EP1619362B1 - Distribution de moteur à combustion - Google Patents

Distribution de moteur à combustion Download PDF

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Publication number
EP1619362B1
EP1619362B1 EP05014341A EP05014341A EP1619362B1 EP 1619362 B1 EP1619362 B1 EP 1619362B1 EP 05014341 A EP05014341 A EP 05014341A EP 05014341 A EP05014341 A EP 05014341A EP 1619362 B1 EP1619362 B1 EP 1619362B1
Authority
EP
European Patent Office
Prior art keywords
transmission element
cam
valve
torsion spring
pivoted lever
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 - Fee Related
Application number
EP05014341A
Other languages
German (de)
English (en)
Other versions
EP1619362A2 (fr
EP1619362A3 (fr
Inventor
Jurij Gartner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP1619362A2 publication Critical patent/EP1619362A2/fr
Publication of EP1619362A3 publication Critical patent/EP1619362A3/fr
Application granted granted Critical
Publication of EP1619362B1 publication Critical patent/EP1619362B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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
    • F01L13/0005—Deactivating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
    • F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L2001/467—Lost motion springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers

Definitions

  • the present invention relates to a valve train of an internal combustion engine according to the preamble of claim 1.
  • valve train for an internal combustion engine has a rotatable drive shaft with at least one cam and an actuatable pivot lever, which is operatively connected to a, a shaft of a gas exchange valve acting second transmission element such that a displacement of the pivot lever along a cam formed between the pivot lever and the second transmission element leads to a change in the lifting height of the acted gas exchange valve.
  • the displacement of the pivot lever by means of a rotation of a shaft and / or the operation of an actuator, wherein an elastic member acts on the pivot lever for contact with the cam.
  • the elastic member is arranged such that the biasing force generated by the elastic member is independent of the displacement of the pivot lever relative to the second transmission member, and that the elastic member is rotatably disposed on the drive shaft relative thereto.
  • the elastic member is arranged by means of a rotatable relative to the drive shaft holder on the drive shaft to which a rolling body is rotatably mounted, which is in rolling contact with the cam.
  • Object of the present invention is to provide a measure that compensate depending on the position of the actuator, the induced over the eccentric displacement.
  • the invention now provides a valve drive with the features in the characterizing part of claim 1 to solve this problem.
  • the invention provides a valve train of an internal combustion engine, wherein the valve drive has a rotatable drive shaft having at least one cam and a first transmission element operable therewith, a pivot lever, which is in operative connection with a second transmission element such that this can act on a shaft of a gas exchange valve namely, such that a displacement of the first transmission element along a control curve formed between the first and the second transmission element leads to a change in the lift height of the gas exchange valve acted upon and the displacement of the first transmission element by means of a rotation of a shaft and / or the actuation of an actuator and takes place elastic member acts on the first transmission element for contact with the cam and this elastic member is arranged such that the biasing force generated by the elastic member of the publisher tion of the first transmission element relative to the second transmission element is independent.
  • the invention thus provides a variable-stroke valve drive, in which the valve lift in a wide range between a full load position with maximum valve lift and a Leerlaufgaswolf with minimal valve lift or a Zylinderabschalt ein can be changed with Nullventilhub and thereby the first cam follower element forming the first transmission element is acted upon by an elastic member against the cam for contact therewith, that the biasing force generated by the elastic member of the for effecting the change of the stroke of Gas exchange valve necessary displacement of the first transmission element relative to the second transmission element is independent.
  • the elastic member is rotatably mounted on the drive shaft relative thereto and that this can be achieved by means of a rotatably mounted on the drive shaft holder which receives and holds the elastic member.
  • the first transmission element is a pivot lever, on which a rolling body is rotatably mounted, which is connected to the cam of the rotatable drive shaft is in rolling engagement.
  • a displacement of the pivot lever on the rolling elements of the second transmission element along the control curve can take place by a predetermined distance, which can be superimposed additively the displacement induced by the eccentric shaft.
  • the elastic member may be a torsion spring which is received by the holder rotatably mounted on the drive shaft and having a spring arm, which in a bore engages the pivot lever and thus keeps the rolling elements on the pivot lever in contact with the cam.
  • the arranged between the drive shaft and the pivot lever torsion spring is tensioned, so that the torsion spring ensures that after the turning away of the cam lobe profile from the contact with the rolling elements of the rolling elements against the cam base circle is pressed and thus the rolling element remains in contact with the cam.
  • control cam is formed on the pivot lever and has a Nullhubkurve and has a Hubrampenab mustard and the pivoting lever thus formed along the control cam on a second transmission element rotatably arranged rolling elements is displaced.
  • this means that the pivoting lever can be displaced along the control cam on the rolling body of the second transmission element, so that the contact point between the pivoting lever or the control cam formed on the pivot lever and the rolling element is in the region between the zero-stroke curve and the lifting ramp section so that, when the contact point is in the zero-stroke curve, a cylinder-selective valve deactivation and thereby cylinder deactivation can be realized, and when the contact point is in the range of the lift ramp portion of the control cam, a change in the lift of the gas exchange valve can be realized, as appropriate the position of the contact point along the Hubrampenabites or its geometric design.
  • the shaft for displacing the first transmission element relative to the second Consequentlysüngselement is an eccentric shaft and displacement of the pivot lever on the rolling elements of the second transmission element along the control cam by a predetermined distance is possible by means of a rotation of the eccentric shaft.
  • a rotation of the eccentric shaft for example, a cylinder bank selective Basic tuning of the lifting height of the gas exchange valve of this cylinder bank can be achieved.
  • the above-mentioned holder is made of a plastic material, on which the torsion spring can be releasably fixed, for example by means of a latching connection.
  • FIG. 1 The drawing now shows a valve train 1 according to an embodiment of the present invention in a schematic view for ease of understanding in a plan view.
  • the valve drive 1 has a drive shaft 2, which is rotated by the base engine, not shown, via a drive in the form of a chain or a toothed belt or the like in rotation.
  • the drive shaft 2 is shown with only one cam 3, but may be the drive shaft with cams of a multi-cylinder internal combustion engine, so that it is readily apparent that the drive shaft 2 may have a plurality of cams 3.
  • the valve drive 1 shown can thus serve for the inlet control of a multi-cylinder multi-valve internal combustion engine.
  • the cam 3 now follows a cam follower component or first transmission element 4 in the form of a pivoting lever.
  • a rolling element 5 is rotatably arranged in the form of a roller on the pivot lever 4, so that it comes between the cam 3 and the roller 5 to a rolling operation.
  • the pivot lever 4 has in the region of the bearing of the roller 5 a bore or receptacle 6, in which a spring arm 7 of a torsion spring 8 engages.
  • the torsion spring 8 is received in a made of a plastic material holder 9, wherein for receiving the torsion spring 8, the holder 9 is formed in two parts and by latching the two housing halves of the holder 9, the torsion spring 8 is fixed in the holder 9.
  • the thus created unit of torsion spring 8 and holder 9 can now be rotatably mounted on a bearing portion of the drive shaft or camshaft 2.
  • the pivot lever 4 can by means of a rotation of an eccentric shaft 10 by 180 degrees from the in Fig. 1 and 2 the drawing shown full load basic position of the valve train in an in Fig. 3 to 6 illustrated idle basic position are shifted, with the in Fig. 1 and 2 the drawing shown full load position of the in Fig. 3 and 4 illustrated idle position in particular differs in that the point of contact between a control arm formed on the pivot lever 4 and arranged on a second transmission element 12 roller 13 from the designated HR ramp portion of the control cam 11 migrates to the NH designated Nullhubabmale the cam 11.
  • the second transmission element 12 in the form of a finger lever can press on a valve stem 15 for actuation of a gas exchange valve 14 and is supported at its end 16 opposite the valve stem 15 at, for example, a hydraulically operating valve clearance compensation element 17.
  • the gas exchange valve 14 is axially guided with its valve stem 15 in a valve stem guide 18 which may be pressed into a cylinder head, not shown, and is kept closed in an unopened state by means of a coil spring 19, so that the valve disc 20 against a in the cylinder head of Internal combustion engine arranged valve seat presses.
  • the holder 9 is rotatably mounted at a bearing point of the drive shaft or camshaft 2, so that a rotation of the camshaft 2 does not lead to a deflection of the spring arm 7 with respect to the center axis 21 of the torsion spring 8, as long as the cam 3 rolls with its base circle on the roller 5. Since the torsion spring 8 in the in Fig. 1 shown basic position exerts a biasing force, the roller 5 is pressed by this biasing force to the cam 3.
  • FIG. 3 The drawing shows the valve gear 1 in the neutral position corresponding to a basic position with the torsion spring 8 in the basic position.
  • the eccentric shaft 10 has been rotated by 180 degrees, which leads to a displacement of the pivot lever 4 along the control cam 11 in the designated zero NH range.
  • the included between the center axis 21 and along the center axis of the spring arm 7 reference axis 23 included angle ⁇ has not changed by the displacement of the pivot lever 4 along the control cam 11 in the region of the zero stroke section of the control cam 11.
  • the base of the torsion spring 8 corresponding biasing force is maintained, so that no change in the friction conditions in the valve train 1 has resulted from the displacement of the pivot lever 4.
  • Fig. 4 The drawing now shows a similar presentation Fig. 3 with rotated cam, so that the gas exchange valve 14 performs a valve lift, which is sufficient for maintaining the idling speed of the internal combustion engine.
  • the valve lift of the gas exchange valve in the full load position is 12 mm, for example, the valve lift in the idling position may be reduced to a value of, for example, 1.5 mm.
  • the biasing force generated in the deflected by the rotation of the cam 3 and tensioned position of the torsion spring 8 corresponds to the biasing force of the torsion spring 8 in the Fig. 2 illustrated deflected position in full load operation.
  • FIG. 5 shows the valve train 1 in a position to provide selective cylinder deactivation.
  • This position was realized by a further displacement of the pivot lever 4 along the zero lift curve NH of the control cam 11 by means of the application of a piston / cylinder unit 24 with, for example, pressure oil from the engine lubricating oil circuit.
  • the application of the piston / cylinder unit 24 now leads to a displacement caused by the displacement of the pivoting lever 4 due to the rotation of the eccentric shaft 10, which is additively superimposed on a further displacement of the pivot lever 4 brought about by the piston / cylinder unit 24 such that the point of contact between the Control cam 11 and the roller 13 has been moved to the end of the zero lift NH.
  • the valve train 1 in which the biasing force of the torsion spring 8 in the unactuated initial position of the biasing force of the torsion spring 8 in the unactuated basic position in the full load position of the valve train 1 and in the idle position of the valve train 1 corresponds (the angle ⁇ has not changed) , performs a rotation of the cam 3 (see Fig. 6 the drawing) to a rolling of the contact point between the roller 13 and the cam 11 in the zero lift curve NH, so that it no longer comes to an opening of the valve stem 15 by the cam follower 12, the gas exchange valve 14 remains closed, the associated cylinder of the engine is excluded from the gas exchange process, the cylinder is selectively switched off.
  • actuated by the cam 3 position and thus deflected and cocked position of the torsion spring 8 corresponds to the biasing force generated by the torsion spring 8 of those of the torsion spring 8 in the tensioned state in idle position of the valve gear 1 and in the tensioned state in full load position of the valve train. 1 is produced.
  • the biasing force of the torsion spring 8 changes in each of the cam 3 not actuated basic position or actuated by the cam 3 deflected biased position not in response to the displacement of the pivot lever 4 and thus not in response to the desired or realized valve lift ,

Landscapes

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

Claims (8)

  1. Distribution de moteur thermique comportant un arbre d'entraînement (2) rotatif ayant au moins une came (3) et actionnant un premier élément de transmission (4) coopérant avec un second élément de transmission (12) sollicitant l'axe (15) d'une soupape d'échange de gaz (14) de façon qu'un déplacement du premier élément de transmission (4) le long d'une courbe de commande (11) entre le premier (4) et le second (12) élément de transmission se traduise par une variation de la levée de la soupape d'échange de gaz (14) ainsi sollicitée et que le déplacement du premier élément de transmission (4) se fait par la rotation d'un arbre (10) et/ou l'actionnement d'un actionneur (24), et un composant élastique (8) sollicite l'élément de transmission (4) pour être en contact avec la came (3),
    - le composant élastique (8) étant installé pour que la force de précontrainte générée par le composant élastique (8), soit indépendant du déplacement du premier élément de transmission (4) par rapport au second élément de transmission (12), et que le composant élastique (8) soit installé à rotation par rapport à l'arbre d'entraînement (2),
    - le composant élastique (8) étant monté sur l'arbre d'entraînement (2) par l'intermédiaire d'un support (9) tournant par rapport à l'arbre d'entraînement (2), et le premier élément de transmission (4) est un levier pivotant muni d'un organe de roulement (5) monté à rotation qui est en prise de roulement avec la came (3),
    distribution caractérisée en ce que
    l'entraînement d'actionneur (24) est un ensemble piston/cylindre dont l'actionnement produit un déplacement du levier pivotant (4) sur l'organe de roulement (13) du second élément de transmission (12) le long de la courbe de commande (11) sur une distance prédéterminée qui est combinée de manière additive au déplacement produit par l'intermédiaire de l'arbre à excentrique (10).
  2. Distribution selon la revendication 1,
    caractérisée en ce que
    le composant élastique (8) est un ressort de rotation venant en prise par un bras de ressort (7) dans un perçage (6) du levier pivotant (4) et maintenant l'organe de roulement (5) en contact avec la came (3).
  3. Distribution selon la revendication 1 ou 2,
    caractérisée en ce que
    la courbe de commande (11) réalisée sur le levier pivotant (4) avec une courbe de course nulle (NH) ainsi qu'un segment de rampe de levée (HR) et le levier pivotant (4) se déplace le long de la courbe de commande (11) par un organe de roulement (13) porté à rotation par le second élément de transmission (12).
  4. Distribution selon l'une des revendications 1 à 3,
    caractérisée en ce que
    l'arbre (10) est un arbre à excentrique dont la rotation produit un déplacement d'un écart prédéterminé du levier pivotant (4) sur l'organe de roulement (13) du second élément de transmission (12) le long de la courbe de commande (11).
  5. Distribution selon l'une des revendications 1 à 4,
    caractérisée en ce que
    le support (9) est de préférence fabriqué en matière plastique.
  6. Distribution selon la revendication 5,
    caractérisée en ce que
    le ressort de rotation (8) est fixé de manière amovible au support (9) par l'intermédiaire d'une liaison enclipée.
  7. Distribution selon la revendication 5 ou 6,
    caractérisée en ce que
    le support (9) avec le ressort de rotation (8) se fixe de manière rotative et amovible à l'arbre d'entraînement (2).
  8. Distribution selon l'une des revendications 2 à 7,
    caractérisée en ce que
    le ressort de rotation 48) est serré à l'aide du support (9) entre l'arbre d'entraînement (2) et l'organe de roulement (5) du levier pivotant (4) de façon que la force de ressort générée par le ressort rotatif (8) soit indépendante du déplacement du levier pivotant (4) par rapport au second élément de transmission (12).
EP05014341A 2004-07-20 2005-07-01 Distribution de moteur à combustion Expired - Fee Related EP1619362B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004035005A DE102004035005A1 (de) 2004-07-20 2004-07-20 Ventiltrieb einer Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP1619362A2 EP1619362A2 (fr) 2006-01-25
EP1619362A3 EP1619362A3 (fr) 2010-01-27
EP1619362B1 true EP1619362B1 (fr) 2011-04-20

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05014341A Expired - Fee Related EP1619362B1 (fr) 2004-07-20 2005-07-01 Distribution de moteur à combustion

Country Status (2)

Country Link
EP (1) EP1619362B1 (fr)
DE (2) DE102004035005A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005040959A1 (de) * 2005-08-30 2007-03-08 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb für eine Brennkraftmaschine
DE102006013915A1 (de) * 2006-03-25 2007-09-27 Daimlerchrysler Ag Hubübertragungsvorrichtung
JP5436103B2 (ja) * 2009-09-03 2014-03-05 株式会社オティックス 可変動弁機構
JP5294156B2 (ja) * 2009-11-12 2013-09-18 スズキ株式会社 内燃機関の可変動弁装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2363891A1 (de) * 1973-07-13 1975-06-26 Daimler Benz Ag Ventilverstellung fuer brennkraftmaschinen
DE2629554A1 (de) * 1976-07-01 1978-01-12 Daimler Benz Ag Lastregelung fuer gemischverdichtende brennkraftmaschinen mit ventilsteuerung
US4469056A (en) * 1983-02-22 1984-09-04 Tourtelot Jr Edward M Dual follower variable valve timing mechanism
DE4420064A1 (de) * 1994-06-08 1995-12-14 Bayerische Motoren Werke Ag Ventiltrieb mit variabler Steuerung der Ventilöffnungswinkel
US5937809A (en) * 1997-03-20 1999-08-17 General Motors Corporation Variable valve timing mechanisms
DE19913742A1 (de) * 1999-03-26 2000-09-28 Bayerische Motoren Werke Ag Vorrichtung zur Hubverstellung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine
DE10038743A1 (de) 2000-08-09 2002-02-21 Daimler Chrysler Ag Vorrichtung zur Entzündung eines brennbaren Gasgemischs für die Abgasanlage einer Brennkraftmaschine und entsprechende Abgasanlage
DE10237104A1 (de) * 2002-08-13 2004-02-26 Bayerische Motoren Werke Ag Ventiltrieb für eine Hubkolben-Brennkraftmaschine
US6684832B1 (en) * 2003-04-28 2004-02-03 Roberto Marcelo Codina Oscillating camshaft controlled valve operating device

Also Published As

Publication number Publication date
EP1619362A2 (fr) 2006-01-25
DE102004035005A1 (de) 2006-02-16
DE502005011266D1 (de) 2011-06-01
EP1619362A3 (fr) 2010-01-27

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