WO2002101258A2 - Kupplungsbetätigungsvorrichtung sowie verfahren zum ermitteln von kupplugsparametern - Google Patents
Kupplungsbetätigungsvorrichtung sowie verfahren zum ermitteln von kupplugsparametern Download PDFInfo
- Publication number
- WO2002101258A2 WO2002101258A2 PCT/DE2002/002072 DE0202072W WO02101258A2 WO 2002101258 A2 WO2002101258 A2 WO 2002101258A2 DE 0202072 W DE0202072 W DE 0202072W WO 02101258 A2 WO02101258 A2 WO 02101258A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- area
- actuator
- force
- actuating
- Prior art date
Links
Classifications
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- 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
-
- 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
- F16D2500/30—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
- F16D2500/30—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
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3028—Voltage
-
- 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
- F16D2500/30401—On-off signal indicating the engage or disengaged position of the clutch
Definitions
- the invention relates to a clutch actuation device, in particular for use in the drive train of a motor vehicle.
- the invention further relates to a method for determining the closed position of a clutch, a method for determining the actuating force of a clutch and a method for determining the temperature of a clutch actuator.
- FIG. 9 shows an exemplary block diagram of a drive train of a motor vehicle equipped with an automated clutch.
- the drive train contains an internal combustion engine 2, a clutch 4 and a transmission 6, from which a drive shaft 8 leads to drive wheels, not shown.
- the transmission 6 is, for example, an automated manual transmission or a conical pulley belt transmission with continuously variable transmission ratio.
- the clutch 4 is, for example, a friction disk clutch of a type known per se with an actuating device 16 which is designed hydraulically, electrically, electrohydraulically or in some other known manner.
- Sensors that may be present in the drive train such as a pressure sensor 18 for detecting the intake pressure of the engine 2, a speed sensor 20 for detecting the speed ⁇ M of the crankshaft of the engine, a sensor 22 for detecting the position ⁇ of an accelerator pedal 24, and a sensor 28 for detecting the position of the selector lever 12 and a further speed sensor 28 for detecting the speed of the drive shaft 2 are connected to the inputs of the control device 14.
- the control unit 14 which contains a microprocessor with associated memories 29 in a manner known per se, Kennfeider and programs are stored with which actuators, such as a load actuator 30 for adjusting the load of the motor 2, the actuating device 16 of the clutch 4 and the actuating device 9 of the transmission 6 can be controlled.
- the individual actuators can be constructed in such a way that their position is known directly in the control unit 14, for example as stepper motors, or additional position transmitters, such as a position transmitter 32 for detecting a parameter relevant for the position S K of the clutch, can be provided.
- the load actuator 30, the actuating device 16 and the actuating device 9 are actuated in a mutually coordinated manner as a function of signals supplied by the sensors, so that comfortable and / or economical driving results.
- a characteristic curve is stored in a memory of the control device 14, which defines a set position of the clutch 4 set by the actuation device 16 as a function of the torque to be transmitted by the clutch 4.
- the clutch torque that can be transmitted should only be as large as is absolutely necessary.
- the required torque to be transmitted results from the driver's request or the position of the accelerator pedal 24 and, for example, the load of the internal combustion engine 2 detected by the sensor 18 and possibly further operating parameters, such as the speed of the engine 2 etc.
- the characteristic curve stored in the control unit 14, which specifies the desired path of an actuator of the clutch moved by the actuating device 16 as a function of the calculated torque to be transmitted, has a decisive influence on comfortable starting and a comfortable handling of the switching process.
- the characteristic curve changes briefly, for example as a result of temperature changes, and long-term in the course the life of the clutch, for example due to wear. It is therefore at
- FIG. 10 shows in detail an example of an actuation device 16.
- a piston 38 operates, the shaft 40 of which has an external toothing which meshes with an internal toothing of a gearwheel 41, which in turn meshes with the external toothing of a pinion 42 of an electric motor 43, which is actuated by the control device 14 ( Figure 4) is controlled.
- the electric motor can be of any suitable type and is controlled, for example, by means of a PWM signal.
- the electric motor is advantageously a stepping motor.
- the master cylinder 36 has a sniffer bore 44 which is connected via a line 45 to an expansion tank (not shown).
- a line 48 leads from the pressure chamber 46 of the cylinder, which leads to a slave cylinder 50, in which a piston 52 works, which is connected via its piston rod, for example, to the release lever 54 of the clutch, which forms an actuator.
- the position A which is generally referred to as the sniffing position, is the position when it is passed over by the piston 38 to the right in accordance with FIG. 4, pressure builds up in the pressure chamber 46 for actuating the clutch.
- an incremental position transmitter 32 known in its construction is provided on the gear 41, for example, which counts the teeth of the gear 41 moving past it and emits corresponding pulses to the control device 14.
- the number of these pulses is a direct measure of the displacement of the master piston 38 or, if the master piston 38 according to FIG. 9 is to the right of the sniffing position A, the movement of the release lever 54.
- the master piston 38 in which a check valve (not shown) is advantageously integrated, so that when the piston 38 opens on the left-hand side in the event of overpressure, is moved to the left beyond the sniffing position A, which also carries the hydraulic path between the pistons 38 and 52 the line 45 is connected and is depressurized.
- the release lever 54 takes its position corresponding to the fully closed or closed position of the clutch Position. If the master cylinder 38 is subsequently moved to the right by the electric motor 42, the release lever 54 is actuated at the moment when the master piston 38 passes over the sniffing position A.
- This position of the master piston 38 can be detected in a wide variety of ways, the respective count of the position sensor 32 being stored as the closed position in the control unit 14.
- the actuating device according to FIG. 10 represents a transmission device in which the master piston acting as an actuating member according to FIG. 11 has a small area 1 on the left of the sniffing position A.
- approximately constant force K is movable and when driving over the sniffer bore, ie to the right of the sniffing position A, with increasing force K against the force of the clutch closing spring, not shown, is movable to open the clutch.
- a linear force-displacement characteristic of the clutch is assumed.
- Such a design of the clutch actuation device with two different areas, the transition point of which corresponds to a certain clutch position, preferably the fully closed clutch position, has, as described, the great advantage that the predetermined clutch position can be reliably recognized.
- the invention has for its object to provide a clutch actuation device with two areas, an actuation of an actuating member actuated by a motorized clutch actuator within the first area not leading to a clutch adjustment, for example adjustment of the clutch in the opening direction, without the known, described hydraulic route with sniffer bore is used.
- the invention is further based on the object of specifying methods with which the advantages of a clutch actuation device with two actuation areas are advantageously used.
- the device according to the invention contains device a transmission device with a mechanical loose section, which is constructed such that the possible "play" between the actuation of the actuator and the actual adjustment or actuation of the clutch within the first range is used up so that when reaching the transition between - See the first area and the second area the actual actuation or the adjustment of the clutch begins.
- the claim 3 is directed to an advantageous method for determining the closed position of a clutch, wherein the detected parameter can be of various types and can be, for example, a parameter measured on the clutch actuator itself or a parameter that is measured within the transmission device or on the clutch itself.
- the method according to the invention can also be used in transmission devices with a hydraulic path and sniffer bore.
- the parameter detected while driving through at least part of the first area and part of the second area is advantageously an operating parameter of the clutch actuator.
- the clutch actuator moves the actuator at a constant speed
- the power consumption of the clutch actuator can be detected, or when the clutch actuator is operated with constant power consumption, the adjustment speed can be detected.
- first start errors can be avoided, which are shown, for example, in an unsatisfactory creep behavior of a vehicle.
- cup springs which are usually present in a conventional clutch assume an indefinite rest position (bandwidth about 1 mm).
- the actuating device with which the clutch is in the closed position immediately after starting the engine and before the clutch is brought into a gripping position for the first time, has a hydraulic section with a sniffer bore so that the closed position can be determined in a sniffing cycle. It goes without saying that the engine can be started with the brake applied and the clutch fully open or with the brake applied, neutral gear engaged and the clutch fully engaged, in the former case it being necessary to shift into neutral before the clutch is engaged.
- the advantage is achieved that a sniffing cycle is carried out in corresponding operating phases of the engine, which occur again and again during vehicle operation, so that effects of heating of the fluid of the hydraulic line and, as a result, possibly resulting gripping point shifts can be compensated.
- Claim 10 is directed to an advantageous method for determining the actuating force of the clutch.
- Claim 11 describes a method for determining the temperature of the clutch actuator.
- the invention which is applicable to all types of motor-operated clutches, is explained below with reference to schematic drawings, for example and with further details.
- FIG. 1 shows a first embodiment of an actuating device for a clutch
- FIG. 2 shows an actuating device modified compared to FIG. 1,
- FIG. 3 shows a force-displacement characteristic curve of an actuating element for a clutch
- FIG. 4 shows a voltage-displacement characteristic of an actuator for actuating a clutch
- FIG. 5 shows a speed-travel characteristic curve of an actuator for actuating a clutch
- FIGS. 6 and 7 curves for explaining the determination of a clutch actuation force
- FIG. 8 shows a family of speed-torque characteristics of an electric motor
- FIG. 9 shows a basic illustration of a drive train known per se
- FIG. 10 shows a clutch actuation device with a hydraulic path
- FIG. 11 shows a force-displacement characteristic of the actuating device according to FIG. 10.
- the following description relates in each case to clutches which are contained, for example, in a drive train according to FIG. 9 and which are actuated by a motor, preferably an electric motor, with the interposition of different transmission devices.
- a motor preferably an electric motor
- FIG. 1 shows a first example of a mechanical transmission link without integrated adjustment.
- a clutch actuator 56 for example an electric motor, linearly moves a tappet 58, which is connected in an articulated manner to a release fork 60, which in turn is locked. is articulated to a release bearing 62 of the clutch 4.
- the release bearing 62 is linearly movable and, in the position shown, is at a distance from the plate spring tongues 64 of the clutch, when the clutch is moved to the left in accordance with FIG. 1, the clutch fully closed in the state shown is opened.
- the kinematic assignment is such that the release bearing 62 can each be moved into a position in which it is located at a distance from the plate spring tongues 64, so that when the clutch actuator 56 is started from a zero position, the release bearing 62 is initially essentially powerless is moved to the left and then opens the clutch against the resistance of the spring.
- the force-displacement characteristic of the release bearing 62 is similar to that indicated in FIG. 10.
- Figure 2 shows a modified embodiment of an actuating device. It differs from that of Figure 1 in that the release fork 60 is a two-armed lever and the release bearing 62 is urged by a preload spring 70 with a significantly weaker force than that of the plate spring tongues 64 in contact with the plate spring tongues 64.
- the tappet 58 is connected to the release fork 60 via a pull rope 68 which loosely sags in the starting position of the actuator 56.
- the embodiment according to FIG. 2 also results in a force-displacement characteristic curve according to FIG. 10 for the adjustment of the tappet 58 in the direction of the arrow of FIG. 2 denoted by s.
- FIG. 3 shows a force-displacement characteristic curve, which has a force that is only weakly dependent on the travel in area 1 and in area 2, in which the clutch is adjusted, initially increases sharply with increasing opening of the clutch and then decreases after passing through a maximum until the clutch is fully open and moves back to area 1 when closing with the same basic operation with hysteresis.
- a course of the characteristic curve can be realized, for example, by inserting a dashed spring 72 into the arrangement in FIG. 1, which spring acts between the release fork 60 and a support fixed to the housing.
- the curved characteristic The course of area 2, which overlaps the linear course of area 1, is realized by appropriate design of the disc springs.
- the point P (FIG. 3 corresponding to the point A in FIG. 10), in which the area 1 merges into the area 2 and which corresponds to the closed position of the clutch, can be detected precisely as a result of the different characteristic curve or conditions on both sides.
- the respective associated position of the position transmitter 32 (FIG. 9) can be stored in the control unit 14, so that the closed position of the clutch in the form of the rotational position of the actuator is known exactly.
- the position P can advantageously be determined by directly tapping operating parameters of the electric motor or actuator 56.
- the current load torque which corresponds to the force, can be calculated from a respective speed and voltage curve of the electric motor if the inertia of the electric motor is eliminated in the case of instational processes.
- a curve of the voltage U with which the electric motor is operated, according to FIG. 4 results with a characteristic curve according to FIG. 3.
- the actuation direction is in accordance with the arrow shown in FIG. 4.
- the kink of the voltage U can be detected by the control unit 14 and the rotational position which the electric motor has at the kink is stored as the closed position P.
- FIG. 5 shows the situation in the event that the electric motor is operated with constant voltage and its speed n is detected.
- Curve 1 shows the case in which the electric motor is operated with a relatively high voltage; the kink in the speed-displacement characteristic curve is strongly rounded, whereas curve II indicates the conditions at low voltage at which the kink at point P is clearly pronounced.
- the closed position of the clutch can also be determined in accordance with the principles of FIGS. 4 and 5 even with the arrangement according to FIG. 10 (position of the electric motor 43 such that the piston 38 is located at position A), with actuation the clutch in the closing direction at point A the torque to be applied by the motor suddenly changes.
- the force to be exerted by the actuator is very small in area 1, as in the case of a hydraulic section. 10 to actuate the actuator in such a way that it is actuated in the area in which the transition between area 1 and area 2 is such that the directional movement from area 1 to area 2 or vice versa causes an oscillation or Back and forth movement with a predetermined amplitude or a predetermined torque is superimposed.
- the point A (FIG. 10) or P (FIG. 3) can be determined precisely from the power consumption of the actuator during a period of the oscillation or the movement response at a predetermined torque.
- Operating cycles of the clutch within which the closed position of the clutch can be determined, can always be inserted during the operation of a motor vehicle when the clutch can be operated from the closed position into an at least partially open position without the driver noticing , for example when the vehicle is at a standstill and the neutral gear is engaged, it being additionally possible for the brake to be actuated by the driver or by an ABS system or vehicle stabilization system, when the vehicle is rolling in zero gear or for a short time when the vehicle is operating with low drive torque.
- a precise knowledge of the closed position of the clutch or the starting point or zero point of its actuation is important because the clutch's gripping point must be approached quickly when starting or when shifting, which is possible because the distance between the clutch's closed position and the clutch's gripping point (Coupling position, in which a predetermined, small torque is transmitted) is stored in the control unit 14, so that when the position of the closed position is known, the gripping point can be approached immediately by appropriate actuation of the actuator. Since the distance between the gripping point and the closed position is flows, for example due to settling losses or thermal changes, both the closed position and the gripping position of the clutch must be updated.
- the distance between the gripping point and the closed position can initially be assumed to be constant and the closed position stored in the control unit 14 can be shifted in accordance with a shift in the gripping point when it is updated until a new one The closed position is updated and the distance is corrected if necessary. Conversely, if it is not possible to update the gripping point after a closing position update, the gripping point can first be shifted in accordance with the updated closing position and only updated later, the distance between the gripping point and the closing point then also being updated, if appropriate, b) actuation force determination
- FIGS. 6 and 7 represent the voltage of the electric motor 56 as a function of the actuating travel s together with the respective actuating direction (arrow).
- the clutch is fully closed (driving through area 1), the electric motor being operated at a constant speed, so that the voltage U is a measure of the force applied.
- the voltage U applied to pass through area 1 (in one direction or the other) is stored as Ui (FIG. 6);
- Fmax (Uma ⁇ / U ⁇ ) X ⁇ + Fs ma ⁇ .
- transient determination methods are also possible, with dynamic components due to inertia being excluded.
- the aforementioned or similar actuation determinations by comparing the actuating force with the compensating force is particularly important for a clutch with targeted overtravel adjustment (no self-adjustment).
- By comparing the actuating force with the largely unchangeable compensating force the state of wear of the clutch and thus the need for targeted readjustment can be detected. Adjustment is necessary when the actuating force has increased by a predetermined amount.
- the temperature of the electric motor that operates the clutch For many applications, it is advantageous to know the temperature of the electric motor that operates the clutch. For example, the maximum torque of the engine and thus the maximum force for adjusting the clutch is dependent on the temperature, so that the clutch adjustment speed, which is taken into account in the interaction of the load actuator actuation of the engine and possibly the gear actuation, has limits.
- the temperature of the electric motor can be determined on the basis of the voltage-speed curve, which the motor is determined when passing through the area in which work is only carried out against the largely constant compensation spring, and the voltage-speed curve is compared with stored temperature-dependent characteristic diagrams of the electric motor ,
- FIG. 8 shows a family of characteristic curves K for different temperatures T, which indicate the dependence of the speed n on the engine torque M, in each case at a reference voltage U R ⁇ f .
- the temperature of the electric motor can be determined as follows:
- the operating point of the actuator ie the armature voltage U ⁇ ⁇ st is determined, the associated torque Mj e t being predetermined by the compensation spring.
- the reference voltage U Re f which, for example, the maximum possible che voltage is the corresponding reference operating point M R ⁇ f, n Ref according to the following
- the determined reference operating point is entered in the map of Figure 8.
- the associated characteristic curve indicates the temperature of the motor with which the clutch can be operated at maximum armature voltage.
- the clutch can be a clutch that is open in the non-actuated state.
- the actuator does not have to be an electric motor; it can be hydraulic, pneumatic or otherwise.
- the sensor assembly can be of a different type, etc.
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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)
- Mechanical Operated Clutches (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2003-7002063A KR20030038698A (ko) | 2001-06-13 | 2002-06-07 | 클러치 작동 장치 및 클러치 파라미터를 검출하는 방법 |
JP2003503984A JP2004529302A (ja) | 2001-06-13 | 2002-06-07 | クラッチ作動装置およびクラッチパラメータを求めるための方法 |
DE10292580T DE10292580D2 (de) | 2001-06-13 | 2002-06-07 | Kupplungsbetätigungsvorrichtung sowie Verfahren zum Ermitteln von Kupplungsparametern |
BR0205609-7A BR0205609A (pt) | 2001-06-13 | 2002-06-07 | Dispositivo de acionamento da embreagem, bem como, processo para a determinação de par metros de embreagem |
US10/733,175 US6896112B2 (en) | 2001-06-13 | 2003-12-10 | Clutch-actuating device and methods of determining clutch parameters |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10128684.8 | 2001-06-13 | ||
DE10128684 | 2001-06-13 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/733,175 Continuation US6896112B2 (en) | 2001-06-13 | 2003-12-10 | Clutch-actuating device and methods of determining clutch parameters |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2002101258A2 true WO2002101258A2 (de) | 2002-12-19 |
WO2002101258A3 WO2002101258A3 (de) | 2003-05-30 |
Family
ID=7688150
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2002/002072 WO2002101258A2 (de) | 2001-06-13 | 2002-06-07 | Kupplungsbetätigungsvorrichtung sowie verfahren zum ermitteln von kupplugsparametern |
Country Status (8)
Country | Link |
---|---|
US (1) | US6896112B2 (de) |
JP (1) | JP2004529302A (de) |
KR (1) | KR20030038698A (de) |
BR (1) | BR0205609A (de) |
DE (2) | DE10225262B4 (de) |
FR (1) | FR2826081B1 (de) |
IT (1) | ITMI20021297A1 (de) |
WO (1) | WO2002101258A2 (de) |
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WO2003074896A2 (de) * | 2002-03-07 | 2003-09-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Steuereinrichtung und verfahren zum positionsabgleich in einer bewegungsübertragung |
EP1614921A1 (de) * | 2004-07-10 | 2006-01-11 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Verfahren zum Einstellen eines Kupplungsmoments |
US7350634B2 (en) | 2004-06-30 | 2008-04-01 | Luk Lamellen Und Kupplungsbau Beteillgungs Kg | Method for adjusting an incremental path measurement unit in an actuation device of a pressure-closed clutch as well as an actuation device |
US7726748B2 (en) * | 2005-09-26 | 2010-06-01 | Zumberge Jon T | Low force level detection system and method |
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US7101310B2 (en) * | 2004-04-19 | 2006-09-05 | Magna Powertrain Usa, Inc. | Model-based control for torque biasing system |
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WO2006003879A1 (ja) * | 2004-07-01 | 2006-01-12 | Yamaha Hatsudoki Kabushiki Kaisha | 作動力伝達機構および鞍乗型車両 |
JP2006170224A (ja) * | 2004-12-10 | 2006-06-29 | Yamaha Motor Co Ltd | クラッチ制御装置、クラッチ制御方法及び鞍乗型車両 |
JP4686179B2 (ja) * | 2004-12-10 | 2011-05-18 | ヤマハ発動機株式会社 | クラッチ接続制御装置、クラッチの接続制御方法及び鞍乗型車両 |
JP4723233B2 (ja) | 2004-12-10 | 2011-07-13 | ヤマハ発動機株式会社 | 鞍乗型車両の変速制御装置、制御方法及び鞍乗型車両 |
JP2006170227A (ja) * | 2004-12-10 | 2006-06-29 | Yamaha Motor Co Ltd | クラッチアクチュエータ及び鞍乗型車両 |
US7306545B2 (en) * | 2005-06-28 | 2007-12-11 | Borgwarner, Inc. | Transfer case clutch calibration method |
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- 2002-06-07 JP JP2003503984A patent/JP2004529302A/ja active Pending
- 2002-06-07 DE DE10225262A patent/DE10225262B4/de not_active Expired - Fee Related
- 2002-06-07 DE DE10292580T patent/DE10292580D2/de not_active Expired - Fee Related
- 2002-06-07 BR BR0205609-7A patent/BR0205609A/pt not_active IP Right Cessation
- 2002-06-11 FR FR0207131A patent/FR2826081B1/fr not_active Expired - Lifetime
- 2002-06-12 IT IT2002MI001297A patent/ITMI20021297A1/it unknown
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Cited By (11)
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WO2003074896A2 (de) * | 2002-03-07 | 2003-09-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Steuereinrichtung und verfahren zum positionsabgleich in einer bewegungsübertragung |
FR2837547A1 (fr) * | 2002-03-07 | 2003-09-26 | Luk Lamellen & Kupplungsbau | Dispositif de commande et procede pour l'alignement de position dans une transmission cinematique |
WO2003074896A3 (de) * | 2002-03-07 | 2004-04-22 | Luk Lamellen & Kupplungsbau | Steuereinrichtung und verfahren zum positionsabgleich in einer bewegungsübertragung |
US7350634B2 (en) | 2004-06-30 | 2008-04-01 | Luk Lamellen Und Kupplungsbau Beteillgungs Kg | Method for adjusting an incremental path measurement unit in an actuation device of a pressure-closed clutch as well as an actuation device |
EP1614921A1 (de) * | 2004-07-10 | 2006-01-11 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Verfahren zum Einstellen eines Kupplungsmoments |
EP1757835A2 (de) * | 2004-07-10 | 2007-02-28 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Verfahren zum Einstellen eines Kupplungsmoments |
EP1757835A3 (de) * | 2004-07-10 | 2007-03-07 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Verfahren zum Einstellen eines Kupplungsmoments |
US7412316B2 (en) | 2004-07-10 | 2008-08-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Method for setting a clutch torque |
US7726748B2 (en) * | 2005-09-26 | 2010-06-01 | Zumberge Jon T | Low force level detection system and method |
CN105179513A (zh) * | 2015-08-24 | 2015-12-23 | 安徽安思恒信息科技有限公司 | 一种带检测的离合传动装置 |
CN105179513B (zh) * | 2015-08-24 | 2019-02-05 | 安徽安思恒信息科技有限公司 | 一种带检测的离合传动装置 |
Also Published As
Publication number | Publication date |
---|---|
US6896112B2 (en) | 2005-05-24 |
FR2826081B1 (fr) | 2009-05-15 |
DE10292580D2 (de) | 2004-08-26 |
US20040188218A1 (en) | 2004-09-30 |
DE10225262B4 (de) | 2013-10-10 |
KR20030038698A (ko) | 2003-05-16 |
FR2826081A1 (fr) | 2002-12-20 |
ITMI20021297A1 (it) | 2003-12-12 |
JP2004529302A (ja) | 2004-09-24 |
WO2002101258A3 (de) | 2003-05-30 |
DE10225262A1 (de) | 2003-02-13 |
BR0205609A (pt) | 2003-06-10 |
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