EP0626035B1 - Commande de soupape pour un moteur a combustion interne - Google Patents

Commande de soupape pour un moteur a combustion interne Download PDF

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Publication number
EP0626035B1
EP0626035B1 EP94902714A EP94902714A EP0626035B1 EP 0626035 B1 EP0626035 B1 EP 0626035B1 EP 94902714 A EP94902714 A EP 94902714A EP 94902714 A EP94902714 A EP 94902714A EP 0626035 B1 EP0626035 B1 EP 0626035B1
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EP
European Patent Office
Prior art keywords
valve
camshaft
control
eccentric
shaft
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 - Lifetime
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EP94902714A
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German (de)
English (en)
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EP0626035A1 (fr
Inventor
Gert Fischer
Johannes Hoehl
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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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
    • F01L13/0021—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
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0047—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other
    • 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

Definitions

  • the invention is based on the preamble of claim 1 from FR-A 2 500 528.
  • the intermediate element is designed as a push rod driven by the exhaust camshaft via an eccentric, which is formed in an opening enclosing a control cam of the intake camshaft with a contact path acted upon by the intake control cam.
  • this known device serves to achieve a substantially longer but unchangeable valve opening period by means of the intermediate element designed as a connecting rod.
  • the eccentrically-controlled push rod which performs a combined tilting and pushing movement, the main objective for a predetermined, fixed valve opening period is, after a relatively rapid valve opening, to keep the valve essentially constant over a considerable portion of the valve opening period and also to close it relatively quickly.
  • a variable valve opening period is neither intended nor kinematically possible with this device, because the circular-arc-shaped end section of the push rod must interact with a flat counter surface of the transmission element designed as a tappet because of its translational movement component.
  • GB-PS 955 988 discloses a valve control which is suitable for changing the valve opening period with a valve lift which can vary within a limited range due to the system.
  • a tappet is provided as a transmission element in a guide, which can be tilted about an axis parallel to the camshaft by means of a control device depending on the speed.
  • the tappet which is provided with a flat contact track, can be tilted both in and against the direction of rotation of the camshaft, as a result of which valve stroke profiles with different valve opening periods are achieved.
  • the guide is connected to a resilient stop, the stop allowing the guide with the tappet to be tilted at low machine speeds via the relatively unyielding control arms to reduce the valve opening period with a possible elimination of the valve overlaps.
  • the stop holds the guide with the plunger in a non-tilted position at high machine speeds, the control arms dodging the starting, eccentrically arranged bolt in a flexible manner.
  • a disadvantage of this known valve control are the flexible control arms of the control device provided for the speed-dependent tilt control, which in a multi-cylinder internal combustion engine lead to different valve opening periods at one and the same speed across all cylinders and are therefore subject to unacceptable fluctuations in performance and exhaust gas quality.
  • valve control for the targeted load and speed-dependent change of the valve opening angle of a gas exchange valve known.
  • This known valve control differs from the valve control described above in that the camshaft is equipped with an eccentrically arranged driver for radially movable engagement in a radial slot of a drive wheel separate from the camshaft.
  • the drive wheel is displaced in a transverse direction relative to the camshaft, with the consequence of a non-uniform rotational speed of the camshaft coupled via the driver when the drive wheel rotates constantly.
  • This valve control which is based on the principle of constantly non-uniform rotational speeds by deliberate decaching of the components which are coupled with one another in rotation, is disadvantageously expensive to construct.
  • the invention has for its object to show a control device for changing the valve opening periods for a generic valve control with system-dependent changes in valve lift, so that exact control is achieved with little construction.
  • a valve control is specified in claims 2 and 3 and in claim 4, in which the intermediate element arranged between the control cam and the valve-side transmission element is a tilting segment movably mounted in a circular arc section concentric with the axis of the camshaft.
  • the difference between the two configurations lies in the rigid control arm arranged relative to the valve stroke direction.
  • the rigid control arm on the tilting segment is designed to extend transversely to the valve stroke direction for the advantageous use of a cam disc or eccentric gear mechanism which is simple in construction, for the positive control of the circular arc section, which is preferably in a tappet, via the circular arc section concentric with the camshaft stored tilting segment.
  • an intermediate element or tilting segment that is positively controlled relative to the tappet is also known, but is controlled as part of a resilient four-link chain via a coupling via a crank mechanism with a flat contact path of the tappet interacting with the change in stroke of the tappet with a simultaneous change the valve opening period of the gas exchange valve acted upon by the tappet.
  • the force-controlled tilting segment according to the invention is part of a push-loop chain, in which, as is known, each transmission link has a rotary joint and a push-joint.
  • a pair of joints is formed from the stroke-actuated tappet with the tilting segment guided about the axis of the camshaft via the concentric circular arc section in the tappet, the rigid, fork-like control arm of which forms the second joint pair with the crank disk or with the eccentric.
  • the example designed according to claim 4 of a tilting segment with a rigid control arm directed in the valve stroke direction also enables the use of a rotating crank or eccentric gear for the positive control of the tilting segment.
  • the difference from the prior art according to the aforementioned DE-A 39 20 895 is the mounting of the tilting segment in the respective transmission member in a circular arc section concentric to the axis of the camshaft for the predominant change in the valve opening period.
  • a preferred embodiment of the invention shown in principle in claim 1 is described in claims 5 to 10.
  • the roller arranged on the transmission element side is moved in a controlled manner relative to the control cam acting with its direction of rotation, and in an opposite rotation angle assignment the role is moved in a controlled manner relative to the control cam acting against its direction of rotation.
  • the roller in the transmission member which is driven in the same direction relative to the control cam
  • a valve lift curve with a large valve opening angle or long valve opening period results, as is advantageous for a high power output of the internal combustion engine.
  • the roller in the transmission element, which is driven in the opposite direction relative to the control cam results in a valve lift curve with a small valve opening angle or short valve opening period, which results in advantageous operation, in particular at low engine speed.
  • the roller in the transmission element which can be displaced in the same direction relative to the direction of rotation of the control cam, results in a lower absolute speed for the line of contact between the control cam and the contact track of the roller compared to a fixedly arranged roller, which corresponds to a large valve opening angle at constant camshaft speed. If the roller is shifted in opposite directions, the contour of the control cam is transmitted more quickly to the transmission element and thus to the respective gas exchange valve. This results in a high absolute speed for the contact line, which corresponds to a small valve opening angle at constant camshaft speed.
  • valve control of the aforementioned CH-PS 390 617 corresponds, like the claimed valve control, kinematically to a thrust loop chain, but is only influenced discontinuously or, if necessary, in a controlled manner due to the operating point-dependent adaptation of the cam spread with unchanged opening and closing times of the respective valve.
  • valve control of GB-PS 649 192 mentioned earlier enables Although a change in the valve opening angle of a gas exchange valve as a function of the operating point, this is achieved, however, in a kinematically different manner with a rotating crank loop, in which two gear members rotating about mutually parallel axes are coupled by means of a sliding joint.
  • the roller which is controlled synchronously in the same and opposite directions relative to the control cam, is provided on a valve lever, preferably on a rocker arm.
  • the rocker arm designed according to the invention is characterized by an advantageously low construction.
  • the advantage of the low design, in particular for a cylinder head, is further promoted by the design of the push rods which move the rollers and which, by means of a fork-like design, comprise the rocker arms in the longitudinal direction for an essentially flush arrangement, at least in the basic circle phase of the control cam.
  • the inlet-side and outlet-side roller push rods can each be driven by means of a separate control shaft.
  • Separate control shafts per se for controllable rocker arms for changing the opening time for the exhaust valve and for changing the closing time for the intake valve are known from US Pat. No. 2,880,712.
  • This control arrangement can be provided particularly advantageously in the case of a cross-flow cylinder head with an ohc arrangement according to claim 10 in the region above the generally angled gas exchange outlet channels, whereby the intake ports can be optimally designed with this cylinder head.
  • valve control 1 denotes a valve control for a gas exchange valve, not shown, of an internal combustion engine.
  • the valve control 1 comprises a camshaft 2 with a control cam 3, which acts on a contact track 4 of a tappet 5 for opening and closing the gas exchange valve, not shown.
  • the contact track 4 is formed on a circular arc section in the tappet 5 in a circular arc section concentric with the camshaft 2 5 'tiltable segment 6, which is part of a control device 7 for changing the valve opening period with a system-related essentially constant stroke of the gas exchange valve.
  • a rigid control arm 8 is arranged transversely to the valve stroke direction, which is in a positively controlled or desmodromic drive connection via two fork-like, free end sections 9 and 10 with a cam disk 12 designed as an eccentric 11.
  • the eccentric 11 is connected to a separate shaft 13 in a rotationally fixed connection, the shaft 13 being driven synchronously by an output wheel 15 of the camshaft 2 via a drive wheel 14.
  • the eccentric shaft 13 is connected via an arbitrary drive device, not shown, in a couplable connection such that the phase position of the eccentric 11 relative to the camshaft 2 is controlled by about 180 ° in a direction from I to II in order to change the valve opening period and finally can be changed progressively from II to I.
  • the tilt control of the tilting segment 6, which serves to change the valve opening periods in the case of valve lift curves with a system-dependent variable valve lift, is superimposed on the tilting movement forced from the valve lift of the tappet 5 and the control arm 8 supported on the control device side.
  • the extent of the superimposed tilting movement is essentially determined from the lever distance of the control arm 8 and the stroke of the eccentric 11, which can also be designed to be stroke-adjustable relative to the shaft 13 for further different valve opening periods.
  • a control cam 17 of a camshaft 18 acts with the contact track 19 in a transmission element 20 - tappet or valve lever - via one Camshaft 18 concentric circular arc section 21 mounted tilting segment 22 together.
  • the tilting segment 22 is equipped with a rigid control arm 23 which is approximately parallel to the transmission member 20 in the valve stroke direction and on which a push rod 24 of a crank or eccentric gear 25 adjustable in rotation with the camshaft 18 rotates in an articulated manner.
  • a valve control 26 shown in FIGS. 3 and 4 comprises a common camshaft 29 with an intake control cam 30 and an exhaust control cam 31 for actuating an intake valve 27 and an exhaust valve 28, each of which has a roller 32 with a contact track 32 'on one act corresponding rocker arm 33.
  • Each of the rollers 32 is arranged in the respective rocker arm 33 between webs 34 which have circular arc sections 35 which are concentric with the axis of the camshaft 29. These circular arc sections 35 serve as guideways for support bolts 36 of the rollers 32.
  • Arms 37 of a fork-shaped push rod 38 engage on both support bolts 36 on both ends of the respective rocker arm 33.
  • Each of the push rods 38 is in drive connection with an eccentric 39 of a shaft 40 of a control device 41 which is driven synchronously with the camshaft 29 and is adjustable in angle of rotation.
  • a single eccentric shaft 40 is used to control the rollers 32 in the inlet and outlet-side drag levers 33.
  • the only eccentric shaft 40 of the control device 41 is provided with a cross flow cylinder head 42 with an ohc
  • the arrangement is preferably arranged on the outlet side above the usually strongly curved gas exchange outlet channels 43. This arrangement, which requires little installation space, advantageously enables approximately in the base circle phase of the respective control cam 30, 31 aligned arrangement of rocker arm 33 and push rod 38.
  • This assignment can be used advantageously in that a reversal point of the roller 32 in an end region of the transmission link or rocker arm-side circular arc sections 35 from the same to the opposite drive and vice versa and one of the two by 180 ° offset extreme positions of the eccentric 39 controlling the push rod 38 are arranged on a straight line which essentially intersects the axis of the eccentric shaft 40.
  • the respective control cam 30, 31 is in a transverse direction to the respective straight line.
  • a harmonic drive of each roller 32 is thus advantageously achieved with the smallest deviations in valve lift and spread caused by the steering movements of the push rod 38.
  • This arrangement has a kinetically favorable effect in the case of a shaft 40 with eccentrics provided for many gas exchange valves of a multi-valve combustion chamber and / or a multi-cylinder internal combustion engine, with which an advantageously balanced overall torque on the eccentric shaft 40 is achieved in total by compensating opposing torques.
  • This balanced total torque is of essential importance for a phase position controllable driving device 44 assigned to the eccentric shaft 40.
  • the eccentric shaft 40 is driven synchronously via a gear transmission 45 to the camshaft 29.
  • the driving device 44 is assigned to the gear 46 on the eccentric shaft 40.
  • the driving device 44 comprises two stop carriers 47 and 48, which are connected to the eccentric shaft 40 in a rotationally fixed manner and arranged at a fixed axial distance, each with a driving stop 49 and 50.
  • one on the eccentric shaft 40 between the stop carriers 47 and 48 - gear 46 is at the same time the stop support 47 - non-rotatably but axially displaceably provided arm 51 for entrainment via one of the stops 49 and 50 which are offset by a predetermined rotation or phase angle - preferably by approximately 180 °.
  • the arm 51 is brought out of engagement with one of the drive-fixed stops 49, 50 by a controlled, axial displacement, and then the arm 51, which is not driven in the direction of rotation, is acted upon by the other stop 50 or 49 for rotational driving .
  • This small, light and simply constructed driving device 44 results from the advantageously selected position of the eccentric shaft 40 in relation to the rollers 32 which are displaced synchronously and in opposite directions relative to the rotating control cams 30, 31 in the drag levers 33 along the circular control cams 30, 31.
  • valve lift curves shown with solid lines correspond to the lift profile of the respective control cam.
  • valve control according to the invention can be combined with a separate device for targeted valve lift change and / or for specific spread change. This opens up the possibility of being able to optimally adapt a valve control to a respective operating point of the internal combustion engine by independently controlling the respective device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Pour une commande de soupape (26), présentée sur la fig. 3, d'un moteur à combustion interne, dans laquelle un arbre à came (29) muni d'une came de commande (30, 31) agit sur une soupage (29) par l'intermédiaire d'un élément de transmission (33) dont la voie de contact (32') située côté came peut être modifiée dans sa position relative par rapport à la came de commande (39, 31) au moyen d'un dispositif de commande (41) afin de modifier le temps d'ouverture de la soupape pour une course de soupape sensiblement constante inhérente au système, l'invention suggère, afin de parvenir à une commande précise, que la voie de contact (32') soit réalisée sur un galet (32) monté à commande forcée par rapport à la tige de culbuteur (33) en synchronisme avec l'arbre à came (29), en tant qu'élément intermédiaire entre la came de commande (30, 31) et la tige de culbuteur (33).

Claims (10)

  1. Commande de soupape pour un moteur à combustion interne selon laquelle,
    - une came de commande (3, 17, 30, 31) d'un arbre à cames (2, 18, 29) agit par un élément intermédiaire (6, 22, 32) et un élément de transmission (5,20, 33) sur une soupape d'échange de gaz (27, 28) dans le sens de la commande de sa course,
    - l'élément intermédiaire (6, 22, 32) a un chemin de contact (6, 19, 32') sollicité par la came de commande (3, 17, 31) au cours de chaque course de soupape par rapport à la came de commande de rotation (3, 17, 30, 31) et est monté de manière mobile par rapport à l'élément de transmission (5, 20, 33),
    caractérisée en ce que
    • l'élément intermédiaire (6, 22, 32) est monté de manière à être guidé de façon mobile par un segment d'arc de cercle (5', 21, 35) essentiellement concentrique à l'axe de l'arbre à cames (2, 18, 29) dans l'organe de transmission (5, 20,33),
    • en coopérant par l'arbre à cames (2, 18, 29) tournant en synchronisme mais avec l'arbre réglable en phase par rapport à cet arbre à cames (2, 18, 29), avec un dispositif de commande (7, 41) de façon qu'à chaque course de soupape, on obtienne une action du chemin de contact (4, 19, 32') définissant la phase d'ouverture de soupape avéc les flancs de l'arbre à cames (3, 17, 30, 31) qui tourne, par un mouvement de l'élément intermédiaire (6, 22, 32) commandé de manière forcée dans le même sens et/ou dans le sens différent par rapport au sens de rotation de la came de commande (3, 17, 30, 31).
  2. Commande de soupape selon la revendication 1,
    caractérisée en ce que
    • le chemin de contact (4) est réalisé sur un segment basculant (6) relié de manière mobile à l'organe de transmission (5) par l'arc de cercle (5'), avec un bras de commande (8), rigide, dirigé transversalement par rapport à la direction de déplacement de la soupape,
    • un segment d'extrémité libre (9, 10) avec une came (12, 11) du dispositif de commande (11) tournant en synchronisme avec l'arbre à cames (2), pour commander le basculement du segment basculant (6), et
    • le mouvement de basculement provoqué par le mouvement de soulèvement de l'élément de transmission (5) et du bras de commande (8) qui s'appuie sur le côté du dispositif de commande, peut être modifié en outre à l'aide de la came (12).
  3. Commande de soupape selon la revendication 2,
    caractérisée en ce que
    • le bras de commande (8) comporte deux segments d'extrémité libres (9, 10) en forme de fourche entre lesquels est entraînée une came (12) en forme d'excentrique par un arbre d'entraînement (13) entraîné en synchronisme avec l'arbre à cames (2),
    • l'excentrique (11) peut être modifié en phase par rapport à l'arbre à cames (2) d'une valeur angulaire prédéterminée (par exemple environ 180°) à l'aide d'une installation d'entraînement (I-II-I) prévue dans la ligne de transmission de l'arbre (13) en pouvant être commandée en phase avec l'arbre à cames (2).
  4. Commande de soupape selon la revendication 1,
    caractérisée en ce que
    • le chemin de contact (19) est réalisé sur un segment basculant (22) en liaison mobile avec l'organe de transmission (20) par le segment d'arc de cercle (21), avec un bras de commande (23), rigide, parallèle à la direction de la course de la soupape,
    • ce bras est soumis à l'action d'une bielle (24) d'une transmission à manivelle ou excentrique (25) du dispositif de commande, relié de manière articulée à la bielle (24) et qui peut tourner en synchronisme avec la transmission à manivelle ou excentrique (25) réglable en phase du dispositif de commande, et
    • l'axe de la transmission (25) correspond sensiblement à la demi-course de l'organe de transmission (20).
  5. Commande de soupape selon la revendication 1,
    caractérisée en ce que
    • l'élément intermédiaire avec le chemin de contact (32') est un galet (32) guidé de manière coulissante sur un segment d'arc de cercle (35) concentrique le long ou dans l'organe de transmission (33), et qui, à chaque course de soupape, est commandé à l'aide d'une bielle (38) d'une transmission à manivelle ou excentrique (39, 40) tournant en synchronisme avec l'arbre à cames (29) du dispositif de commande (41) entre la came de commande (30, 31) et l'organe de transmission (33), transversalement à la direction de déplacement de la soupape, par rapport à la came de commande tournante (30, 31), avec une commande forcée en synchronisme, dans le même sens ou dans le sens opposé.
  6. Commande de soupape selon la revendication 1 et 5,
    caractérisée en ce que
    • l'élément de transmission est un levier (33) avec un galet (32) monté entre les branches (34) par l'intermédiaire d'un goujon de support (36),
    • ce galet pouvant être déplacé le long des segments d'arc de cercle (35) concentriques servant de chemins de guidage au goujon de support (36) dans les branches (34) à l'aide de la bielle (38) de la transmission à excentrique (39, 40) agissant sur le goujon de support (36), avec un déplacement dans le même sens ou dans le sens opposé,
    • la bielle (38) en forme de fourche agit avec ses bras (37) prévus des deux côtés du levier de soupape (33) sur le goujon de support (36).
  7. Commande de soupape selon la revendication 5 et 6,
    caractérisée en ce que
    • l'élément de transmission (33) portant le galet (32) et l'axe (40) muni de l'excentrique (39) sont associés de façon qu'un point d'inversion du galet (32) se trouve dans une zone d'extrémité du segment d'arc de cercle (35) du côté de l'élément de transmission, pour l'entraînement dans le même sens vers le sens opposé et inversement et l'une des deux positions extrêmes décalées de 180° de l'excentrique (39) commandant la bielle (38) sur une droite coupant principalement l'axe géométrique de l'axe d'excentrique (40) et
    • une installation d'entraînement (44) à commande de phase est commutée dans la liaison d'entraînement de l'axe d'excentrique (40) et de l'arbre à cames (29).
  8. Commande de soupape selon l'une ou plusieurs des revendications 1 à 7,
    caractérisée en ce que
    • l'installation d'entraînement (44) comprend deux supports de butée (47, 48) avec chaque fois une butée d'entraînement (49, 50) sur l'axe (40) du dispositif de commande respectif, de manière solidaire en rotation et avec une distance axiale fixe, et
    • sur l'axe (40), entre les supports de butée (47, 48), de manière solidaire en rotation et coulissant axialement, un bras (59) pour l'entraînement par l'intermédiaire de l'une des butées (49, 50) décalées d'une phase prédéterminée (par exemple environ 180°), le bras (51) de réglage de phase de l'arbre (40) étant mis hors de prise de l'une des butées fixes d'entraînement (49, 50) par un déplacement axial commandé, puis l'autre bras (51) sans entraînement, suivant dans le sens de rotation étant sollicité pour être entraîné en rotation par l'autre butée (50, 49) solidaire de l'entraînement.
  9. Commande de soupape selon les revendications 5 à 8,
    caractérisée en ce que
    • un arbre à cames (29) commun pour le levier tiré (33) prévu comme élément de transmission pour les soupapes d'admission et d'échappement (27, 28) agit avec chaque came de commande (30, 31) sur chaque levier tiré (33) par un galet (32) commandé dans le même sens et dans le sens opposé en permanence, en synchronisme par rapport à l'arbre à cames,
    • un seul arbre (40) réglable en phase, tournant en synchronisme avec l'arbre à cames (29) et appartenant au dispositif de commande (41) avec l'excentrique (39) pour les galets (32) commandés par la bielle est prévu pour les leviers tirés (33) associés respectivement à la soupape d'admission et à la soupape d'échappement (27, 28).
  10. Commande de soupape selon l'une des revendications 1 à 9,
    caractérisée en ce que
    • pour une culasse (42) à flux transversal avec une disposition ohc, l'unique arbre à excentrique (40) pour commander les éléments intermédiaires ou les galets (32) des éléments de transmission ou leviers tirés (33) particuliers pour les soupapes d'admission et d'échappement (27, 28) est prévu dans la zone au-dessus des canaux d'échappement (43) d'échange de gaz,
    • l'arbre à excentrique (40) est entraîné avec l'arbre à cames (29) par une liaison d'entraînement (45) et
    • la roue d'entraînement (46) du côté de l'arbre de l'excentrique forme une installation d'entraînement (44) commandée en phase pour les supports de butée (47, 48).
EP94902714A 1992-12-13 1993-12-08 Commande de soupape pour un moteur a combustion interne Expired - Lifetime EP0626035B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4242060 1992-12-13
DE4242060 1992-12-13
PCT/EP1993/003451 WO1994013935A1 (fr) 1992-12-13 1993-12-08 Commande de soupape pour un moteur a combustion interne

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EP0626035A1 EP0626035A1 (fr) 1994-11-30
EP0626035B1 true EP0626035B1 (fr) 1997-08-13

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DE (1) DE59307123D1 (fr)
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Cited By (2)

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Publication number Priority date Publication date Assignee Title
WO1999064729A1 (fr) 1998-06-05 1999-12-16 Bayerische Motoren Werke Aktiengesellschaft Mecanisme de distribution pour un moteur a combustion interne
DE102011001612A1 (de) * 2011-03-29 2012-10-04 Pierburg Gmbh Vorrichtung zur diskreten Phasenverschiebung

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DE4418909A1 (de) * 1994-05-31 1995-12-07 Bayerische Motoren Werke Ag Ventilsteuerung mit einer Anordnung zur variablen Änderung der Öffnung und Schließung eines Hubventils,insbesondere für Brennkraftmaschinen
EP0717174A1 (fr) * 1994-12-12 1996-06-19 Isuzu Motors Limited Système de commande de soupape pour moteur à combustion interne
DE19537377A1 (de) * 1995-10-06 1997-04-10 Bayerische Motoren Werke Ag Vorrichtung zur Veränderung des Hubverlaufes von Brennkraftmaschinen-Ventilen
US5937809A (en) * 1997-03-20 1999-08-17 General Motors Corporation Variable valve timing mechanisms
JP2001164911A (ja) * 1999-12-10 2001-06-19 Yamaha Motor Co Ltd ４サイクルエンジンの動弁機構
CN112523875B (zh) * 2020-12-01 2022-08-12 广西玉柴机器股份有限公司 一种船用发动机越控功能的控制方法

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US2266077A (en) * 1938-10-03 1941-12-16 Henry A Roan Internal combustion engine
US2880712A (en) * 1958-07-03 1959-04-07 Henry A Roan Variable valve timing for overhead cam engines
FR2500528B1 (fr) * 1981-02-20 1985-10-11 Ferrer Jean Mecanisme de commande des soupapes d'admission, d'un moteur a combustion interne, pour un temps d'admission prolonge
US4469056A (en) * 1983-02-22 1984-09-04 Tourtelot Jr Edward M Dual follower variable valve timing mechanism
US4530318A (en) * 1984-01-20 1985-07-23 Carol M. Semple Intake and exhaust valve system for internal combustion engine
DE3519319A1 (de) * 1985-05-30 1986-12-04 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Variable ventilsteuerung fuer eine hubkolben-brennkraftmaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999064729A1 (fr) 1998-06-05 1999-12-16 Bayerische Motoren Werke Aktiengesellschaft Mecanisme de distribution pour un moteur a combustion interne
DE102011001612A1 (de) * 2011-03-29 2012-10-04 Pierburg Gmbh Vorrichtung zur diskreten Phasenverschiebung
DE102011001612B4 (de) * 2011-03-29 2013-02-28 Pierburg Gmbh Vorrichtung zur diskreten Phasenverschiebung

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EP0626035A1 (fr) 1994-11-30
DE59307123D1 (de) 1997-09-18
WO1994013935A1 (fr) 1994-06-23

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