EP1663693A1 - Antriebsstrang eines allradfahrzeuges mit kupplungen und verfahren zum steuern und regeln der kupplungen des antriebsstranges - Google Patents
Antriebsstrang eines allradfahrzeuges mit kupplungen und verfahren zum steuern und regeln der kupplungen des antriebsstrangesInfo
- Publication number
- EP1663693A1 EP1663693A1 EP04765432A EP04765432A EP1663693A1 EP 1663693 A1 EP1663693 A1 EP 1663693A1 EP 04765432 A EP04765432 A EP 04765432A EP 04765432 A EP04765432 A EP 04765432A EP 1663693 A1 EP1663693 A1 EP 1663693A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- clutch
- drive
- clutches
- vehicle
- transmission
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
- B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
- B60K23/0808—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles for varying torque distribution between driven axles, e.g. by transfer clutch
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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
-
- 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
- F16D48/064—Control of electrically or electromagnetically actuated clutches
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
-
- 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
- F16D2500/1025—Electric motor with threaded transmission
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
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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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10431—4WD Clutch dividing power between the front and the rear axle
-
- 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
- F16D2500/104—Clutch
- F16D2500/10443—Clutch type
- F16D2500/1045—Friction clutch
-
- 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
- F16D2500/507—Relating the vehicle
-
- 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
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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
- 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
- F16D2500/70422—Clutch parameters
- F16D2500/70432—From the input shaft
- F16D2500/70434—Input shaft torque
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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
- 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
- F16D2500/70422—Clutch parameters
- F16D2500/70438—From the output shaft
- F16D2500/7044—Output shaft torque
Definitions
- the invention relates to a drive train of an all-wheel-drive vehicle with at least two drivable vehicle axles and with a main transmission arranged between a drive machine and the vehicle axles, and a method for controlling and regulating such a drive train.
- a drive torque of a drive train generated by a drive machine is introduced into a transmission and, depending on a converted variable corresponding to the transmission ratio set in the transmission, is led to drive wheels of the vehicle.
- vehicles such as four-wheel drive cars or four-wheel drive trucks, which are designed with a plurality of drivable vehicle axles
- the power of a drive machine in the drive train of such a vehicle is distributed to vehicle axles which are each connected to the power flow.
- differential gears are usually used for power distribution, with longitudinal differentials, viewed in the direction of travel, being used for longitudinal distribution of the drive power of the drive machine to a plurality of driven vehicle axles of a vehicle.
- transverse differentials or differential gears are used in relation to the direction of travel of a vehicle for a transverse distribution of the drive power to drive wheels of a vehicle axle.
- bevel gear differentials spur gear differentials in planetary design or also worm gear differentials represent types of differential gears that are conventionally used in practice.
- spur gear differentials are mostly used as longitudinal differentials because of the possibility of asymmetrical torque distribution.
- bevel gear differentials have become a standard for transverse compensation in vehicles, and worm gear differentials are used both for longitudinal distribution and for transverse distribution of drive torque or transmission output torque in the drive train.
- clutch-controlled all-wheel drives in which clutches, such as multi-plate clutches, are used with a clutch torque that can be adjusted from the outside.
- the clutch torque can be selected according to the current driving state of the vehicle. In this way it is possible to adapt the torque distribution between the front and rear axles to the dynamic axle load changes, i.e. depending on acceleration, incline, load etc.
- this object is achieved with a drive train according to the features of patent claim 1 and a method for controlling and regulating a drive train according to the features of patent claim 8.
- an all-wheel drive vehicle which is designed with at least two drivable vehicle axles, with a main transmission between a prime mover and the main axles arranged to represent different gear ratios, and with three controllable and controllable frictional clutches, a first clutch between the main transmission and a first vehicle axle and a second clutch and a third clutch are each arranged between an axle transmission connected downstream of the main transmission and a drive wheel of the second vehicle axle, and the transmission capabilities of the clutches can each be set via an actuator system, a drive torque of the drive machine is both in The longitudinal direction between the drivable vehicle axles and in the transverse direction on one of the vehicle axles depending on the variable transmission capabilities of the couplings.
- the respective arrangement of the second clutch and the third clutch between the axle drive and one of the drive wheels of the second vehicle axle enables the transverse distribution of the drive torque applied to the second vehicle axle in the drive train, so that the operating conditions of the drive train deteriorating the driving behavior of a vehicle in a simple manner counteracted and agility and driving stability, for example when cornering, can be improved.
- the transmission capabilities of the three clutches are set to distribute a drive torque between the drivable vehicle axles such that one of the clutches is operated in a synchronous state while the other two clutches are operated slipping improvable.
- the transmission capacity of the clutches, which are operated in a slip manner is varied between a lower limit value and an upper limit value, which corresponds to a synchronous state of the two clutches.
- the drive torque can be distributed in any ratio, that is, with degrees of longitudinal distribution of the drive torque between 0% and 100%, between the drivable vehicle axles as required and in an efficiency-optimized manner.
- a part of the drive torque supplied to the second vehicle axle is in any ratio, i. H. with degrees of transverse distribution of the drive torque between 0% and 100%, can also be distributed between the drivable drive wheels of the second vehicle axle as required and in an efficiency-optimized manner.
- the method according to the invention in the control and regulation of the drive train offers the possibility of operating one of the three clutches in a slip-free state, while the other two clutches are operated at a low differential speed resulting from the required drive power distribution, which in itself advantageously reduce power losses in the drive train, which leads to a good efficiency of the drive train.
- the driving operation of a vehicle designed with the drive train according to the invention is advantageously also ensured when two of the three clutches have a functional failure.
- Fig.l is a highly schematic representation of a drive train of an all-wheel drive vehicle according to the invention.
- FIG. 2 shows a graphical representation of a relationship between transmission capabilities of a first clutch, a second and a third clutch of the drive train according to FIG. 1 and a longitudinal distribution of the drive torque between two drivable vehicle axles of the drive train; 3 shows a further graphical representation of a relationship between the transmission capabilities of the second clutch and the third clutch of the drive train according to FIG. 1 and a degree of transverse distribution of the drive torque between the drive wheels of the second vehicle axle; 4 shows a schematic diagram of part of an actuator for setting the transmission capacity of the second clutch and the third clutch from FIG. 1; and
- FIG. 5 shows a schematic diagram of part of an actuator for setting the transmission capacity of the first clutch from FIG. 1.
- a drive train 1 of an all-wheel drive vehicle is shown in a highly schematic representation.
- the drive train 1 comprises a drive unit 2 and a main transmission 3, which can be any transmission known per se from practice.
- the drive unit 2 is designed as an internal combustion engine and, in an advantageous development, can also be designed as an electric motor.
- a first clutch k_VA is arranged in a longitudinal drive train 1_HA between the main transmission 3, which is provided to represent different gear ratios, and a first drivable vehicle axle 4, which is connected in a known manner on each side of the vehicle to at least one drive wheel 4A, 4B.
- the first clutch k_VA is arranged between the main transmission 3 and a device 6 for compensating for differential speeds between the drive wheels 4A and 4B of the first vehicle axle 4, the device 6 in the present case being designed as a transverse distributor gear known per se.
- a ntriebsizer 5A, 5B of the second vehicle axle 5 is a two-te coupling k_HA_L or a third clutch k_HA_R arranged in cross-distribution lines q_HA_L and q_HA_R.
- the transverse distribution of the part of the drive torque supplied to the second vehicle axle 5 is carried out via the variably adjustable transmission capabilities of the two clutches k_HA_L and k_HA_R, one of the two clutches k_HA_L and k_HA_R preferably being operated in a synchronous state and the other clutch in each case k_HA_R or k_HA_L is operated slipping.
- a degree of transverse distribution of the part of the drive torque supplied to the second vehicle axle 5 between 0% and 100% based on one of the two drive wheels 5A or 5B can be achieved.
- the degree of transverse distribution is related to the activation of the second clutch k_HA_L of the third clutch k_HA_R in such a way that the entire portion of the Drive torque, which, that drive wheel 5A or 5B is supplied to 100% is the second vehicle axle leads 5 supplied ⁇ which the synchronously operated clutch k_HA_R or k_HA_L downstream, if the other coupling k_HA_L or k_HA_R the transverse distributor strands q_HA_L and q_HA_R with such a reduced transmission capacity is operated that no torque is transmitted via this clutch.
- the three clutches k_VA, k_HA_L and k_HA_R of the drive train 1 are designed here as control and controllable frictional multi-plate clutches, the transmission capabilities of which can be set via an actuator system 8 shown in FIGS. 4 and 5 and the output side of a transmission output of a transmission unit in FIG. 1 only schematically shown transfer case 9 are arranged.
- the three clutches k_VA, k_HA_L and k_HA_R it is possible to distribute a drive torque of the drive machine 2 or a transmission output torque of the main transmission 3 variably and as required between the two drivable vehicle axles 4, 5.
- Fig. 2 shows three highly schematic curves, a first curve gk_VA which a course of a transmission capacity of the first clutch ⁇ k_VA between a lower limit value W (u) and an upper limit value W (O).
- Another profile gk_HA represents the profile of the transmission capability of the second clutch k_HA_L or the third clutch k_HA_R, which corresponds to the profile gk_VA of the transmission capability of the first clutch k_VA.
- a third course lvt graphically represents the course of a longitudinal distribution of the drive torque between the two vehicle axles 4 and 5, the first vehicle axle 4 in the present case representing the front axle (VA) and the second vehicle axle 5 the rear axle (HA) of an all-wheel-drive vehicle.
- the basic principle of controlling the three clutches k_VA, k_HA_L and k_HA_R of the drive train is that one of the three clutches k_VA, k_HA_L or k_HA_R is operated in a synchronous state over the entire operating range of drive train 1, while the other two clutches k_HA_R and k_HA_L or k_HA_R and K_VA or k_HA_L and k_VA are operated in a slipping manner in order to be able to set the longitudinal distribution degree lvt of the drive torque between the two vehicle axles 4 and 5 as required between 0% and 100% based on one of the two vehicle axles 4 or 5.
- the joint graphical representation of the transmission capabilities of the second clutch k_HA_L and the third clutch k_HA_R in FIG. 2 was selected because when the first clutch k_VA is open and a synchronous state of one of the two clutches k_HA_L or k_HA_R, the drive torque of the internal combustion engine 2 is fully applied the second vehicle axle 5 is guided.
- the first clutch k_VA and the synchronously operated second clutch k_HA_L or third clutch k_HA_R are open, the drive torque is guided completely in the direction of the second vehicle axle 5, regardless of the set transmission capacity of the third clutch k_HA_R or the second clutch k_HA_L.
- the transmission capability of the second clutch k_HA_L is controlled and regulated in the range between point I and a second point II of the diagram according to FIG. 2 such that the second clutch k_HA_L remains in its synchronous state.
- the transmission capacity of the third clutch k_HA_R is not essential for the course of the longitudinal distribution degree lvt of the drive torque and can be used to set a desired transverse distribution degree qvt of the second vehicle axle 5
- the longitudinal distribution degree lvt is initially only changed by changing the transmission capacity of the first clutch k_VA, which is shown graphically in FIG. 2 by the curve gk_VA of the transmission capacity of the first clutch k_VA.
- the transmission capacity of the first clutch k_VA is changed between points I and II from its lower limit value W (u), at which the first clutch k_VA does not transmit any torque, in the direction of the upper limit value W (o) of the transmission capacity, at which the first clutch k_VA is also in its synchronous state.
- W (u) the lower limit value
- W (o) the upper limit value
- the transmission capacity of the first clutch k_VA is continuously increased in the range between point I and point II.
- the longitudinal distribution degree lvt of the drive torque between the two vehicle axles 4 and 5 changes, since k VA increases with the transmission capacity of the first clutch an increasing part of the drive torque is guided in the direction of the front vehicle axis 4.
- the transmission capability of the first clutch k_VA is regulated and controlled in such a way that the first clutch k_VA is kept in its synchronous state.
- the transmission capacity of the second clutch k_HA_L is continuously reduced in the direction of the lower limit value W (u) of the transmission capacity, based on the upper limit value W (o) of the transmission capacity, at which the second clutch k_HA_L is synchronous, at which the second clutch k_HA_L essentially no longer transmits torque in the direction of the rear vehicle axle 5.
- the profile lvt of the longitudinal distribution degree lvt of the drive torque between the vehicle axles 4 and 5 increases with increasing reduction in the transmission capacity of the second clutch k_HA_L up to its maximum value in point III, at which the drive torque is completely, ie 100% is transmitted to the front axle 4, the transmission capability of the third clutch k_HA_R in point III also being set to the lower limit value W (u).
- W the transmission capability of the third clutch k_HA_R in point III
- a ⁇ is adjustable, that the first clutch k_VA is operated in its syn-synchronous state and the second clutch k_HA_L and the third clutch k_HA_R are operated simultaneously slipping.
- the drive torque is then 100% guided to the first vehicle axle 4 when the second clutch k_HA_L and the third clutch k_HA_R no longer transmit torque.
- Transfer case 9 advantageously the possibility of executing the main transmission 3 without a separate starting element, such as a hydrodynamic torque converter or a frictional starting clutch, or having to integrate a starting element as an additional component in the drive train, since either the first clutch k_VA, the second clutch k_HA_L and / or the third clutch k_HA_R or all three clutches can take over the function of a starting element.
- a separate starting element such as a hydrodynamic torque converter or a frictional starting clutch
- the main transmission 3 is designed, for example, as a continuously variable transmission with a chain variator, there is advantageously the possibility of adjusting the variator in its starting ratio when the vehicle is stationary, since the stationary output of the vehicle is separated from the main transmission 3 when the clutches k_VA, k_HA_L and k_HA_R are open ,
- Another profile gk_HA_R represents the profile of the transmission capability of the third clutch k_HA_R, which corresponds to the profile gk_HA_L of the second clutch k_HA_L.
- a third curve qvt graphically represents the curve of a degree of transverse distribution of the part of the drive torque supplied to the second vehicle axle 5 between the two drive wheels 5A and 5B of the second vehicle axle 5.
- the transmission capability of the first clutch k_HA_L is regulated and controlled in this way. ensures that the first clutch k_HA_L is kept in its synchronous state.
- the transmission capacity of the third clutch k_HA_R is changed from its lower limit value W (u), at which it does not transmit any torque, in the direction of the upper limit value W (o) of transmission capacity, at which the third clutch k_HA_R also changes in synchronism Condition.
- the transmission capability of the third clutch k_HA_R is regulated and controlled in such a way that the third clutch k_HA_R is kept in its synchronous state.
- the transmission capability of the second clutch k_HA_L is steadily reduced, starting from the upper limit value W (o) of the transmission capability, at which the second clutch k_HA_L is synchronous, in the direction of the lower limit value W (u) of the transmission capability, at which the second clutch k_HA_L im Essentially no longer transmits torque in the direction of the first drive wheel 5A of the second vehicle axle 5.
- the profile qvt of the degree of transverse distribution of the part of the drive torque supplied to the second vehicle axle 5 increases with increasing reduction in the transmission capacity of the second clutch k_HA_L up to its maximum value in point VI, at which the second Part of the drive torque supplied to the vehicle axle 5 is completely transmitted to the second drive wheel 5B of the second vehicle axle 5.
- An improvement in the efficiency of the drive train in the area of the second vehicle axle is achieved by the above-described procedure for controlling and regulating the second and third clutches k_HA_L or k_HA_R, since one of the two clutches k_HA_L or k_HA_R is always operated without slip, while the other clutch k_HA_R or k_HA_L with a drive power distribution dependent on the operating situation tion in the drive train in the region of the second vehicle axle 5 corresponding differential speed is operated.
- this operating strategy the friction losses can be minimized with all the advantages of a clutch-controlled all-wheel drive in the area of a vehicle axle.
- the second clutch k_HA_L and the third clutch k_HA_R are both only operated simultaneously when the first clutch k_VA is operated in its synchronous state to set a desired degree of longitudinal distribution lvt in the manner described in FIG. 2.
- FIGS. 4 and 5 a part of the actuator system 8, shown only schematically in FIG. 1, for controlling and regulating the three clutches k_VA, k_HA_L and k_HA_R is shown, the part of the actuator system 8 shown in FIG Actuation of the second clutch k_HA_L and the third clutch k_HA_R is carried out by means of two actuators 11 and 12.
- the actuators 11 and 12 each drive two ball screws 13 and 14 to actuate the second clutch k_HA_L and the third clutch k_HA_R.
- the actuation of the actuators 11 and 12 is coupled to one another such that an actuation of the second clutch k_HA_L or the third clutch k_HA_R corresponds to the actuation of the third clutch k_HA_R or the second clutch k_HA_L and an actuation of the first clutch k_VA.
- the actuation of the second clutch k_HA_L and the third clutch k_HA_R is to change the degree of transverse distribution gvt such that the transmission capacity of the second clutch k HA L or third clutch k_HA_R is varied, while the transmission capability of the third clutch k_HA_R or the second clutch k_HA_L is kept constant at a value which preferably brings about a synchronous state of the second clutch k_HA_L or the third clutch k_HA_R.
- the actuator system 8 for the second clutch k_HA_L and the third clutch k_HA_R is designed with the actuators 11 and 12, each designed as an electric motor, whose rotary drive movements by means of the ball screws 13 and 14 or the converter devices into a linear actuation movement for the second clutch k_HA_L and the third clutch k_HA_R are convertible.
- the ball screws 13 and 14 are each designed with a nut 13A and 14A, with ball screws 13B, 14B and with spindles 13C and 14C.
- the nuts 13A and 14A can be driven in rotation by the electric motors 11, 12 and are fixed in the axial direction. Furthermore, the nuts 13A and 14A are operatively connected to the spindles 13C and 14C via the ball screw 13B and 14B.
- the spindles 13C and 14C of the ball screws 13 and 14 are connected in a rotationally fixed manner to components 15 fixed to the housing and are displaceable in the axial direction of the nuts 13A and 14A in such a way that rotation of the nuts 13A and 14A in each case one in the axial direction of the ball screws 13 and 14 directional translational movement of the spindles 13C and 14 C results.
- the second clutch k_HA_L and third clutch k__HA_R which are each designed as multi-plate clutches, or their disk packs 16 and 17 are open or in frictional engagement depending on an axial position of the spindles 13C and 14C of the ball screws 13 and 14.
- Inner disks 16A and 17A of the second clutch k_HA_L and the third clutch k_HA_R are rotatably connected to a drive shaft 18, via which the part of the transmission output torque of the main transmission 3 supplied to the second vehicle axle 5 is applied to the second clutch k_HA__L and the third clutch k_HA_R.
- Outer plates 16B and 17B are in turn connected to the first drive wheel 5A or the second drive wheel 5B of the second vehicle axle 5.
- the adjustment of the spindles 13C and 14C of the ball screws 13 and 14 in the axial direction is dependent on the directions of rotation of the nuts 13A and 12 starting from the electric motors 12 14A dependent.
- the electric motors 11 and 12 are controlled as a function of the transmission capabilities of the second clutch k_HA_L and the third clutch k_HA_R to be set in each case.
- the spindles 13C and 14C are each translationally moved in the direction of the disk packs 16 and 17 in order to increase the transmission capacity of the second clutch k_HA_L and the third clutch k_HA_R.
- the spindle 13C of the first ball screw drive 13 or the spindle 14C of the second ball screw Drive 14 is moved in the direction of the second ball screw 14 or the first ball screw 13 in order to reduce the transmission capacity of the second clutch k_HA_L or the transmission capacity of the third clutch k_HA_R by reducing the contact forces between the outer plates 16B and 17B and the inner plates 16A and 17A.
- the two nuts 13A and 14A are supported in the axial direction of the part of the actuator system 8 shown in FIG. 4 via cylindrical roller bearings 19 and 20 in the axial direction against a bevel gear 21 which is operatively connected to the drive shaft 18. Furthermore, further tapered roller bearings 22 and 23 are arranged between the disk packs 16 and 17 of the second clutch k_HA_L and the third clutch k_HA_R, via each of which an axial actuation movement of the spindle 13C or 14C on the disk pack 16 or 17 of the second clutch k_HA_L or the third Coupling k_HA_R can be applied.
- FIG. 5 shows a further part of the actuator system 8, which is provided to control the first clutch k_VA.
- This part of the actuator system 8 essentially corresponds to the part of the actuator system 8 shown in FIG. 4, which is used for the control and regulation of the second clutch k_HA_L.
- the part of the actuator system 8 shown in FIG. 5 is designed with a ball screw 23, which is in the same A rt and manner as the ball screws 13 and 14 of FIG. 4 with a nut 23A, a ball screw 23B, and a spindle 23c is formed.
- the nut 23A can be driven in rotation by an actuator 24 designed as an electric motor and is fixed in the axial direction of the drive shaft 18.
- a rotation of the nut 23A causes a translational movement of the spindle 23C which is mounted in a rotationally fixed manner, the translational displacement of the spindle 23C in the direction of a disk set 25 of the first clutch k_VA or away therefrom being effected by a left or right rotation of the electric motor 24.
- the three clutches are controlled by a hydraulic actuator system, the hydraulic actuator system being designed as a separate system or being integrated into a hydraulic control system of the main transmission.
- the first clutch via an electromechanical system and the second clutch and third clutch via a hydraulic control system.
- the wide The three clutches can be controlled and regulated using a combined control system that includes both electromechanical and hydraulic components.
- the three clutches are actuated with piezoelectric or electromagnetic actuators.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Electromagnetism (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10344972A DE10344972A1 (de) | 2003-09-27 | 2003-09-27 | Antriebsstrang eines Allradfahrzeuges und Verfahren zum Steuern und Regeln eines Antriebsstranges |
PCT/EP2004/010552 WO2005035295A1 (de) | 2003-09-27 | 2004-09-21 | Antriebsstrang eines allradfahrzeuges mit kupplungen und verfahren zum steuern und regeln der kupplungen eines antriebsstranges |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1663693A1 true EP1663693A1 (de) | 2006-06-07 |
Family
ID=34353137
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04765432A Withdrawn EP1663693A1 (de) | 2003-09-27 | 2004-09-21 | Antriebsstrang eines allradfahrzeuges mit kupplungen und verfahren zum steuern und regeln der kupplungen des antriebsstranges |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1663693A1 (de) |
CN (1) | CN1863690A (de) |
DE (1) | DE10344972A1 (de) |
WO (1) | WO2005035295A1 (de) |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT7553U1 (de) | 2004-02-23 | 2005-05-25 | Magna Drivetrain Ag & Co Kg | Antriebsstrang eines allradgetriebenen fahrzeuges |
DE102005021901A1 (de) * | 2005-05-12 | 2006-11-16 | Zf Friedrichshafen Ag | Vorrichtung und Verfahren zum Einstellen einer Übertragungsfähigkeit eines reibschlüssigen Schaltelementes |
DE102005034091B4 (de) * | 2005-07-21 | 2015-01-08 | Zf Friedrichshafen Ag | Verfahren zum Steuern der Übertragungsfähigkeiten zweier reibschlüssiger Schaltelemente |
DE102005035211A1 (de) * | 2005-07-28 | 2007-02-01 | Zf Friedrichshafen Ag | Verfahren zum Steuern eines Fahrzeugantriebsstranges |
DE102006013542A1 (de) | 2006-03-24 | 2007-09-27 | Audi Ag | Antriebssystem für allradgetriebene Kraftfahrzeuge |
US8925702B2 (en) | 2006-07-18 | 2015-01-06 | Borgwarner Inc. | PTM multiplex hydraulic diagram with two position spool valve |
DE102008000206A1 (de) | 2008-02-01 | 2009-08-06 | Zf Friedrichshafen Ag | Fahrzeugantriebsstrang mit wenigstens zwei Fahrzeugachsen, einer Brennkraftmaschine und einer Getriebeeinrichtung |
DE102008000611A1 (de) | 2008-03-12 | 2009-09-17 | Zf Friedrichshafen Ag | Getriebevorrichtung eines Fahrzeugantriebsstranges |
US8640811B2 (en) * | 2008-08-29 | 2014-02-04 | Volvo Construction Equipment Ab | Frame-steered vehicle and a method for controlling a frame-steered vehicle |
CA2677392C (en) | 2008-09-09 | 2016-11-29 | Magna Powertrain Usa, Inc. | Power take-off unit with active coupling and hypoid disconnect system |
CN102341261B (zh) | 2009-03-09 | 2015-06-10 | 麦格纳动力系美国有限公司 | 具有主动干式分离系统的全轮驱动装置 |
JP5523869B2 (ja) * | 2010-02-26 | 2014-06-18 | アイシン・エーアイ株式会社 | 車両の駆動状態制御装置 |
DE102010045502B4 (de) * | 2010-09-15 | 2016-03-24 | Audi Ag | Achsantriebseinrichtung für Torque-Vectoring und Torque-Splitting |
CN102152745A (zh) * | 2011-04-07 | 2011-08-17 | 扬州大学 | 磁悬浮电动汽车 |
DE102014007090B3 (de) * | 2014-05-15 | 2015-09-10 | Audi Ag | Verfahren zum Betreiben eines Antriebsstrangs für ein Kraftfahrzeug sowie entsprechender Antriebsstrang |
US10094427B2 (en) * | 2015-10-20 | 2018-10-09 | GM Global Technology Operations LLC | Ball cam actuated dog clutch |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62292529A (ja) * | 1986-06-11 | 1987-12-19 | Nissan Motor Co Ltd | 四輪駆動車用駆動力配分制御装置 |
JPH03118233A (ja) * | 1989-09-29 | 1991-05-20 | Mazda Motor Corp | 車両の動力伝達装置 |
JPH04129837A (ja) * | 1990-09-19 | 1992-04-30 | Mitsubishi Motors Corp | 駆動力制御装置 |
JPH04146819A (ja) * | 1990-10-09 | 1992-05-20 | Mitsubishi Motors Corp | 駆動力制御装置 |
JP3409439B2 (ja) * | 1994-06-17 | 2003-05-26 | 日産自動車株式会社 | 左右輪と前後輪の駆動力配分総合制御装置 |
US5690002A (en) * | 1996-03-06 | 1997-11-25 | Borg-Warner Automotive, Inc. | Method of operating a vehicle differential |
DE10000901A1 (de) * | 2000-01-12 | 2001-07-19 | Mannesmann Sachs Ag | System und Verfahren zum Einregeln eines Kolbens in einem Zylinder |
US6484857B2 (en) * | 2001-02-01 | 2002-11-26 | New Venture Gear, Inc. | Torque transfer clutch with ball screw actuator |
US6780132B2 (en) * | 2002-08-02 | 2004-08-24 | Visteon Global Technologies, Inc. | Selectively actuated transfer case |
-
2003
- 2003-09-27 DE DE10344972A patent/DE10344972A1/de not_active Withdrawn
-
2004
- 2004-09-21 EP EP04765432A patent/EP1663693A1/de not_active Withdrawn
- 2004-09-21 CN CNA2004800280026A patent/CN1863690A/zh active Pending
- 2004-09-21 WO PCT/EP2004/010552 patent/WO2005035295A1/de not_active Application Discontinuation
Non-Patent Citations (1)
Title |
---|
See references of WO2005035295A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE10344972A1 (de) | 2005-04-21 |
CN1863690A (zh) | 2006-11-15 |
WO2005035295A1 (de) | 2005-04-21 |
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