EP0962629B1 - Variable valve drive for internal combustion engine - Google Patents

Variable valve drive for internal combustion engine Download PDF

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Publication number
EP0962629B1
EP0962629B1 EP99107959A EP99107959A EP0962629B1 EP 0962629 B1 EP0962629 B1 EP 0962629B1 EP 99107959 A EP99107959 A EP 99107959A EP 99107959 A EP99107959 A EP 99107959A EP 0962629 B1 EP0962629 B1 EP 0962629B1
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EP
European Patent Office
Prior art keywords
valve
roller
rocker arm
lever
accordance
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
Application number
EP99107959A
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German (de)
French (fr)
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EP0962629A3 (en
EP0962629A2 (en
Inventor
Gert Fischer
Michael Bidlingmaier
Stefan Föster
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of EP0962629A2 publication Critical patent/EP0962629A2/en
Publication of EP0962629A3 publication Critical patent/EP0962629A3/en
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • 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
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the invention relates according to the preamble of claim 1 to a variable valve train for an internal combustion engine, in which a lift valve of a Control cam of a camshaft is actuated by means of a valve lever which via a in its valve distal end region arranged curved path with interposition a controllably displaceable roller cooperates with the control cam such that the transverse to the camshaft axis of rotation against and in the direction of rotation Control cam discontinuously shifting role of opening and opening Closing times of the lift valve at constant opening angles in combination with variable valve lifts as a result of the change in the roller valve lever ratios serves.
  • variable valve train with a rocker arm is for example from the EP 0 717 174 A1.
  • variable valve lifts achieved by changing the rocker arm ratio which coincides with the controlled change of the position of the roll from a tilting axis near position to a tilt axis away from the position along the cam lever integrated cam track results.
  • the invention is based on the object, the generic valve train to the effect to improve that, especially in the low load range of the internal combustion engine especially small valve lifts with variably adjusted valve opening angle additionally achieved.
  • valve gear according to the invention is achievable that with a controlled under fixed positioned roller away moving opening edge and closing edge of the control cam over the evading by the displaceable tilting axis Valve lever initially no valve actuation occurs and this is given only when the role only about from the beginning to the end of the cam tip the control cam controlled activates the valve lever for valve actuation.
  • the advantage of the invention is that the additionally achievable variable valve opening angle ⁇ 120 ° crankshaft with variable valve strokes ⁇ 1.5 mm, in particular when using a rocker arm as a valve lever.
  • An advantageous embodiment of the invention is achieved in that a rocker arm tiltable about its tilting axis arranged with a fixed in a housing Bearing bridge along a straight path lifting Hubzylinder in conjunction stands, wherein the end remote from the rocker arm of a preloaded spring acted upon lifting cylinder in a guide portion of the predetermined Hubverlagerung the tilting axis appropriately sized slot for engagement of a in the bearing bridge arranged stop pin comprises, as well as in this Guide section is provided a recess for engaging the game a shift pin, which releases the against the spring between the ends the slot in the area of the cam tip of the control cam on the role and the rocker arm pivotable about the valve stem side rocker arm rest driven lift cylinder is controlled.
  • the invention offers the advantage of a valve drive with only one rocker arm, in connection with the lifting cylinder over the prior art Technique includes less moving masses.
  • valve gear advantageously allows a configuration with a single camshaft with control cams for inlet and outlet globe valves, comprising one fixed to a housing arranged rocker arm shaft mounted rocker arm for an outlet globe valve, being between the rocker arm and the relative to this lower in one Cylinder head arranged camshaft, the control shaft is provided for actuation the role between the inlet control cam and the rocker arm with controlled displaceable tilting axis for variable operation or control of the inlet lift valve preferably in the lower load range of the internal combustion engine, in particular in idle part load range.
  • Valve gear can with this in a further advantageous manner in a combustion chamber inflowing air imparted a swirling motion for better mixture formation become.
  • a controllably displaceable roller 7 With the transverse to the camshaft rotation axis 8 against and in the direction of rotation of the control cam 3 discontinuously displaceable roller 7 is the change of the opening and Closing time points of the lift valve 2, 2 'at constant valve opening angles in combination with variable valve strokes as a result of the change in the roller-related Rocker arm ratios achieved, as for example, from the in FIG 3 upper Hubkurvenschar emerges.
  • valve train 1 In accordance with the object of this valve train 1 is to be improved so that in particular at low load ranges of the engine particularly small, variable Valve lifts are achieved at variable valve opening angles.
  • camshaft rotation axis 8 is substantially parallel Tilting axis 9 of the rocker arm 5 relative to the camshaft 4 along a path 10th so controlled dynamically displaced that with displaced tilt axis 9 along the transverse to a connecting line 11 of the roller center 12 with the rocker arm rest 13 on the shaft end of the lift valve 2, 2 'directed web 10 of the rocker arm 5 via the only approximately from the initial area to about the end of the cam tip 14 of the control cam 3 controlled roller 7 is activated for valve actuation.
  • variable valve train 1 is in an advantageous Way an additionally achievable variable valve opening angle ⁇ 120 ° crankshaft achieved with variable valve strokes ⁇ 1.5 mm, as for example Figure 3 is shown with the Hubkurvenschar near the abscissa.
  • the roller 7 is on both sides attacking Handlebar 36 with a control arm 37 a via a worm gear 38 motor intermittently drivable control shaft 39 in drive connection, each with the roller 7 cooperating control cam 3 to the cam tip 14 thereafter and before the closing edge has a ramp-like section.
  • This ramp-like section causes at a camshaft axis of rotation 8 concentric curved path 6 on the rocker arm 5 according to FIG 3 at each lift curve of the upper Hubkurveschar after the curve vertex a roof-like sloping course.
  • This roof-like course is over the ramp-like extending section in conjunction with the rocker arm kinematics chosen so that the valve opening angle of the Hubkurvenschar near the abscissa in accordance with the invention Way are preferably ⁇ 100 ° crankshaft.
  • valve drive 1 is a single Camshaft 4 with control cam 3, 40 for inlet and outlet globe valves 2, 2 'and 41st with a mounted on a fixed housing rocker arm shaft 42 rocker arm 43 for an outlet lift valve 41, wherein between the rocker arm shaft 42 and the arranged relative to this deeper in a cylinder head 44 camshaft 4 the Control shaft 39 is provided for actuating the roller 7 between the inlet control cam 3 and the rocker arm 5 with controlled displaceable tilting axis. 9 for variable operation or for the variable control of the inlet lift valve 2, 2 '.
  • the tilting axis 9 can also be along a curved path be relocatable. Further, both lift valves 2, 2 'may be shown for each of those shown in FIG Set of curves accordingly synchronously operated.
  • a drag lever as a valve lever use Find is a drag lever as a valve lever use Find.

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

Description

Die Erfindung bezieht sich nach dem Oberbegriff des Patentanspruches 1 auf einen variablen Ventiltrieb für eine Brennkraftmaschine, bei dem ein Hubventil von einem Steuernocken einer Nockenwelle mittels eines Ventilhebels betätigt ist, der über eine in seinem ventilfernen Endbereich angeordnete Kurvenbahn unter Zwischenschaltung einer gesteuert verlagerbaren Rolle mit dem Steuernocken zusammenwirkt derart, daß die quer zur Nockenwellen-Drehachse gegen und in Drehrichtung des Steuernockens diskontinuierlich verlagerbare Rolle der Änderung der Öffnungsund Schließzeitpunkte des Hubventils bei konstanten Öffnungswinkeln in Kombination mit variablen Ventilhüben infolge der Änderung der rollenbedingten Ventilhebelübersetzungen dient.The invention relates according to the preamble of claim 1 to a variable valve train for an internal combustion engine, in which a lift valve of a Control cam of a camshaft is actuated by means of a valve lever which via a in its valve distal end region arranged curved path with interposition a controllably displaceable roller cooperates with the control cam such that the transverse to the camshaft axis of rotation against and in the direction of rotation Control cam discontinuously shifting role of opening and opening Closing times of the lift valve at constant opening angles in combination with variable valve lifts as a result of the change in the roller valve lever ratios serves.

Ein derartiger variabler Ventiltrieb mit einem Kipphebel ist beispielsweise aus der EP 0 717 174 A1 bekannt. Bei diesem bekannten Ventiltrieb sind variable Ventilhübe durch Änderung des Kipphebel-Übersetzungsverhältnisses erzielt, das sich mit der gesteuerten Veränderung der Position der Rolle von einer kippachsennahen Position zu einer kippachsenfernen Position längs der am Kipphebel integrierten Kurvenbahn ergibt. Mit dieser über die Rolle erzielten variablen Kipphebelübersetzung ist systembedingt verbunden auch eine relative Änderung der Position der Rolle zu dem mit ihr zusammenwirkenden Steuernocken derart, daß mit einer Kipphebelübersetzung in Richtung kleiner Kippwinkel die Rolle früher mit der Öffnungsflanke in Eingriff kommt und damit die Öffnungs- und Schließzeitpunkte des Hubventils nach "früh" verstellt sind. Damit verbunden ist ein zwischen den jeweiligen Öffnungs- und Schließzeitpunkten des Hubventils durch die Bemessung des Steuernockens gegebener konstanter Öffnungswinkel, der bei jedem der erreichbaren verminderten Ventilhübe konstant bleibt.Such a variable valve train with a rocker arm is for example from the EP 0 717 174 A1. In this known valve train are variable valve lifts achieved by changing the rocker arm ratio, which coincides with the controlled change of the position of the roll from a tilting axis near position to a tilt axis away from the position along the cam lever integrated cam track results. With this over the role achieved variable rocker arm translation is systemically linked also a relative change in the position of the role too the cooperating with them control cam such that with a Kipphebelübersetzung in the direction of small tilt angle the role earlier with the opening edge engages and thus the opening and closing times of the Lift valve are adjusted to "early". Related to this is a between the respective Opening and closing times of the lift valve by the design of the Control cam given constant opening angle, which at each of the achievable reduced valve lifts remains constant.

Nachteilig bei diesem bekannten Ventiltrieb ist, daß zur Erzielung einer gewünschten Gasdynamik im Brennraum der Brennkraftmaschine zum einen aus kinematischen Gründen keine ausreichend geringen Ventilhübe zu erreichen sind und zum anderen die Ventilöffnungswinkel konstant bleiben. Dokument EP 0686756 zeigt einen Ventiltrieb, bei dem auch die Ventilhübe änderbar sind.A disadvantage of this known valve train that to achieve a desired Gas dynamics in the combustion chamber of the internal combustion engine on the one hand from kinematic Reasons are not sufficiently low valve lifts can be achieved and the other the valve opening angle remain constant. Document EP 0686756 shows a valve train, in which the valve strokes are changeable.

Der Erfindung liegt die Aufgabe zugrunde, den gattungsgemäßen Ventiltrieb dahingehend zu verbessern, daß insbesondere in niederem Lastbereich der Brennkraftmaschine besonders kleine Ventilhübe bei variabel angepaßten Ventilöffnungswinkel zusätzlich erzielt sind.The invention is based on the object, the generic valve train to the effect to improve that, especially in the low load range of the internal combustion engine especially small valve lifts with variably adjusted valve opening angle additionally achieved.

Diese Aufgabe ist mit dem Patentanspruch 1 dadurch gelöst, daß die mit der Nockenwellen-Drehachse im wesentlichen parallele Kippachse des Ventilhebels relativ zur Nockenwelle längs einer Bahn derart gesteuert dynamisch verlagerbar ist, daß mit verlagerter Kippachse längs der quer zu einer Verbindungsgeraden der Rollenmitte mit der Ventilhebelauflage am Schaftende des Hubventils gerichteten Bahn der Ventilhebel über die lediglich etwa vom Anfangsbereich bis zum Endbereich der Nockenspitze des Steuernockens gesteuerte Rolle zur Ventilbetätigung aktiviert ist.This object is achieved with the patent claim 1, characterized in that with the Camshaft axis of rotation substantially parallel tilting axis of the valve lever controlled in a dynamically displaceable manner relative to the camshaft along a path, that with displaced tilt axis along the transverse to a connecting line of the Roller center with the valve lever support on the shaft end of the lift valve directed Trajectory of the valve lever on the only about the beginning of the range to the end the cam tip of the control cam controlled roller for valve actuation is activated.

Mit dem erfindungsgemäßen Ventiltrieb ist erreichbar, daß mit einer unter der gesteuert fix positionierten Rolle hinwegbewegten Öffnungsflanke und Schließflanke des Steuernockens über den durch die verlagerbare Kippachse ausweichenden Ventilhebel zunächst keine Ventilbetätigung erfolgt und diese erst gegeben ist, wenn die Rolle lediglich etwa vom Anfangsbereich bis zum Endbereich der Nockenspitze des Steuernockens gesteuert den Ventilhebel zur Ventilbetätigung aktiviert. With the valve gear according to the invention is achievable that with a controlled under fixed positioned roller away moving opening edge and closing edge of the control cam over the evading by the displaceable tilting axis Valve lever initially no valve actuation occurs and this is given only when the role only about from the beginning to the end of the cam tip the control cam controlled activates the valve lever for valve actuation.

Der Vorteil der Erfindung ist, daß der zusätzlich jeweils erzielbare variable Ventil-Öffnungswinkel <120° Kurbelwelle bei variablen Ventilhüben <1,5 mm ist, insbesondere bei Verwendung eines Kipphebels als Ventilhebel.The advantage of the invention is that the additionally achievable variable valve opening angle <120 ° crankshaft with variable valve strokes <1.5 mm, in particular when using a rocker arm as a valve lever.

Eine vorteilhafte Ausgestaltung der Erfindung ist dadurch erreicht, daß ein Kipphebel um seine Kippachse kippbeweglich mit einem in einer gehäusefest angeordneten Lagerbrücke längs einer geraden Bahn hubgeführten Hubzylinder in Verbindung steht, wobei der am kipphebelfernen Ende von einer vorgespannten Feder beaufschlagte Hubzylinder in einem Führungsabschnitt ein der vorbestimmten Hubverlagerung der Kippachse entsprechend bemessenes Langloch zum Eingriff eines in der Lagerbrücke angeordneten Anschlagbolzens umfaßt, sowie ferner in diesem Führungsabschnitt eine Ausnehmung vorgesehen ist zum spielbehafteten Eingriff eines Schaltbolzens, der zur Freigabe des gegen die Feder zwischen den Enden des Langloches im Bereich der Nockenspitze des Steuernockens über die Rolle und den um die ventilschaftseitige Kipphebelauflage schwenkbaren Kipphebel hubbeweglich angetriebenen Hubzylinders ansteuerbar ist.An advantageous embodiment of the invention is achieved in that a rocker arm tiltable about its tilting axis arranged with a fixed in a housing Bearing bridge along a straight path lifting Hubzylinder in conjunction stands, wherein the end remote from the rocker arm of a preloaded spring acted upon lifting cylinder in a guide portion of the predetermined Hubverlagerung the tilting axis appropriately sized slot for engagement of a in the bearing bridge arranged stop pin comprises, as well as in this Guide section is provided a recess for engaging the game a shift pin, which releases the against the spring between the ends the slot in the area of the cam tip of the control cam on the role and the rocker arm pivotable about the valve stem side rocker arm rest driven lift cylinder is controlled.

Gegenüber bekannten variablen Ventiltrieben mit mehreren, schaltbaren Ventilhebeln bietet die Erfindung den Vorteil eines Ventiltriebes mit lediglich einem Kipphebel, der in Verbindung mit dem Hubzylinder gegenüber dem bekannten Stand der Technik weniger bewegte Massen umfaßt.Compared to known variable valve trains with multiple, switchable valve levers the invention offers the advantage of a valve drive with only one rocker arm, in connection with the lifting cylinder over the prior art Technique includes less moving masses.

Der vorbeschriebene, grundsätzliche Aufbau des erfindungsgemäßen Ventiltriebes ermöglicht in vorteilhafter Weise eine Ausgestaltung mit einer einzigen Nockenwelle mit Steuernocken für Ein- und Auslaß-Hubventile, umfassend einen auf einer gehäusefest angeordneten Kipphebelwelle gelagerten Kipphebels für ein Auslaß-Hubventil, wobei zwischen der Kipphebelwelle und der relativ zu dieser tiefer in einem Zylinderkopf angeordneten Nockenwelle die Steuerwelle vorgesehen ist zur Betätigung der Rolle zwischen dem Einlaß-Steuernocken und dem Kipphebel mit gesteuert verlagerbarer Kippachse zum variablen Betrieb bzw. Steuerung des Einlaß-Hubventils vorzugsweise im unteren Lastbereich der Brennkraftmaschine, insbesondere im leerlaufnahen Teillastbereich.The above-described, basic structure of the valve gear according to the invention advantageously allows a configuration with a single camshaft with control cams for inlet and outlet globe valves, comprising one fixed to a housing arranged rocker arm shaft mounted rocker arm for an outlet globe valve, being between the rocker arm and the relative to this lower in one Cylinder head arranged camshaft, the control shaft is provided for actuation the role between the inlet control cam and the rocker arm with controlled displaceable tilting axis for variable operation or control of the inlet lift valve preferably in the lower load range of the internal combustion engine, in particular in idle part load range.

Neben einer vorteilhaft baulich kompakten Anordnung des erfindungsgemäßen Ventiltriebes kann mit diesem in weiterer vorteilhafter Weise der in einen Brennraum einströmenden Luft eine Drallbewegung zur besseren Gemischausbildung aufgeprägt werden.In addition to an advantageously structurally compact arrangement of the invention Valve gear can with this in a further advantageous manner in a combustion chamber inflowing air imparted a swirling motion for better mixture formation become.

Dies gilt in weiterer Ausgestaltung der Erfindung insbesondere bei einem Zylinderkopf mit zwei Einlaß-Hubventilen je Brennraum, wobei die zugeordneten Kipphebel mit verlagerbarer Kippachse jeweils gesondert ansteuerbar angeordnet sind derart, daß eines der Hubventile mit konstantem Öffnungswinkel bezüglich einer Ein-/Auslaßüberschneidung und eines Ventilhubes variabel gesteuert ist und daß das andere Hubventil mit variablem Ventil-Öffnungswinkel <100° Kurbelwelle mit Ventilhüben <1,1 mm variabel gesteuert ist.This applies in a further embodiment of the invention, in particular in a cylinder head with two inlet lift valves per combustion chamber, with the associated rocker arms are arranged separately controllable with displaceable tilting axis in such a way, that one of the globe valves with a constant opening angle with respect to a Inlet / Auslaßüberschneidung and a valve lift is variably controlled and that the other globe valve with variable valve opening angle <100 ° crankshaft with Valve strokes <1.1 mm is variably controlled.

Damit kann in vorteilhafter Weise durch gezielte Drallerzeugung im Brennraum eine verbesserte Verbrennung mit verringertem Verbrauch erzielt werden.This can advantageously by targeted swirl generation in the combustion chamber a improved combustion with reduced consumption can be achieved.

Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels beschrieben. Es zeigt

Figur 1
eine abschnittsweise gezeigte Anordnung des erfindungsgemäßen Ventiltriebes in einem nicht näher gezeigten Zylinderkopf einer Brennkraftmaschine,
Figur 2
den erfindungsgemäßen Ventiltrieb vergrößert dargestellt mit im Schnitt gezeigter Einrichtung zur Kippachsen-Steuerung,
Figur 3
mit dem erfindungsgemäßen Ventiltrieb erzielbar Hubverläufe, vorzugsweise für ein oder mehrere Einlaßventile.
The invention is described with reference to an embodiment shown in the drawing. It shows
FIG. 1
a sectionally shown arrangement of the valve gear according to the invention in a cylinder head of an internal combustion engine, not shown in detail,
FIG. 2
the valve gear according to the invention shown enlarged with shown in section means for tilt axis control,
FIG. 3
achievable with the valve gear according to the invention Hubverläufe, preferably for one or more intake valves.

Bei einem variablen Ventiltrieb 1 für eine nicht näher dargestellte Brennkraftmaschine ist ein Hubventil 2, 2' von jeweils einem Steuernocken 3 einer Nockenwelle 4 mittels jeweils eines einteiligen Kipphebels 5 betätigt, der über eine in seinem ventilfernen Endbereich angeordnete Kurvenbahn 6 unter Zwischenschaltung einer gesteuert verlagerbaren Rolle 7 mit dem Steuernocken 3 zusammenwirkt. Mit der quer zur Nockenwellen-Drehachse 8 gegen und in Drehrichtung des Steuernockens 3 diskontinuierlich verlagerbaren Rolle 7 ist die Änderung der Öffnungsund Schließzeitpunktpunkte des Hubventils 2, 2' bei konstanten Ventil-Öffnungswinkeln in Kombination mit variablen Ventilhüben infolge der Änderung der rollenbedingten Kipphebelübersetzungen erzielt, wie dies beispielsweise aus der in Figur 3 oberen Hubkurvenschar hervorgeht.In a variable valve train 1 for a non-illustrated internal combustion engine is a lifting valve 2, 2 'of a control cam 3 of a camshaft 4 actuated by means of a respective one-piece rocker arm 5, the one in his valve distal end region arranged cam track 6 with interposition a controllably displaceable roller 7 cooperates with the control cam 3. With the transverse to the camshaft rotation axis 8 against and in the direction of rotation of the control cam 3 discontinuously displaceable roller 7 is the change of the opening and Closing time points of the lift valve 2, 2 'at constant valve opening angles in combination with variable valve strokes as a result of the change in the roller-related Rocker arm ratios achieved, as for example, from the in FIG 3 upper Hubkurvenschar emerges.

Aufgabengemäß soll dieser Ventiltrieb 1 derart verbessert werden, daß insbesondere bei niederen Lastbereichen der Brennkraftmaschine besonders kleine, variable Ventilhübe bei variablen Ventil-Öffnungswinkeln erzielt sind.In accordance with the object of this valve train 1 is to be improved so that in particular at low load ranges of the engine particularly small, variable Valve lifts are achieved at variable valve opening angles.

Erfindungsgemäß ist die mit der Nockenwellen-Drehachse 8 im wesentlichen parallele Kippachse 9 des Kipphebels 5 relativ zur Nockenwelle 4 längs einer Bahn 10 derart gesteuert dynamisch verlagerbar, daß mit verlagerter Kippachse 9 längs der quer zu einer Verbindungsgeraden 11 der Rollenmitte 12 mit der Kipphebelauflage 13 am Schaftende des Hubventils 2, 2' gerichteten Bahn 10 der Kipphebel 5 über die lediglich etwa vom Anfangsbereich bis etwa zum Endbereich der Nockenspitze 14 des Steuemockens 3 gesteuerte Rolle 7 zur Ventilbetätigung aktiviert ist.According to the invention with the camshaft rotation axis 8 is substantially parallel Tilting axis 9 of the rocker arm 5 relative to the camshaft 4 along a path 10th so controlled dynamically displaced that with displaced tilt axis 9 along the transverse to a connecting line 11 of the roller center 12 with the rocker arm rest 13 on the shaft end of the lift valve 2, 2 'directed web 10 of the rocker arm 5 via the only approximately from the initial area to about the end of the cam tip 14 of the control cam 3 controlled roller 7 is activated for valve actuation.

Mit dem erfindungsgemäß weitergebildeten variablen Ventiltrieb 1 ist in vorteilhafter Weise ein zusätzlich jeweils erzielbarer variabler Ventil-Öffnungswinkel <120° Kurbelwelle bei variablen Ventilhüben <1,5 mm erreicht, wie dies beispielsweise aus Figur 3 mit der Hubkurvenschar nahe der Abszisse aufgezeigt ist.With the invention further developed variable valve train 1 is in an advantageous Way an additionally achievable variable valve opening angle <120 ° crankshaft achieved with variable valve strokes <1.5 mm, as for example Figure 3 is shown with the Hubkurvenschar near the abscissa.

Eine. hinsichtlich kleinem Bauraum konstruktiv vorteilhafte Ausgestaltung mit geringen Ventiltriebmassen ist in Ausgestaltung der Erfindung dadurch erreicht, daß der Kipphebel 5 um seine Kippachse 9 kippbeweglich mit einem in einer gehäusefest angeordneten Lagerbrücke 15 längs der geraden Bahn 10 hubgeführten Hubzylinder 16 in Verbindung steht, wobei der am kipphebelfernen Ende von einer vorgespannten Feder 17 beaufschlagte Hubzylinder 16 in einem Führungsabschnitt ein der vorbestimmten Hubverlagerung der Kippachse 9 entsprechend bemessenes Langloch 18 zum Eingriff eines in der Lagerbrücke 15 angeordneten Anschlagbolzens 19 umfaßt sowie ferner in diesem Führungsabschnitt eine Ausnehmung 20 vorgesehen ist zum spielbehafteten Eingriff eines Schaltbolzens 21. Dieser ist zur Freigabe des gegen die Feder 17 zwischen den Enden des Langloches 18 im Bereich der Nockenspitze 14 des Steuernockens 3 über die Rolle 7 und den um die ventilschaftseitige Kipphebelauflage 13 schwenkbaren Kipphebel 5 hubbeweglich angetriebenen Hubzylinders 16 ansteuerbar, wobei der hierbei um die Kipphebelauflage 13 schwenkende Kipphebel 5 keine Betätigung des Hubventils 2, 2' bewirkt.A. With regard to small space constructively advantageous embodiment with low Valve drive masses is achieved in an embodiment of the invention in that the rocker arm 5 about its tilting axis 9 tiltable with a fixed in a housing arranged bearing bridge 15 along the straight path 10 lifting Hubzylinder 16 is in communication, wherein the end remote from the toggle lever of a prestressed Spring 17 acted upon lifting cylinder 16 in a guide section the predetermined stroke displacement of the tilting axis 9 appropriately dimensioned Slot 18 for engaging a arranged in the bearing bracket 15 stop pin 19 includes and further in this guide section a recess 20th is provided for the playful engagement of a shift pin 21. This is for Release the against the spring 17 between the ends of the slot 18 in the area the cam tip 14 of the control cam 3 on the roller 7 and the order Valve stem-side rocker arm support 13 pivoting rocker arm 5 hubbeweglich driven lifting cylinder 16 controllable, wherein this case to the Kipphebelauflage 13 pivoting rocker arm 5 no actuation of the lift valve 2, 2 'causes.

Zur Erzielung einer niedrigen Bauweise ist der Hubzylinder 16 in vorteilhafter Weise von einer Bügelfeder 17 beaufschlagt und zur Erzielung eines im wesentlichen geräuschfreien Ventiltriebes über ein hydraulisches Ventilspiel-Ausgleichselement bzw. HVA 22 auf einem mit dem Kipphebel 5 über zylindrische Gelenkflächen zusammenwirkenden Gelenkstein 23 abgestützt. Zur Ölversorgung des HVA 22 kommuniziert der zum Schaltbolzen 21 diametral fluchtend angeordnete, hohle Anschlagbolzen 19 mit einer Ölkammer 24 einer in der Lagerbrücke 15 ausgebildeten Verteilerleitung 25 zur Fortleitung des Öls über eine im Langloch 18 vorgesehene Durchbrechung 26 des Hubzylinders 16 in dessen mit dem HVA 22 in Verbindung stehenden Innenraum 27, der federseitig über eine in einem Verschluß 28 vorgesehene Einrichtung entlüftet ist. Mittels der vorgespannten Bügelfeder 17 ist der Formschluß der an der Verlagerung der Kippachse 9 beteiligten Bauteile gewährleistet.To achieve a low design of the lifting cylinder 16 is in an advantageous manner acted upon by a bow spring 17 and to achieve a substantially noise-free Valve gear via a hydraulic valve clearance compensation element or HVA 22 on a cooperating with the rocker arm 5 via cylindrical articular surfaces Joint stone 23 supported. To the oil supply of the HVA 22 communicates the locking pin 21 diametrically aligned, hollow stop pin 19 with an oil chamber 24 formed in the bearing bracket 15 Distribution line 25 for the passage of the oil through a slot 18 provided in the Opening 26 of the lifting cylinder 16 in which with the HVA 22 in conjunction standing interior 27, the spring side via a provided in a closure 28 Device is vented. By means of the prestressed bow spring 17 is the Form-fitting ensures the participating in the relocation of the tilting axis 9 components.

Zur gesteuerten, dynamischen Verlagerung der Kippachse 9 wirkt eine ansteuerbare Betätigungseinrichtung 29, 29' über eine winkelverstellbare Schaltwelle 30, 30' mit einem drehfest angeordneten, federelastischen Hebel 31, 31' auf den jeweiligen Schaltbolzen 21 antreibend ein, wobei in der Phase der Betätigung des Hubventils 2, 2' mit über den Hubzylinder 16 blockierten Schaltbolzen 21 bei zugleich angesteuerter Betätigungseinrichtung 29, 29' über die Schaltwelle 30, 30' der federbelastete Hebel 31, 31' derart vorgespannt ist, daß bei Erreichen der Grundkreisphase der Rolle 7 am Steuernocken 3 der Schaltbolzen 21 aus der Ausnehmung 20 im Hubzylinder 16 ausgerückt und in ausgerückter Position über den Hebel 31, 31' gehalten ist.For controlled, dynamic displacement of the tilting axis 9 acts a controllable Actuating device 29, 29 'via an angle-adjustable control shaft 30, 30' with a rotationally fixed, resilient lever 31, 31 'on the respective Shift pin 21 drivingly, wherein in the phase of actuation of the lift valve 2, 2 'with blocked over the lifting cylinder 16 switching pin 21 at the same time driven Actuator 29, 29 'via the switching shaft 30, 30' of the spring-loaded Lever 31, 31 'is biased such that upon reaching the base circle phase the roller 7 on the control cam 3 of the shift pin 21 from the recess 20 disengaged in the lifting cylinder 16 and in disengaged position on the lever 31, 31 'is held.

Damit kann die im Gelenkstein 23 des Kipphebels 5 festgelegte Kippachse 9 entsprechend dem drehenden Steuernocken 3 zwischen den Enden des Langloches 18 hubbeweglich geführt werden, wobei mit Erreichen des unteren Endes des Langloches 18 die freie Schwenkbewegung des Kipphebels 5 um seine Kipphebelauflage 13 am Schaftende des Hubventils 2, 2' beendet ist und somit die Rolle 7 am Ende der Öffnungsflanke vom Anfangsbereich bis zum Endbereich der Nockenspitze 14 des Steuernockens 3 den Kipphebel 5 zur Betätigung des Hubventils 2, 2' aktiviert und anschließend im Bereich der Schließflanke bezüglich einer Ventilhubbetätigung wieder wirkungslos ist.Thus, the set in the hinge stone 23 of the rocker arm 5 tilting axis 9 accordingly the rotating control cam 3 between the ends of the elongated hole 18 to be guided Hubbeweglich, with reaching the lower end of the Langloches 18 the free pivotal movement of the rocker arm 5 about its rocker arm rest 13 at the shaft end of the lift valve 2, 2 'is completed and thus the role 7 at the end of the opening flank from the starting area to the end of the Cam tip 14 of the control cam 3, the rocker arm 5 for actuating the lift valve 2, 2 'activated and then in the region of the closing edge with respect to a Valve lift operation is again ineffective.

Zur vorteilhaften Vereinfachung der Montage der flachbauenden Bügelfeder 17, die einerseits im Hinblick auf das HVA 22 und andererseits auf die nicht gezeigte Rückstellfeder des zugehörigen Hubventils 2, 2' abgestellt ist, wird weiter vorgeschlagen, daß die auf den Hubzylinder 16 einwirkende Bügelfeder 17 in geringem Abstand über der Lagerbrücke 15 verlaufend angeordnet ist und über einen ösenartigen Endabschnitt 32 an einer seitlichen Stirnfläche 33 der Lagerbrücke 15 mittels einer mit dem Anschlagbolzen 19 fluchtenden Verschraubung 34 befestigt ist, die ferner als Anschlag einer vorgespannten Druckfeder 35 für den in der Lagerbrücke 15 schiebebeweglich angeordneten Anschlagbolzen 19 dient. Zur leichten Demontage des aus Ölführungsgründen hohlen Anschlagbolzens 19 kann dieser an seiner Innenseite mit einem Gewinde versehen sein zum Angriff einer Demontage-Schraube (nicht gezeigt).For advantageous simplification of the assembly of the flat-forming bow spring 17, the on the one hand with regard to the HVA 22 and on the other hand on the return spring, not shown the associated lift valve 2, 2 'is turned off, it is further proposed that acting on the lifting cylinder 16 bow spring 17 at a small distance is arranged extending over the bearing bridge 15 and an eye-like End portion 32 on a lateral end face 33 of the bearing bracket 15 by means of a is fastened with the stop pin 19 aligned screw 34, the further as a stop of a prestressed compression spring 35 for the in the bearing bridge 15th slidingly arranged stop pin 19 is used. For easy disassembly of the oil guide reasons hollow stop pin 19, this can on its inside be threaded to attack a disassembly screw (Not shown).

Wie weiter aus Figur 2 hervorgeht, steht die Rolle 7 über beiderseits angreifende Lenker 36 mit einem Steuerarm 37 einer über ein Schneckengetriebe 38 motorisch diskontinuierlich antreibbaren Steuerwelle 39 in Antriebsverbindung, wobei jeder mit der Rolle 7 zusammenwirkende Steuemocken 3 an die Nockenspitze 14 anschließend und vor der Schließflanke einen rampenartig verlaufenden Abschnitt aufweist. Dieser rampenartig verlaufende Abschnitt bewirkt bei einer zur Nockenwellen-Drehachse 8 konzentrisch ausgebildeten Kurvenbahn 6 am Kipphebel 5 gemäß Figur 3 bei jeder Hubkurve der oberen Hubkurvenschar nach dem Kurvenscheitel einen dachartig abfallenden Verlauf. Dieser dachartige Verlauf ist über den rampenartig verlaufenden Abschnitt in Verbindung mit der Kipphebel-Kinematik so gewählt, daß die Ventil-Öffnungswinkel der Hubkurvenschar nahe der Abszisse in erfindungsgemäßer Weise vorzugsweise <100° Kurbelwelle sind.As further shown in Figure 2, the roller 7 is on both sides attacking Handlebar 36 with a control arm 37 a via a worm gear 38 motor intermittently drivable control shaft 39 in drive connection, each with the roller 7 cooperating control cam 3 to the cam tip 14 thereafter and before the closing edge has a ramp-like section. This ramp-like section causes at a camshaft axis of rotation 8 concentric curved path 6 on the rocker arm 5 according to FIG 3 at each lift curve of the upper Hubkurveschar after the curve vertex a roof-like sloping course. This roof-like course is over the ramp-like extending section in conjunction with the rocker arm kinematics chosen so that the valve opening angle of the Hubkurvenschar near the abscissa in accordance with the invention Way are preferably <100 ° crankshaft.

Zur Erzielung eines vorteilhaft kompakt bauenden Ventiltriebes 1 dient eine einzige Nockenwelle 4 mit Steuernocken 3, 40 für Ein- und Auslaß-Hubventile 2, 2' bzw. 41 mit einem auf einer gehäusefest angeordneten Kipphebelwelle 42 gelagerten Kipphebel 43 für ein Auslaß-Hubventil 41, wobei zwischen der Kipphebelwelle 42 und der relativ zu dieser tiefer in einem Zylinderkopf 44 angeordneten Nockenwelle 4 die Steuerwelle 39 vorgesehen ist zur Betätigung der Rolle 7 zwischen dem Einlaß-Steuernocken 3 und dem Kipphebel 5 mit gesteuerte verlagerbarer Kippachse 9 zum variablen Betrieb bzw. zur variablen Steuerung des Einlaß-Hubventils 2, 2'.To achieve an advantageously compact valve drive 1 is a single Camshaft 4 with control cam 3, 40 for inlet and outlet globe valves 2, 2 'and 41st with a mounted on a fixed housing rocker arm shaft 42 rocker arm 43 for an outlet lift valve 41, wherein between the rocker arm shaft 42 and the arranged relative to this deeper in a cylinder head 44 camshaft 4 the Control shaft 39 is provided for actuating the roller 7 between the inlet control cam 3 and the rocker arm 5 with controlled displaceable tilting axis. 9 for variable operation or for the variable control of the inlet lift valve 2, 2 '.

Die vorbeschriebene, kompakte Anordnung ist insbesondere dann vorteilhaft, wenn bei einem Zylinderkopf 44 mit zwei Einlaß-Hubventilen 2, 2' je Brennraum die zugeordneten Kipphebel 5 mit verlagerbarer Kippachse 9 jeweils gesondert über die Betätigungseinrichtungen 29, 29' ansteuerbar angeordnet sind derart, daß eines der Hubventile 2' mit konstantem Öffnungswinkel bezüglich einer Ein-/Auslaß-Überschneidung und eines Ventilhubes variabel gesteuert ist und daß das andere Hubventil 2 erfindungsgemäß mit variablem Ventil-Öffnungswinkel <100° Kurbelwelle mit Ventilhüben <1,1 mm variabel gesteuert ist. Damit kann die nicht gezeigte Brennkraftmaschine im unteren Lastbereich, insbesondere im leerlaufnahen Teillastbereich verbrauchsgünstig betrieben werden durch eine gezielte Drallbildung der Ladung in einem Brennraum. The above-described, compact arrangement is particularly advantageous when in a cylinder head 44 with two inlet globe valves 2, 2 'per combustion chamber assigned Toggle 5 with displaceable tilting axis 9 each separately via the actuators 29, 29 'are arranged controllable such that one of the Stroke valves 2 'with constant opening angle with respect to an inlet / outlet overlap and one valve lift is variably controlled and that the other lift valve 2 according to the invention with variable valve opening angle <100 ° crankshaft with Valve strokes <1.1 mm is variably controlled. Thus, the internal combustion engine, not shown in the lower load range, especially in idle part load range be operated economically by a targeted swirling the Cargo in a combustion chamber.

Im Rahmen der Erfindung kann die Kippachse 9 auch längs einer gekrümmten Bahn verlagerbar sein. Ferner können beide Hubventile 2, 2' für jede der in Figur 3 gezeigten Kurvenschar entsprechend synchron betätigt sein.In the context of the invention, the tilting axis 9 can also be along a curved path be relocatable. Further, both lift valves 2, 2 'may be shown for each of those shown in FIG Set of curves accordingly synchronously operated.

Weiter kann im Rahmen der Erfindung auch ein Schlepphebel als Ventilhebel Verwendung finden.Further, in the context of the invention, a drag lever as a valve lever use Find.

Claims (10)

  1. A variable valve drive for an internal combustion engine
    wherein a gate valve (2, 2') is operated by a control cam (3) of a camshaft (4) by means of a valve lever (5) which
    via a curved track (6) situated in its end region remote from the valve, co-operates with the control cam (3) with interposition of a roller (7) movable in controlled manner, so that
    the roller (7), discontinuously movable transversely of the camshaft axis (8) in and against the direction of rotation of the control cam (3), is useable for altering the opening and closing times of the gate valve (2, 2') at constant opening angles in combination with variable valve strokes as a result of the change in the valve-lever transmission ratios via the roller,
    characterised in that
    the tilting axis (9), substantially parallel to the camshaft axis (8), of the valve lever (5) is dynamically movable in controlled manner along a track (10) relative to the camshaft (4) such that
    when the tilting axis (9) is moved along the track (10) transversely of a line (11) connecting the middle (12) of the roller to the support (13) of the valve lever on the shank end of the gate valve (2, 2'), the valve lever (5) is activated for valve operation via the roller (7), which is controlled approximately only from the initial region to approximately the end region of the peak (14) of the control cam (3).
  2. A valve drive in accordance with claim 1, characterised in that the respective additionally attainable variable valve opening angle is < 120° crank shaft angle at variable valve strokes < 1.5, when a rocker arm (5) is used as the valve lever.
  3. A valve drive in accordance with claims 1 and 2, characterised in that
    a rocker arm (5) tiltable around its axis (9) is connected to a reciprocating cylinder (16) guided in a stroke along a straight track (10) in a bearing bridge (15) fixed to the casing, wherein
    a guide portion of the reciprocating cylinder (16), operated by a prestressed spring (17) at the end remote from the rocker arm, has a slot (18) dimensioned in accordance with the set displacement of the tilting axis (9) during the stroke, in order to engage a stop pin (19) disposed in the bearing bridge (15), and
    the said guide portion is formed with a recess (20) for engagement, subject to clearance, of a crank rod (21) which
    can be actuated in order to release the reciprocating cylinder (16), which is driven in a stroke against the spring (17) between the ends of the slot (18) in the region of the peak (14) of the control cam (3) via the roller (7) and via the rocker arm (5), which is pivotable round its support (13) on the valve shank.
  4. A valve drive in accordance with claims 1 to 3, characterised in that
    the reciprocating cylinder (16) acted upon by a fastening spring (17) is supported by a hydraulic valve-clearance compensating element (HVA22) on a link block (23) co-operating with the rocker arm (5) via cylindrical link surfaces, wherein
    in order to supply oil to the HVA (22), a hollow stop pin (19) disposed diametrically in line with the crank rod (21) communicates with an oil chamber (24) of a distribution line (25) formed in the bearing bridge (15) in order to convey the oil through an aperture (26) in the slot (18) of the cylinder (16) into the interior (27) thereof, which is in contact with the HVA (22) and
    is ventilated on the spring side via a device provided in a closure means (28).
  5. A valve drive in accordance with claims 1 to 4, characterised in that
    an actuatable operating device (29, 29'), via a variable-angle control shaft (30, 30'), acts on and drives a respective co-rotatable resilient lever (31, 31') on the respective crank rod (21), wherein
    in the phase of operating the gate valve (2, 2'), each respective resilient lever (31, 31') is so stressed by the crank rod (21) blocked via the reciprocating cylinder (16), with simultaneously actuated operating device (29, 29') via the respective control shaft (31, 31') that
    when the pitch circle phase of the roller (7) is reached on the control cam (3), the crank rod (21) is disengaged from the recess (20) in the reciprocating cylinder (16) and is held in the disengaged position above the respective lever (30, 30').
  6. A valve drive in accordance with claims 1 to 5, characterised in that
    the fastening spring (17) acting on the reciprocating cylinder (16) is disposed at a short distance above the bearing bridge (15) and
    via an eyelet-like end portion (32), is fastened to a lateral endface (33) of the bearing bridge (15) by screws (34) aligned with the stop pin (19),
    the screws also serving as a stop of a prestressed pressure spring (35) for the stop pin (19) slidably disposed on the bearing bridge (15).
  7. A valve drive in accordance with claims 1 to 6, characterised in that
    the roller (7), via guide rods (36) engaging on each side, is connected for drive purposes to a control arm (37) of a control shaft (39) discontinuously drivable by a motor via a worm gear (38), wherein
    each control cam (3) co-operating with the roller (7) has a sloping portion adjoining the cam peak (14) and in front of the closure flank, and
    the curved track (6) on the rocker arm (5) is concentric with the camshaft axis (8).
  8. A valve drive in accordance with claims 1 to 7, characterised by
    a single camshaft (4) with control cams (3, 40) for inlet and outlet gate valves (2, 2'; 41) comprising a rocker arm (43), mounted on a shaft (42) fixed to the casing, for an outlet gate valve (41), wherein
    between the rocker-arm shaft (42) and the camshaft (4) disposed below it in a cylinder head (44), a control shaft (39) is provided for operating the roller (7) between the inlet control cam (3) and the rocker arm (5) having a controlled movable tilting axis (9), for variable operation or control of the inlet gate valve (2, 2').
  9. A valve drive in accordance claims 1 to 8, characterised in that
    in the case of a cylinder head (44) with two inlet gate valves (2, 2') per combustion chamber, the associated rocker arms (5) having a movable tilting axis (9) are each separately controllable, such that
    one of the gate valves (2') is variably controlled with a constant valve opening angle relative to an inlet/outlet overlap and a valve stroke, and
    the other gate valve (2) is variably controlled with a variable valve opening angle < 100° crankshaft with valve strokes < 1.1 mm.
  10. A valve drive in accordance with claim 9, characterised in that the second gate valve (2) with a variable valve opening angle is actuated at lower engine loads, especially at near-idling loads.
EP99107959A 1998-06-05 1999-04-22 Variable valve drive for internal combustion engine Expired - Lifetime EP0962629B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19825308A DE19825308A1 (en) 1998-06-05 1998-06-05 Variable valve train for an internal combustion engine
DE19825308 1998-06-05

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EP0962629A2 EP0962629A2 (en) 1999-12-08
EP0962629A3 EP0962629A3 (en) 2000-10-18
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EP (1) EP0962629B1 (en)
DE (2) DE19825308A1 (en)
ES (1) ES2221259T3 (en)

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DE10120451A1 (en) * 2001-04-26 2002-10-31 Ina Schaeffler Kg Shaft rotatable by electric motor
GR20010100295A (en) 2001-06-18 2003-02-27 Εμμανουηλ Παττακος Variable valve gear
DE10258277A1 (en) * 2002-12-13 2004-06-24 Mahle Ventiltrieb Gmbh Control device for gas exchange valves of an internal combustion engine
EP1697619B1 (en) * 2003-08-18 2009-04-08 Manousos Pattakos Variable valve gear
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Also Published As

Publication number Publication date
EP0962629A3 (en) 2000-10-18
DE59909838D1 (en) 2004-08-05
US6145485A (en) 2000-11-14
DE19825308A1 (en) 1999-12-09
EP0962629A2 (en) 1999-12-08
ES2221259T3 (en) 2004-12-16

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