EP2002147A1 - Dispositif de detection du couple de rotation sur une transmission a courroie sur poulies coniques - Google Patents

Dispositif de detection du couple de rotation sur une transmission a courroie sur poulies coniques

Info

Publication number
EP2002147A1
EP2002147A1 EP07721976A EP07721976A EP2002147A1 EP 2002147 A1 EP2002147 A1 EP 2002147A1 EP 07721976 A EP07721976 A EP 07721976A EP 07721976 A EP07721976 A EP 07721976A EP 2002147 A1 EP2002147 A1 EP 2002147A1
Authority
EP
European Patent Office
Prior art keywords
shaft
ramp
balls
ramp surfaces
torque
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Withdrawn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
EP07721976A
Other languages
German (de)
English (en)
Inventor
Wolfgang Gantner
Andreas GÖTZ
Eugen Kremer
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.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP2002147A1 publication Critical patent/EP2002147A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
    • F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed- or reversing-gearings for conveying rotary motion
    • F16H59/14—Inputs being a function of torque or torque demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/065—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions hydraulic actuating means

Definitions

  • the invention relates to a torque sensing device for a cone pulley wrap transmission.
  • Cone pulley as used for example in motor vehicles, generally contain two pairs of conical disks, which are wrapped by a belt, for example, a link chain, wrapped. By opposing change in the distance between the conical disks of each conical disk pair, the transmission ratio can be changed continuously.
  • a pair of conical disks preferably the drive side, includes an integrated torque sensor with which the torque acting on a drive motor is detected and a contact pressure between the conical disks of the associated disk pair is changed in accordance with the torque.
  • Such conical-pulley transmission with integrated torque sensor are described, for example, in DE 42 34 294 A1, DE 19 54 644 A1, DE 40 26 683, DE 195 45 492 A1 and DE 199 51 950 A1.
  • FIG. 4 shows a cross section through a drive-side part of a conical-disk drive transmission.
  • an input shaft 10 which is formed integrally with a fixed disk, not shown, is axially displaceable, but rotatably connected to the input shaft, a spacer plate 14 is arranged.
  • a cylindrical ring 16 is rigidly fixed in the radially outer region with two radially spaced walls in which a piston 18 operates, so that according to the Fig. Right side of the piston 18, a first pressure chamber 20 is formed by formed in the travel plate 14 radial holes 22, an annular space 24 between the washer 14 and the shaft 10 and formed in the shaft 10 radial bore 26 and axial bore 28 can be acted upon by hydraulic pressure, which is variable for a translation adjustment.
  • the overall annular piston 18 is rigidly connected to a generally cup-shaped support ring 30, which in turn is rigidly connected to the input shaft 10. At the front end of the support ring 30 ramp surfaces 32 are formed.
  • a generally annular sensing piston 36 is arranged to be axially displaceable while sealing against the peripheral surface of the input shaft 10 and an inner circumferential surface of the support ring 30.
  • the sensing piston 36 is formed with a projection directed toward the travel disc 14, on the rear side of which ramp surfaces 38 are formed, which form counter surfaces to the ramp surfaces 32.
  • ramp surfaces 32 and 38 are rolling elements, in the example shown balls 40, respectively.
  • a second pressure chamber 42 is formed, which is acted upon by the input shaft 10 leading supply line 44 with hydraulic pressure, wherein the hydraulic fluid via a likewise formed in the input shaft 10 derivative 46 can be derived.
  • the effective cross section of the leading into the second pressure chamber inlet opening 48 is determined by the axial position of the spacer plate 14.
  • the effective cross section of the outgoing from the second pressure chamber 42 discharge opening 50 is determined by the position of the sensing piston 36.
  • the sensing piston 36 protrudes with circumferentially spaced axial arms 52 through recesses of the support ring 30 therethrough.
  • the radial outer surfaces of the arms 52 are provided with axially and radially directed teeth, which are in engagement with an internal toothing of an input gear 54, which is mounted by means of a bearing 8 axially substantially immovably on the input shaft 10.
  • a ring member 56 is rigidly connected to the cylinder ring 16, the inside of which forms a guide surface 58 against which the balls 40 and which limits the radial outward movement of the balls 40.
  • the known, in particular by the sensing piston 36, the ramp surfaces 32 and 38 and the guide surface 58 and the balls 40 formed torque sensing device has the following characteristics:
  • a first solution of the invention task is achieved with a torque sensing device for a conical-pulley, which torque sensing device includes a rigidly connected to a shaft of a conical disk pair ramp surface, another ramp surface which is rigidly connected to a shaft surrounding, relative to the shaft axially displaceable and rotatable Fühikolben which ramp surfaces are designed such that changes in a change in the effective between the sensing piston and the shaft torque, the axial position of the sensing piston by rolling arranged between the ramp surfaces balls on the ramp surfaces, and a rigidly connected to a travel disc guide surface at the radial Inside the balls abut, wherein the travel disc with the shaft rotatably and axially displaceably connected and with a dependent of the axial position of the sensing piston hydraulic pressure in the direction of a rigid mi t is the shaft connected fixed disc is urged and the guide surface is shaped such that the radial distance between the balls and the axis of the shaft on the axial distance between the distance disc and the fixed disc depends
  • Another object of the invention is to provide a torque sensing device for a conical-pulley transmission which includes a torque sensing device rigidly connected to a shaft of a cone pulley pair ramp surface, a further ramp surface which is rigidly connected to a shaft engaging, relative to the shaft axially displaceable and rotatable sensing piston, which Ramp surfaces are formed such that the axial position of the sensing piston changes by rolling arranged between the ramp surfaces balls on the ramp surfaces with a change in the effective between the sensing piston and the shaft torque, and a rigidly connected to a travel disc guide surface, at its radial inner side the balls with their radially outer Abut area, wherein the travel disc with the shaft rotatably and axially slidably connected and is urged with a dependent of the axial position of the sensing piston hydraulic contact pressure towards a rigidly connected to the shaft fixed disk and the guide surface is shaped such that the radial distance between the balls and the axis of the shaft depends on the axial distance between the travel disc and
  • the pitch of the ramp surfaces decreases with increasing distance from their lowest point such that the quotient of contact pressure and torque is substantially independent of the positions of the ramp surfaces and the guide surface relative to one another.
  • the negative effect of the radial displacement of the contact point with respect to the centers of the balls can be compensated.
  • FIG. 2 shows three sectional views, cut in the plane H-II of FIG. 4, wherein the ball is relative to the guide surface with respect to the circumferential direction in different positions
  • Fig. 3 is a view similar to FIG. 1 with respect to FIG. 1 different shape of the ramp surface
  • FIG. 4 shows a cross section through a drive-side portion of a conical-pulley wrap-type transmission of a type known per se.
  • Fig. 1 shows in the figure part a) a ball 40 between the ramp surfaces 32 and 38, which are formed in the circumferential direction repetitively on the support ring 30 and the sensing piston 36.
  • Fig. 1a represents the FWm ⁇ ment upset state in which the sensing piston 36 is maximally approximated to the support ring 30.
  • ramp surface 38 in the circumferential direction (y) due to a torque introduced by the input gear 54 relative to the ramp surface 32 of the support ring 30 is shifted, so that the ball 40 on the ramp surfaces by a certain extent is rolled and increases the distance between the support ring 30 and the sensing piston 36.
  • a line connecting the points of contact P 1 and P 2 and the center M of the ball makes an angle with the X direction (direction of the axis of the input shaft 10).
  • the mold surface 58 seen in a section according to H-II of Fig. 4 has the 2, wherein only one half is shown starting from the location radially above the lowest point of the ramp surface 32 of the support ring 30 in the circumferential direction.
  • the guide surface has in its middle region a plateau 60 against which the ball 40 rests in the position according to FIG. 2 a) at the point Pi.
  • Fig. 2b shows the contact between the ball 40 and the guide surface 58 in the state of Fig. 1 b), wherein the contact points P 2 , P 3 emigrate laterally and a plane containing the points Bi, M, B 2 , P 4th (Middle between P 2 and P 3 ), remains radially directed.
  • the contact point P5 In the position according to FIG. 2c), which corresponds to the pumping position, ie the greatest possible displacement between the ramp surfaces 32 and 38 in the circumferential direction, the contact point P5 has moved further away from the effective contact point P4 of FIG. 2c.
  • the guide surface 58 may be matched to the ramp surfaces 32 and 38 such that a plane containing the points of contact of the ball with the ramp surfaces and the guide surface as well as the ball center lies in the radial direction. This ensures that the force acting on the balls 40 with increasing speed centrifugal force is completely taken over by reaction forces and there is no unfavorable speed dependence of the contact pressure.
  • the guide surface 58 may also be configured such that the points of contact of the ball with the ramp surfaces and with the guide surface define a plane having a predetermined angle with the radial direction. As a result, a prescribable speed dependence of the contact pressure is achieved, which can be taken into account in the hydraulic control of the conical disk wrap transmission.
  • Fig. 3 shows a comparison with the Fig. 1 modified form of the ramp surfaces, wherein only the ramp surface 32 of the support ring 30 is shown.
  • the pitch ⁇ of the ramp surface 32 changes in the circumferential direction y, the pitch becoming smaller as the distance from the lowest point increases.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

L'invention concerne un dispositif de détection du couple de rotation pour une transmission à courroie enroulée sur poulies coniques, qui contient une surface inclinée reliée solidairement à un arbre d'une paire de poulies coniques, une autre surface inclinée reliée solidairement à un piston de détection qui chevauche l'arbre et qui peut coulisser axialement et tourner par rapport à l'arbre, les surfaces inclinées étant configurées de telle sorte que lors d'une modification du couple de rotation qui agit entre le piston de détection et l'arbre, la position axiale du piston de détection se modifie par roulement de billes disposées entre les surfaces inclinées et qui roulent sur les surfaces inclinées, et une surface de guidage reliée solidairement à une poulie sur le côté radialement intérieur de laquelle reposent les billes, la poulie mobile étant reliée à rotation solidaire à l'arbre et à coulissement axial par rapport à ce dernier et étant repoussée en direction d'une poulie fixe reliée solidairement à l'arbre, par une pression hydraulique qui dépend de la position axiale du piston de détection, la surface façonnée ayant une forme telle que la distance radiale entre les billes et l'axe de l'arbre dépend de la distance axiale entre la poulie mobile et la poulie fixe, la surface de guidage étant configurée de telle sorte que les points de contact de chaque bille avec les surfaces inclinées, le point de contact de ces billes avec la surface de guidage et le centre de ces billes soient situés dans un plan orienté radialement.
EP07721976A 2006-03-24 2007-03-05 Dispositif de detection du couple de rotation sur une transmission a courroie sur poulies coniques Withdrawn EP2002147A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006013795 2006-03-24
PCT/DE2007/000401 WO2007110026A1 (fr) 2006-03-24 2007-03-05 Dispositif de détEction du couple de rotation sur une transmission a courroie sur poulies coniques

Publications (1)

Publication Number Publication Date
EP2002147A1 true EP2002147A1 (fr) 2008-12-17

Family

ID=38068690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07721976A Withdrawn EP2002147A1 (fr) 2006-03-24 2007-03-05 Dispositif de detection du couple de rotation sur une transmission a courroie sur poulies coniques

Country Status (6)

Country Link
EP (1) EP2002147A1 (fr)
JP (1) JP2009531610A (fr)
KR (1) KR20080104021A (fr)
CN (1) CN101410650A (fr)
DE (1) DE112007000502A5 (fr)
WO (1) WO2007110026A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008059807A1 (de) 2007-12-19 2009-06-25 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrauliksystem
DE102009016293A1 (de) 2008-04-29 2009-11-05 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentfühlvorrichtung
DE102010011822A1 (de) 2009-04-14 2010-10-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentfühlvorrichtung
DE102010051910A1 (de) 2009-11-30 2011-06-09 Schaeffler Technologies Gmbh & Co. Kg Dreheinführungsvorrichtung
DE112011101093A5 (de) 2010-03-29 2013-04-11 Schaeffler Technologies AG & Co. KG Hydrauliksystem
CN103867678B (zh) * 2014-03-20 2016-05-18 程乃士 一种锥盘式无级变速器
EP3128207B1 (fr) 2014-03-20 2019-12-04 Changzhou Dongfeng Continuously Variable Transmission Co., Ltd. Transmission à variation continue de type à disques biseautés
DE102017110961A1 (de) 2017-05-19 2018-11-22 Schaeffler Technologies AG & Co. KG Dreheinführungsvorrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4234294B4 (de) * 1991-10-19 2008-04-03 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Kegelscheibenumschlingungsgetriebe
JP3537329B2 (ja) * 1998-11-16 2004-06-14 日本精工株式会社 軸力発生装置およびトラクションドライブ変速装置
JP4848559B2 (ja) * 2000-12-20 2011-12-28 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 組み込まれたトルク感応器を備えた無段変速可能な円錐形プーリ巻掛け伝動装置
JP2002250418A (ja) * 2001-02-12 2002-09-06 Luk Lamellen & Kupplungsbau Beteiligungs Kg 統合されたトルクフィーラを備えた、無段階に調節可能な円錐円板巻掛け伝動装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007110026A1 *

Also Published As

Publication number Publication date
JP2009531610A (ja) 2009-09-03
DE112007000502A5 (de) 2008-11-27
CN101410650A (zh) 2009-04-15
WO2007110026A1 (fr) 2007-10-04
KR20080104021A (ko) 2008-11-28

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