EP1484479A2 - Dispositif de commande variable de soupape pour moteur à combustion interne - Google Patents

Dispositif de commande variable de soupape pour moteur à combustion interne Download PDF

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Publication number
EP1484479A2
EP1484479A2 EP04102518A EP04102518A EP1484479A2 EP 1484479 A2 EP1484479 A2 EP 1484479A2 EP 04102518 A EP04102518 A EP 04102518A EP 04102518 A EP04102518 A EP 04102518A EP 1484479 A2 EP1484479 A2 EP 1484479A2
Authority
EP
European Patent Office
Prior art keywords
contoured
valve
fork
shaped member
movement
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.)
Withdrawn
Application number
EP04102518A
Other languages
German (de)
English (en)
Other versions
EP1484479A3 (fr
Inventor
Ennio Ascari
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.)
Hpe High Performance Engineering Srl
Original Assignee
Hpe High Performance Engineering Srl
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 Hpe High Performance Engineering Srl filed Critical Hpe High Performance Engineering Srl
Publication of EP1484479A2 publication Critical patent/EP1484479A2/fr
Publication of EP1484479A3 publication Critical patent/EP1484479A3/fr
Withdrawn legal-status Critical Current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
    • F01L13/0021—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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to a variable-lift timing system for an internal combustion engine.
  • this device comprises an intermediate rocker arm located between the camshaft and the valve rocker arm, and which, activated by the cam, in turn activates the valve rocker arm, and therefore the valve, by means of an appropriately shaped shoe.
  • the hinge location of the intermediate rocker arm is adjustable to vary the opening profile of the valve.
  • This system provides for considerable adjustment of the valve lift profile, but is debatable in terms of size, overall complexity, and by comprising a floating intermediate rocker arm (not hinged to the cylinder head) held in place by a return spring.
  • variable-lift timing system for an internal combustion engine, as claimed in Claim 1.
  • Number 10 in Figures 1 to 5 indicates a variable-lift timing system for an internal combustion engine 100.
  • internal combustion engine 100 comprises a cylinder head 101, in which conduits 102, 103 are formed for feeding air, with or without fuel, into a combustion chamber 104, or for expelling burnt gases from combustion chamber 104 to an exhaust device (not shown).
  • Each conduit 102, 103 has a valve 11 (only the one relative to conduit 103 is shown in Figures 2 to 5) comprising a rod 11a terminating with a head 11b for closing an outlet 103a of conduit 103 into respective combustion chamber 104.
  • Valve 11 is also acted on by known elastic return means (not shown) for restoring valve 11 to its initial position once valve 11 is acted on by an actuating mechanism 12 comprising a shaft 13 having one or more cams 14 in the first embodiment in Figures 1 to 6.
  • An intermediate assembly 15 is located between cam 14 and the end 11c of rod 11 opposite head 11b, and is divided into two separate contoured members 15a, 15b hinged about respective pivots 16, 17 fixed in known manner (not described) to cylinder head 101.
  • Member 15a comprises a contoured bottom surface 18 resting on end 11c of rod 11; and a top surface 19 (flat in the example shown in the accompanying drawings) on which a floating roller 20 rests for the reasons explained later on.
  • Floating roller 20 is free to rotate about its axis (a) and to translate along a trajectory determined by a fork-shaped member 23 described in detail later on.
  • Member 15b in turn comprises a bottom surface 21 (flat in the example shown in the accompanying drawings) which also contacts roller 20; and a top surface 22 acted on by cam 14.
  • Rollers 19, 21 may be shaped to move roller 20 according to predetermined laws of motion, and in any event must be such that, when fork-shaped member 23 is rotated in the rest condition (valve 11 closed), roller 20 is moved while remaining in contact at all times with both surfaces 19, 21.
  • valve 11 In actual use, when shaft 13 rotates in the direction of arrow F1, cam 14 rotates member 15b about pivot 17; which rotation is transmitted first to roller 20 and then to the other member 15a, which in turn, as stated, rotates about pivot 16. Since surface 18 of member 15a rests on end 11c, valve 11 is also moved in the direction and senses indicated by two-way arrow F2. The elastic return member (not shown) acting on valve 11 obviously ensures all the parts in the mechanism are maintained contacting throughout the travel of valve 11.
  • cam 14 As is known, continuous rotation of cam 14 produces a continuous variation in the position of valve 11 or so-called lift movement or profile.
  • varying the imposed trajectory of axis (a) of roller 20 by means of fork-shaped member 23 described later on), it is possible to vary the lift movement of the valve as a whole, which will always be characterized by being maximum for the same position of cam 14
  • the maximum value Hmax1 or Hmax2 of the distance between head 11b and outlet 103a depends on the position of fork-shaped member 23 guiding roller 20.
  • valve movement profile as a whole can be said to be characterized by lifts which increase as the distance, when valve 11 is closed, between roller 20 and pivot 16 of member 15a gets smaller.
  • Fork-shaped member 23 is rotated about a pivot 24, also fitted to cylinder head 101, by, for example, a contoured shaft 25 rotated about an axis 26 by means described below with reference to Figure 1.
  • slot 23a as opposed to being straight, is curved to impose a given trajectory on roller 20.
  • the lift of valve 11 is reduced by simply moving roller 20 in the direction of arrow F6, either by continuing to rotate contoured shaft 25 in the direction of arrow F3 and exploiting the profile of contoured shaft 25, or by inversely rotating fork-shaped member 23 in the direction of arrow F7 by rotating contoured shaft 25 in the direction of arrow F8, thus moving roller 20 away from pivot 16 of member 15a and towards pivot 17 of member 15b.
  • the lift movement is varied by varying, by means of fork-shaped member 23, the trajectory roller 20 is permitted to describe by rotation of member 15b.
  • Fork-shaped member 23 may also be provided with an elastic retaining system for holding it in contact with its position adjusting system (contoured shaft 25 in the example shown) and preventing possible vibratory movements when fork-shaped member 23 is subjected to no load (in the rest position).
  • the angular position of contoured shaft 25 may be determined using a system controlled by an electronic central control unit 29, as shown in Figure 1.
  • Central control unit 29 receives input data relative to the operating conditions, and to control of the regulating members, of internal combustion engine 100, and processes the input data to rotate contoured shaft 25 in the direction of arrow F3 or F8, and so move fork-shaped member 23, and position roller 20, accordingly.
  • contoured shaft 25 may be rotated by means of an electric motor 30 controlled by electronic central control unit 29.
  • the output shaft 31 of electric motor 30 is fitted with a first gear 32a, which meshes with a second gear 32b integral with a worm 33.
  • Worm 33 engages an internal thread formed in a bush 34, to which two cranks 37, 38, both integral with contoured shaft 25, are hinged by respective pins 35, 36.
  • Rotation of contoured shaft 25 may be controlled using a known position sensor 39 connected electrically to electronic central control unit 29.
  • electronic central control unit 29 supplies electric motor 30 with a signal indicating the direction in which gear 32a is to be rotated.
  • Rotation of gear 32a obviously rotates worm 33 and moves bush 34 in either one of the senses indicated by two-way arrow F9, thus rotating contoured shaft 25, and so rotating fork-shaped member 23, resting against contoured shaft 25, about pivot 24. Since pins 20a are housed inside the slot 23a defined by the prongs 27 of fork-shaped member 23, rotation of fork-shaped member 23 produces a shift in the trajectory along which the axis (a) of roller 20 can move, thus changing the lever ratios and therefore the lift movement of valve 11 (compare Figures 2 and 4).
  • Figure 7 shows a second embodiment, in which the same camshaft 13 activates two separate valves 111 and 112, and which comprises one contoured shaft 25, one fork-shaped member 23, and one roller 20 astride two intermediate assemblies 150, 151, each relative to a corresponding valve 111, 112. Operation is practically the same as described with reference to the first embodiment in Figures 1 to 6.
  • Figure 8 shows a third embodiment of the present invention, which simultaneously activates two valves 111, 112, as in the second embodiment in Figure 7, but which comprises two fork-shaped members 130, 131 integral with each other and rotating about the same pivot 24. Operation is the same as described with reference to the other embodiments.
  • the timing system according to the present invention has the following advantages:

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP04102518A 2003-06-06 2004-06-04 Dispositif de commande variable de soupape pour moteur à combustion interne Withdrawn EP1484479A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO20030347 ITBO20030347A1 (it) 2003-06-06 2003-06-06 Sistema di distribuzione ad alzata variabile per un motore endotermico.
ITBO20030347 2003-06-06

Publications (2)

Publication Number Publication Date
EP1484479A2 true EP1484479A2 (fr) 2004-12-08
EP1484479A3 EP1484479A3 (fr) 2005-08-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04102518A Withdrawn EP1484479A3 (fr) 2003-06-06 2004-06-04 Dispositif de commande variable de soupape pour moteur à combustion interne

Country Status (2)

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EP (1) EP1484479A3 (fr)
IT (1) ITBO20030347A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006120050A1 (fr) 2005-05-12 2006-11-16 Luigi Conti Moteur a combustion interne dote d’un systeme de levee de soupape a variation continue

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1234968A2 (fr) 2001-02-15 2002-08-28 Bayerische Motoren Werke Aktiengesellschaft Procédé pour synchroniser le remplissage de cylindres d'un moteur à combustion interne

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE370440A (fr) *
FR2472078A1 (fr) * 1979-12-21 1981-06-26 Baguena Michel Distribution variable pour moteur a quatre temps
JPS60228717A (ja) * 1984-04-27 1985-11-14 Suzuki Motor Co Ltd ４サイクルエンジンのバルブリフト可変装置
JP2944264B2 (ja) * 1991-07-23 1999-08-30 株式会社ユニシアジェックス 内燃機関の動弁装置
DE10117584A1 (de) * 2001-04-07 2002-10-10 Willi Roth Vorrichtung zum stufenlosen variieren des Hubes der Gaswechselventile von Verbrennungsmotoren
DE10136612A1 (de) * 2001-07-17 2003-02-06 Herbert Naumann Variable Hubventilsteuerungen

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1234968A2 (fr) 2001-02-15 2002-08-28 Bayerische Motoren Werke Aktiengesellschaft Procédé pour synchroniser le remplissage de cylindres d'un moteur à combustion interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006120050A1 (fr) 2005-05-12 2006-11-16 Luigi Conti Moteur a combustion interne dote d’un systeme de levee de soupape a variation continue
US7665434B2 (en) 2005-05-12 2010-02-23 Luigi Conti Internal combustion engine with continuous variable valve lift system

Also Published As

Publication number Publication date
EP1484479A3 (fr) 2005-08-24
ITBO20030347A1 (it) 2004-12-07

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