support unit against cam, such that chips arising during chip removing process are not penetrated into intermediate space
EP1996819B1 (en) * 2006-03-17 2012-04-11 Hilite Germany GmbH Hydraulic circuit, especially for camshaft adjusters, and corresponding control element
GB2440157B (en) * 2006-07-20 2011-01-19 Mechadyne Plc Variable phase mechanism
DE112007002915B4 (en) * 2006-12-04 2020-10-29 Daimler Ag Adjustment device for phase adjustment of a camshaft
GB2445570B (en) * 2007-01-09 2011-04-06 Mechadyne Plc Rotary hydraulic coupling
WO2008140897A1 (en) * 2007-05-14 2008-11-20 Borgwarner Inc. Cam mounted accumulator
DE102007026824A1 (en) * 2007-06-06 2008-12-11 Muhr Und Bender Kg Method for producing cams for assembled camshafts
WO2009010332A1 (en) * 2007-07-18 2009-01-22 Schaeffler Kg Valve part for a hydraulic control valve
DE102007040017B4 (en) * 2007-08-24 2020-09-17 Schaeffler Technologies AG & Co. KG Timing setting device for an internal combustion engine with manufacturing process
US8104511B2 (en) * 2007-08-27 2012-01-31 Parker Hannifin Corporation Sequential stepped directional control valve
DE102007041552A1 (en) * 2007-08-31 2009-03-05 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007053688A1 (en) * 2007-11-10 2009-05-14 Schaeffler Kg Control valve assembly for camshaft adjuster of internal combustion engine, comprises hollow cylindrical valve housing and hydraulic control valve for controlling pressure medium flow
DE102007058491A1 (en) * 2007-12-05 2009-06-10 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102008005277A1 (en) * 2008-01-19 2009-07-23 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
EP2093388B1 (en) * 2008-02-19 2014-10-08 hofer mechatronik GmbH Cam phaser for an internal combustion engine
DE102009034011B4 (en) * 2008-10-07 2018-04-05 Schaeffler Technologies AG & Co. KG Pressure accumulator to support the pressure medium supply of a camshaft adjuster an internal combustion engine
DE102009022869A1 (en) * 2009-05-27 2010-12-09 Hydraulik-Ring Gmbh Vane phaser system
DE102009050779B4 (en) * 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller with a friction disc and mounting method
DE102010008001B4 (en) * 2010-02-15 2022-03-10 Schaeffler Technologies AG & Co. KG Device for the variable setting of valve lift curves of gas exchange valves of an internal combustion engine
DE102010019005B4 (en) * 2010-05-03 2017-03-23 Hilite Germany Gmbh Schwenkmotorversteller
DE102010053685B4 (en) * 2010-12-08 2014-10-30 Schwäbische Hüttenwerke Automotive GmbH Device for adjusting the rotational angular position of a camshaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654926A1 (en) * 1996-03-22 1997-11-20 Daimler Benz Ag Device for angular adjustment of camshaft with respect to crankshaft on IC engine
DE19955507A1 (en) * 1999-11-18 2001-06-07 Daimler Chrysler Ag Camshaft adjuster for IC engines has connection screw shaft integrated in camshaft
DE102005048732A1 (en) * 2005-10-12 2007-04-19 Schaeffler Kg Hydraulic directional valve

Also Published As

Publication number Publication date
CN102061953B (en) 2013-03-20
US20110114047A1 (en) 2011-05-19
CN102061953A (en) 2011-05-18
EP2322769A1 (en) 2011-05-18
DE102009052841A1 (en) 2011-05-19

Similar Documents

Publication Publication Date Title
EP2322769B1 (en) Camshaft drive with a camshaft and a camshaft hub
DE102012201567B4 (en) Design of a hydraulic oil channel between a central valve and a volume accumulator of a camshaft adjuster
EP2326804B1 (en) Camshaft adjuster
EP2331797B1 (en) Device for variably adjusting the control times of gas exchange valves of an internal combustion engine
DE102016204779B4 (en) Camshaft adjustment system for an internal combustion engine of a motor vehicle
DE102010019004B4 (en) Swivel motor adjuster with a hydraulic valve
EP3219942B1 (en) Camshaft adjuster
DE102004036096A1 (en) Control valve for a device for changing the timing of an internal combustion engine
EP2924248A1 (en) Hydraulic valve for a pivoting engine adjuster of a camshaft
EP2870327B1 (en) Vane type phasing device with hydraulic control valve
DE102008036182A1 (en) Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102012210178B4 (en) Control valve of a camshaft adjuster
EP2487339B1 (en) Camshaft adjuster with a pressure storage unit
DE102010023864B4 (en) Central valve for a Schwenkmotornockenwellenversteller
DE102012201573A1 (en) Phaser
DE102012211870A1 (en) Hydraulic camshaft adjuster with central locking and adjustable locking clearance
EP3015662B1 (en) Hydraulic valve and a tilt motor adjuster
DE102007035672B4 (en) Phaser
DE102012211108B4 (en) Camshaft adjusting device for an internal combustion engine
DE102014223503A1 (en) Fast-switching hydraulic camshaft adjuster with two check valves in the same direction
DE102010023863A1 (en) Assembled camshaft for camshaft drive system for actuating charge-cycle valve of internal combustion engine, has piston supported opposite to camshaft insert and directly mounted within pipe for pivoting rotor against stator
WO2015165444A1 (en) Hydraulic phase adjuster for a camshaft
EP2536925B1 (en) Device for variable adjustment of the control times of gas exchange valves of an internal combustion engine
DE102015106230A1 (en) Swivel motor adjuster for a camshaft
DE102013114303A1 (en) Compressor system with a Kolbenhubeinstellvorrichtung

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL 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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20110601

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: HILITE GERMANY GMBH

17Q First examination report despatched

Effective date: 20121126

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

INTG Intention to grant announced

Effective date: 20130514

RIN1 Information on inventor provided before grant (corrected)

Inventor name: SELKE, ANDRE

Inventor name: SCHULZE, DIETMAR

Inventor name: KNECHT, ANDREAS

Inventor name: HOHMANN, MARC

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL 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 RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 623595

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130815

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: 502010004111

Country of ref document: DE

Effective date: 20130919

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130724

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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: 20130717

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: 20130724

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: 20131024

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: 20130724

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: 20130724

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: 20131125

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: 20131124

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: 20130724

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: 20130724

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: 20130724

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: 20130724

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: 20131025

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: 20130724

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: 20130724

BERE Be: lapsed

Owner name: HILITE GERMANY G.M.B.H.

Effective date: 20131031

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

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: 20130724

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: 20130724

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: 20130724

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: 20130724

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: 20130724

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130724

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: 20130724

Ref country code: IT

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: 20130724

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: 20140425

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010004111

Country of ref document: DE

Effective date: 20140425

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: 20131031

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

Ref country code: IE

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

Effective date: 20131029

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

Ref country code: SM

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: 20130724

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20141029

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: 20130724

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

Ref country code: LI

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

Effective date: 20141031

Ref country code: RS

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: 20131024

Ref country code: CH

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

Effective date: 20141031

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: 20130724

Ref country code: LU

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

Effective date: 20131029

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: 20130724

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: 20101029

Ref country code: GB

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

Effective date: 20141029

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: 20130724

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 623595

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151029

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

Ref country code: FR

Payment date: 20161020

Year of fee payment: 7

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: 20151029

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180629

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: 20171031

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

Ref country code: AL

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: 20130724

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

Ref country code: DE

Payment date: 20191021

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502010004111

Country of ref document: DE

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: 20210501