EP0638706A1 - Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne - Google Patents

Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne Download PDF

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Publication number
EP0638706A1
EP0638706A1 EP93119520A EP93119520A EP0638706A1 EP 0638706 A1 EP0638706 A1 EP 0638706A1 EP 93119520 A EP93119520 A EP 93119520A EP 93119520 A EP93119520 A EP 93119520A EP 0638706 A1 EP0638706 A1 EP 0638706A1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
cam
valve
lift
valve train
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.)
Withdrawn
Application number
EP93119520A
Other languages
German (de)
English (en)
Inventor
Harald Unger
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke 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
Priority claimed from DE19934326331 external-priority patent/DE4326331A1/de
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0638706A1 publication Critical patent/EP0638706A1/fr
Withdrawn legal-status Critical Current

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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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • 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
    • F01L13/0021—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 rocker arm ratio
    • F01L13/0026—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 rocker arm ratio by means of an eccentric
    • 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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/06—Timing or lift different for valves of same cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/245—Arrangement of valve stems in cylinder heads the valve stems being orientated at an angle with the cylinder axis

Definitions

  • the invention relates to a valve train of an internal combustion engine with at least two parallel-acting lift valves per cylinder, each actuated by a cam and a transmission element, the valve lift course of which can be adjusted differently from one another.
  • Such a valve train is known for example from DE 37 39 246 A1.
  • the transmission member is designed as a rocker arm, wherein individual rocker arms of the lift valves assigned to a single cylinder can be connected to one another via coupling elements. Since different cams are assigned to the individual rocker arms in this known prior art, it is thus possible, by appropriate control of these rocker arm clutches, to actuate a specific lift valve either directly by the cam assigned to it or by the cam of another lift valve. The course of the valve stroke of this particular lift valve can thus be varied in different ways from that of another lift valve.
  • the support points of the transmission members are adjustable via rotatable eccentrics located on a common eccentric shaft, the elevation curves of the at least two eccentrics per cylinder differing from one another.
  • the support points of the transmission elements interposed between the individual cams and the individual valves are adjustable.
  • these transmission links can be a rocker arm or also a rocker arm or rocker arm, but other embodiments are also possible, for example a link element having a link track for a roller. If the support point of this rocker arm or rocker arm or of the link element is now shifted, a modified stroke curve results for the respectively associated lift valve, since the cam stroke is transmitted in different ways.
  • This principle for varying the valve stroke course is known per se (DE 38 33 540 C2), but this known embodiment does not specify how the support point of the transmission element can be shifted in a simple manner.
  • eccentrics on which the transmission members are supported are part of a common eccentric shaft - if several cylinders are arranged in series, this eccentric shaft can extend over all cylinders - which can be rotated in a simple manner.
  • the eccentrics assigned to an individual cylinder also differ. As a result, it is possible, as desired, to actuate the valves assigned to these individual eccentrics in different ways from one another, or to adjust their stroke course in different ways from one another.
  • the reference numeral 1 denotes a cylinder head of an internal combustion engine. In the illustration according to FIG. 1, this cylinder head extends across several cylinders perpendicular to the plane of the drawing. At least two inlet channels 2 to a combustion chamber 3 are provided per cylinder, a lift valve 4 being provided in a known manner per inlet channel 2. This lift valve is actuated by a cam 5a of a camshaft 5, the cam 5a acting on a roller 6, which in turn rolls on the tappet 7 of the lift valve 4.
  • the roller 6 is of stepped design and has a plurality of rolling stages 6a, 6b, 6c. With the rolling stage 6a, the roller 6 rests on the tappet 7, while the rolling stage 6b is in contact with the cam 5a. Finally, with the rolling stage 6c, the roller 6 rolls on a slide track 8a of a slide element 8, so that the roller 6 is guided as a whole through this slide element 8 in accordance with the slide track 8a. Overall, the link element 8 and the roller 6 thus form the so-called transmission element 9 located between the cam 5a and the lift valve 4.
  • this transmission element 9 or the link element 8 is supported on an eccentric 10a, which is machined out of an eccentric shaft 10. If the eccentric shaft 10 is now rotated about its longitudinal axis 10b - two different positions are shown in FIGS. 1, 2 - the support point of the link element 8 or of the transmission element 9 is shifted. This also changes the position of the roller 6 or the sliding track 8a, which ultimately guides the roller 6 moved by the rotating cam 5a. When the support point of the transmission element 9 is changed, however, as can be seen, different valve lifts result with the same cam stroke. In Figure 1, the maximum achievable valve stroke h is shown at maximum cam stroke. In contrast, in FIG. 2 the eccentric shaft 10 is rotated through 180 ° about its longitudinal axis 10b. The resulting displacement of the transmission element 9 results in a valve lift of almost the amount 0 at maximum cam lift, i.e. the lift valve 4 is only opened minimally.
  • a reset lever 11 which also engages the rolling step 6a of the roller 6 and thus always presses this roller against the cam 5a.
  • This reset lever 11 is acted upon in a corresponding manner by a compression spring 12a.
  • the compression spring 12a is clamped between a pressure element 12b acting on the reset lever 11 and a guide element 12c screwed into the cylinder head 1.
  • the longitudinal guide 13 for the link element 8 is also only shown in principle.
  • FIG. 3 shows, two lift valves 4, 4 'are provided for each individual cylinder 14a, 14b of the internal combustion engine cylinder head 1.
  • Each lift valve 4, 4 'of an individual Cylinder 14a or 14b is assigned its own cam 5a, 5a 'and its own transmission element 9, 9' in the form of its own link element 8, 8 'and its own roller 6, 6'.
  • Each link element 8, 8 ' is supported on its own eccentric 10a, 10a' of the eccentric shaft 10 which extends over the entire cylinder head 1.
  • FIGS. 1, 2 show, the two eccentrics 10a, 10a 'assigned to a cylinder 14a or 14b differ in their geometry.
  • the two eccentrics 10a, 10a 'of a cylinder are identical only in the points of the minimum and the maximum eccentric stroke. Thus, if the eccentric shaft 10 is in the position shown in FIG. 2, the two lift valves 4, 4 'of a cylinder remain almost closed despite the maximum cam stroke. If, on the other hand, the eccentric shaft 10 is in the position according to FIG. 1, the two lift valves 4, 4 'are opened to the maximum at maximum cam lift (valve lift h). In the intermediate positions of the eccentric shaft, on the other hand, the two lift valves 4, 4 'are opened to different degrees at maximum cam lift. The course of the valve stroke of these two lift valves 4, 4 'per cylinder 14a or 14b can thus be varied in different ways by adjusting the eccentric shaft 10.
  • FIG. 4 shows various valve lift profiles in a diagram.
  • the crank angle or camshaft angle is plotted on the abscissa, the ordinate indicates the valve lift that can be achieved.
  • the associated position of the eccentric shaft 10 is indicated for each of the five valve lift profiles selected by way of example.
  • the numerical value given on the rising branch refers to the first lift valve 4, while the numerical value given on the falling branch indicates the required eccentric shaft position for the second lift valve 4 '.
  • the position the eccentric shaft 10 is described by degrees of angle, the position according to FIG. 2 corresponding to 0 ° and the position according to FIG. 1 representing the value of 180 °.
  • the reference number 1 again designates a cylinder head of an internal combustion engine.
  • This cylinder head also extends across several cylinders perpendicular to the plane of the drawing.
  • At least two inlet ducts 2 to the combustion chamber 3 are provided per cylinder, a lift valve 4 being provided for each inlet duct 2.
  • Each lift valve 4, 4 ' is actuated by a cam 5a, 5a' of a camshaft, each cam acting on a rocker arm 16, 16 ', which in turn acts on a rocker arm 17, 17'.
  • a hydraulic lash adjuster 18, 18 ' is mounted in the rocker arm 17, 17' on which ultimately the stem of the lift valve 4, 4 'is supported.
  • the rocker arm 16 and the rocker arm 17 form a transmission member 19 or 19 ', by means of which the stroke profile of the cam 5a or 5a' is transmitted to the lift valve 4 or 4 '.
  • the transmission link 19 or the rocker arm 16 is supported on an eccentric 10a, which is machined out of an eccentric shaft 10. If the eccentric shaft 10 is rotated about its longitudinal axis 10b, the support point of the rocker arm 16 or the transmission member 19 is shifted. Such a change in the support point of the transmission member 19 results in different valve lifts for the same cam stroke, since, due to the changed support of the rocker arm 16 when the cam 5a rotates with respect to the rocker arm 17, a different path of motion is passed through, so that the rocker arm 17 is deflected differently. In particular, it is hereby possible to achieve not only a maximum valve lift but also a valve lift of almost the amount 0 at which the lift valve 4 is opened only minimally.
  • the rocker arm 16 is guided by an elongated bolt guide, designated in its entirety by the reference number 20.
  • the rocker arm 16 has an elongated hole 20a, via which it is suspended in a bolt 20b, which is fastened to the cylinder head in a bearing point 20c. Because of this elongated bolt guide 20, the rocker arm 16 can thus assume different positions.
  • the elongated bolt guide 20 can also be designed the other way round, ie the bolt 20b can be attached to the rocker arm 16 and the elongated hole 20a can then be provided in the cylinder head bearing point 20c.
  • each lift valve 4, 4 ' is assigned its own cam 5a, 5a' and its own transmission link 19, 19 'in the form of its own rocker arm 16, 16' and its own rocker arm 17, 17 '.
  • Each rocker arm 16, 16 ' is supported on its own eccentric 10a, 10a' of the eccentric shaft 10 which extends over the entire cylinder head 1.
  • 5 shows, the two eccentrics 10a, 10a 'assigned to a cylinder or combustion chamber 3 differ in their geometry.
  • the two eccentrics 10a, 10a 'of a cylinder / combustion chamber are identical only in the points of the minimum and the maximum eccentric stroke.
  • the two lift valves 4, 4 'of a cylinder remain almost closed despite the maximum cam stroke. If, on the other hand, the eccentric shaft 10 is rotated from the position shown, and the eccentrics 10a, 10a 'accordingly adjust the rocker arms 16, 16' on account of their then maximum eccentric stroke, the two lift valves 4, 4 'are opened to the maximum with a maximum cam stroke . In the intermediate positions of the eccentric shaft 10, on the other hand, the two lift valves 4, 4 'are opened to different degrees at maximum cam lift. The course of the valve lift of these two lift valves 4, 4 'can thus be changed in different ways from one another by adjusting the eccentric shaft 10.
  • the transmission link 19 is formed by a rocker arm 16 and by a rocker arm 17 connected downstream, an extremely reliable construction results, which is furthermore distinguished by a space-saving design.
  • a rolling friction is realized in the contact areas between the cam 5a and the rocker arm 16 and between the rocker arm 16 and the rocker arm 17.
  • the rocker arm 16 carries a roller 16b and the rocker arm 17 carries a roller 17b.
  • each rocker arm 16 is guided between the two arms 16c of the rocker arm, which in some cases has two arms, and is mounted on a roller axle (not specified in more detail) which is fastened in these rocker arm arms. Due to the two-armed nature of the rocker arm 16 in the section that emerges in particular from the illustration according to FIG. 4, the eccentric 10a associated with this rocker arm 16 is also formed in two parts, in particular for weight reduction. H. a separate eccentric disk is provided for each of the rocker arm 16c, the two adjacent eccentric disks, which are only spaced apart from one another by the width of the roller 16b, of course having the same configuration.
  • the rocker arm 17 has - as is known per se - a rocker arm bearing 17a, from which a rocker arm 17c leads to a receptacle 17d which carries the hydraulic lash adjuster 18 acting on the lift valve 4.
  • the roller 17b is arranged on the side of the rocker arm 17c. This asymmetrical design, which can be seen particularly clearly from FIG. 9, results in an extremely space-saving design.
  • the roller 17b is also mounted on one Axle that is attached on the one hand to the rocker arm 17c and on the other hand to a further secondary arm 17e. This secondary arm 17e also leads from the rocker arm bearing 17a to the receptacle 17d.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP93119520A 1993-08-05 1993-12-03 Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne Withdrawn EP0638706A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4326331 1993-08-05
DE19934326331 DE4326331A1 (de) 1992-07-15 1993-08-05 Ventiltrieb einer Brennkraftmaschine

Publications (1)

Publication Number Publication Date
EP0638706A1 true EP0638706A1 (fr) 1995-02-15

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Application Number Title Priority Date Filing Date
EP93119520A Withdrawn EP0638706A1 (fr) 1993-08-05 1993-12-03 Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne

Country Status (3)

Country Link
US (1) US5373818A (fr)
EP (1) EP0638706A1 (fr)
JP (1) JP3245492B2 (fr)

Cited By (17)

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Publication number Priority date Publication date Assignee Title
EP0780547A1 (fr) 1995-12-22 1997-06-25 Siemens Aktiengesellschaft Dispositif permettant de varier la loi de leveé d'une soupape de moteur à combustion interne
WO1998003778A1 (fr) 1996-07-20 1998-01-29 Dieter Reitz Mecanisme de distribution et culasse de moteur a combustion interne
WO1999009303A1 (fr) 1997-08-14 1999-02-25 Siemens Aktiengesellschaft Procede d'ajustement de la levee d'une soupape
DE19810369C1 (de) * 1998-03-10 1999-08-12 Siemens Ag Vorrichtung zur Messung des Ventilhubes
DE19920512A1 (de) * 1999-05-05 2000-11-09 Opel Adam Ag Vorrichtung zur Betätigung eines Ventiles mit variablem Hub an Brennkraftmaschinen
US6164254A (en) * 1997-08-14 2000-12-26 Siemens Aktiengesellschaft Method for setting valve lift
DE19942934A1 (de) * 1999-09-08 2001-03-15 Siemens Ag Verfahren zum Messen des maximalen Ventilhubes
EP1143118A3 (fr) * 2000-04-07 2002-11-13 Bayerische Motoren Werke Aktiengesellschaft Dispositif pour varier la levée d'une soupape dans la culasse d'un moteur à combustion interne
WO2004057160A1 (fr) * 2002-12-21 2004-07-08 Ina-Schaeffler Kg Levier intermediaire d'un mecanisme de commande variable de soupape d'un moteur a combustion interne
DE10251007B4 (de) * 2001-11-15 2007-09-06 Avl List Gmbh Mit fremdzündbaren Kraftstoff betriebene Brennkraftmaschine
DE102006018512A1 (de) * 2006-04-21 2007-10-25 Schaeffler Kg Rollenelement für ein schwenkbewegliches Maschinenteil
EP1666714A3 (fr) * 2004-10-14 2010-08-11 Bayerische Motoren Werke Aktiengesellschaft Carter pour moteur à combustion
DE102010048709A1 (de) 2010-10-19 2012-04-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
WO2012126648A1 (fr) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Entraînement de soupapes à commande mécanique et système d'entraînement de soupapes à commande mécanique
DE102013113815A1 (de) 2013-12-11 2015-06-11 Pierburg Gmbh Übertragungsanordnung für einen mechanisch steuerbaren Ventiltrieb
DE102014114396A1 (de) 2014-10-02 2016-04-07 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
EP3073072A2 (fr) 2015-03-26 2016-09-28 Pierburg GmbH Commande de soupape à commande mécanique et système de commande de soupape pouvant être commandé

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IT1285853B1 (it) * 1996-04-24 1998-06-24 Fiat Ricerche Motore a combustione interna con valvole ad azionamento variabile.
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DE10016103A1 (de) 2000-03-31 2001-10-04 Audi Ag Variable Ventilsteuerung
DE10052811A1 (de) * 2000-10-25 2002-05-08 Ina Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
WO2002081872A1 (fr) 2001-04-05 2002-10-17 Stephen William Mitchell Systeme de distribution a programme variable
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DE10206465A1 (de) * 2002-02-16 2003-08-28 Mahle Ventiltrieb Gmbh Steuereinrichtung für Gaswechselventile eines Verbrennungsmotors
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AU2003242323A1 (en) * 2002-05-17 2003-12-02 Koichi Hatamura Engine valve driver
WO2003098013A1 (fr) 2002-05-17 2003-11-27 Yamaha Hatsudoki Kabushiki Kaisha Dispositif d'entrainement de soupape de moteur
US6659053B1 (en) 2002-06-07 2003-12-09 Eaton Corporation Fully variable valve train
DE10228022B4 (de) * 2002-06-20 2009-04-23 Entec Consulting Gmbh Ventilhubvorrichtung zur Hubverstellung der Gaswechselventile einer Verbrennungskraftmaschine
DE10261304B4 (de) * 2002-12-27 2009-01-22 BÖSL-FLIERL, Gerlinde Ventilhubvorrichtung zur variablen Ventilsteuerung der Gaswechselventile einer Verbrennungskraftmaschine
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CA2518949A1 (fr) 2003-03-11 2004-09-23 Yamaha Hatsudoki Kabushiki Kaisha Mecanisme de soupape variable pour moteur a combustion interne
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EP1618293B1 (fr) * 2003-03-29 2008-09-24 Hydraulik-Ring Gmbh Dispositif de poussoir a soupape variable utilise pour ajuster les soupapes d'echange de gaz dans un moteur a combustion interne
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US6886510B2 (en) 2003-04-02 2005-05-03 General Motors Corporation Engine valve actuator assembly with dual hydraulic feedback
JP4248343B2 (ja) 2003-05-01 2009-04-02 ヤマハ発動機株式会社 エンジンの動弁装置
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AU2004265498A1 (en) * 2003-08-18 2005-02-24 Emmanouel Pattakos Variable valve gear
JP4247529B2 (ja) * 2003-08-22 2009-04-02 ヤマハ発動機株式会社 内燃機関の動弁機構
JP2005069014A (ja) * 2003-08-25 2005-03-17 Yamaha Motor Co Ltd 内燃機関の動弁機構
JP4237643B2 (ja) 2003-08-25 2009-03-11 ヤマハ発動機株式会社 内燃機関の動弁機構
JP4039383B2 (ja) * 2003-10-21 2008-01-30 トヨタ自動車株式会社 水素利用内燃機関
US6945204B2 (en) * 2003-11-12 2005-09-20 General Motors Corporation Engine valve actuator assembly
DE602004006649T2 (de) * 2003-12-18 2008-01-31 Toyota Jidosha Kabushiki Kaisha, Toyota Variabler ventilmechanismus
JP4225321B2 (ja) 2003-12-18 2009-02-18 トヨタ自動車株式会社 可変動弁機構
RU2330164C2 (ru) * 2004-01-16 2008-07-27 Хонда Мотор Ко., Лтд. Система привода клапанов двигателя
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WO1998003778A1 (fr) 1996-07-20 1998-01-29 Dieter Reitz Mecanisme de distribution et culasse de moteur a combustion interne
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DE19942934B4 (de) * 1999-09-08 2005-08-04 Siemens Ag Verfahren zum Verwenden des Wertes des maximalen Ventilhubes eines Gaswechselventils
EP1143118A3 (fr) * 2000-04-07 2002-11-13 Bayerische Motoren Werke Aktiengesellschaft Dispositif pour varier la levée d'une soupape dans la culasse d'un moteur à combustion interne
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US7055478B2 (en) 2002-12-21 2006-06-06 Ina-Schaeffler Kg Intermediate lever for a variable valve train of an internal combustion engine
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WO2012052216A1 (fr) 2010-10-19 2012-04-26 Kolbenschmidt Pierburg Innovations Gmbh Distribution à commande mécanique et ensemble de distribution à commande mécanique
US8807104B2 (en) 2010-10-19 2014-08-19 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve operating mechanism, and mechanically controllable valve operating mechanism arrangement
WO2012126648A1 (fr) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Entraînement de soupapes à commande mécanique et système d'entraînement de soupapes à commande mécanique
DE102011014744A1 (de) 2011-03-22 2012-09-27 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
US9133737B2 (en) 2011-03-22 2015-09-15 Kolbenschmidt Pierburg Innovations Gmbh Mechanically controllable valve drive and mechanically controllable valve drive arrangement
DE102013113815A1 (de) 2013-12-11 2015-06-11 Pierburg Gmbh Übertragungsanordnung für einen mechanisch steuerbaren Ventiltrieb
EP2905437A2 (fr) 2013-12-11 2015-08-12 Pierburg GmbH Système de transmission pour une commande de soupape pouvant être commandée mécaniquement
US9464540B2 (en) 2013-12-11 2016-10-11 Pierburg Gmbh Transfer assembly for a mechanically controllable valve train
DE102014114396A1 (de) 2014-10-02 2016-04-07 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
EP3006684A1 (fr) 2014-10-02 2016-04-13 Pierburg GmbH Commande de soupape a commande mecanique et systeme de commande de soupape pouvant etre commande
EP3073072A2 (fr) 2015-03-26 2016-09-28 Pierburg GmbH Commande de soupape à commande mécanique et système de commande de soupape pouvant être commandé
DE102015104633A1 (de) 2015-03-26 2016-09-29 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung

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