WO2018196913A1 - Verfahren zur adaption einer momentenkennlinie einer reibungskupplung - Google Patents
Verfahren zur adaption einer momentenkennlinie einer reibungskupplung Download PDFInfo
- Publication number
- WO2018196913A1 WO2018196913A1 PCT/DE2018/100279 DE2018100279W WO2018196913A1 WO 2018196913 A1 WO2018196913 A1 WO 2018196913A1 DE 2018100279 W DE2018100279 W DE 2018100279W WO 2018196913 A1 WO2018196913 A1 WO 2018196913A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- torque
- friction clutch
- offset
- input shaft
- clutch
- 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
- F16D35/00—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion
- F16D35/005—Fluid clutches in which the clutching is predominantly obtained by fluid adhesion with multiple lamellae
-
- 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
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3026—Stroke
-
- 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
- F16D2500/3041—Signal inputs from the clutch from the input shaft
- F16D2500/30415—Speed of the input shaft
-
- 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
- F16D2500/51—Relating safety
- F16D2500/5102—Detecting abnormal operation, e.g. unwanted slip or excessive 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
- F16D2500/51—Relating safety
- F16D2500/5104—Preventing 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
- 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
- F16D2500/702—Look-up tables
- F16D2500/70252—Clutch torque
-
- 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
- F16D2500/702—Look-up tables
- F16D2500/70252—Clutch torque
- F16D2500/70264—Stroke
-
- 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
- F16D2500/708—Mathematical model
Definitions
- the invention relates to a method for adapting a torque characteristic of a wet-running friction clutch, which in an automated hydraulic clutch actuation system is driven by a hydrostatic actuator.
- a method for the adaptation of parameters of a clutch which has a hydrostatic clutch actuator with a pressure sensor in a motor vehicle.
- the pressure system is used to form an abscissa offset the pressure-displacement curve, the so-called touch point, which also applies to the torque-displacement curve.
- the friction system is adjusted by a factor, the so-called coefficient of friction to the current situation.
- there is also a drag torque map which is additively added to the respective characteristic curve. The map depends on the path of the clutch actuator, the temperature of the friction clutch, the flow of cooling oil and the slip of the clutch.
- the touch point is calculated from the pressure signal and adapted.
- the clutch control comprises a hydrostatic path and is controlled by means of adaptive algorithms. In particular with wet-running friction clutches, an effect of floating occurs. In this error range, neither the touch point nor the coefficient of friction, which are parameters of the friction clutch, can be learned in the case of deviations of the torque below 50-80 Nm in the wet friction system.
- This deviation is represented by the curve B1 in FIG. 6 and limited to moments below 150 Nm.
- the touch point can not be adjusted because the printing system produces a poor signal-to-noise ratio, because in the error range the pressure is too low, even though the printing system is fully functional. Also, when feeding back the deviation from the torque system you would have two conflicting inputs, which rather leads to the persistence of the touch point.
- the coefficient of friction should in principle not be adjusted at low torques, since an error of a few Nm would result in an unrealistically large change in the coefficient of friction (see FIG. 7).
- the drag torque map that is decisive for a wet-running friction clutch could be learned, the drag torque map hitherto applies independently of the input shaft in other situations, such as when synchronizing the pre-selection gear of the clutch, and would therefore be faulty there. lead learners. Therefore, the learning of the current drag torque map in the considered error case should be avoided in order to initiate any errors in other operating points.
- the invention has for its object to provide a method for the adaptation of a parameter of a friction clutch, in which the error in the Aufschwimm Scheme the wet clutch is reliably prevented.
- the object is achieved by adapting a torque characteristic of the wet-running friction clutch to a volatile torque offset in an error range characterized by a torque collapse of the friction clutch.
- This has the advantage that it is possible to dispense with a determination of the touch point or friction value and that a reliable adaptation of the errors takes place only through the adaptation of the torque characteristic in the predetermined error range. It is assumed that the remaining parallel adaptations of the scanning point, pressure, coefficient of friction and / or shapes are frozen during this torque adaptation. In the proposed method, an error is learned in the most probable cause, here the torque break-in, whereby the error can be corrected.
- the torque offset when leaving the error range by the friction clutch, gradually, preferably reset to zero. This ensures that no after-effects of the error correction are present in the normal driving range of the friction clutch.
- the torque offset is reset in a ramp. This has the advantage that there is a gradual transition of the friction clutch from the fault case to the normal mode of operation, which ensures that a vehicle occupant does not perceive these different adaptation processes.
- the error range of the friction clutch is described by an input shaft speed that is less than a predetermined speed threshold value and / or a pressure in the hydraulic clutch actuation system that is less than a predefined pressure threshold value.
- the threshold values are selected for the offset adaptation so that each offset can be learned quickly so that there is hardly any delay in the special driving states affected by the torque collapse. These driving conditions include a vehicle crawling, starting and rolling out with a return trip.
- the input shaft speed of the friction clutch is determined and a 0 rpm input shaft offset map is determined, which is superimposed to a speed threshold input shaft offset map by interpolation.
- the 0 rpm input shaft map is generated from a measured extreme map and the speed threshold input wave offset map by weighted linear combination.
- the linear combination represents a particularly simple mathematical method, which can be realized very quickly. In the event of an error, the torque offset can thus be calculated very quickly and nevertheless accurately.
- the linear combination is based on a weighting factor, which depends on a statistically determined torque offset in the error range. When the offset determination is started, a new friction clutch is assumed, in which the weighting factor assumes zero as the initial value. The weighting factor can vary between 0 and 1 during operation of the friction clutch.
- the weighting factor is proportional to a statistically averaged negative torque offset, which is determined at input shaft speeds below the speed threshold.
- FIG. 1 shows a schematic structure of a hydrostatic clutch actuation system
- FIG. 2 shows a first exemplary embodiment of the method according to the invention
- FIG. 3 shows an example of a torque-displacement characteristic according to the first exemplary embodiment of the method according to the invention
- 4 shows a second embodiment of the method according to the invention
- Fig. 7 is a Reibwertadaption according to the prior art.
- a hydrostatic clutch actuation system 1 is shown schematically with a hydrostatic clutch actuator 3, as this comes in vehicles used.
- the hydrostatic clutch actuation system 1 comprises a control unit 2 which actuates the hydrostatic clutch actuator 3.
- a piston 4 of a master cylinder 5 is moved to the right along an actuator path L_act, whereby the volume in the master cylinder 5 is displaced and a pressure p in the master cylinder 5 is established.
- This pressure p is transmitted via a hydraulic fluid 6, which serves as a pressure medium, via a hydraulic line 7 to a slave cylinder 8, which actuates the friction clutch 9 directly.
- the friction clutch 9 is designed as a wet-running clutch.
- a wet-running friction clutch contains, for example, a disk pack that comes into contact with a fluid, for example oil, with a disk stacked on the input side and on the output side in each case received by a disk carrier, alternately layered disks.
- the opening and closing of the wet-running friction clutch takes place by axial clamping of the disk set.
- the proposed method is used in particular when the effect of floating, in which the oil can not be displaced between the individual fins, resulting in a momentum break.
- the pressure p is determined in the master cylinder 5 by means of a pressure measuring device 10, which is connected to the control unit 2.
- the distance traveled by the clutch actuator 3 L_act path is determined by a displacement sensor 1 1.
- the distance traveled by the clutch actuator 3 L_act path is equated below with the path of the friction clutch 9.
- a general observer 12 is stored in the control unit 2, which is connected in parallel to the actually existing clutch actuation system 1 (FIG. 2).
- the observer 12 comprises a control engineering model 13 which simulates the real clutch actuation system 1. det.
- the real clutch actuation system 1 as well as the model 13 are supplied with the same input variables, such as, for example, the path L_act which the clutch actuator 3 travels when the friction clutch 9 is actuated.
- the real clutch actuation system 1 supplies a transmitted clutch torque T_CL_tr of the driving engine, which is also referred to as drive train torque, and is fed to a summation point 14, at which a torque value T_CL_M calculated by the model 13 is supplied, from which a torque difference ⁇ is determined represents an input variable of a model correction unit 15.
- a query is made in block 100 as to whether the friction clutch 9 can be observed. This is always the case when the friction clutch 9 is in any operating state except the closed or open state and no other clutch is active. If the friction clutch 9 is not observable, the torque offset is ramped to 0 in a ramp (block 101).
- the system proceeds to block 102, where it is queried whether the input shaft speed Ni ps is less than 1000 rpm and / or whether the pressure p in the real clutch actuation system 1 is less than, for example, 20 bar.
- the input shaft speed Nips of 1000 rpm represents a speed threshold, while the pressure of 20 bar indicates a pressure threshold.
- the unit of measure rpm means revolution per minute, ie revolution per minute.
- the gain factor adap_fac is determined in block 103, which characterizes a statistically averaged offset of the torque characteristic curve of the friction clutch 9. From this, an offset difference is determined, which is fed to the model 13, which determines a torque T_CL_M of the friction clutch 9 to be controlled from this offset difference.
- block 104 it is queried whether the sign of the negative moment difference - ⁇ is equal to the sign of the offset. If this is the case, the torque balance has failed so that the torque offset must be reduced. This is slowly driven to 0 in block 105. If, however, it is determined in block 104 that the sign comparison has led to a negative result, the coefficient of friction in block 106 is determined via
- T_CL_M FC * f_nom (L_act-TP) + drag + offset, in which
- FIG. 3 shows by way of example a torque adaptation by an offset correction.
- the moment T_CL is shown above the path L_act.
- the curve B shows a nominal torque characteristic of the wet-running friction clutch 9.
- the dashed curve B1 represents the real torque curve, as it occurs in the case of floating of the wet-running friction clutch 9 at a predetermined path L_act.
- This real clutch characteristic curve B1 indicates that, in the event of an error, too little torque is provided by the friction clutch 9.
- the offset is determined when the friction clutch 9 is open, while the ramp-like shutdown always takes place when the clutch is closed.
- the curve C shows the adapted by means of the method according to the invention adapted torque characteristic. It should be mentioned that the characteristic C exists only temporarily, as long as the offset is not reduced.
- FIG. 4 shows a second exemplary embodiment of the method according to the invention, in which the offset determination is improved by taking account of the input shaft rotational speed nips.
- Both blocks 200 and 201 the current path of the clutch actuator L_act is supplied.
- Both the output of the block 200 and the output of the block 201 lead to a block 202 in which a 0 rpm input wave offset map is generated.
- the block produced in block 206 The result at point 207 is multiplied by the drag nips> 1000 provided in block 201 and passed to point 205.
- the values of the 0 rpm input shaft offset characteristic value determined in block 202 are superimposed on a 1000 rpm input shaft offset characteristic field 208 by interpolation.
- the drag nips> 1000 provided in block 201 are assigned a multiplied by another weighting factor determined in block 210. This is 1 if the input shaft speed is> 1000 rpm.
- the product formed in block 209 is added to a further product formed in block 212.
- the product formed in block 212 is formed from the result of block 205 of the Orpm input wave offset map (block 202) and another weighting factor determined in block 213. This is always 0 if the input shaft speed is nips> 1000rpm.
- the nominal torque characteristic B which corresponds to the O rpm input shaft offset characteristic curve, is also shown.
- the characteristic B1 corresponds in its deviations to the 1000rpm input shaft offset characteristic.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020197034342A KR102548140B1 (ko) | 2017-04-26 | 2018-03-27 | 마찰 클러치의 토크 특성곡선 적응 방법 |
DE112018002185.8T DE112018002185A5 (de) | 2017-04-26 | 2018-03-27 | Verfahren zur adaption einer momentenkennlinie einer reibungskupplung |
CN201880038997.6A CN110770460A (zh) | 2017-04-26 | 2018-03-27 | 用于适应性修改摩擦离合器的力矩特性曲线的方法 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017108931 | 2017-04-26 | ||
DE102017108931.4 | 2017-04-26 |
Publications (1)
Publication Number | Publication Date |
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WO2018196913A1 true WO2018196913A1 (de) | 2018-11-01 |
Family
ID=61912924
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2018/100279 WO2018196913A1 (de) | 2017-04-26 | 2018-03-27 | Verfahren zur adaption einer momentenkennlinie einer reibungskupplung |
Country Status (4)
Country | Link |
---|---|
KR (1) | KR102548140B1 (de) |
CN (1) | CN110770460A (de) |
DE (2) | DE112018002185A5 (de) |
WO (1) | WO2018196913A1 (de) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10308517A1 (de) * | 2003-02-26 | 2004-09-09 | Volkswagen Ag | Verfahren zur Kupplungskennlinienadaption |
DE102011080716A1 (de) * | 2010-08-30 | 2012-04-05 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Steuerung einer Reibungskupplung |
DE102012204940A1 (de) | 2011-04-15 | 2012-10-18 | Schaeffler Technologies AG & Co. KG | Verfahren zur Adaption von Parametern einer Kupplung |
US20150167759A1 (en) * | 2013-12-17 | 2015-06-18 | Hyundai Motor Company | Method of adjusting characteristics of dry clutch |
DE102015205884A1 (de) * | 2015-04-01 | 2016-10-06 | Schaeffler Technologies AG & Co. KG | Verfahren zur Adaption eines hydrostatischen Tastpunktes einer in einem hydraulischen Kupplungsbetätigungssystem angeordneten Kupplung |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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GB2319818B (en) * | 1994-02-23 | 1998-10-07 | Luk Getriebe Systeme Gmbh | Monitoring method for a torque transfer system |
CN103703264B (zh) * | 2011-06-06 | 2016-05-18 | 丰田自动车株式会社 | 自动离合器控制装置 |
CN103917799B (zh) * | 2011-08-08 | 2016-09-14 | 舍弗勒技术股份两合公司 | 用于控制双离合器变速器的方法 |
DE102012220179B4 (de) * | 2011-11-24 | 2024-05-02 | Schaeffler Technologies AG & Co. KG | Verfahren zur Überprüfung einer korrekten Befüllung eines hydraulischen Kupplungssystems |
DE102011089031A1 (de) * | 2011-12-19 | 2013-06-20 | Zf Friedrichshafen Ag | Verfahren und Steuerungseinrichtung zur Bestimmung eines Berührpunkts einer Reibkupplung |
DE102014218895A1 (de) * | 2013-10-04 | 2015-04-09 | Schaeffler Technologies Gmbh & Co. Kg | Kupplungswartung |
DE112015000818A5 (de) * | 2014-02-14 | 2016-10-20 | Schaeffler Technologies AG & Co. KG | Verfahren zur Bestimmung einer Kennlinie einer Kupplung eines Kupplungsbetätigungssystems in einem Antriebsstrang, insbesondere eines Kraftfahrzeuges |
DE102015210175A1 (de) * | 2015-06-02 | 2016-12-08 | Schaeffler Technologies AG & Co. KG | Verfahren zur Steuerung einer automatisiert betätigten Reibungskupplung |
WO2017025087A1 (de) * | 2015-07-23 | 2017-02-16 | Schaeffler Technologies AG & Co. KG | Verfahren zur steuerung einer automatisierten reibungskupplung |
DE102015226539A1 (de) | 2015-12-22 | 2017-06-22 | Volkswagen Aktiengesellschaft | "Verfahren zur Steuerung und/oder Regelung einer nasslaufenden Kupplung eines Kraftfahrzeugs" |
-
2018
- 2018-03-27 DE DE112018002185.8T patent/DE112018002185A5/de active Pending
- 2018-03-27 WO PCT/DE2018/100279 patent/WO2018196913A1/de active Application Filing
- 2018-03-27 KR KR1020197034342A patent/KR102548140B1/ko active IP Right Grant
- 2018-03-27 CN CN201880038997.6A patent/CN110770460A/zh active Pending
- 2018-04-23 DE DE102018109720.4A patent/DE102018109720B4/de active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10308517A1 (de) * | 2003-02-26 | 2004-09-09 | Volkswagen Ag | Verfahren zur Kupplungskennlinienadaption |
DE102011080716A1 (de) * | 2010-08-30 | 2012-04-05 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Steuerung einer Reibungskupplung |
DE102012204940A1 (de) | 2011-04-15 | 2012-10-18 | Schaeffler Technologies AG & Co. KG | Verfahren zur Adaption von Parametern einer Kupplung |
US20150167759A1 (en) * | 2013-12-17 | 2015-06-18 | Hyundai Motor Company | Method of adjusting characteristics of dry clutch |
DE102015205884A1 (de) * | 2015-04-01 | 2016-10-06 | Schaeffler Technologies AG & Co. KG | Verfahren zur Adaption eines hydrostatischen Tastpunktes einer in einem hydraulischen Kupplungsbetätigungssystem angeordneten Kupplung |
Also Published As
Publication number | Publication date |
---|---|
KR20200003389A (ko) | 2020-01-09 |
CN110770460A (zh) | 2020-02-07 |
DE102018109720A1 (de) | 2018-10-31 |
DE102018109720B4 (de) | 2024-01-25 |
KR102548140B1 (ko) | 2023-06-29 |
DE112018002185A5 (de) | 2020-01-02 |
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