An engine, a transmission unit which is connected to the engine and is shifted by an engagement apparatus, and a differential unit which connects the transmission unit and a drive wheel are included. The differential unit includes a first rotary element connected to an output element of the transmission unit, a second rotary element connected to a first rotary machine, and a third rotary element connected to the drive wheel. When an output from the first rotary machine is limited, the engagement apparatus is slipped and an operation point of the engine is changed. The change of the operation point can cause an increase in torque of the engine.

A method of synchronizing the countershaft speed, in the direct gear, for a hybrid application. The transmission (1) comprises a main transmission (HG) comprising two parallel partial transmissions with at least one countershaft (VW), an output shaft (3), and two planetary transmissions (PG1, PG2) each comprising a carrier (ST1, ST2), sun gear (SR1, SR2) and ring gear (HR1, HR2). Each partial transmission has a transmission input shaft (4, 5), with a hollow first input shaft (4) and the solid second input shaft (5). The first planetary transmission (PG1) connects as a range group to the main transmission (HG). The main transmission (HG) comprises first (R1), second (R2), third (R3), fourth (R4) and fifth gear planes (R5) and first (S1), second (S2), third (S3) and fourth shift elements (S4). Synchronization of the countershaft speed to a target speed, in direct gear, is performed via speed control of the electric machine (2).

A method of synchronizing the countershaft speed, in the direct gear, for a hybrid application. The transmission (1) comprises a main transmission (HG) comprising two parallel partial transmissions with at least one countershaft (VW), an output shaft (3), and two planetary transmissions (PG1, PG2) each comprising a carrier (ST1, ST2), sun gear (SR1, SR2) and ring gear (HR1, HR2). Each partial transmission has a transmission input shaft (4, 5), with a hollow first input shaft (4) and the solid second input shaft (5). The first planetary transmission (PG1) connects as a range group to the main transmission (HG). The main transmission (HG) comprises first (R1), second (R2), third (R3), fourth (R4) and fifth gear planes (R5) and first (S1), second (S2), third (S3) and fourth shift elements (S4). Synchronization of the countershaft speed to a target speed, in direct gear, is performed via speed control of the electric machine (2).

A displayed rotation speed control apparatus for a hybrid vehicle includes: a displayed rotation speed controller having a display mode in which a target primary rotation speed stepwisely set is displayed as a driving source rotation speed in the rotation speed display device in the simulated stepwise shift mode, when the mode is switched from the EV mode to the HEV mode to initiate a starting of the engine, and when the mode is switched from the continuous shift mode to the simulated stepwise shift mode while an actual engine speed is smaller than a predetermined rotation speed, the displayed rotation speed controller being configured to display a value obtained by retarding the actual engine speed, during a period from the initiation of the starting of the engine to a rotation speed smaller than a predetermined rotation speed.

A displayed rotation speed control apparatus for a hybrid vehicle includes: a displayed rotation speed controller having a display mode in which a target primary rotation speed stepwisely set is displayed as a driving source rotation speed in the rotation speed display device in the simulated stepwise shift mode, when the mode is switched from the EV mode to the HEV mode to initiate a starting of the engine, and when the mode is switched from the continuous shift mode to the simulated stepwise shift mode while an actual engine speed is smaller than a predetermined rotation speed, the displayed rotation speed controller being configured to display a value obtained by retarding the actual engine speed, during a period from the initiation of the starting of the engine to a rotation speed smaller than a predetermined rotation speed.

A control device for a vehicle is provided. The control device includes an automatic transmission constituted of a stepwise variable transmission mechanism configured to switch a plurality of shift stages by engagement and disengagement of a plurality of friction engaging elements, an engine as a driving source, a motor configured to assist a driving force of the engine, a hydraulic controller configured to supply a hydraulic pressure to control the engagement and the disengagement of the friction engaging element, and a control unit configured to control the automatic transmission to a target speed ratio through changing the shift stage of the stepwise variable transmission mechanism. The control unit performs a learning control that learns at least one of hydraulic pressure of the engagement and the disengagement of the friction engaging element, and inhibits the assist of the driving force to the engine by the motor in performing the learning control.

In accordance with an example embodiment, a transmission may include a first mode in which a low range clutch is engaged and a first synchronizer is in a first engaged condition causing an output shaft to rotate relative to a first range shaft based upon a ratio of a first range gear to a second range gear. The transmission may include a second mode in which a high range clutch is engaged and a second synchronizer is in a first engaged condition causing the output shaft to rotate relative to a second range shaft based upon a ratio of the first range gear to the second range gear. A shift from the first mode to the second mode includes engaging the second synchronizer in the first engaged condition before disengaging the low range clutch and engaging the high range clutch.

In accordance with an example embodiment, a transmission may include a first mode in which a low range clutch is engaged and a first synchronizer is in a first engaged condition causing an output shaft to rotate relative to a first range shaft based upon a ratio of a first range gear to a second range gear. The transmission may include a second mode in which a high range clutch is engaged and a second synchronizer is in a first engaged condition causing the output shaft to rotate relative to a second range shaft based upon a ratio of the first range gear to the second range gear. A shift from the first mode to the second mode includes engaging the second synchronizer in the first engaged condition before disengaging the low range clutch and engaging the high range clutch.

A method for operating a drive train of a motor vehicle, where the drive train includes a drive aggregate, a group transmission connected between the drive aggregate and a drive output, and a separating cutch connected between the drive aggregate and the group transmission. If a speed is lower than a limit value, the separating clutch is opened and for transmission preselection one or all the other sub-transmission(s) is/are changed to a friction-force-locking condition. The separating clutch is then at least partially closed and the drive aggregate is brought to a defined rotation speed. When a friction-force-locking group transmission is required, it is checked whether a starting gearshift or a driver-desired shift for the group transmission is called for and the target rotation speed of the drive aggregate is checked. Depending on the results, the sub-transmission can be synchronized by a transmission brake or by the drive aggregate.

A drive force control system for a vehicle configured to accurately imitate a change in a drive force in a model vehicle. A drive torque simulator computes a virtual drive torque supposed to be delivered to drive wheels of the model vehicle in response to a manual operation to manipulate the vehicle, based on torque changing factors of a powertrain of the model vehicle. An actual torque calculator computes a target torque of a motor that is practically delivered to the drive wheels in the vehicle based on the virtual drive torque computed by the drive torque simulator, taking account of torque changing factors of the powertrain of the vehicle.