WO2011015182A1 - Système hydraulique de commande hydraulique d'une boîte de vitesses à double embrayage - Google Patents

Système hydraulique de commande hydraulique d'une boîte de vitesses à double embrayage Download PDF

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Publication number
WO2011015182A1
WO2011015182A1 PCT/DE2010/000897 DE2010000897W WO2011015182A1 WO 2011015182 A1 WO2011015182 A1 WO 2011015182A1 DE 2010000897 W DE2010000897 W DE 2010000897W WO 2011015182 A1 WO2011015182 A1 WO 2011015182A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
valve
control
pressure
hydraulic system
Prior art date
Application number
PCT/DE2010/000897
Other languages
German (de)
English (en)
Inventor
Martin Staudinger
Marco Grethel
Roshan Willeke
Eric MÜLLER
Reinhard Stehr
Original Assignee
Schaeffler Technologies Gmbh & 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 Gmbh & Co. Kg filed Critical Schaeffler Technologies Gmbh & Co. Kg
Priority to DE112010003203T priority Critical patent/DE112010003203A5/de
Priority to CN201080034723.3A priority patent/CN102483151B/zh
Publication of WO2011015182A1 publication Critical patent/WO2011015182A1/fr

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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
    • F16H61/02—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 the signals used
    • F16H61/0202—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 the signals used the signals being electric
    • F16H61/0204—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 the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
    • 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
    • F16H61/0021—Generation or control of line 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
    • F16H61/688—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 two inputs, e.g. selection of one of two torque-flow paths by clutches
    • 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
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor

Definitions

  • Hydraulic system for the hydraulic control of a dual clutch transmission
  • the invention relates to a hydraulic system for the hydraulic actuation of a dual-clutch transmission with a first partial transmission and a second partial transmission each having a clutch, with a hydraulic energy source for supplying the hydraulic system with hydraulic energy, and with a first hydraulic device for driving the first partial transmission and with a second hydraulic device for driving the second partial transmission.
  • Hydraulic systems for the hydraulic control and supply of a transmission are known.
  • the pump drive is a mechanical pump drive, which is coupled to the combustion engine.
  • this mechanical pump drive can be supplemented by an E-pump arrangement (that is, an electric motor with a pump).
  • the invention has for its object to provide an improved hydraulic system, in particular with as few hydraulic components to enable control and clutch cooling of a transmission, in particular dual-clutch transmission, in particular to get along with the smallest possible number and variety of parts on hydraulic components, beyond a low energy consumption and a allow low leakage, and / or interpret the control at least partially safety shutdown.
  • the object is in a hydraulic system for the hydraulic control and supply of a transmission, in particular a dual-clutch transmission, with a first partial transmission and a second partial transmission each with a clutch, with a hydraulic energy source for supplying the hydraulic system with hydraulic energy, with a first hydraulic device for driving the first sub-transmission and with a second hydraulic device for driving the second partial transmission, achieved in that by means of the first hydraulic device and the second hydraulic device each have a first control pressure and a second control pressure are adjustable, for engaging gears of the dual-clutch transmission of the respective first control pressure and the respective second control pressure by means of a first multiplexer valve of the first hydraulic device and by means of a second multi-tip valve of the second hydraulic device in each case optionally on a first double surface enkolben of the respective hydraulic device or on a second double-surface piston of the respective hydraulic device are conductive.
  • Each of the hydraulic devices has two double-surface pistons, that is, a first double-surface piston and a second dual-surface piston.
  • four gears of each partial transmission of the dual-clutch transmission can be controlled per hydraulic device. It is possible to make do with only two control pressures, which can be advantageously switched by means of the corresponding upstream multiplexer valve on one of the double-surface piston for driving. It is advantageous to drive two double-surface piston only one corresponding valve for generating the first control pressure and the second control pressure necessary, depending on whether the first double-surface piston or the second double-surface piston is to be controlled, the corresponding upstream multiplexer valve selectively switch the two control pressures on the first double-surface piston or the second double-surface piston of the respective hydraulic device or can guide.
  • the object is alternatively or additionally in a hydraulic system for the hydraulic control and supply of a transmission, in particular a dual-clutch transmission, with a first partial transmission and a second partial transmission each with a clutch, with a hydraulic energy source for supplying the hydraulic system with hydraulic energy, with a first hydraulic device for driving the first partial transmission and with a second hydraulic device for driving the second partial transmission, achieved in that the hydraulic system comprises at least one safety valve device by means of the optional at least one of the hydraulic devices for driving the corresponding gear unit of the dual clutch transmission is depressurized switchable, wherein additionally by means of a locking device the safety valve device both hydraulic devices of the hydraulic power source are at least decoupled.
  • one of the partial transmission can be depressurized, wherein advantageously the respective other partial transmission still remains functional.
  • Unpressurised switching can be understood as meaning a laying or switching through of corresponding hydraulic lines to a tank of the hydraulic system.
  • Uncoupling can be understood as meaning a separation of corresponding hydraulic lines.
  • first multiplexer valve of the first hydraulic device and the second multiplexer valve of the second hydraulic device and the blocking device can be actuated by means of a first pilot valve.
  • a pilot valve can be understood to mean an electrically controllable proportional valve for generating a hydraulic control pressure controlling the multiplexer valves and the blocking device.
  • the blocking device in a first control position of the first pilot valve, the blocking device is closed and the multiplexer valves are not actuated, in a second control position of the first pilot valve, the blocking device is closed. - A - device is opened and the multiplexer valves are unconfirmed, and in a third control position of the first pilot valve, the locking device is opened and the multiplexer valves are actuated.
  • control positions an increasing control pressure or alternatively optionally set a decreasing control pressure, advantageously three different control states are adjustable by means of a pilot valve, wherein advantageously the first control position can be set at a de-energized state of the pilot valve, advantageously in a possible power failure, a safety function is given by blocking the locking device.
  • the first pilot valve is electrically controllable, assumes the first control position in a de-energized state, and the second control position and the third control position with increasing current supply.
  • the de-energized state including in case of power failure, a safety shutdown or a hydraulic separation of the downstream hydraulic devices.
  • the locking device has a locking slide.
  • the function can be realized by means of a simple locking slide, in particular by means of a locking slide which shuts off two lines in parallel.
  • the first partial transmission has a first coupling valve for driving a first clutch of the first partial transmission and the second partial transmission has a second coupling valve for actuating a second clutch of the second partial transmission, wherein the coupling valves a safety valve of the safety valve device downstream of the locking device the safety valve device are connected downstream.
  • the coupling valves are branched between the safety valve and the gate valve, wherein advantageously, despite a closing of the gate valve, the coupling valves can be supplied with hydraulic energy, so the clutches are actuated accordingly.
  • the multiplexer valves and thus the gear actuators of the dual-clutch transmission can be separated from the hydraulic energy source, with both clutches are still controlled with open safety valve. It is also possible, with the gate valve open, to depressurize one of the partial transmissions of the dual-clutch transmission, that is to say the corresponding gear actuators and the clutch actuation without pressure. th, wherein the respective other partial transmission remains fully functional or hydraulically controlled.
  • this also results in the possibility to realize a minimal leakage, since even in the case of non-actuation of the gear actuator, the multiplexer valves can be separated from the hydraulic energy source, that is not below the system pressure and consequently have a minimal leakage.
  • first double-surface piston and the second double-surface piston are each designed as a uniform-area piston with two equal pressure surfaces acting in opposite directions.
  • a corresponding control of the double-surface piston can be carried out symmetrically, so be carried out by an identical setting of the control pressures depending on the position of the multiplexer valves.
  • first hydraulic device and the second hydraulic device each have a double pressure regulator, by means of which the respective first control pressure and second control pressure are adjustable.
  • double pressure regulator by means of the double pressure regulator, the correspondingly parallel piston connected downstream by means of the multiplexer valve can be actuated.
  • each of the double pressure regulator has a control position in which the first control pressure and the second control pressure can be switched to a tank.
  • this control position that is, for example, in driving situations of the dual-clutch transmission, in which no change in gear occurs, the corresponding downstream equal-area piston can be depressurized, which also results in a minimum leakage.
  • the object is also achieved in a dual-clutch transmission with a first partial transmission and a second partial transmission, which can be controlled by means of and / or with a hydraulic system described above. This results in the advantages described above.
  • FIGURE 1 shows a hydraulic system for the hydraulic control and supply of a dual-clutch transmission.
  • first partial transmission 5 is part of the hydraulic system
  • first hydraulic system and the second partial transmission 7 as part of the hydraulic system upstream of the second hydraulic system.
  • the hydraulic system 1 is supplied with a first, electrically driven pump 9 and a second, mechanically driven pump 11 with hydraulic energy.
  • the electrically driven first pump 9, a storage charging valve 13 is connected downstream.
  • the accumulator charging valve 13 is spring-reset and has a double pressure feedback.
  • the accumulator charging valve 13 is used for regulating or adjusting a level or accumulator pressure of a hydraulic accumulator 15.
  • the accumulator charging valve 13 are two check valves and a throttle connected downstream.
  • a filter for filtering a corresponding hydraulic medium is provided. In a first switching position, which is shown in Figure 1, the accumulator charging valve 13 is connected in the direction of the pressure accumulator 15, so that it can be charged by means of the first pump 9 with hydraulic energy.
  • the accumulator charging valve 13 is in a second switching position, in which the funded by the first pump 9 volumetric flow couplings 17 can be supplied for cooling .
  • Each of the partial transmissions 5 and 7 of the dual-clutch transmission 3 has one of the clutches 17.
  • adeölstrompriorticiansventils 19 which is connected upstream of the clutches 17 and the accumulator charging valve 13 downstream, a corresponding volume flow to the respectively more stressed, for example actuated, the clutches 17 are prioritized.
  • thedeölstrompriorticiansventil 19 two opposing pressure surfaces on which a clutch actuation pressure of actuation cylinders 21 of the clutches 17 is connected.
  • the accumulator charging valve 13 and the accumulator 15, a safety valve 23 is connected downstream.
  • the safety valve 23 has a double pressure feedback and serves to safety shutdown of the partial transmissions 5 and 7 of the dual clutch transmission 3.
  • a middle position which is shown in Figure 1
  • the pressure accumulator 15 and the first pump 9 to the two partial transmissions 5 and 7 of the dual-clutch transmission 3 through.
  • either one of the partial transmissions 5, 7 of the first pump 9 and the pressure accumulator 15 is selectively assigned, wherein the respective other of the partial transmissions 5, 7 is connected to a pressureless tank 25 of the hydraulic system 1.
  • the safety valve 23 is followed by a locking device in the form of a locking slide 27.
  • the locking slide 27 and the safety valve 23 form a safety device of the hydraulic system 1.
  • the first partial transmission 5 and the second partial transmission 7 can be separated from the first pump 9 and the pressure accumulator 15 in a first switching position, which is shown in FIG become. In a second switching position, these can be switched through to the first pump 9 and the pressure accumulator 15.
  • the actuating cylinder 21 is diverted to actuate the clutches 17, so that they are advantageously controlled or actuated even when the gate valve 27 is closed. All other functions of the partial transmissions 5, 7, in particular a gear actuator, are separated from the pressure accumulator 15 and the first pump 9, in the first switching position of the locking slide 27 shown in FIG.
  • an electrically operable coupling valve 29 is connected upstream of these.
  • the coupling valves 29 are connected downstream of the safety valve 23 and are arranged downstream of the locking slide 27 or branched off, so that the advantageous supply of hydraulic energy is given even when the gate valve 27 is closed.
  • the locking slide 27 is followed by two double pressure control valves 31, by means of which a first control pressure 33 and a second control pressure 35 are adjustable.
  • the double-pressure control valves 31 have a double pressure feedback and allow in a middle position to set the control pressures 33 and 35 to the tank level or to put on the tank 25. In a right and a left switching position, one of the control pressures 33 and 35 can be set to the tank 25 and the other in each case to a desired pressure level.
  • a total of four double-surface pistons which are designed as equal-area pistons 37, can be actuated.
  • Each of the partial transmissions 5, 7 has a first and a second of the uniform-area pistons 37, wherein in each case between two of the uniform-area pistons 37 one of the partial transmissions 5, 7 and the associated Doppeldruckregelventil 31 a multiplexer valve 39 is connected.
  • Each of the multiplexer valves 39 has two switching positions, wherein in a first switching position, one of the equal-area pistons 37 is acted on by the control pressures 33 and 35 and the respective other is connected to the tank 25 on both sides.
  • a control of a total of four gear stages of the respective partial transmission 5, 7 take place.
  • the second pump 11 of the hydraulic power source is mechanically driven by an internal combustion engine 41, which is the dual-clutch transmission 3 upstream. Between the internal combustion engine 41 and the second pump 11, a hydraulically actuated or switchable clutch 43 is connected. Advantageously, the second pump 11 can be decoupled from this for saving mechanical energy of the internal combustion engine 41 or be driven mechanically only when necessary.
  • the second pump 11 is followed by a cooler arrangement 45.
  • the cooler arrangement 45 has a cooler and a check valve connected in parallel therewith, which, for example, at a high backpressure pressure, that is to say a comparatively cold hydraulic medium, can bypass this on the cooler of the cooler arrangement 45.
  • the cooler arrangement 45 is followed by a cooling oil valve 49.
  • the cooling oil valve 49 can occupy a total of three switching positions, wherein in a first switching position, one of the clutches 17, in a second switching position, the respective other of the clutches 17 are connected to the second pump 11, so can be acted upon by this for cooling with hydraulic medium.
  • a middle position which is shown in Figure 1
  • both clutches 17 are separated from the second pump 11.
  • a corresponding flow of the second pump 11 is connected to the tank 25.
  • an additional cooling of the hydraulic medium takes place, for example to set or reach a desired temperature in the tank 25.
  • the control of the locking slide 27 and the two multiplexer valves 39 is carried out hydraulically by means of a first pilot valve 51.
  • a corresponding pilot pressure for controlling the locking slide 27 and the multiplexer valves 39 can take place.
  • the gate valve 27 is initially closed. This switching position assumes the first pilot valve 51 in the de-energized state.
  • the multiplexer valves 39 are initially not actuated.
  • further increasing energization of the first proportional valve 51 and thus further increasing control pressure finally turn the multiplexer valves 39 in their second switching position, so that the corresponding other equal-area piston 37 of the partial transmission 5, 7 can be controlled.
  • the required control of the double pressure valves 31 is carried out hydraulically by means of a respective second pilot valve 53.
  • the second pilot valves 53 are also electrically operated proportional valves for setting a the double pressure control valves 31 hydraulically controlling pilot pressure. With increasing current supply, first of all a pressure regulation of the second control pressure 35, a pressure-less connection of the two control pressures 33 and 35, as well as further increasing current supply, can be used to control the first control pressure 33.
  • control of the safety valve 23 is also hydraulically by means of a third electrically controllable pilot valve 55th
  • the double pressure regulator 31 and the safety valve 23 can also be actuated directly by a proportional solenoid.
  • the switchable clutch 43 In a de-energized state of the fourth pilot valve 57, the switchable clutch 43 is initially opened so that no mechanical energy from the internal combustion engine 41 for driving on the second pump 11 is transmitted. With increasing energization initially closes the switchable coupling 43. With further increasing energization, the three switching positions of the cooling oil valve 49 can be adjusted. It is conceivable, the cooling oil valve 49 alternately to pulse in its two end positions, thereby to supply both of the clutches 17 with a corresponding cooling oil volume flow. Further, it is possible to set a duty cycle, for example, to supply one of the clutches 17 with a higher cooling oil volume flow.
  • the uniform-area pistons 37 realize so-called gear actuator pistons for actuating or for engaging gears of the dual-clutch transmission 3.
  • Each of the uniform-surface pistons 37 has two pressure surfaces of the same size, which are in opposite directions. set directions work. Upstream of these are the two multiplexer valves 39, which distribute two controlled pressures, the first control pressure 33 and the second control pressure 35, respectively, to a total of four piston surfaces per partial transmission 5, 7 of the equal-area piston 37.
  • Each of the multiplexer valves 39 is thus responsible for one of the partial transmissions 5, 7.
  • Each of the multiplexer valves 39 is preceded by a double-pressure regulating valve 31, which can adjust one of the control pressures 33, 35 in each direction from a central position. In the middle position, the double pressure control valves 31 or both outputs are connected to the tank 25.
  • the double pressure control valves 31 are piloted by means of the second pilot valves 53, but could alternatively be operated directly.
  • the pilot valves 51 to 57 represent pressure regulator.
  • Both double pressure control valves 31 are connected downstream of a common small gate valve 27, which can simultaneously separate a system pressure supplied by the first pump 9 from both partial transmissions 5, 7.
  • the safety valve 23 is designed as a pressure regulator, which in a middle position, both partial transmissions 5, 7 fully to the system pressure, ie to the first pump 9 turns on. In each case one of the partial transmissions 5, 7 can be depressurized starting from the middle position, wherein advantageously the respective other of the partial transmissions 5, 7 is then at the full system pressure.
  • Both the gate valve 27 and the two multiplexer valves 39 are advantageously hydraulically controlled by the same first pilot valve 51.
  • first pilot valve 51 In the de-energized state of the first pilot valve 51 locks the gate valve 27 and both multiplexer valves 39 are in a normal position. If the pilot pressure is raised by the first pilot valve, the gate valve 27 initially opens. As long as it is closed, the multiplexer valves 39 are also advantageously not needed. The multiplexer valves 39 still remain in the basic position. If the pilot pressure is further raised via the first pilot valve 51, the multiplexer valves 39 switch to another stop.
  • the first pilot valve 51 can advantageously occupy three switching positions for controlling the blocking slide 27 and the two multiplexer valves 39.
  • the gear actuator of the dual-clutch transmission 3 can therefore mit- Tels the locking slide 27 are depressurized, although the clutches 17 can still be operated. By this measure, a leakage of the hydraulic system 1 can be reduced to a minimum. If, in addition, one of the clutches 17 is to be depressurized, this is still possible by means of the safety valve 23. The only pressurized leaks then arise only on the pilot valves 51 to 57 and the clutch valves 29.
  • the control of the dual-clutch transmission 3 by means of only seven electromagnets of the pilot valves 51 to 57 and the clutch valves 29 done.
  • the third pilot valves 53 not directly to the stopper valve 27 but directly to the safety valve 23, ie to divert the latter at the same location as the couplings 21.
  • the double pressure control valves 31 thus remain controllable despite the closed gate valve 27, for example to switch the control pressures 33, 35 together to the tank 25.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un système hydraulique de commande et d'alimentation hydraulique d'une boîte de vitesses, notamment d'une boîte de vitesses à double embrayage, comprenant une première boîte de vitesse partielle et une deuxième boîte de vitesses partielle qui présentent respectivement un embrayage, avec: - une source d'énergie hydraulique pour alimenter le système hydraulique en énergie hydraulique; - un premier dispositif hydraulique pour commander la première boîte de vitesses partielle; - un deuxième dispositif hydraulique pour commander la deuxième boîte de vitesses partielle. Pour produire un système hydraulique amélioré, il est prévu qu'une première pression de commande et une deuxième pression de commande puissent être ajustées respectivement au moyen du premier dispositif hydraulique et du deuxième dispositif hydraulique, pour passer les rapports de la boîte de vitesses à double embrayage, la première pression de commande en question et la deuxième pression de commande en question pouvant être guidées, au moyen d'une première soupape multiplex du premier dispositif hydraulique et au moyen d'une deuxième soupape multiplex du deuxième dispositif hydraulique, sélectivement sur un premier piston à double face du dispositif hydraulique concerné ou sur un deuxième piston à double face du dispositif hydraulique concerné.
PCT/DE2010/000897 2009-08-06 2010-07-29 Système hydraulique de commande hydraulique d'une boîte de vitesses à double embrayage WO2011015182A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112010003203T DE112010003203A5 (de) 2009-08-06 2010-07-29 Hydrauliksystem zum hydraulischen Ansteuern eines Doppelkupplungsgetriebes
CN201080034723.3A CN102483151B (zh) 2009-08-06 2010-07-29 以液压方式控制双离合器变速器的液压系统

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102009036427.7 2009-08-06
DE102009036427 2009-08-06
DE102009055900.0 2009-11-26
DE102009055900 2009-11-26

Publications (1)

Publication Number Publication Date
WO2011015182A1 true WO2011015182A1 (fr) 2011-02-10

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Country Status (3)

Country Link
CN (1) CN102483151B (fr)
DE (2) DE112010003203A5 (fr)
WO (1) WO2011015182A1 (fr)

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EP2410213A3 (fr) * 2010-07-21 2012-05-16 hofer mechatronik GmbH Système hydraulique de transmission pour boîte de vitesses à plusieurs embrayages et procédé de commande avec des vannes hydrauliques pour des boîtes de vitesses comprenant plusieurs embrayages offrant une meilleure sécurité de fonctionnement
EP3093533A3 (fr) * 2015-05-11 2017-11-08 GETRAG B.V. & Co. KG Chaine cinematique de vehicule automobile et son procede de fonctionnement
WO2018055204A1 (fr) 2016-09-26 2018-03-29 Hofer Mechatronik Gmbh Circuit hydraulique d'une transmission à embrayage double, en particulier comprenant une commande d'embrayage, et procédé de réaction d'urgence

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CN101858431A (zh) * 2010-04-17 2010-10-13 浙江吉利汽车研究院有限公司 一种双离合器自动变速器换档用液压装置
DE102011005284B4 (de) * 2011-03-09 2021-11-04 Zf Friedrichshafen Ag Verfahren zur Realisierung des Segelbetriebs bei einem Kraftfahrzeug mit einem Automatgetriebe
DE102011005852A1 (de) * 2011-03-21 2012-09-27 Zf Friedrichshafen Ag Verfahren zum Steuern eines automatischen oder automatisierten Schaltsystems
DE102011100849A1 (de) * 2011-05-06 2012-11-08 Audi Ag Doppelkupplungsgetriebe
DE102011100808A1 (de) * 2011-05-06 2012-11-08 Audi Ag Kupplungsgetriebe, insbesondere Doppelkupplungsgetriebe, mit hydraulischem Betätigungssystem
DE102011100799B4 (de) * 2011-05-06 2017-06-01 Audi Ag Doppelkupplungsgetriebe, Verfahren zum Betreiben
DE102011100809B4 (de) * 2011-05-06 2018-05-17 Audi Ag Kupplungsgetriebe mit Sicherheitsventilanordnung
DE102011100836A1 (de) * 2011-05-06 2012-11-08 Audi Ag Hydraulikkreis, Verfahren zum Betreiben
US8834310B2 (en) * 2012-10-24 2014-09-16 Ford Global Technologies, Llc Paths for supplying fluid to clutches of an automatic transmission
DE102012022086B4 (de) 2012-11-09 2023-05-11 Volkswagen Aktiengesellschaft Hydraulische Steuerungsvorrichtung
DE202013101840U1 (de) * 2013-04-26 2014-07-29 Hofer Mechatronik Gmbh Hydraulische Schaltung eines Doppelkupplungsgetriebes
DE102013008701B3 (de) 2013-05-22 2014-10-09 Audi Ag Verfahren zum Betreiben einer Getriebeeinrichtung sowie entsprechende Getriebeeinrichtung
DE102013216285A1 (de) * 2013-08-16 2015-02-19 Schaeffler Technologies Gmbh & Co. Kg Kühlsystem
EP3080473B1 (fr) * 2013-12-09 2019-08-21 Schaeffler Technologies AG & Co. KG Système hydraulique pour double embrayage ainsi que procédé de commande ou de refroidissement du double embrayage
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