WO2022017561A1 - Procédé de commande de chaîne cinématique - Google Patents

Procédé de commande de chaîne cinématique Download PDF

Info

Publication number
WO2022017561A1
WO2022017561A1 PCT/DE2021/100585 DE2021100585W WO2022017561A1 WO 2022017561 A1 WO2022017561 A1 WO 2022017561A1 DE 2021100585 W DE2021100585 W DE 2021100585W WO 2022017561 A1 WO2022017561 A1 WO 2022017561A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
slave cylinder
relief valve
friction clutches
supply device
Prior art date
Application number
PCT/DE2021/100585
Other languages
German (de)
English (en)
Inventor
Frederic Pfister
Marc Rambert
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN202180059096.7A priority Critical patent/CN116194692A/zh
Publication of WO2022017561A1 publication Critical patent/WO2022017561A1/fr

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
    • F16H61/04—Smoothing ratio shift
    • F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
    • F16H61/061—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • 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
    • F16H61/68—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 stepped gearings
    • F16H61/684—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 stepped gearings without interruption of drive
    • F16H61/686—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 stepped gearings without interruption of drive with orbital gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/90—Vehicles comprising electric prime movers
    • B60Y2200/91—Electric vehicles
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
    • F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0269—Single valve for switching between fluid supply to actuation cylinder or draining to the sump
    • 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
    • F16H61/04—Smoothing ratio shift
    • F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
    • F16H61/061—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means
    • F16H2061/064—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means for calibration of pressure levels for friction members, e.g. by monitoring the speed change of transmission shafts
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds

Definitions

  • Wheel drives in which a drive unit, for example an electric motor drives a drive wheel of a motor vehicle with the interposition of a switchable gear such as a planetary gear are known, for example, from the publications DD 278 307 A and EP 2 597 336 B1.
  • a drive unit for example an electric motor drives a drive wheel of a motor vehicle with the interposition of a switchable gear such as a planetary gear
  • a switchable gear such as a planetary gear
  • components of the planetary gear such as ring gear and/or carrier are fixed to the housing by means of a brake band, so that different translations can be switched from the different translations with and without a rotating ring gear or carrier.
  • the brake band can be actuated in different ways by means of electric or hydraulic actuators, for example by means of hydrostatically actuated friction clutches.
  • Such planetary gears are controlled by a control unit which controls the corresponding actuators.
  • the object of the invention is the further development of a method for controlling a wheel drive of a motor vehicle.
  • the object of the invention is to precisely control friction clutches and to adapt them neutrally for the vehicle occupants with regard to vibrations and noise.
  • the proposed method is used to control a wheel drive arranged, for example, on two or all drive wheels of a motor vehicle wise wheel drives.
  • a central and/or several decentralized control units are provided, which control a drive unit and a gear each of a wheel drive. It goes without saying that a wheel drive controlled by the method is also covered by the inventive concept and can be claimed as an additional subject matter if necessary.
  • the respective wheel drive contains a drive unit, preferably an electric motor.
  • the electric motor can be provided in a driving or recuperative manner.
  • An at least two-speed planetary gear is connected downstream of the electric motor or its rotor.
  • the planetary gear is designed at least in one stage, preferably in two stages.
  • As components of the planetary gear at least one sun gear, a ring gear and at least one web with rotatable and distributed over the circumference arranged planetary gears are provided.
  • the planet gears are each meshed with a sun gear and the associated ring gear.
  • one component of the planetary gear for example a sun wheel of a first stage, serves as the drive and is firmly connected to the rotor.
  • two webs of different stages can be connected to the output, so that without reversing the direction of rotation, both a ring gear and a web can be connected to the housing, preferably in an intersecting manner and in opposite directions, in order to set two different transmission ratios between input and output.
  • two of the components can be fixed to the housing of the planetary gear for switching the planetary gear, that is to say they can be connected to the housing.
  • the ring gear can be connected to the housing by means of a first friction clutch and the web can be connected to the housing by means of a second friction clutch.
  • the friction Couplings are designed, for example, as forcibly closed friction clutches, that is, the friction clutches are closed under hydrostatic pressure and are thus connected to the housing.
  • the ring gear or web are arranged such that they can rotate relative to the housing.
  • the friction clutches are alternately closed and opened.
  • the friction clutches are actuated in an overlapping manner, ie one friction clutch is opened and the other friction clutch is closed.
  • the hydrostatic actuation of the friction clutches takes place by means of a hydraulic unit controlled by a control unit.
  • the hydraulic unit contains a pressure supply device, for example an electrically operated pump. Both Hy draulic units of the two friction clutches can be fed from a common pressure supply device.
  • the hydraulic unit contains a slave cylinder which actuates the friction clutch and is connected to the pressure supply device by means of a pressure line. Under pressure, the slave cylinder is shifted axially against the action of a spring element, for example a return spring. If the pressure is released from the slave cylinder, the slave cylinder piston, which is prestressed by the spring element, moves to its rest position and the frictional engagement of the friction clutch is released.
  • a pressure valve controlled by the control unit for example electromagnetically actuated, is installed in the pressure line between the pressure supply device and the slave cylinder. relief valve switched.
  • the pressure relief valve connects the slave cylinder in a first switching position with the pressure supply device. In a second switching position, the slave cylinder is connected to an unpressurized sump.
  • the pressure relief valve is preferably actively switched from the second switch position to the first switch position, contrary to a return spring.
  • the touch and release point of the friction clutches are preferably determined in the course of a change due to the actuation of the pressure relief valve while the motor vehicle is stationary using a pressure change detected by a pressure sensor arranged in the pressure line behind the pressure relief valve.
  • the touch and release point is adapted when the motor vehicle is stationary, ie when the wheels are stationary, so that the influence of this is excluded.
  • the method can be carried out essentially without vibrations and noise for the occupants.
  • the contact point is advantageously determined at a first pressure value with the pressure of a slave cylinder piston of the slave cylinder changing significantly from a lower gradient to a greater gradient when the slave cylinder is currently connected to the pressure supply device by means of the pressure relief valve. placed. This means that the contact point is determined when the friction clutch closes after the pressure relief valve has closed.
  • the detachment point is defined at a second pressure value with the pressure of a slave cylinder piston of the slave cylinder changing significantly from a higher slope to a lower slope when the pressure relief of the slave cylinder is currently switched by means of the pressure relief valve.
  • the release point is determined with the friction clutch opening after the pressure relief valve has been opened.
  • the contact and release points of the two friction clutches are each determined separately after switching on the pressure reducing valve by the pressure changes in the pressure line being recorded by the pressure sensor over time and evaluated.
  • the individual pressure values are preferably recorded and evaluated at fixed time intervals, for example interrupts of the recording and evaluating control unit.
  • the pressure values are allocated during a determination of the contact or detachment point, for example at each interrupt, in a clocked manner in a FIFO data register with a fixed number of storage locations.
  • the pressure values are gradually read in serially and shifted on, with the sum of the pressure values of the register being determined at each time cycle.
  • the totals are each compared with a predetermined total value of the contact or separation point and the pressure value that is essential for the contact or separation point is determined for a predetermined total value.
  • the pressure values located at the storage locations can each be loaded with a coefficient that is specifically predetermined for the storage location.
  • a data value located in the register at a centrally arranged memory location can have the smallest coefficient in terms of magnitude and the an Pressure values located in both chronological directions from this spaced memory locations can be subjected to increasing coefficients in terms of amount.
  • Figure 1 shows a crossover shift of a planetary gear by means of two pressurized slave cylinders over time
  • FIG. 2 shows a schematically illustrated hydraulic unit for actuating one of the two friction clutches
  • FIG. 3 Pressure curves of the pressurized slave cylinders to determine the touch and release points of the friction clutches and
  • FIG. 4 shows an evaluation scheme for determining the tactile and detachment points by means of FIR.
  • FIG. 1 shows the schematically illustrated diagram 100 of the rotational speed n of an output of a planetary gear or of the pressure p acting on two slave cylinders, each of which actuates a friction clutch, over time t.
  • Ge shows an overlap circuit of the two friction clutches for the control of a planetary gear, in that one friction clutch com- ponents of the planetary gear—here a floating wheel and a carrier—is alternately connected to the housing.
  • the overlapping shift takes place from fast to slow with the speed n(1) present at the output of the planetary gearbox at the beginning of the overlapping shift and the speed n(2) present after the overlapping shift.
  • the curve 101 shows the course of the speed n over time t during the overlap shift.
  • Curve 102 shows the progression of pressure p(K1) of the slave cylinder actuating the first friction clutch and curve 103 shows pressure p(K2) of the slave cylinder actuating the second friction clutch over time t during the overlapping shift.
  • the first friction clutch is closed by the pressure value p(K1,1) applied, which means that the component actuated by this friction clutch, for example the ring gear, is braked firmly in the housing. There is no pressure on the slave cylinder of the second friction clutch, so that it is open and the web transfers the applied torque to the output.
  • the slave cylinder of the first friction clutch is relieved of pressure and the slave cylinder of the second friction clutch is pressurized by appropriate switching on of pressure relief valves.
  • the curve 102 shows the steeply falling branch 104 until the preload on the disk pack of disks and counter disks of the first friction clutch is reduced at the release point AP and no more torque is transmitted via the first friction clutch.
  • the slave cylinder piston is displaced along the flat branch 105 by means of the spring element acting on it, up to the end position. The position of the detachment point is determined by evaluating the two gradients of the branches 104, 105.
  • the curve 103 shows a slowly increasing pressure along the branch 106 on the slave cylinder of the second friction clutch after a short reaction time after the pressure relief valve has been closed.
  • contact point TP When contact point TP is reached, the lamellae and counter lamellae of the lamellar set of the second friction clutch come into contact and are preloaded. This results in the steep rise in pressure in branch 107 until the second friction clutch is fully engaged.
  • the touch point TP is determined by evaluating the slopes of the branches 106, 107.
  • FIG. 2 shows schematically the hydraulic unit 200 for one of the two friction clutches.
  • a hydraulic unit 200 is provided for each of the friction clutches. hen.
  • the hydraulic unit 200 contains the pressure supply device 201, which is designed here as a pump 203 driven by the electric motor 202.
  • the pressure supply device 201 can be available to both hydraulic units of the friction clutch.
  • the pressure relief valve 204 is arranged in the pressure line 205 between the pressure supply device 201 and the slave cylinder 206 and switches between the slave cylinder 206 on the one hand and on the other hand optionally between the pressure supply device 201 and the unpressurized sump 207, so that the slave cylinder 206 is pressurized or relieved of pressure can be.
  • the slave cylinder piston 208 is displaced under pressure against the action of the spring element 209 and, after overcoming the idle travel As, prestresses the lamellar pack 210 of the friction clutch.
  • the pressure relief valve 204 shown here open is closed, first the slave cylinder 206 is filled and the slave cylinder piston 208 is displaced against the action of the spring element 209 to the touch point TP, the pressure in the pressure line 205 increases slowly but steadily. When the slave cylinder piston 208 or a component connected to it reaches the disk set 210 at the contact point TP, the pressure in the pressure line increases with a steeper gradient, since the disk set 210 is prestressed.
  • the friction clutch begins to transmit torque at touch point TP by means of the beginning frictional contact between the disks and counter disks of disk set 210, so that the transition between the pressure with a small gradient and the pressure with a large gradient can be assigned the pressure value at the touch point.
  • the pressure sensor 211 is provided for detecting the pressure in the pressure line 205 .
  • the detachment point of the friction clutch is determined in a similar manner after the pressure relief valve 204 opens, by evaluating the steeply falling pressure up to the detachment of the disks and counter-disks of the disk set 210 and the pressure dropping with a slight incline when the spring element 209 is relieved.
  • the friction clutch is designed according to the normally open principle. This means that the friction clutch is opened when there is no pressure in the pressure line 205 and is closed under pressure. This means that the component of the planetary gear set assigned to this friction clutch is connected to the housing under pressure.
  • Figure 3 shows the diagram 300 with the pressure p over the travel s of the slave cylinder piston 208 after a switching of the pressure relief valve 204.
  • the curve 301 shows the pressure behavior of the pressure line 205 when the pressure relief valve 204 is currently closed with the branch 302 rising with a slight incline and the branch 303 rising steeply after the touch point TP.
  • the curve 304 shows the pressure behavior of the pressure line 205 shortly after the opening of the pressure relief valve 204 with the steep branch 305 up to the separation point AP and the branch 306 with a lower gradient until the pressure line is completely depressurized.
  • the touch point TP is determined in the direction of the increasing travel s of the slave cylinder piston 208 by register 307 with five memory locations c4, c3, c2, c1, cO according to the FIFO principle (first-in-first-out) with pressure values in Time intervals of interrupts of the control unit filled and according to the principle of a filter with a finite impulse response (FIR; finite impulse response filter) is evaluated.
  • FIR finite impulse response filter
  • the detachment point AP is determined in the direction of the decreasing path s of the slave cylinder piston 208 by means of the register 308.
  • the touch point TP or separation point AP is recognized when the value resulting from the FIR filter corresponds to a calibrated value.
  • the corresponding pressure value is then assigned to touch point TP or release value AP.
  • the pressure hysteresis of the hydraulic unit 200 can be determined from the pressure difference Dr between the curves 301 and 304 or the branches 302, 306 with the contact point TP and the separation point AP.
  • FIG. 4 shows the principle of the FIR filter for determining the touch point TP of FIG. 3, for example.
  • the coefficients k4, k3, k2, k1, k0 with the values -6, -3, 0, 3, 6 are assigned to the pressure values briefly stored at the memory locations c4, c3, c2, c1, c0 of the FIFO register 307 .
  • the sum is formed from the pressure values p(cn) of the storage locations c4, c3, c2, c1, c0 according to the given formula. If this sum corresponds to a calibrated value, the pressure value p(C2) is accepted as the pressure value for the contact point TP.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

Abstract

L'invention concerne un procédé de commande d'un entraînement de roue d'un véhicule à moteur, comportant un moteur électrique, comportant une transmission planétaire à au moins deux vitesses reliée en aval dudit moteur électrique, et comportant au moins une roue d'entraînement reliée en aval de la transmission planétaire, les engrenages de la transmission planétaire étant déplacés au moyen de deux embrayages à friction à commande hydrostatique destinés à immobiliser un élément respectif de la transmission planétaire de façon à être statique par rapport à une enveloppe. Afin de pouvoir déplacer les engrenages dans la transmission planétaire de manière synchrone et sans influences NVH sur les occupants du véhicule à moteur, chaque embrayage à friction est actionné au moyen d'une unité hydraulique (200) dotée d'un dispositif d'alimentation en pression (201), d'un cylindre esclave (206) destiné à agir sur l'embrayage à friction contre l'action d'un élément ressort (209), d'une soupape de détente de pression (204) disposée dans une conduite sous pression (205) entre le dispositif d'alimentation en pression (201) et le cylindre esclave (206), et d'un capteur de pression (211) disposé dans la conduite sous pression (205) entre la soupape de détente de pression (204) et le cylindre esclave (206), et un point de serrage et de desserrage (TP, AP) des embrayages à friction sont chacun déterminés au cours d'un changement de pression qui varie en raison du fonctionnement de la soupape de détente de pression (204) et qui est détecté par le capteur de pression (211) pendant que le véhicule à moteur est à l'arrêt.
PCT/DE2021/100585 2020-07-22 2021-07-06 Procédé de commande de chaîne cinématique WO2022017561A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202180059096.7A CN116194692A (zh) 2020-07-22 2021-07-06 用于控制动力总成的方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020119333 2020-07-22
DE102020119333.5 2020-07-22

Publications (1)

Publication Number Publication Date
WO2022017561A1 true WO2022017561A1 (fr) 2022-01-27

Family

ID=76958674

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2021/100585 WO2022017561A1 (fr) 2020-07-22 2021-07-06 Procédé de commande de chaîne cinématique

Country Status (3)

Country Link
CN (1) CN116194692A (fr)
DE (1) DE102021117344A1 (fr)
WO (1) WO2022017561A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021119141B3 (de) * 2021-07-23 2022-10-27 Schaeffler Technologies AG & Co. KG Verfahren zur Ermittlung eines Tastpunkts einer Trennkupplung eines Hybridmoduls

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD278307A1 (de) 1988-12-22 1990-05-02 Gisag Stammbetrieb Des Veb Kom Radmotor fuer mobile maschinen
WO2011124197A1 (fr) * 2010-04-08 2011-10-13 Schaeffler Technologies Gmbh & Co. Kg Procédé de commande d'un embrayage automatisé
US20160091059A1 (en) * 2014-09-29 2016-03-31 Benoit Boulet Seamless transmission systems and methods for electric vehicles
EP3162647A1 (fr) * 2015-10-30 2017-05-03 Hyundai Motor Company Appareil et procédé pour l'apprentissage d'un point de contact tactile d'embrayage de moteur de véhicule électrique hybride
US20180172092A1 (en) * 2016-12-15 2018-06-21 Hyundai Motor Company Touch point learning apparatus and method for clutch
EP2597336B1 (fr) 2010-07-23 2020-02-26 NTN Corporation Dispositif d'entraînement de moteur intégré à la roue

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD278307A1 (de) 1988-12-22 1990-05-02 Gisag Stammbetrieb Des Veb Kom Radmotor fuer mobile maschinen
WO2011124197A1 (fr) * 2010-04-08 2011-10-13 Schaeffler Technologies Gmbh & Co. Kg Procédé de commande d'un embrayage automatisé
EP2597336B1 (fr) 2010-07-23 2020-02-26 NTN Corporation Dispositif d'entraînement de moteur intégré à la roue
US20160091059A1 (en) * 2014-09-29 2016-03-31 Benoit Boulet Seamless transmission systems and methods for electric vehicles
EP3162647A1 (fr) * 2015-10-30 2017-05-03 Hyundai Motor Company Appareil et procédé pour l'apprentissage d'un point de contact tactile d'embrayage de moteur de véhicule électrique hybride
US20180172092A1 (en) * 2016-12-15 2018-06-21 Hyundai Motor Company Touch point learning apparatus and method for clutch

Also Published As

Publication number Publication date
DE102021117344A1 (de) 2022-01-27
CN116194692A (zh) 2023-05-30

Similar Documents

Publication Publication Date Title
EP2242662B1 (fr) Dispositif pour réduire la chute de la force de traction
EP2504211B1 (fr) Procédé et dispositif pour le fonctionnement d'un véhicule hybride
DE102008051458A1 (de) Verteilergetriebe für einen Kraftfahrzeugantriebsstrang
WO2003006841A2 (fr) Procede pour adapter le reglage d'un embrayage dans un systeme de transmission non classique d'un vehicule
DE112012006767T5 (de) Fahrzeuggetriebesteuerung
DE102005004389A1 (de) System zur Reduzierung des Antriebsstrangsreaktionsdrehmoments
WO2001006152A1 (fr) Dispositif pour commander en fonction de la temperature un embrayage ou une boite de vitesses de vehicule automobile
EP1880116B1 (fr) Transmission d'un vehicule automobile
WO2003087616A1 (fr) Procede de detection d'une fuite dans un systeme de debrayage hydraulique d'un embrayage double d'une transmission a changement parallele
DE102011017516A1 (de) Verfahren zur Bestimmung von Kenngrößen eines Automatikgetriebes
DE19824772A1 (de) Vorrichtung zur Steuerung eines Einrückzustandes
DE10344106B4 (de) Schaltstrategie und Getriebesteuerung für ein Getriebe, insbesondere für ein Doppelkupplungsgetriebe
DE102007003924A1 (de) Verfahren und Vorrichtung zur Ansteuerung eines Automatgetriebes eines Fahrzeuges und Hydrauliksystem eines Automatgetriebes
WO2022017561A1 (fr) Procédé de commande de chaîne cinématique
WO1996036824A1 (fr) Boite d'inversion couplable sous charge
DE10347114A1 (de) Verfahren, Vorrichtung und deren Verwendung zum Betrieb eines Kraftfahrzeuges
DE102011011921A1 (de) Verfahren zum Überwachen einer Kupplung
DE102020120988B3 (de) Verfahren zur Steuerung einer Überschneidungsschaltung einer hydraulisch betätigten Doppelkupplung
DE102011008250B4 (de) System zum Steuern eines Getriebes
EP1065401A2 (fr) Procédé de commande d'un embrayage pendant la phase de démarrage, avec la détermination d'une valeur de couple desirée
EP1632694B1 (fr) Chaîne cinématique comportant une boîte de vitesses comportant deux arbres d'entrée en parallèle
EP0482049B1 (fr) Dispositif et procede pour l'utilisation d'une unite de transmission a variation continue d'un vehicule automobile
DE102006018791A1 (de) Verfahren zum Betreiben eines Automatgetriebes
DE102013213751A1 (de) Verfahren zum Losbrechen einer nasslaufenden Kupplung eines Kraftfahrzeuges bei tiefen Temperaturen
WO2001061217A1 (fr) Procede de detection de la position d'actionnement d'un actionneur de boite de vitesses automatique

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 21742703

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 21742703

Country of ref document: EP

Kind code of ref document: A1