WO2002070923A2 - Verfahren zum steuern und/oder regeln eines automatisierten getriebes eines fahrzeuges - Google Patents
Verfahren zum steuern und/oder regeln eines automatisierten getriebes eines fahrzeuges Download PDFInfo
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- WO2002070923A2 WO2002070923A2 PCT/DE2002/000786 DE0200786W WO02070923A2 WO 2002070923 A2 WO2002070923 A2 WO 2002070923A2 DE 0200786 W DE0200786 W DE 0200786W WO 02070923 A2 WO02070923 A2 WO 02070923A2
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- torque
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- 238000000034 method Methods 0.000 title claims abstract description 106
- 230000001276 controlling effect Effects 0.000 title claims abstract description 8
- 230000001105 regulatory effect Effects 0.000 title claims abstract description 8
- 238000010168 coupling process Methods 0.000 claims abstract description 11
- 230000005540 biological transmission Effects 0.000 claims description 50
- 230000008569 process Effects 0.000 claims description 29
- 230000001419 dependent effect Effects 0.000 claims description 19
- 230000008859 change Effects 0.000 claims description 11
- 230000007935 neutral effect Effects 0.000 claims description 4
- 230000003111 delayed effect Effects 0.000 claims description 3
- 230000001360 synchronised effect Effects 0.000 claims description 3
- 238000001514 detection method Methods 0.000 claims description 2
- 230000005021 gait Effects 0.000 claims 2
- 230000008878 coupling Effects 0.000 abstract description 4
- 238000005859 coupling reaction Methods 0.000 abstract description 4
- 238000011161 development Methods 0.000 description 15
- 238000010586 diagram Methods 0.000 description 11
- 230000008901 benefit Effects 0.000 description 4
- 230000007704 transition Effects 0.000 description 4
- 238000004088 simulation Methods 0.000 description 3
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- 238000006243 chemical reaction Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
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- 230000036461 convulsion Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
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- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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
- 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
- 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
-
- 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
-
- 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
-
- 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
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/11—Stepped 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
- 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
-
- 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
- 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
- B60W2510/06—Combustion engines, Gas turbines
- B60W2510/0638—Engine speed
-
- 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
- B60W2510/10—Change speed gearings
- B60W2510/1005—Transmission ratio engaged
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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
- B60W2510/10—Change speed gearings
- B60W2510/1015—Input shaft speed, e.g. turbine speed
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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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/02—Clutches
- B60W2710/021—Clutch engagement state
- B60W2710/023—Clutch engagement rate
-
- 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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/02—Clutches
- B60W2710/027—Clutch torque
-
- 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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
- B60W2710/0644—Engine speed
-
- 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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
- B60W2710/0666—Engine torque
-
- 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
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
- B60W2710/0666—Engine torque
- B60W2710/0672—Torque change rate
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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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
- F16H63/50—Signals to an engine or motor
- F16H2063/506—Signals to an engine or motor for engine torque resume after shift transition, e.g. a resume adapted to the driving style
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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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
- F16H63/50—Signals to an engine or motor
- F16H63/502—Signals to an engine or motor for smoothing gear shifts
Definitions
- the invention relates to a method for controlling and / or regulating an automated transmission of a vehicle, in particular a motor vehicle, with which an engagement process is carried out when changing gear.
- Automated transmissions are known from vehicle technology, thereby enabling automation of the drive train of a vehicle, in particular a motor vehicle. It is also known that automated clutches are used in a transmission. In the known method for controlling and / or regulating the automated transmission, in particular a clutch engagement process is automated when a desired gear change is carried out.
- the invention has for its object to provide a method for controlling and / or regulating the automated transmission, which is further improved in particular with regard to comfort and speed aspects.
- this can, for. B. can be achieved by appropriately specifying the engine torque during the gear change.
- the engine torque at the beginning of the gear change can be reduced in good time when disengaging and can be built up again at the same time as the clutch is engaged after the gear change.
- the torque intervention in the engine torque can preferably be carried out during pull switching operations.
- the torque intervention can also be provided for other types of switching operations.
- the course of the engine torque has at least one section during the torque intervention.
- the course of the engine torque during the engagement process can be specified by means of a straight line with a variable gradient. Since the engine follows the specification only slowly at the beginning, the straight line can be started at a relatively high starting value, thus forcing the engine control to start quickly.
- the course of the engine torque is broken down into two sections of different incline and / or different curve shape. This means that the demands for a rapid increase in engine torque at the start of the engagement process and for a gentler increase in the further course of the Engine torque are met.
- a jump in the course of the engine torque can be avoided, which z. B. positively influences the consumption and the emission of the engine.
- the engine torque curve is broken down into several sections, there are a multitude of options for achieving a comfortable engine torque build-up using the method according to the invention.
- a development of the invention can provide that the course of the engine torque is broken down into two sections, e.g. an e-function can be combined with a ramp-like function. Another possibility is that the course of the engine torque is specified by an e-function and a straight line with a minimum gradient. Of course, other suitable curves of the engine torque are also possible. For example, the course of the engine torque can also be broken down into more than two sections, so that the engagement process is further optimized with regard to comfort and speed using the method according to the invention.
- Another embodiment of the invention provides that the clutch torque is specified independently of the actual engine torque in the method according to the invention.
- Different strategies can be followed to match crankshaft and transmission input shaft speed. For example, a speed adjustment can be achieved in particular in downshifts by increasing the engine power to increase the speed and in particular in upshifts by increasing the negative crankshaft torque to increase the deceleration.
- a step-by-step specification of the full clutch minimum torque and / or a switchover of the setpoint specification of the motor from the speed to the torque control is provided. This can be carried out in particular when the slip between the transmission input shaft and the crankshaft falls below a predetermined maximum slip threshold and / or the respective gear is detected.
- the measures mentioned can be combined with one another either as an alternative or as desired. Of course, other conditions can also be taken into account in the aforementioned strategy of the method according to the invention.
- the engine is firmly connected to the drive train in the method according to the invention.
- the gradient of the deceleration of the vehicle can increase significantly in the further course. This reaction is particularly desirable for sporty drivers.
- the engine torque specification can be ended by the transmission control of the automated transmission if, for. B. the torque specification corresponds to a driver's desired torque. Of course, other suitable sizes can also be taken into account.
- Another development of the invention provides that, in another strategy, the control of the motor is maintained via the target speed specification and / or an abrupt specification of a minimum torque is provided on the clutch. This is realized in particular when the slip between the transmission input shaft and the crankshaft falls below a predetermined maximum slip threshold and the gear is recognized.
- the measures mentioned can be combined with one another as an alternative or as desired. Of course, other conditions can also be taken into account in the aforementioned strategy of the method according to the invention.
- the target engine speed is tracked according to a changing actual speed of the transmission input shaft.
- After reaching the target clutch torque can be changed to a torque specification and the engine torque z. B. linear or parabolic or the like to the driver's desired torque.
- the clutch target torque can, for example, correspond to the minimum clutch torque, a drag torque or a multiple or fraction of these moments.
- the engine torque can e.g. B. in train circuits to the driver's desired torque and z. B. can be reduced to the driver's desired torque at overrun.
- the torque can be set by the transmission control, for example. Reaching the driver's desired torque can be ended again.
- Another development of the invention can provide that, as a further strategy, the clutch is closed after the detection of neutral except for a clutch minimum torque and / or the engine speed is controlled via the target speed setting to a gearbox input shaft target speed and / or an abrupt course a minimum clutch torque is specified while maintaining the speed specification for the motor. This is used in particular when the slip between the transmission input shaft and the crankshaft falls below a maximum slip threshold and the gear is recognized.
- the measures mentioned can be combined with one another as an alternative or as desired. Of course, other conditions can also be taken into account in the aforementioned strategy of the method according to the invention.
- the clutch can already be at neutral up to a minimum torque, which, for. B. is provided as a touch point or small moment.
- the transmission input shaft can be brought to a desired transmission input shaft target speed not only by the synchronization, but also by the motor.
- This has the advantage that both the synchronization work and the synchronization time are reduced during the synchronization, but the switching speed is advantageously increased in the method according to the invention.
- the clutch is closed prematurely, which, for. B.
- the clutch is fully or partially opened again before reaching the transmission input shaft target speed, so that the residual synchronization work completely or at least mostly through the transmission synchronization can be provided.
- the clutch torque is set as a function of the actual engine torque and / or the current slip and other parameters dependent on the shifting type during the engagement process.
- the circuit type-dependent parameters serve to differentiate between upshift, downshift, push and pull shifts.
- the actual engine torque can be influenced by a specification of the target engine torque by the transmission control, so that the smoothest possible smooth smoothing of engine speed and transmission speed is achieved during the transition of the clutch from sliding to holding state.
- the target speed and / or the target torque can be specified. After the engine speed has increased to the gearbox input speed, it can be switched to engine target torque control while the torque is being established when the gear is detected. For example, in the case of a thrust shift, the engine torque can drop to the thrust torque. After there was no slip on the clutch before, the engine drag torque can increase the slip on the clutch again, because the clutch is slowly closed depending on engine torque and slip.
- This embodiment of the method according to the invention can be used in particular in all vehicles with a multi-step transmission in which the engine speed is raised or lowered during a shift. If no engine speed interface is available for these vehicles, an increase or decrease in speed can also be achieved by specifying positive or negative drive torques. It is also possible that these measures are related be combined. Of course, the method according to the invention can also be used
- Vehicles with other transmission systems are used.
- Another embodiment of the invention can provide that the engaging process is delayed when a desired gear change, ie the clutch can, for. B. be closed according to a ramp-shaped function as soon as z. B. the engine speed is greater than the transmission input speed. This can be provided in particular for train downshifts.
- the increase can be carried out via a global control, for example with the factors Kn and K 22 .
- the desired clutch torque can preferably be determined using the following equation:
- the build-up of the clutch torque is carried out both via the factors Kn and / or K 22 and also directly z.
- B. is gradient limited. The aim here is that the clutch torque is initially built up as quickly as possible, but at the end of the torque build-up, the gradient of the clutch torque is not chosen too high, so that there is no discontinuity in the course of the actual clutch torque.
- this can be achieved by building up the desired clutch torque, which for example essentially follows an e-function.
- This has the advantage that the set-up initially takes place suddenly and relatively moderately at the end before the maximum value is reached. The clutch torque is thus built up quickly and discontinuity in the course of the clutch torque is avoided.
- Another further development can provide that the clutch torque is built up according to a ramp-shaped function and / or combined with a suitable offset.
- the offset can e.g. B. constant, gear dependent, pedal value dependent, pedal value gradient dependent, engine speed dependent, gear speed dependent and / or depending on the gradient of the engine speed.
- other suitable variables can also be used, which can influence the offset in the method according to the invention.
- Another development of the invention can provide that when the clutch torque is built up, an early clutch engagement is carried out, ie before the engine speed exceeds the transmission speed and the synchronization point is reached.
- One can determine, for example, from gear information whether it is an upshift or downshift. For example, in the case of very strong downshifts (e.g. voiload shifts), this information, depending on the pedal value, the pedal value gradient, the engine speed and / or the engine speed gradient, can be used to start building up the clutch torque as soon as the gear is engaged and the pedal is operated.
- the coupling or the coupling process can be made more comfortable.
- the clutch is initially only closed to the extent that the motor accelerates and the synchronization point can be reached. This can e.g. B. can be achieved that the clutch setpoint torque at the synchronizing point is initially built up with a ramp with a small gradient and after reaching the synchronizing point with a ramp with a larger gradient.
- the structure of the clutch torque is predetermined as a function of the slip.
- the slope of the course of the clutch torque can be changed accordingly. It is Z. B. possible that the build-up of the clutch torque begins when a predetermined negative slip is reached before the synchronization point. Furthermore, it is conceivable that the build-up of the clutch torque is accelerated if a predetermined positive slip limit is exceeded after the synchronous point.
- suitable combinations of the abovementioned possibilities for building up the clutch torque can also be used in order to further optimize the method according to the invention.
- This embodiment of the method according to the invention can be used in all automated manual transmissions as well as in automated clutches with an electronic clutch management.
- Another embodiment of the invention can provide that the torque intervention specifies both the clutch torque and the engine torque during the engagement process during a gear change.
- the comfort according to the invention can be improved and the speed can be further increased when changing gear.
- the interruption of the power transmission can advantageously be ended by the reconstruction of the engine and clutch torque and the speed difference between the engine and the transmission speed can be reduced. This means that the slip is also reduced. It should be noted that when a speed equality is reached, the gradients from the engine and the gearbox speed should be as large as possible to avoid a jerk at the transition from
- the clutch torque should be greater than the engine torque in order to reach the state of detention. Since only the clutch torque is responsible for the vehicle acceleration during the slip phase, the course of the clutch torque can therefore be as steady or smooth as possible and discontinuities can be avoided in an advantageous manner. In vehicles with E-gas, the engine torque could also be brought up to the torque desired by the driver.
- both the clutch torque and the engine torque are used as manipulated variables.
- This can e.g. B. can be provided by a multi-size control.
- a z. B. simultaneous specification of a desired slip value and / or a desired engine torque and / or a clutch torque the engagement process can be further optimized in the method according to the invention.
- a slip control can be combined with a torque control in this embodiment of the invention.
- the aforementioned types of regulation can also be used separately or combined or combined with other suitable regulations.
- FIG. 1 shows different profiles of a given engine torque over time
- FIG. 2 curves of the actual engine speed and the desired engine speed as well as the desired clutch torque during an engagement process according to a first engagement strategy
- FIG. 3 curves of the actual engine speed and the desired engine speed as well as the desired clutch torque during an engagement process according to a second engagement strategy
- FIG. 4 curves of the actual engine speed and the desired engine speed as well as the desired clutch torque during an engagement process according to a third engagement strategy
- Figure 5 curves of the actual engine speed and the target engine speed and the target clutch torque during a clutch-in process according to a fourth clutch strategy
- FIG. 6 curves of different engine and transmission parameters in the simulation of a coupling process.
- Various curves of the engine torque during a coupling process are shown in FIG.
- the course 1 shows the specified engine torque, in which a step function is combined with a ramp function.
- the specified engine torque is broken down into two sections, the jump function being provided in order to initially build the engine torque to 20 Nm. Then the motor torque is increased with the ramp function to a final value which is around 60 Nm.
- the course 2 shows the predetermined engine torque, the course 2 being broken down into two sections.
- the course of the engine torque is influenced by an e-function. From a value of approximately 20 Nm of engine torque, a ramp-like function follows as a second section. The ramp-like function increases the engine torque to a maximum of 60 Nm.
- the course 3 shows the specified engine torque, which is also broken down into two sections.
- the engine torque is influenced by an e-function and then ends with a minimum gradient at a maximum value of the engine torque of 60 Nm.
- FIGS. 2 to 5 each show the curves of the actual engine speed and the desired engine speed as well as the desired clutch torque during an engagement process in accordance with various engagement strategies.
- the course 4 in FIGS. 2 to 5 represents the actual engine speed and the course 5 each represents the target engine speed during a clutch engagement process.
- the course 6 of the target clutch torque corresponds to a clutch engagement strategy with a ramp-shaped function.
- the course 7 of the target clutch torque essentially follows an e-function. This has the advantage that the structure is initially abrupt and relatively gentle at the end of the coupling process, that is before the maximum value is reached expires. Thus, the clutch torque is built up quickly and discontinuities in the course are avoided.
- FIG. 3 shows the ramp-shaped profile 6 of the desired clutch torque.
- the course 8 of the target clutch torque follows a ramp-shaped function which is combined with an offset. As shown in FIG. 3, this offset can be chosen to be constant. But it is also possible that it is dependent on suitable signals.
- FIG. 4 shows the course 9 of the desired clutch torque, in which two ramp-shaped functions are combined with one another, which have different slopes. Furthermore, the course 10 of the engine torque is shown. The transition between the two ramp-shaped functions of the course 9 of the target clutch torque takes place in FIG. 4 when the clutch torque is greater than the engine torque.
- the slopes of the ramp-shaped function are chosen to be constant in FIG. Of course, they can also depend on one or more signals.
- FIG. 5 again shows two diagrams, the curves 4.5 of the actual engine speed and the target engine speed over time being shown in a first diagram and the curves 11, 12 of the target clutch torques of different engagement strategies being shown in the second diagram. It is clear from FIG. 5 that the courses 11, 12 of the desired clutch torque are shown as a function of the slip, which is indicated in the upper diagram.
- the build-up of the clutch torque is started if a certain negative slip ⁇ n1 has been reached before the synchronous point in time 13.
- the build-up of the clutch torque after the synchronization point 13 is accelerated if there is a predetermined positive slip ⁇ n2 after the synchronization point 13.
- a simulation of a coupling process is shown in FIG. 6 with the aid of several diagrams. In the first diagram 101, the target slip dn SO ⁇ and the actual slip dn is shown over time. This represents the slip control in the method according to the invention.
- the second diagram 102 shows an engine torque control of the method according to the invention, in which the driver's desired torque Mmot so n and the actual engine torque Mmotis t are shown over time.
- Diagram 103 shows the speeds during the engagement process.
- the engine speed is designated n mot and the transmission speed n get and is shown over time.
- the fourth diagram 104 shows the torques during a clutch engagement process.
- the friction torque of a clutch is designated with M R and the actual engine torque with Mmotj St and is shown over time.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Transportation (AREA)
- Automation & Control Theory (AREA)
- Control Of Transmission Device (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2003-7011525A KR20030080059A (ko) | 2001-03-07 | 2002-03-04 | 차량의 자동 트랜스미션을 제어 및/또는 조정하기 위한 방법 |
AU2002252955A AU2002252955A1 (en) | 2001-03-07 | 2002-03-04 | Method for controlling and/or regulating an automatic gearbox in a vehicle |
DE10290843.5T DE10290843B4 (de) | 2001-03-07 | 2002-03-04 | Verfahren zum Steuern und/oder Regeln eines automatisierten Getriebes eines Fahrzeuges mit dem ein Einkuppelvorgang bei einem Gangwechsel durchgeführt wird |
BR0207934-8A BR0207934A (pt) | 2001-03-07 | 2002-03-04 | Processo para o controle e/ou a regulaegm de uma caixa de câmbio automatizada de um veìculo |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10111007.3 | 2001-03-07 | ||
DE10111007 | 2001-03-07 |
Publications (2)
Publication Number | Publication Date |
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WO2002070923A2 true WO2002070923A2 (de) | 2002-09-12 |
WO2002070923A3 WO2002070923A3 (de) | 2003-01-03 |
Family
ID=7676637
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2002/000786 WO2002070923A2 (de) | 2001-03-07 | 2002-03-04 | Verfahren zum steuern und/oder regeln eines automatisierten getriebes eines fahrzeuges |
Country Status (7)
Country | Link |
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KR (1) | KR20030080059A (de) |
AU (1) | AU2002252955A1 (de) |
BR (1) | BR0207934A (de) |
DE (2) | DE10290843B4 (de) |
FR (1) | FR2822111B1 (de) |
IT (1) | ITMI20020479A1 (de) |
WO (1) | WO2002070923A2 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1747958A1 (de) * | 2005-07-26 | 2007-01-31 | Nissan Motor Company, Limited | Drehzahlbegrezung eines Verbrennungsmotors beim Gangwechsel |
DE102006003724A1 (de) * | 2006-01-26 | 2007-08-02 | Zf Friedrichshafen Ag | Verfahren zur Steuerung eines Kraftfahrzeug-Antriebsstrangs |
KR100849568B1 (ko) | 2005-07-26 | 2008-07-31 | 닛산 지도우샤 가부시키가이샤 | 엔진의 과회전 방지 장치 및 엔진의 과회전 방지 방법 |
EP2987695A1 (de) * | 2014-08-18 | 2016-02-24 | Scania CV AB | Drehmomentsteuerung für einen verbrennungsmotor |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10256360B4 (de) | 2002-12-03 | 2018-03-29 | Volkswagen Ag | Verfahren und Vorrichtung zur Überwachung positiver Momenteneingriffe in einem Motorsteuergerät |
DE102005036477A1 (de) | 2005-08-03 | 2007-02-15 | Daimlerchrysler Ag | Verfahren und Steuerungseinrichtung zum Einstellen einer Drehzahl einer Welle eines Zahnräderwechselgetriebes |
DE102005049178A1 (de) | 2005-10-14 | 2007-04-19 | Zf Friedrichshafen Ag | Verfahren und Vorrichtung zur Steuerung eines Gangwechsels eines automatisierten Schaltgetriebes |
FR2927968B1 (fr) * | 2008-02-27 | 2010-05-07 | Peugeot Citroen Automobiles Sa | Procede de passage montant avec couple moteur negatif, pour boite de vitesses a crabots |
Citations (3)
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US5983740A (en) * | 1996-03-14 | 1999-11-16 | Luk Getriebe-Systeme Gmbh | Apparatus and method for controlling a torque transmitting system and a transmission using wheel speed sensor for engine RPM |
DE19963678A1 (de) * | 1998-12-31 | 2000-08-03 | Dana Corp Toledo Ohio | Verfahren zum gesteuerten Betreiben einer Antriebsstranganordnung eines Fahrzeugs |
US6113517A (en) * | 1997-04-09 | 2000-09-05 | Luk Getriebe-Systeme Gmbh | Motor vehicle with a power train having an automated clutch |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19622572B4 (de) * | 1995-06-14 | 2007-11-08 | Luk Gs Verwaltungs Kg | Hydrauliksystem und Verfahren zum Entlüften des Hydrauliksystems sowie röhrenförmiges Bauteil hierfür |
JP3504097B2 (ja) * | 1996-11-28 | 2004-03-08 | 本田技研工業株式会社 | 車両用自動変速機の油圧制御装置 |
-
2002
- 2002-03-04 WO PCT/DE2002/000786 patent/WO2002070923A2/de not_active Application Discontinuation
- 2002-03-04 DE DE10290843.5T patent/DE10290843B4/de not_active Expired - Fee Related
- 2002-03-04 BR BR0207934-8A patent/BR0207934A/pt not_active IP Right Cessation
- 2002-03-04 DE DE10209512A patent/DE10209512A1/de not_active Withdrawn
- 2002-03-04 KR KR10-2003-7011525A patent/KR20030080059A/ko not_active Application Discontinuation
- 2002-03-04 AU AU2002252955A patent/AU2002252955A1/en not_active Abandoned
- 2002-03-07 FR FR0202877A patent/FR2822111B1/fr not_active Expired - Fee Related
- 2002-03-07 IT IT2002MI000479A patent/ITMI20020479A1/it unknown
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5983740A (en) * | 1996-03-14 | 1999-11-16 | Luk Getriebe-Systeme Gmbh | Apparatus and method for controlling a torque transmitting system and a transmission using wheel speed sensor for engine RPM |
US6113517A (en) * | 1997-04-09 | 2000-09-05 | Luk Getriebe-Systeme Gmbh | Motor vehicle with a power train having an automated clutch |
DE19963678A1 (de) * | 1998-12-31 | 2000-08-03 | Dana Corp Toledo Ohio | Verfahren zum gesteuerten Betreiben einer Antriebsstranganordnung eines Fahrzeugs |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1747958A1 (de) * | 2005-07-26 | 2007-01-31 | Nissan Motor Company, Limited | Drehzahlbegrezung eines Verbrennungsmotors beim Gangwechsel |
KR100849568B1 (ko) | 2005-07-26 | 2008-07-31 | 닛산 지도우샤 가부시키가이샤 | 엔진의 과회전 방지 장치 및 엔진의 과회전 방지 방법 |
US7476178B2 (en) | 2005-07-26 | 2009-01-13 | Nissan Motor Co., Ltd. | Device and method for preventing over-rotation of engines |
KR100881255B1 (ko) * | 2005-07-26 | 2009-02-05 | 닛산 지도우샤 가부시키가이샤 | 엔진의 과회전 방지 장치 및 엔진의 과회전 방지 방법 |
DE102006003724A1 (de) * | 2006-01-26 | 2007-08-02 | Zf Friedrichshafen Ag | Verfahren zur Steuerung eines Kraftfahrzeug-Antriebsstrangs |
EP2987695A1 (de) * | 2014-08-18 | 2016-02-24 | Scania CV AB | Drehmomentsteuerung für einen verbrennungsmotor |
Also Published As
Publication number | Publication date |
---|---|
ITMI20020479A1 (it) | 2003-09-08 |
FR2822111B1 (fr) | 2008-04-04 |
BR0207934A (pt) | 2004-03-02 |
DE10290843B4 (de) | 2019-02-28 |
KR20030080059A (ko) | 2003-10-10 |
DE10209512A1 (de) | 2002-11-07 |
DE10290843D2 (de) | 2003-11-20 |
FR2822111A1 (fr) | 2002-09-20 |
ITMI20020479A0 (it) | 2002-03-07 |
AU2002252955A1 (en) | 2002-09-19 |
WO2002070923A3 (de) | 2003-01-03 |
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