WO2003069134A1 - Actionneur rotatif, notamment pour distribution a programme variable et/ou mecanisme d'actionnement de soupape a disque variable - Google Patents

Actionneur rotatif, notamment pour distribution a programme variable et/ou mecanisme d'actionnement de soupape a disque variable Download PDF

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Publication number
WO2003069134A1
WO2003069134A1 PCT/EP2003/050001 EP0350001W WO03069134A1 WO 2003069134 A1 WO2003069134 A1 WO 2003069134A1 EP 0350001 W EP0350001 W EP 0350001W WO 03069134 A1 WO03069134 A1 WO 03069134A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
rotary actuator
actuator according
worm
worm gear
Prior art date
Application number
PCT/EP2003/050001
Other languages
English (en)
Inventor
Jean-François Berlemont
Dominique Bodart
Manfred Kolkman
Original Assignee
Delphi Technologies, Inc.
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 Delphi Technologies, Inc. filed Critical Delphi Technologies, Inc.
Publication of WO2003069134A1 publication Critical patent/WO2003069134A1/fr

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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
    • 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
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • 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
    • 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
    • F01L2013/0073—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 "Delphi" type

Definitions

  • the present invention generally relates to a rotary actuator, in particular for a variable valve timing and/or variable valve lift valve actuating mechanism.
  • variable valve timing and/or variable valve lift valve actuating mechanisms has the capability of potentially improving the system performance of an engine by reducing pump work and valve train friction, controlling engine load and internal exhaust dilution, improving charge preparation, increasing peak power and enabling the use of various transient control strategies not otherwise available.
  • US 6,019,076 discloses a variable valve timing mechanism, which is ap- plicable for operating individual or multiple valves.
  • dual engine valves are driven by an oscillatable rocker cam that is actuated by a linkage driven by a rotary cam.
  • the linkage is pivoted on a control member that is in turn pivotable about the axis of the rotary cam and angularly adjustable to vary the orientation of the rocker cam and thereby vary the valve lift and timing.
  • the rotary cam is carried on a camshaft and the oscillatable rocker cam is pivoted on the rotational axis of the rotary cam.
  • a control shaft connects with the control member through an angled slider and slot connection that provides a variable angular ratio for improved charge control at low valve lifts.
  • a rotary actuator is applied to drive the control shaft to its various angular positions. It includes a small electric motor that drives a worm through a shaft. The worm engages a worm gear formed as a segmented gear. The worm gear is directly connected to an end of the control shaft for rotating the control shaft through its full angular motion.
  • the mechanism driven by the control shaft generates some reaction torque on the control shaft itself, and thus on the actuator mechanism.
  • fluctua- tions in reaction torque can cause some uncontrolled movements in the actuator mechanism. This diminishes the accuracy of actuator positioning, generates some noise and causes an intensive wear of the actuator elements.
  • a spiral spring is generally provided to apply a biasing torque on the worm gear.
  • the biasing torque has to be larger than the maximum reaction torque from the driven mechanism.
  • the spring generally provides a linear torque in function of the angular position of the worm gear. Therefore, if the maximum reaction torque occurs after a small angular displacement, the biasing torque will be much larger than necessary for a greater angular displacement. This negatively impacts the power consumption of the actuator, as well as its response time.
  • Another disadvantage of such an actuator is that an extra space is required for accommodating the spiral spring, which increases the actuator size.
  • the object of the present invention is to provide an improved rotary actuator, which does not present the above-mentioned disadvantages. This object is achieved by a rotary actuator as claimed in claim 1.
  • a rotary actuator comprises a worm gear to be coupled to an actuatable element.
  • a worm engages the worm gear so as to rotate the latter and a motor is provided for driving the worm.
  • the rotary actuator comprises hydraulic biasing means for transmitting a biasing torque to the worm gear in such a way as to bias it in one rotating direction.
  • a hydraulic biasing means permits to apply a biasing torque, which does not depend on the angular position of the worm gear.
  • the hydraulic biasing means will preferably be designed in such a way that the biasing torque exceeds the maximum reaction torque expected from the mechanism driven by the actuator.
  • the different elements of the actuator mechanism, and in particular the worm and the worm gear will remain wedged against each other in the same way, even if there is lash in the actuator mechanism. Fluctua- tions in reaction torque will thus not affect the actuator mechanism, whereby positioning accuracy is improved, efficiency is maintained, and noise and wear are reduced.
  • the biasing torque will not necessarily increase with the angular displacement, driving of the worm gear requires less power from the motor driving the worm, thereby allowing energy savings.
  • the worm gear is preferably formed as a segmented gear having a hub and a gear portion. Moreover, the segmented gear comprises a force transmitting element connected to the gear hub and having an essentially radially extending biasing surface loaded by a hydraulic fluid. The worm gear is thus biased by a hydraulic fluid. The pressure of the hydraulic fluid and the area of the biasing surface can be set to obtain the desired biasing torque.
  • the actuator shall preferably be designed in such a way that when the force transmitting element rotates with the worm gear, the biasing surface has a constant area. Hence, if the hydraulic pressure delivered by the hydraulic pressure source is constant, the biasing torque will remain constant irrespective of the angular position of the worm gear.
  • the actuator comprises a body with a cavity therein, this cavity having the form of a cylindrical sector dimensioned in such a way as to allow rotation of the worm gear therein.
  • the cavity in the actuator body cooperates with the force transmitting element and the hub to form a pressure chamber for the hydraulic fluid, wherein the biasing surface forms an inner surface of the pressure chamber.
  • the pressure chamber comprises an abutment surface for the force transmitting element, which defines an angular stop position of the segmented gear.
  • the supply of hydraulic fluid from the hydraulic pressure source to the pressure chamber is preferably done through a hydraulic pressure passage in the actuator body, which opens into the pressure chamber in the abutment surface.
  • the hydraulic pressure source to be in communication with the pressure chamber in any position of the segmented gear, so that the pressure exerted by the hydraulic fluid can be permanently controlled, whenever the size of the pressure chamber is increased or decreased due to rotation of the worm gear.
  • the desired pressure can be maintained in the pressure chamber, so as to allow a precise control of the biasing torque.
  • the use of such a pressure chamber allows to obtain a very compact actuator.
  • the force transmitting element may have an end portion protruding beyond the gear portion in radial direction, this end portion being in contact with the inner surface of the cavity.
  • a sealing member shall advantageously border the force transmitting ele- ment and the hub portion forming the pressure chamber.
  • the force transmitting element is preferably contiguous to the gear portion of the segmented gear.
  • the actuatable element may be directly connected to the worm gear.
  • the actuatable element may e.g. be a rotary shaft mounted in the hub.
  • the actuatable element may however also be coupled to the worm gear through a connecting element, such as e.g. an output shaft mounted in a central bore in the hub and connected to the actuatable element.
  • a connecting element such as e.g. an output shaft mounted in a central bore in the hub and connected to the actuatable element.
  • the output shaft may comprise a force transmitting element loaded by the hydraulic fluid.
  • the present rotary actuator is particularly well adapted to be used with a variable valve timing and/or variable valve lift valve actuating mechanism, for e.g. actuating the mechanism controlling the valve lift.
  • the actuator may either be provided in an individual housing, or integrated in the cylinder head.
  • the oil of the cylinder head will preferably be used as hydraulic fluid for the rotary actuator.
  • the oil pressure in the cylinder head will generally be sufficient to produce a biasing torque on the worm gear that is superior to the maximum reaction torque from the mechanism driven by the rotary actuator.
  • Fig.1 is a sectional view through a first embodiment of a rotary actuator in accordance with the present invention, the segmented gear being in one end position;
  • Fig.2 is a perspective view of the segmented gear of the rotary actuator of Fig.1 ;
  • Fig.3 is a sectional view of the rotary actuator of Fig.1 showing the segmented gear in the other end position.
  • similar or equivalent elements are indicated by same reference signs.
  • Fig.1 shows a preferred embodiment of a rotary actuator 10 in accordance with the present invention.
  • the actuator 10 comprises a body 12 and is adapted to effect the actuation of a rotary output shaft 14.
  • Such an actuator 10 is particularly suited for actuation of a variable valve timing and/or variable lift valve actuating mechanism in an internal combustion engine.
  • the output shaft 14 is coupled to the variable timing and/or variable lift valve actuating mechanism so that rotation of the output shaft 14 allows to control the valve lift.
  • reference sign 16 indicates a worm that is provided about an elongate shaft 18, which is mounted for rotation in the actuator body 12 by means of roller bearings 20, 20' or the like.
  • the worm 16 may either be integral with the elongate shaft 18 or mounted thereon.
  • the elongate shaft 18 is connected to a driving motor (e.g. an electric motor; not shown) for driving the worm 16.
  • Reference sign 22 indicates a segmented gear rotatably mounted in the actuator body 12.
  • the segmented gear 22 comprises a hub 24 and a gear portion 26, preferably integral with each other (see also Fig.2). Furthermore, the hub 24 has a central bore 28 in which the output shaft 14 is mounted.
  • the axis of rotation 30 of the segmented gear 22 is perpendicular to and spaced from the axis of rotation 32 of the worm 16 so that the gear portion 26 is in mesh with the worm 16 and that accordingly rotation of the worm 16 effects rotation of the segmented gear 22.
  • the present rotary actuator 10 comprises a hydraulic biasing means for transmitting a biasing torque to the segmented gear 22 to bias it in one of its rotating directions, indicated by arrow 34 in Fig.1.
  • the segmented gear 22 comprises a force transmit- ting element 36, which is connected to the hub 24.
  • the force transmitting element 36 has an end portion 38 which protrudes beyond the gear portion 26 in radial direction.
  • This force transmitting element 36 is preferably contiguous to, and integral with, the gear portion 26 and has an essentially radially extending biasing surface 40.
  • Reference sign 42 indicates a cavity in the actuator body 12 having the form of a cylindrical sector, the cylindrical surface 44 of the cavity 42 having an axis coaxial with the rotations] axis 30 of the segmented gear 22.
  • the cavity 42 cooperates with the force transmitting element 36 and the hub 24 to form a pressure chamber, the biasing surface 40 forming a surface of this pressure chamber.
  • a hydraulic pressure source (not shown) delivers a hydraulic fluid, which is supplied to the pressure chamber through a hydraulic fluid passage 46 in the actuator body 12.
  • the hydraulic fluid thus fills the cavity 42 and loads the biasing surface 40 of the force transmitting element 36.
  • a biasing torque is transmitted to the worm gear 22, which is biased in the direction of arrow 34.
  • the rotational travel of the segmented gear 22 is limited by two abutment surfaces 48, 48', which are spaced from the rotational axis 30 of the segmented gear 22 at a distance greater than the outer diameter of the hub 24 but less than the outside radius of the gear portion 26. Consequently, as can be seen in Fig.1, with extreme counter-clockwise rotation of the segmented gear 22, the end surface 50 of the gear portion 26 abuts against the first abutment surface 48 and thereby limits the counter-clockwise rotation of the segmented gear 22. Conversely, upon extreme clockwise rotation of the segmented gear 22, the biasing surface 40 abuts against the other abutment surface 48' of the actuator body 12 and thereby limits the counter-clockwise rotational travel of the segmented gear 22.
  • the second abutment surface 48' is part of the pressure chamber, and that the hydraulic fluid passage 46 opens into the pressure chamber in this abutment surface 48'. Hence, the hydraulic fluid passage 46 is in communication with the pressure chamber in any position of the segmented gear 22.
  • the size of the cavity 42 is such that the end portion 38 of the force transmitting element 36 remains in contact with the cylindrical surface 44 over its whole angular motion, whereby a closed pressure chamber is obtained.
  • the segmented gear 22 is advantageously provided with a seal 52 that surrounds the force transferring member 36 and the part of the hub 24 cooperating in the formation of the pressure chamber so as to avoid any leakage of hydraulic fluid. As can be seen from Figs.1 and 3, as the segmented gear 22 is rotated in the counter-clockwise direction, the size of the pressure chamber increases and the area of the biasing surface 40 remains constant whereas a larger part of the hub 24 is in the pressure chamber.
  • the pressure exerted by the hydraulic fluid on the hub has no incidence on the biasing torque.
  • the area of the biasing surface 40 remains constant, the biasing torque on the segmented gear 22 only depends on the pressure exerted by the hydraulic fluid.
  • the biasing torque applied to the segmented gear 22 can thus be controlled by varying the hydraulic pressure source.
  • the hydraulic pressure source will preferably be set so that the biasing torque applied to the segmented gear 22 exceeds the maximum reaction torque that is expected from the driven mechanism.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un actionneur rotatif comprenant un engrenage à vis sans fin (22) à coupler à un élément actionnable et une vis sans fin (16) rentrant en contact avec ledit engrenage à vis sans fin (22), de manière à faire tourner ce dernier. Un moteur permet d'actionner la vis sans fin (16). Il faut remarquer que ledit actionneur comprend un dispositif de polarisation hydraulique permettant de transmettre un couple de polarisation à l'engrenage à vis sans fin (22), afin de le polariser dans un sens de rotation.
PCT/EP2003/050001 2002-02-13 2003-01-27 Actionneur rotatif, notamment pour distribution a programme variable et/ou mecanisme d'actionnement de soupape a disque variable WO2003069134A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
LU90896 2002-02-13
LU90896A LU90896B1 (en) 2002-02-13 2002-02-13 Rotary actuator in particular for a variable valve timing and/or variable lift valve actuating mechanism

Publications (1)

Publication Number Publication Date
WO2003069134A1 true WO2003069134A1 (fr) 2003-08-21

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PCT/EP2003/050001 WO2003069134A1 (fr) 2002-02-13 2003-01-27 Actionneur rotatif, notamment pour distribution a programme variable et/ou mecanisme d'actionnement de soupape a disque variable

Country Status (2)

Country Link
LU (1) LU90896B1 (fr)
WO (1) WO2003069134A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1741882A1 (fr) * 2005-07-08 2007-01-10 Honda Motor Co., Ltd Dispositif de commande variable de levage de soupape pour un moteur à combustion interne
WO2007058092A1 (fr) * 2005-11-14 2007-05-24 Toyota Jidosha Kabushiki Kaisha Mecanisme de soupape variable pour moteur a combustion interne
EP1905968A1 (fr) 2006-09-19 2008-04-02 Nissan Motor Co., Ltd. Mécanisme d'actionnement de soupape variable pour moteur à combustion interne
WO2012122845A1 (fr) * 2011-03-16 2012-09-20 奇瑞汽车股份有限公司 Dispositif de commande à arbre excentrique pour mécanisme de levée de soupape entièrement variable

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6075708A (ja) * 1983-09-30 1985-04-30 Nissan Motor Co Ltd 内燃機関の吸排気弁駆動装置
US6019076A (en) * 1998-08-05 2000-02-01 General Motors Corporation Variable valve timing mechanism
EP1092843A1 (fr) * 1999-10-08 2001-04-18 Toyota Jidosha Kabushiki Kaisha Dispositif de commande de soupape variable pour moteur à combustion interne
US6311659B1 (en) * 1999-06-01 2001-11-06 Delphi Technologies, Inc. Desmodromic cam driven variable valve timing mechanism

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6075708A (ja) * 1983-09-30 1985-04-30 Nissan Motor Co Ltd 内燃機関の吸排気弁駆動装置
US6019076A (en) * 1998-08-05 2000-02-01 General Motors Corporation Variable valve timing mechanism
US6311659B1 (en) * 1999-06-01 2001-11-06 Delphi Technologies, Inc. Desmodromic cam driven variable valve timing mechanism
EP1092843A1 (fr) * 1999-10-08 2001-04-18 Toyota Jidosha Kabushiki Kaisha Dispositif de commande de soupape variable pour moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 215 (M - 409) 3 September 1985 (1985-09-03) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1741882A1 (fr) * 2005-07-08 2007-01-10 Honda Motor Co., Ltd Dispositif de commande variable de levage de soupape pour un moteur à combustion interne
US7281505B2 (en) 2005-07-08 2007-10-16 Honda Motor Co., Ltd. Variable lift valve operating system for internal combustion engine
WO2007058092A1 (fr) * 2005-11-14 2007-05-24 Toyota Jidosha Kabushiki Kaisha Mecanisme de soupape variable pour moteur a combustion interne
US7721691B2 (en) 2005-11-14 2010-05-25 Toyota Jidosha Kabushiki Kaisha Variable valve mechanism for internal combustion engine
EP1905968A1 (fr) 2006-09-19 2008-04-02 Nissan Motor Co., Ltd. Mécanisme d'actionnement de soupape variable pour moteur à combustion interne
US7707980B2 (en) 2006-09-19 2010-05-04 Nissan Motor Co., Ltd. Variable valve actuation mechanism for an internal combustion engine
WO2012122845A1 (fr) * 2011-03-16 2012-09-20 奇瑞汽车股份有限公司 Dispositif de commande à arbre excentrique pour mécanisme de levée de soupape entièrement variable

Also Published As

Publication number Publication date
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