EP0962629A2 - Variable valve drive for internal combustion engine - Google Patents

Variable valve drive for internal combustion engine Download PDF

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Publication number
EP0962629A2
EP0962629A2 EP99107959A EP99107959A EP0962629A2 EP 0962629 A2 EP0962629 A2 EP 0962629A2 EP 99107959 A EP99107959 A EP 99107959A EP 99107959 A EP99107959 A EP 99107959A EP 0962629 A2 EP0962629 A2 EP 0962629A2
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EP
European Patent Office
Prior art keywords
valve
rocker arm
roller
lift
cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP99107959A
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German (de)
French (fr)
Other versions
EP0962629B1 (en
EP0962629A3 (en
Inventor
Gert Fischer
Michael Bidlingmaier
Stefan Föster
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0962629A2 publication Critical patent/EP0962629A2/en
Publication of EP0962629A3 publication Critical patent/EP0962629A3/en
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Publication of EP0962629B1 publication Critical patent/EP0962629B1/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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 to a preamble of claim 1 variable valve train for an internal combustion engine, in which a globe valve by a Control cam of a camshaft is actuated by means of a valve lever, which via a cam track arranged in its end region remote from the valve with interposition a controlled relocatable role cooperates with the control cam such that the transverse to the camshaft axis of rotation against and in the direction of rotation of the control cam discontinuously relocatable role of changing the opening and Combination times of the globe valve with constant opening angles in combination with variable valve strokes due to the change in the valve lever ratios due to the roller serves.
  • variable valve train with a rocker arm is for example from the EP 0 717 174 A1 is known.
  • this known valve train there are variable valve lifts achieved by changing the rocker gear ratio that matches the controlled change in the position of the roll from a position close to the tilting axis to a position away from the tilt axis along the cam track integrated on the rocker arm results.
  • this variable rocker arm ratio achieved via the roller system-related, there is also a relative change in the position of the role the control cam cooperating with it in such a way that with a rocker arm ratio in the direction of a small tilt angle, the roller used to have the opening flank comes into engagement and thus the opening and closing times of the The lift valve is adjusted to "early". This is connected between the respective Opening and closing times of the globe valve by dimensioning the Control cam given constant opening angle that at each of the achievable reduced valve strokes remains constant.
  • a disadvantage of this known valve train is that in order to achieve a desired one Gas dynamics in the combustion chamber of the internal combustion engine are kinematic Reasonably low valve strokes cannot be achieved and for others the valve opening angles remain constant.
  • the invention is based on the object, the generic valve train to improve that, especially in the low load range of the internal combustion engine especially small valve lifts with variably adjusted valve opening angles additionally achieved.
  • valve train With the valve train according to the invention it can be achieved that with one controlled under the fixedly positioned roller moving opening flank and closing flank of the control cam over the one evading by the shiftable tilt axis Valve lever initially no valve actuation and this is only given when the role only from about the beginning to the end of the cam tip of the control cam controlled the valve lever activated 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.
  • a rocker arm tiltable about its tilt axis with one arranged in a housing-fixed Bearing bridge connected along a straight path with stroke-guided lifting cylinders stands, with the end distal to the rocker arm by a prestressed spring acted upon lifting cylinders in a guide section of the predetermined stroke displacement elongated hole dimensioned according to the tilt axis for engaging a includes stop pin arranged in the bearing bridge, and further in this Guide section a recess is provided for engagement with play a shift pin that is used to release the against the spring between the ends the slot in the area of the cam tip of the control cam over the roller and the rocker arm, which is pivotable about the rocker arm support on the valve stem side, can be moved driven lifting cylinder is controllable.
  • the invention offers the advantage of a valve train with only one rocker arm, which in connection with the lifting cylinder compared to the known state of the Technology includes less moving masses.
  • valve train advantageously allows a configuration with a single camshaft with control cams for intake and exhaust lift valves, comprising one on a housing arranged rocker arm shaft mounted rocker arm for an outlet lift valve, being between the rocker arm shaft and the relative to this deeper in one Cylinder head arranged camshaft, the control shaft is provided for actuation the role between the inlet control cam and the rocker arm also controlled relocatable tilt 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 the low-load partial load range.
  • valve train can be used in a further advantageous manner in a combustion chamber Incoming air has a swirl movement for better mixture formation become.
  • variable valve train 1 for an internal combustion engine, not shown in detail is a lift valve 2, 2 'of a control cam 3 of a camshaft 4 actuated by means of a one-piece rocker arm 5, which in its valve path remote end region arranged cam 6 with interposition a controlled displaceable roller 7 cooperates with the control cam 3.
  • a lift valve 2, 2 'of a control cam 3 of a camshaft 4 actuated by means of a one-piece rocker arm 5, which in its valve path remote end region arranged cam 6 with interposition a controlled displaceable roller 7 cooperates with the control cam 3.
  • the transverse to the camshaft axis of rotation 8 against and in the direction of rotation of the control cam 3 discontinuously relocatable roller 7 is the change of opening and Closing times of the lift valve 2, 2 'at constant valve opening angles in combination with variable valve strokes due to the change in the roller-related Rocker arm ratios achieved, such as from the figure 3 upper lifting curve family emerges.
  • this valve train 1 should be improved such that, in particular especially small, variable at low load ranges of the internal combustion engine Valve strokes are achieved with variable valve opening angles.
  • the axis of rotation 8 is essentially parallel Tilt axis 9 of the rocker arm 5 relative to the camshaft 4 along a path 10 controlled in such a way dynamically displaceable that with shifted tilt axis 9 along the transverse to a connecting straight line 11 of the roller center 12 with the rocker arm rest 13 at the switching end of the lift valve 2, 2 'directed path 10 of the rocker arm 5 that only from about the beginning to the end of the cam tip 14 of the control cam 3 controlled roller 7 is activated for valve actuation.
  • variable valve train 1 further developed according to the invention is advantageous Way an additionally achievable variable valve opening angle ⁇ 120 ° crankshaft achieved with variable valve strokes ⁇ 1.5 mm, such as from Figure 3 is shown with the family of stroke curves near the abscissa.
  • a structurally advantageous design with a small amount of space with little Valve train masses is achieved in an embodiment of the invention in that the rocker arm 5 is tiltable about its tilt axis 9 with one in a housing-fixed arranged bearing bracket 15 along the straight path 10 stroke-guided lifting cylinders 16 is connected, the end distal to the rocker arm being pretensioned Spring 17 acted upon lifting cylinder 16 in a guide section the predetermined stroke displacement of the tilt axis 9 dimensioned accordingly
  • Elongated hole 18 for engaging a stop pin arranged in the bearing bracket 15 19 includes and also in this guide section a recess 20th is provided for engagement of a switching pin 21 with play.
  • the lifting cylinder 16 is advantageous acted upon by a bow spring 17 and to achieve a substantially noise-free Valve drive via a hydraulic valve lash compensation element or HVA 22 on a cooperating with the rocker arm 5 via cylindrical articular surfaces Articulated 23 supported.
  • a controllable acts for the controlled, dynamic displacement of the tilt axis 9 Actuating device 29, 29 'via an angle-adjustable switching shaft 30, 30' with a non-rotatable, resilient lever 31, 31 'on the respective Switching pin 21 driving, being in the phase of actuation of the globe valve 2, 2 'with switching bolts 21 blocked via the lifting cylinder 16 while at the same time being actuated Actuator 29, 29 'via the switching shaft 30, 30' of the spring-loaded Lever 31, 31 'is biased such that when the base circle phase is reached the roller 7 on the control cam 3 of the switching pin 21 from the recess 20 disengaged in the lifting cylinder 16 and in the disengaged position via the lever 31, 31 'is held.
  • the tilt axis 9 defined in the articulation block 23 of the rocker arm 5 can be corresponding the rotating control cam 3 between the ends of the elongated hole 18 can be moved in a lifting motion, with reaching the lower end of the Elongated hole 18, the free pivoting movement of the rocker arm 5 around its rocker arm rest 13 is ended at the shaft end of the lift valve 2, 2 'and thus the role 7 at the end of the opening flank from the start area to the end area 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 area of the closing flank with respect to a Valve stroke actuation is ineffective again.
  • the on the one hand with regard to the HVA 22 and on the other hand to the return spring, not shown of the associated lift valve 2, 2 ' is further proposed that the acting on the lifting cylinder 16 bow spring 17 at a short distance is arranged extending over the bearing bridge 15 and over an eyelet-like End section 32 on a lateral end face 33 of the bearing bracket 15 by means of a with the stop bolt 19 aligned screw 34 is attached, which also as a stop for a prestressed compression spring 35 for the bearing bracket 15 stop pin 19 arranged for sliding movement.
  • this can be on the inside be threaded to attack a disassembly screw (Not shown).
  • the roller 7 stands above both sides Handlebar 36 with a control arm 37 a motor via a worm gear 38 discontinuously drivable control shaft 39 in drive connection, each with the roller 7 cooperating control cam 3 to the cam tip 14 then and has a ramp-like section in front of the closing flank.
  • This ramp-like section brings about the axis of rotation relative to the camshaft 8 concentrically formed cam track 6 on the rocker arm 5 according to the figure 3 for each stroke curve of the upper curve family after the curve vertex a roof-like slope.
  • This roof-like course is over the ramp-like running section in connection with the rocker arm kinematics selected so that the valve opening angle of the family of lifting curves near the abscissa in the invention Way are preferably ⁇ 100 ° crankshaft.
  • a single valve drive serves to achieve an advantageously compact valve train 1
  • Control shaft 39 is provided for actuating the roller 7 between the inlet control cam 3 and the rocker arm 5 with controlled shiftable tilt axis 9 for variable operation or for variable control of the inlet lift valve 2, 2 '.
  • the compact arrangement described above is particularly advantageous if in the case of a cylinder head 44 with two intake lift valves 2, 2 'per combustion chamber, the associated Rocker arm 5 with displaceable tilt axis 9 each separately via the actuating devices 29, 29 'are arranged such that one of the Lift valves 2 'with a constant opening angle with respect to an inlet / outlet overlap and a valve stroke is variably controlled and that the other stroke valve 2 according to the invention with variable valve opening angle ⁇ 100 ° crankshaft Valve strokes ⁇ 1.1 mm are variably controlled. So that the internal combustion engine, not shown in the lower load range, especially in the partial load range close to idling are operated in a fuel-efficient manner by means of a targeted swirl formation Charge in a combustion chamber.
  • the tilt axis 9 can also be along a curved path be relocatable. Furthermore, both lift valves 2, 2 'for each of those shown in Figure 3 Curve family must be operated synchronously.
  • rocker arm can also be used as a valve lever within the scope of the invention 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)

Abstract

The device has a valve lever (5) with a tilting axis (9), which is parallel to the pivot axis (8) of the cam shaft and can be dynamically displaced relative to the cam shaft (4) along a path (10). Due to this, the valve lever is activated for valve operation via the roller (7), which is controlled only from approx. the front to the end section of the cam tip (14) of the radial cam (3). The additional variable valve opening angle ≤ 120 degrees is ≤ 1,5 with variable valve strokes, when the valve lever is a rocker arm.

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 Öffnungs-und Schließzeitpunkte des Hubventils bei konstanten Öffnungswinkeln in Kombination mit variablen Ventilhüben infolge der Änderung der rollenbedingten Ventilhebelübersetzungen dient.The invention relates to a preamble of claim 1 variable valve train for an internal combustion engine, in which a globe valve by a Control cam of a camshaft is actuated by means of a valve lever, which via a cam track arranged in its end region remote from the valve with interposition a controlled relocatable role cooperates with the control cam such that the transverse to the camshaft axis of rotation against and in the direction of rotation of the control cam discontinuously relocatable role of changing the opening and Combination times of the globe valve with constant opening angles in combination with variable valve strokes due to the change in the valve lever ratios due to the roller 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-Ubersetzungsverhältnisses 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 is known. In this known valve train there are variable valve lifts achieved by changing the rocker gear ratio that matches the controlled change in the position of the roll from a position close to the tilting axis to a position away from the tilt axis along the cam track integrated on the rocker arm results. With this variable rocker arm ratio achieved via the roller system-related, there is also a relative change in the position of the role the control cam cooperating with it in such a way that with a rocker arm ratio in the direction of a small tilt angle, the roller used to have the opening flank comes into engagement and thus the opening and closing times of the The lift valve is adjusted to "early". This is connected between the respective Opening and closing times of the globe valve by dimensioning the Control cam given constant opening angle that at each of the achievable reduced valve strokes 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.A disadvantage of this known valve train is that in order to achieve a desired one Gas dynamics in the combustion chamber of the internal combustion engine are kinematic Reasonably low valve strokes cannot be achieved and for others the valve opening angles remain constant.

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 improve that, especially in the low load range of the internal combustion engine especially small valve lifts with variably adjusted valve opening angles 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 Schaffende 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 claim 1 in that with Camshaft axis of rotation essentially parallel tilt axis of the valve lever can be dynamically displaced in a controlled manner relative to the camshaft along a path, that with shifted tilt axis along the transverse to a connecting straight line Align the center of the roller with the valve lever support at the creative end of the globe valve Track the valve lever over only about from the start area to the end area 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 train according to the invention it can be achieved that with one controlled under the fixedly positioned roller moving opening flank and closing flank of the control cam over the one evading by the shiftable tilt axis Valve lever initially no valve actuation and this is only given when the role only from about the beginning to the end of the cam tip of the control cam controlled the valve lever activated 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 tilt axis with one arranged in a housing-fixed Bearing bridge connected along a straight path with stroke-guided lifting cylinders stands, with the end distal to the rocker arm by a prestressed spring acted upon lifting cylinders in a guide section of the predetermined stroke displacement elongated hole dimensioned according to the tilt axis for engaging a includes stop pin arranged in the bearing bridge, and further in this Guide section a recess is provided for engagement with play a shift pin that is used to release the against the spring between the ends the slot in the area of the cam tip of the control cam over the roller and the rocker arm, which is pivotable about the rocker arm support on the valve stem side, can be moved driven lifting cylinder is controllable.

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 several switchable valve levers the invention offers the advantage of a valve train with only one rocker arm, which in connection with the lifting cylinder compared to the known state of the Technology 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 train according to the invention advantageously allows a configuration with a single camshaft with control cams for intake and exhaust lift valves, comprising one on a housing arranged rocker arm shaft mounted rocker arm for an outlet lift valve, being between the rocker arm shaft and the relative to this deeper in one Cylinder head arranged camshaft, the control shaft is provided for actuation the role between the inlet control cam and the rocker arm also controlled relocatable tilt 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 the low-load partial 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 The valve train can be used in a further advantageous manner in a combustion chamber Incoming air has a swirl movement 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.In a further embodiment of the invention, this applies in particular to a cylinder head with two inlet lift valves per combustion chamber, the associated rocker arm each with a displaceable tilting axis are separately controllable in such a way that that one of the globe valves with a constant opening angle with respect to a Inlet / outlet overlap and a valve lift is variably controlled and that the other globe valve with variable valve opening angle <100 ° crankshaft Valve strokes <1.1 mm are variably controlled.

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

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
Figure 1
4 shows an arrangement of the valve drive according to the invention shown in sections in a cylinder head of an internal combustion engine (not shown in more detail),
Figure 2
the valve train according to the invention is shown enlarged with a device for tilt axis control shown in section,
Figure 3
stroke profiles achievable with the valve train according to the invention, preferably for one or more inlet 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 Öffnungs-und 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.With a variable valve train 1 for an internal combustion engine, not shown in detail is a lift valve 2, 2 'of a control cam 3 of a camshaft 4 actuated by means of a one-piece rocker arm 5, which in its valve path remote end region arranged cam 6 with interposition a controlled displaceable roller 7 cooperates with the control cam 3. With the transverse to the camshaft axis of rotation 8 against and in the direction of rotation of the control cam 3 discontinuously relocatable roller 7 is the change of opening and Closing times of the lift valve 2, 2 'at constant valve opening angles in combination with variable valve strokes due to the change in the roller-related Rocker arm ratios achieved, such as from the figure 3 upper lifting curve family 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.According to the task, this valve train 1 should be improved such that, in particular especially small, variable at low load ranges of the internal combustion engine Valve strokes are achieved with 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 Schaltende des Hubventils 2, 2' gerichteten Bahn 10 der Kipphebel 5 über die lediglich etwa vom Anfangsbereich bis etwa zum Endbereich der Nockenspitze 14 des Steuernockens 3 gesteuerte Rolle 7 zur Ventilbetätigung aktiviert ist.According to the invention, the axis of rotation 8 is essentially parallel Tilt axis 9 of the rocker arm 5 relative to the camshaft 4 along a path 10 controlled in such a way dynamically displaceable that with shifted tilt axis 9 along the transverse to a connecting straight line 11 of the roller center 12 with the rocker arm rest 13 at the switching end of the lift valve 2, 2 'directed path 10 of the rocker arm 5 that only from about the beginning to 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 variable valve train 1 further developed according to the invention is advantageous Way an additionally achievable variable valve opening angle <120 ° crankshaft achieved with variable valve strokes <1.5 mm, such as from Figure 3 is shown with the family of stroke curves 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 structurally advantageous design with a small amount of space with little Valve train masses is achieved in an embodiment of the invention in that the rocker arm 5 is tiltable about its tilt axis 9 with one in a housing-fixed arranged bearing bracket 15 along the straight path 10 stroke-guided lifting cylinders 16 is connected, the end distal to the rocker arm being pretensioned Spring 17 acted upon lifting cylinder 16 in a guide section the predetermined stroke displacement of the tilt axis 9 dimensioned accordingly Elongated hole 18 for engaging a stop pin arranged in the bearing bracket 15 19 includes and also in this guide section a recess 20th is provided for engagement of a switching pin 21 with play. This is for Release of the against the spring 17 between the ends of the elongated hole 18 in the area the cam tip 14 of the control cam 3 via the roller 7 and the order valve stem side rocker arm rest 13 pivotable rocker arm 5 movable driven lifting cylinder 16 can be controlled, which in this case around the rocker arm rest 13 pivoting rocker arm 5 does not actuate the lift valve 2, 2 '.

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 Gelenketein 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.In order to achieve a low construction, the lifting cylinder 16 is advantageous acted upon by a bow spring 17 and to achieve a substantially noise-free Valve drive via a hydraulic valve lash compensation element or HVA 22 on a cooperating with the rocker arm 5 via cylindrical articular surfaces Articulated 23 supported. Communicates to the oil supply of the HVA 22 the hollow stop bolt arranged diametrically aligned with the switching pin 21 19 with an oil chamber 24 formed in the bearing bridge 15 Distribution line 25 for conveying the oil through a provided in the slot 18 Opening 26 of the lifting cylinder 16 in connection with the HVA 22 standing interior 27, the spring side via a provided in a closure 28 Device is vented. By means of the pretensioned bow spring 17 Form-fit of the components involved in the displacement of the tilt axis 9 is ensured.

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.A controllable acts for the controlled, dynamic displacement of the tilt axis 9 Actuating device 29, 29 'via an angle-adjustable switching shaft 30, 30' with a non-rotatable, resilient lever 31, 31 'on the respective Switching pin 21 driving, being in the phase of actuation of the globe valve 2, 2 'with switching bolts 21 blocked via the lifting cylinder 16 while at the same time being actuated Actuator 29, 29 'via the switching shaft 30, 30' of the spring-loaded Lever 31, 31 'is biased such that when the base circle phase is reached the roller 7 on the control cam 3 of the switching pin 21 from the recess 20 disengaged in the lifting cylinder 16 and in the disengaged position via 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 tilt axis 9 defined in the articulation block 23 of the rocker arm 5 can be corresponding the rotating control cam 3 between the ends of the elongated hole 18 can be moved in a lifting motion, with reaching the lower end of the Elongated hole 18, the free pivoting movement of the rocker arm 5 around its rocker arm rest 13 is ended at the shaft end of the lift valve 2, 2 'and thus the role 7 at the end of the opening flank from the start area to the end area 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 area of the closing flank with respect to a Valve stroke actuation is ineffective again.

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).To advantageously simplify the assembly of the flat bow spring 17, the on the one hand with regard to the HVA 22 and on the other hand to the return spring, not shown of the associated lift valve 2, 2 'is further proposed that the acting on the lifting cylinder 16 bow spring 17 at a short distance is arranged extending over the bearing bridge 15 and over an eyelet-like End section 32 on a lateral end face 33 of the bearing bracket 15 by means of a with the stop bolt 19 aligned screw 34 is attached, which also as a stop for a prestressed compression spring 35 for the bearing bracket 15 stop pin 19 arranged for sliding movement. For easy disassembly of the hollow stop pin 19 for reasons of oil guidance, this can be on the 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 Steuernocken 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 can further be seen from FIG. 2, the roller 7 stands above both sides Handlebar 36 with a control arm 37 a motor via a worm gear 38 discontinuously drivable control shaft 39 in drive connection, each with the roller 7 cooperating control cam 3 to the cam tip 14 then and has a ramp-like section in front of the closing flank. This ramp-like section brings about the axis of rotation relative to the camshaft 8 concentrically formed cam track 6 on the rocker arm 5 according to the figure 3 for each stroke curve of the upper curve family after the curve vertex a roof-like slope. This roof-like course is over the ramp-like running section in connection with the rocker arm kinematics selected so that the valve opening angle of the family of lifting curves near the abscissa in 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'.A single valve drive serves to achieve an advantageously compact valve train 1 Camshaft 4 with control cams 3, 40 for intake and exhaust lift valves 2, 2 'and 41 with a rocker arm mounted on a rocker arm shaft 42 fixed to the housing 43 for an outlet lift valve 41, between the rocker shaft 42 and the camshaft 4 which is arranged deeper in a cylinder head 44 relative to this Control shaft 39 is provided for actuating the roller 7 between the inlet control cam 3 and the rocker arm 5 with controlled shiftable tilt axis 9 for variable operation or for 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 compact arrangement described above is particularly advantageous if in the case of a cylinder head 44 with two intake lift valves 2, 2 'per combustion chamber, the associated Rocker arm 5 with displaceable tilt axis 9 each separately via the actuating devices 29, 29 'are arranged such that one of the Lift valves 2 'with a constant opening angle with respect to an inlet / outlet overlap and a valve stroke is variably controlled and that the other stroke valve 2 according to the invention with variable valve opening angle <100 ° crankshaft Valve strokes <1.1 mm are variably controlled. So that the internal combustion engine, not shown in the lower load range, especially in the partial load range close to idling are operated in a fuel-efficient manner by means of a targeted swirl formation Charge 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 tilt axis 9 can also be along a curved path be relocatable. Furthermore, both lift valves 2, 2 'for each of those shown in Figure 3 Curve family must be operated synchronously.

Weiter kann im Rahmen der Erfindung auch ein Schlepphebel als Ventilhebel Verwendung finden.Furthermore, a rocker arm can also be used as a valve lever within the scope of the invention Find.

Claims (10)

Variabler Ventiltrieb für eine Brennkraftmaschine bei dem ein Hubventil (2, 2') von einem Steuernocken (3) einer Nockenwelle (4) mittels eines Ventilhebels (5) betätigt ist, der über eine in seinem ventilfernen Endbereich angeordnete Kurvenbahn (6) unter Zwischenschaltung einer gesteuert verlagerbaren Rolle (7) mit dem Steuernocken (3) zusammenwirkt derart, daß die quer zur Nockenwellen-Drehachse (8) gegen und in Drehrichtung des Steuernockens (3) diskontinuierlich verlagerbare Rolle (7) der Änderung der Öffnungs- und Schließzeitpunkte des Hubventils (2, 2') bei konstanten Öffnungswinkeln in Kombination mit variablen Ventilhüben infolge der Änderung der rollenbedingten Ventilhebelübersetzungen dient,
dadurch gekennzeichnet, daß die mit der Nockenwellen-Drehachse (8) im wesentlichen parallele Kippachse (9) des Ventilhebels (5) relativ zur Nockenwelle (4) längs einer Bahn (10) derart gesteuert dynamisch verlagerbar ist, daß mit verlagerter Kippachse (9) längs der quer zu einer Verbindungsgeraden (11) der Rollenmitte (12) mit der Ventilhebelauflage (13) am Schaltende des Hubventils (2, 2') gerichteten Bahn (10) der Ventilhebel (5) über die lediglich etwa vom Anfangsbereich bis etwa zum Endbereich der Nockenspitze (14) des Steuernockens (3) gesteuerte Rolle (7) zur Ventilbetätigung aktiviert ist. Variable valve train for an internal combustion engine in which a lift valve (2, 2 ') is actuated by a control cam (3) of a camshaft (4) by means of a valve lever (5) which Interacts with the control cam (3) via a cam track (6) arranged in its end region remote from the valve, with the interposition of a controllably displaceable roller (7) such that the roller (7) which can be shifted discontinuously transversely to the camshaft axis of rotation (8) against and in the direction of rotation of the control cam (3) to change the opening and closing times of the lift valve (2, 2 ') at constant opening angles in combination with variable valve strokes as a result of the change serves the role-related valve lever ratios,
characterized, that the with the camshaft axis of rotation (8) substantially parallel tilt axis (9) of the valve lever (5) relative to the camshaft (4) along a path (10) is dynamically shifted in such a way that With a shifted tilt axis (9) along the path (10) of the valve lever (5), which is directed transversely to a connecting straight line (11) of the roller center (12) with the valve lever support (13) at the switching end of the lift valve (2, 2 '), over only about from the start area to approximately the end area of the cam tip (14) of the control cam (3) controlled roller (7) is activated for valve actuation. Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß der zusätzlich jeweils erzielbare variable Ventil-Öffnungswinkel <120° Kurbelwelle bei variablen Ventilhüben <1,5 ist bei Verwendung eines Kipphebels (5) als Ventilhebel.Valve train according to claim 1, characterized in that the additional Variable valve opening angle achievable in each case <120 ° crankshaft with variable Valve strokes <1.5 is when using a rocker arm (5) as a valve lever. Ventiltrieb nach Anspruch 1 und 2, dadurch gekennzeichnet, daß ein Kipphebel (5) um seine Kippachse (9) kippbeweglich mit einem in einer gehäusefest angeordneten Lagerbrücke (15) längs einer 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), der 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 ist. Valve train according to claim 1 and 2, characterized in that a rocker arm (5) about its tilt axis (9) can be tilted with a lifting bridge (16) which is arranged in a housing-fixed bearing bridge (15) along a straight path (10), whereby the lifting cylinder (16) acted on by a pretensioned spring (17) at the end remote from the rocker arm comprises, in a guide section, an elongated hole (18) dimensioned for the predetermined stroke displacement of the tilting axis (9) for engaging a stop bolt (19) arranged in the bearing bridge (15), such as Furthermore, a recess (20) is provided in this guide section for engagement of a switching pin (21) with play to release the spring (17) between the ends of the elongated hole (18) in the area of the cam tip (14) of the control cam (3) via the roller (7) and the rocker arm (5) that can be pivoted about the valve stem side rocker arm rest (13) driven lifting cylinder (16) can be controlled. Ventiltrieb nach den Ansprüchen 1 bis 3, dadurch gekennzeichnet, daß der von einer Bügelfeder (17) beaufschlagte Hubzylinder (16) über ein hydraulisches Ventilspiel-Ausgleichselement (HVA 22) auf einem mit dem Kipphebel (5) über zylindrische Gelenkflächen zusammenwirkenden Gelenkstein (23) abgestützt ist, wobei zur Ölversorgung des HVA (22) ein zum Schaltbolzen (21) diametral fluchtend angeordneter, hohler Anschlagbolzen (19) mit einer Ölkammer (24) einer in der Lagerbrücke (15) ausgebildeten Verteilerleitung (25) kommuniziert 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. Valve train according to claims 1 to 3, characterized in that the lifting cylinder (16) acted upon by a bow spring (17) is supported via a hydraulic valve lash compensation element (HVA 22) on a rocker block (23) which interacts with the rocker arm (5) via cylindrical articulated surfaces, whereby For supplying oil to the HVA (22), a hollow stop pin (19), which is diametrically aligned with the switching pin (21), communicates with an oil chamber (24) of a distributor line (25) formed in the bearing bracket (15) in order to convey the oil through a hole in the slot ( 18) provided opening (26) of the lifting cylinder (16) in its interior (27) in connection with the HVA (22), the is vented on the spring side via a device provided in a closure (28). Ventiltrieb nach den Ansprüchen 1 bis 4, dadurch gekennzeichnet, daß eine ansteuerbare Betätigungseinrichtung (29, 29') über eine winkelverstellbare Schallwelle (30, 30') mit jeweils einem drehfest angeordneten, federelastischen Hebel (31, 31') auf den jeweiligen Schaltbolzen (21) antreibend einwirkt, 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 jeweilige Schaltwelle (30, 30') der jeweilige federelastische 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 jeweiligen Hebel (31, 31') gehalten ist. Valve train according to claims 1 to 4, characterized in that a controllable actuating device (29, 29 ') via an angle-adjustable sound wave (30, 30'), each with a non-rotatably arranged, resilient lever (31, 31 ') drivingly acts on the respective switching pin (21), wherein in the phase of actuation of the lift valve (2, 2 ') with switching bolts (21) blocked via the lifting cylinder (16) while the actuating device (29, 29') is actuated via the respective switching shaft (30, 30 ') the respective spring-elastic lever ( 31, 31 ') is biased such that when the base circle phase of the roller (7) on the control cam (3) is reached, the switching pin (21) is disengaged from the recess (20) in the lifting cylinder (16) and held in the disengaged position by the respective lever (31, 31 '). Ventiltrieb nach den Ansprüchen 1 bis 5, dadurch gekennzeichnet, daß die auf den Hubzylinder (16) einwirkende Bügelfeder (17) in geringen 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. Valve train according to claims 1 to 5, characterized in that the acting on the lifting cylinder (16) bow spring (17) is arranged at a short distance above the bearing bracket (15) and Via an eyelet-like end section (32) on a lateral end face (33) of the bearing bracket (15) by means of a screw (34) aligned with the stop bolt (19), which also serves as a stop for a prestressed compression spring (35) for the stop bolt (19) which is arranged in the bearing bridge (15) and can be moved by sliding. Ventiltrieb nach den Ansprüchen 1 bis 6, dadurch gekennzeichnet, daß die Rolle (7) über beiderseits angreifende Lenker (36) mit einem Steuerarm (37) einer über ein Schneckengetriebe (38) motorisch diskontinuierlich antreibbaren Steuerwelle (39) in Antriebsverbindung steht, wobei jeder mit der Rolle (7) zusammenwirkende Steuernocken (3) an die Nockenspitze (14) anschließend und vor der Schließflanke einen rampenartig verlaufenden Abschnitt aufweist, und ferner die Kurvenbahn (6) des Kipphebels (5) konzentrisch zur Nockenwellen-Drehachse (8) ausgebildet ist. Valve train according to claims 1 to 6, characterized in that the roller (7) on both sides engaging handlebars (36) with a control arm (37) of a worm gear (38) motor-driven discontinuous control shaft (39) is in drive connection, wherein each control cam (3) cooperating with the roller (7) adjoins the cam tip (14) and has a ramp-like section in front of the closing flank, and further the cam track (6) of the rocker arm (5) is concentric with the camshaft axis of rotation (8). Ventiltrieb nach den Ansprüchen 1 bis 7, gekennzeichnet durch eine einzige Nockenwelle (4) mit Steuernocken (3, 40) für Ein- und Auslaß-Hubventile (2, 2'; 41), umfassend einen 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 gesteuert verlagerbarer Kippachse (9) zum variablen Betrieb bzw. Steuerung des Einlaß-Hubventils (2, 2'). Valve train according to claims 1 to 7, characterized by a single camshaft (4) with control cams (3, 40) for intake and exhaust lift valves (2, 2 '; 41), comprising a rocker arm (43) mounted on a rocker arm shaft (42) fixed to the housing for an exhaust lift valve ( 41), where Between the rocker arm shaft (42) and the camshaft (4) located lower in a cylinder head (44) relative to this, the control shaft (39) is provided for actuating the roller (7) between the inlet control cam (3) and the rocker arm (5 ) with a controllably displaceable tilting axis (9) for variable operation or control of the inlet lift valve (2, 2 '). Ventiltrieb nach den Ansprüchen 1 bis 8, dadurch gekennzeichnet, daß bei einem Zylinderkopf (44) mit zwei Einlaß-Hubventilen (2, 2') je Brennraum die zugeordneten Kipphebel (5) mit verlagerbarer Kippachse (9) jeweils gesondert ansteuerbar angeordnet sind derart, daß eines der Hubventile (2') mit konstantem Ventil-Öffnungswinkel bezüglich einer Ein-/Auslaß-Überschneidung und eines Ventilhubes variabel gesteuert ist und daß das andere Hubventil (2) mit variablem Ventil-Öffnungswinkel <100° Kurbelwelle mit Ventilhüben <1,1 mm variabel gesteuert ist. Valve train according to claims 1 to 8, characterized in that that in a cylinder head (44) with two intake lift valves (2, 2 ') per combustion chamber, the associated rocker arms (5) with displaceable tilt axis (9) are each separately controllable such that one of the lift valves (2 ') with a constant valve opening angle with respect to an inlet / outlet overlap and a valve lift is variably controlled and that the other stroke valve (2) with variable valve opening angle <100 ° crankshaft with valve strokes <1.1 mm is variably controlled. Ventiltrieb nach Anspruch 9, dadurch gekennzeichnet, daß das zweite Hubventil (2) mit variablem Ventil-Öffnungswinkel im unteren Lastbereich der Brennkraftmaschine, insbesondere im leerlaufnahen Teillastbereich angesteuert ist.Valve train according to claim 9, characterized in that the second lift valve (2) with variable valve opening angle in the lower load range of Internal combustion engine, in particular driven in the low-load partial load range is.
EP99107959A 1998-06-05 1999-04-22 Variable valve drive for internal combustion engine Expired - Lifetime EP0962629B1 (en)

Applications Claiming Priority (2)

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DE19825308 1998-06-05
DE19825308A DE19825308A1 (en) 1998-06-05 1998-06-05 Variable valve train for an internal combustion engine

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EP0962629A2 true EP0962629A2 (en) 1999-12-08
EP0962629A3 EP0962629A3 (en) 2000-10-18
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EP (1) EP0962629B1 (en)
DE (2) DE19825308A1 (en)
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Also Published As

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EP0962629B1 (en) 2004-06-30
US6145485A (en) 2000-11-14
DE59909838D1 (en) 2004-08-05
DE19825308A1 (en) 1999-12-09
ES2221259T3 (en) 2004-12-16
EP0962629A3 (en) 2000-10-18

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