EP1268988B1 - Commande de soupape variable avec element coulissant et course a vide - Google Patents

Commande de soupape variable avec element coulissant et course a vide Download PDF

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Publication number
EP1268988B1
EP1268988B1 EP01927792A EP01927792A EP1268988B1 EP 1268988 B1 EP1268988 B1 EP 1268988B1 EP 01927792 A EP01927792 A EP 01927792A EP 01927792 A EP01927792 A EP 01927792A EP 1268988 B1 EP1268988 B1 EP 1268988B1
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EP
European Patent Office
Prior art keywords
valve
cam
sliding
cam follower
valve train
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
EP01927792A
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German (de)
English (en)
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EP1268988A1 (fr
Inventor
Rainer Wurms
Stefan Dengler
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.)
Audi AG
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Audi AG
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Filing date
Publication date
Application filed by Audi AG filed Critical Audi AG
Publication of EP1268988A1 publication Critical patent/EP1268988A1/fr
Application granted granted Critical
Publication of EP1268988B1 publication Critical patent/EP1268988B1/fr
Anticipated expiration legal-status Critical
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
    • 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
    • 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

Definitions

  • the invention relates to a variable valve control for reciprocating engines, in particular internal combustion engines, according to the preamble of claim 1.
  • Such a variable valve control shows the DE 42 23 173 A1, in which an adjustable in the cylinder head of the engine link member with an adjusting ramp and a roller between the cam of a camshaft on the one hand and the bucket tappet on the shaft end of a globe valve on the other hand is switched.
  • an adjustable in the cylinder head of the engine link member with an adjusting ramp and a roller between the cam of a camshaft on the one hand and the bucket tappet on the shaft end of a globe valve on the other hand is switched.
  • By moving the slide member relative to the cam both a full stroke and partial strokes can be controlled to zero stroke.
  • a valve actuation occurs at full stroke, which results in terms of valve lift and speed profile of the geometry of the cam and the Verstellrampe and which can be optimized accordingly.
  • the object of the invention is to provide a variable valve control of the generic type, which allows large valve lift changes with a largely smooth valve actuation and the robust design and cost manufacturable.
  • the cam and the valve operating element in particular a rocker arm, a free travel, which causes a pre-acceleration (excitation movement) of the roller package both full stroke and in the partial strokes of the lift valve, so that the generating movement (opening movement) of the lift valve with positive and negative desired valve acceleration is controlled substantially by the Verstellrampe the gate part.
  • This decoupling of excitation movement and generation movement which is carried out by the geometric design of the cam and the adjustment ramp, creates a speed profile largely independent of the set valve lift without increased acceleration peaks and, associated therewith, a robust valve drive improved in terms of wear and operating noise.
  • valve train also allows larger valve strokes or a larger Hubverstell Scheme due to the use of a rocking lever with the associated lower leverage ratios and due to the general arrangement of Verstellrampe approximately perpendicular to the cam axis, the smaller lateral emigration of the roll package in particular cause in the excitement.
  • Aniauf the rocker arm for the roll package can be aligned parallel to the direction of the sliding part.
  • the Verstellrampe the link member is formed in a slot-shaped slotted guide, the opposite guide surface forms a Vorbevantungsrampe in the excitation movement of the roll package, which represents a jerk-free transition in the start-ramp section of the Verstellrampe for generating movement. This results in a smooth sliding sliding the roll package on the rocker arm with subsequent seamless generation movement.
  • the roller package can be advantageously biased by means of at least a simple leg spring against the cam.
  • the leg spring may preferably be supported on the link part with the one leg and acts with a second, extended leg on the roller package, this biasing against the cam.
  • the roller package can lift off from the rocker arm - whereby a permanent contact between the roller package and the cam is made - and it can be made on the compensating element backlash between the rocker arm, the cam member and the valve stem.
  • the rocker arm in order to achieve a rigid and high design accuracy producing construction of the rocker arm is pivotally mounted in the cylinder head via at least one rocker arm axis.
  • the hydraulic valve clearance compensation element could be arranged on the cooperating with the shaft end of the lift valve end of the rocking lever.
  • Figs. 1 and 2 10 designates a camshaft which is rotatably mounted in a cylinder head 12 only partially shown a multi-cylinder reciprocating internal combustion engine and carries cam 14 for actuating inlet globe valves, with only one globe valve or its Vertilschaft 16th is shown.
  • a link member 18 is slidably mounted in the cylinder head 12 via fitting holes 20 on stationary guide pins 22.
  • the slide part 18 can be adjusted in the direction of the double arrow 24 by means of an adjustment device (not shown) (eg an eccentric shaft which is hydraulically or electrically adjusted).
  • the approximately U-shaped link member 18 with a base wall 56 has in the lateral legs 26,28 depending on a slotted guide with a Verstellrampe 30 and a Vorbenchungsrampe 32.
  • roller package 34 In the upwardly open, slot-shaped slotted guide 30,32 a roller package 34 is slidably inserted.
  • the roller package 34 has a central roller 34 a (FIG. 2) which starts against the cam 14.
  • Adjacent to the left and right are two further rollers 34b, 34c, which roll on the abutment surfaces 36a, 36b of an oscillating lever 36, said rollers being mounted roller-mounted on a transmission pin 34d, which cooperates with the said ramps 30,32.
  • the rocker arm 36 is composed of a first, H-shaped rocker arm part 40 and an intermediate rocker arm part 42, which are arranged as follows:
  • the first oscillating lever part 40 is pivotally mounted on stationary oscillating lever axles 46 via bearing bores 44 and carries the abutment surfaces 36a, 36b for the rollers 34b, 34c of the roller package 34. Furthermore, the oscillating lever part 40 has a transverse driver 48 which is disposed on the second oscillating lever part arranged therebetween 42 acts in the manner of a rocker.
  • the second oscillating lever part 42 is supported, on the one hand, via a ball socket 50 on a valve play compensation element 52 having a corresponding ball head, which is arranged in the cylinder head 12 as shown. Its other end carries a driver 53 which cooperates with the shaft end of the lift valve 16.
  • the described arrangement creates an exact valve actuation with a resting valve clearance compensation element 52 (lower moving masses).
  • the adjustment ramp 30 as a whole is approximately perpendicular to the adjustment direction 24 of the link member 18 and the roller package 34 acts on the rocker arm 36, wherein its contact surfaces 36a, 36b are aligned parallel to the adjustment direction 24.
  • the rocker arm 36 is located substantially below the camshaft axis of rotation 10 a between the tangential to the cam 14 adjustable link member 18 and the lift valve sixteenth
  • the oscillating lever 36 (see Fig. 3 and 4) and its oscillating lever part 40 is in the position shown in FIG. 1 and 2 (corresponds to the full stroke) with the lift valve 16 closed to a stop 54 of the base wall 56 of the link member 18, wherein the rocker arm 36 is kept free of play via the valve play compensation element 52.
  • roller package 34 has a free travel s, viewed between the contact surfaces 36a, 36b of the rocker arm 36 and the base circle 14b of the cam 14th
  • the roller package 34 is first pre-accelerated in an excitation movement in the region of the free travel s, wherein this Leerweg s with decreasing valve lift (adjustment of the link member 18 in FIG. 1 of the drawing to the right) increases accordingly.
  • This excitation movement of the roller package 34 increases by the illustrated shape of the Vorbeschreibungsrampe 30 until the transmission pin 34d moves to the Anfauframpen section 30a of the Verstellrampe 30, while at the same time runs over the rollers 34b, 34c on the thrust surfaces 36a, 36b of the rocker arm 36 and in the further generating movement, the lift valve 16 is actuated.
  • the section 30a runs essentially substantially tangentially to the cam 14 or its arrival and departure ramp.
  • FIG. 5 shows the movement curves during a full stroke and FIG. 6 shows the movement curves during a partial lift of the lift valve 16.
  • the vertical lines indicate the respective valve lift s v .
  • the curve a corresponds to the adjustment movement of the roller package 34, the proportions of the excitation movement corresponding to the free travel s of the roller package 34.
  • the curve d describes the geometric design of the Verstellrampe 30, which in conjunction with the interpretation of the curve a, the actual valve lift according to curve e over the valve lift s v results.
  • the further curve f describes the profile of the valve acceleration, it being noteworthy that the acceleration peaks at full stroke (FIG. 5) and partial stroke (FIG. 6) are approximately equal.
  • the described valve train thus enables "full" valve lift curves e for the full stroke of the lift valves 16, without increased acceleration peaks during partial lift.

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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

L'invention concerne une commande de soupape variable pour moteur à piston alternatif, notamment pour moteur à combustion interne, comprenant au moins une came disposée sur un arbre à cames logé rotatif dans une culasse de cylindres. Ladite came actionne une soupape par l'intermédiaire d'un ensemble à rouleaux guidé dans une partie coulissante le long d'une rampe de déplacement et d'un élément d'actionnement de la soupape disposé en aval. La course de la soupape est réglable grâce au déplacement de la partie coulissante relativement à la came. L'ensemble à rouleaux est précontraint élastiquement contre ladite came. L'invention est caractérisée en ce qu'une course à vide (s), permettant un mouvement d'excitation de l'ensemble à rouleaux, est située entre le cercle de base de la came et l'élément d'actionnement de la soupape, afin de réaliser une commande de soupape robuste aux accélérations régulières. Selon l'invention, l'élément d'actionnement de la soupape est de préférence un levier oscillant constitué de deux parties et doté d'une fonction de bascule, et la partie coulissante comporte de préférence un guide de coulisse doté d'une rampe de préaccélération supplémentaire pour l'ensemble à rouleaux.

Claims (13)

  1. Commande de soupape variable pour moteurs à piston alternatif, en particulier moteurs à combustion interne, avec au moins une came d'un arbre à cames monté rotatif dans une tête de cylindre, laquelle came commande une soupape à course rectiligne par le biais d'un ensemble de rouleaux guidé de manière à être poussé le long d'une rampe de réglage dans un élément coulissant et d'un élément de commande de soupape placé après, sachant que la soupape à course rectiligne peut être réglée de manière variable par le déplacement de l'élément coulissant par rapport à la came et que l'ensemble de rouleaux est précontraint par ressort contre les cames.
    caractérisé en ce que,
    entre le cercle de base des cames (14b) et l'élément de commande de la soupape (36), est prévue une rampe de pré-accélération (32) permettant une pré-accélération comme mouvement d'excitation de l'ensemble de rouleaux (34) dans la zone d'une course à vide (s), sachant que l'ensemble de rouleaux (34) est relevé avec une installation dans la zone du cercle de base de cames (14b) correspondant à la course à vide (s) à partir de l'élément de commande de la soupape (36).
  2. Commande de soupape selon la revendication 1, caractérisée en ce que le mouvement d'excitation de l'ensemble de rouleaux (34) correspond à l'accélération initiale et à la décélération finale du contour de la came (14, figure 5, courbe a, course à vide s).
  3. Commande de soupape selon la revendication 1 ou 2, caractérisée en ce que la rampe de réglage (30) est alignée au total à peu près perpendiculairement au mouvement de réglage (flèche double 24) de l'élément coulissant (18) et en ce que l'ensemble de rouleaux (34) agit sur un levier oscillant (36) appuyé de manière mobile d'un côté, qui est disposé pour l'essentiel en dessous de l'axe de rotation des arbres à cames (10a) entre l'élément coulissant (18) réglable tangentiellement à la came (14) et l'extrémité de la tige de la soupape à course rectiligne (16).
  4. Commande de soupape selon les revendications 1 à 3, caractérisée en ce que la rampe de réglage (30) comporte un tronçon de rampe de démarrage (30a) passant presque tangentiellement par rapport à la came (14).
  5. Commande de soupape selon les revendications 3 et 4, caractérisée en ce que les surfaces d'arrêt (36a, 36b) du levier oscillant (16) sont dirigées parallèlement au sens de déplacement (24) de l'élément coulissant (18) pour l'ensemble de rouleaux (34).
  6. Commande de soupape selon une ou plusieurs des revendications 1 à 5, caractérisée en ce que la rampe de réglage (30) est réalisée dans un guidage coulissant en forme de fente, dont la surface de guidage opposée forme une rampe de pré-accélération (32) pour le mouvement d'excitation (course à vide s) de l'ensemble de rouleaux (34).
  7. Commande de soupape selon une ou plusieurs des revendications 1 à 6, caractérisée en ce que l'ensemble de rouleaux (34) est précontraint au moins par un ressort hélicoïdal (56) contre la came (14).
  8. Commande de soupape selon la revendication 7, caractérisée en ce qu'au moins un ressort hélicoïdal (56) est tenu avec l'une de ses branches (56b) directement contre l'élément coulissant (18).
  9. Commande de soupape selon une ou plusieurs des revendications 1 à 8, caractérisée en ce que le levier oscillant (36) se trouve dans la position finale de la soupape à course rectiligne (16) contre une butée (54) de l'élément coulissant (18).
  10. Commande de soupape selon une ou plusieurs des revendications 1 à 9, caractérisée en ce que l'élément coulissant (19) est guidé par le biais d'alésages ajustés (20) correspondants sur des goupilles de guidage (22) fixées à la tête de cylindre (12).
  11. Commande de soupape selon une ou plusieurs des revendications 1 à 10, caractérisée en ce que le levier oscillant (36) est logé de manière orientable par le biais d'un ou de plusieurs axes de levier oscillant (46).
  12. Commande de soupape selon une ou plusieurs des revendications 1 à 11, caractérisée en ce que le levier oscillant (36) est réalisé au moins en deux parties, sachant que le premier élément du levier oscillant (40) est logé de manière orientable par le biais des axes du levier oscillant (46) et comporte les surfaces d'arrêt (36a) pour l'ensemble de rouleaux (34) et coopère par commande avec un deuxième élément du levier oscillant ajouté en parallèle, qui est en appui de manière orientable d'une part sur un élément de compensation hydraulique du jeu de soupape (52)et d'autre part est en prise à l'extrémité de la tige de la soupape à course rectiligne (16).
  13. Soupape de commande selon la revendication 12, caractérisée en ce que le premier élément de levier oscillant (40) est réalisé en forme de H avec deux tronçons de course avec surfaces d'arrêt (36a) et un entraînement s'étendant transversalement(48) agissant sur le deuxième élément de levier oscillant et en ce que le deuxième élément de levier oscillant (42) passe entre les deux tronçons de course du premier élément de levier oscillant (40).
EP01927792A 2000-03-31 2001-03-23 Commande de soupape variable avec element coulissant et course a vide Expired - Lifetime EP1268988B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10016103A DE10016103A1 (de) 2000-03-31 2000-03-31 Variable Ventilsteuerung
DE10016103 2000-03-31
PCT/EP2001/003342 WO2001075279A1 (fr) 2000-03-31 2001-03-23 Commande de soupape variable avec element coulissant et course a vide

Publications (2)

Publication Number Publication Date
EP1268988A1 EP1268988A1 (fr) 2003-01-02
EP1268988B1 true EP1268988B1 (fr) 2006-03-08

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ID=7637154

Family Applications (1)

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EP01927792A Expired - Lifetime EP1268988B1 (fr) 2000-03-31 2001-03-23 Commande de soupape variable avec element coulissant et course a vide

Country Status (6)

Country Link
US (1) US6715456B2 (fr)
EP (1) EP1268988B1 (fr)
JP (1) JP2003529708A (fr)
DE (2) DE10016103A1 (fr)
ES (1) ES2256231T3 (fr)
WO (1) WO2001075279A1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10136612A1 (de) * 2001-07-17 2003-02-06 Herbert Naumann Variable Hubventilsteuerungen
US6837475B2 (en) * 2001-09-21 2005-01-04 Honda Giken Kogyo Kabushiki Kaisha Valve-operating device for engine
DE10235403A1 (de) * 2002-08-02 2004-02-12 Bayerische Motoren Werke Ag Schwenkhebel für einen hubvariablen Ventiltrieb
DE10239908A1 (de) 2002-08-30 2004-02-26 Audi Ag Variable Ventilsteuerung
DE10239909A1 (de) * 2002-08-30 2004-02-26 Audi Ag Variable Ventilsteuerung
JP4093849B2 (ja) * 2002-11-29 2008-06-04 株式会社オティックス 可変動弁機構
DE10303128A1 (de) * 2003-01-28 2004-07-29 Fev Motorentechnik Gmbh Vollvariabler mechanischer Ventiltrieb für eine Kolbenbrennkraftmaschine mit justierbarem Ventilspielausgleich
JP4278590B2 (ja) 2004-08-31 2009-06-17 株式会社日立製作所 内燃機関の可変動弁装置
JP2006283630A (ja) * 2005-03-31 2006-10-19 Honda Motor Co Ltd エンジンの動弁装置
DE102005026054B4 (de) 2005-06-07 2007-04-12 Dr.Ing.H.C. F. Porsche Ag Verfahren und Vorrichtung zur Überwachung der Funktionstüchtigkeit einer Ventilhub-Verstelleinrichtung einer Brennkraftmaschine in einer Kaltstartphase
EP2157292A1 (fr) 2008-08-20 2010-02-24 Delphi Technologies, Inc. Ensemble de soupape d'échappement pour moteur à combustion interne
EP2184453A1 (fr) 2008-11-05 2010-05-12 Delphi Technologies, Inc. Ensemble de soupape d'échappement pour moteur à combustion interne
US9133735B2 (en) 2013-03-15 2015-09-15 Kohler Co. Variable valve timing apparatus and internal combustion engine incorporating the same
DE102018130428A1 (de) * 2018-11-30 2020-06-04 Bayerische Motoren Werke Aktiengesellschaft Hubvariabler Ventiltrieb mit wenigstens zwei Arbeitslagen
DE102019133590A1 (de) * 2019-12-09 2021-06-10 Bayerische Motoren Werke Aktiengesellschaft Hubsteller für einen hubvariablen Ventiltrieb mit zwei Arbeitslagen

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US4138973A (en) * 1974-06-14 1979-02-13 David Luria Piston-type internal combustion engine
US4526142A (en) * 1981-06-24 1985-07-02 Nissan Motor Company, Limited Variable valve timing arrangement for an internal combustion engine or the like
DE3833540A1 (de) * 1988-10-01 1990-04-12 Peter Prof Dr Ing Kuhn Vorrichtung zur betaetigung der ventile an verbrennungsmotoren mit veraenderlicher ventilerhebungskurve
DE4135257C2 (de) * 1991-10-25 1998-09-03 Peter Prof Dr Ing Kuhn Vorrichtung zur Betätigung der Ventile in Verbrennungsmotoren mittels umlaufender Nocken
DE4221134C1 (fr) * 1992-06-27 1993-07-01 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4223173A1 (de) 1992-07-15 1994-01-20 Bayerische Motoren Werke Ag Ventiltrieb einer Brennkraftmaschine
DE4322480C2 (de) * 1993-07-06 1996-05-02 Meta Motoren Energietech Vorrichtung zur variablen Ventilsteuerung von Brennkraftmaschinen
EP0638706A1 (fr) * 1993-08-05 1995-02-15 Bayerische Motoren Werke Aktiengesellschaft Dispositif de commande d'actionnement des soupapes d'un moteur à combustion interne
IT1285853B1 (it) * 1996-04-24 1998-06-24 Fiat Ricerche Motore a combustione interna con valvole ad azionamento variabile.
DE19701203A1 (de) * 1997-01-15 1998-07-23 Daimler Benz Ag Variable Ventilsteuerung für Brennkraftmaschinen
AUPO508497A0 (en) * 1997-02-13 1997-03-06 Armstrong, Mark Frederick Improvements in poppet valve actuation

Also Published As

Publication number Publication date
WO2001075279A1 (fr) 2001-10-11
DE10016103A1 (de) 2001-10-04
US6715456B2 (en) 2004-04-06
JP2003529708A (ja) 2003-10-07
DE50109157D1 (de) 2006-05-04
ES2256231T3 (es) 2006-07-16
EP1268988A1 (fr) 2003-01-02
US20030037739A1 (en) 2003-02-27

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