WO2021069021A1 - Dispositif d'embrayage double, dispositif hydraulique et procédé permettant de commander un dispositif hydraulique - Google Patents

Dispositif d'embrayage double, dispositif hydraulique et procédé permettant de commander un dispositif hydraulique Download PDF

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Publication number
WO2021069021A1
WO2021069021A1 PCT/DE2020/100839 DE2020100839W WO2021069021A1 WO 2021069021 A1 WO2021069021 A1 WO 2021069021A1 DE 2020100839 W DE2020100839 W DE 2020100839W WO 2021069021 A1 WO2021069021 A1 WO 2021069021A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
valve
pump
active
actuation
Prior art date
Application number
PCT/DE2020/100839
Other languages
German (de)
English (en)
Inventor
Yunfan Wei
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 CN202080063181.6A priority Critical patent/CN114375372A/zh
Publication of WO2021069021A1 publication Critical patent/WO2021069021A1/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
    • 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
    • F16D48/00—External control of clutches
    • F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
    • F16D48/066—Control of fluid pressure, e.g. using an accumulator
    • 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
    • F16D2048/0263—Passive valves between pressure source and actuating cylinder, e.g. check valves or throttle 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
    • 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
    • F16D2048/0266—Actively controlled valves between pressure source and actuation cylinder
    • 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
    • F16D2048/0287—Hydraulic circuits combining clutch actuation and other hydraulic systems
    • F16D2048/029—Hydraulic circuits combining clutch actuation with clutch lubrication or cooling
    • 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
    • F16D2500/30—Signal inputs
    • F16D2500/302—Signal inputs from the actuator
    • F16D2500/3022—Current
    • 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
    • F16D2500/30—Signal inputs
    • F16D2500/302—Signal inputs from the actuator
    • F16D2500/3024—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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/70—Details about the implementation of the control system
    • F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
    • F16D2500/70402—Actuator parameters
    • F16D2500/7041—Position

Definitions

  • the invention relates to a method for controlling a hydraulic device for a double clutch device according to the preamble of claim 1. Furthermore, the invention relates to a hydraulic device according to claim 9 and a double clutch device according to claim 10.
  • a hydraulic device for a double clutch device is described, for example, in DE 102019 123965.6. This shows a single rail structure in which each of the two clutches of the double clutch device is assigned a clutch valve for controlling the fluid pressure for clutch actuation and at least one spring pressure accumulator and one check valve are arranged.
  • the object of the present invention is to control a hydraulic device for a double clutch device in a simple and reliable manner.
  • At least one of these objects is achieved by a method for controlling a hydraulic device with the features according to claim 1.
  • the double clutch device can be operated efficiently, economically and reliably.
  • Control can include control and / or regulation of the hydraulic device.
  • the actuation current can be a value less than the maximum actuation current and greater than an actuation current that is dependent on the sum of the fluid setpoint pressure and a pressure hysteresis parameter.
  • the double clutch device can be arranged in a drive train of a vehicle, in particular a motor vehicle.
  • the Double clutch device can be effective in a power shiftable E-axle.
  • the E-axis can have at least two switchable gear ratios.
  • the pump can be driven electrically.
  • An electric motor can be assigned to the pump.
  • the pump can be operated independently of the speed of the clutch. This enables a sufficient minimum speed of the pump to be achieved. Furthermore, the energy requirement of the pump can be reduced.
  • the clutch cooling device can be supplied hydraulically via the pump or via another pump.
  • the pump and the other pump can be operated by a common electric motor.
  • the pump and the additional pump can each be operated by their own electric motor.
  • the speed of the two electric motors can be set independently of each other.
  • the hydraulic device can have at least one spring pressure accumulator as hydraulic capacity.
  • the spring pressure accumulator can be assigned to one of the two clutches. Each clutch can also be assigned its own spring pressure accumulator.
  • the spring pressure accumulator can be arranged between the pump and the respective clutch valve.
  • the hydraulic device can have at least one check valve.
  • the check valve can be assigned to one of the two clutches. Each clutch can also be assigned its own check valve.
  • the check valve can be arranged between the pump and the respective clutch valve.
  • the spring pressure accumulator can be arranged between the check valve and the respective clutch valve.
  • a further hydraulic control state which corresponds to a second closed state in which the clutch valve assigned to the active clutch is actuated by an actuation current that is less than or equal to a maximum actuation current and the pump speed depends on the cooling speed required for clutch cooling is controlled.
  • the system pressure valve can be inactive in the second closed state.
  • the actuation current of the system pressure valve can be zero.
  • the actuation current of the active clutch associated clutch valve can have a value smaller than the maximum actuation current and greater than an actuation current that is dependent on the sum of the target fluid pressure and a pressure hysteresis parameter.
  • the predetermined actuation current of the clutch valve and / or the system pressure valve is preferably set as a function of the temperature. This allows the temperature-dependent conditions to be influenced.
  • the system pressure valve in the slip state and / or in the first closed state, is actuated by an actuating current that is dependent on a fluid system pressure that is one pressure difference higher than the target fluid pressure. In this way, a fluid pressure that is sufficient to maintain the target fluid pressure can be set.
  • the pressure difference in the slip state can be unequal to the pressure difference in the first closed state.
  • a first fluid supply path proceeds from the pump, to which the first and second clutch valves are assigned, the system pressure valve being arranged between the pump and the first and second clutch valve.
  • a second fluid supply path to the clutch cooling device which is arranged parallel to the first fluid supply path, starts from the pump.
  • the clutch cooling device can effect a spray fluid cooling.
  • the active clutch is the torque-transmitting clutch or the clutch selected for further torque transmission.
  • the actuation current of the inactive clutch is set via the clutch valve assigned to it independently of the respective operating state of the clutch valve assigned to the active clutch, the pump and the system pressure valve.
  • the fluid pressure in the fluid branch of the inactive clutch can be set separately from the fluid pressure in the fluid branch of the active clutch.
  • the clutch valve assigned to this clutch is closed during the transition from an active to an inactive clutch.
  • the fluid pressure in the fluid branch assigned to this clutch can be increased briefly beforehand.
  • Figure 1 A block diagram of a Flydraulik device for a
  • Double clutch device for carrying out a method in a special embodiment of the invention.
  • Figure 2 A block diagram of a further hydraulic device for a
  • Double clutch device for carrying out a method in a special embodiment of the invention.
  • Figure 3 A block diagram of a further hydraulic device for a
  • Double clutch device for carrying out a method in a special embodiment of the invention.
  • Figure 4 A block diagram of a method for controlling the
  • Figure 5 A block diagram of a method for controlling the
  • Figure 6 A block diagram of a method for controlling the
  • FIG. 7 A block diagram of a method in a further special one
  • FIG. 8 A block diagram of a method in a further special one
  • FIG. 1 shows a block diagram of a hydraulic device 10 for a double clutch device 12 for carrying out a method in a special embodiment of the invention.
  • the double clutch device 12 is arranged in a drive train of a vehicle, in particular a motor vehicle, and has a hydraulically operated first clutch K1 and a hydraulically operated second clutch K2 for alternating torque transmission between a drive element, for example an internal combustion engine and / or an electric motor and a transmission .
  • a drive element for example an internal combustion engine and / or an electric motor and a transmission .
  • the double clutch device 12 comprises a hydraulically operated clutch cooling device C for cooling at least one of the two clutches K1, K2. Both the first clutch K1, the second clutch K2 and the clutch cooling device C are hydraulically connected to the hydraulic device 10.
  • the hydraulic device 10 includes a first pump and a second pump, both of which are driven by an electric motor E.
  • a system pressure valve SV is also arranged, followed by a first clutch valve KV1 assigned to the first clutch K1 and a second clutch valve KV2 assigned to the second clutch K2 and arranged parallel to the first clutch valve KV1.
  • the first clutch valve KV1 is provided for controlling the fluid pressure for clutch actuation of the first clutch K1 and the second clutch valve KV2 is provided for controlling the fluid pressure for clutch actuation of the second clutch K2.
  • the first pump PH provides at least the fluid pressure required for actuating the clutch.
  • the second pump PL can be used for Provide clutch cooling via the clutch cooling device C required fluid pressure.
  • the first clutch valve KV1 and the second clutch valve KV2 are each preceded by a spring pressure accumulator SC as a hydraulic capacity.
  • a check valve RV is arranged upstream of the respective spring pressure accumulator SC.
  • the first pump PH can increase the fluid pressure in the respective fluid branch 14 (single rail) assigned to the clutch and thereby charge the spring pressure accumulator SC, a fluid pressure drop in the direction of the first pump PH being prevented by the respective check valve RV.
  • the first pump 1 can be relieved or even switched off when there is sufficient fluid pressure in the respective fluid branch 14.
  • FIG. 2 shows a block diagram of a further fly hydraulic device 10 for a double clutch device 12 for carrying out a method in a special embodiment of the invention.
  • the structure is the same as the structure shown in FIG. 1 except for the differences indicated below.
  • the first pump PH is driven by an electric motor E and the second pump PL is driven by a further electric motor E.
  • the speed and the delivery volume of the second pump PL can be adapted independently of the speed of the electric motor E driving the first pump PH.
  • FIG. 3 shows a block diagram of a further hydraulic device 10 for a double clutch device 12 for carrying out a method in a special embodiment of the invention.
  • the structure is the same as the structure shown in FIG. 2 except for the differences indicated below.
  • the first fluid supply path L1 which supplies the first and second clutches K1, K2 with fluid pressure for clutch actuation, is separate from the second fluid supply path L2, which feeds the clutch cooling device C with fluid pressure.
  • a spring-loaded check valve RVS is assigned to the first fluid supply path L1.
  • FIG. 4 shows a block diagram of a method 20 for controlling the hydraulic device from FIG. 1.
  • the double clutch device is controlled in such a way that a distinction is always made between active and inactive clutch. In particular, it is avoided that both clutches K1, K2 are active at the same time.
  • a clutch is preferably active when it is actuated hydraulically to actuate the clutch in order to transmit torque or to initiate torque transmission.
  • the moving clutch that is, the torque-transmitting clutch, is the active clutch.
  • the other clutch i.e. the upcoming clutch that continues to take over the torque transmission, is the active clutch, especially when starting from an open state to the clutch contact point.
  • the coming clutch is also the active clutch, with the exception of a torque increase of the outgoing clutch, i.e. the clutch to be released with regard to torque transmission, before the two clutches overlap.
  • the first activation state A1 corresponds to a filling state in which the system pressure valve and the clutch valve assigned to the active clutch are activated via a, in particular temperature-dependent, predetermined actuation current.
  • the system actuation current l_pcv_Sys is equal to the specified system filling actuation current l_sys_bef and the actuation current l_pcv_act assigned to the active clutch is equal to the specified clutch filling actuation current l_pcv_bef.
  • the pump speed n corresponds to a supply speed n_np that enables a sufficient volume flow.
  • the second activation state A2 corresponds to a slip state in which the clutch valve assigned to the active clutch is controlled according to the target fluid pressure p_tgt_act of the active clutch.
  • the system pressure valve is actuated via a system actuation current I_pcv_Sys which is dependent on a pressure difference Dr compared to the fluid setpoint pressure p_tgt_act in the fluid system pressure associated with the active clutch, which is higher than the fluid system pressure.
  • the third activation state A3 corresponds to a first closed state in which the clutch valve assigned to the activated clutch is actuated by a maximum actuation current I_max.
  • the system pressure valve is actuated via a system actuation current I_pcv_Sys which is dependent on a pressure difference Dr compared to the fluid setpoint pressure p_tgt_act in the fluid system pressure associated with the active clutch, which is higher than the fluid system pressure.
  • the pressure ratio from the existing fluid pressure p_act in the fluid branch assigned to the active clutch to the fluid target pressure p_tgt_act plus a respective pressure hysteresis parameter p_hys_L or p_hys_FI influences the selection between the third control state A3 and the fourth control state A4.
  • the pressure hysteresis parameters p_hys_L or p_hys_FI can be variable depending on the operating state, for example depending on the temperature and the pressure.
  • the actuation current l_pcv_inact of the clutch valve assigned to the inactive clutch is set as a function of a predefined target fluid pressure p_tgt_inact, regardless of the fluid pressure in the fluid branch assigned to the active clutch and the system fluid pressure.
  • the pump speed n corresponds to a supply speed n_np which enables a sufficient volume flow and which is set to be constant, but can also depend on different operating states such as temperature or pressure.
  • FIG. 5 shows a block diagram of a method 20 for controlling the fly hydraulic device from FIG. 2. Since the first pump and the second pump are each operated by their own electric motor, the first pump speed n_H of the first pump and the second pump speed n_L of the second pump can also be separated can be adjusted from each other.
  • the first and second speed are each set to the cooling speed n_cool required for clutch cooling. This also applies to the fourth control state A4. In the other activation states, however, the first pump speed n_H of the first pump is set in order to provide a sufficient volume flow during the second pump speed n_L of the second pump corresponds to the cooling speed n_cool.
  • FIG. 7 shows a block diagram of a method 20 in a further special embodiment of the invention for controlling the hydraulic device from FIG. 1.
  • this includes a transfer method N1 which, when the active state changes between the two clutches K1, K2 is applied.
  • the clutch that becomes inactive or the spring pressure accumulator assigned to this clutch is briefly recharged via a maximum actuation current l_max before this fluid branch is decoupled from the system pressure.
  • the other clutch is activated and the control states specified in module M1 in FIG. 4 are switched.
  • FIG. 8 indicates a further possibility of a transfer process N2. Only the spring pressure accumulator is charged over the period dt, which shortens the reloading process.

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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 procédé (20) permettant de commander un dispositif hydraulique (10) pour un dispositif d'embrayage double (12) qui a au moins un premier embrayage pouvant être actionné par voie hydraulique (K1) et un second embrayage pouvant être actionné par voie hydraulique (K2) chacun pour le transfert de couple et un dispositif de refroidissement d'embrayage actionné par voie hydraulique (C) destiné à refroidir au moins l'un des deux embrayages (K1, K2), et le dispositif hydraulique (10) comprend une pompe (PH, PL), une soupape de pression de système (SV) et une première soupape d'embrayage (KV1) permettant de réguler la pression de fluide destinée à l'actionnement d'embrayage du premier embrayage (K1) et une seconde soupape d'embrayage (KV2) permettant de réguler la pression de fluide destinée à l'actionnement d'embrayage du second embrayage (K2) et la pompe (PH, PL) fournit au moins la pression de fluide requise pour l'actionnement d'embrayage et par rapport à l'actionnement d'embrayage, un seul des deux embrayages (K1, K2) est commandé en tant qu'embrayage actif sur une base dépendante du fonctionnement au moyen de l'un des états de régulation hydraulique suivants : un état de remplissage (A1) ; un état de glissement (A2) ; un premier état fermé (A3).
PCT/DE2020/100839 2019-10-08 2020-10-01 Dispositif d'embrayage double, dispositif hydraulique et procédé permettant de commander un dispositif hydraulique WO2021069021A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202080063181.6A CN114375372A (zh) 2019-10-08 2020-10-01 双离合器设备、液压设备和用于操控液压设备的方法

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102019126986.5 2019-10-08
DE102019126986 2019-10-08
DE102019130158 2019-11-08
DE102019130158.0 2019-11-08

Publications (1)

Publication Number Publication Date
WO2021069021A1 true WO2021069021A1 (fr) 2021-04-15

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Application Number Title Priority Date Filing Date
PCT/DE2020/100839 WO2021069021A1 (fr) 2019-10-08 2020-10-01 Dispositif d'embrayage double, dispositif hydraulique et procédé permettant de commander un dispositif hydraulique

Country Status (3)

Country Link
CN (1) CN114375372A (fr)
DE (1) DE102020125635A1 (fr)
WO (1) WO2021069021A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021124216B3 (de) 2021-09-20 2022-12-01 Schaeffler Technologies AG & Co. KG Hydraulikvorrichtung und Verfahren zum Betrieb einer Hydraulikvorrichtung
DE102022123079B4 (de) 2022-09-12 2024-09-12 Schaeffler Technologies AG & Co. KG Verfahren zur Ansteuerung einer Kupplungsbetätigungsaktuatorik

Citations (4)

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JPS60183232A (ja) * 1984-02-29 1985-09-18 Kawasaki Heavy Ind Ltd パワ−シフト式トランスミツシヨンの液圧クラツチ接続制御装置
EP1253341A2 (fr) * 2001-04-23 2002-10-30 ZF Sachs AG Système d'embrayage avec une installation d'embrayages multiples à actionnement hydraulique
WO2017186710A1 (fr) * 2016-04-26 2017-11-02 Avl Commercial Driveline & Tractor Engineering Gmbh Circuit hydraulique, dispositif de transmission de couple muni d'un circuit hydraulique, procédé permettant de faire fonctionner un circuit hydraulique
WO2020216396A1 (fr) * 2019-04-25 2020-10-29 Schaeffler Technologies AG & Co. KG Procédé de commande d'un système hydraulique pourvu d'une pompe et de plusieurs vannes, et système hydraulique

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JPH0729569B2 (ja) * 1983-06-29 1995-04-05 いすゞ自動車株式会社 自動クラッチ制御装置
DE10143833B4 (de) * 2001-09-07 2013-06-06 Zf Friedrichshafen Ag Kupplungssystem in einem Antriebsstrang zwischen einer Antriebseinheit und einem Getriebe
US20090032360A1 (en) * 2007-08-02 2009-02-05 Tetsushi Asano Hydraulic Vehicle Clutch System and Method
DE102011100837B4 (de) * 2011-05-06 2017-10-12 Audi Ag Kupplungsgetriebe, Verfahren zum Betreiben eines Kupplungsgetriebes
DE102011100836A1 (de) * 2011-05-06 2012-11-08 Audi Ag Hydraulikkreis, Verfahren zum Betreiben
DE102011100838B4 (de) * 2011-05-06 2018-05-09 Audi Ag Doppelkupplungsgetriebe, mit wenigstens einer Pumpe, einem der Pumpe nachgeschalteten Volumensteuerventil, einem der Pumpe nachgeschalteten Kühler und einem dem Kühler nachgeschalteten Schaltventil
DE112014005597A5 (de) * 2013-12-09 2016-11-03 Schaeffler Technologies AG & Co. KG Hydraulikanordnung für Doppelkupplung sowie Verfahren zumAnsteuern oder Kühlen der Doppelkupplung
DE102014211675A1 (de) * 2014-06-18 2015-12-24 Robert Bosch Gmbh Kupplungssystem und Verfahren zur Durchführung eines Kupplungstrennvorgangs

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60183232A (ja) * 1984-02-29 1985-09-18 Kawasaki Heavy Ind Ltd パワ−シフト式トランスミツシヨンの液圧クラツチ接続制御装置
EP1253341A2 (fr) * 2001-04-23 2002-10-30 ZF Sachs AG Système d'embrayage avec une installation d'embrayages multiples à actionnement hydraulique
WO2017186710A1 (fr) * 2016-04-26 2017-11-02 Avl Commercial Driveline & Tractor Engineering Gmbh Circuit hydraulique, dispositif de transmission de couple muni d'un circuit hydraulique, procédé permettant de faire fonctionner un circuit hydraulique
WO2020216396A1 (fr) * 2019-04-25 2020-10-29 Schaeffler Technologies AG & Co. KG Procédé de commande d'un système hydraulique pourvu d'une pompe et de plusieurs vannes, et système hydraulique

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CN114375372A (zh) 2022-04-19

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