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
  • F16D2500/108—Gear
  • F16D2500/1086—Concentric shafts
• • 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
  • F16D2500/308—Signal inputs from the transmission
  • F16D2500/30806—Engaged transmission ratio
• • 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
  • F16D2500/70—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 determining the crosstalk behavior of a
• hydrostatic dual-clutch transmission of a motor vehicle which has two partial transmission clutches, which are each arranged between a drive unit and a respective sub-transmission, wherein the two sub-transmission clutches are actuated independently of each other via a Sectiongetriebekupplungsaktorik, wherein acting during actuation of the part of the clutch clutch actuator to the sub-transmission clutch actuating pressure and determining a clutch actuation travel covered by the partial transmission clutch, from which a crosstalk amount is determined for each partial transmission clutch.
• Double clutch transmission understood in which in particular for the actuation of the two automated friction clutches per a hydrostatically operated actuator HCA (Hydrostatic Clutch Actuator) is provided, as disclosed for example in DE 10 2010 047 801 A1 or DE 10 2010 047 800 A1.
• a hydrostatically operated actuator has in particular a pressure sensor and a displacement sensor for targeted movement and positioning of the actuator along the clutch actuation path.
• Dual clutch transmissions - also referred to as dual clutches or parallel shift transmissions for short - have long been known and are shown, for example, in DE 10 2008 023 360 A1.
• EP 1 554 502 B1 discloses a method for modeling and compensating such crosstalk operations.
• the Coefficient of friction of the friction clutch included as a proportionality Therefore, a friction-adjusted, nominal clutch torque of a friction clutch is determined, and from this the shift of the characteristic in the case of a crosstalk during the actuation of the other friction clutch is determined.
• this method is complex and comparatively inaccurate.
• Pressure signal for modeling the crosstalk can be used, as is known from WO 201 1/124329 A1. This describes a very simple modeling of the crosstalk by a correction quantity for the compensation of the changed position of the friction clutch is determined by means of a pressure representing the Hydrostataktors size. However, no method is disclosed as to how these model parameters can be determined on the test bench. In addition, only one parameter set for all vehicles would be determined by test bench measurements. However, the crosstalk is subject to component tolerances and is thus different from clutch to clutch (at least slightly).
• the invention is therefore based on the object of specifying a method for determining the over-talk behavior of a hydrostatic double-clutch system of a motor vehicle, in which the component tolerances of the clutches are taken into account.
• each crosstalk is derived from a map that is generated in response to the actuation pressures of both partial transmission clutches.
• each map is determined by the determination of pressure-displacement characteristics during movement of the partial transmission clutches along the respective Kupplungsbetuschistsweges and a comparison with a reference characteristic, wherein for predetermined pressure values the associated position shift is determined.
• each partial transmission clutch is separated from each other
• the reference characteristic represents the pressure-path behavior of the actuated partial transmission clutch without crosstalk influences.
• a crosstalk behavior of the sub-transmission clutches with one another is suppressed because the stationary sub-transmission clutch remains in a preferably open state and thus no crosstalk occurs on the moving sub-transmission clutch.
• a partial transmission clutch for adjusting a defined pressure in a partially closed position is moved and held in this, while for the other sub-transmission clutch by performing a complete closing / opening operation, a path-pressure characteristic is recorded to determine the crosstown , By adjusting the defined pressure in the partially closed partial transmission clutch whose crosstalk can be reliably determined on the other partial transmission clutch, which is completely traversed to receive a path-pressure curve.
• both partial transmission clutches are moved simultaneously to determine the crosstalk quantities. It is considered that the phase space, which is spanned by the two coupling positions, is uniformly covered.
• the crosstalk quantities are adapted over the life of the motor vehicle.
• changes in the partial transmission clutches for example due to wear, are registered along their clutch actuation path and taken into account in determining the crosstalk behavior.
• a compensation of the crosstalk behavior and a resulting highly accurate control of the partial transmission clutches are ensured during the clutch operation.
• the crosstalk quantities are adapted adaptively.
• the crosstalk sizes are adjusted in each coupling process, whereby a variety of changes in the crosstalk between the sub-transmission clutches can be compensated.
• the adaptive adaptation improves the clutch torque accuracy and increases ride comfort.
• the crosstalk quantities are determined incrementally. This incremental determination is advantageous in particular when the crosstalk quantities are determined regularly and simplifies the determination of the crosstalk quantities.
• the position of the associated partial transmission clutch for adjusting an undisturbed position is corrected by means of the respective crosstalk. This ensures that the coupling always moves to the actual desired position and that elasticities between the couplings are compensated.
• Figure 1 Schematic representation of a drive train of a motor vehicle with a
• Figure 2 schematic construction of a hydraulic clutch actuator for a
• FIG. 1 shows a schematic diagram of a drive train 1 of a motor vehicle with a dual-clutch transmission.
• a drive unit 2 for example an internal combustion engine
• the dual-clutch transmission consists of two trains and in this case has a first partial transmission clutch 4, which is connected to a first partial transmission clutch 4. 9 drives.
• the drive unit 2 is also connected to a second partial transmission clutch 5, which leads to a second partial transmission 8.
• the two partial transmissions 8, 9 are guided via an axle differential 10 to a drive axle 1 1 of the motor vehicle.
• Partial gear 9 the odd gears such as 1, 3, 5, while the second partial transmission 8, the straight gears as 2, 4, 6 includes.
• both partial transmission clutches 4, 5 When operating the dual-clutch transmission, for example, when changing from a first gear to second gear both partial transmission clutches 4, 5 must be actuated, since by means of the first partial transmission clutch 4, the first gear is designed while using the second partial transmission clutch 5, the second gear is engaged.
• Each sub-transmission clutch 4, 5 is actuated by a Sectiongetriebekupplungsaktorik 6, 7, which includes an electric motor.
• the Railgetriebekupplungsaktorik 6, 7 is connected to a control unit 12 which controls the Generalgetriebekupplungsaktorik 6, 7 when needed.
• elasticities occur, which lead to a mutual influence of the Kupplungsverfahrweges the partial transmission clutches 4, 5, said mutual interference is referred to as crosstalk.
• a hydraulic, hydrostatic clutch actuator (HCA) is used as a partial transmission clutch actuator 6, 7, the schematic structure of which is to be explained in greater detail with reference to FIG. 2 on the basis of the partial transmission clutch actuator 6.
• the Operagetriebekupplungsaktorik 6 includes on the donor side, the control unit 12, which drives the electric motor 13. With a change in position of the electric motor 13 and an actuated by the electric motor 13 piston 15 of the master cylinder 14 along the Aktorweges to the right, the volume of the master cylinder 14 is changed, whereby a pressure p is built up in the master cylinder 14, which via a hydraulic fluid 16 via a hydraulic line 17 to the slave side 18 of the Operagetriebe clutch actuator 6 is transmitted.
• the hydraulic line 17 is adapted with respect to its length and shape of the installation space situation of the vehicle.
• On the slave side 18 causes the pressure p of the hydraulic fluid 16 in a slave cylinder 19, a path change, which is transmitted to the partial transmission clutch 5 in order to actuate them.
• the pressure p in the master cylinder 14 on the encoder side 20 of the partial transmission clutch actuator 6 can be determined by means of a pressure sensor 21.
• the path traveled by the piston 15 of the master cylinder 14 is determined by means of a displacement sensor 22.
• Component elasticities between the partial transmission clutches 4, 5 occur when actuated, crosstalk quantities are determined whose determination comprises several phases.
• a reference characteristic curve is determined for each partial transmission clutch 4, 5.
• a corresponding path-pressure reference characteristic KL4 ref is determined by closing and opening the partial transmission clutch 4.
• a corresponding path-pressure reference characteristic KL5 ref for the second partial transmission clutch 5 is determined.
• the determination of the reference characteristics KL4 ref , KL5 ref takes place for both partial transmission clutches 4, 5 independently of each other, wherein the partial transmission clutch 4, 5, whose path-pressure curve is not determined, remains fully open.
• the crosstalk influence is determined in a second phase.
• the partial transmission clutch 4 is partially closed to assume a fixed clutch position x4, where i is the index for various positions of the partial transmission clutch 4.
• a path-pressure curve KL5 tes t , i is then recorded for the second partial transmission clutch 5 by closing and opening the partial transmission clutch 5.
• Ax5i j Position shifts of the partial transmission clutch 5 due to crosstalk
• Ax4i j Position shifts of the partial transmission clutch 4 due to crosstalk (identically zero in this measurement)
• the measurements are repeated with reversed roles of the two partial transmission clutches 4, 5, ie the sub-transmission clutch 5 moves to a fixed position ⁇ 5, while the sub-transmission clutch 4 performs a complete opening-closing operation, wherein their path-pressure characteristics KL4 test, i be recorded.
• the crosstalk quantities Ax4, Ax5 are determined from the measured variables recorded in the second phase.
• ⁇ 5 K5 (p4, p5), where K4 and K5 represent maps of the respective partial transmission clutch 4, 5.
• the input variables for the characteristic maps K4 and K5 are the pressures p1, p2 of the two partial transmission clutches 4, 5. Depending on the variance of the crosstalk, the maps K4, K5 have a dimension of 3 ⁇ 3 or 10 ⁇ 10 values.
• the characteristic diagram parameters can be determined from the recorded measured variables, for example by means of a least-square algorithm.
• the crosstalk quantities ⁇ 4 and ⁇ 5 are stored in the memory 23 of the control unit 12 of the dual-clutch transmission designed as an EEPROM.
• the current pressure values p4, p5 from the maps the current crosstalk amounts ⁇ 4, ⁇ 5, which position shifts of the partial transmission clutches 4, 5 correspond calculated and used in the clutch control of the control unit 12 to correct the clutch travel to be set.
• These crosstalk quantities ⁇ 4, ⁇ 5 stored in the memory 23 of the control unit 12 are adapted during driving operation of the motor vehicle. Through the adaptation, the
• the crosstalk quantities ⁇ 4, ⁇ 5 are determined during commissioning at the end of the belt either in the motor vehicle or on the test bench or after installation in the motor vehicle in the service. These crosstalk quantities are stored in the memory 23 of the control unit 13 for further use while driving.

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

Priority Applications (2)

Applications Claiming Priority (4)

Publications (1)

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ID=47714033

Family Applications (1)

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Citations (6)

Family Cites Families (3)

• 2013
  • 2013-01-31 WO PCT/EP2013/051835 patent/WO2013124129A1/de active Application Filing
  • 2013-01-31 DE DE112013001093.3T patent/DE112013001093A5/de active Pending
  • 2013-01-31 CN CN201380006203.5A patent/CN104067017B/zh active Active
  • 2013-01-31 DE DE201310201566 patent/DE102013201566A1/de not_active Withdrawn

Patent Citations (7)

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