EP2609304B1 - Valve train of a combustion piston engine - Google Patents

Valve train of a combustion piston engine Download PDF

Info

Publication number
EP2609304B1
EP2609304B1 EP11730299.2A EP11730299A EP2609304B1 EP 2609304 B1 EP2609304 B1 EP 2609304B1 EP 11730299 A EP11730299 A EP 11730299A EP 2609304 B1 EP2609304 B1 EP 2609304B1
Authority
EP
European Patent Office
Prior art keywords
solenoid
permanent magnet
camshaft
valve train
brake rotor
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
EP11730299.2A
Other languages
German (de)
French (fr)
Other versions
EP2609304A1 (en
Inventor
Frank Richter
Reiner Keller
Markus Wannags
Ilja Imgrunt
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2609304A1 publication Critical patent/EP2609304A1/en
Application granted granted Critical
Publication of EP2609304B1 publication Critical patent/EP2609304B1/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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/352—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
    • F01L2001/3522—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 with electromagnetic brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/12—Fail safe operation

Definitions

  • the invention relates to a valve train of a combustion piston engine, comprising a superposition gear with two input elements and an output element comprehensive adjusting device for phase adjustment of a camshaft according to the preamble of patent claim 1.
  • Known adjusting devices for phase adjustment of a camshaft are designed as hydraulic turntable or as electromechanical turntable, which are arranged directly between the provided with a chain or toothed belt sprocket hub and the rotatably connected to the camshaft axis of the camshaft sprocket.
  • a disadvantage of such direct rotary adjusting devices are the high translation forces caused by the low translation and the high control effort for setting a specific phase angle.
  • the superposition gear generally has two input elements and an output element, wherein the first input element, for example via a chain or toothed belt drive, is in drive connection with the crankshaft, the second input element is in communication with a controllable actuator, and the output element is non-rotatably connected to the camshaft.
  • a superposition gear is preferably a simple planetary gear or one consisting of components of two Planetenrad arrangementsn coupled planetary gear used.
  • the actuator may be used as a servo-controlled rotary drive, such as a rotary actuator. be designed as an electric motor or as a hydraulic turntable, or as a controllable braking device.
  • a particularly simple and cost-effective in terms of their structure and controllability braking device is designed as a controllable friction brake, a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the second input element and by the magnetic field of the electromagnet against a housing-fixed friction surface includes releasable brake rotor. Since the second input elements in the unbraked state would rotate faster than the first input element, a certain phase angle of the associated camshaft is maintained by the setting of a specific, acting on the brake rotor and thus on the second input element mean braking torque. Starting from this phase position of the camshaft, an adjustment is achieved early by a brief increase in the braking torque and late by a brief reduction in the braking torque.
  • a first such adjusting device for the phase adjustment of a camshaft with a superposition gear and a standing in operative connection with this braking device is from the DE 10 2006 011 806 A1 known.
  • the superposition gear of this actuator is as a coupled planetary gear with two sun gears with different diameters and tooth numbers and a plurality of rotatably mounted two-stage planetary gear planet carrier formed, wherein the first input element are formed by the planet carrier, the second input element by the smaller sun gear, and the output member by the larger sun gear.
  • the braking device is designed as an electromagnetically controllable friction brake, which comprises a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the smaller sun gear and by the magnetic field of the electromagnet against a arranged on the magnetic body friction surface brake rotor.
  • electromagnet is switched off the disc-shaped brake rotor is pressed by a spring axially against the planet carrier, whereby at least one locking element engages in a corresponding recess of the planet carrier, whereby the planetary gear is locked in and rigidly rotates.
  • the superposition gear of this adjusting device is designed as a simple planetary gear with a sun gear, a plurality of rotatably mounted planetary planet carrier and a ring gear, wherein the first input element by the planet carrier, the second input element by the sun gear and the output member by the Ring gear are formed.
  • Another generic adjusting device for phase adjustment of a camshaft according to the DE 10 2008 043 673 A1 has an inverse control characteristic.
  • the superposition gear is as in the actuator after the DE 10 2006 028 554 A1 designed as a simple planetary gear.
  • the rotatably mounted and axially displaceable on a rigidly connected to the sun gear shaft mounted brake rotor is arranged axially outside of the electromagnet and clamped by a spring axially against a freely rotatably mounted pressure plate.
  • the pressure plate is disposed axially within the electromagnet adjacent to the planet carrier and has control cam for engagement in recesses of the planet carrier and of control lugs of the ring gear, whereby a lock of the planet carrier with the ring gear in an emergency position is reached with the electromagnet off.
  • the brake rotor is pressed with the solenoid switched off by the spring against a housing-fixed friction surface.
  • the electromagnet is turned on, the thrust washer is axially pulled away from the planet carrier against the restoring force of the spring and thus releases the lock between the planet carrier and the ring gear.
  • the brake rotor is axially pulled away from the housing-fixed friction surface according to the strength of the magnetic field against the restoring force of the spring and thus reduces the effective braking torque.
  • a disadvantage of the known adjusting devices for phase adjustment of a camshaft is thus the permanent power consumption of the electromagnet during operation of the internal combustion piston engine and the respective adjusting device. Also, in each case, a relatively strong magnetic field is required in order to achieve against the restoring force of the spring, a sufficiently high braking torque for adjusting and holding the respective phase angle of the camshaft.
  • the invention has the object, a valve train of a combustion piston engine with an adjusting device for phase adjustment of a camshaft of the type mentioned in terms of to develop a lower energy consumption and a simplified structure of the adjusting device.
  • the invention is therefore based on a known valve train of a combustion piston engine, which has a superposition gear with two input elements and an output element comprehensive adjusting device for phase adjustment of a camshaft.
  • the first input element is, e.g. via a chain or toothed belt drive, with a crankshaft in drive connection
  • the second input element is in operative connection with a controllable braking device
  • the output element is non-rotatably connected to the camshaft.
  • the braking device is designed as an electromagnetically controllable friction brake, which comprises a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the second input element and can be pressed by the magnetic field of the electromagnet against a housing-fixed friction surface brake rotor.
  • the permanent magnet is advantageously designed and arranged such that the camshaft is automatically held in a defined initial position or adjusted in the engine start and a failure of the power supply of the electromagnet and / or its control by the set base braking torque. This ensures that the electromagnet must be turned on only to adjust the current phase position of the camshaft, and that on a special safety device (Fail Save), as provided in the known actuators positive locking between the brake rotor and the second input element of the superposition gear or between the first input element and the output element of the superposition gearing, can be dispensed with.
  • a special safety device as provided in the known actuators positive locking between the brake rotor and the second input element of the superposition gear or between the first input element and the output element of the superposition gearing
  • the permanent magnet could be arranged radially inside or outside the electromagnet or on the side facing away from the electromagnet axially adjacent to the brake rotor.
  • this would disadvantageously lead to increased construction costs and larger dimensions of the braking device. Therefore, it is provided herein that the permanent magnet is disposed within the magnetic flux of the electromagnet, so that the magnetic body of the electromagnet and the adjacent portion of the brake rotor is used to form a closed magnetic flux circuit of the permanent magnet. In addition, this will improve the superposition of the magnetic fields of both magnets and thus the controllability of the resulting braking torque.
  • Such an arrangement of the permanent magnet may be expediently realized such that the permanent magnet is annular and has an axial alignment of its poles (N, S), as well as in a corresponding radially inner or outer recess of the magnetic body of the electromagnet is arranged.
  • the permanent magnet is annular and has a radial orientation of its poles (N, S), and in a corresponding axially outer, i. arranged on the side remote from the brake rotor arranged recess of the magnetic body of the electromagnet.
  • the adjustment of the phase angle of the camshaft now takes place in a simple manner in that the magnetic field of the permanent magnet for increasing the braking torque acting on the brake rotor, i. for adjusting the camshaft in the early direction, amplified by a suitable control device by a rectified polarity of the electromagnet and to reduce the braking torque acting on the brake rotor, i. for adjusting the camshaft toward late, is attenuated by an opposite polarity of the electromagnet.
  • the brake rotor can be provided between the first input element and the output element of the superposition gear effective limit stops for limiting the adjustment of the phase adjustment of the camshaft to a permissible phase angle range.
  • FIG. 1 An in Fig. 1 partially formed valve train of a combustion piston engine is provided with an adjusting device 1 for phase adjustment of a camshaft 2, which comprises a superposition gear 3 with two input elements 4, 5 and an output element 6 and a controllable braking device 7.
  • the superposition gear 3 is exemplified as a simple planetary gear 8 with a sun gear 9, a plurality of rotatably mounted planet gears 10 supporting planet carrier 11 and a ring gear 12 is formed.
  • the planet carrier 11 forms the first input element 4 and is provided with a chain sprocket 13, via which by means of a timing chain, not shown, a positive drive connection with the crankshaft of the internal combustion piston engine.
  • the sun gear 9 forms the second input element 5, which is in operative connection with the braking device 7.
  • the ring gear 12 forms the output element 6 and is connected via a plurality of screws 14 rigidly connected to the camshaft 2.
  • the braking device 7 is designed as an electromagnetically controllable friction brake 15 and comprises a housing-fixed electromagnet 16 with a U-shaped and made of a ferromagnetic material magnetic body 17 and a magnetic coil 18 and a mecanicaxialver leopardung 19 rotationally fixed and axially displaceable on the axially elongated At least in the area adjacent to the magnetic body 17 region of the brake rotor 21 is made of a ferromagnetic material, so that it is pressed when the electromagnet 16 by the generated magnetic field axially against friction surfaces 22 of the magnetic body 17 and thus on the Sun gear 9 effective braking torque is generated.
  • a permanent magnet 23 which in the present case is annular, has an axial orientation of the poles N, S, and in a corresponding radially outer recess 24 of the magnetic body 17 of the electromagnet 16 is arranged.
  • the permanent magnet 23 is disposed within the magnetic flux of the electromagnet 16, whereby on the one hand, the superposition of the magnetic fields of both magnets 16, 23 improves and on the other the common use of the magnetic body 17 to amplify the magnetic field and its friction surfaces 22 for braking the brake rotor 21 through both Magnets 16, 23 is enabled.
  • the advantageous function of the adjusting device 1 according to the invention is that a constant magnetic field is generated by the permanent magnet 23 and thus without energy expenditure, pressed by the brake rotor 21 against the friction surfaces 22 of the magnetic body 17 and thus effective on the sun gear 9 of the superposition gear 3 base -Bremsmoment is generated.
  • the permanent magnet 23 is preferably dimensioned such that the camshaft 2 is automatically held in a defined basic position or adjusted in the engine start and a failure of the power supply of the solenoid 16 and / or its control by the set base braking torque in this. As a result, it is possible to dispense with a form-locking interlock between the brake rotor 21 and the planet carrier 11 or between the planet carrier 11 and the ring gear 12, which is associated with a space gain and cost savings.
  • the magnetic field of the permanent magnet 23 is increased to increase the brake rotor 21 effective braking torque, ie for adjusting the camshaft 2 in the direction early, by a rectified polarity of the electromagnet 16 and effective to reduce the on the brake rotor 21 Braking torque, ie for adjusting the camshaft 2 in the late direction, weakened by an opposite polarity of the electromagnet 16.
  • FIG. 2 Shown second variant of the adjusting device 1 according to the invention for the phase adjustment of a camshaft 2 differs from the in Fig. 1 shown variant only in that the ring-shaped permanent magnet 23 'now has a radial alignment of its poles (N, S) and in a corresponding axially outer, ie on the side remote from the brake rotor 21 side recess 24' of the magnetic body 17 of the electromagnet 16th is arranged.

Description

Die Erfindung betrifft einen Ventiltrieb eines Verbrennungskolbenmotors, mit einer ein Überlagerungsgetriebe mit zwei Eingangselementen und einem Ausgangselement umfassenden Stellvorrichtung zur Phasenverstellung einer Nockenwelle gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a valve train of a combustion piston engine, comprising a superposition gear with two input elements and an output element comprehensive adjusting device for phase adjustment of a camshaft according to the preamble of patent claim 1.

Aufgrund steigender Anforderungen bezüglich der Leistung, des Drehmoments, des Kraftstoffverbrauchs und des Emissionsverhaltens sind moderne Viertakt-Verbrennungskolbenmotoren fast ausnahmslos mit Stellvorrichtungen zur Phasenverstellung der Einlass- und/oder Auslassnockenwellen versehen, mittels der die Öffnungs- und Schließzeiten der Einlass- und/oder Auslassventile im Wesentlichen drehzahl- und lastabhängig verändert werden können. Durch eine geeignete Phasenverstellung der Einlass- und Auslassnockenwellen sind ein stabiler Leerlauf, ein erhöhtes Drehmoment bei niedrigen Motordrehzahlen, eine erhöhte Maximalleistung und verringerte Schadstoffemissionen im Teillastbetrieb des betreffenden Verbrennungskolbenmotors erreichbar.Due to increasing demands on performance, torque, fuel consumption and emissions behavior, modern four-stroke internal combustion piston engines are almost invariably provided with phasing devices for the intake and / or exhaust camshafts, by means of which the intake and / or exhaust valves are open and closed Essentially speed and load can be changed. By properly phasing the intake and exhaust camshafts, stable idling, increased torque at low engine speeds, increased maximum power, and reduced pollutant emissions in part-load operation of the subject internal combustion engine can be achieved.

Bekannte Stellvorrichtungen zur Phasenverstellung einer Nockenwelle sind als hydraulische Drehsteller oder als elektromechanische Drehsteller ausgebildet, die unmittelbar zwischen der mit einem Ketten- oder Zahnriemenzahnkranz versehenen Nabe und der drehfest mit der Nockenwelle verbundenen Achse des Nockenwellenrades angeordnet sind. Nachteilig an derartigen direkten Drehstellvorrichtungen sind jedoch die durch die geringe Übersetzung bedingten hohen Stellkräfte und der hohe Steuerungsaufwand für die Einstellung eines bestimmten Phasenwinkels.Known adjusting devices for phase adjustment of a camshaft are designed as hydraulic turntable or as electromechanical turntable, which are arranged directly between the provided with a chain or toothed belt sprocket hub and the rotatably connected to the camshaft axis of the camshaft sprocket. A disadvantage of such direct rotary adjusting devices, however, are the high translation forces caused by the low translation and the high control effort for setting a specific phase angle.

Zur Verbesserung der Steuerungseigenschaften sind daher Verstellvorrichtungen zur Phasenverstellung einer Nockenwelle vorgeschlagen worden, bei denen im Ventiltrieb zwischen der Kurbelwelle und der Nockenwelle ein mit einem Stellantrieb in Triebverbindung stehendes Überlagerungsgetriebe angeordnet ist. Das Überlagerungsgetriebe weist allgemein zwei Eingangselemente und ein Ausgangselement auf, wobei das erste Eingangselement, z.B. über einen Ketten- oder Zahnriementrieb, mit der Kurbelwelle in Triebverbindung steht, das zweite Eingangselement mit einem steuerbaren Stellantrieb in Verbindung steht, und das Ausgangselement drehfest mit der Nockenwelle verbunden ist.To improve the control properties adjusting devices for phase adjustment of a camshaft have therefore been proposed, in which in the valve train between the crankshaft and the camshaft with an actuator in drive connection standing superposition gear is arranged. The superposition gear generally has two input elements and an output element, wherein the first input element, for example via a chain or toothed belt drive, is in drive connection with the crankshaft, the second input element is in communication with a controllable actuator, and the output element is non-rotatably connected to the camshaft.

Als Überlagerungsgetriebe wird bevorzugt ein einfaches Planetengetriebe oder ein aus Komponenten von zwei Planetenradsätzen bestehendes gekoppeltes Planetengetriebe verwendet. Der Stellantrieb kann als ein hilfskraftgesteuerter Drehantrieb, wie z.B. als Elektromotor oder als hydraulischer Drehsteller, oder als eine steuerbare Bremseinrichtung ausgebildet sein.As a superposition gear is preferably a simple planetary gear or one consisting of components of two Planetenradsätzen coupled planetary gear used. The actuator may be used as a servo-controlled rotary drive, such as a rotary actuator. be designed as an electric motor or as a hydraulic turntable, or as a controllable braking device.

Eine hinsichtlich ihres Aufbaus und ihrer Steuerbarkeit besonders einfache und kostengünstige Bremseinrichtung ist als eine steuerbare Reibungsbremse ausgebildet, die einen gehäusefesten Elektromagneten mit einem Magnetkörper und einer Magnetspule sowie einen drehfest und axial verschiebbar mit dem zweiten Eingangselement verbundenen und durch das Magnetfeld des Elektromagneten gegen eine gehäusefeste Reibfläche drückbaren Bremsrotor umfasst. Da das zweite Eingangselementen im ungebremsten Zustand schneller als das erste Eingangselement rotieren würde, wird durch die Einstellung eines bestimmten, auf den Bremsrotor und damit auf das zweite Eingangselement wirksamen mittleren Bremsmomentes eine bestimmte Phasenlage der zugeordneten Nockenwelle eingehalten. Ausgehend von dieser Phasenlage der Nockenwelle wird eine Verstellung nach früh durch eine kurzzeitige Erhöhung des Bremsmomentes und nach spät durch eine kurzzeitige Verringerung des Bremsmomentes erreicht.A particularly simple and cost-effective in terms of their structure and controllability braking device is designed as a controllable friction brake, a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the second input element and by the magnetic field of the electromagnet against a housing-fixed friction surface includes releasable brake rotor. Since the second input elements in the unbraked state would rotate faster than the first input element, a certain phase angle of the associated camshaft is maintained by the setting of a specific, acting on the brake rotor and thus on the second input element mean braking torque. Starting from this phase position of the camshaft, an adjustment is achieved early by a brief increase in the braking torque and late by a brief reduction in the braking torque.

Eine erste derartige Stellvorrichtung zur Phasenverstellung einer Nockenwelle mit einem Überlagerungsgetriebe und einer mit diesem in Wirkverbindung stehenden Bremseinrichtung ist aus der DE 10 2006 011 806 A1 bekannt. Das Überlagerungsgetriebe dieser Stellvorrichtung ist als ein gekoppeltes Planetengetriebe mit zwei Sonnenrädern mit unterschiedlichen Durchmessern und Zähnezahlen sowie einem mehrere drehbar gelagerte zweistufige Planetenräder tragenden Planetenträger ausgebildet, wobei das erste Eingangselement durch den Planetenträger, das zweite Eingangselement durch das kleinere Sonnenrad, und das Ausgangselement durch das größere Sonnenrad gebildet sind.A first such adjusting device for the phase adjustment of a camshaft with a superposition gear and a standing in operative connection with this braking device is from the DE 10 2006 011 806 A1 known. The superposition gear of this actuator is as a coupled planetary gear with two sun gears with different diameters and tooth numbers and a plurality of rotatably mounted two-stage planetary gear planet carrier formed, wherein the first input element are formed by the planet carrier, the second input element by the smaller sun gear, and the output member by the larger sun gear.

Die Bremseinrichtung ist als eine elektromagnetisch steuerbare Reibungsbremse ausgebildet, die einen gehäusefesten Elektromagneten mit einem Magnetkörper und einer Magnetspule sowie einen drehfest und axial verschiebbar mit dem kleineren Sonnenrad verbundenen sowie durch das Magnetfeld des Elektromagneten gegen eine an dem Magnetkörper angeordnete Reibfläche drückbaren Bremsrotor umfasst. Bei abgeschaltetem Elektromagneten wird der scheibenförmige Bremsrotor von einer Feder axial gegen den Planetenträger gedrückt, wodurch mindestens ein Verriegelungselement in eine entsprechende Ausnehmung des Planetenträgers einrastet, wodurch das Planetengetriebe in sich blockiert ist und starr umläuft. Bei eingeschaltetem Elektromagneten wird der Bremsrotor gegen die Rückstellkraft der Feder axial nach außen gegen die Reibfläche des Magnetkörpers gezogen, wodurch die Kopplung zwischen dem kleineren Sonnenrad sowie dem Planetenträger aufgehoben und das kleinere Sonnenrad entsprechend dem wirksamen Bremsmoment abgebremst wird.The braking device is designed as an electromagnetically controllable friction brake, which comprises a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the smaller sun gear and by the magnetic field of the electromagnet against a arranged on the magnetic body friction surface brake rotor. When the electromagnet is switched off the disc-shaped brake rotor is pressed by a spring axially against the planet carrier, whereby at least one locking element engages in a corresponding recess of the planet carrier, whereby the planetary gear is locked in and rigidly rotates. When the electromagnet is turned on, the brake rotor against the restoring force of the spring is pulled axially outwardly against the friction surface of the magnetic body, whereby the coupling between the smaller sun gear and the planet carrier canceled and the smaller sun gear is decelerated according to the effective braking torque.

Eine hinsichtlich ihres funktionalen Aufbaus weitgehend identische Stellvorrichtung zur Phasenverstellung einer Nockenwelle ist in der DE 10 2006 028 554 A1 beschrieben. Im Unterschied zu der vorgenannten Stellvorrichtung ist das Überlagerungsgetriebe dieser Stellvorrichtung als ein einfaches Planetengetriebe mit einem Sonnenrad, einem mehrere drehbar gelagerte Planetenräder tragenden Planetenträger und einem Hohlrad ausgebildet, wobei das erste Eingangselement durch den Planetenträger, das zweite Eingangselement durch das Sonnenrad und das Ausgangselement durch das Hohlrad gebildet sind.A largely identical in terms of their functional structure adjusting device for phase adjustment of a camshaft is in the DE 10 2006 028 554 A1 described. In contrast to the aforementioned adjusting device, the superposition gear of this adjusting device is designed as a simple planetary gear with a sun gear, a plurality of rotatably mounted planetary planet carrier and a ring gear, wherein the first input element by the planet carrier, the second input element by the sun gear and the output member by the Ring gear are formed.

Eine weitere gattungsgemäße Stellvorrichtung zur Phasenverstellung einer Nockenwelle gemäß der DE 10 2008 043 673 A1 weist dagegen eine inverse Steuerungscharakteristik auf. Das Überlagerungsgetriebe ist wie bei der Stellvorrichtung nach der DE 10 2006 028 554 A1 als ein einfaches Planetengetriebe ausgebildet. Der drehfest und axial verschiebbar auf einer starr mit dem Sonnenrad verbundenen Welle gelagerte Bremsrotor ist dagegen axial außerhalb des Elektromagneten angeordnet und über eine Feder axial gegenüber einer frei drehbar gelagerten Druckscheibe verspannt. Die Druckscheibe ist axial innerhalb des Elektromagneten benachbart zu dem Planetenträger angeordnet und weist Steuernocken zum Eingriff in Ausnehmungen des Planetenträgers und von Steuernasen des Hohlrades auf, wodurch bei abgeschaltetem Elektromagneten eine Verriegelung des Planetenträgers mit dem Hohlrad in einer Notlaufposition erreichbar ist. Außerdem wird der Bremsrotor bei abgeschaltetem Elektromagneten durch die Feder gegen eine gehäusefeste Reibfläche gedrückt. Bei eingeschaltetem Elektromagneten wird die Druckscheibe gegen die Rückstellkraft der Feder axial von dem Planetenträger weggezogen und damit die Verriegelung zwischen dem Planetenträger und dem Hohlrad gelöst. Zugleich wird der Bremsrotor entsprechend der Stärke des Magnetfeldes gegen die Rückstellkraft der Feder axial von der gehäusefesten Reibfläche weggezogen und damit das wirksame Bremsmoment reduziert.Another generic adjusting device for phase adjustment of a camshaft according to the DE 10 2008 043 673 A1 has an inverse control characteristic. The superposition gear is as in the actuator after the DE 10 2006 028 554 A1 designed as a simple planetary gear. The rotatably mounted and axially displaceable on a rigidly connected to the sun gear shaft mounted brake rotor, however, is arranged axially outside of the electromagnet and clamped by a spring axially against a freely rotatably mounted pressure plate. The pressure plate is disposed axially within the electromagnet adjacent to the planet carrier and has control cam for engagement in recesses of the planet carrier and of control lugs of the ring gear, whereby a lock of the planet carrier with the ring gear in an emergency position is reached with the electromagnet off. In addition, the brake rotor is pressed with the solenoid switched off by the spring against a housing-fixed friction surface. When the electromagnet is turned on, the thrust washer is axially pulled away from the planet carrier against the restoring force of the spring and thus releases the lock between the planet carrier and the ring gear. At the same time, the brake rotor is axially pulled away from the housing-fixed friction surface according to the strength of the magnetic field against the restoring force of the spring and thus reduces the effective braking torque.

Nachteilig an den bekannten Stellvorrichtungen zur Phasenverstellung einer Nockenwelle ist somit der permanente Energieverbrauch des Elektromagneten während des Betriebs des Verbrennungskolbenmotors und der jeweiligen Stellvorrichtung. Ebenfalls ist bei diesen Stellvorrichtungen jeweils ein relativ starkes Magnetfeld erforderlich, um gegen die Rückstellkraft der Feder ein ausreichend hohes Bremsmoment zum Einstellen und Halten des jeweiligen Phasenwinkels der Nockenwelle zu erzielen.A disadvantage of the known adjusting devices for phase adjustment of a camshaft is thus the permanent power consumption of the electromagnet during operation of the internal combustion piston engine and the respective adjusting device. Also, in each case, a relatively strong magnetic field is required in order to achieve against the restoring force of the spring, a sufficiently high braking torque for adjusting and holding the respective phase angle of the camshaft.

Vor diesem Hintergrund liegt der Erfindung die Aufgabe zugrunde, einen Ventiltrieb eines Verbrennungskolbenmotors mit einer Stellvorrichtung zur Phasenverstellung einer Nockenwelle der eingangs genannten Art im Hinblick auf einen geringeren Energieverbrauch und einen vereinfachten Aufbau der Stellvorrichtung weiterzubilden.Against this background, the invention has the object, a valve train of a combustion piston engine with an adjusting device for phase adjustment of a camshaft of the type mentioned in terms of to develop a lower energy consumption and a simplified structure of the adjusting device.

Diese Aufgabe ist in Verbindung mit den Merkmalen des Oberbegriffs des Anspruchs 1 dadurch gelöst, dass axial benachbart zu dem Bremsrotor ein Permanentmagnet angeordnet ist, durch dessen Magnetfeld der Bremsrotor zur Einstellung eines Basis-Bremsmomentes mit einer entsprechenden Basis-Anpresskraft gegen eine gehäusefeste Reibfläche drückbar ist.This object is achieved in conjunction with the features of the preamble of claim 1, characterized in that axially adjacent to the brake rotor, a permanent magnet is arranged, through the magnetic field of the brake rotor for setting a base braking torque with a corresponding base contact pressure against a housing-fixed friction surface can be pressed ,

Vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Ventiltriebs sind Gegenstand der Unteransprüche.Advantageous embodiments and further developments of the valve train according to the invention are the subject of the dependent claims.

Die Erfindung geht demnach aus von einem an sich bekannten Ventiltrieb eines Verbrennungskolbenmotors, der eine ein Überlagerungsgetriebe mit zwei Eingangselementen und einem Ausgangselement umfassende Stellvorrichtung zur Phasenverstellung einer Nockenwelle aufweist. Das erste Eingangselement steht, z.B. über einen Ketten- oder Zahnriementrieb, mit einer Kurbelwelle in Triebverbindung, das zweite Eingangselement steht mit einer steuerbaren Bremseinrichtung in Wirkverbindung, und das Ausgangselement ist drehfest mit der Nockenwelle verbunden. Die Bremseinrichtung ist als eine elektromagnetisch steuerbare Reibungsbremse ausgebildet, die einen gehäusefesten Elektromagneten mit einem Magnetkörper und einer Magnetspule sowie einen drehfest und axial verschiebbar mit dem zweiten Eingangselement verbundenen sowie durch das Magnetfeld des Elektromagneten gegen eine gehäusefeste Reibfläche drückbaren Bremsrotor umfasst.The invention is therefore based on a known valve train of a combustion piston engine, which has a superposition gear with two input elements and an output element comprehensive adjusting device for phase adjustment of a camshaft. The first input element is, e.g. via a chain or toothed belt drive, with a crankshaft in drive connection, the second input element is in operative connection with a controllable braking device, and the output element is non-rotatably connected to the camshaft. The braking device is designed as an electromagnetically controllable friction brake, which comprises a housing-fixed electromagnet with a magnetic body and a magnetic coil and a rotatably and axially slidably connected to the second input element and can be pressed by the magnetic field of the electromagnet against a housing-fixed friction surface brake rotor.

Durch die erfindungsgemäße Anordnung eines Permanentmagneten axial benachbart zu dem Bremsrotor wird nun ein weitgehend konstantes Magnetfeld erzeugt, durch das der Bremsrotor bei abgeschaltetem Elektromagneten mit einer bestimmten Basis-Anpresskraft gegen eine gehäusefeste Reibfläche gedrückt und somit ein auf das zweite Eingangselement wirksames Basis-Bremsmoment eingestellt wird. Zur Einstellung eines von diesem Basis-Bremsmoment abweichenden Bremsmoments ist nun nur noch eine Erhöhung oder Verringerung der Basis-Anpresskraft mittels des Elektromagneten erforderlich, was gegenüber den bekannten Stellvorrichtungen einen deutlich geringeren Energieaufwand erfordert.The inventive arrangement of a permanent magnet axially adjacent to the brake rotor, a substantially constant magnetic field is now generated, pressed by the brake rotor with the electromagnet off with a certain base contact pressure against a housing-fixed friction surface and thus an effective on the second input element base braking torque is set , To set one of this base brake torque Deviating braking torque is now only an increase or decrease in the base contact force by means of the electromagnet required, which requires a significantly lower energy consumption compared to the known adjusting devices.

Der Permanentmagnet ist vorteilhaft derart ausgebildet und angeordnet, dass die Nockenwelle beim Motorstart und bei einem Ausfall der Spannungsversorgung des Elektromagneten und/oder seiner Steuerung durch das eingestellte Basis-Bremsmoment selbsttätig in einer definierten Grundstellung gehalten oder in diese verstellt wird. Hierdurch wird erreicht, dass der Elektromagnet nur zur Verstellung der aktuellen Phasenlage der Nockenwelle eingeschaltet werden muss, und dass auf eine spezielle Sicherheitsvorrichtung (Fail Save), wie eine bei den bekannten Stellvorrichtungen vorgesehene formschlüssige Verriegelung zwischen dem Bremsrotor und dem zweiten Eingangselement des Überlagerungsgetriebes oder zwischen dem ersten Eingangselement und dem Ausgangselement des Überlagerungsgetriebes, verzichtet werden kann.The permanent magnet is advantageously designed and arranged such that the camshaft is automatically held in a defined initial position or adjusted in the engine start and a failure of the power supply of the electromagnet and / or its control by the set base braking torque. This ensures that the electromagnet must be turned on only to adjust the current phase position of the camshaft, and that on a special safety device (Fail Save), as provided in the known actuators positive locking between the brake rotor and the second input element of the superposition gear or between the first input element and the output element of the superposition gearing, can be dispensed with.

Im Prinzip könnte der Permanentmagnet radial innerhalb oder außerhalb des Elektromagneten oder auf der von dem Elektromagneten abgewandten Seite axial benachbart zu dem Bremsrotor angeordnet sein. Dies würde jedoch nachteilig zu einem erhöhten Bauaufwand und größeren Abmessungen der Bremseinrichtung führen. Daher ist vorliegend vorgesehen, dass der Permanentmagnet innerhalb des Magnetflusses des Elektromagneten angeordnet ist, so dass der Magnetkörper des Elektromagneten und der angrenzende Abschnitt des Bremsrotors zur Bildung eines geschlossenen Magnetflusskreises des Permanentmagneten genutzt wird. Zudem wird hierdurch die Überlagerung der Magnetfelder beider Magnete und somit die Steuerbarkeit des resultierenden Bremsmomentes verbessert.In principle, the permanent magnet could be arranged radially inside or outside the electromagnet or on the side facing away from the electromagnet axially adjacent to the brake rotor. However, this would disadvantageously lead to increased construction costs and larger dimensions of the braking device. Therefore, it is provided herein that the permanent magnet is disposed within the magnetic flux of the electromagnet, so that the magnetic body of the electromagnet and the adjacent portion of the brake rotor is used to form a closed magnetic flux circuit of the permanent magnet. In addition, this will improve the superposition of the magnetic fields of both magnets and thus the controllability of the resulting braking torque.

Eine derartige Anordnung des Permanentmagneten kann zweckmäßig derart realisiert sein, dass der Permanentmagnet ringförmig ausgebildet ist und eine axiale Ausrichtung seiner Pole (N, S) aufweist, sowie in einer entsprechenden radial inneren oder äußeren Ausnehmung des Magnetkörpers des Elektromagneten angeordnet ist.Such an arrangement of the permanent magnet may be expediently realized such that the permanent magnet is annular and has an axial alignment of its poles (N, S), as well as in a corresponding radially inner or outer recess of the magnetic body of the electromagnet is arranged.

Alternativ dazu ist es auch möglich, dass der Permanentmagnet ringförmig ausgebildet ist und eine radiale Ausrichtung seiner Pole (N, S) aufweist, sowie in einer entsprechenden axial äußeren, d.h. auf der dem Bremsrotor abgewandten Seite angeordneten Ausnehmung des Magnetkörpers des Elektromagneten angeordnet ist.Alternatively, it is also possible that the permanent magnet is annular and has a radial orientation of its poles (N, S), and in a corresponding axially outer, i. arranged on the side remote from the brake rotor arranged recess of the magnetic body of the electromagnet.

Die Verstellung des Phasenwinkels der Nockenwelle erfolgt nun auf einfache Weise dadurch, dass das Magnetfeld des Permanentmagneten zur Erhöhung des auf den Bremsrotor wirksamen Bremsmomentes, d.h. zur Verstellung der Nockenwelle in Richtung früh, mittels einer geeigneten Steuerungsvorrichtung durch eine gleichgerichtete Polung des Elektromagneten verstärkt und zur Verringerung des auf den Bremsrotor wirksamen Bremsmomentes, d.h. zur Verstellung der Nockenwelle in Richtung spät, durch eine entgegengerichtete Polung des Elektromagneten abgeschwächt wird.The adjustment of the phase angle of the camshaft now takes place in a simple manner in that the magnetic field of the permanent magnet for increasing the braking torque acting on the brake rotor, i. for adjusting the camshaft in the early direction, amplified by a suitable control device by a rectified polarity of the electromagnet and to reduce the braking torque acting on the brake rotor, i. for adjusting the camshaft toward late, is attenuated by an opposite polarity of the electromagnet.

Zur Absicherung gegen Montagefehler der Stelleinrichtung und gegen einen übermäßigen Verschleiß an der gehäusefesten Bremsfläche und an dem Bremsrotor können zwischen dem ersten Eingangselement und dem Ausgangselement des Überlagerungsgetriebes wirksame Endanschläge zur Begrenzung des Verstellbereichs der Phasenverstellung der Nockenwelle auf einen zulässigen Phasenwinkelbereich vorgesehen sein.To protect against assembly errors of the adjusting device and against excessive wear on the housing-fixed braking surface and the brake rotor can be provided between the first input element and the output element of the superposition gear effective limit stops for limiting the adjustment of the phase adjustment of the camshaft to a permissible phase angle range.

Zur Verdeutlichung der Erfindung ist der Beschreibung eine Zeichnung mit Ausführungsbeispielen beigefügt. In dieser zeigt

Fig. 1
einen Ausschnitt eines Ventiltriebs mit einer erfindungsgemäßen Stellvorrichtung zur Phasenverstellung einer Nockenwelle in einem Längsmittelschnitt, und
Fig. 2
eine zweite Variante der erfindungsgemäßen Stellvorrichtung zur Phasenverstellung einer Nockenwelle nach Fig. 1.
To clarify the invention, the description is accompanied by a drawing with exemplary embodiments. In this shows
Fig. 1
a detail of a valve train with an adjusting device according to the invention for phase adjustment of a camshaft in a longitudinal center section, and
Fig. 2
A second variant of the adjusting device according to the invention for the phase adjustment of a camshaft after Fig. 1 ,

Ein in Fig. 1 ausschnittweise abgebildeter Ventiltrieb eines Verbrennungskolbenmotors ist mit einer Stellvorrichtung 1 zur Phasenverstellung einer Nockenwelle 2 versehen, die ein Überlagerungsgetriebe 3 mit zwei Eingangselementen 4, 5 und einem Ausgangselement 6 sowie eine steuerbare Bremseinrichtung 7 umfasst. Vorliegend ist das Überlagerungsgetriebe 3 beispielhaft als ein einfaches Planetengetriebe 8 mit einem Sonnenrad 9, einem mehrere drehbar gelagerte Planetenräder 10 tragenden Planetenträger 11 und einem Hohlrad 12 ausgebildet. Der Planetenträger 11 bildet das erste Eingangselement 4 und ist mit einem Kettenzahnkranz 13 versehen, über den mittels einer nicht abgebildeten Steuerkette eine formschlüssige Triebverbindung mit der Kurbelwelle des Verbrennungskolbenmotors besteht. Das Sonnenrad 9 bildet das zweite Eingangselement 5, das mit der Bremseinrichtung 7 in Wirkverbindung steht. Das Hohlrad 12 bildet das Ausgangselement 6 und ist über mehrere Schrauben 14 starr mit der Nockenwelle 2 verbunden.An in Fig. 1 partially formed valve train of a combustion piston engine is provided with an adjusting device 1 for phase adjustment of a camshaft 2, which comprises a superposition gear 3 with two input elements 4, 5 and an output element 6 and a controllable braking device 7. In the present case, the superposition gear 3 is exemplified as a simple planetary gear 8 with a sun gear 9, a plurality of rotatably mounted planet gears 10 supporting planet carrier 11 and a ring gear 12 is formed. The planet carrier 11 forms the first input element 4 and is provided with a chain sprocket 13, via which by means of a timing chain, not shown, a positive drive connection with the crankshaft of the internal combustion piston engine. The sun gear 9 forms the second input element 5, which is in operative connection with the braking device 7. The ring gear 12 forms the output element 6 and is connected via a plurality of screws 14 rigidly connected to the camshaft 2.

Die Bremseinrichtung 7 ist als eine elektromagnetisch steuerbare Reibungsbremse 15 ausgebildet und umfasst einen gehäusefesten Elektromagneten 16 mit einem im Querschnitt U-förmigen und aus einem ferromagnetischen Material bestehenden Magnetkörper 17 und einer Magnetspule 18 sowie einen über eine Innenaxialverzahnung 19 drehfest und axial verschiebbar auf der axial verlängerten Außenverzahnung 20 des Sonnenrades 9 gelagerten Bremsrotor 21. Zumindest im an den Magnetkörper 17 angrenzenden Bereich besteht der Bremsrotor 21 aus einem ferromagnetischen Material, so dass dieser bei eingeschaltetem Elektromagneten 16 durch das erzeugte Magnetfeld axial gegen Reibflächen 22 des Magnetkörpers 17 gedrückt und somit ein auf das Sonnenrad 9 wirksames Bremsmoment erzeugt wird.The braking device 7 is designed as an electromagnetically controllable friction brake 15 and comprises a housing-fixed electromagnet 16 with a U-shaped and made of a ferromagnetic material magnetic body 17 and a magnetic coil 18 and a Innenaxialverzahnung 19 rotationally fixed and axially displaceable on the axially elongated At least in the area adjacent to the magnetic body 17 region of the brake rotor 21 is made of a ferromagnetic material, so that it is pressed when the electromagnet 16 by the generated magnetic field axially against friction surfaces 22 of the magnetic body 17 and thus on the Sun gear 9 effective braking torque is generated.

Erfindungsgemäß ist nun ein Permanentmagnet 23 vorgesehen, der vorliegend ringförmig ausgebildet ist, eine axiale Ausrichtung der Pole N, S aufweist, und in einer entsprechenden radial äußeren Ausnehmung 24 des Magnetkörpers 17 des Elektromagneten 16 angeordnet ist. Hierdurch ist der Permanentmagnet 23 innerhalb des Magnetflusses des Elektromagneten 16 angeordnet, wodurch zum einen die Überlagerung der Magnetfelder beider Magnete 16, 23 verbessert und zum anderen die gemeinsame Nutzung des Magnetkörpers 17 zur Verstärkung des Magnetfeldes und dessen Reibflächen 22 zur Abbremsung des Bremsrotors 21 durch beide Magnete 16, 23 ermöglicht wird.According to the invention, a permanent magnet 23 is now provided, which in the present case is annular, has an axial orientation of the poles N, S, and in a corresponding radially outer recess 24 of the magnetic body 17 of the electromagnet 16 is arranged. As a result, the permanent magnet 23 is disposed within the magnetic flux of the electromagnet 16, whereby on the one hand, the superposition of the magnetic fields of both magnets 16, 23 improves and on the other the common use of the magnetic body 17 to amplify the magnetic field and its friction surfaces 22 for braking the brake rotor 21 through both Magnets 16, 23 is enabled.

Die vorteilhafte Funktion der erfindungsgemäßen Stellvorrichtung 1 besteht darin, dass durch den Permanentmagneten 23 und somit ohne Energieaufwand ein konstantes Magnetfeld erzeugt wird, durch das der Bremsrotor 21 gegen die Reibflächen 22 des Magnetkörpers 17 gedrückt und somit ein auf das Sonnenrad 9 des Überlagerungsgetriebes 3 wirksames Basis-Bremsmoment erzeugt wird.The advantageous function of the adjusting device 1 according to the invention is that a constant magnetic field is generated by the permanent magnet 23 and thus without energy expenditure, pressed by the brake rotor 21 against the friction surfaces 22 of the magnetic body 17 and thus effective on the sun gear 9 of the superposition gear 3 base -Bremsmoment is generated.

Der Permanentmagnet 23 ist bevorzugt derart dimensioniert, dass das die Nockenwelle 2 beim Motorstart und bei einem Ausfall der Spannungsversorgung des Elektromagneten 16 und/oder seiner Steuerung durch das eingestellte Basis-Bremsmoment selbsttätig in einer definierten Grundstellung gehalten oder in diese verstellt wird. Dadurch kann auf eine bei den bekannten Stellvorrichtungen jeweils vorgesehene formschlüssige Verriegelung zwischen dem Bremsrotor 21 und dem Planetenträger 11 bzw. zwischen dem Planetenträger 11 und dem Hohlrad 12 verzichtet werden, was mit einem Bauraumgewinn und mit Kosteneinsparungen verbunden ist.The permanent magnet 23 is preferably dimensioned such that the camshaft 2 is automatically held in a defined basic position or adjusted in the engine start and a failure of the power supply of the solenoid 16 and / or its control by the set base braking torque in this. As a result, it is possible to dispense with a form-locking interlock between the brake rotor 21 and the planet carrier 11 or between the planet carrier 11 and the ring gear 12, which is associated with a space gain and cost savings.

Zur Verstellung der Phasenlage der Nockenwelle 2 wird das Magnetfeld des Permanentmagneten 23 zur Erhöhung des auf den Bremsrotor 21 wirksamen Bremsmomentes, d.h. zur Verstellung der Nockenwelle 2 in Richtung früh, durch eine gleichgerichtete Polung des Elektromagneten 16 verstärkt und zur Verringerung des auf den Bremsrotor 21 wirksamen Bremsmomentes, d.h. zur Verstellung der Nockenwelle 2 in Richtung spät, durch eine entgegengerichtete Polung des Elektromagneten 16 abgeschwächt. Durch die Verstellung des auf den Bremsrotor 21 wirksamen Bremsmomentes relativ zu dem durch den Permanentmagneten 23 erzeugten Basis-Bremsmomentes ist der Energieverbrauch des Elektromagneten 16 gegenüber den bekannten Stellvorrichtungen deutlich niedriger, und die Steuerbarkeit des Bremsmomentes durch eine erhöhte Dynamik verbessert.To adjust the phase position of the camshaft 2, the magnetic field of the permanent magnet 23 is increased to increase the brake rotor 21 effective braking torque, ie for adjusting the camshaft 2 in the direction early, by a rectified polarity of the electromagnet 16 and effective to reduce the on the brake rotor 21 Braking torque, ie for adjusting the camshaft 2 in the late direction, weakened by an opposite polarity of the electromagnet 16. By the adjustment of on the braking rotor 21 effective braking torque relative to the base brake torque generated by the permanent magnet 23, the energy consumption of the electromagnet 16 compared to the known actuators significantly lower, and improves the controllability of the braking torque by increased dynamics.

Eine in Fig. 2 abgebildete zweite Variante der erfindungsgemäßen Stellvorrichtung 1 zur Phasenverstellung einer Nockenwelle 2 unterscheidet sich von der in Fig. 1 abgebildeten Variante nur dadurch, dass der ringförmig ausgebildete Permanentmagnet 23' nunmehr eine radiale Ausrichtung seiner Pole (N, S) aufweist und in einer entsprechenden axial äußeren, d.h. auf der von dem Bremsrotor 21 abgewandten Seite angeordneten Ausnehmung 24' des Magnetkörpers 17 des Elektromagneten 16 angeordnet ist.An in Fig. 2 Shown second variant of the adjusting device 1 according to the invention for the phase adjustment of a camshaft 2 differs from the in Fig. 1 shown variant only in that the ring-shaped permanent magnet 23 'now has a radial alignment of its poles (N, S) and in a corresponding axially outer, ie on the side remote from the brake rotor 21 side recess 24' of the magnetic body 17 of the electromagnet 16th is arranged.

Bezugszeichenreference numeral

11
Stellvorrichtunglocking device
22
Nockenwellecamshaft
33
ÜberlagerungsgetriebeSuperposition gear
44
Erstes EingangselementFirst input element
55
Zweites EingangselementSecond input element
66
Ausgangselementoutput element
77
Bremseinrichtungbraking means
88th
Planetengetriebeplanetary gear
99
Sonnenradsun
1010
Planetenradplanet
1111
Planetenträgerplanet carrier
1212
Hohlradring gear
1313
KettenzahnkranzChain sprocket
1414
Schraubescrew
1515
Reibungsbremsefriction brake
1616
Elektromagnetelectromagnet
1717
Magnetkörpermagnetic body
1818
Magnetspulesolenoid
1919
Innenverzahnunginternal gearing
2020
Außenverzahnungexternal teeth
2121
Bremsrotorbrake rotor
2222
Reibflächefriction surface
23, 23'23, 23 '
Permanentmagnetpermanent magnet
24, 24'24, 24 '
Ausnehmungrecess
NN
Pol von PermanentmagnetPole of permanent magnet
SS
Pol von PermanentmagnetPole of permanent magnet

Claims (7)

  1. Valve train of a combustion piston engine, having an actuating apparatus (1), which comprises a variable-ratio gear mechanism (3) having two input elements (4, 5) and one output element (6), for phase adjustment of a camshaft (2), the first input element (4) of the said actuating apparatus being connected in a driving manner to a crankshaft, and the second input element (5) of the said actuating apparatus being operatively connected to a controllable brake device (7), and the output element (6) of the said actuating apparatus being connected to the camshaft (2) in a rotationally fixed manner, wherein the brake device (7) is designed as an electromagnetically controllable friction brake (15) which comprises a solenoid (16) which is fixed to the housing and has a magnet body (17) and a magnet coil (18), and also comprises a brake rotor (21) which is connected in a rotationally fixed and axially movable manner to the second input element (5) and can be pushed by the magnetic field of the solenoid (16) against a friction surface (22) which is fixed to the housing, characterized in that a permanent magnet (23, 23') is arranged axially adjacent to the brake rotor (21), it being possible for the brake rotor (21) to be pushed at a corresponding base pressing force against a friction surface (22), which is fixed to the housing, by the magnetic field of the said permanent magnet, to set a base braking torque.
  2. Valve train according to Claim 1, characterized in that the permanent magnet (23, 23') is designed and arranged in such a way that the camshaft (2) is held in a defined basic position or moved to the said defined basic position automatically by the set base braking torque when the motor is started and in the event of a failure in the voltage supply to the solenoid (16) and/or the control means of the said solenoid.
  3. Valve train according to Claim 1 or 2, characterized in that the permanent magnet (23, 23') is arranged within the magnetic flux of the solenoid (16).
  4. Valve train according to Claim 3, characterized in that the permanent magnet (23) is of annular design and has an axial orientation of its poles (N, S), and also is arranged in a corresponding radially inner or outer recess (24) in the magnet body (17) of the solenoid (16).
  5. Valve train according to Claim 3, characterized in that the permanent magnet (23') is of annular design and has a radial orientation of its poles (N, S), and also is arranged in a corresponding axially outer recess (24') in the magnet body (17) of the solenoid (16).
  6. Valve train according to at least one of Claims 1 to 5, characterized in that the magnetic field of the permanent magnet (23, 23') can be intensified in order to increase the braking torque, which acts on the brake rotor (21), by means of a control apparatus by the solenoid (16) being polarized in the same direction, and can be reduced in order to reduce the braking torque, which acts on the brake rotor (21), by the solenoid (16) being polarized in the opposite direction.
  7. Valve train according to at least one of Claims 1 to 6, characterized in that end stops which act between the first input element (4) and the output element (6) of the variable-ratio gear mechanism (3) are provided for limiting the adjustment range of the phase adjustment of the camshaft (2) to a permissible phase angle range.
EP11730299.2A 2010-08-27 2011-07-07 Valve train of a combustion piston engine Not-in-force EP2609304B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010039861A DE102010039861A1 (en) 2010-08-27 2010-08-27 Valve gear of a combustion piston engine
PCT/EP2011/061473 WO2012025287A1 (en) 2010-08-27 2011-07-07 Valve train of a combustion piston engine

Publications (2)

Publication Number Publication Date
EP2609304A1 EP2609304A1 (en) 2013-07-03
EP2609304B1 true EP2609304B1 (en) 2014-11-05

Family

ID=44628171

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11730299.2A Not-in-force EP2609304B1 (en) 2010-08-27 2011-07-07 Valve train of a combustion piston engine

Country Status (5)

Country Link
US (1) US8707918B2 (en)
EP (1) EP2609304B1 (en)
JP (1) JP2013536362A (en)
DE (1) DE102010039861A1 (en)
WO (1) WO2012025287A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014001397A1 (en) * 2014-02-04 2015-08-06 Daimler Ag Camshaft adjusting device
DE102014006809A1 (en) * 2014-05-08 2015-11-12 Daimler Ag Camshaft adjusting device
DE102014009188A1 (en) * 2014-06-12 2015-12-17 Daimler Ag Method for adjusting a phase angle of a camshaft
DE102014009726A1 (en) 2014-06-28 2015-12-31 Daimler Ag Camshaft adjusting device with an electromechanical brake unit
DE102014011152A1 (en) 2014-07-25 2015-01-15 Daimler Ag Camshaft adjuster for adjusting a phasing of a camshaft
US9545903B2 (en) * 2015-02-02 2017-01-17 Goodrich Corporation Electromechanical brake actuator with variable speed epicyclic gearbox
DE102016007818A1 (en) 2016-06-23 2017-12-28 Daimler Ag Adjusting gear with a tooth-free active connection

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10220687A1 (en) 2002-05-10 2003-11-20 Ina Schaeffler Kg Camshaft adjuster with electric drive
JP3986371B2 (en) 2002-06-07 2007-10-03 株式会社日立製作所 Valve timing control device for internal combustion engine
DE10352361B4 (en) * 2003-11-10 2020-08-27 Schaeffler Technologies AG & Co. KG Camshaft adjuster with electric drive
JP2005146993A (en) * 2003-11-17 2005-06-09 Hitachi Ltd Valve timing control device for internal combustion engine
CN1993538A (en) * 2004-09-01 2007-07-04 日锻汽门株式会社 Phase varying device of engine
DE102006011806A1 (en) 2006-03-15 2007-10-04 Zf Friedrichshafen Ag Adjustment device for a camshaft
DE102006028554B4 (en) 2006-06-22 2018-03-08 Daimler Ag adjustment
JP2008115867A (en) * 2007-11-26 2008-05-22 Hitachi Ltd Control device for variable valve timing mechanism
JP2009228427A (en) * 2008-03-19 2009-10-08 Hitachi Ltd Valve timing control device of internal combustion engine
DE102008031505A1 (en) * 2008-07-03 2010-01-07 Daimler Ag camshaft unit
DE102008043673A1 (en) 2008-11-12 2010-05-20 Zf Friedrichshafen Ag Camshaft adjustment system for internal combustion engine, has differential drives formed as planet gear with output element comprising hollow wheel
DE102008043671A1 (en) * 2008-11-12 2010-05-20 Zf Friedrichshafen Ag Adjustment system for camshafts of an internal combustion engine
DE102008060926A1 (en) 2008-12-06 2010-06-10 Daimler Ag Cam shaft phase position adjusting device, has brake unit provided for producing brake torque introducing adjustment process, and actuator unit reducing brake torque of brake unit actively in operating mode
DE102008060927A1 (en) 2008-12-06 2010-06-10 Daimler Ag Phase adjusting device for adjusting phasing of shaft, particularly valve drive adjusting device, has gear unit, which has drive element for adjusting phasing, and has operating actuator unit
DE102010021774A1 (en) 2010-05-27 2011-12-01 Daimler Ag Adjusting device for an internal combustion engine valve drive device

Also Published As

Publication number Publication date
EP2609304A1 (en) 2013-07-03
JP2013536362A (en) 2013-09-19
DE102010039861A1 (en) 2012-03-01
US8707918B2 (en) 2014-04-29
WO2012025287A1 (en) 2012-03-01
US20130146007A1 (en) 2013-06-13

Similar Documents

Publication Publication Date Title
EP2609304B1 (en) Valve train of a combustion piston engine
DE3830382C1 (en)
DE102007049072A1 (en) Phase adjuster for an internal combustion engine with an Oldham clutch
DE102008050827A1 (en) Adjusting device for adjusting compression ratios of Otto engine crankshaft, has actuator displacing locking mechanism into free running position in fail-safe position to allow crankshaft to automatically take minimum compression position
WO2007093479A1 (en) Camshaft adjuster having a variable ratio gear unit
WO2011042391A1 (en) Camshaft arrangement
EP2294289A1 (en) Camshaft unit
DE102008039009A1 (en) Camshaft adjuster for adjusting phasing of camshaft or crankshaft of internal combustion engine, has pre-transmission gearbox and adjustment mechanism which is formed as triple-shaft gearbox
DE102010045258B4 (en) Device for phase shifting the angle of rotation of a drive wheel to a driven wheel
DE102011078818A1 (en) Cam shaft adjustment system for internal combustion engine, comprises outer camshaft, in which inner camshaft is arranged concentric to outer camshaft, and rotation changing element is directly or indirectly attached to cylinder head
DE102008020909B4 (en) Decompression device for an internal combustion engine
DE102015214623A1 (en) Camshaft adjusting device
DE102008050824A1 (en) Emergency brake for use in electromechanical adjusting device for camshaft of internal combustion engine, has brake disk or magnet housing moved between free-running and braking positions by magnetic force generated by energizing coil
DE102010039426A1 (en) Valve train for internal combustion piston engine, has locking element provided with ratchet tooth, which is projected axially above external periphery of brake rotor and engaged with recesses
DE10236894A1 (en) Valve timing control system for internal combustion engines
EP2486249A1 (en) Camshaft arrangement
DE102007003997A1 (en) Adjustment device for the axial adjustment of a camshaft by means of a Verstellaktuators
DE102018129673A1 (en) Actuating mechanism for a camshaft adjusting device for actuating a concentric camshaft arrangement
DE102015008196A1 (en) Camshaft adjuster with two-stage eccentric gear
DE102012203984A1 (en) Device i.e. camshaft adjuster, for displacing camshaft of internal combustion engine of motor car, has gearing tracks axially arranged at distance from each other by annular gap, and output ring gears rotatably inserted into annular gap
DE102004062038A1 (en) Device for changing the timing of an internal combustion engine
WO2007016986A1 (en) Adjusting device for an internal combustion engine, in particular a camshaft adjusting device
DE102005052966A1 (en) Adjusting device for adjusting of components in internal combustion engine, has gearbox unit which is formed as spur gear and spring element accelerates driving unit after exceeding breakover point
EP2966290B1 (en) Valve device for exhaust gas recirculation in a combustion engine
DE102004027636A1 (en) Control device for adjusting the angle of rotation of a camshaft

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: 20130128

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

DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502011004892

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F01L0001352000

Ipc: F01L0001344000

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/344 20060101AFI20140303BHEP

Ipc: F01L 1/352 20060101ALI20140303BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140520

INTG Intention to grant announced

Effective date: 20140526

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTC Intention to grant announced (deleted)
INTG Intention to grant announced

Effective date: 20140707

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): 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: 694773

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141115

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: 502011004892

Country of ref document: DE

Effective date: 20141218

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20141105

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: 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: 20141105

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: 20150305

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: 20141105

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: 20141105

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: 20150305

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: 20141105

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: 20150205

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: 20141105

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: 20150206

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: 20141105

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: 20141105

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: 20141105

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: 20141105

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: 20141105

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

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: 20141105

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: 20141105

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: 20141105

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: 20141105

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011004892

Country of ref document: DE

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: 20150806

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

Ref country code: DE

Payment date: 20150630

Year of fee payment: 5

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

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: 20141105

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: 20141105

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: 20141105

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: 20150707

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

Effective date: 20150707

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: LI

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

Effective date: 20150731

Ref country code: CH

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

Effective date: 20150731

Ref country code: GB

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

Effective date: 20150707

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160331

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: 20150731

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: 20141105

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: 20150707

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011004892

Country of ref document: DE

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: 20141105

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: 20170201

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: 20141105

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: 20141105

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: 20110707

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: 20150731

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 694773

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160707

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: 20160707

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: 20141105

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: 20141105

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: 20141105