WO2012000472A1 - Hydrostataktor und verfahren zur steuerung eines hydrostataktors - Google Patents
Hydrostataktor und verfahren zur steuerung eines hydrostataktors Download PDFInfo
- Publication number
- WO2012000472A1 WO2012000472A1 PCT/DE2011/001260 DE2011001260W WO2012000472A1 WO 2012000472 A1 WO2012000472 A1 WO 2012000472A1 DE 2011001260 W DE2011001260 W DE 2011001260W WO 2012000472 A1 WO2012000472 A1 WO 2012000472A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- master cylinder
- pressure
- pressure medium
- temperature
- slave cylinder
- Prior art date
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
- F16D48/06—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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/102—Actuator
- F16D2500/1021—Electrical type
- F16D2500/1023—Electric motor
- F16D2500/1024—Electric motor combined with hydraulic 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
-
- 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
- F16D2500/10443—Clutch type
- F16D2500/1045—Friction clutch
-
- 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
- F16D2500/30—Signal inputs
- F16D2500/304—Signal inputs from the clutch
- F16D2500/30404—Clutch temperature
- F16D2500/30405—Estimated clutch temperature
-
- 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
- F16D2500/305—Signal inputs from the clutch cooling
- F16D2500/3055—Cooling oil properties
- F16D2500/3056—Cooling oil temperature
-
- 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
- F16D2500/308—Signal inputs from the transmission
- F16D2500/30802—Transmission oil properties
- F16D2500/30803—Oil temperature
-
- 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
- F16D2500/50—Problem to be solved by the control system
- F16D2500/501—Relating the actuator
- F16D2500/5014—Filling the actuator cylinder with fluid
-
- 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
- F16D2500/50—Problem to be solved by the control system
- F16D2500/501—Relating the actuator
- F16D2500/5016—Shifting operation, i.e. volume compensation of the master cylinder due to wear, temperature changes or leaks in the 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
- F16D2500/50236—Adaptations of the clutch characteristics, e.g. curve clutch capacity torque - clutch actuator displacement
-
- 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
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
- F16D2500/50245—Calibration or recalibration of the clutch touch-point
- F16D2500/50266—Way of detection
- F16D2500/50275—Estimation of the displacement of the clutch touch-point due to the modification of relevant parameters, e.g. temperature, wear
-
- 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
- F16D2500/70406—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
-
- 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
- F16D2500/706—Strategy of control
- F16D2500/70605—Adaptive correction; Modifying control system parameters, e.g. gains, constants, look-up tables
-
- 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
- F16D2500/706—Strategy of control
- F16D2500/70668—Signal filtering
Definitions
- the invention relates to a Hydrostataktor and a method for controlling a Hydrostataktors with one of an electric drive and a hydrostatic path with a predetermined temperature at a predetermined pressure center Ivolumen containing a master cylinder with an axially displaced by the drive master cylinder piston and one with the master cylinder by means of a Slave cylinder associated with a pressure line as a result of a via the pressure line from the master cylinder to the slave cylinder pressure of a pressure medium along an actuating travel displaceable Nehmerzylinderkolben and at least one temperature detection device.
- German patent application no. 10 2009 051 245.4 discloses a hydrostatic actuator in which an electric drive axially displaces the master cylinder piston of the master cylinder, whereby a slave cylinder adjoining via a pressure line is actuated and an aggregate, for example a friction clutch in a drive train of a Motor vehicle actuated.
- the pressure medium guided in the hydrostatic section between master cylinder and slave cylinder is exposed to the operating temperatures of the motor vehicle and expands its pressure medium volume with increasing temperature.
- the pressure medium may heat up due to internal friction during a displacement within the hydrostatic path, in particular at bottlenecks. This leads to a pressure build-up in the hydrostatic path and thus to an unwanted axial displacement of the slave cylinder piston.
- reacting aggregates such as a depressed friction clutch can cause disturbances in operation, such as a change in the touch point and / or the torque to be transmitted via the friction clutch.
- sniffer bores are provided on such hydraulic sections, which establish a connection between the pressure medium volume of the hydrostatic section and a pressureless expansion tank such as a reservoir when the master cylinder piston is at rest.
- a pressureless expansion tank such as a reservoir when the master cylinder piston is at rest.
- the object of the invention is therefore to propose a Hydrostataktor and a method for its operation, which can be operated during operation without sacrificing the ride comfort with extended snoop cycles.
- the object is by a method for controlling a Hydrostataktors with one of an electric drive and a hydrostatic path with a predetermined temperature at a pressure medium volume containing a master cylinder with an axially displaced by the drive master cylinder piston and connected to the master cylinder by means of a pressure line slave cylinder a slave cylinder piston displaceable along an actuation path as well as at least one temperature detection device, wherein a temperature-dependent change of the pressure medium volume determined and caused by the change path difference of Nehmerzyiinderkolbens by acting on the master cylinder piston through the Drive is compensated.
- the hydrostatic actuator actuates, for example, axially actuated units in a motor vehicle, for example brakes or preferably friction clutches, which are provided for example as compressed friction clutches between a crankshaft of an internal combustion engine and in each case one transmission input shaft of a partial drive train of a dual clutch transmission in a drive train of a motor vehicle.
- brakes or preferably friction clutches which are provided for example as compressed friction clutches between a crankshaft of an internal combustion engine and in each case one transmission input shaft of a partial drive train of a dual clutch transmission in a drive train of a motor vehicle.
- the path difference is to be obtained from a change of temperature values of the pressure medium, of these leading mechanical components and the environment of these calculating and predictive model and compensated by means of a control of the drive.
- no additional sensor devices such as temperature detection devices should be provided.
- a model should be based on the existing sensor devices. Therefore, at least one temperature and one actual speed of the master cylinder piston are used as input variables for the calculation of the model.
- additional signals for example, a pressure sensor of the master cylinder, a position sensor of the master cylinder and / or slave cylinder sensor and / or the like may be considered in the model.
- the Hydrostataktor consists of the electric drive with the master cylinder, the pressure line and the slave cylinder, for example, a concentrically arranged around a transmission input shaft slave cylinder of a friction clutch.
- the hydraulic path in the form of the pressure chamber of the master cylinder, the pressure chamber of the slave cylinder and the pressure chamber connecting this contains the pressure medium volume.
- the three components of the hydraulic system are located in areas with different ambient temperatures. Since the heat conduction via the pressure medium but also via the mechanical components of the hydrostatic path is relatively small due to small Wärmleitkocontinenten, a temperature gradient forms along the pressure medium line and the pressure medium therein.
- the model determines at least the temperatures in the above-mentioned three sections master cylinder (GZ), pressure line (DL) and slave cylinder (NZ) and the pressure medium contained in these three sections and the surrounding surrounding areas separated from each other , calculated or recorded.
- GZ master cylinder
- DL pressure line
- NZ slave cylinder
- a heat exchange takes place both between the environment and the mechanical components of the three sections and between the mechanical components and the pressure medium.
- a heat flow occurs within the sections. In the example described, therefore, nine temperatures and eight heat flows occur, which are advantageously taken into account in the model.
- heat flows through the friction clutch, the electric drive, an additional heating and inner viscous friction of the pressure medium can be considered.
- the input variables can be used to determine the temperature of the drive cz , the
- Temperature of the pressure line ⁇ and the temperature of the slave cylinder NZ are determined. Furthermore, the temperatures can of the pressure medium in these
- the heat flows, DL ⁇ NZ contain an additional contribution due to the moving mass flow due to the transported in the pressure line during actuation pressure medium.
- the moving pressure medium thus transports heat from one section to the next.
- the heat outputs produced for example by the electrical components such as power transistors of the drive can be used as electrical
- a Hydrostataktor particular for actuating a friction clutch, in particular a pressed friction clutch in a drive train of a motor vehicle with one of an electric drive and a hydrostatic path with a predetermined temperature at a predetermined pressure medium volume containing a master cylinder with one of the drive axially displaced Geberzy- linderkolben and one connected to the master cylinder by means of a pressure line slave cylinder with a displaceable as a result of a via the pressure line from the master cylinder to the slave cylinder pressure of a pressure medium along an actuating travel displaceable slave cylinder piston, at least one temperature sensing device and an electronic control unit for controlling the electric drive to carry out of the procedure described in the documents.
- the model described in the method can be implemented as a software routine in the electronic control unit of the hydrostatic actuator.
- FIG. 1 shows a block diagram of a model for compensating temperature-dependent pressure fluctuations of the pressure medium in a hydrostatic section of a hydrostatic actuator
- Figure 2 is a schematic representation of a hydrostatic section of a Hydrostataktors
- FIG. 3 shows a schematically represented volume element of the hydrostatic section of FIG. 2.
- the pressure medium volume V which is constant at least in the steady state of the pressure p and at constant temperature T is usually constant, and the temperature T as Input variables.
- the currently available data of the pressure p in the pressure medium of the detected or determined temperature T or other temperatures available from sensor devices and / or further model calculations and the pressure medium volume V are compensated in the node 1 with the output values y (k
- Flow rate u of the pressure medium cyclically in the loop 5 calculates and predicts temperature values T (k
- the node 7 is turned on, which corrects the previously determined temperature values T ⁇ k
- the temperature and the flow rate dependent heat fluxes l (T, u ) and the powers P (T, u ) are determined based on the input variables of the temperature T (k
- k) are, in addition to the predicted temperature T (k + 1
- GZ ⁇ DL is the distance between the two center points of mass, ⁇ the thermal conductivity and GZ the mean line cross-sectional area of the pressure line.
- CZ ⁇ DL is the distance of the two center points of mass
- A is the thermal conductivity
- ⁇ DL is the mean cross-sectional area of the pipe.
- U M, UQZ are the current average velocities of the liquid in the area of the actuator and in the area of the line. Thieves- Considering the mass flow, which arises due to the thermal expansion is not considered in this simple approach.
- x are the contact surface between liquid and mechanical components
- the heat flows between the mechanical components and the environment depend on the specific design, such as design of Hydrostataktors and its arrangement in the motor vehicle and can be both through the heat conduction via contact surfaces, such as attachment of the Hydrostataktors on the transmission through the contact surfaces formed thereby and / or Convection.
- the heat flows are due to the relationships considered.
- the heat input in block 3 describes the heat produced by the electronics in the actuator.
- Block 3 takes into account, where " x the average velocity of the liquid in the respective Ab-
- x represents the line radius and x represents the volume of the line section.
- volume expansion results with the likewise temperature-dependent volume expansion coefficient a from the individual dimensions in the various sections:
- the current volume is given by V ⁇ + 1 ' ⁇ ⁇ I ⁇ + ⁇ V . Since the line cross-sections are known, the expected longitudinal displacement can be determined, and the pressure change can be determined with the pressure characteristic being stored.
- the pressure gradient between the reservoir and the hydrostatic section on the master cylinder is also included in the estimation of the duration of a pressure equalization.
- FIG. 2 shows a schematic representation of a subdivided and generalized to different volume sections hydrostatic section 8, which are exposed in different environments, such as engine compartment, clutch bell and the like to different temperatures and can assume different cross-sections and pipe shapes.
- the volume sections n-1, n, n + 1, ... apart from a first volume element 1 and a last volume element N of the hydraulic path 8 are provided with a constant length ⁇ n .
- heat transport through mass transport since by the movement of the piston of the master and slave cylinder 9, 10, the pressure medium is moved back and forth. The displacement of the pressure medium takes place in each case by the volume contribution 11 of each volume element.
- volume change 2 occurs due to the change in temperature, a volume change 2, which also brings a mass transport with it and changes the total length of the hydrostatic section 8 due to the increase in volume.
- the temperature profile between the centers of mass 13 of the volume elements is assumed to be linear, as can be seen in the lower part of Figure 2 graph.
- FIG. 3 schematically shows the nth volume element of FIG. 2.
- I is the heat flow of the volume element with respect to the adjacent volume elements
- Ibb is that in the hydrostatic path 8 (FIG. 2).
- Each of the volume elements has the length
- the source term is made up of an addendum due to the heat production due to the
- volume element 1 the heat flow 1 is the one from the master cylinder piston
- the mechanical components forming the hydrostatic section have a heat transfer equation without volume exchange:
- T n A n "T n + A m T n + A n R + 1 T n + 1 + a" T? + P n
- ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ ( ⁇ _ ⁇ ) ⁇ ⁇ + A NN T N + a N T N +1 + P N
- the integration of the differential equation system in the model can be done discretely, for example by means of an Eulerian method:
Landscapes
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180032381.6A CN102985717B (zh) | 2010-06-28 | 2011-06-09 | 静液压促动器和用于控制静液压促动器的方法 |
DE112011102157T DE112011102157A5 (de) | 2010-06-28 | 2011-06-09 | Hydrostataktor und Verfahren zur Steuerung eines Hydrostataktors |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010025333.2 | 2010-06-28 | ||
DE102010025333 | 2010-06-28 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012000472A1 true WO2012000472A1 (de) | 2012-01-05 |
Family
ID=44653921
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2011/001260 WO2012000472A1 (de) | 2010-06-28 | 2011-06-09 | Hydrostataktor und verfahren zur steuerung eines hydrostataktors |
Country Status (3)
Country | Link |
---|---|
CN (1) | CN102985717B (de) |
DE (2) | DE112011102157A5 (de) |
WO (1) | WO2012000472A1 (de) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT513478B1 (de) * | 2012-10-02 | 2015-06-15 | Avl List Gmbh | Verfahren zum Betreiben eines Antriebsstranges |
AT513477B1 (de) * | 2012-10-02 | 2015-06-15 | Avl List Gmbh | Verfahren zum Betreiben eines Antriebsstranges |
DE102013220324A1 (de) | 2012-10-31 | 2014-04-30 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Betätigung einer Reibungskupplung |
WO2014071944A2 (de) * | 2012-11-07 | 2014-05-15 | Schaeffler Technologies AG & Co. KG | Verfahren zum betrieb einer hydrostatische aktoranordnung |
DE102013221046A1 (de) * | 2012-11-28 | 2014-05-28 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Steuerung einer Reibungskupplung |
DE102014201212A1 (de) * | 2014-01-23 | 2015-07-23 | Robert Bosch Gmbh | Verfahren zur Positionierung eines Kupplungsaktuators eines Kraftfahrzeugs |
DE102015213297A1 (de) * | 2015-07-15 | 2017-01-19 | Schaeffler Technologies AG & Co. KG | Verfahren zur Steuerung eines Kupplungsaktors, vorzugsweise zur Ansteuerung einer unbetätigt geschlossenen Kupplung |
CN108138871B (zh) * | 2015-10-08 | 2020-07-07 | 舍弗勒技术股份两合公司 | 用于控制摩擦离合器的方法 |
DE102016205890A1 (de) * | 2016-04-08 | 2017-10-12 | Schaeffler Technologies AG & Co. KG | Verfahren zur Ermittlung einer Systemtemperatur einer hydrostatischen Strecke eines hydraulischen Kupplungssystems |
DE102016125090A1 (de) | 2016-11-07 | 2018-05-09 | Schaeffler Technologies AG & Co. KG | Verfahren zur Bestimmung einer Ansteuerstrategie einer automatisierten Kupplung, insbesondere eines Fahrzeuges |
DE102016223037B4 (de) | 2016-11-22 | 2023-03-23 | Schaeffler Technologies AG & Co. KG | Verfahren zur Betätigung einer Kupplung, insbesondere einer Hybridtrennkupplung eines Hybridfahrzeuges |
DE102017103815A1 (de) | 2017-02-24 | 2018-08-30 | Schaeffler Technologies AG & Co. KG | Verfahren zur Bestimmung einer Temperatur einer Hydraulikflüssigkeit in einem hydraulischen Kupplungsbetätigungssystem |
DE102017113064A1 (de) * | 2017-06-14 | 2018-12-20 | Schaeffler Technologies AG & Co. KG | Verfahren zur Temperaturkompensation eines Vorlastpunktes einer Kupplung eines Fahrzeuges |
DE102017113348A1 (de) | 2017-06-19 | 2018-12-20 | Schaeffler Technologies AG & Co. KG | Verfahren zur Betätigung einer Hybridtrennkupplung eines Hybridfahrzeuges |
DE102018209855A1 (de) * | 2018-06-19 | 2020-01-16 | Zf Friedrichshafen Ag | Thermisches Kupplungsmodell |
CN113294455B (zh) * | 2021-04-27 | 2023-01-03 | 浙江吉利控股集团有限公司 | 用于离合器的电液执行机构及其控制方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009022450A1 (en) * | 2007-08-10 | 2009-02-19 | Toyota Jidosha Kabushiki Kaisha | Automatic clutch control apparatus |
GB2458502A (en) * | 2008-03-20 | 2009-09-23 | Ford Global Tech Llc | A Method and Apparatus for Determining the Engagement State of a Clutch |
WO2010020523A1 (de) * | 2008-08-19 | 2010-02-25 | Robert Bosch Gmbh | Verfahren zur kompensation von volumenänderungen eines hydraulikfluids in einer hydraulischen betätigungseinrichtung zur betätigung einer kupplung, sowie hydraulische betätigungseinrichtung |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4131253B2 (ja) * | 2004-06-10 | 2008-08-13 | 日産自動車株式会社 | 車両の発進摩擦要素制御装置 |
JP4492585B2 (ja) * | 2006-05-29 | 2010-06-30 | 日産自動車株式会社 | ハイブリッド車両の制御装置及びハイブリッド車両の制御方法。 |
DE112010004215A5 (de) | 2009-10-29 | 2012-08-23 | Schaeffler Technologies AG & Co. KG | Hydrostataktor |
-
2011
- 2011-06-09 DE DE112011102157T patent/DE112011102157A5/de not_active Withdrawn
- 2011-06-09 DE DE102011103750A patent/DE102011103750A1/de not_active Withdrawn
- 2011-06-09 CN CN201180032381.6A patent/CN102985717B/zh not_active Expired - Fee Related
- 2011-06-09 WO PCT/DE2011/001260 patent/WO2012000472A1/de active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2009022450A1 (en) * | 2007-08-10 | 2009-02-19 | Toyota Jidosha Kabushiki Kaisha | Automatic clutch control apparatus |
GB2458502A (en) * | 2008-03-20 | 2009-09-23 | Ford Global Tech Llc | A Method and Apparatus for Determining the Engagement State of a Clutch |
WO2010020523A1 (de) * | 2008-08-19 | 2010-02-25 | Robert Bosch Gmbh | Verfahren zur kompensation von volumenänderungen eines hydraulikfluids in einer hydraulischen betätigungseinrichtung zur betätigung einer kupplung, sowie hydraulische betätigungseinrichtung |
Also Published As
Publication number | Publication date |
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DE112011102157A5 (de) | 2013-05-02 |
CN102985717B (zh) | 2016-05-04 |
DE102011103750A1 (de) | 2011-12-29 |
CN102985717A (zh) | 2013-03-20 |
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