Abstract: Described herein is a method for reducing noise in a driveline of a motor vehicle, the method including detecting a condition initiating a noise event of the driveline by using one or more sensors on board the vehicle; and controlling, as a function of the detected condition and of a signal of said one or more sensors, an actuation of one or more actuators that govern corresponding devices that can be connected to the driveline and configured for generating a torsional pre-load condition in the driveline itself.

Abstract: Described herein is a method for reducing noise in a driveline of a motor vehicle, the method including detecting a condition initiating a noise event of the driveline by using one or more sensors on board the vehicle; and controlling, as a function of the detected condition and of a signal of said one or more sensors, an actuation of one or more actuators that govern corresponding devices that can be connected to the driveline and configured for generating a torsional pre-load condition in the driveline itself.

Abstract: An electro-hydraulic control apparatus for a motor-vehicle transmission having at least five forward gears and one reverse gear, including first, second and third shift forks, each movable in at least one engagement position to engage a respective gear, first, second and third hydraulic actuators each arranged to control the movement of a respective shift fork in the respective at least one engagement position, and a slide valve selectively movable into one of at least three operating positions in each of which the slide valve selects a respective hydraulic actuator, wherein a first operating position is an end-of-travel position and corresponds to the selection of the first hydraulic actuator, and wherein a second operating position is also an end-of-travel position and corresponds to the selection of the second hydraulic actuator.

Abstract: An electro-hydraulic control apparatus for a motor-vehicle transmission having at least five forward gears and one reverse gear, including first, second and third shift forks, each movable in at least one engagement position to engage a respective gear, first, second and third hydraulic actuators each arranged to control the movement of a respective shift fork in the respective at least one engagement position, and a slide valve selectively movable into one of at least three operating positions in each of which the slide valve selects a respective hydraulic actuator, wherein a first operating position is an end-of-travel position and corresponds to the selection of the first hydraulic actuator, and wherein a second operating position is also an end-of-travel position and corresponds to the selection of the second hydraulic actuator.

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: The control apparatus comprises, in its version intended for a double-clutch transmission, first, second and third shift forks each movable between first and second engagement positions to engage a respective gear, of which the first shift fork is able to engage at least the first gear and the second shift fork is able to engage at least the second gear, first, second and third double-acting hydraulic actuators arranged to control each the movement of a respective shift fork between the first and second engagement position, of which the first hydraulic actuator is associated to the first shift fork and the second hydraulic actuator is associated to the second shift fork, a slide valve selectively movable into one of at least three operating positions in each of which the slide valve selects a respective hydraulic actuator, and first and second gear shift solenoid valves for controlling the supply of fluid to the hydraulic actuator each time selected by the slide valve or the connection of that actuator to a t

Abstract: The control apparatus comprises, in its version intended for a double-clutch transmission with six or seven forward gears and one reverse gear, a first shift fork for engaging the first gear or the third gear, respectively, a second shift fork for engaging the reverse gear or the fifth gear, respectively, a first hydraulic actuator arranged to control the movement of the first shift fork, a second hydraulic actuator arranged to control the movement of the second shift fork, a selection slide valve which can be moved into a first operating position in which the first hydraulic actuator is selected and a second operating position in which the second hydraulic actuator is selected, a pilot solenoid valve for controlling the movement of the slide valve between the first and second operating positions, and first and second gear shift solenoid valves for controlling the supply of fluid to the hydraulic actuator each time selected by the slide valve or the connection of said actuator with a tank.

Abstract: The gearbox comprises an engagement sleeve movable between a neutral position and one engagement position for engagement of one given gear, and a shift fork operatively connected to the engagement sleeve for controlling the movement thereof between the neutral position and the engagement position. The shift fork is slidably mounted on a stationary support rod, which is provided with a pair of bushes defining a first axial abutment surface for stopping the movement of the shift fork in the direction from the neutral position to the engagement position and a second axial abutment surface for stopping the movement of the shift fork in the direction from the engagement position to the neutral position. The neutral position of the shift fork is axially spaced from the second axial abutment surface.

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 monitors a gear-change operation in a motor vehicle provided with an engine whose crankshaft is connected to a transmission having a gearbox) comprising first and second primary shafts connectable to the crankshaft of the engine by respective friction clutches controlled by corresponding actuators, and a secondary or output shaft connectable to the primary shafts by gears defining a plurality of velocity ratios or gears. The method comprises the operation of verifying and validating the detection of the disengagement of the previously engaged gear by detecting the angular velocity of the primary shaft corresponding to the gear to be disengaged, and comparing the detected value of said angular velocity with at least one reference angular velocity.

Abstract: The control system comprises detectors or estimators capable of supplying electrical signals or data indicative of the values of predetermined state variables including the angular velocity of the crankshaft of the engine, the difference between this angular velocity and the angular velocity of the primary shaft of the gearbox, and the torque delivered by the engine crankshaft and the torque transmitted by the friction clutch; calculating devices capable of supplying signals indicating the errors between the values of the state variables and respective reference values; filter devices capable of incrementing, within a predetermined frequency band, the relative weight selectively of the error of angular velocity of the crankshaft of the engine, and of the error of the abovementioned difference of angular velocity; processing devices capable of generating, in accordance with predetermined transfer functions, output signals or data indicating a torque partial value or contribution to be delivered by the engin

Abstract: A process that estimates the torque transmitted by a friction clutch coupled to the shaft of a motor vehicle engine. The process includes determining the angular speed of the engine shaft and the torque developed by this shaft; calculating the difference between the measured value of the engine shaft's angular speed and an estimated value of the angular speed; and determining an estimated value of the torque transmitted by the clutch, corresponding to the calculated value of the difference or error in the engine shaft angular speed. The estimated value of the torque is used, along with the value measured or otherwise determined of the torque developed by the engine shaft, to obtain the estimated value of the angular speed of the engine shaft on the basis of a predetermined mathematical model.

Abstract: A powertrain control system for management and supervision of engine and servo-assisted gearbox control modules is arranged for determining the power to be applied to the drive wheels of the vehicle as a function of signals indicative of commands imparted by the driver, of the engine and gearbox state parameters and of possible requirements from the engine and gearbox control modules and supplementary on board vehicle traction/drive control systems; calculating data indicative of the torque to be delivered at the engine drive shaft, the torque transmissible by the clutch and the required transmission ratio, as a function of the determined value of the power to be applied to the drive wheels, of the state parameters and of the requirements of the engine and gearbox control modules and the traction/drive control systems; and transmitting the calculated data as signals to the engine and gearbox control modules.

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 monitors a gear-change operation in a motor vehicle provided with an engine whose crankshaft is connected to a transmission having a gearbox) comprising first and second primary shafts connectable to the crankshaft of the engine by respective friction clutches controlled by corresponding actuators, and a secondary or output shaft connectable to the primary shafts by gears defining a plurality of velocity ratios or gears. The method comprises the operation of verifying and validating the detection of the disengagement of the previously engaged gear by detecting the angular velocity of the primary shaft corresponding to the gear to be disengaged, and comparing the detected value of said angular velocity with at least one reference angular velocity.

Abstract: The procedure estimates the torque transmitted by a friction clutch coupled to the shaft of a motor vehicle engine and controlled by means of an actuator, the procedure comprising the operations of: measuring or otherwise determining the angular speed of the engine shaft and the torque developed by this shaft; calculating the difference or error between the measured value of the engine shaft's angular speed and an estimated value of the said angular speed; and, using an electronic controller, determining an estimated value of the torque transmitted by the clutch, corresponding to the calculated value of the said difference or error in the engine shaft angular speed; the estimated value of the torque transmitted by the clutch being used, along with the value measured or otherwise determined of the torque developed by the engine shaft, to obtain the said estimated value of the angular speed of the engine shaft on the basis of a predetermined mathematical model.

Abstract: The control system comprises detectors or estimators capable of supplying electrical signals or data indicative of the values of predetermined state variables including the angular velocity of the crankshaft of the engine, the difference between this angular velocity and the angular velocity of the primary shaft of the gearbox, and the torque delivered by the engine crankshaft and the torque transmitted by the friction clutch; calculating devices capable of supplying signals indicating the errors between the values of the state variables and respective reference values; filter devices capable of incrementing, within a predetermined frequency band, the relative weight selectively of the error of angular velocity of the crankshaft of the engine, and of the error of the abovementioned difference of angular velocity; processing devices capable of generating, in accordance with predetermined transfer functions, output signals or data indicating a torque partial value or contribution to be delivered by the engin

Abstract: The control apparatus comprises, in its version intended for a double-clutch transmission, first, second and third shift forks each movable between first and second engagement positions to engage a respective gear, of which the first shift fork is able to engage at least the first gear and the second shift fork is able to engage at least the second gear, first, second and third double-acting hydraulic actuators arranged to control each the movement of a respective shift fork between the first and second engagement position, of which the first hydraulic actuator is associated to the first shift fork and the second hydraulic actuator is associated to the second shift fork, a slide valve selectively movable into one of at least three operating positions in each of which the slide valve selects a respective hydraulic actuator, and first and second gear shift solenoid valves for controlling the supply of fluid to the hydraulic actuator each time selected by the slide valve or the connection of that actuator to a t

Abstract: The gearbox comprises an engagement sleeve movable between a neutral position and one engagement position for engagement of one given gear, and a shift fork operatively connected to the engagement sleeve for controlling the movement thereof between the neutral position and the engagement position. The shift fork is slidably mounted on a stationary support rod, which is provided with a pair of bushes defining a first axial abutment surface for stopping the movement of the shift fork in the direction from the neutral position to the engagement position and a second axial abutment surface for stopping the movement of the shift fork in the direction from the engagement position to the neutral position. The neutral position of the shift fork is axially spaced from the second axial abutment surface.