EP1828644A1 - Procede et dispositif permettant de determiner une grandeur de glissement decrivant la securite de transmission de couple d'une transmission a variation continue a poulies coniques - Google Patents

Procede et dispositif permettant de determiner une grandeur de glissement decrivant la securite de transmission de couple d'une transmission a variation continue a poulies coniques

Info

Publication number
EP1828644A1
EP1828644A1 EP05810649A EP05810649A EP1828644A1 EP 1828644 A1 EP1828644 A1 EP 1828644A1 EP 05810649 A EP05810649 A EP 05810649A EP 05810649 A EP05810649 A EP 05810649A EP 1828644 A1 EP1828644 A1 EP 1828644A1
Authority
EP
European Patent Office
Prior art keywords
slip
pressure
conical
modulation
belt
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Withdrawn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
EP05810649A
Other languages
German (de)
English (en)
Inventor
Michael Reuschel
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 EP1828644A1 publication Critical patent/EP1828644A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H59/36—Inputs being a function of speed
    • F16H59/46—Inputs being a function of speed dependent on a comparison between speeds
    • F16H2059/465—Detecting slip, e.g. clutch slip ratio
    • 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
    • F16H2061/0075—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 characterised by a particular control method
    • F16H2061/0087—Adaptive control, e.g. the control parameters adapted by learning

Definitions

  • the invention relates to a method and a device for determining a slip size describing the torque transmission reliability between two cone pulley pairs of a conical pulley belt transmission which are frictionally engaged with a belt.
  • Such drive trains include, for example, a belt pulley with continuously variable transmission.
  • a suitable contact pressure between belt and conical disks is important. Suitable means that the pressure on the one hand ensures that the belt does not slip, and on the other hand is not unnecessarily high, in order not to generate undue component loads and to worsen the efficiency due to the high hydraulic pressure to be provided.
  • an exact knowledge of the torque transmission security or the slip state between the conical disks of the belt transmission and the belt means is required.
  • a direct measurement of this slip is expensive, since in addition to the rotational speeds of the cone pulley pairs and the speed of the belt and the exact effective radii must be known on which the frictional engagement between the belt and the conical surfaces of the cone pulley pairs.
  • the invention has for its object to provide a method and a device of the type described input, with a for the torque transmission reliability of the belt transmission as meaningful slip size can be determined.
  • the part of the object relating to the method is achieved by a method for determining a slip size describing the torque transfer safety between two conical disk pairs of a conical disk belt transmission in frictional engagement, in which method a contact pressure between at least one conical disk pair and the belt is modulated and the slip size is modulated Reaction of the speed difference of the cone pulley pairs is determined on the modulation of the contact pressure, wherein the pressure modulation is performed with a frequency lying above the inventorsverstellfrequenz of the transmission and a predetermined amplitude.
  • the pressure modulation therefore takes place at a frequency higher than the transmission ratio of the transmission, i. a frequency at which the transmission does not respond to a contact pressure change with an opposite change in the distance between the conical disks of each cone pulley pair. This ensures that with a modulation of the contact pressure associated changes in the difference in the rotational speeds of the conical disk pairs go back only to change in the slip due to a change in the contact pressure.
  • the modulation of the contact pressure is carried out with a predetermined amplitude, so that influences of changes in the modulation amplitude can be switched to the measured slip size.
  • a contact pressure between at least one pair of conical disks and the belt is modulated, and the slip magnitude is based on the reaction of the speed differential of the belt pulley pairs to the belt pulley pair Determines modulation of the contact pressure, wherein the pressure modulation takes place with a frequency lying above the inventorsverstellfrequenz the transmission, the frequency of the pressure modulation is detected and the slip size is determined in dependence on the frequency. In this way, the influence of the frequency on the determined slip size can be taken into account in the evaluation.
  • a normalized slip quantity is determined from the determined slip quantity (s) by means of at least one characteristic curve containing a dependence of the slip quantity on a parameter of the pressure modulation (for example frequency or amplitude).
  • This normalized slip size provides a reproducible and objective measure of the instantaneous torque transfer capability of the belt drive and can be used to control the contact forces between pulleys and belting means. This is advantageous in that this normalized slip size then depends essentially only on the level of contact pressure, which is of central importance for the operation of the transmission.
  • the effective contact pressure on the driven cone pulley pair is modulated. It is also advantageous if, in the case of a plurality of pressure chambers acting on a cone pulley pair, the effective contact pressure is modulated in the chamber having the greatest effective cross-section.
  • the slip size can be determined, for example, using the lock-in principle.
  • the determination of the slip size is carried out using at least one bandpass filtering.
  • a device for determining a slip size describing the torque transmission reliability between two conical disk pairs of a conical disk worm gear in frictional engagement contains a device for generating a modulation of the contact pressure exerted by the at least one conical disk pair on the belt a device for determining the rotational speeds of the cone pulley pairs, means for detecting at least one parameter of the contact pressure modulation, an analysis and determination device for determining the difference in the rotational speeds of the cone pulley pairs and for determining the slip size, which analysis and determination device according to a method according to one of Claims 1 to 6 works.
  • FIG. 1 shows a block diagram of a part of a drive train of a motor vehicle with a belt-driven conical-pulley transmission and associated control
  • FIG. 2 shows curves which show a pressure modulation and the reaction of the speed difference to the pressure modulation.
  • FIG. 3 shows a characteristic curve for explaining the determination of a normalized slip quantity and Figure 4, the determination of a slip size according to the lock-in principle.
  • an input shaft 6 of a conical-pulley belt drive is driven by an internal combustion engine 4 with the interposition of a not shown, preferably automatic, clutch and a change-speed gearbox.
  • the input shaft 6 is rigidly connected to a conical disk 8 of a drive-side pulley set SS1.
  • Another conical disk 10 is rotatably and axially displaceably arranged on the input shaft 6.
  • pressure chambers 12 and 14 are arranged, by the pressurization of the force is variable, with which the conical disk 10 in the direction of the conical disk 8 can be pressed.
  • a driven-side conical disk pair SS2 has a conical disk 18 rigidly connected to an output shaft 16 and an axially movable conical disk 20 which can be urged toward the conical disk 18 by pressurizing associated pressure chambers 22, 24. Between the two pulley sets SS1 and SS2 runs around a belt 26, for example, a link chain.
  • the contact force with which the belt 26 frictionally engages the conical surfaces of the conical disk pairs is controlled by means of hydraulic valves 28, 30 and 32, which determine the pressures in the pressure chambers.
  • an electronic control unit 34 located at the input signals from sensors that contain essential information for the control of the valves, which are converted according to stored in the control unit 34 algorithms in control signals for the valves. Further outputs of the control unit 34 can control, for example, an automatic clutch.
  • the hydraulic valve 32 can be controlled independently of a mechanical torque sensor without connection to the control unit 34 and determines a basic pressure.
  • the hydraulic valves 28 and 30 for ratio adjustment are not both mandatory.
  • the control unit 34 communicates via a bus line 36 with further control devices or electronic devices of the vehicle. Construction and function of the arrangement described so far are known per se and are therefore not explained in detail.
  • a suitable contact pressure between the belt 26 and the conical disk pairs SS1 and SS2 is important. This contact pressure must, as explained, be such that the belt drive does not slip, i. inadmissibly high, and on the other hand is not pressed unnecessarily strong.
  • a slip size must be determined, which corresponds to the slip or torque transmission capability or safety of the transmission and due to which the contact pressures can be controlled by the controller 34 such that the transmission, depending on the operating conditions, with a predetermined , optimal slip is running.
  • the input shaft 6 is provided with a rotation speed sensor 38, and the output shaft 16 is provided with a rotation speed sensor 40.
  • the speed sensors are connected to an analysis and determination device 42 which communicates with the controller 34 via the bus 36.
  • programs are stored, with which, for example, the hydraulic valve 30 can be actuated such that the pressure in the pressure chamber 24 of the driven-side pulley set SS2 is modulated in a predetermined manner.
  • the instantaneous pressure is detected by means of a pressure sensor 44 which is connected to the control unit 34, so that the instantaneous pressure in the control unit 34 and (via the bus line 36) in the analysis and determination device 42 is known.
  • FIG. 3 shows a curve which indicates how the speed ratio changes as a function of the amplitude of the pressure modulation with constant excitation frequency and transmission reliability.
  • a pressure amplitude of 1 bar a certain change in the speed difference is achieved, which is taken as a norm in FIG.
  • the measured change in the rotational speed difference or the determined slip magnitude increases and, at a pressure amplitude of, for example, approximately 2.5, is approximately twice the value measured at the pressure amplitude of 1.
  • a slip quantity measured at a specific pressure amplitude can thus be normalized to the slip variable measured at a pressure amplitude of, for example, 1 bar, so that a normalized slip quantity can be determined on the basis of the characteristic which is independent of the respective known amplitude of the modulated slip Contact pressure is.
  • a frequency-dependent curve for a constant pressure amplitude can be measured, so that a frequency normalization of a measured slip size is possible.
  • Characteristics in the manner of Figure 3 are determined for a respective transmission and are stored as characteristics or maps (pressure and frequency dependence of the normalization factor), for example in the analysis and determination device and used for the determination of the actual slip state of the respective operating point.
  • characteristics or maps pressure and frequency dependence of the normalization factor
  • the curve A indicates the modulation ⁇ p of the contact pressure over time.
  • the low-pass filtered translation can be obtained, for example, by a corresponding filtering of the speed ratio n1 / n2.
  • the curve C indicates the sign of the fluctuation of the modulated pressure around its mean and has the value -1 when the pressure is above the mean and +1 when the pressure is below the mean.
  • the curve D shows the product of the curves B and C and is a measure of the absolute value of the respective change in the speed difference.
  • the curve E indicates the mean value of the curve D and is a measure of the slip S.
  • the slip size determined in each case according to the lock-in principle can be converted into a normalized slip size by using the characteristic, for example according to FIG. 3, and reliably indicates the respective torque transmission security or the slip of the belt drive as normalized slip quantity, so that the pressures for an optimal setting of the respective slip or the torque transmission safety of the transmission can be used.
  • the invention can be modified in many ways. For example, two corresponding pressure chambers of the pulley sets according to FIG. 1 can be operated simultaneously with pressure modulation. However, as shown, it is advantageous to modulate the pressure only in the larger pressure chamber of the driven-side pulley set.
  • the pressure modulation to determine the respective torque transmission safety can be done while driving a motor vehicle in each case when a slight change in the slip is not critical.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)

Abstract

L'invention vise à déterminer une grandeur de glissement décrivant la sécurité de transmission de couple entre deux paires de poulies coniques d'une transmission à variation continue à poulies coniques, ces paires de poulies coniques étant en contact de frottement par un moyen d'enroulement. A cet effet, on module la pression d'appui entre au moins une paire de poulies coniques et le moyen d'enroulement et on détermine la grandeur de glissement à partir de la réaction de la différence de vitesses de rotation des paires de poulies coniques sur la modulation de la pression d'appui. La modulation de pression est effectuée à l'aide d'une fréquence supérieure à la fréquence de réglage de transmission de la transmission et d'une amplitude prédéterminée.
EP05810649A 2004-12-18 2005-11-24 Procede et dispositif permettant de determiner une grandeur de glissement decrivant la securite de transmission de couple d'une transmission a variation continue a poulies coniques Withdrawn EP1828644A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004060994 2004-12-18
PCT/DE2005/002110 WO2006063547A1 (fr) 2004-12-18 2005-11-24 Procede et dispositif permettant de determiner une grandeur de glissement decrivant la securite de transmission de couple d'une transmission a variation continue a poulies coniques

Publications (1)

Publication Number Publication Date
EP1828644A1 true EP1828644A1 (fr) 2007-09-05

Family

ID=35744806

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05810649A Withdrawn EP1828644A1 (fr) 2004-12-18 2005-11-24 Procede et dispositif permettant de determiner une grandeur de glissement decrivant la securite de transmission de couple d'une transmission a variation continue a poulies coniques

Country Status (7)

Country Link
US (1) US7377878B2 (fr)
EP (1) EP1828644A1 (fr)
JP (1) JP5114798B2 (fr)
KR (1) KR20070087566A (fr)
CN (1) CN101080589B (fr)
DE (1) DE112005002937A5 (fr)
WO (1) WO2006063547A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101502203B1 (ko) * 2008-09-26 2015-03-12 로베르트 보쉬 게엠베하 무단 변속기의 마찰 접촉의 수직 항력을 제어하기 위한 방법
DE102010039172B4 (de) * 2010-08-11 2023-12-07 Zf Friedrichshafen Ag Verfahren zur Ermittlung eines Anlegebetätigungsdruckwertes eines reibschlüssigen Schaltelements
CN102353536B (zh) * 2011-07-11 2013-12-18 程乃士 无级变速器用挠性传动元件快速测试跑合系统
CN106144787A (zh) * 2016-08-04 2016-11-23 江苏金喷灌排设备有限公司 具有防止皮带打滑装置的喷灌机

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
DE4120540C1 (fr) * 1991-06-21 1992-11-05 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
DE19544061B4 (de) * 1994-12-06 2005-09-01 Volkswagen Ag Verfahren zur Betätigungsregelung von Schaltelementen oder Stellgliedern von Automatikgetrieben
DE19937053A1 (de) * 1998-08-17 2000-02-24 Daimler Chrysler Ag Verfahren und Vorrichtung für ein Ventil
DE10050218A1 (de) * 2000-10-11 2002-04-25 Volkswagen Ag Verfahren zur Anpresskraftregelung für stufenlos verstellbare Getriebe
DE10111607A1 (de) * 2001-03-10 2002-10-31 Conti Temic Microelectronic Verfahren zur Steuerung eines stufenlosen Getriebes
WO2002101264A2 (fr) 2001-06-13 2002-12-19 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Procede et systeme pour reguler la capacite de transmission de couple d'un ensemble transmettant un couple par friction
JP3597808B2 (ja) 2001-09-28 2004-12-08 トヨタ自動車株式会社 無段変速機の滑り検出装置
DE10310831A1 (de) * 2002-04-10 2003-11-06 Luk Lamellen & Kupplungsbau Antriebsstrang und Verfahren zu dessen Betrieb
US20060058128A1 (en) * 2004-08-24 2006-03-16 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Belt-driven conical-pulley transmission, method for producing it, and motor vehicle having such a transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006063547A1 *

Also Published As

Publication number Publication date
JP2008524516A (ja) 2008-07-10
CN101080589A (zh) 2007-11-28
JP5114798B2 (ja) 2013-01-09
KR20070087566A (ko) 2007-08-28
US20080004157A1 (en) 2008-01-03
WO2006063547A1 (fr) 2006-06-22
CN101080589B (zh) 2010-05-12
DE112005002937A5 (de) 2007-08-30
US7377878B2 (en) 2008-05-27

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