EP2722498A1 - Dispositif d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape - Google Patents

Dispositif d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape Download PDF

Info

Publication number
EP2722498A1
EP2722498A1 EP13003193.3A EP13003193A EP2722498A1 EP 2722498 A1 EP2722498 A1 EP 2722498A1 EP 13003193 A EP13003193 A EP 13003193A EP 2722498 A1 EP2722498 A1 EP 2722498A1
Authority
EP
European Patent Office
Prior art keywords
valve
hva
piston
exhaust
cylinder unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13003193.3A
Other languages
German (de)
English (en)
Other versions
EP2722498B1 (fr
Inventor
Heribert Möller
Rainer Kalass
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.)
MAN Truck and Bus SE
Original Assignee
MAN Truck and Bus SE
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 MAN Truck and Bus SE filed Critical MAN Truck and Bus SE
Publication of EP2722498A1 publication Critical patent/EP2722498A1/fr
Application granted granted Critical
Publication of EP2722498B1 publication Critical patent/EP2722498B1/fr
Active 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • 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

Definitions

  • the present invention relates to a device for actuating at least one exhaust valve of a valve-controlled internal combustion engine for motor vehicles according to the preamble of patent claim 1.
  • the object of the invention is to develop the generic device with structurally simple means such that both in regular operation and in engine braking operation or EVB a functionally reliable and trouble-free valve train can be achieved.
  • At least one means be provided between the driving cam of the valve drive and the at least one outlet valve, which counteracts one of the adjusting action of the HVA but exerts a smaller force in this respect.
  • valve-drive-side means is in particular a means to understand that directly or indirectly influences the movement of the valve train and / or at least temporarily enters into operative connection with the valve train.
  • Another positive effect of one of the adjusting action of the HVA counteracting or counteracting agent is that it is reduced in a compression of the HVA or the HVA agent, the entire compression distance in the fired operation. With this reduced compression travel, movement is reduced, which in turn reduces friction losses.
  • the lower force of the at least one means which counteracts the adjustment effect of the HVA, is to be understood as force at a location, for example at the location of the agent, and follows in particular from a force comparison of the force of the at least one agent with the, possibly due to leverage, resulting force of the HVA at the location of the at least one agent.
  • the means applying a lower, opposing force than the adjusting action of the HVA may more preferably comprise at least one magnet, for example a permanent magnet or an electromagnet, and / or at least one spring element, e.g. a leg spring, and / or at least one rubbery elastic element, e.g. a drawstring, be, the structurally and manufacturing technology easily executed and mounting technology can be conveniently arranged or can.
  • the means for applying the counteracting force of the HVA lower, opposing force applying means may e.g.
  • Such a means can thus be both a permanently acting biasing element and a temporarily acting biasing element.
  • this means for example, acts as a function of the speed limited in time. This could be effected, for example, by means of an electromagnet, which is then activated at specific times.
  • a magnet may further be provided that not only the attractive forces of a magnet are exploited, but alternatively or optionally additionally the repulsive force of several magnets is utilized, which in each case of the specific local arrangement of Magnets depends.
  • the repulsive force of several, in particular two magnets this can be arranged on the actuator-valve bridge contact point, whereby the magnets not only the second piston-cylinder unit, but also the weight or mass inertia of the preferably designed as a rocker arm actuator counteract.
  • attracting magnets can be used, which are each assigned to the adjacent and / or cooperating components.
  • Such a magnet can basically be made of any suitable material or material.
  • a particular advantage is the production of the magnet made of neodymium.
  • Such a neodymium magnet has the advantage that its magnetic properties can be activated only after manufacture or assembly, so that, for example, chip accumulation on the magnet during manufacture or assembly can be advantageously avoided.
  • opposing force applying means which is preferably formed by a magnet
  • a sacrificial magnet in particular metallic impurities, such as. a metal abrasion, etc., can accumulate, so that these impurities are not accumulated on the agent itself or in its vicinity.
  • metallic impurities such as. a metal abrasion, etc.
  • This can alternatively or additionally but also by a corresponding surface geometry, for example, a container-like collecting and receiving bead, etc. realized or implemented.
  • the actuating element may be a two-armed rocker arm, at the lever acting on the exhaust valve, the first piston-cylinder unit and on its cooperating with the cam of the camshaft lever middle or directly the HVA is arranged.
  • the rocker arm can be embodied in one or more parts, in particular in two parts, with a cam lever which starts at the cam of the camshaft and an actuating lever which acts on the exhaust valve, wherein the HVA with the means applying an opposing force is preferably connected between the cam lever and the actuating lever. This achieves a specifically limited coupling of the two mass components in EVB operation without adversely affecting the lash adjuster function of the HVA.
  • a plurality, in particular two exhaust valves can be provided in the valve train per cylinder of the internal combustion engine, which are actuated jointly by a valve bridge of the actuating element or rocker arm, wherein the first piston-cylinder unit is arranged in the valve bridge and, for example, only one exhaust valve to achieve the EVB function.
  • the first piston-cylinder unit and the HVA can be jointly supplied by a pressure-circulation lubricating oil system of the internal combustion engine with pressure oil, wherein in the supply line to the first piston-cylinder unit, a check valve is arranged and the pressure chamber of the first piston-cylinder unit Furthermore, in the closed state of the at least one exhaust valve has a controlled via a stationary counter-holder discharge line and wherein the piston-cylinder unit and the valve spring of the exhaust valve are tuned so that the exhaust valve defined remains open in the engine braking with appropriately closed exhaust valve in the exhaust system of the internal combustion engine ,
  • the at least one, the opposing force applying means thereby ensures effectively that the valve bridge and the anvil specifically cooperate in the dynamic movement in the EVB function so that the piston-cylinder unit and the pressure chamber is reliably supplied with lubricating oil.
  • the at least one means applying an opposing force to the HVA in an additional or alternative embodiment of the invention may also be arranged on the valve bridge and / or on the actuating lever of the rocker arm and thus acting between valve bridge and actuating element and / or on the valve bridge and / or be used on the stationary counter-holder and thus acting between the valve bridge and counter-holder.
  • the two variants for themselves, as well as a combination of both variants serve to reliably maintain the described EVB function.
  • the counter-holder and / or the valve bridge may be provided with a piston-cylinder unit (third piston-cylinder unit).
  • This third piston-cylinder unit serves to "readjust" the anvil valve bridge abutment connection, in particular the anvil valve-bridge closure contact, in response to the intended compensation movement of the HVA element for wear compensation of the valve train wear.
  • the valve disk may "dig in” over the life of the engine in the valve seat, thereby increasing the closed position (rest position) of the valve and, accordingly, the valve seat Valve stem is increased.
  • a valve-controlled reciprocating internal combustion engine in particular a four-stroke reciprocating internal combustion engine (diesel engine), shown, in which in addition to the not apparent intake valves two exhaust valves 2, 3 (only the valve stems are visible ) are guided displaceably.
  • the valves 2, 3 kept closed in a known manner valve springs are not shown here.
  • the valve train acting on the exhaust valves 2, 3 is composed of a driving cam 4 of a camshaft of the internal combustion engine 1, a rocker arm 6 pivotably mounted on a fixed rocker shaft 5 and a valve bridge 7 spanning the two exhaust valves 2, 3.
  • the functionally two-armed rocker arm 6 is exemplified here in two parts, with a cam lever 6a and acting on the valve bridge 7 operating lever 6b, which protrude from the bearing on the rocker shaft 5 to both sides.
  • the cam lever 6a of the rocker arm 6 is pivotally mounted by means of a separate pivot axis 8 on the actuating lever 6b and carries a rotatably mounted on an axle 9 roller 10, which starts at the cam 4 for driving the rocker arm 6.
  • a hydraulic valve clearance compensation element 11 which will be described below in connection with the Fig. 2 will be explained in more detail.
  • the actuating lever 6b of the rocker arm 6 acts on the valve bridge 7 via an adjusting screw 12 (with lock nut) and via a connecting cup 13 mounted spherically thereon at a location positioned between the two outlet valves 2, 3.
  • a stationary counter-holder 14 is provided above the valve bridge 7, whose function will be explained.
  • a piston-cylinder unit 15 is arranged, with a limited slidably guided in a pressure chamber 16 piston 17, which acts on the one outlet valve 2.
  • the pressure chamber 16 is connected via a feed channel 18 with an integrated non-return valve element, for example a ball check valve 19, and not shown, generally designated 20 feed channels in the connecting cup 13, the adjusting screw 12, the rocker arm 6 and finally on the Toggle shaft 5 is connected to the pressure circulation lubricating oil system of the internal combustion engine. It is understood that further channels 20 are provided for lubricating the moving parts of the valve train in the rocker arm 6 (see also Fig. 2 ).
  • a discharge channel 21 defined cross section is also provided, which opens into the pressure chamber 16 of the piston-cylinder unit 15 and which is controlled via the stationary counter-holder 14 as follows.
  • the Fig. 2 shows in enlarged scale and schematically a portion of the rocker arm 6 with the cam lever 6a and partially the actuating lever 6b, in which the likewise designed as a piston-cylinder unit HVA 11 is integrated.
  • a pressure chamber 22 connected to a feed channel 20 is formed in the actuating lever 6b, in which a first piston 23 is displaceably guided, which acts by means of a plunger 24 on the cam lever 6a.
  • a second piston 25 is slidably guided, which defines a second pressure chamber 26, in which a check valve element, in particular a ball check valve 27, is arranged. Further, a vent hole 20a is provided.
  • a valve clearance occurring in the transmission chain between the cam 4 and the outlet valves 2, 3 or the valve bridge 7 can be eliminated in a known manner, for example, by wear, the plunger 24 correspondingly extending or retracting and the distance s (FIG. Fig. 1 ) between the cam lever 6a and the operating lever 6b of the rocker arm 6 is changed accordingly.
  • At least one means is provided between the cam 4 and the outlet valves 2, 3, which exerts a counteracting force of the HVA opposing force in the valve drive.
  • This agent is in accordance with Fig. 1 and 2 is formed by at least one permanent magnet 28 (shown hatched) which is inserted into the cam lever 6a and which exerts a magnetic force (attraction force) on the adjacent portion of the operating lever 6b and / or the piston 23 or plunger 24.
  • This power must be lower be as the force exerted by the HVA 11 Nachstellmoment so as not to affect the regular, fired operation of the internal combustion engine or the regular valve clearance adjustment.
  • This permanent magnet 28 or possibly another permanent magnet 28a could also be provided in the anvil 14, the tightening force is directed to the valve bridge 7, thus counteracting a lifting of the valve bridge 7 from the anvil 14 in the base circle passage of the cam lever 6a at an engine braking.
  • the permanent magnet 28a could also be provided in the connecting cup 13 or kinematically reversed in the valve bridge 7.
  • a leg spring 29 may be arranged with two radially projecting spring arms 29a, wherein the spring arms 29a engage with right angles protruding ends 29b in recesses or holes (without reference numerals) of the lever 6a, 6b and exert a slight bias on the levers 6a, 6b against the readjustment direction of the HVA.
  • a spring and / or rubber-elastic element here by way of example a drawstring 30 may be provided which biases the two levers 6a, 6b defined to one another.
  • the drawstring could, for example, be buttoned or otherwise fastened to free receptacles on free end faces of the cam lever 6a and of the actuation lever 6b.
  • the function of the adjusting action of the HVA 11 with less force counteracting means 28 and / or 28a and / or 29 and / or 30 show the Graphics according to the Fig. 3 to 5 representing the valve lift or opening curves 31, 32 of the exhaust valve 2 and an intake valve over 720 degrees crank angle (KW) of the crankshaft of the internal combustion engine.
  • the graphic corresponds to Fig. 3 and 4 the function without the use of an opposing force wielding means 28, 29 and / or 30, while the graph Fig. 5 this with the means 28, 29 and / or 30 describes.
  • the Fig. 3 shows first the operating state of the internal combustion engine with engine braking or EVB function.
  • the exhaust valve 2 (curve 31) is opened in the intermediate position (curve section 31 a).
  • the exhaust valves 2, 3 as recorded in the curved section 31 b are opened at about 180 degrees KW and closed again at about 330 degrees KW. Due to the upcoming exhaust back pressure and after filling the pressure chamber 16 in the piston-cylinder unit 15 (curve section 31c), the exhaust valve 2 is opened again to the intermediate position (curve section 31d) for compression braking.
  • the relatively linear curve 33 recorded above describes the measured position of the plunger 24 of the HVA 11 during this cycle of operation and without the counteracting force applying means 28, 29 or 30.
  • the curve 33 shows a minimum sinking 33a of the plunger 24 under the load of the valve opening at 31 b and in particular an adjustment (arrows 38) of the plunger 24 after closing the exhaust valves 2, 3 in the area 33 b.
  • This adjustment results from the indifferent movements when opening the exhaust valve 2 controlled by the exhaust back pressure and can interfere with a reliable function of EVB.
  • the Fig. 4 shows the operating state of the internal combustion engine in the transition from the braking operation in the fired operation, wherein the exhaust valve 2 in the region 31 a (power stroke) is still open in the intermediate position.
  • the exhaust valve 2 in the region 31 a power stroke
  • the exhaust valves 2, 3 curve portion 31 b
  • the intake valves with the opening curve 32 open and close in the range between 330 degrees KW to 540 degrees KW in the usual way.
  • the overlying curve 33 of the plunger 24 of the HVA again shows the sinking at 33a and the required readjustment at over the curve portion 31 c lying curve portion 33b.
  • FIG. 5 shows the described valve train with the adjusting effect of the HVA 11 with less force counteracting means 28, 29 or 30 during engine braking operation.
  • the lines 34 in this case limit the range of approximately 120 degrees KW to 420 degrees KW, in which these means 28, 29, 30 do not act due to the significantly higher actuating forces of the cam drive (outside of the cam base circle).
  • the position of the valve bridge 7 may change during the passage of the cam base circle, resulting in the 6 and 7 is shown schematically by the different altitude of the valve bridge 7 with respect to the counter-holder 14. Also in this case, however, the aforementioned closure of the discharge channel 21 must be ensured. This is in the embodiment according to the 6 and 7 achieved by the third piston-cylinder unit 35.
  • a biasing means arranged in the counter-holder 14 eg, as shown a spring 36, alternatively or cumulatively, the biasing member may be formed as an elastomer or by means of repelling magnets
  • the biasing member may be formed as an elastomer or by means of repelling magnets
  • Both the HVA 11 and the third piston-cylinder unit 35 must factory and therefore provide in the state of a new, unused engine extension and Einfahrreseven. This accommodates any change in the valve train mechanism.
  • a permanent magnet 37, 38 may be arranged in the counter-holder 14 and the valve bridge 7. These two permanent magnets 37, 38 attract each other, whereby over the valve bridge 7 and the connecting cup 13 one of the adjusting action of the HVA 11 opposing force is exerted.
  • the third piston-cylinder unit 35 may also be arranged in the valve bridge 7.
  • the magnets can preferably be arranged in a separate component region, in addition to, for example, further elements, such as the illustrated third piston-cylinder unit 35.
  • a one-piece rocker arm or rocker arm can be provided with or without roller contact to the cam 4.
  • the means for exerting a force counteracting the HVA counteracting force can also be carried out differently than shown, but with the same function.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP13003193.3A 2012-10-22 2013-06-22 Dispositif d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape Active EP2722498B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012020594.5A DE102012020594A1 (de) 2012-10-22 2012-10-22 Vorrichtung zum Betätigen zumindest eines Auslassventils einer ventilgesteuerten Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP2722498A1 true EP2722498A1 (fr) 2014-04-23
EP2722498B1 EP2722498B1 (fr) 2016-03-30

Family

ID=48746195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13003193.3A Active EP2722498B1 (fr) 2012-10-22 2013-06-22 Dispositif d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape

Country Status (6)

Country Link
US (1) US8881703B2 (fr)
EP (1) EP2722498B1 (fr)
CN (1) CN103775161B (fr)
BR (1) BR102013027025B1 (fr)
DE (1) DE102012020594A1 (fr)
RU (1) RU2636286C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2851525A1 (fr) * 2013-09-19 2015-03-25 MAN Truck & Bus AG Dispositif et procédé d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape
US11118520B2 (en) * 2019-08-28 2021-09-14 Volkswagen Aktiengesellschaft Method for cylinder equalization of an internal combustion engine
US20240125253A1 (en) * 2022-10-12 2024-04-18 Cummins Inc. Valve actuation system comprising a discrete lost motion device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017114575A1 (de) * 2017-06-29 2019-01-03 Man Truck & Bus Ag Variabler Ventiltrieb
CN111638151B (zh) * 2020-07-15 2022-02-22 一汽解放汽车有限公司 一种检测摩擦副的抗磨损性能的试验方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999051864A2 (fr) * 1998-04-03 1999-10-14 Diesel Engine Retarders, Inc. Rattrapeur de jeu hydraulique a frein de decompression
DE10047141A1 (de) * 1999-09-22 2001-03-29 Mack Trucks Vorrichtung für einen Zweitaktkompressionsmotorbremsbetrieb bei einem Viertaktmotor und Verfahren zur Durchführung eines solchen Betriebes
EP2143896A1 (fr) * 2008-07-11 2010-01-13 MAN Nutzfahrzeuge Aktiengesellschaft Moteur à combustion interne doté d'un dispositif de frein moteur
US20100319657A1 (en) 2009-06-02 2010-12-23 Jacobs Vehicle Systems, Inc. Method and system for single exhaust valve bridge brake
US20110120411A1 (en) * 2009-11-23 2011-05-26 International Engine Intellectual Property Company, Llc Solenoid control for valve actuation in engine brake

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5085315B2 (ja) * 2004-03-15 2012-11-28 ジェイコブス ビークル システムズ、インコーポレイテッド 一体化したロストモーションシステムを有する弁ブリッジ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999051864A2 (fr) * 1998-04-03 1999-10-14 Diesel Engine Retarders, Inc. Rattrapeur de jeu hydraulique a frein de decompression
DE10047141A1 (de) * 1999-09-22 2001-03-29 Mack Trucks Vorrichtung für einen Zweitaktkompressionsmotorbremsbetrieb bei einem Viertaktmotor und Verfahren zur Durchführung eines solchen Betriebes
EP2143896A1 (fr) * 2008-07-11 2010-01-13 MAN Nutzfahrzeuge Aktiengesellschaft Moteur à combustion interne doté d'un dispositif de frein moteur
US20100319657A1 (en) 2009-06-02 2010-12-23 Jacobs Vehicle Systems, Inc. Method and system for single exhaust valve bridge brake
US20110120411A1 (en) * 2009-11-23 2011-05-26 International Engine Intellectual Property Company, Llc Solenoid control for valve actuation in engine brake

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2851525A1 (fr) * 2013-09-19 2015-03-25 MAN Truck & Bus AG Dispositif et procédé d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape
US11118520B2 (en) * 2019-08-28 2021-09-14 Volkswagen Aktiengesellschaft Method for cylinder equalization of an internal combustion engine
US20240125253A1 (en) * 2022-10-12 2024-04-18 Cummins Inc. Valve actuation system comprising a discrete lost motion device

Also Published As

Publication number Publication date
RU2636286C2 (ru) 2017-11-21
US8881703B2 (en) 2014-11-11
RU2013146935A (ru) 2015-04-27
BR102013027025B1 (pt) 2021-07-27
BR102013027025A2 (pt) 2014-10-14
EP2722498B1 (fr) 2016-03-30
US20140109852A1 (en) 2014-04-24
DE102012020594A1 (de) 2014-04-24
CN103775161B (zh) 2017-10-27
CN103775161A (zh) 2014-05-07

Similar Documents

Publication Publication Date Title
DE10220904B4 (de) Vorrichtung zum Verstellen des Hubs eines von einer Nockenwelle betätigten Ventils
DE112004001450B4 (de) Vorrichtung für eine Brennkraftmaschine
DE10047141B4 (de) Vorrichtung für einen Zweitaktkompressionsmotorbremsbetrieb bei einem Viertaktmotor und Verfahren zur Durchführung eines solchen Betriebes
EP2722498B1 (fr) Dispositif d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape
DE112009002211B4 (de) Motorbremseinrichtung für eine Brennkraftmaschine
EP0285877B1 (fr) Dispositif de commande de soupape
WO2008116704A1 (fr) Mécanisme de distribution d'un moteur à combustion interne comportant une soupape champignon désactivable
EP3418513B1 (fr) Dispositif de transmission de force
DE102008059207A1 (de) Nockenfolger zur Betätigung eines Gaswechselventils einer Brennkraftmaschine
DE102006002145A1 (de) Gaswechselventilbetätigungsvorrichtung
AT511041B1 (de) Brennkraftmaschine
EP1619362B1 (fr) Distribution de moteur à combustion
WO2012149921A2 (fr) Mécanisme de distribution et procédé de variation de temps de commande
DE102012215869A1 (de) Ventiltrieb für eine Brennkraftmaschine
EP1588027B1 (fr) Culbuteur d'entrainement hydraulique
DE102015213627B3 (de) Hydraulikelement mit Motorbremsfunktion für eine Viertakthubkolbenbrennkraftmaschine und Viertakthubkolbenbrennkraftmaschine
DE102007016752A1 (de) Ventiltrieb einer Brennkraftmaschine
EP2851525B1 (fr) Dispositif et procédé d'actionnement d'au moins une soupape d'échappement d'un moteur à combustion interne commandé par soupape
EP3173593A1 (fr) Commande de soupape variable comprenant un culbuteur
DE112005002543B4 (de) Brennkraftmaschine und ein Verfahren zum Betreiben einer Brennkraftmaschine
EP1831507A1 (fr) Mecanisme de commande de soupape variable de moteur a combustion interne
EP2803826B1 (fr) Dispositif d'actionnement de deux soupapes d'échappement, sollicitées via un pont de soupape, d'un moteur à combustion interne commandé par soupape
DE102017204877A1 (de) Ventiltrieb für einen Verbrennungsmotor sowie Zylinderkopf
AT6651U1 (de) Variable ventiltriebsvorrichtung für eine brennkraftmaschine
DE10134890A1 (de) Ventilsteuerung für in einem Bremsmodus zu betreibende Brennkraftmaschinen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

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

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20140711

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20151125

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: 785650

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160415

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: 502013002324

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 4

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: 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: 20160330

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: 20160630

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: 20160701

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: 20160330

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

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: 20160330

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: 20160330

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: 20160330

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

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: 20160730

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: 20160330

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: 20160330

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

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: 20160801

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: 20160330

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: 20160330

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: 20160330

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: 20160330

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: 20160330

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: 20160330

Ref country code: BE

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

Effective date: 20160630

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013002324

Country of ref document: DE

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: 20160330

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: 20160330

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20170103

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: CH

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

Effective date: 20160630

Ref country code: LI

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

Effective date: 20160630

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: 20160622

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: 20160330

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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

Effective date: 20170622

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: 20170622

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

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: 20130622

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

Ref country code: LU

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

Effective date: 20160622

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: 20160330

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: 20160330

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: 20160330

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: 20160330

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: BG

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

Effective date: 20160330

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: 20160330

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: 20160330

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20190204

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 785650

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180622

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502013002324

Country of ref document: DE

Owner name: MAN TRUCK & BUS SE, DE

Free format text: FORMER OWNER: MAN TRUCK & BUS AG, 80995 MUENCHEN, DE

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: 20180622

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

Ref country code: SE

Payment date: 20230317

Year of fee payment: 11

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

Ref country code: NL

Payment date: 20230626

Year of fee payment: 11

Ref country code: FR

Payment date: 20230622

Year of fee payment: 11

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

Ref country code: IT

Payment date: 20230620

Year of fee payment: 11

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

Ref country code: DE

Payment date: 20240627

Year of fee payment: 12