WO2003074312A2 - Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe - Google Patents
Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe Download PDFInfo
- Publication number
- WO2003074312A2 WO2003074312A2 PCT/DE2003/000645 DE0300645W WO03074312A2 WO 2003074312 A2 WO2003074312 A2 WO 2003074312A2 DE 0300645 W DE0300645 W DE 0300645W WO 03074312 A2 WO03074312 A2 WO 03074312A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- torque
- vehicle
- engine
- eng
- Prior art date
Links
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T7/00—Brake-action initiating means
- B60T7/12—Brake-action initiating means for automatic initiation; for initiation not subject to will of driver or passenger
- B60T7/122—Brake-action initiating means for automatic initiation; for initiation not subject to will of driver or passenger for locking of reverse movement
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
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- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
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- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/11—Stepped gearings
- B60W10/113—Stepped gearings with two input flow paths, e.g. double clutch transmission selection of one of the torque flow paths by the corresponding input clutch
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/18009—Propelling the vehicle related to particular drive situations
- B60W30/18027—Drive off, accelerating from standstill
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/18009—Propelling the vehicle related to particular drive situations
- B60W30/18063—Creeping
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- B60W30/1819—Propulsion control with control means using analogue circuits, relays or mechanical links
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/19—Improvement of gear change, e.g. by synchronisation or smoothing gear shift
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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
- F16D29/00—Clutches and systems of clutches involving both fluid and magnetic actuation
- F16D29/005—Clutches and systems of clutches involving both fluid and magnetic actuation with a fluid pressure piston driven by an electric motor
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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
- F16D48/062—Control by electric or electronic means, e.g. of fluid pressure of a clutch system with a plurality of fluid actuated clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- 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
- F16D48/08—Regulating clutch take-up on starting
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
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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
- F16H—GEARING
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- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/688—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches
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- B60W2050/0008—Feedback, closed loop systems or details of feedback error signal
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- B60W2510/00—Input parameters relating to a particular sub-units
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- B60W2510/0208—Clutch engagement state, e.g. engaged or disengaged
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0208—Clutch engagement state, e.g. engaged or disengaged
- B60W2510/0225—Clutch actuator position
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0241—Clutch slip, i.e. difference between input and output speeds
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
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- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0275—Clutch torque
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- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/02—Clutches
- B60W2510/0291—Clutch temperature
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
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- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
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- B60W2510/182—Brake pressure, e.g. of fluid or between pad and disc
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- B60W2710/00—Output or target parameters relating to a particular sub-units
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- B60W2710/02—Clutches
- B60W2710/027—Clutch torque
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- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
- B60W2710/0666—Engine torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- 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
- F16D2500/1025—Electric motor with threaded transmission
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F16D2500/00—External control of clutches by electric or electronic means
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- F16D2500/1026—Hydraulic
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Definitions
- the invention relates to a method for performing a shift in a dual clutch transmission with at least two transmission input shafts, each of which is coupled to the engine via a clutch.
- Double clutch transmissions are known from automotive engineering.
- a double clutch transmission preferably has two transmission input shafts, each of which is coupled to the motor shaft via a clutch.
- the method for performing a shift can be changed from one gear ratio to the next higher or lower gear ratio without interrupting the tractive force.
- the invention has for its object to propose a method for performing a shift in a dual clutch transmission, with which overlapping shifts can be carried out as conveniently as possible.
- This object can be achieved according to the invention in particular by a method for performing a shift in a double clutch transmission with at least two transmission input shafts, each of which is coupled to the motor shaft via a clutch, in which after the detection of a shift request, the clutch assigned to the active, torque-transmitting transmission input shaft to is opened to the slip limit and at which the engine torque is controlled depending on the type of gearshift in order to achieve a vehicle acceleration desired by the driver.
- the aim of the shift strategy according to the invention is to enable comfortable shifting from one transmission input shaft to the other transmission input shaft.
- the shift comfort is positively influenced by the smooth vehicle acceleration during the shift. This means that significant and Sudden changes in the driver's desired acceleration or the desired wheel torque can be prevented in an advantageous manner.
- a transition can be provided while the clutch is disengaged and another transition can be provided while the new clutch is being closed.
- the engine torque can be actively used to increase or decrease to ensure smooth slip-to-stick transitions on the clutches so that the engine speed can be controlled to achieve slippage during shifting and improve engine synchronization compared to the speed of the new transmission input shaft ,
- quick and comfortable gear changes can be made possible, particularly in the case of an ESG double clutch transmission. This is particularly due to the suitable control of the clutches and the engine torque.
- an additional torque can be used to achieve the vehicle acceleration desired by the driver.
- the moment of an electric motor or the like can preferably be used. Torque control for the output torque is thus supported by the active use of the electric motor torque, preferably on the new transmission input shaft during the shift. It is particularly advantageous in the method according to the invention that the required vehicle acceleration is determined as a function of certain vehicle and / or transmission sizes when the torque of the electric motor is activated.
- a target torque of the electric motor is calculated for instantaneous control. The calculated target torque of the electric motor can be used if the target torque is, for example, within predetermined minimum and maximum limit values.
- a further development of the invention can provide that the type of shift and thus also the type of loading of the double clutch transmission is preferably determined shortly before the shift begins.
- the type of gearshift is preferably determined in the method according to the invention in order to optimize the gear change depending on the type of gearshift.
- the type of circuit it is also possible for the type of circuit to be determined as a separate method, regardless of the switching strategy.
- a method according to the invention is therefore also proposed, with which the determination of the power flow in a transmission, in particular in a double clutch transmission, is possible. If this method is used in the context of the proposed dual clutch shift strategy, the comfort when changing gear can be further improved.
- various methods for determining the power flow in the double clutch transmission are specified, with which it is determined whether the transmission has a pulling or a pushing operation.
- Three situations can preferably be considered in a double clutch shift, on the basis of which the determination of the power flow in the drive train is possible.
- the train-push estimate can preferably be carried out immediately before the shift, ie before the start of the clutch change, so that the result obtained is advantageously as up-to-date as possible. It is also possible to make this estimate at another suitable time.
- the state can be considered in which one clutch is open and the other clutch slips or sticks.
- e.g. B. linear shutdown or the like of the coupling torque of the overriding clutch can be brought into the slip state if it is not already in the slip.
- the drive train is under tensile load or
- the transmission is subject to slip under thrust. Accordingly, there are the following
- the state can be considered in which a clutch is liable.
- the entered engine torque T ⁇ ng and the dynamic engine torque ⁇ eng ⁇ J closely are taken into account. If the entered engine torque T ⁇ ng is greater than the dynamic engine torque ⁇ eng - J eng , the gearbox is in the pull state, ie the engine would be accelerated if the clutch was opened at this moment.
- there is a thrust condition namely when the entered engine torque T en g is smaller than the dynamic engine torque ⁇ eng ⁇ J eng , where ⁇ mg is the engine acceleration and J ⁇ ng is the moment of inertia of the engine. This results in the following conditions:
- Thrust condition T ⁇ ng ⁇ narrow ⁇ J narrow
- the state can be considered in which none of the clutches is liable.
- a train operation can be defined in that the sum of the transmitted moments of the clutches is positive.
- the transmitted clutch torque is equal to the minimum value from the set clutch torque T c i a / b and the slip limit of the clutch T ⁇ IB .
- Shear load sign ( ⁇ eng - i A - ⁇ vehlde i A ⁇ T ⁇ emd + sign ⁇ eng - i B - ⁇ vehlcle ) - i B -T ⁇ ⁇ i 0
- ⁇ ⁇ h i c i e are the vehicle speed, i A the overall gear ratio of the first transmission input shaft, i ß the overall gear ratio of the second gear
- the methods shown for determining the train thrust condition make it possible in an advantageous manner to use the appropriate shift strategy (train upshift, push upshift, train downshift or push downshift) during a double clutch shift.
- the appropriate shift strategy train upshift, push upshift, train downshift or push downshift
- unnecessary changes from the train state to the overrun state or vice versa are avoided, and consequently running through the gear play, which can have a negative effect on the driver's sense of comfort.
- the comfort impairment is minimized by the dual clutch strategy presented.
- the slip limits of the two clutches can be determined by the method according to the invention.
- the slip limit (r c ⁇ p ) of the first clutch (A) can preferably be determined using the following formula
- the external vehicle torque T V ⁇ h i c i e can be determined from the following equation:
- the state can also be considered in which the first clutch A adheres and the second clutch B is preferably open.
- the clutch torque of the transmitting clutch A can be brought into the slip state by linearly reducing the clutch torque.
- the external vehicle torque can be determined in particular after the clutch A slip-slip transition. It is also possible that the external vehicle torque is determined after a slip-stick transition.
- Tvehicie ⁇ vehicle 'J vehicle ⁇ si 8 n ( ⁇ eng ⁇ l' Vehicle) 'l A ' T clA ⁇ si 8 n ( ⁇ eng ⁇ ' Vehicle) "' T clB)
- afeng is the engine speed , ⁇ veh ⁇ cle ä ⁇ e
- downshift downshift with positive torque, which is transmitted from the engine to the output. As a result, the engine pulls the vehicle (e.g. kickdown).
- the engine torque to increase to form a slip reserve and to keep the engine speed above the speed of the old transmission input shaft associated with the starting gear.
- the old clutch assigned to the starting gear can be opened with a constant ramp function and the new clutch assigned to the target gear can be closed with the same ramp function, the engine torque being reduced to a minimum in order to increase the engine speed with the speed of the new transmission input shaft assigned to the target gear synchronize and wherein the torque of the electric motor is controlled such that the vehicle acceleration desired by the driver is achieved.
- a next embodiment of the invention can provide that the engine torque is reduced to a minimum in the case of an upshift in overrun mode or an overrun upshift in order to synchronize the engine speed with the speed of the new transmission input shaft. Then the vehicle acceleration can be controlled with the old clutch. If the engine speed drops below the speed of the new shaft, the old clutch can be opened with a constant ramp function and the new clutch can be closed. Finally, can the torque of the electric motor can be controlled such that the vehicle acceleration desired by the driver is achieved.
- the engine torque can be increased during a downshift in train operation or a downshift in order to synchronize the engine speed with the speed of the new transmission input shaft.
- Vehicle acceleration is controlled with the old clutch. If the engine speed rises above the speed of the new shaft, the old clutch can be opened with a constant ramp function and the new clutch can be closed. Finally, the moment of the electric motor is controlled in such a way that the vehicle acceleration desired by the driver is achieved.
- the engine torque can be reduced to a minimum in a downshift operation in overrun mode or in an overrun downshift, in order to form a slip reserve and to keep the engine speed below the speed of the old transmission input shaft.
- the engine torque can then be increased to synchronize the engine speed with the speed of the new transmission input shaft.
- the torque of the electric motor can be controlled in such a way that the vehicle acceleration desired by the driver is achieved.
- the aforementioned switching strategies for the individual circuit types can also be modified and combined with one another as desired in order to further improve the proposed method for performing a circuit, in particular with regard to the switching comfort.
- Figure 1 is a schematic model of a drive train of a vehicle with a dual clutch transmission
- Figure 2 is a simulation of a train upshift with electric motor support according to a method according to the invention
- Figure 3 is a simulation of a thrust upshift with electric motor support according to the inventive method
- Figure 4 is a simulation of a train downshift with electric motor support according to the inventive method
- Figure 5 is a simulation of a thrust downshift with electric motor support according to the inventive method
- FIG. 6 shows a flow diagram of the method according to the invention
- FIG. 7 shows a flow diagram of the control of the electric motor
- FIG. 8 shows a flow diagram of a possible train-push estimate
- Figure 9 is a flowchart of a possible estimate of an external
- FIG. 1 shows a schematic model of the drive train of a vehicle with a double clutch transmission.
- the method according to the invention is illustrated on the basis of the model.
- the model consists of an internal combustion engine with a torque that is equal to the moment of inertia J en g and a total engine torque T en g.
- the first transmission input shaft is connected to the engine via a first clutch, so that a maximum torque T C IA is transmitted can and is connected to the output shaft with a first gear with a ratio i A.
- the second transmission input shaft is also connected to the engine via a second clutch, so that a maximum torque T C IB is transmitted can and is also with the output shaft via a second gear with the
- Transmission input shaft is engaged via a gear ratio i ⁇ m .
- Output shaft or output shaft is connected to the motor by a moment of inertia
- Vehicle Jvehicie connected which is influenced by a driving resistance T v ⁇ hicie.
- the following simplifications are provided in the model:
- Gears on both transmission input shafts are preselected, i.e. no gear synchronization is simulated.
- the motor, the electric motor and the clutch dynamics are assumed to be linear and there is no dead time before the feedback. That the change in torque begins immediately after the request and with a constant defined ramp compared to the requested torque.
- the real dynamic behavior of the engine can have a significant effect on the shift strategy.
- FIGS. 2 to 5 show the method according to the invention and the shift strategy for different types of shift with the support of the electric motor. Three diagrams are shown one below the other, the upper diagram showing the speed of the engine, the first transmission input shaft and the second transmission input shaft as well as the clutch slip over time.
- the middle diagram shows the clutch torque T C ⁇ A of the first clutch, the clutch torque T C IB of the second clutch, the engine torque T en g and the torque T e m o tor of the electric motor over time, with different driving states 1 to 11 (driving state 1 "start”, driving state 2 “driving with shaft A”, driving state 3 "preparing upshift", driving state 4 "torque transmission to shaft B", driving state 5 “ending upshift”, driving state 6 “driving with shaft B”", Driving state 7” prepare for downshift ", driving state 8" torque transmission to shaft A “, driving state 9" end downshift ", driving state 10" idle “, Driving state 11 “Other”). While the speed of the vehicle and the vehicle acceleration are shown over time in the diagram below, it should be noted that the shift can be carried out more quickly if the torque ramp of the clutches and the engine are increased and the new clutch has a higher torque during phase 3.
- the torque of the old clutch is reduced to the slip limit and then the engine torque T en g is increased until the old clutch slips.
- the engine torque T ⁇ ng is controlled via the vehicle acceleration desired by the driver to ensure that the engine speed is kept above the speed of the old transmission input shaft.
- the torque transmitted by the old clutch is reduced to 0 via a constant ramp, while the torque transmitted by the new clutch is increased to the slip limit or slightly above with the same ramp.
- the torque T em o t or the electric motor is controlled such that the driver's desired vehicle acceleration is achieved. If the torque on the old disengaged clutch takes the value zero, the engine torque T en g is reduced to a minimum torque in order to accelerate the engine synchronization.
- the new clutch is activated up to or slightly above the slip limit, whereby the vehicle acceleration can be further regulated with the electric motor.
- the engine torque T en g is increased to just below the driver's desired engine torque in order to achieve a continuous smooth Reach slip transfer.
- the vehicle acceleration can then be controlled further with the electric motor.
- FIG. 3 shows a thrust upshift with the support of an electric motor in accordance with the proposed shift strategy. It should be noted that the peak in the course of the acceleration is a numerical effect of the simulation process and is therefore not to be expected in the vehicle.
- the thrust torque should be maintained at the output throughout the entire torque transmission from the old transmission input shaft to the new transmission input shaft. This is usually achieved by reducing the engine speed below the speed of the new transmission input shaft before torque transmission. Otherwise, opening the old clutch and closing the new clutch will increase vehicle acceleration. Em but with the support of the torque T otor the electric motor can be cast on the other hand, the torque transmission can be carried out before the engine speed is below the speed of the new transmission input shaft. In this case, the new clutch can support the synchronization of the engine speed and therefore speed up the shift significantly.
- the torque of the old clutch is reduced to the slip limit and then the engine torque T ⁇ ng is reduced until the old clutch slips.
- the engine torque T ⁇ n g is then reduced to a minimum, the transmitted torque of the old clutch being reduced to the value 0 via a constant ramp, while the transmitted torque of the new clutch is increased to the slip limit or slightly above with the same ramp, the moment T e mo t o . of the electric motor is controlled in such a way that the driver's desired vehicle acceleration is achieved.
- the new clutch is activated up to the slip limit or slightly above it, whereby the vehicle acceleration can be further regulated with the electric motor until engine synchronization is achieved.
- the engine torque T ⁇ n g is increased to just below the driver's desired engine torque in order to achieve a continuous slip- adhesion transition when the engine speed matches the speed of the new one Transmission input shaft is almost synchronized.
- the vehicle acceleration can then be controlled further with the electric motor.
- FIG. 4 shows the simulation of a train downshift with the support of the electric motor. It should be noted that the shift can be carried out more quickly if the torque ramp of the clutches and the motor are increased and the new clutch assumes a higher torque during phase 3.
- the pulling torque should be maintained at the output throughout the entire torque transmission from the old transmission input shaft to the new transmission input shaft. This is usually achieved by increasing the engine speed above the speed of the new transmission input shaft before torque transmission. Otherwise, opening the old clutch and closing the new clutch will reduce vehicle acceleration. However, with the support of the torque T emo tor of the electric motor can be acted against, the torque transmission can be carried out before the engine speed is above the speed of the new transmission input shaft. In this case, the new clutch can support the synchronization of the engine speed and therefore accelerate the shift significantly.
- the torque of the old clutch is reduced to the slip limit and then the engine torque T ⁇ n g is increased until the old clutch slips.
- the engine torque T en g is then controlled via the vehicle acceleration desired by the driver.
- the transmitted torque of the old clutch is reduced to 0 via a constant ramp, while the transmitted torque of the new clutch is increased to the slip limit or slightly above with the same ramp.
- the moment T emoto . of the electric motor is controlled in such a way that the driver's desired vehicle acceleration is achieved.
- the new clutch is activated up to the slip limit or slightly above it, whereby the vehicle acceleration can be further regulated with the electric motor until engine synchronization is achieved.
- the engine torque T en g is increased to just below the driver's desired engine torque in order to achieve a continuous slip-adhesion transition when the Engine speed is almost synchronized with the speed of the new transmission input shaft.
- the vehicle acceleration can then be controlled further with the electric motor.
- FIG. 5 shows a thrust downshift with the support of the electric motor. It should be noted that in this simulation, the electric motor only slightly supports the shifting process in order to achieve the desired vehicle acceleration, which consequently almost assumes the value zero. The first peak in vehicle acceleration is a numerical effect in the simulation.
- the thrust torque should be maintained at the output throughout the entire torque transmission from the old transmission input shaft to the new transmission input shaft. This is usually achieved by reducing the engine speed below the speed of the new transmission input shaft before torque transmission. In this situation, the old clutch is opened to increase vehicle acceleration and the new clutch is closed to reduce vehicle acceleration. These reactions can cancel each other out.
- the torque Temo to r of the electric motor is used to adjust the vehicle acceleration and to control.
- the torque of the old clutch is reduced to the slip limit and then the engine torque T en g is reduced until the old clutch slips.
- the engine torque T en g is then reduced to a minimum, the transmitted torque of the old clutch being reduced to the value 0 via a constant ramp, while the transmitted torque of the new clutch is increased to the slip limit or slightly above with the same ramp, where the moment T ⁇ mot o . of the electric motor is controlled in such a way that the driver's desired vehicle acceleration is achieved.
- the engine torque T eng is increased to be sufficiently above the driver's desired engine torque so that the engine synchronization is accelerated.
- the new clutch is activated up to or slightly above the slip limit, whereby the vehicle acceleration can be further regulated with the electric motor. If the Engine speed is nearly synchronized with the speed of the new transmission input shaft, the engine torque T eng is increased to just above the driver's desired engine torque to provide a continuous smooth slip to achieve adhesion transition. The vehicle acceleration can then be controlled further with the electric motor.
- FIG. 6 shows a flowchart of the method according to the invention for performing a shift in a double clutch transmission (shift strategy) for upshifts, overruns, downshifts and / or downshifts.
- the shift strategy suggests comfortable shifting, in particular with an ESG transmission, with and without the support of an electric motor.
- a control strategy for changing gear ratios is therefore preferably presented in an ESG dual clutch transmission.
- the aim of this strategy is to control the output torque or vehicle acceleration in order to carry out a comfortable overlap shift.
- the primary control means can be the electric motor. If the torque T emo t o r of the electric motor is not large enough, one of the clutches or the like can also be used to control the output torque.
- this control strategy defines four different types of overlap shifts, namely train upshifts, thrust upshifts, train downshifts and push downshifts. All these types of switching can be carried out with minimal jerk and high comfort, with a sufficient torque T ⁇ mot o . is provided by the electric motor or by the internal combustion engine. The upshifts and the downshifts can be carried out much faster and more comfortably when using the electric motor. Switching strategies with the electric motor are also possible, which reduce the energy input in the clutches in order to minimize the heat load and wear.
- the engine torque T en g is increased to form a slip reserve and the engine speed is greater than the speed of the old one Gearbox input shaft held. Then the old clutch is opened with a constant ramp function and the new clutch is closed with the same ramp function. The engine torque T en g is reduced to a minimum in order to synchronize the engine speed with the speed of the new transmission input shaft assigned to the target gear.
- the torque T e m oto r of the electric motor is controlled in such a way that the vehicle acceleration desired by the driver is achieved.
- the engine torque T is close to a minimum, in order to synchronize the engine speed with the speed of the new transmission input shaft. Then the vehicle acceleration is controlled with the old clutch. When the engine speed drops below the speed of the new shaft, the old clutch is opened with a constant ramp function and the new clutch is closed. Finally, the torque T em o t or the electric motor is driven such that the desired vehicle acceleration by the driver is achieved.
- the engine torque T ⁇ ng is increased in order to synchronize the engine speed with the speed of the new transmission input shaft. Then the vehicle acceleration is controlled with the old clutch. When the engine speed rises above the speed of the new shaft, the old clutch is opened with a constant ramp function and the new clutch is closed.
- the torque T e mo t or of the electric motor is controlled such that the vehicle acceleration desired by the driver is achieved.
- the engine torque T en g is reduced to a minimum in order to form a slip reserve and to keep the engine speed below the speed of the old transmission input shaft. Then the old clutch is opened with a constant ramp function and the new clutch is closed with the same ramp function. The engine torque T ⁇ n g is increased in order to synchronize the engine speed with the speed of the new transmission input shaft. The moment of the Electric motors are controlled in such a way that the vehicle acceleration desired by the driver is achieved.
- FIG. 7 shows a flow chart for the torque control of the electric motor.
- the torque T ⁇ mot or of the electric motor is used as an additional torque to achieve the vehicle acceleration desired by the driver (box 101).
- the required vehicle acceleration (box 102) is determined in dependence on certain vehicle and / or transmission parameters (box 103).
- vehicle and / or transmission sizes for. B. the gear ratio on the transmission input shafts, the engine speed, the vehicle speed and the vehicle acceleration can be used.
- the external vehicle torque T is then determined vehicularly (box 104) and then a target torque of the electric motor is calculated as a function of vehicle and / or transmission sizes (106) (box 105).
- vehicle and / or transmission sizes for. B.
- FIG. 8 shows a flow diagram which clarifies the pull-push estimate used in the method according to the invention.
- Dual clutch transmission is in train operation when the entered
- Engine torque T narrow is greater than the dynamic engine torque ⁇ narrow ⁇ J narrow .
- Thrust operation is when the entered engine torque T en g is less than the dynamic engine torque ⁇ mg • en .
- the pull / push condition is defined by the fact that the sum of the transmitted coupling torques is positive (pull condition) or negative (push condition).
- FIG. 9 shows a flow diagram of the estimation of the external vehicle torque. Three different methods are presented in it.
- the external vehicle torque Tv e hicie can be determined from the following equation:
- the external vehicle torque can be calculated from the following equation:
- ⁇ -feng is the engine speed , ⁇ vehwle d ⁇ e
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Transmission Device (AREA)
- Hybrid Electric Vehicles (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
Claims
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/DE2003/000645 WO2003074312A2 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe |
EP03743291A EP1485270A2 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe |
KR10-2004-7013884A KR20040098659A (ko) | 2002-03-07 | 2003-02-28 | 트윈클러치기어박스에서 기어단수변속의 실시 방법 |
JP2003572799A JP4286149B2 (ja) | 2002-03-07 | 2003-02-28 | ツインクラッチ式トランスミッションにおけるギアシフト実施方法 |
AU2003227013A AU2003227013A1 (en) | 2002-03-07 | 2003-02-28 | Method for carrying out gear shifting in a twin-clutch gearbox |
DE10390836T DE10390836D2 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum Durchführen einer Schaltung bei einem Doppelkupplungsgetriebe |
DE10308692A DE10308692A1 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum Durchführen einer Schaltung bei einem Doppelkupplungsgetriebe |
FR0302760A FR2837257A1 (fr) | 2002-03-07 | 2003-03-06 | Procede pour la realisation d'un changement de vitesse dans une boite de vitesses a double embrayage |
US10/711,245 US7094176B2 (en) | 2002-03-07 | 2004-09-03 | Method for carrying out gear shifting in a twin-clutch gearbox |
Applications Claiming Priority (16)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10209917 | 2002-03-07 | ||
DE10209917.0 | 2002-03-07 | ||
DE10308719A DE10308719A1 (de) | 2002-03-07 | 2003-02-28 | Steuereinrichtung und Verfahren zum Positionsabgleich in einer Bewegungsübertragung |
DE10308712.5A DE10308712B4 (de) | 2002-03-07 | 2003-02-28 | Fahrzeug mit einem Antriebsstrang und Verfahren zum Regeln des Antriebsstranges eines Fahrzeuges |
DE10308713.3A DE10308713B4 (de) | 2002-03-07 | 2003-02-28 | Doppelkupplungsgetriebe und Verfahren zum Steuern und/oder Regeln eines Doppelkupplungsgetriebes bei einer Überschneidungsschaltung |
DE10308714A DE10308714A1 (de) | 2002-03-07 | 2003-02-28 | Doppelkupplungsgetriebe und Verfahren zum Steuern von wenigstens zwei Kupplungen bei einem Doppelkupplungsgetriebe eines Fahrzeuges |
DE10308716A DE10308716A1 (de) | 2002-03-07 | 2003-02-28 | Verfahren zur Anpassung der Kupplungskennlinien in einem Doppelkuppllungssystem |
DE10308690A DE10308690A1 (de) | 2002-03-07 | 2003-02-28 | Getriebe und Schaltstrategie für ein Getriebe, insbesondere für ein Doppelkupplungsgetriebe, eines Fahrzeuges |
DE10308689A DE10308689A1 (de) | 2002-03-07 | 2003-02-28 | Doppelkupplungsgetriebe und Verfahren zum Durchführen einer Schaltung bei einem Doppelkupplungsgetriebe |
PCT/DE2003/000645 WO2003074312A2 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe |
DE10308691A DE10308691A1 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum Auswählen eines Ganges eines nicht aktiven Teilgetriebes eines Doppelkupplungssystems |
DE10308700.1A DE10308700B4 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum Durchführen einer Hochschaltung von einem Anfangsgang in einen Zielgang bei dem Doppelkupplungsgetriebe eines Fahrzeuges |
DE10308697A DE10308697A1 (de) | 2002-03-07 | 2003-02-28 | Doppelkupplungsgetriebe und Verfahren zum Durchführen einer Schaltung bei einem Doppelkupplungsgetriebe |
DE10308748A DE10308748A1 (de) | 2002-03-07 | 2003-02-28 | Verfahren, Vorrichtung und deren Verwendung zum Betrieb eines Kraftfahrzeuges, insbesondere zur Ansteuerung eines Parallelschaltgetriebes |
DE10308699A DE10308699A1 (de) | 2002-03-07 | 2003-02-28 | Getriebe und Verfahren zum Ansteuern eines Kriechmomentes bei einem automatischen Getriebe eines Fahrzeuges |
DE10308698A DE10308698A1 (de) | 2002-03-07 | 2003-02-28 | Getriebe und Anfahrstrategie für ein Getriebe, insbesondere für ein Doppelkupplungsgetriebe, eines Fahrzeuges |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/711,245 Continuation US7094176B2 (en) | 2002-03-07 | 2004-09-03 | Method for carrying out gear shifting in a twin-clutch gearbox |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2003074312A2 true WO2003074312A2 (de) | 2003-09-12 |
WO2003074312A3 WO2003074312A3 (de) | 2004-02-26 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2003/000645 WO2003074312A2 (de) | 2002-03-07 | 2003-02-28 | Verfahren zum durchführen einer schaltung bei einem doppelkupplungsgetriebe |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1485270A2 (de) |
AU (1) | AU2003227013A1 (de) |
DE (2) | DE10308692A1 (de) |
FR (1) | FR2837257A1 (de) |
WO (1) | WO2003074312A2 (de) |
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JP2005214417A (ja) * | 2004-01-27 | 2005-08-11 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | パラレルシフト伝動装置をアップシフトする方法 |
JP2005226836A (ja) * | 2004-02-13 | 2005-08-25 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | ギアチェンジを制御する方法およびギアチェンジを制御する装置 |
WO2005080830A3 (de) * | 2004-02-17 | 2006-03-02 | Volkswagen Ag | Verfahren zur betätigung mindestens zweier parallel im antriebsstrang eines kraftfahrzeugs drehmomentübertragenden kupplungen und getriebesteuerung |
CN102007028A (zh) * | 2008-04-14 | 2011-04-06 | 罗伯特.博世有限公司 | 混合驱动装置中的离合器的滑转运行 |
KR101510015B1 (ko) * | 2013-12-18 | 2015-04-07 | 현대자동차주식회사 | Dct 차량의 변속 제어 방법 |
KR20150139719A (ko) * | 2014-06-03 | 2015-12-14 | 현대자동차주식회사 | Amt의 변속 제어방법 및 장치 |
US9341260B2 (en) | 2014-05-21 | 2016-05-17 | Hyundai Motor Company | Shift control method for DCT vehicle |
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EP1950462B1 (de) * | 2007-01-24 | 2010-08-25 | Getrag Ford Transmissions GmbH | Verfahren zum Betrieb einer ein Schaltgetriebe und einen Motor umfassenden Antriebseinheit |
US7985163B2 (en) * | 2007-12-13 | 2011-07-26 | Ford Global Technologies, Llc | Adaptive clutch torque control for a powershift transmission |
FR2961772B1 (fr) * | 2010-06-23 | 2013-03-15 | Peugeot Citroen Automobiles Sa | Procede de changement de rapport de vitesse montant sous couple avec detection des jeux de boite de vitesses |
DE102010061823B4 (de) | 2010-11-24 | 2020-02-13 | Zf Friedrichshafen Ag | Verfahren zum Betreiben eines Antriebsstrangs |
DE102010053624A1 (de) * | 2010-12-07 | 2012-06-14 | Sew-Eurodrive Gmbh & Co. Kg | Fahrzeug und Verfahren zum Betreiben eines Fahrzeugs |
DE102011077125A1 (de) * | 2011-06-07 | 2012-12-13 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Antriebsvorrichtung sowie Vorrichtung zum Betreiben der Antriebsvorrichtung |
WO2013000450A1 (de) | 2011-06-30 | 2013-01-03 | Schaeffler Technologies AG & Co. KG | Verfahren zur steuerung einer doppelkupplung in einem doppelkupplungsgetriebe |
JP5902423B2 (ja) * | 2011-09-20 | 2016-04-13 | アイシン・エーアイ株式会社 | 車両の動力伝達制御装置 |
EP2765049B1 (de) * | 2011-10-07 | 2020-12-02 | Yamaha Hatsudoki Kabushiki Kaisha | Fahrzeugsteuerungsvorrichtung, fahrzeug und motor |
US9017217B2 (en) | 2012-11-08 | 2015-04-28 | Ford Global Technologies, Llc | Pilot downshifting system and method |
JP6288048B2 (ja) | 2015-11-19 | 2018-03-07 | トヨタ自動車株式会社 | 自動変速機の変速制御装置 |
EP3791083B1 (de) * | 2018-05-08 | 2022-03-09 | GKN Automotive Ltd. | Verfahren zur steuerung eines aktuators einer aktuatoreinrichtung eines kraftfahrzeuges |
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2003
- 2003-02-28 DE DE10308692A patent/DE10308692A1/de not_active Withdrawn
- 2003-02-28 WO PCT/DE2003/000645 patent/WO2003074312A2/de active Application Filing
- 2003-02-28 DE DE10390836T patent/DE10390836D2/de not_active Expired - Fee Related
- 2003-02-28 EP EP03743291A patent/EP1485270A2/de not_active Withdrawn
- 2003-02-28 AU AU2003227013A patent/AU2003227013A1/en not_active Abandoned
- 2003-03-06 FR FR0302760A patent/FR2837257A1/fr active Pending
Patent Citations (3)
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DE4333899A1 (de) * | 1993-10-05 | 1995-07-13 | Bosch Gmbh Robert | Verfahren zur Steuerung des Abtriebsmoments eines automatischen Schaltgetriebes |
US20010022245A1 (en) * | 1998-10-02 | 2001-09-20 | Luk Lamellen Und Kupplungsbau Gmbh | Motor vehicle |
DE19939334A1 (de) * | 1999-08-19 | 2001-03-08 | Daimler Chrysler Ag | Verfahren zum Schalten eines Doppelkupplungsgetriebes und Doppelkupplungsgetriebe |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005214417A (ja) * | 2004-01-27 | 2005-08-11 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | パラレルシフト伝動装置をアップシフトする方法 |
JP2005226836A (ja) * | 2004-02-13 | 2005-08-25 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | ギアチェンジを制御する方法およびギアチェンジを制御する装置 |
WO2005080830A3 (de) * | 2004-02-17 | 2006-03-02 | Volkswagen Ag | Verfahren zur betätigung mindestens zweier parallel im antriebsstrang eines kraftfahrzeugs drehmomentübertragenden kupplungen und getriebesteuerung |
JP2007522397A (ja) * | 2004-02-17 | 2007-08-09 | フオルクスワーゲン・アクチエンゲゼルシヤフト | 自動車の駆動歯車列においてトルク伝動する少なくとも二つの並列なクラッチを作動する方法と伝動装置制御部 |
US7488272B2 (en) | 2004-02-17 | 2009-02-10 | Volkswagen Ag | Method for the actuation of at least two clutches transmitting torque in parallel in the drive train of a motor vehicle and transmission control unit |
US8494739B2 (en) | 2008-04-14 | 2013-07-23 | Robert Bosch Gmbh | Slip operation of a clutch in hybrid drive devices |
CN102007028A (zh) * | 2008-04-14 | 2011-04-06 | 罗伯特.博世有限公司 | 混合驱动装置中的离合器的滑转运行 |
CN102007028B (zh) * | 2008-04-14 | 2014-10-15 | 罗伯特.博世有限公司 | 混合驱动装置中的离合器的滑转运行 |
KR101510015B1 (ko) * | 2013-12-18 | 2015-04-07 | 현대자동차주식회사 | Dct 차량의 변속 제어 방법 |
DE102014114879B4 (de) | 2013-12-18 | 2023-01-26 | Hyundai Motor Company | Schaltsteuerverfahren in einem Doppelkupplungsgetriebe-Fahrzeug |
US9341260B2 (en) | 2014-05-21 | 2016-05-17 | Hyundai Motor Company | Shift control method for DCT vehicle |
KR20150139719A (ko) * | 2014-06-03 | 2015-12-14 | 현대자동차주식회사 | Amt의 변속 제어방법 및 장치 |
KR101664545B1 (ko) | 2014-06-03 | 2016-10-11 | 현대자동차주식회사 | Amt의 변속 제어방법 및 장치 |
Also Published As
Publication number | Publication date |
---|---|
FR2837257A1 (fr) | 2003-09-19 |
DE10308692A1 (de) | 2003-09-18 |
DE10390836D2 (de) | 2005-02-10 |
AU2003227013A1 (en) | 2003-09-16 |
WO2003074312A3 (de) | 2004-02-26 |
EP1485270A2 (de) | 2004-12-15 |
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