EP1831507B1 - Mecanisme de commande de soupape variable de moteur a combustion interne - Google Patents

Mecanisme de commande de soupape variable de moteur a combustion interne Download PDF

Info

Publication number
EP1831507B1
EP1831507B1 EP05792392A EP05792392A EP1831507B1 EP 1831507 B1 EP1831507 B1 EP 1831507B1 EP 05792392 A EP05792392 A EP 05792392A EP 05792392 A EP05792392 A EP 05792392A EP 1831507 B1 EP1831507 B1 EP 1831507B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
internal combustion
stroke
hydraulic
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
EP05792392A
Other languages
German (de)
English (en)
Other versions
EP1831507A1 (fr
Inventor
Volker Schmidt
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP1831507A1 publication Critical patent/EP1831507A1/fr
Application granted granted Critical
Publication of EP1831507B1 publication Critical patent/EP1831507B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2107—Follower

Definitions

  • the invention relates to a variable valve train of an internal combustion engine for actuating a gas exchange valve. Its movement follows a stroke of a cam and a stroke of the cam superimposed on the stroke of the cam and independent of the stroke of the cam stroke of a piston of a hydraulic force application device.
  • This is connected to a hydraulic fluid line with adjustable hydraulic fluid pressure and has a piston acting on the pressure chamber and a hydraulic valve clearance compensation device with a radially limited by a housing work space.
  • the DE 43 18 293 A1 a hydraulic force application device on a finger lever drive with a pivot bearing, which supports a cam operated rocker arm in the direction of actuation of the gas exchange valve pivotally.
  • the hydraulic force application device expands the functionality of a hydraulic valve clearance compensation device by a hydraulic stroke, which is variably adjustable and is superimposed on the predetermined by the cam mechanical stroke on the gas exchange valve.
  • this superimposition reduces the gas exchange valve lift in terms of maximum lift and / or opening time to complete shutdown of the gas exchange valve possible.
  • by the superimposition of the hydraulic and the mechanical stroke also an extension of the stroke generated by the cam in terms of an earlier opening time or a later closing time or an increased maximum stroke or combinations of the like possible.
  • a substantially conventional pivot bearing with hydraulic valve clearance compensation which is familiar to the person skilled in the art.
  • This pivot bearing is guided longitudinally movable in an additional outer housing which is mounted in a recess of the internal combustion engine.
  • an underside of the pivot bearing together with an inner wall of the outer housing comprises a pressure chamber which is connected to a pressure-adjustable hydraulic medium line.
  • the present invention is therefore the object of a valvetrain of the type mentioned in such a way that the disadvantages are avoided.
  • the hydraulic force application device should therefore be characterized firstly by minimal space requirement and thus be used in modern space-constrained internal combustion engines.
  • their moving components should have the lowest possible mass in order to operate the gas exchange valve with the highest possible acceleration values.
  • the force application device should be able to be produced as inexpensively as possible with low complexity.
  • the housing also serves to radially limit the pressure chamber.
  • the hydraulic force application device is thus designed such that the working space of the hydraulic valve clearance compensation device and the pressure chamber are radially bounded by a common housing. This eliminates the need for a separate outer housing, the wall thickness would lead to a significant increase in diameter and length of the force application device. Their minimal space requirement thus enables an excellent adaptability of the valve train according to the invention in already existing internal combustion engines. At the same time, due to the low complexity of the hydraulic force application device, cost-effective manufacturability is given.
  • the mass of these moving components is low, so that good acceleration values can be achieved when the gas exchange valve is actuated.
  • the expense for generating the hydraulic drive power can be maintained at a low level in view of a good efficiency of the internal combustion engine.
  • a particularly advantageous embodiment of the valve train according to the invention provides according to claim 2 that the pressure chamber of the piston and a piston facing the first end face of a longitudinally movably guided in the housing compensating piston of the hydraulic valve clearance compensation device is axially limited.
  • the working space of the hydraulic valve lash adjuster is arranged separately from the pressure chamber and is axially delimited by a piston facing away from the second end face of the balance piston.
  • proven components of conventional high-volume technology can be used. For example, it is possible to continue to use the return spring of the hydraulic valve lash adjuster designed for the comparatively small stroke of the compensating piston.
  • the pressure chamber is identical to the working space of the hydraulic valve lash adjuster.
  • the piston can be used as a large-volume hydraulic fluid reservoir for supplying the working space of the hydraulic valve clearance compensation device.
  • it can be advantageous in terms of manufacturing technology to produce the piston in one piece together with the compensation piston.
  • the valve train should allow at least one secondary stroke of the gas exchange valve during a lift-free base circle phase of the cam according to claim 4. This results in advantageous ways to recirculate exhaust gas in high volumes and precisely adjustable dosage internally.
  • This form of exhaust gas recirculation is in particular the basis for operation of the internal combustion engine with homogeneous and self-igniting charge.
  • HCCl Homogeneous Charge Compression Ignition
  • combustion method is used both for self-ignited diesel internal combustion engines as well as externally ignited gasoline internal combustion engines, at least in part-load operation of the internal combustion engine mainly for the purpose of reducing emissions.
  • the combustion process is determined in the HCCl process essentially by controlling the charge composition and the charge temperature profile.
  • a high charge temperature for controlling the ignition timing is desired.
  • a very effective means for increasing the charge temperature is the increase of the residual gas content, ie the increase of the content of not flushed or purged and recirculated into the cylinder exhaust gas of the previous combustion cycle in the cylinder charge for the next combustion cycle.
  • the residual gas content on the operating point of the internal combustion engine must be fully variable, with residual gas quantities of 60% of the cylinder charge and more may be required. Residual gas components can no longer be provided at this altitude via internal exhaust gas recirculation through conventional valve overlap or via an arrangement for external exhaust gas recirculation.
  • the HCCl process with unacceptable combustion processes is extremely sensitive to changes in charge characteristics. so that in addition to the provision of residual gas in the required amount also a combustion cycle-faithful, high-precision and cylinder-specific dosing of the residual gas content is required.
  • the secondary stroke is carried out according to claim 5, preferably at an outlet valve.
  • exhaust gas which has already been ejected into the exhaust passage is sucked back into the combustion chamber via the then opened exhaust valve during the intake stroke of the internal combustion engine.
  • the valve gear according to the invention as an engine brake in particular in air-compressing internal combustion engines for safety-relevant supplementation of the service brake.
  • engine brakes are usually used as a continuous brake in commercial vehicles and are based on the principle that the drag torque of the combustion engine located in overrun and not fueled by increasing the charge exchange work can be significantly increased and the vehicle is slowed down.
  • the exhaust valve is opened again during the compression phase, so that the cylinder charge is not compressed like a gas spring, but is pushed into the outlet channel with the application of pushing work.
  • exhaust gas recirculation it may also be expedient, according to claim 6, for the secondary stroke to take place at an inlet valve.
  • exhaust gas is expelled in Ausschiebetakt the internal combustion engine with the intake valve again open in the inlet channel and sucked back into the combustion chamber during the intake stroke.
  • valve train A preferred embodiment of the valve train is proposed in claim 7, wherein the valve gear as a drag lever drive and the hydraulic force application device are designed as a pivot bearing.
  • the lubricating oil of the internal combustion engine is used according to claim 8 for the sake of simplicity.
  • any other suitable fluids in a hydraulic fluid circuit which would then be separated from the lubricating oil circuit of the internal combustion engine.
  • valve train 1 is disclosed using the example of a drag lever drive 2 with a pivot bearing 3a as part of a hydraulic force application device 4a.
  • a gas exchange valve 5 which is actuated via a drag lever 6 by a cam 7 in the opening direction.
  • the drag lever 6 is mounted on the pivot bearing 3a in the direction of actuation of the gas exchange valve 5 and has a rotatably mounted roller 8 as low-friction contact surface 9 to the cam 7.
  • the cam 7 has a cam elevation phase 10, which generates a stroke on the gas exchange valve 5, and a lift-free base circle phase 11th
  • a piston 14 with an outer circumferential surface 15 and a compensating piston 16 with an outer circumferential surface 17 are longitudinally movably guided.
  • a first end portion 18 of the piston 14 faces a first end face 19 of the balance piston 16, while a second end portion 20 of the piston 14 is designed to be spherical for the pivotable mounting of the finger lever 6.
  • a second, the piston 14 facing away from end 21 of the balance piston 16 defines a working space 22a of a hydraulic valve clearance compensation device 23a.
  • the piston 14 is spaced from the first end face 19 of the compensating piston 16 and defines together with this a volume-variable pressure chamber 24a of the hydraulic force application device 4a.
  • the lash adjuster 23a communicates with a hydraulic mast supply "S-LA".
  • the compensating piston 16 is expediently designed as a hollow body 25 in order to separate the pressure chamber 24a from the working chamber 22a of the valve lash adjuster 23a and at the same time to create a hydraulic medium reservoir 26 for the working chamber 22a.
  • the pressure chamber 24a is connected via at least one passage opening 27 in the housing 13a with a hydraulic medium line "SP" whose hydraulic fluid pressure is adjustable.
  • SP hydraulic medium line
  • FIG. 1 assumes the pivot bearing 3a at low hydraulic fluid pressure in the hydraulic medium line "SP” a basic position "A", in which the piston 14 rests with its first end portion 18 on the first end face 19 of the balance piston 16.
  • the gas exchange valve 5 is closed, since at the same time the cam 7 rests with its base circle phase 11 on the roller 8.
  • the hydraulic force applying means 4a generates a stroke of the gas exchange valve 5 superposed on the stroke of the cam 7 by increasing the volume of the pressure space 24a by increasing the hydraulic medium pressure in the hydraulic medium line "SP".
  • the piston 14 is spaced from the balance piston 16 and actuates the drag lever 6 regardless of the stroke of the cam 7 in the opening direction of the gas exchange valve 5. This situation is in Fig. 2 for a stroke position "B" of the piston 14 is shown.
  • This passage 28 can be shown be formed as a recess 29, which interrupts a to the first end face 19 of the balance piston 16 is substantially parallel end face 30 of the first end portion 18 of the piston 14. It is alternatively or additionally also possible to connect the pressure chamber 24a via a passage opening into the outer circumferential surface 15 of the hollow-cylindrical piston 14 with a closed contour.
  • FIGS. 3 and 4 disclose a non-inventive valve train 1 with a pivot bearing 3b, which relative to the pivot bearing 3a of Figures 1 and 2 essentially differs by the merging of a working space 22b of a valve play compensation device 23b with a pressure chamber 24b of a hydraulic force application device 4b.
  • the following explanations are therefore limited to the representation of the essential feature differences between the two embodiments.
  • FIG. 3 the pivot bearing 3b is shown in a basic position "C".
  • the basic position "C” corresponds to a mounting position of the hydraulic valve clearance compensation device 23b, wherein an end face 31 of a piston 32 facing away from the drag lever 6 is slightly spaced from a shoulder 33 of a housing 13b.
  • the piston 32 serves for the axial delimitation of the working space 22b, which is identical to the pressure space 24b.
  • the working space 22b for the purpose of volume change of the pressure chamber 24b via a passage opening 27 in the housing 14b with the hydraulic medium line "SP" is connected.
  • the piston 32 is in the FIGS. 3 and 4 shown as a one-piece piston 32, which also serves for the pivotable mounting of the finger lever 6. Equally, however, the use of a multi-part piston is possible, with an upper part of the drag lever 6 superimposed and a lower part for limiting the working space 22b common pressure chamber 24b is used.
  • FIG. 4 is the pivot bearing 3b at a stroke position "D" with significantly increased distance of the end face 31 of the piston 32 to the shoulder 33 of the housing 13b shown.
  • the hydraulic medium line “SP” is again operated as a drain line.
  • the hydraulic fluid line “SP” is to be closed at the pivot bearing 3b at the latest when the cam elevation phase 11 engages with the roller 8 in order to maintain the function of the valve lash adjuster 23b.
  • valve lash adjuster 23b can finally take place in a known manner via a check valve 34, which connects the hydraulic medium line "S-P" independent hydraulic fluid supply "S-LA” with the working space 22b.
  • valve train 1 has been explained using the example of a finger lever valve drive 2 as a preferred embodiment.
  • the idea of the invention can equally be implemented in other types of valve trains, such as cup drives or pushrod drives.
  • the scope of the invention should also include valve trains, which are designed switchable by coupling means to selectively transfer strokes of several cams depending on the coupling state to the gas exchange valve 6. This applies equally to valve trains that continuously vary the stroke of the gas exchange valve 6 by means of a cam and other adjusting elements.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (8)

  1. Commande de soupape variable (1) d'un moteur à combustion interne pour l'actionnement d'une soupape d'échange de gaz (5), dont le mouvement suit une course d'une came (7) ainsi qu'une course d'un piston (14, 32) d'un dispositif hydraulique d'application de force (4a, 4b) superposée à la course de la came (7) et indépendante de la course de la came (7), le dispositif d'application de force étant connecté à une conduite de fluide hydraulique (S-P) à pression de fluide hydraulique ajustable, et présentant un espace de pression (24a, 24b) qui alimente le piston (14, 32) au moins de manière indirecte ainsi qu'un dispositif hydraulique de compensation du jeu de soupape (23a, 23b) avec un espace de travail (22a, 22b) limité radialement par un boîtier (13a, 13b), caractérisée en ce que le boîtier (13a, 13b) sert simultanément à limiter radialement l'espace de pression (24a, 24b).
  2. Commande de soupape selon la revendication 1, caractérisée en ce que l'espace de pression (24a) est limité axialement par le piston (14) et un premier côté frontal (19) tourné vers le piston (14) d'un piston de compensation (16) du dispositif de compensation du jeu de soupape (23a) guidé de manière déplaçable longitudinalement dans le boîtier (13a), un deuxième côté frontal (21) du piston de compensation (16), opposé au piston (14), limitant axialement l'espace de travail (22a) du dispositif de compensation du jeu de soupape (23a), séparé de l'espace de pression (24a) .
  3. Commande de soupape selon la revendication 2, caractérisée en ce que le piston de compensation (16) est réalisé sous forme de corps creux (25).
  4. Commande de soupape selon la revendication 1, caractérisée en ce que la soupape d'échange de gaz (5) effectue au moins une course secondaire pendant une phase de cercle de base (11) de la came (7) .
  5. Commande de soupape selon la revendication 4, caractérisée en ce que la soupape d'échange de gaz (5) est une soupape d'échappement du moteur à combustion interne.
  6. Commande de soupape selon la revendication 4, caractérisée en ce que la soupape d'échange de gaz (5) est une soupape d'admission du moteur à combustion interne.
  7. Commande de soupape selon la revendication 1, caractérisée en ce que la commande de soupape (1) est réalisée sous forme de commande à culbuteur (2) et le dispositif d'application de force (4a, 4b) est réalisé sous forme de palier pivotant (3a, 3b), le boîtier (13a, 13b) étant monté dans un évidement cylindrique creux du moteur à combustion interne.
  8. Commande de soupape selon la revendication 1, caractérisée en ce que l'agent hydraulique est de l'huile de lubrification du moteur à combustion interne.
EP05792392A 2004-11-04 2005-10-12 Mecanisme de commande de soupape variable de moteur a combustion interne Expired - Fee Related EP1831507B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004053203A DE102004053203A1 (de) 2004-11-04 2004-11-04 Variabler Ventiltrieb einer Brennkraftmaschine
PCT/EP2005/010943 WO2006048100A1 (fr) 2004-11-04 2005-10-12 Mecanisme de commande de soupape variable de moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1831507A1 EP1831507A1 (fr) 2007-09-12
EP1831507B1 true EP1831507B1 (fr) 2013-01-02

Family

ID=35482160

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05792392A Expired - Fee Related EP1831507B1 (fr) 2004-11-04 2005-10-12 Mecanisme de commande de soupape variable de moteur a combustion interne

Country Status (4)

Country Link
US (1) US7568460B2 (fr)
EP (1) EP1831507B1 (fr)
DE (1) DE102004053203A1 (fr)
WO (1) WO2006048100A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010018208A1 (de) * 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hydraulisches Ventilspiel-Ausgleichselement für Hubkolbenbrennkraftmaschinen
DE102011101239A1 (de) * 2011-05-11 2012-11-15 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Hydrostößel mit einer zweiten Ölzuführung zur
FI20135003L (fi) * 2013-01-03 2014-07-04 Waertsilae Finland Oy Pakoventtiilijärjestely ja menetelmä pakoventtiilin sulkeutumisen kontrolloimiseksi

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3385274A (en) 1967-07-13 1968-05-28 Gen Motors Corp Variable stroke hydraulic valve lifter
US3439661A (en) 1968-01-11 1969-04-22 Michael A Weiler Controlled displacement hydraulic lifter
US4350129A (en) * 1976-10-01 1982-09-21 Nissan Motor Company, Limited Spark-ignition internal combustion engine capable of preventing noxious gas emissions
US4502425A (en) * 1981-01-20 1985-03-05 Marlene A. Wride Variable lift cam follower
JPS63297710A (ja) 1987-05-29 1988-12-05 Isuzu Motors Ltd バルブラツシユアジヤスタ−
DE4000531A1 (de) 1990-01-10 1990-06-13 Roland Schmidt Verstellvorrichtung zur veraenderung von ventilsteuerzeiten und ventilhub
DE4102537A1 (de) * 1991-01-29 1992-07-30 Man Nutzfahrzeuge Ag Auslass-ventilstoessel fuer eine brennkraftmaschine
US5451029A (en) * 1992-06-05 1995-09-19 Volkswagen Ag Variable valve control arrangement
DE4317607A1 (de) 1992-06-05 1993-12-09 Volkswagen Ag Variabler Ventiltrieb für ein Hubventil
DE4318293A1 (de) 1992-06-13 1993-12-16 Volkswagen Ag Schlepphebel-Ventiltrieb für ein Hubventil
ES2116123T3 (es) * 1995-04-04 1998-07-01 Steyr Nutzfahrzeuge Procedimiento para el frenado por motor con un motor de combustion interna de cuatro tiempos.

Also Published As

Publication number Publication date
EP1831507A1 (fr) 2007-09-12
US20080115749A1 (en) 2008-05-22
DE102004053203A1 (de) 2006-06-01
WO2006048100A1 (fr) 2006-05-11
US7568460B2 (en) 2009-08-04

Similar Documents

Publication Publication Date Title
EP1807609B1 (fr) Mecanisme de commande de soupape de moteur a combustion interne
DE112004001450B4 (de) Vorrichtung für eine Brennkraftmaschine
DE102010037567B4 (de) Elektrohydraulische variable Ventilhub-Vorrichtung
DE102005040649A1 (de) Variabler Ventiltrieb einer Brennkraftmaschine
EP1662098B1 (fr) Commande de soupape variable de moteur à combustion interne
EP3418513B1 (fr) Dispositif de transmission de force
EP1831507B1 (fr) Mecanisme de commande de soupape variable de moteur a combustion interne
WO2006037422A1 (fr) Commande de soupape variable pour un moteur a combustion interne
EP3401517B1 (fr) Levier moteur de soupape
DE102006048549A1 (de) Hydraulisches Ventilspielausgleichselement mit Leerhubfunktion für einen Ventiltrieb eines Verbrennungsmotors
DE60310743T2 (de) Vorrichtung zum ventilausschalten einer brennkraftmaschine
DE3923371C1 (en) IC engine valve control system - can adjust exhaust valve lift to give throttle effect during engine braking
DE4202506A1 (de) Variabler ventiltrieb fuer ein hubventil
WO2015074652A1 (fr) Mécanisme de commande de soupape hydraulique d'un moteur à combustion interne
DE4124184A1 (de) Hydraulischer tassenstoessel
DE102015213627B3 (de) Hydraulikelement mit Motorbremsfunktion für eine Viertakthubkolbenbrennkraftmaschine und Viertakthubkolbenbrennkraftmaschine
WO2014037130A1 (fr) Commande de soupapes pour un moteur à combustion interne
EP1607587A2 (fr) Came de commande de soupape pour moteur à combustion interne
EP3536917B1 (fr) Mécanisme de soupapes variable pourvu de système de cames coulissantes pour un moteur à combustion interne
WO2006037408A1 (fr) Mecanisme de distribution variable de moteur a combustion interne
WO2008116703A1 (fr) Mécanisme de distribution d'un moteur à combustion interne
DE10205888B4 (de) Hydraulische Ventilbetätigungsvorrichtung
DE112005002543B4 (de) Brennkraftmaschine und ein Verfahren zum Betreiben einer Brennkraftmaschine
DE102022117873B3 (de) Ventilanordnung für einen Ventiltrieb einer Brennkraftmaschine
DE4334006C2 (de) Vorrichtung zur Erhöhung der Motorbremsleistung einer 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: 20070419

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

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

Designated state(s): DE FR GB IT SE

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

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

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 SE

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: DE

Ref legal event code: R096

Ref document number: 502005013391

Country of ref document: DE

Effective date: 20130314

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: 20130102

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: 20131003

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: 20130102

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502005013391

Country of ref document: DE

Effective date: 20131003

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013391

Country of ref document: DE

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

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

Effective date: 20140213

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013391

Country of ref document: DE

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

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20130103

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013391

Country of ref document: DE

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

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

Effective date: 20140213

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013391

Country of ref document: DE

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

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20130103

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

Effective date: 20131012

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

Ref country code: GB

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

Effective date: 20131012

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013391

Country of ref document: DE

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

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

Effective date: 20150126

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

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: FR

Payment date: 20161027

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: 20170102

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005013391

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180629

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

Ref country code: DE

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

Effective date: 20180501

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

Ref country code: FR

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

Effective date: 20171031

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

Effective date: 20230522