EP1588027B1 - Culbuteur d'entrainement hydraulique - Google Patents

Culbuteur d'entrainement hydraulique Download PDF

Info

Publication number
EP1588027B1
EP1588027B1 EP03780118A EP03780118A EP1588027B1 EP 1588027 B1 EP1588027 B1 EP 1588027B1 EP 03780118 A EP03780118 A EP 03780118A EP 03780118 A EP03780118 A EP 03780118A EP 1588027 B1 EP1588027 B1 EP 1588027B1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
control
cam
valve
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP03780118A
Other languages
German (de)
English (en)
Other versions
EP1588027A1 (fr
Inventor
Rainer Albat
Uwe Meyer
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.)
Mercedes Benz Group AG
Original Assignee
Daimler 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 Daimler AG filed Critical Daimler AG
Publication of EP1588027A1 publication Critical patent/EP1588027A1/fr
Application granted granted Critical
Publication of EP1588027B1 publication Critical patent/EP1588027B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • 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
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the invention relates to a valve drive for piston internal combustion engines with at least one control cam, an additional cam, a first rocker arm and a second rocker arm, which are pivotally mounted on a rocker shaft, wherein the first rocker arm is in operative contact with at least a first cylinder valve, at least the Additional cam is in operative contact with the second rocker arm and the second rocker arm via an actuating element with the first rocker arm in force flow can be brought.
  • a rocker cam assembly with a first control cam and a second control cam is shown on page 12.
  • the control cams are in each case operatively connected to a cylinder valve via a rocker arm which is mounted pivotably on a rocker arm shaft.
  • An additional control cam is assigned a further rocker arm, which has a controlling actuator is positively connected to the rocker arms. The actuator is moved axially to the rocker shaft.
  • the invention has for its object to form a valve drive and arrange such that a flexible control of a motor valve is guaranteed.
  • control cam is in operative contact with the second rocker arm. This ensures that only the second rocker arm with the control cam and the auxiliary cam or with the timing gear is to bring into operative contact.
  • the control cam and the additional cam are in this case arranged on a common cam track, whereby a total of the control drive is structurally simplified.
  • Active contact means that in addition to a possible lubricant film and / or a clearance compensation element there is a direct contact between the respective transmission parts.
  • a brake system based on the valve drive according to the invention can also be implemented in newer engine designs. A constant throttle is no longer necessary. In addition to the simple design of the space is optimally utilized.
  • the valve drive according to the invention can also be used with the camshafts lying below and on top.
  • the actuating element has a locking direction, which corresponds to the direction of a locking force acting between the first rocker arm and the second rocker arm and the locking direction is arranged with respect to a center axis of the rocker shaft perpendicular and spaced therefrom. Due to the distance of the locking direction or the blocking force to the central axis of the rocker shaft, a lever can be realized, which can be optimally designed according to the applied control forces.
  • the adjustment of the Adjusting element are proportional to the distance to the central axis and thus with the distance to the central axis also changeable.
  • the adjusting element is designed as a movable piston and connected to a control line and a control valve for pressure medium.
  • the formation of the actuating element as a hydraulically actuated piston ensures a simple and wear-free control.
  • control line has a check valve, which is associated with a bypass line.
  • a check valve which is associated with a bypass line.
  • the piston is movably arranged within a pressure medium cylinder connected to the control line and with a first end face against the first rocker arm can be applied directly or indirectly.
  • the control valve When the control valve is closed, a relative movement between the piston and the pressure medium cylinder is prevented, so that the adjusting movement of the second rocker arm is at least partially transmitted to the first rocker arm.
  • the control valve When the control valve is open, the pressure fluid volume of the pressure cylinder is reduced and the second rocker arm performs until the closing of the control valve a free travel, in which the first rocker arm stops in its rest position.
  • the piston within the pressure medium cylinder is associated with the pressure force of the pressure medium counteracting return element.
  • first rocker arm is pivotally mounted on the rocker arm shaft or on the second rocker arm.
  • the check valve is associated with a bypass line, not shown, is sucked via the pressure medium. It is also advantageous that the first rocker arm, the actuating element and the second rocker arm form a structural unit.
  • either the control cam is in operative contact with the first rocker arm and the additional cam only with the second rocker arm.
  • the additional cam could be used in case of need by activating the actuator. This can be a motor-saving operation or high-power engine operation be realized, which in addition to the usual shape of the control cam needs a modified form of control cam.
  • the valve actuator 1 essentially has a first rocker arm 2.1 and a second rocker arm 2.2, which are pivotally mounted on a rocker shaft 2.
  • the first rocker arm 2.1 is associated with a first cylinder valve 3.1 and a second cylinder valve 3.2, which are actuated at a pivoting movement of the first rocker arm 2.1 to the rocker arm shaft 2 and the center axis 2.3.
  • the first rocker arm 2.1 and the second rocker arm 2.2 are in this case arranged with respect to the central axis 2.3 of the rocker shaft 2 in succession and mechanically coupled via a control element 5 designed as a piston.
  • the piston 5 is here mounted displaceably within a pressure medium cylinder 9 of the second rocker arm 2.2.
  • the pressure medium cylinder 9 is connected via a control line 6 with a control valve 7 and a check valve 8 in operative connection.
  • the actuating piston 5 is located with its pressure medium cylinder 9 opposite end face 5.1 against a stop surface 5.2 of the second rocker arm 2.2 or is against this applied.
  • FIG. 1 would be with a closed control valve 7, an actuation of the second rocker arm 2.2 by a plunger 11 according to FIG. 2 lead up to a driving or a corresponding pivoting movement of the first rocker arm 2.1.
  • the pressure medium located in the pressure medium cylinder 9 could flow neither via the check valve 8 nor via the closed control valve 7, so that the holding position of the actuating piston 5 in accordance FIG. 1 is guaranteed.
  • a return element 10 is arranged between the actuating piston 5 and the second rocker arm 2.2.
  • the resetting element 10 designed as a spring element ensures a return movement of the adjusting piston within the pressure medium cylinder 9 when the control valve 7 is open.
  • the control cam 4.1 and two additional cams 4.2, 4.3 or auxiliary cams are actuated by the plunger 11 or a cam FIG. 2 generated pivotal movement of the second rocker arm 2.2 is transmitted via the control piston 5 with the control valve 7 closed to the first rocker arm 2.1 and thus to the first cylinder valve 3.1 and the second cylinder valve 3.2.
  • the control valve 7 Only a part of the pivoting movement executed by the second rocker arm 2.2 can thus be transmitted to the first rocker arm 2.1.
  • control valve 7 could be opened after passing through the pivoting passage, generated by the control cam 4.1, so that the pivoting movement generated by the auxiliary cam 4.2 and / or the auxiliary cam 4.3 only from the second Rocker arm 2.2 is executed and the first rocker arm 2.1 remains unactuated.
  • the control cam 4.1 and the auxiliary cam 4.2, 4.3 according to FIG. 2 are arranged on a cam track, ie they together form a cam.
  • the lifting movement generated by the cam or plunger 11 is transmitted via the second rocker arm 2.2 and the control piston 5 to the first rocker arm 2.1 and thus to the cylinder valve 3.2.
  • the arranged within the pressure cylinder 9 actuating piston 5 in this case is applied to the stop surface 5.2 of the first rocker arm 2.1 and takes it with the control valve 7 closed.
  • the control line 6 is in this case at least partially disposed within the rocker shaft 2 and leads from this to the control valve 7 and the check valve eighth
  • FIG. 3 illustrated schematic diagram of the power flow between the individual drive links shows the control cam 4.1, the auxiliary cam 4.2, 4.3, the first rocker arm 2.1, the second rocker arm 2.2, the control piston 5 and the cylinder valves 3.1, 3.2.
  • the connecting lines between the individual drive links represent the realizable form-locking connections.
  • the control cam 4.1 and the auxiliary cams 4.2, 4.3 are in operative contact with the second rocker arm 2.2 directly.
  • the second rocker arm 2.2 is in operative contact with the pressure medium cylinder 9 and the pressure medium cylinder 9 via the control piston 5 with the first rocker arm 2.1.
  • the first rocker arm 2.1 in turn is in direct contact with the cylinder valves 3.1, 3.2 in operative contact or in force.
  • control cam is 4.1 directly to the first rocker arm 2.1 and this with the Cylinder valves 3.1, 3.2 in operative contact. Only the auxiliary cams 4.2, 4.3 are via the second rocker arm 2.2, the pressure medium cylinder 9, the control piston 5 and the first rocker arm 2.1 with the cylinder valves 3.1, 3.2 in operative contact.

Abstract

L'invention concerne un entraînement de soupapes (1) destiné à des moteurs à combustion interne à pistons. Selon l'invention, un premier culbuteur (2.1) se trouve en contact actif avec au moins une première soupape de cylindre (3.1), au moins une came supplémentaire (4.2) se trouve en contact actif avec un deuxième culbuteur (2.2), et le deuxième culbuteur (2.2) peut être amené en liaison de force avec le premier culbuteur (2.1) par l'intermédiaire d'un actionneur (5). La came de commande (4.1) se trouve en contact actif avec le deuxième culbuteur (2.2), et le premier culbuteur (2.1) peut être amené au moins partiellement en marche synchrone, par rapport à l'angle vide (α), avec le deuxième culbuteur (2.2), par l'intermédiaire de l'actionneur (5).

Claims (10)

  1. Entraînement de soupapes (1) destiné à des moteurs à combustion interne à pistons avec au moins une came dé commande (4.1), une came supplémentaire (4.2), un premier culbuteur (2.1) et un second culbuteur ( (2.2) qui sont disposés sur une arbre de culbuteur (2) de façon tourner, le premier culbuteur (2.1) se trouve en contact actif avec au moins une première soupape de cylindre (3.1), vau moins la came supplémentaire (4.2) se trouve en contact actif avec le deuxième culbuteur (2,2), et le deuxième culbuteur (2.2) peut être amené en liaison de force avec le premier culbuteur (2.1) par l'intermédiaire d'un actionneur (5), caractérisé en ce que la came de commande (4.1) se trouve en contact actif avec le deuxième culbuteur (22).
  2. Dispositif selon la revendication 1, caractérisé en ce que l'actionneur (5) présente un sens de blocage qui correspond au sens d'une force de blocage agissant entre le premier culbuteur (2.1) et le second culbuteur (2.2) et le sens de blocage est placé par rapport une ligne médiane (2.3) de l'arbre de culbuteur (2) perpendiculairement et à distance de celle-ci.
  3. Dispositif selon la revendication 1, caractérisé en ce qu'il est prévu entre le premier culbuteur (2.1) et le second culbuteur (2.2) un angle vide α qui peut être régie par l'actionneur (5) par rapport à un mouvement de bascule sur l'arbre de culbuteur (2).
  4. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur (5) est formé en tant que piston mobile et relié à un câble-pilote (6) et à une vanne de commande (7) pour un fluide sous pression.
  5. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que le câble-pilote (6) présente un clapet anti-retour (8) qui est associés à une conduite de dérivation.
  6. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que le pison (5) est dispose de manière à pourvoir se déplacer à l'intérieur d'un vérin (9) à fluide sous pression relié au câble-pilote et qui peut être appliqué directement ou indirectement contre le premier culbuteur (2.1).
  7. Dispositif salon l'une quelconque des revendications précédentes, caractérisé en ce que le piston (5) est associé à l'intérieur du vérin (9) à fluide sous pression à un élément de rappel (10) agissant contre la pression du fluide sous pression.
  8. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier culbuteur (2.1) est monté pivotant sur l'arbre (2) de culbuteur ou sur le second culbuter (2.2).
  9. Dispositif selon l'une quiconque des revendications précédentes, caractérisé en ce que le premier culbuteur (2.1), l'actionneur (5) et le second culbuteur (2.2) forment une unité modulaire.
  10. Dispositif selon l'une quelconque des revendications précédentes, caractérisé en ce que la came de commande (4.1) se trouve éventuellement en contact actif avec le premier culbuteur (2.1) et la came supplémentaire (4.2) se trouve en contact actif uniquement avec le second culbuteur (2.1).
EP03780118A 2003-01-30 2003-12-04 Culbuteur d'entrainement hydraulique Expired - Fee Related EP1588027B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10303567 2003-01-30
DE10303567A DE10303567A1 (de) 2003-01-30 2003-01-30 Hydraulischer Mitnehmerkipphebel
PCT/EP2003/013687 WO2004067923A1 (fr) 2003-01-30 2003-12-04 Culbuteur d'entrainement hydraulique

Publications (2)

Publication Number Publication Date
EP1588027A1 EP1588027A1 (fr) 2005-10-26
EP1588027B1 true EP1588027B1 (fr) 2010-09-01

Family

ID=32695032

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03780118A Expired - Fee Related EP1588027B1 (fr) 2003-01-30 2003-12-04 Culbuteur d'entrainement hydraulique

Country Status (5)

Country Link
US (1) US7182054B2 (fr)
EP (1) EP1588027B1 (fr)
JP (1) JP4672372B2 (fr)
DE (2) DE10303567A1 (fr)
WO (1) WO2004067923A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017118852A1 (de) 2017-08-18 2019-02-21 Man Truck & Bus Ag Kraftübertragungsvorrichtung für variablen Ventiltrieb

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006002145A1 (de) * 2006-01-17 2007-07-19 Daimlerchrysler Ag Gaswechselventilbetätigungsvorrichtung
JP4931621B2 (ja) * 2007-01-29 2012-05-16 株式会社オティックス 内燃機関の可変動弁機構
AT505832B1 (de) * 2008-09-18 2011-01-15 Avl List Gmbh Motorbremseinrichtung für eine brennkraftmaschine
CN102733884B (zh) * 2011-03-30 2016-02-03 奚勇 一种集成式的发动机制动装置
DE102013006304A1 (de) * 2013-04-12 2014-10-16 Man Diesel & Turbo Se Ventiltrieb für eine Brennkraftmaschine und Brennkraftmaschine
CN106930798B (zh) * 2017-03-20 2019-08-16 上海尤顺汽车部件有限公司 驱动发动机制动器的正时控油方法和机构

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3332405A (en) 1965-10-01 1967-07-25 Jacobs Mfg Co Internal combustion engine brake
US4690110A (en) * 1985-04-26 1987-09-01 Mazda Motor Corporation Variable valve mechanism for internal combustion engines
JPS61175206A (ja) * 1985-07-23 1986-08-06 Mazda Motor Corp エンジンの弁作動装置
JP2639471B2 (ja) * 1989-03-24 1997-08-13 フジオーゼックス株式会社 内燃機関用弁のリフト調節装置
JPH03271511A (ja) * 1990-03-22 1991-12-03 Fuji Heavy Ind Ltd 可変バルブタイミング式動弁装置
DE4025569C1 (en) * 1990-08-11 1991-07-18 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De Valve brake for vehicle IC engine - has separately controllable cylinder outlet valves for drive and braking functions
JPH062518A (ja) * 1992-06-15 1994-01-11 Otix:Kk 内燃機関の動弁装置
JPH0633713A (ja) * 1992-07-17 1994-02-08 Mitsubishi Motors Corp 可変バルブタイミング機構付き動弁系構造
JPH07189633A (ja) * 1993-12-27 1995-07-28 Nissan Motor Co Ltd 内燃機関の可変動弁装置
JP3319920B2 (ja) * 1995-10-12 2002-09-03 株式会社ユニシアジェックス エンジンの弁作動装置
JPH09112234A (ja) * 1995-10-20 1997-04-28 Hino Motors Ltd エンジンのバルブメカニズム
US5651336A (en) * 1995-12-26 1997-07-29 Chrysler Corporation Variable valve timing and lift mechanism
JPH10103034A (ja) * 1996-09-24 1998-04-21 Toyota Motor Corp 内燃機関のオイル供給装置
DE19729198A1 (de) * 1997-07-09 1999-01-14 Deutz Ag Bremsvorrichtung für eine ventilgesteuerte Brennkraftmaschine
JP3764595B2 (ja) * 1998-12-24 2006-04-12 株式会社日立製作所 エンジン補助ブレーキ装置
JP2001132423A (ja) * 1999-11-04 2001-05-15 Hino Motors Ltd バルブタイミング可変装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017118852A1 (de) 2017-08-18 2019-02-21 Man Truck & Bus Ag Kraftübertragungsvorrichtung für variablen Ventiltrieb
US10895175B2 (en) 2017-08-18 2021-01-19 Man Truck & Bus Ag Force transmission device for variable valve drive
EP3892831A1 (fr) 2017-08-18 2021-10-13 MAN Truck & Bus SE Dispositif de transmission de force pour un mécanisme de distribution variable

Also Published As

Publication number Publication date
JP4672372B2 (ja) 2011-04-20
DE50313053D1 (de) 2010-10-14
US7182054B2 (en) 2007-02-27
DE10303567A1 (de) 2004-08-12
WO2004067923A1 (fr) 2004-08-12
EP1588027A1 (fr) 2005-10-26
US20050252466A1 (en) 2005-11-17
JP2006514192A (ja) 2006-04-27

Similar Documents

Publication Publication Date Title
EP0736672B1 (fr) Procédé de freinage moteur pour moteur à combustion interne à quatre temps
EP2625395B1 (fr) Moteur à combustion interne à quatre temps présentant un frein moteur
DE10047141B4 (de) Vorrichtung für einen Zweitaktkompressionsmotorbremsbetrieb bei einem Viertaktmotor und Verfahren zur Durchführung eines solchen Betriebes
WO1997021910A1 (fr) Dispositif d'actionnement de soupapes d'un moteur a piston avec levee de soupape variable, notamment d'un moteur a combustion interne a piston
DE19908286A1 (de) Variable Ventilsteuerung für Brennkraftmaschinen
EP3444451A1 (fr) Dispositif de transfert d'énergie pour un mécanisme de distribution
EP0733783B1 (fr) Ensemble de culbuteur pour actionnement d'une soupape
EP1588027B1 (fr) Culbuteur d'entrainement hydraulique
DE102008059207A1 (de) Nockenfolger zur Betätigung eines Gaswechselventils einer Brennkraftmaschine
DE4405189A1 (de) Stößel für ein schaltbares Ventil einer Brennkraftmaschine
EP3418513A1 (fr) Dispositif de transmission de force
WO1999056008A1 (fr) Element d'appui pour un basculeur d'un mecanisme de distribution d'un moteur a combustion interne
DE102007050818A1 (de) Brennkraftmaschine
DE10145622B4 (de) Ventil zum Steuern von Flüssigkeiten
AT519812B1 (de) Mechanische Ventilbetätigungsvorrichtung
EP1493902A1 (fr) Dispositif pour désactiver une soupape
DE4202506A1 (de) Variabler ventiltrieb fuer ein hubventil
DE19623257A1 (de) Einrichtung zur Betätigung von Ventilen an einer Kolbenmaschine mit veränderbarem Ventilhub, insbesondere einer Kolbenbrennkraftmaschine
EP1619362A2 (fr) Distribution de moteur à combustion
DE102017205814A1 (de) Mechanische Ventilbetätigungsvorrichtung
DE102007008790A1 (de) Variable Ventilhubvorrichtung
DE102013113815A1 (de) Übertragungsanordnung für einen mechanisch steuerbaren Ventiltrieb
DE19758372C2 (de) Druckmittelversorgung für ein Motorbremssystem eines mehrzylindrischen 4-Takt-Hubkolbenverbrennungsmotors
DE112005002543B4 (de) Brennkraftmaschine und ein Verfahren zum Betreiben einer Brennkraftmaschine
AT6651U1 (de) Variable ventiltriebsvorrichtung für eine brennkraftmaschine

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: 20050625

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

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

Owner name: DAIMLERCHRYSLER AG

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

Owner name: DAIMLER AG

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50313053

Country of ref document: DE

Date of ref document: 20101014

Kind code of ref document: P

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: 20100901

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: 20110606

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 50313053

Country of ref document: DE

Effective date: 20110606

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

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

Ref country code: DE

Payment date: 20150227

Year of fee payment: 12

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

Ref country code: GB

Payment date: 20150331

Year of fee payment: 12

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

Ref country code: FR

Payment date: 20150331

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50313053

Country of ref document: DE

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

Effective date: 20151204

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160831

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: 20160701

Ref country code: GB

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

Effective date: 20151204

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: 20151231