WO2005064187A1 - Systeme hydraulique pour deux embrayages a disques - Google Patents

Systeme hydraulique pour deux embrayages a disques Download PDF

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Publication number
WO2005064187A1
WO2005064187A1 PCT/EP2003/013933 EP0313933W WO2005064187A1 WO 2005064187 A1 WO2005064187 A1 WO 2005064187A1 EP 0313933 W EP0313933 W EP 0313933W WO 2005064187 A1 WO2005064187 A1 WO 2005064187A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pressure
reservoir
control valve
hydraulic system
Prior art date
Application number
PCT/EP2003/013933
Other languages
German (de)
English (en)
Inventor
Artur Grunwald
Theodor Gassmann
Colin Zaers
Original Assignee
Gkn Driveline International 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 Gkn Driveline International Gmbh filed Critical Gkn Driveline International Gmbh
Priority to AU2003294821A priority Critical patent/AU2003294821A1/en
Priority to PCT/EP2003/013933 priority patent/WO2005064187A1/fr
Publication of WO2005064187A1 publication Critical patent/WO2005064187A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/104—Clutch
    • F16D2500/10406—Clutch position
    • F16D2500/10425—Differential clutch

Definitions

  • the invention relates to a hydraulic system for acting on at least two Stellzylindem for clutches, which are used in the drive train of a motor vehicle.
  • a preferred application for such a hydraulic system is the operation of two multi-plate clutches in a differential gear, as described for example in the earlier applications 103 17 316.1, 103 29 770.7 and 103 35 674.6 of the Applicant.
  • the application of the invention is not limited thereto, but also includes the operation differently arranged multi-plate clutches, z. B. in different transverse and / or longitudinally locking differentials or clutches in the drive train of a motor vehicle.
  • a first solution lies in a hydraulic system for acting on at least two Stellzylindem for clutches, especially multi-plate clutches, which are used in the drive train of a motor vehicle, comprising a reservoir, an electric motor driven reversible pump, each a flow line to each of the actuating cylinders, one control valve in each of the flow lines. It is possible that the control valves are each 2/2-way valves, or alternatively, that the control valves are each proportional valves.
  • a hydraulic system for acting on at least two Stellzylindem for clutches, in particular multi-plate clutches, which are used in the drive train of a motor vehicle comprising a reservoir, an electric motor driven pump, in each case a flow line from the pump to each of the actuating cylinders, respectively a return line from each of the actuating cylinders to the reservoir, one control valve in each of the flow lines, one control valve in each of the return lines.
  • the control valves are each 2/2-way valves or that the control valves in the flow lines proportional valves and the control valves in the return lines 2/2-way valves.
  • a third solution consists in a hydraulic system for acting on at least two Stellzylindem for clutches, especially multi-plate clutches, which are used in the drive train of a motor vehicle, comprising a reservoir, an electric motor driven pump, each a flow line from the pump to each of the actuating cylinder, each a return line from each of the actuating cylinders to the reservoir, one control valve in each of the flow lines, one controllable throttle in each of the return lines.
  • the function of this solution corresponds largely to the previously mentioned second solution, the pressure reduction in Stellzylindem here via the controllable throttles.
  • a fourth solution proposes a hydraulic system for acting on at least two Stellzylindem for clutches, in particular multi-plate clutches, which are used in the drive train of a motor vehicle, comprising a reservoir, an electric motor driven reversible pump, each a flow line from each of the pump connections to one of the actuating cylinder, one discharge line from each of the supply lines to the reservoir, one control valve in each of the discharge lines.
  • Another solution consists in a hydraulic system for acting on at least two Stellzylindem for clutches, in particular multi-plate clutches, which are used in the drive train of a motor vehicle, comprising a reservoir and two electric motor drivable pumps, each a flow line from each of the pumps to each of the actuating cylinder, one return line from each of the actuating cylinders to the reservoir, one control valve in each of the supply lines, one control valve in each of the return lines, a connecting line between the two flow lines, each connecting between the respective pump and the respective control valve, and another control valve is arranged.
  • check valves are arranged in suction lines from the reservoir to the respective pump.
  • the pressure build-up does not depend on a form which is maintained in a hydraulic system comprising a hydraulic pump driven by an internal combustion engine, but that the pressure build-up by the need-based electromotive drive follows at least one hydraulic pump.
  • the electric motor and the pump are to be integrated, as described for example in the earlier application 103 31 161.0 of the Applicant.
  • the actuating cylinder and a multi-plate clutch can be integrated so that driving the Pump causes a flow to the hydraulic actuating cylinder and then a pressure buildup, the working piston of the hydraulic Stelizylinders via a needle bearing and a pressure plate actuates the multi-plate clutch. After a few revolutions of the pump rotor hydraulic pressure is built up in the actuator cylinder. Leakage on the pump side and / or on the piston side can be compensated by continuously driving the pump rotor.
  • the proposed concept offers a simple structure, more flexibility in the choice of components, better packaging, weight and cost reduction compared to the actuators used today.
  • the integration of a pressure sensor offers the possibility of representing closed control loops.
  • the pump is operated in the direction of pressure build-up.
  • the electric motor is energized until the required pressure is set on the actuating cylinder.
  • the operating mode can be executed in a closed loop, ie. H. the energization of the electric motor of the pump takes place in a closed loop with the measured pressure on the actuating cylinder as a manipulated variable.
  • Deactivation a) Disconnect the electric motor. The pressure is reduced via the pump to the reservoir. b) Active reset by activating the pump in the opposite direction. Afterwards all valves are open.
  • the pump is activated in the direction of pressure build-up.
  • the control valves in the supply lines to the Stellzylindem left and right remain open / be opened. Due to the parallel connection of the two supply lines, the same pressure arises at both Stellzylindem.
  • the energization of the electric motor of the pump is carried out according to the desired pressure in the multi-plate clutches or according to the measurement signal of the left pressure sensor or the right pressure sensor.
  • Deactivation a) Disconnect the electric motor. The pressure is reduced via the pump to the reservoir. b) Active reset by activating the pump in the opposite direction. Afterwards all valves open.
  • two operating modes can be distinguished. a) If necessary, the pump is switched on and energized until the required pressure is set on the actuating cylinder. b) (shorter response times than a)) The pump always delivers hydraulic fluid in the individual unpressurized clutch circuits (all valves open). If necessary, the pump power is increased and the frequency controlled control valves in the flow and return of the pressure circuits, the pressure on the Stellzylindem set. (Alternating control of the switching valves in flow and return)
  • Both operating modes can be executed as closed control loops. That is, the energization of the electric motor of the pump (mode a)) or the frequency control of the switching valves (mode b)) takes place in a closed loop with the measured pressure as a manipulated variable.
  • Non-activated axis All valves are in the "open" position or flow position (failsafe) a) The pump is switched off, the pressure circuits are connected without pressure to the reservoir, the actuators are not pressurized. b) The pump delivers pressureless oil through the two parallel open clutch circuits into the reservoir (all valves open).
  • the pressure on the left setting cylinder is set by selectively opening and closing the control valves (frequency-controlled) in the flow and return of the pressure circuit. Deactivation: see: “1. Not activated axis ".
  • the delivery rate of the pump is increased to maximum delivery.
  • the pressure at the adjusting cylinder is adjusted by selective opening and closing of the control valves (frequency-controlled) in the flow and return of the pressure circuits. Deactivation: see: “1. Not activated axis ".
  • the pump is switched on if necessary and works against the respective throttles
  • the electric motor of the pump is energized so that adjusts itself to the actuating cylinder, the required pressure.
  • the energization of the electric motor of the pump takes place in a closed loop with the measured pressure as a manipulated variable.
  • Non-activated axle All control valves are in the "open" position or the flow-through position (failsafe)
  • the pump is switched off, the pressure circuits are connected to the reservoir without pressure and the actuating cylinders are not pressurized.
  • Increased torque requirement on the left side Activation of the left clutch
  • the pump is activated.
  • the control valve in the flow to the right actuating cylinder is closed.
  • the control valve in the flow to the left actuating cylinder is / remains open.
  • the pressure is measured via the pressure sensor on the left actuating cylinder and the electric motor of the pump is energized in such a way that the desired pressure is set on the left actuating cylinder.
  • the pump is activated.
  • the control valves in the headers to the left and right Stellzylindem remain / are opened. Due to the parallel connection of the two pressure circuits, the same pressure arises at both Stellzylindem.
  • the energization of the electric motor of the pump is carried out according to the desired pressure in the multi-plate clutches or after processing the measuring signal of one of the pressure sensors on the left or right actuating cylinder.
  • the pump is switched on in the desired direction and energized until the required pressure is established on the actuating cylinder.
  • a simultaneous activation of both actuating cylinders is not possible in this variant.
  • the operating mode can be executed as closed loop. That means that the The pump's electric motor operates in a closed loop with the measured pressure as the control variable.
  • Deactivation a) Opening the control valve in the return, electric motor not energized. b) Active reset by activating the pump in the opposite direction with the control valve closed in the return line. In this case, the control valve remain closed on the opposite side, if the other side should be activated very quickly. c) Active reset by activating the pump in the opposite direction with control valve closed in the return and open control valve on the opposite side. The opposite side is not affected.
  • the electric motor of the pump is activated to the right side.
  • the pressure is measured via the pressure sensor on the right actuating cylinder and the electric motor of the pump is energized in such a way that the desired pressure is set on the right actuating cylinder.
  • Deactivation a) Opening the control valve in the return, electric motor not energized. b) Active reset by activating the pump in the opposite direction with the control valve closed in the return line. In this case, the control valve on the Remain closed on the opposite side, if the opposite side is to be activated very quickly, c) Active reset by activating the pump in the opposite direction with closed control valve in the return and open control valve on the other side. The opposite side remains unaffected.
  • the second pump can take over all the functions of the failed pump when the connection valve is open.
  • the check valves behind the pumps prevent the failure of a pump that the still functioning pump pumped through the failed pump in the reservoir.
  • control valves in the flow are optional. In case of failure or without these control valves, the actuating cylinder can still be operated in mode a). Both operating modes can be executed as closed control loops. That is, the energization of the electric motor of the pump (mode a)) or the frequency control of the control valves (mode b)) takes place in a closed loop with the measured pressure as a manipulated variable.
  • All control valves in the supply and return lines are de-energized (failsafe) in the "open" position or in the flow-through position
  • the connection valve is closed (failsafe)
  • a) The pumps are switched off, the pressure circuits are connected to the reservoir without pressure the actuating cylinders are not subjected to any pressure
  • b) The pumps convey hydraulic fluid through the two parallel open pressure circuits into the reservoir essentially without pressure.
  • the left pump is activated.
  • the control valve in the return from the left actuating cylinder is closed.
  • the connection valve is closed.
  • the control valve in the flow to the left actuating cylinder remains open.
  • the pressure is measured via the pressure sensor on the left actuating cylinder and the electric motor of the pump is energized in such a way that the desired pressure is set on the left actuating cylinder.
  • the connection valve is closed.
  • the capacity of the left pump is increased to maximum delivery.
  • the pressure on the left setting cylinder is set by selectively opening and closing the control valves (frequency-controlled) in the supply and return of the left-hand pressure circuit.
  • the energizing of the electric motors of the pumps takes place after the desired pressure in the lamellar couplings or after processing the measuring signal of one of the pressure sensors on the left or right actuating cylinder.
  • the delivery rate of the pumps is increased to maximum delivery.
  • the connecting valve is opened.
  • the pressure at the adjusting cylinder is set by selectively opening and closing the control valves (frequency-controlled) in the flow and return of the pressure circuits.
  • Both pumps work on an actuating cylinder via the open connection valve.
  • the second actuating cylinder is switched off (supply valve closed, return valve open).
  • the connecting valve and the flow valves of both actuating cylinders are opened (return valves closed) until pressure equalization is established.
  • a part of the energy from the closed multi-plate clutch (high pressure) to be closed multi-plate clutch (low pressure level) are redirected (reduced power consumption, smaller pumps / motors).
  • the flow valve is closed to the actuating cylinder of the multi-plate clutch to be switched off and the return valve open.
  • the multi-plate clutch to be activated is pressurized via one or both pumps.
  • FIG. 1 shows a hydraulic system according to the invention in a first embodiment
  • FIG. 2 shows a hydraulic system according to the invention in a second embodiment
  • FIG. 3 shows a hydraulic system according to the invention in a third embodiment
  • FIG. 4 shows a hydraulic system according to the invention in a fourth embodiment
  • FIG. 5 shows a hydraulic system according to the invention in a fifth embodiment
  • FIG. 6 shows a differential gear for connection to a hydraulic system according to the invention.
  • Electric motor 11 drivable reversible hydraulic pump 12 which is connected via a first line 13, the supply or return line may be connected to a reservoir 14.
  • the pump 12 is further via a line 15, which may also be flow or return line, via branches 15 ⁇ , 15 2 , 15 3 , in which control valves 16 ⁇ , 16 2 , 16 3 are arranged, with three Stellzylindem 17 ⁇ 17 2 , 17 3 connected.
  • pressure sensors 18 ⁇ , 18 2 , 18 3 are arranged for pressure monitoring of pending in the Stellzylindem 17 Druk- kes.
  • the pump 12 When the pump 12 is driven by the electric motor 11 in a first conveying direction, the pump sucks in hydraulic medium from the reservoir 14 via the line 13 and delivers it via the lines 15 to the adjusting cylinders 17.
  • the control valves 16 are here, as in the drawing shown, opened.
  • the pressure in the Stellzylindem 17 is monitored by the pressure sensors 18, wherein the pressure in first approximation may be a monitoring quantity for the clutch torque of actuated by Stellzylindem clutches.
  • the control valves 16 can be brought into their closed position. With sufficient tightness of the system so that the pressure can be maintained in the pressure cylinders, so that no further pump drive must be done, ie the electric motor 11 can be set to de-energize in terms of reducing energy consumption.
  • control valves 16 can be opened at short notice and the pump 12 can be driven again at short notice.
  • the electric motor 11 can be set to de-energize even with open control valves 16, in which case a backflow of hydraulic medium from the Stellzylindem 17 in the reservoir 14 may optionally be done under the influence of return springs on the actuating cylinder.
  • a 3 may be control valves executed 16 ⁇ , 16 2, 16 3, a proportional valve 16 'used in place of each of the former.
  • the electric motor 11 may be provided with a parking brake, which is effective in StromlosTER, so that here certain positions of the actuating cylinder can be held without the electric motor must draw electricity.
  • FIG. 2 shows a hydraulic system according to the invention in a second embodiment, which has partial agreement with that shown in FIG.
  • the electric motor 11 drives a not or not necessarily reversible pump 12 ', which sucks via a suction line 13 from the reservoir 14 hydraulic medium and flow lines 15-t, 15 2 , 15 3 and control valves 16- ⁇ , 16 second , 16 3 the actuating cylinder 17 1 t 17 2 , 17 3 supplied.
  • the actuating cylinders are further via return lines 19 ⁇ , 19 2 , 19 3 , in which further control valves 20- ⁇ , 20 2 , 20 3 are connected to the reservoir 14.
  • the pressure is in turn detected by pressure sensors 18 ⁇ 18 2 , 18 3 .
  • a pressure buildup and thus an adjustment of the actuating cylinder in the sense of closing the multi-plate clutches takes place with driven pump 12, open control valves 15 and closed control valves 20.
  • the control valves 15 can be additionally closed and the electric motor 11 de-energized.
  • a pressure reduction takes place exclusively by opening the control valves 20 and return flow of the hydraulic medium via the return lines 19 in the reservoir 14.
  • the control valves 15th , 20 are clocked with different frequencies, so that can be mapped to the Stellzylindem 17 substantially steady pressure increases or pressure reductions.
  • the pressure line 15 3 and return line 19 3 is partially marked with dashed lines.
  • FIG. 3 shows a hydraulic system according to the invention in a further modified embodiment, wherein this hydraulic system largely corresponds to that shown in FIG. Same details as in Figure 2 are assigned the same reference numerals. The foregoing description is hereby incorporated by reference.
  • a pump 12 with a preferred conveying direction and flow lines 15- ⁇ , 15 2 , 15 3 to the Stellzylindem 17- ⁇ , 17 2 , 17 3 and return lines 19- ⁇ , 19 2 , 19 3 of the Stellzylindem 17 provided to the reservoir 14.
  • control valves 16- ⁇ , 16 2 , 16 3 in the return lines instead of the other control valves shown above, in this case controllable chokes 21 1 t 21 2 , 21 3 , the pressure reduction in Stellzylindem 17 and thus serve to relieve the acted upon by Stellzylindem couplings.
  • controllable chokes 21 1 t 21 2 , 21 3 the pressure reduction in Stellzylindem 17 and thus serve to relieve the acted upon by Stellzylindem couplings.
  • the supply line 15 3 and the return line 19 3 is shown in phantom again.
  • the possibility of applying a third Stelizylinders 17 3 and further actuating cylinder by the same pump is hereby clarified.
  • FIG. 4 shows a hydraulic system according to the invention in a further embodiment, which will be described below.
  • An electric motor 11 drives a reversible pump 12 in either a first or a second direction.
  • a first line 15 ⁇ connects the pump directly with a first actuating cylinder 17 ⁇ and a second line 15 2, the pump directly with a second actuating cylinder 17 second Of the lines 15 branch off Ab Kunststoff- or suction 22 ⁇ , 22 2 , in which control valves 23 ⁇ , 23 2 sitting.
  • the diversion and suction lines 22 are connected to a reservoir 14.
  • the pressure reduction in the actuating cylinder 17- ⁇ by opening the control valve 23 ⁇ in the line 22- ⁇ done and analogous to the pressure reduction in the actuating cylinder 17 2 by opening the control valve 23 2 in the line 22 second
  • the pressure reduction is hereby essentially by restoring forces of spring arrangements in the respective multi-disc clutch or on the respective actuating cylinder.
  • the pressure in the actuating cylinder 17 ⁇ be accelerated degraded by the valve 23 ⁇ is kept closed and with the valve open 23 2 in the line 22 2, the direction of rotation of the pump is reversed, so that from the line 15 ⁇ in the line 22 second Hydraulic medium is pumped out. Accordingly, an accelerated pressure reduction in the actuating cylinder 17 2 carried by the control valve 23 2 is kept closed and the control valve 23- ⁇ in the line 22 ⁇ is opened. By appropriate drive of the pump then the pressure in the line 15 2 can be reduced by pumping off hydraulic fluid via the line 22 ⁇ into the reservoir 14.
  • FIG. 5 shows a further hydraulic system according to the invention, which will be described below.
  • the system is essentially symmetrical.
  • a first driven by an electric motor 11 ⁇ pump 12 with a preferred conveying direction sucks through a line 13- ⁇ and a check valve 26 ⁇ from a reservoir 14 and promotes via a flow line 15 ⁇ hydraulic fluid to a first actuating cylinder 17-.
  • a first flow control valve 16- t is provided in the line 15 ⁇ a first flow control valve 16- t is provided.
  • a return line 19- ⁇ in a first return control valve 20 ⁇ is arranged back to the reservoir 14.
  • a pressure sensor 18 is provided on the actuating cylinder 17i.
  • a second driven by an engine H 2 pump 12 2 with a preferred conveying direction sucks through a line 13 2 and a check valve 26 2 from the reservoir 14 and delivers via a flow line 15 2 hydraulic medium to a second actuating cylinder 17 second
  • a second flow control valve 16 2 is provided in the line 15 2 .
  • a return line 19 2 From the second actuating cylinder 17 2 extends a return line 19 2 , in which a second return control valve 2O 2 is arranged, back to the reservoir 14.
  • a pressure sensor 18 2 is provided on the actuating cylinder 17 2 .
  • the hydraulic system has a cross-connection line 24 with a further connection control valve 25 which connects the pressure lines 15 ⁇ 15 2 respectively between the pumps 12- ⁇ , 12 2 and the flow control valves 16- ⁇ , 16 2 .
  • a differential gear is shown, which can be connected to a hydraulic circuit according to the invention according to one of the figures 1 to 5 for control.
  • a multi-part axle housing 51 is shown, which receives the individual parts of the differential gear.
  • a longitudinal shaft 18 with a pinion 19 can be seen, which is in engagement with a ring gear 17 of a differential carrier 16.
  • side gears 21, 22 are arranged coaxially, which mesh with differential gears 25, 26.
  • the differential gears are rotatably mounted on a pin 20 in the differential carrier.
  • the side shafts 23, 24 are inserted, which end in flanges 53, 54, are connected to the propeller shafts of a vehicle axle.
  • a spur gear 40 is placed, which meshes with a spur gear 41 on a countershaft 39, which is parallel to the side shafts 23, 24 outside the differential carrier 16.
  • 39 spur gears 38 are pushed onto the countershaft, which mesh with spur gears 35, 36 which are each integral with the clutch baskets 33, 34 of two cam clutches 27, 28.
  • the inner and outer disks are not shown here in detail.
  • the differential carrier 16 is mounted in tapered roller bearings 55, 56 in the axle housing 51, the countershaft 39 in ball bearings 57, 58.
  • the side shafts 23, 24 are based in needle bearings 59, 60 in the axle housing 51 and needle bearings 61, 62 in the differential carrier 16 from.
  • the clutch baskets 33, 34 of said multi-plate clutches by means of needle bearings 63, 64 are mounted on the side shafts 23, 24, the clutch baskets 33, 34 of said multi-plate clutches by means of needle bearings 63, 64 are mounted.
  • the multi-plate clutches are by means of two hydraulic Stellzylinder- units 17 ⁇ , 17 2 controllably operated, each having a cylindrical annular space 29, 30, an axially displaceable therein annular piston 31, 32 and a pressure medium connection 15 ⁇ , 15 2 include.
  • the controllable loading of the multi-plate clutches 27, 28 takes place here by varying the hydraulic pressure in the annular chambers 29, 30 and thus the travel of the annular piston 31, 32.

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

Abstract

L'invention concerne un système hydraulique servant à solliciter au moins deux vérins d'actionnement (171, 172) pour des embrayages utilisables dans la chaîne cinématique d'un véhicule automobile. Le système hydraulique selon l'invention comprend un réservoir (14), une pompe réversible (12) pouvant être entraînée par moteur électrique, une conduite d'amenée (151, 152) respectivement pour chaque vérin d'actionnement (171, 172), ainsi qu'une soupape de commande (161, 162) respectivement dans chacune des conduites d'amenée (151, 152).
PCT/EP2003/013933 2003-12-09 2003-12-09 Systeme hydraulique pour deux embrayages a disques WO2005064187A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2003294821A AU2003294821A1 (en) 2003-12-09 2003-12-09 Hydraulic system for two multiplate clutches
PCT/EP2003/013933 WO2005064187A1 (fr) 2003-12-09 2003-12-09 Systeme hydraulique pour deux embrayages a disques

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2003/013933 WO2005064187A1 (fr) 2003-12-09 2003-12-09 Systeme hydraulique pour deux embrayages a disques

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Publication Number Publication Date
WO2005064187A1 true WO2005064187A1 (fr) 2005-07-14

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006061516A1 (de) * 2006-12-18 2008-06-19 Getrag Driveline Systems Gmbh Hydraulikanordnung zur Ansteuerung zweier Aktuatoren
EP1975446A1 (fr) * 2007-03-27 2008-10-01 Univance Corporation Dispositif de transmission de force
EP2020522A1 (fr) 2007-08-02 2009-02-04 HONDA MOTOR CO., Ltd. Système d'embrayage hydraulique et procédé pour un véhicule
EP2020521A1 (fr) 2007-08-02 2009-02-04 Honda Motor Co., Ltd Système d'embrayage hydraulique et procédé pour un véhicule
WO2010063377A1 (fr) * 2008-12-05 2010-06-10 Gm Global Technology Operations, Inc. Système hydraulique et procédé de commande de pression
WO2010081743A1 (fr) * 2009-01-19 2010-07-22 Gkn Driveline International Gmbh Dispositif d'actionnement
WO2011076627A1 (fr) * 2009-12-23 2011-06-30 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Système d'embrayage et procédé permettant de faire fonctionner un système d'embrayage
EP2333330A3 (fr) * 2009-12-10 2012-10-24 Centa-Antriebe Kirschey GmbH Embrayage avec protection contre surcharge pour une éolienne
DE102011102277A1 (de) * 2011-05-23 2012-11-29 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kupplungsanordnung und Antriebsstrang für ein Kraftfahrzeug
US8900086B2 (en) 2007-08-02 2014-12-02 Honda Motor Co., Ltd. Hydraulic vehicle clutch system, drivetrain for a vehicle including same, and method
US8939268B2 (en) 2011-06-07 2015-01-27 Fte Automotive Gmbh Hydraulic actuating device for actuation of clutches in, in particular, a multi-clutch transmission for motor vehicles
DE102014102250A1 (de) * 2014-02-21 2015-08-27 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kupplungsanordnung, Kraftfahrzeugantriebsstrang und Kupplungssteuerverfahren
US11111972B2 (en) 2017-07-11 2021-09-07 Schaeffler Technologies AG & Co. KG Method for identifying leaks by means of an actuator

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US8938958B2 (en) 2006-12-18 2015-01-27 Getrag Driveline Systems Gmbh Hydraulic arrangement for the activation of two actuators
EP1975446A1 (fr) * 2007-03-27 2008-10-01 Univance Corporation Dispositif de transmission de force
US8256593B2 (en) 2007-03-27 2012-09-04 Univance Corporation Driving force transmitting device
EP2020521A1 (fr) 2007-08-02 2009-02-04 Honda Motor Co., Ltd Système d'embrayage hydraulique et procédé pour un véhicule
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EP2020522A1 (fr) 2007-08-02 2009-02-04 HONDA MOTOR CO., Ltd. Système d'embrayage hydraulique et procédé pour un véhicule
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WO2010081743A1 (fr) * 2009-01-19 2010-07-22 Gkn Driveline International Gmbh Dispositif d'actionnement
CN102387931A (zh) * 2009-01-19 2012-03-21 Gkn动力传动系统国际有限责任公司 促动组件
DE102009005410B4 (de) * 2009-01-19 2012-04-12 Gkn Driveline International Gmbh Aktuierungsanordnung und Verfahren zum Zuschalten einer Antriebsachse im Antriebsstrang eine Kraftfahrzeugs sowie Antriebsanordnung
KR101313991B1 (ko) 2009-01-19 2013-10-01 게케엔 드리펠린 인터나쇼날 게엠베하 작동 장치, 작동 장치를 구비한 구동 장치 및 작동 장치에 의해 구동 차축을 접속하기 위한 방법
US8739953B2 (en) 2009-01-19 2014-06-03 Gkn Driveline International Gmbh Actuating assembly
EP2333330A3 (fr) * 2009-12-10 2012-10-24 Centa-Antriebe Kirschey GmbH Embrayage avec protection contre surcharge pour une éolienne
US8511452B2 (en) 2009-12-23 2013-08-20 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Clutch system and method for operating a clutch system
CN102667215A (zh) * 2009-12-23 2012-09-12 克诺尔商用车制动系统有限公司 离合器系统和用于运行离合器系统的方法
DE102009060182B4 (de) * 2009-12-23 2012-03-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kupplungssystem und Verfahren zum Betreiben eines Kupplungssystems
WO2011076627A1 (fr) * 2009-12-23 2011-06-30 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Système d'embrayage et procédé permettant de faire fonctionner un système d'embrayage
WO2012159838A3 (fr) * 2011-05-23 2013-03-21 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Ensemble embrayage et chaîne cinématique pour un véhicule automobile
DE102011102277A1 (de) * 2011-05-23 2012-11-29 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kupplungsanordnung und Antriebsstrang für ein Kraftfahrzeug
US9126576B2 (en) 2011-05-23 2015-09-08 GETRAG Getriebe—und Zahnradfabrik Harmann Hagenmeyer GmbH & Cie KG Clutch arrangement and drivetrain for a motor vehicle
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US8939268B2 (en) 2011-06-07 2015-01-27 Fte Automotive Gmbh Hydraulic actuating device for actuation of clutches in, in particular, a multi-clutch transmission for motor vehicles
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