Abstract: A method of controlling a pickup manoeuvre of a hybrid vehicle is actuated with an engine off, an electric motor active and a first clutch being open. In a first phase of the manoeuvre, vehicle advancement is obtained by progressively closing the second clutch so that the input shaft is set in rotation with an increasing speed, while the motor rotates at an increasing speed higher than a speed of the input shaft with the second clutch in a slip condition. Upon a request for starting the engine, the first clutch is progressively closed so that the engine starts to be driven by the motor, while the second clutch is kept in the slip condition, which is maintained until the engine and motor rotate substantially at a same speed, higher than the speed of the input shaft, and once this condition is reached, closing of the second clutch is started.

Abstract: A method of controlling a vehicle hybrid propulsion system is provided. The propulsion system includes an internal combustion engine, first and second clutches, an electric motor, and a gearbox having an input shaft and an output shaft connected to drive wheels. The method includes a first operating mode of starting the engine by the motor, a second operating mode of actuating a gear shift, and a third operating mode which actuates starting of the engine and the gear shift. The method includes passing from the first to the third operating modes even if starting of the engine has not been completed, or passing from the second to the third operating modes even if actuation of the gear shift has not been completed, so that the transition from one operating mode to another can be freely actuated at any time, depending upon operating conditions of the hybrid propulsion system.

Abstract: A method of controlling a pickup manoeuvre of a hybrid vehicle is actuated with an engine off, an electric motor active and a first clutch being open. In a first phase of the manoeuvre, vehicle advancement is obtained by progressively closing the second clutch so that the input shaft is set in rotation with an increasing speed, while the motor rotates at an increasing speed higher than a speed of the input shaft with the second clutch in a slip condition. Upon a request for starting the engine, the first clutch is progressively closed so that the engine starts to be driven by the motor, while the second clutch is kept in the slip condition, which is maintained until the engine and motor rotate substantially at a same speed, higher than the speed of the input shaft, and once this condition is reached, closing of the second clutch is started.

Abstract: A method of controlling a vehicle hybrid propulsion system is provided. The propulsion system includes an internal combustion engine, first and second clutches, an electric motor, and a gearbox having an input shaft and an output shaft connected to drive wheels. The method includes a first operating mode of starting the engine by the motor, a second operating mode of actuating a gear shift, and a third operating mode which actuates starting of the engine and the gear shift. The method includes passing from the first to the third operating modes even if starting of the engine has not been completed, or passing from the second to the third operating modes even if actuation of the gear shift has not been completed, so that the transition from one operating mode to another can be freely actuated at any time, depending upon operating conditions of the hybrid propulsion system.

Abstract: The method comprises the steps of: storing a curve or characteristic of torque transmitted by the friction clutch as a function of the position of the clutch, calculating a desired value of the torque to be transmitted by means of the clutch, and modifying the position of the clutch so as to bring it to the position to which the desired transmitted torque value corresponds according to the stored curve or characteristic, upon the occurrence of predetermined operative conditions, estimating the value of the torque transmitted by the clutch, by means of an algorithm, as a function of the detected instantaneous values of the torque delivered and of the angular velocity of the shaft of the engine, and detecting the corresponding instantaneous position or estimate position of the clutch, and then modifying the previously stored curve or characteristic in accordance with predetermined procedures in dependence on the difference between the estimated value of the torque transmitted and that value of the torque tra

Abstract: According to the method the crossover phase of the friction clutches is performed by defining a linear torque profile for the first friction clutch having a given initial value and a zero final value, a linear torque profile for the second friction clutch having a zero initial value and a given final value, and a linear torque profile for the engine having a given initial value and a given final value. The final value of the torque profile of the second friction clutch is calculated, the initial value of the engine torque being known, by determining a final value of the longitudinal acceleration of the vehicle equal to a given percentage of the initial value of the longitudinal acceleration of the vehicle. The final value of the engine torque profile is calculated, the final value of the torque profile of the second friction clutch being known, on the basis of the final value determined for the longitudinal acceleration of the vehicle.

Abstract: The method comprises the steps of: storing a curve or characteristic of torque transmitted by the friction clutch as a function of the position of the clutch, calculating a desired value of the torque to be transmitted by means of the clutch, and modifying the position of the clutch so as to bring it to the position to which the desired transmitted torque value corresponds according to the stored curve or characteristic, upon the occurrence of predetermined operative conditions, estimating the value of the torque transmitted by the clutch, by means of an algorithm, as a function of the detected instantaneous values of the torque delivered and of the angular velocity of the shaft of the engine, and detecting the corresponding instantaneous position or estimate position of the clutch, and then modifying the previously stored curve or characteristic in accordance with predetermined procedures in dependence on the difference between the estimated value of the torque transmitted and that value of the torque tra

Abstract: According to the method the crossover phase of the friction clutches is performed by defining a linear torque profile for the first friction clutch having a given initial value and a zero final value, a linear torque profile for the second friction clutch having a zero initial value and a given final value, and a linear torque profile for the engine having a given initial value and a given final value. The final value of the torque profile of the second friction clutch is calculated, the initial value of the engine torque being known, by determining a final value of the longitudinal acceleration of the vehicle equal to a given percentage of the initial value of the longitudinal acceleration of the vehicle. The final value of the engine torque profile is calculated, the final value of the torque profile of the second friction clutch being known, on the basis of the final value determined for the longitudinal acceleration of the vehicle.

Abstract: What is described is a control system for controlling the driving-away maneuver in a motor vehicle provided with a gearbox comprising a primary input shaft which can be coupled to a drive shaft of a propulsion system of the vehicle by means of a servo-assisted friction clutch, wherein a control unit receives at its input signals indicating a command imparted by the driver of the motor vehicle by operating the accelerator pedal, and generates—on the basis of a mathematical reference model—reference torque request signals indicating the reference torques requested from the drive shaft and from the friction clutch during the driving-away manoeuvre, and also generates—by comparison between signals indicating the estimated angular velocities of the drive shaft and of the primary gear shaft, and detected signals indicating the actual angular velocities of the drive shaft and of the primary gear shaft—corresponding corrective contributions, in such a way as to construct command signals for controlling torque actuato

Abstract: What is described is a control system for controlling the coupling between a driveshaft of a motor vehicle propulsion system and a primary input shaft of a gearbox by means of a servo-assisted friction clutch. A control unit receives at its input signals indicating a command imparted by the driver of the motor vehicle by operating the accelerator pedal in a driving-away or gear-changing manoeuvre, and generates—on the basis of a mathematical reference model—reference torque request signals indicating the reference torques requested from the driveshaft and from the friction clutch, the said request signals or data varying in time in such a way as to cause synchronization between the angular velocities of the driveshaft and of the primary gear shaft to be reached at the same moment as the difference between the angular accelerations of the said shafts becomes zero.

Abstract: What is described is a control system for controlling the coupling between a driveshaft of a motor vehicle propulsion system and a primary input shaft of a gearbox by means of a servo-assisted friction clutch. A control unit receives at its input signals indicating a command imparted by the driver of the motor vehicle by operating the accelerator pedal in a driving-away or gear-changing manoeuvre, and generates—on the basis of a mathematical reference model—reference torque request signals indicating the reference torques requested from the driveshaft and from the friction clutch, the said request signals or data varying in time in such a way as to cause synchronization between the angular velocities of the driveshaft and of the primary gear shaft to be reached at the same moment as the difference between the angular accelerations of the said shafts becomes zero.