EP0626035B1 - Valve control for an internal combustion engine - Google Patents

Valve control for an internal combustion engine 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)
French (fr)
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EP0626035A1 (en
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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Publication of EP0626035A1 publication Critical patent/EP0626035A1/en
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    • 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.

Abstract

For a valve control (26) of an internal combustion engine shown in Fig. 3, in which a camshaft (29) with control cam (30, 31) acts on a valve (27, 28) via a transmission element (33), the position of the contact path (32') of which on the cam side can be altered in relation to the control cam (30, 31) by means of a control device (41) to change the valve opening time for a substantially constant valve travel conditioned by the system, in order to achieve precise control it is proposed that the contact path (32') be formed on a roller (32) compulsorily controlled relatively to the push rod (33) in synchronism with the camshaft (29) as an intermediate component between the control cam (30, 31) and the push rod (33).

Description

Die Erfindung geht gemäß dem Oberbegriff des Patentanspruches 1 von der FR-A 2 500 528 aus.The invention is based on the preamble of claim 1 from FR-A 2 500 528.

Bei dieser bekannten Ventilsteuerung ist das Zwischenelement als eine von der Auslaß-Nockenwelle über einen Exzenter angetriebene Schubstange gestaltet, die in einer einen Steuernocken der Einlaß-Nockenwelle umschließenden Durchbrechung mit einer vom Einlaß-Steuernocken beaufschlagten Kontaktbahn ausgebildet ist. Diese bekannte Vorrichtung dient gegenüber einem herkömmlichen Ventiltrieb mit einem direkt auf ein ventilseitiges Übertragungsglied einwirkenden Steuernocken dazu, mittels des als Schubstange gestalteten Zwischenelementes eine wesentlich längere, aber unveränderbare Ventilöffnungsperiode zu erzielen. Mit der exzentergesteuerten, eine kombinierte Kipp- und Schubbewegung ausführenden Schubstange ist bei vorbestimmter, fixer Ventilöffnungsperiode das Hauptziel, nach einer relativ raschen Ventilöffnung das Ventil über einen erheblichen Anteil der Ventilöffnungsperiode im wesentlichen konstant offenzuhalten und ferner relativ rasch zu schließen. Kinematisch ist dies dadurch erreicht, daß die zur Ventilachse schräg in der Schubstange angeordnete Kontaktbahn während des Nockeneingriffes zur Einlaß-Nockenwelle exzentergesteuert eng benachbart gehalten ist, wobei die Schubstange durch den Nockeneingriff mit der schrägen Kontaktbahn in Richtung Ventilöffnung zusätzlich um den Exzenter der Auslaß-Nockenwelle geschwenkt ist zur konstanten Offenhaltung des Einlaßventiles.In this known valve control, 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. Compared to a conventional valve train with a control cam acting directly on a valve-side transmission element, 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. With 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. This is achieved kinematically by the fact that the contact track, which is arranged obliquely to the valve axis in the push rod, is kept closely adjacent to the inlet camshaft during cam engagement, the push rod being additionally around the eccentric of the exhaust camshaft by the cam engagement with the oblique contact track in the direction of the valve opening is pivoted to keep the inlet valve open.

Eine variable Ventilöffnungsperiode ist mit dieser Vorrichtung weder beabsichtigt noch kinematisch möglich, weil der kreisbogenförmige Endabschnitt der Schubstange wegen ihrem translatorischen Bewegungsanteil mit einer ebenen Gegenfläche des als Stößel gestalteten Übertragungselementes zusammenwirken muß.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.

Aus der GB-PS 955 988 ist demgegenüber eine zur Änderung der Ventilöffnungsperiode bei systembedingt in geringen Grenzen veränderlichem Ventilhub geeignete Ventilsteuerung bekannt. Bei dieser bekannten Ventilsteuerung ist als Übertragungsglied ein Stößel vorgesehen in einer Führung, die mittels einer Steuervorrichtung drehzahlabhängig um eine zur Nockenwelle parallele Achse kippbar ist. Der mit einer ebenen Kontaktbahn versehene Stößel ist sowohl in als auch gegen die Drehrichtung der Nockenwelle kippbar, wodurch Ventilhubverläufe mit unterschiedlichen Ventilöffnungsperioden erreicht sind. Die Steuervorrichtung umfaßt für das drehzahlabhängige, relativ zur Drehrichtung der Nockenwelle gleich- und gegensinnige Kippen der Führung einem mit der Nockenwelle umlaufenden, außermittig angeordneten Bolzen, der mit an der Stößel-Führung angeordneten, relativ steifen aber elastisch biegbaren Steuerarmen zusammenwirkt.GB-PS 955 988, on the other hand, 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. In this known valve control, 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 control device for the speed-dependent, relative to the direction of rotation of the camshaft in the same and opposite directions tilting of the guide a rotating with the camshaft, eccentrically arranged bolt which interacts with arranged on the tappet guide, relatively stiff but elastically bendable control arms.

Zur Kontrolle des drehzahlabhängigen Kippens steht die Führung mit einem nachgiebigen Anschlag in Verbindung, wobei der Anschlag bei niedrigen Maschinendrehzahlen ein Kippen der Führung mit dem Stößel über die dabei relativ unnachgiebigen Steuerarme zur Verringerung der Ventilöffnungsperiode mit einer möglichen Eleminierung der Ventilüberschneidungen ermöglicht. Dagegen hält der Anschlag bei hohen Maschinendrehzahlen die Führung mit dem Stößel in einer nicht gekippten Position, wobei die Steuerarme dem anlaufenden, exzentrisch angeordneten Bolzen biegeelastisch ausweichen.To control the speed-dependent tilting, 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. In contrast, 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.

Nachteilig bei dieser bekannten Ventilsteuerung sind die zur drehzahlabhängigen Kippsteuerung vorgesehenen biegeelastischen Steuerarme der Steuervorrichtung, die bei einer mehrzylindrigen Brennkraftmaschine über sämtliche Zylinder zu unterschiedlichen Ventilöffnungsperioden bei ein und derselben Drehzahl führen und damit Leistung und Abgasqualität nicht akzeptablen Schwankungen unterliegen.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.

Weiter ist aus der GB-PS 649192 eine Ventilsteuerung zur gezielten last- und drehzahlabhängigen Änderung der Ventilöffnungswinkel eines Gaswechselventils bekannt. Diese bekannte Ventilsteuerung unterscheidet sich von der vorbeschriebenen Ventilsteuerung dadurch, daß die Nockenwelle mit einem exzentrisch angeordneten Mitnehmer ausgerüstet ist zum radial beweglichen Eingriff in einen Radialschlitz eines von der Nockenwelle gesonderten Antriebsrades. Zur Änderung der Ventilöffnungswinkel wird das Antriebsrad relativ zur Nockenwelle in einer Querrichtung verlagert mit der Folge eines bei konstant drehendem Antriebsrades ungleichförmiger Drehgeschwindigkeiten der über den Mitnehmer gekuppelten Nockenwelle. Diese auf dem Prinzip der ständig ungleichförmigen Drehgeschwindigkeiten durch gezielte Desachsierung der mit einander drehend gekuppelten Bauteile beruhenden Ventilsteuerung ist in nachteiliger Weise bauaufwendig.From GB-PS 649192 there is a 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. To change the valve opening angle, 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.

Der Erfindung liegt die Aufgabe zugrunde, für eine gattungsgemäße Ventilsteuerung eine Steuervorrichtung zur Änderung der Ventilöffnungsperioden bei systembedingt in Grenzen veränderlichen Ventilhub aufzuzeigen, daß so bei geringem Bauaufwand eine exakte Steuerung erzielt ist.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.

Diese Aufgabe ist mit den Merkmalen des Patentanspruches 1 gelöst. Der Vorteil der im Anspruch 1 im Prinzip beschriebenen Erfindung ist in einer genauen Steuerung zur Änderung der Ventilöffnungsperioden bei konstant drehenden Nocken- und Steuervorrichtungswellen zu sehen, wobei die genaue Steuerung mittels einer zwangsgesteuerten Antriebsverbindung zwischen den gleichförmig drehenden Nocken- und Steuervorrichtungswellen erzielt ist. Dies ergibt den weiteren Vorteil, daß bei Änderung der Phasenlage der Steuerwelle der Steuervorrichtung relativ zur Nockenwelle aufgrund fehlender Drehungleichförmigkeiten Belastungsspitzen in der Ventilsteuerung vermieden sind.This object is achieved with the features of claim 1. The advantage of the invention described in principle in claim 1 is to be seen in a precise control for changing the valve opening periods with constantly rotating cam and control device shafts, the precise control being achieved by means of a positively controlled drive connection between the uniformly rotating cam and control device shafts. This has the further advantage that when the phase position of the control shaft of the control device changes relative to the camshaft, stress peaks in the valve control are avoided due to the lack of rotational irregularities.

In ersten Ausgestaltungen der Erfindung ist in den Ansprüchen 2 und 3 sowie im Anspruch 4 jeweils eine Ventilsteuerung angegeben, bei der das zwischen dem Steuernocken und dem ventilseitigen Übertragungsglied angeordnete Zwischenelement ein in einem zur Achse der Nockenwelle konzentrischen Kreisbogenabschnitt beweglich gelagertes Kippsegment ist. Der Unterschied der beiden Ausgestaltungen liegt in dem jeweils relativ zur Ventilhubrichtung angeordneten starren Steuerarm. Bei der nach den Ansprüchen 2 und 3 getroffenen Ausgestaltung ist der starre Steuerarm am Kippsegment quer zur Ventilhubrichtung sich erstreckend ausgebildet zum vorteilhaften Einsatz eines im Aufbau einfachen Kurvenscheiben- bzw. Exzenter-Getriebes zur Zwangssteuerung des vorzugsweise in einem Stößel über den zur Nockenwelle konzentrischen Kreisbogenabschnitt beweglich gelagerten Kippsegmentes.In the first embodiments of the invention, 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. In the embodiment made according to claims 2 and 3, 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.

Aus der DE-A 39 20 895 ist zwar auch ein relativ zum Stößel zwangsgesteuertes Zwischenelement bzw. Kippsegment bekannt, das jedoch als Teil einer durchschlagenden Viergelenkkette über eine Koppel von einem Kurbelgetriebe gesteuert mit einer ebenen Kontaktbahn des Stößels zusammenwirkend der Hubänderung des Stößels bei gleichzeitiger Änderung der Ventilöffnungsperiode des vom Stößel beaufschlagten Gaswechselventils dient. Demgegenüber ist das erfindungsgemäß zwangsgesteuerte Kippsegment Teil einer Schubschleifenkette, bei der bekanntlich jedes Getriebeglied je ein Dreh- und ein Schubgelenk aufweist. In der erfindungsgemäß angewandten Schubschleifenkette ist die eine Gelenkpaarung aus dem hubbetätigten Stößel mit dem um die Achse der Nockenwelle über den konzentrischen Kreisbogenabschnitt im Stößel geführten Kippsegment gebildet, dessen starrer, gabelartiger Steuerarm mit der Kurbelscheibe bzw. mit dem Exzenter die zweite Gelenkpaarung bildet. Diese so gestaltete Schubschleifenkette ermöglicht gegenüber dem vorgenannten Stand der Technik bei kinematisch systembedingtem, in engen Grenzen abweichendem Ventilhub und abweichender Spreizung eine vorrangige Änderung der Ventilöffnungsperiode.From DE-A 39 20 895, 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. In contrast, 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. In the push-loop chain used according to the invention, 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. This shear loop chain designed in this way enables a priority change in the valve opening period in relation to the aforementioned prior art in the case of a kinematic system-dependent valve stroke which differs within narrow limits and a different spread.

Das nach Anspruch 4 gestaltete Beispiel eines Kippsegmentes mit in Ventilhubrichtung gerichteten starrem Steuerarm ermöglicht zur Zwangssteuerung des Kippsegmentes ebenfalls die Verwendung eines umlaufenden Kurbel- oder Exzenter-Getriebes. Der Unterschied zum Stand der Technik nach der vorerwähnten DE-A 39 20 895 ist die Lagerung des Kippsegmentes im jeweiligen Übertragungsglied in einem zur Achse der Nockenwelle konzentrischen Kreisbogenabschnitt zur überwiegenden Änderung der Ventilöffnungsperiode.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.

Ein bevorzugtes Ausführungsbeispiel der im Anspruch 1 prinzipiell dargestellten Erfindung ist in den Ansprüchen 5 mit 10 beschrieben. Anstelle des bislang als Kippsegment beschriebenen Zwischenelementes ist dieses nach Anspruch 5 als eine im/am Übertragungsglied längs des konzentrischen Kreisbogenabschnittes verschiebbar angeordnete Rolle ausgebildet, die im Gegensatz zu der bekannten Vorrichtung zur Änderung der Nockenspreizung nach der CH-PS 390 617 (= GB-PS 969 297) bei jedem Ventilhub mittels einer Schubstange eines mit der Nockenwelle synchron drehenden, drehwinkelverstellbaren Kurbel- oder Exzenter-Getriebes der Steuervorrichtung zwischen dem Steuernocken und dem jeweiligen Übertragungsglied - Stößel oder Ventilhebel - quer zur Ventilhubrichtung relativ zum drehenden Steuernocken synchron zwangsgesteuert gleich- und gegensinnig angetrieben ist.A preferred embodiment of the invention shown in principle in claim 1 is described in claims 5 to 10. Instead of the intermediate element previously described as a tilting segment, it is designed according to claim 5 as a roller which is displaceably arranged in / on the transmission element along the concentric circular arc section and which, in contrast to the known device for changing the cam spread according to CH-PS 390 617 (= GB-PS 969 297) with each valve stroke by means of a push rod of a crank or eccentric gear mechanism of the control device, which rotates synchronously with the camshaft and is adjustable in terms of angle of rotation, between the control cam and the respective transmission element - tappet or valve lever - transversely to the valve stroke direction relative to the rotating control cam, synchronously and in the same direction in opposite directions is driven.

Bei der erfindungsgemäßen Ventilsteuerung wird in einer vorbestimmten Drehwinkelzuordnung der synchron zur Nockenwelle drehenden Steuerwelle der Steuervorrichtung die übertragungsgliedseitig angeordnete Rolle relativ zum einwirkenden Steuernocken mit dessen Drehrichtung gesteuert mitbewegt und in einer dazu entgegengesetzten Drehwinkelzuordnung wird die Rolle relativ zum einwirkenden Steuernocken entgegen dessen Drehrichtung gesteuert bewegt. Mit der relativ zum Steuernocken gleichsinnig gesteuert angetriebenen Rolle im Übertragungsglied ergibt sich ein Ventilhubverlauf mit großem Ventilöffnungswinkel bzw. langer Ventilöffnungsperiode, wie er vorteilhaft für eine hohe Leistungsentfaltung der Brennkraftmaschine ist. Die demgegenüber relativ zum Steuernocken gegensinnig gesteuert angetriebene Rolle im Übertragungsglied hat einen Ventilhubverlauf mit kleinem Ventilöffnungswinkel bzw. kurzer Ventilöffnungsperiode zur Folge, wodurch sich insbesondere bei niederer Drehzahl der Brennkraftmaschine ein vorteilhafter Betrieb ergibt.In the valve control according to the invention, in a predetermined rotation angle assignment of the control shaft rotating synchronously with the camshaft of the control device, 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. With 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. In contrast, 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.

Die erfindungsgemäß relativ zur Drehrichtung des Steuernockens gleichsinnig verlagerbare Rolle im Übertragungsglied ergibt für die Berührungslinie zwischen Steuernocken und Kontaktbahn der Rolle gegenüber einer feststehend angeordneten Rolle eine geringere Absolutgeschwindigkeit, der bei konstanter Drehzahl der Nockenwelle ein großer Ventilöffnungswinkel entspricht. Bei gegensinnig verlagerter Rolle wird die Kontur des Steuernockens rascher dem Übertragungsglied und damit dem jeweiligen Gaswechselventil übermittelt. Für die Berührungslinie ergibt sich somit eine hohe Absolutgeschwindigkeit, der bei konstanter Nockenwellen-Drehzahl ein kleiner Ventilöffnungswinkel entspricht.According to the invention, 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.

Zu dieser erfindungsgemäßen Änderung der Ventilöffnungswinkel eines Gaswechselventils sind der vorgenannten CH-PS 390 617 weder Anregungen noch Hinweise zu entnehmen, da die zwar über einen Exzenter schubstangengesteuerte Rolle zwischen dem Steuernocken und dem Kreisbogenabschnitt des Stößels lediglich diskontinuierlich zur gleichzeitigen Verstellung des Öffnungs- und Schließzeitpunktes des Ventils verstellt wird. Erreicht ist damit lediglich eine Änderung der Nockenspreizung, wie dies auch bei modernen Vorrichtungen zur direkten Drehwinkeländerung der Nockenwelle relativ zur Kurbelwelle üblich ist.For this change of the valve opening angle of a gas exchange valve according to the invention, the aforementioned CH-PS 390 617 neither suggests nor gives any hints, since the roller controlled by an eccentric rod between the control cam and the arc section of the tappet is only discontinuous for simultaneous adjustment of the opening and closing times of the Valve is adjusted. All that is achieved is a change in the cam spread, as is also customary in modern devices for directly changing the angle of rotation of the camshaft relative to the crankshaft.

Die Ventilsteuerung der vorerwähnten CH-PS 390 617 entspricht zwar wie die beanspruchte Ventilsteuerung kinematisch einer Schubschleifenkette, die aber wegen betriebspunktabhängiger Anpassung der Nockenspreizung bei unveränderten Öffnungs- und Schließzeitpunkten des jeweiligen Ventils lediglich diskontinuierlich bzw. bedarfsweise gesteuert beeinflußt ist. Demgegenüber ermöglicht die Ventilsteuerung der weiter vorne erwähnten GB-PS 649 192 zwar eine betriebspunktabhängige Änderung der Ventilöffnungswinkel eines Gaswechselventils, die jedoch kinematisch abweichend mit einer umlaufenden Kurbelschleife erzielt ist, bei der zwei um zueinander parallel versetzte Achsen drehende Getriebeglieder mittels eines Schubgelenkes gekoppelt sind. Da im Gegensatz hierzu die Getriebeglieder einer Schubschleifenkette je ein Dreh- und ein Schub-Gelenk umfassen, ist eine Kombination der Gegenstände der beiden o.g. Dokumente weder kinematisch sinnvoll, noch führt sie in naheliegender Weise zu der erfinderischen Ventilsteuerung, mittels gezielter Änderung der Absolutgeschwindigkeiten der Berührungslinie zwischen Steuernocken und Zwischenelement durch zur Nockenwelle synchrone Steuerung des Zwischenelementes die Ventilöffnungswinkel betriebspunktabhängig zu ändern.The 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. In contrast, the 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. In contrast to this, since the transmission links of a push-loop chain each comprise a rotary and a push-joint, a combination of the objects of the two documents mentioned above is neither kinematically meaningful, nor does it lead to the inventive valve control in an obvious manner by means of a targeted change in the absolute speeds of the contact line to change the valve opening angle depending on the operating point between the control cam and the intermediate element by controlling the intermediate element synchronously with the camshaft.

In bevorzugter Weiterbildung der im Anspruch 5 beschriebenen Ausführung der Erfindung ist die relativ zum Steuernocken synchron gleich- und gegensinnig gesteuerte Rolle gemäß Anspruch 6 an einem Ventilhebel vorgesehen, vorzugsweise an einem Schlepphebel. Im Vergleich mit einem üblichen Rollen-Schlepphebel kennzeichnet sich der erfindungsgemäß gestaltete Schlepphebel durch eine vorteilhaft niedrige Bauweise. Dem Vorteil der niedrigen Bauweise, insbesondere für einen Zylinderkopf, ist weiter förderlich die Gestaltung der die Rollen verlagernden Schubstangen, die durch eine gabelartige Gestaltung die Schlepphebel in Längsrichtung umfassen für eine zumindest in der Grundkreisphase des Steuernockens im wesentlichen fluchtende Anordnung. Diese in einer Ebene eines Zylinderkopfes vorteilhafte Anordnung von Schlepphebel und Rollen-Schubstange ergibt neben kinematischen Vorteilen der Steuervorrichtung insbesondere kinetische Vorteile mit der weiteren Ausgestaltung nach Anspruch 7. Die darin beschriebene Zuordnung der Rollen-Umkehrpunkte zu Exzenter-Totpunktstellungen der Steuerwelle der Steuervorrichtung ergibt mit zunehmender Anzahl der Exzenter bei einem mehrventiligen Brennraum und/oder einer mehrzylindrigen Brennkraftmaschine ein durch Ausgleich entgegengesetzt wirkender Drehmomente in der Summe ein vorteilhaft ausgeglichenes Gesamtdrehmoment. Dies ermöglicht in weiterer vorteilhafter Weise eine einfache und leichtbauende phasenlagensteuerbare Mitnahmeeinrichtung für die Steuerwelle vorzusehen. Eine bevorzugte Ausgestaltung der Mitnahmeeinrichtung ist im Anspruch 8 beschrieben.In a preferred development of the embodiment of the invention described in claim 5, 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. In comparison with a conventional roller 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. This advantageous arrangement of rocker arm and roller push rod in one plane of a cylinder head results in addition to kinematic advantages of the control device, in particular kinetic advantages with the further embodiment according to claim 7. The assignment of the roller reversal points to eccentric dead center positions of the control shaft of the control device described therein With an increasing number of eccentrics in a multi-valve combustion chamber and / or a multi-cylinder internal combustion engine, a torque acting by counteracting in total counteracts an advantageously balanced overall torque. In a further advantageous manner, this makes it possible to provide a simple and lightweight phase-position-controllable driving device for the control shaft. A preferred embodiment of the driving device is described in claim 8.

In einer Brennkraftmaschine, bei der sowohl die Einlaßals auch die Auslaßventile mit erfindungsgemäß mit gesteuerten Rollen ausgerüsteten Schlepphebeln zusammenwirken, können die einlaßseitigen sowie die auslaßseitigen Rollen-Schubstangen jeweils mittels einer gesonderten Steuerwelle angetrieben sein. Gesonderte Steuerwellen an sich für steuerbare Kipphebel zur Änderung des Öffnungszeitpunktes beim Auslaßventil und zur Änderung des Schließzeitpunktes beim Einlaßventil sind aus der US-PS 2 880 712 bekannt.In an internal combustion engine in which both the inlet and the outlet valves cooperate with finger levers equipped with controlled rollers according to the invention, 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.

Eine hinsichtlich geringem Bauraum und kleinem Bauaufwand vorteilhafte Ventilsteuerung mit einer einzigen, erfindungsgemäß gestaltete Rollen-Schlepphebel für Ein- und Auslaß-Ventile betätigenden Nockenwelle ist gemäß Anspruch 9 dadurch erreicht, daß eine einzige, mit Exzenter besetzte, drehwinkelverstellbare Steuerwelle über gabelartige Schubstangen sowohl die Rollen der Einlaß-Schlepphebel als auch die Rollen der Auslaß-Schlepphebel relativ zu den jeweiligen Steuernocken der Nockenwelle synchron gleich- und gegensinnig steuert.An advantageous in terms of small space and small construction valve control with a single, according to the invention designed cam follower for intake and exhaust valve actuating camshaft is achieved according to claim 9 in that a single, eccentric, angularly adjustable control shaft via fork-like push rods both the roles the inlet rocker arm and the rollers of the exhaust rocker arm control synchronously in the same and opposite directions relative to the respective control cam of the camshaft.

Diese Steuerungsanordnung läßt sich besonders vorteilhaft bei einem Querstrom-Zylinderkopf mit ohc-Anordnung gemäß Anspruch 10 im Bereich oberhalb der im allgemeinen abgewinkelt verlaufenden Gaswechsel-Auslaßkanäle vorsehen, wodurch bei diesem Zylinderkopf die Einlaßkanäle optimal gestaltet werden können.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.

Die Erfindung ist anhand von in der Zeichnung zum Teil schematisch dargestellten Ausführungsbeispielen beschrieben. Es zeigt

Figur 1
eine erste Ventilsteuerung mit einem Stößel, der nockenseitig mit einem Kippsegment ausgerüstet ist,
Figur 2
eine zweite, schematisch dargestellte Ventilsteuerung mit einem gegenüber Figur 1 abgewandelten Kippsegment,
Figur 3
eine dritte Ventilsteuerung mit erfindungsgemäß gestalteten Schlepphebeln in perspektivischer Ansicht,
Figur 4
die Ventilsteuerung nach Figur 3 mit einer in Explosionsdarstellung gezeigten Mitnahmeeinrichtung, und in
Figur 5
Hubkurven für Ein- und Auslaß-Ventile bei geänderten Öffnungs- und Schließzeitpunkten, erzielt mit einer der o.g. Ventilsteuerungen.
The invention is described with reference to exemplary embodiments which are shown schematically in part in the drawing. It shows
Figure 1
a first valve control with a tappet which is equipped on the cam side with a tilting segment,
Figure 2
2 shows a second, schematically illustrated valve control with a tilting segment which is modified compared to FIG. 1,
Figure 3
A third valve control with rocker arms designed according to the invention in a perspective view,
Figure 4
3 with a driving device shown in an exploded view, and in
Figure 5
Stroke curves for intake and exhaust valves with changed opening and closing times, achieved with one of the above-mentioned valve controls.

In Figur 1 ist mit 1 eine Ventilsteuerung für ein nicht gezeigtes Gaswechselventil einer Brennkraftmaschine bezeichnet. Die Ventilsteuerung 1 umfaßt eine Nockenwelle 2 mit einem Steuernocken 3, der auf eine Kontaktbahn 4 eines Stößels 5 einwirkt zum Öffnen und Schließen des nicht gezeigten Gaswechselventils.In FIG. 1, 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.

Die Kontaktbahn 4 ist ausgebildet an einem im Stößel 5 in einem zur Nockenwelle 2 konzentrischen Kreisbogenabschnitt 5' kippbeweglich gelagerten Kippsegment 6, das Teil einer Steuervorrichtung 7 zur Änderung der Ventilöffnungsperiode bei systembedingt im wesentlichen konstantem Hub des Gaswechselventils ist. Am Kippsegment 6 ist ein starrer Steuerarm 8 quer zur Ventilhubrichtung angeordnet, der über zwei gabelartige, freie Endabschnitte 9 und 10 mit einer als Exzenter 11 gestalteten Kurvenscheibe 12 in zwangsgesteuerter bzw. desmodromischer Antriebsverbindung steht.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. On the tilting segment 6, 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.

Der Exzenter 11 steht mit einer gesonderten Welle 13 in drehfester Verbindung, wobei die Welle 13 über ein Antriebsrad 14 von einem Abtriebsrad 15 der Nockenwelle 2 ständig synchron angetrieben ist. Mit dem Antriebsrad 14 steht die Exzenter-Welle 13 über eine beliebige, nicht gezeigte Mitnahmeeinrichtung in kuppelbarer Verbindung derart, daß die Phasenlage des Exzenters 11 relativ zur Nockenwelle 2 zwecks Änderung der Ventilöffnungsperiode gesteuert jeweils um ca. 180° in einer Richtung von I nach II und schließlich von II weiter nach I fortschreitend veränderbar ist. Die der Änderung der Ventilöffnungsperioden bei Ventilhubkurven mit systembedingt in Grenzen veränderbarem Ventilhub dienende Kippsteuerung des Kippsegmentes 6 ist der aus dem Ventilhub des Stößels 5 und dem steuervorrichtungsseitig abgestützten Steuerarm 8 erzwungenen Kippbewegung überlagert. Das Maß der überlagerten Kippbewegung bestimmt sich im wesentlichen aus dem Hebelabstand des Steuerarmes 8 und dem Hub des Exzenters 11, der relativ zur Welle 13 auch hubverstellbar ausgebildet sein kann für weitere unterschiedliche Ventilöffnungsperioden.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. With the 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.

Bei der in Figur 2 schematisch dargestellten Ventilsteuerung 16 wirkt ein Steuernocken 17 einer Nockenwelle 18 mit der Kontaktbahn 19 eines in einem Übertragungsglied 20 - Stößel oder Ventilhebel - über einen zur Nockenwelle 18 konzentrischen Kreisbogenabschnitt 21 gelagerten Kippsegmentes 22 zusammen. Das Kippsegment 22 ist mit einem neben dem Übertragungsglied 20 in Ventilhubrichtung etwa parallelen, starren Steuerarm 23 ausgerüstet, an dem eine Schubstange 24 eines mit der Nockenwelle 18 synchron drehenden, drehwinkelverstellbaren Kurbel- oder Exzenter-Getriebes 25 gelenkig angreift.In the valve control 16 shown schematically in FIG. 2, 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.

Eine in den Figuren 3 und 4 gezeigte Ventilsteuerung 26 umfaßt zur Betätigung eines Einlaßventiles 27 und eines Auslaßventiles 28 eine gemeinsame Nockenwelle 29 mit einem Einlaß-Steuernocken 30 und einem Auslaß-Steuernocken 31, die jeweils über eine Rolle 32 mit einer Kontaktbahn 32' auf einen entsprechenden Schlepphebel 33 einwirken. Jede der Rollen 32 ist im jeweiligen Schlepphebel 33 zwischen Stegen 34 angeordnet, die zur Achse der Nockenwelle 29 konzentrische Kreisbogenabschnitte 35 aufweisen. Diese Kreisbogenabschnitte 35 dienen als Führungsbahnen für Tragbolzen 36 der Rollen 32. An jedem Tragbolzen 36 greifen beidendig beiderseits des jeweiligen Schlepphebels 33 angeordnete Arme 37 einer gabelartig gestalteten Schubstange 38 an. Jede der Schubstangen 38 steht mit einem Exzenter 39 einer zur Nockenwelle 29 synchron angetriebenen, drehwinkelverstellbaren Welle 40 einer Steuervorrichtung 41 in Antriebsverbindung.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.

Wie aus Figur 3 ersichtlich, dient eine einzige Exzenter-Welle 40 zur Steuerung der Rollen 32 in den einlaß- und auslaß-seitigen Schlepphebeln 33. Die einzige Exzenter-Welle 40 der Steuervorrichtung 41 ist bei einem lediglich angedeuteten Querstrom-Zylinderkopf 42 mit ohc-Anordnung vorzugsweise auslaßseitig oberhalb der üblicherweise stark gekrümmten Gaswechsel-Auslaßkanäle 43 angeordnet. Diese einen geringen Einbauraum erfordernde Anordnung ermöglicht in vorteilhafter Weise eine in der Grundkreisphase des jeweiligen Steuernockens 30, 31 in etwa fluchtende Anordnung von Schlepphebel 33 und Schubstange 38. Diese Zuordnung läßt sich dahingehend vorteilhaft nutzen, daß ein Umkehrpunkt der Rolle 32 in einem Endbereich der übertragungsglied- bzw. schlepphebelseitigen Kreisbogenabschnitte 35 vom gleich- zum gegensinnigen Antrieb und vice versa sowie eine der beiden um 180° versetzten Extremstellungen des die Schubstange 38 steuernden Exzenters 39 auf einer die Achse der Exzenter-Welle 40 im wesentlichen schneidenden Geraden angeordnet sind. Der jeweilige Steuernocken 30, 31 ist hierbei zur jeweiligen Geraden in einer quergerichteten Stellung.As can be seen from FIG. 3, 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.

Kinematisch ist damit in vorteilhafter Weise im wesentlichen ein harmonischer Antrieb jeder Rolle 32 mit den geringsten, durch die Lenkbewegungen der Schubstange 38 bedingten Abweichungen an Ventilhub und Spreizung erzielt. Kinetisch günstig wirkt sich diese Anordnung bei einer Welle 40 mit für viele Gaswechselventile eines mehrventiligen Brennraumes und/oder einer mehrzylindrigen Brennkraftmaschine vorgesehene Exzenter aus, womit durch Ausgleich entgegengesetzt wirkender Drehmomente in der Summe ein vorteilhaft ausgeglichenes Gesamtdrehmoment an der Exzenterwelle 40 erreicht ist.Kinematically, 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.

Dieses ausgeglichene Gesamtdrehmoment ist von wesentlicher Bedeutung für eine der Exzenter-Welle 40 zugeordnete, phasenlagensteuerbare Mitnahmeeinrichtung 44. Wie die Figuren 3 und 4 zeigen, ist die Exzenter-Welle 40 über ein Zahnradgetriebe 45 zur Nockenwelle 29 synchron angetrieben. Aus Figur 4 ist ersichtlich, daß die Mitnahmeeinrichtung 44 dem Zahnrad 46 auf der Exzenter-Welle 40 zugeordnet ist. Die Mitnahmeeinrichtung 44 umfaßt zwei mit der Exzenter-Welle 40 drehfest verbundene und in festem axialem Abstand angeordnete Anschlagträger 47 und 48 mit je einem Mitnehmer-Anschlag 49 und 50. Ferner einen auf der Exzenter-Welle 40 zwischen den Anschlagträgern 47 und 48 - Zahnrad 46 ist hierbei zugleich der Anschlagträger 47 - drehfest, jedoch axial verschiebbar vorgesehenen Arm 51 zur Mitnahme über einen der um einen vorbestimmten Dreh- bzw. Phasen-Winkel - vorzugsweise um ca. 180° - versetzten Anschläge 49 und 50.This balanced total torque is of essential importance for a phase position controllable driving device 44 assigned to the eccentric shaft 40. As FIGS. 3 and 4 show, the eccentric shaft 40 is driven synchronously via a gear transmission 45 to the camshaft 29. From Figure 4 it can be seen that 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. Furthermore, 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 °.

Zur Drehwinkelverstellung der Exzenter-Welle 40 relativ zur Nockenwelle 29 ist der Arm 51 durch eine gesteuerte, axiale Verlagerung außer Eingriff mit einem der antriebsfesten Anschläge 49, 50 gebracht und anschließend der in Drehrichtung antriebslose Arm 51 vom anderen Anschlag 50 bzw. 49 zur Drehmitnahme beaufschlagt. Diese klein, leicht und einfach gebaute Mitnahmeeinrichtung 44 resultiert auf der vorteilhaft gewählten Lage der Exzenter-Welle 40 zu den in den Schlepphebeln 33 längs Kreisbogenabschnitten 35 gleich- und gegensinnig relativ zu den drehenden Steuernocken 30, 31 synchron verlagerten Rollen 32.To adjust the angle of rotation of the eccentric shaft 40 relative to the camshaft 29, 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.

Gemäß Figur 5 ist es bevorzugtes Ziel der Erfindung, mit jeder der vorbeschriebenen Ventilsteuerungen bei einer Brennkraftmaschine in niedrigen Drehzahlen kleine Ventil-Öffnungswinkel mit geringer oder kleiner Überschneidung und in hohen Drehzahlen große Ventil-Öffnungswinkel mit viel Überschneidung zur Ausbildung einer hohen Gasdynamik zu erreichen. Unter den in Figur 5 gezeigten Einlaß- und Auslaß-Ventilhubkurven entsprechen die mit durchgehenden Linien dargestellten Ventilhubkurven dem Hubprofil des jeweiligen Steuernockens. Diese sind mit der erfindungsgemäßen Ventilsteuerung bei gleichsinnig synchron zum jeweiligen Steuernocken gesteuertem Zwischenelement in Richtung großer Ventilöffnungswinkel entsprechend den punktiert dargestellten Ventilhubkurven änderbar und bei gegensinnig synchron gesteuertem Zwischenelement in Richtung kleiner Ventil-Öffnungswinkel entsprechend den strichliert dargestellten Ventilhubkurven.According to FIG. 5, it is a preferred aim of the invention to achieve small valve opening angles with little or little overlap at low speeds and large valve opening angles with a lot of overlap at high speeds with each of the above-described valve controls in an internal combustion engine to form a high gas dynamic. Under the inlet and outlet valve lift curves shown in FIG. 5, the valve lift curves shown with solid lines correspond to the lift profile of the respective control cam. These can be changed with the valve control according to the invention with the intermediate element controlled in the same direction synchronously with the respective control cam in the direction of large valve opening angles in accordance with the valve lift curves shown in dotted lines and with counter-synchronously controlled intermediate element in the direction of small valve opening angles in accordance with the valve lift curves shown in broken lines.

Die erfindungsgemäße Ventilsteuerung kann bei Bedarf mit einer gesonderten Einrichtung zur gezielten Ventilhubänderung und/oder zur gezielten Spreizungsänderung kombiniert werden. Dies eröffnet die Möglichkeit, durch eine jeweils unabhängige Ansteuerung der jeweiligen Einrichtung eine Ventilsteuerung optimal einem jeweiligen Betriebspunkt der Brennkraftmaschine anpassen zu können.If necessary, the 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.

Claims (10)

  1. A valve control system for an internal combustion engine
    - wherein a control cam (3, 17, 30, 31) on a camshaft (2, 18, 29) acts via an intermediate element (6, 22, 32) and a transmission member (5, 20, 33) on a gas change valve (27, 28) so as to bring about the stroke, wherein
    - the intermediate element (6, 22, 32) is disposed so as to be driven in motion via a contact path (4, 19, 32') acted upon by the control cam (3, 17, 30, 31) during each valve stroke relative to the rotating control cam (3, 17, 30, 31) and to the transmission member (5, 20, 33),
    characterised in that
    - the intermediate element (6, 22, 32) is disposed so as to be guided in motion in/on the transmission member (5, 20, 33) via an arcuate portion (5', 21, 35) substantially concentric with the axis of the camshaft (2, 18, 29) and
    - is in driving connection with a shaft of a control device (7, 41) rotating in synchronism with the camshaft (2, 18, 29) and having an adjustable angle of rotation relative to the said camshaft (2, 18, 29), in such a way that
    - during each valve stroke, engagement between the contact path (4, 19, 32') and the flanks of the rotating control cam (3, 17, 30, 31), such engagement determining the valve opening phase, is obtained by a mechanically controlled movement of the intermediate element (6,22,32) in the same or opposite direction to the direction of rotation of the control cam (3, 17, 30, 31).
  2. A valve control system according to claim 1, characterised in that
    - the contact path (4) is formed on a tilting segment (6) connected for motion to the transmission member (5) via the arcuate portion (5') and with a rigid control arm (8) extending at an angle to the direction of the valve stroke,
    - the free end portion (9, 10) of the arm co-operating with a cam plate (12 or 11) rotating in synchronism with the camshaft (2) and belonging to the control device (7) so as to control the tilting of the tilting segment (6) in such a way that
    - the tilting motion of the tilting segment (6), determined by the stroke of the transmission member (5) and by the control arm (8), which is supported on the side of the control device, is additionally variable by means of the cam plate (12).
  3. A valve control system according to claim 2, characterised in that
    - the control arm (8) has two forked projecting end portions (9, 10) between which a cam plate (12) in the form of an eccentric (11) is driven in rotary motion via a shaft (13) driven in synchronism by the camshaft (2), wherein
    - the phase position of the eccentric (11) relative to the camshaft (2) is variable by a predetermined angle of rotation (e.g. about 180°) by means of a synchronising device (I - II - I) which is controllable in phase positions and is provided in the drive connection between the shaft (13) and the camshaft (2).
  4. A valve control system according to claim 1, characterised in that
    - the contact path (19) is formed on a tilting segment (22) connected in movable manner to the transmission member (20) via the arcuate portion (21) and with a rigid control arm (23) parallel in the valve stroke direction,
    - a connecting rod (24) of a crank or eccentric drive (25) of the control device and having an adjustable angle of rotation and rotating in synchronism with the camshaft (18) pivotably engages the control arm, and
    - the axis of the drive (25) is provided at about half the stroke of the transmission member (20).
  5. A control device system according to claim 1, characterised in that
    - the intermediate element with a contact path (32') is a roller (32) guided for movement in/on the transmission member (33) along concentric arcuate portions (35), and
    - at each valve stroke the roller is driven by a connecting rod (38) of a crank drive or eccentric drive (39, 40) at an adjustable angle of rotation and rotating in synchronism with the camshaft (29) and belonging to the control device (41), between the control cam (30, 31) and the transmission member (33) at an angle to the valve stroke direction relative to the rotating control cam (30, 31), synchronised and mechanically controlled in the same and in the opposite direction.
  6. A valve control system according to claim 1 and 5, characterised in that
    - the transmission member is a valve lever (33) with a roller (32) disposed on a bearing pin (36) between webs (34) on the lever side,
    - the roller being movable along the concentric arcuate portions (35) serving as guide tracks for the bearing pin (36) in the webs (34) by means of the connecting rod (38) of the eccentric drive (39, 40) engaging the bearing pin (36), in the same and in the opposite direction, wherein
    - the arms (37) of the forked connecting rod (38), disposed on each side of the valve lever (33), engage the two ends of the bearing pin (36).
  7. A valve control system according to claim 5 and 6, characterised in that
    - the transmission member (33) bearing the roller (32) and the shaft (40) comprising the eccentric (39) are associated with one another in such a manner that
    - a reversal point of the roller (32) in an end region of the arcuate portion (35) on the transmission-member side from driving in the same to driving in the opposite direction and vice versa, and one of the two extreme positions, offset by 180°, of the eccentric (39) controlling the connecting rod (38) are disposed on a straight line substantially intersecting the axis of the eccentric shaft (40), and
    - a synchronising device (44) controllable as to phase position is shiftable in a drive connection of the eccentric shaft (40) by means of the camshaft (29).
  8. A valve control system according to one or more of claims 1 to 7, characterised in that
    - the synchronising device (44) comprises two abutment-holders (47, 48) disposed non-rotatably and with a fixed axial spacing on the shaft (40) of the respective control device and each with a driving abutment (49, 50), and
    - an arm (51) provided non-rotatably and axially movably on the shaft (40) between the abutment-holders (47, 48) for synchronising via one of the abutments (49, 50) offset by a predetermined angle of rotation or phase angle (e.g. about 180°), wherein
    - for the purpose of adjusting the angle of rotation of the shaft (40), the arm (51) can be brought by a controlled axial displacement out of engagement with one of the abutments (49, 50) secured to the drive, after which the arm (51), which is not driven in the direction of rotation, is acted upon by the other abutment (50, 49) secured to the drive, so as to be driven in rotation.
  9. A valve control system according to claims 5 to 8, characterised in that
    - a camshaft (29) common to the drag levers (33) provided as transmission members for inlet and exhaust valves (27, 28) acts via each control cam (30, 31) on each drag lever (33) via a roller (32) disposed in the lever and constantly controlled in synchronism in the same and in the opposite direction to the camshaft (29), wherein
    - a single shaft (40) of the control device (41) adjustable as to angle of rotation and rotating in synchronism with the camshaft (29) and with an eccentric (39) is provided for the rollers (32), controlled by connecting rods, on the drag levers (33) associated with the inlet and exhaust valves (27, 28) respectively.
  10. A valve control system according to claims 1 to 9, characterised in that
    - in the case of a cross-current cylinder head (42) with ohc arrangement the single eccentric shaft (40) for controlling the intermediate elements or the rollers (32) on the separate transmission members or drag levers (33) for the inlet and exhaust valves (27, 28) is disposed in the region above the gas-change exhaust passages (43), wherein
    - the eccentric shaft (40) is in drive connection (45) with the camshaft (29) and
    - the driving wheel (46) on the eccentric-shaft side is one of the abutment-holders (47, 48) on the synchronising device (44) controllable as to phase position.
EP94902714A 1992-12-13 1993-12-08 Valve control for an internal combustion engine Expired - Lifetime EP0626035B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4242060 1992-12-13
DE4242060 1992-12-13
PCT/EP1993/003451 WO1994013935A1 (en) 1992-12-13 1993-12-08 Valve control for an internal combustion engine

Publications (2)

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

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DE (1) DE59307123D1 (en)
WO (1) WO1994013935A1 (en)

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WO1999064729A1 (en) 1998-06-05 1999-12-16 Bayerische Motoren Werke Aktiengesellschaft Valve timing system for an internal combustion engine
DE102011001612A1 (en) * 2011-03-29 2012-10-04 Pierburg Gmbh Device for discrete phase shift

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DE4418909A1 (en) * 1994-05-31 1995-12-07 Bayerische Motoren Werke Ag Valve control with an arrangement for variably changing the opening and closing of a globe valve, in particular for internal combustion engines
EP0717174A1 (en) * 1994-12-12 1996-06-19 Isuzu Motors Limited Valve operating system for internal combustion engine
DE19537377A1 (en) * 1995-10-06 1997-04-10 Bayerische Motoren Werke Ag Device for changing the stroke of internal combustion engine valves
US5937809A (en) * 1997-03-20 1999-08-17 General Motors Corporation Variable valve timing mechanisms
JP2001164911A (en) * 1999-12-10 2001-06-19 Yamaha Motor Co Ltd Valve system of four-cycle engine
CN112523875B (en) * 2020-12-01 2022-08-12 广西玉柴机器股份有限公司 Control method for override function of marine engine

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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 (en) * 1981-02-20 1985-10-11 Ferrer Jean MECHANISM FOR CONTROLLING THE INTAKE VALVES OF AN INTERNAL COMBUSTION ENGINE FOR AN EXTENDED INTAKE TIME
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 (en) * 1985-05-30 1986-12-04 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart VARIABLE VALVE CONTROL FOR A PISTON PISTON COMBUSTION ENGINE

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999064729A1 (en) 1998-06-05 1999-12-16 Bayerische Motoren Werke Aktiengesellschaft Valve timing system for an internal combustion engine
DE102011001612A1 (en) * 2011-03-29 2012-10-04 Pierburg Gmbh Device for discrete phase shift
DE102011001612B4 (en) * 2011-03-29 2013-02-28 Pierburg Gmbh Device for discrete phase shift

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DE59307123D1 (en) 1997-09-18
EP0626035A1 (en) 1994-11-30

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