Abstract: A control device and method controls a vehicle having an internal combustion engine connected to an automatic transmission via a torque converter with a lockup device. The torque of the internal combustion engine is limited the by a torque limit value based on a speed difference between an input rotational speed and an output rotational speed of the torque converter during acceleration in a non-lockup state. The torque-limiting of the internal combustion engine is prohibited torque-limiting upon a prescribed condition being met. The prescribed condition is met by a heating request, during hill climbing/towing, during travel at high vehicle speeds, when the accelerator pedal opening angle exceeds or is equal to a prescribed opening angle, when the torque limit value is greater than a target torque, in a range other than a D range, or in a mode other than normal mode.

Abstract: An oil pressure control device has a mechanical oil pump (O/P) driven by a motor/generator (MG), an electric oil pump (M/O/P) driven by a sub motor (S/M) and a line pressure regulating valve (104). In a case where a state is changed from a state in which the motor/generator (MG) is stopped and the electric oil pump (M/O/P) is driven to a state in which the motor/generator (MG) is started and the electric oil pump (M/O/P) is stopped, when a total flow amount of a working fluid discharge flow amount of the mechanical oil pump (O/P) and a working fluid discharge flow amount of the electric oil pump (M/O/P) is equal to or greater than a pressure regulation limit flow amount of the pressure regulating valve (104), the working fluid discharge flow amount of the electric oil pump (M/O/P) is decreased.

Abstract: An oil pressure control device for a vehicle is configured such that, when switching from an oil pressure supply by means of a mechanical oil pump driven by a motor/generator to an oil pressure supply by means of an electric oil pump driven by a sub-motor, a supply ratio of oil supplied from the mechanical oil pump and a supply ratio of oil supplied from the electric oil pump, are adjusted based on an oil pressure difference between a first oil pressure and a second oil pressure, via first and second flapper valves. When the first oil pressure becomes less than or equal to a pump drive threshold, an increase in the second oil pressure is initiated, and the first oil pressure and the second oil pressure are made to match at a predetermined equilibrium oil pressure higher than a required line pressure.

Abstract: A vehicle is provided with a mechanical oil pump (O/P) that is driven by a motor/generator (MG), an electric oil pump (M/O/P) that is driven by a sub-motor (S/M) and a second clutch (CL2) that transmits the drive force of the motor/generator (MG) to left and right drive wheels (LT, RT). When an accelerator pedal is depressed while a brake pedal is still depressed, an integrated controller (10) drives the electric oil pump (M/O/P) before the brake pedal is released, and oil pressure supplied to the second clutch (CL2) is increased.

Abstract: A hydraulic control device includes: a mechanical oil pump (O/P) that is driven by a motor/generator (M/G) and that generates a first hydraulic pressure (P1); an electric oil pump (M/O/P) that is driven by a sub-motor (S/M) and that generates a second hydraulic pressure (P2); and a controller (10). When a demanded drive force from a driver is generated while in a low-vehicle-speed region which is lower than a first vehicle speed (V1) at which the output of the mechanical oil pump (O/P) becomes unstable, the controller (10) controls the electric oil pump (M/O/P) such that the second hydraulic pressure (P2) becomes larger than a compensative hydraulic pressure (P?) found by subtracting the first hydraulic pressure (P1) from a necessary hydraulic pressure (Pne) determined in accordance with the demanded drive force.

Abstract: An oil pressure control device has a mechanical oil pump (O/P) driven by a motor/generator (MG), an electric oil pump (M/O/P) driven by a sub motor (S/M) and a line pressure regulating valve (104). In a case where a state is changed from a state in which the motor/generator (MG) is stopped and the electric oil pump (M/O/P) is driven to a state in which the motor/generator (MG) is started and the electric oil pump (M/O/P) is stopped, when a total flow amount of a working fluid discharge flow amount of the mechanical oil pump (O/P) and a working fluid discharge flow amount of the electric oil pump (M/O/P) is equal to or greater than a pressure regulation limit flow amount of the pressure regulating valve (104), the working fluid discharge flow amount of the electric oil pump (M/O/P) is decreased.

Abstract: A vehicle is provided with a mechanical oil pump (O/P) that is driven by a motor/generator (MG), an electric oil pump (M/O/P) that is driven by a sub-motor (S/M) and a second clutch (CL2) that transmits the drive force of the motor/generator (MG) to left and right drive wheels (LT, RT). When an accelerator pedal is depressed while a brake pedal is still depressed, an integrated controller (10) drives the electric oil pump (M/O/P) before the brake pedal is released, and oil pressure supplied to the second clutch (CL2) is increased.

Abstract: A hydraulic control device includes: a mechanical oil pump (O/P) that is driven by a motor/generator (M/G) and that generates a first hydraulic pressure (P1); an electric oil pump (M/O/P) that is driven by a sub-motor (S/M) and that generates a second hydraulic pressure (P2); and a controller (10). When a demanded drive force from a driver is generated while in a low-vehicle-speed region which is lower than a first vehicle speed (V1) at which the output of the mechanical oil pump (O/P) becomes unstable, the controller (10) controls the electric oil pump (M/O/P) such that the second hydraulic pressure (P2) becomes larger than a compensative hydraulic pressure (P?) found by subtracting the first hydraulic pressure (P1) from a necessary hydraulic pressure (Pne) determined in accordance with the demanded drive force.

Abstract: An oil pressure control device for a vehicle is configured such that, when switching from an oil pressure supply by means of a mechanical oil pump driven by a motor/generator to an oil pressure supply by means of an electric oil pump driven by a sub-motor, a supply ratio of oil supplied from the mechanical oil pump and a supply ratio of oil supplied from the electric oil pump, are adjusted based on an oil pressure difference between a first oil pressure and a second oil pressure, via first and second flapper valves. When the first oil pressure becomes less than or equal to a pump drive threshold, an increase in the second oil pressure is initiated, and the first oil pressure and the second oil pressure are made to match at a predetermined equilibrium oil pressure higher than a required line pressure.

Abstract: The first planetary gear set is configured to integrally rotate by a first clutch. The first element is coupled with the fifth element. The second element is configured to be locked through a first brake to a stationary section and configured to be coupled through a second clutch with the ninth element. The third element is coupled with the input shaft. The fourth element is configured to be coupled through a third clutch with the ninth element. The sixth element is locked to the stationary section. The seventh element is configured to be locked through a second brake to the stationary section. The eighth element is coupled with an output shaft. The ninth element is coupled with the twelfth element. The tenth element is configured to be coupled through a fourth clutch with the output shaft. The eleventh element is coupled with the input shaft.

Abstract: A control apparatus for a vehicle includes an automatic transmission configured to attain a predetermined shift-stage by releasing an engaged friction-engagement element and by engaging a released friction-engagement element; a variation-start detecting section configured to detect that a parameter which varies with a progress of inertia phase has varied; a memorizing section configured to sequentially memorize a state of the vehicle; and a learning section configured to correct a control quantity for a next-time shift of the transmission on the basis of the state of vehicle memorized at a timing earlier by a given time interval than a timing when the variation-start detecting section detects that the parameter has varied.

Abstract: The first planetary gear set is configured to integrally rotate by a first clutch. The first element is coupled with the fifth element. The second element is configured to be locked through a first brake to a stationary section and configured to be coupled through a second clutch with the ninth element. The third element is coupled with the input shaft. The fourth element is configured to be coupled through a third clutch with the ninth element. The sixth element is locked to the stationary section. The seventh element is configured to be locked through a second brake to the stationary section. The eighth element is coupled with an output shaft. The ninth element is coupled with the twelfth element. The tenth element is configured to be coupled through a fourth clutch with the output shaft. The eleventh element is coupled with the input shaft.

Abstract: When gear shift to second gear shift stage is completed and frictional engagement element is judged to be in slip state by slip state judging unit in a state in which input torque is input torque upper limit value, a value obtained by subtracting first predetermined amount from the input torque upper limit value is set as a decrease side input torque upper limit value. When next gear shift to the second gear shift stage is completed with the decrease side input torque upper limit value set and the frictional engagement element is not judged to be in slip state by the slip state judging unit in a state in which the input torque is the decrease side input torque upper limit value, a value obtained by adding second predetermined amount to the decrease side input torque upper limit value is set as a new input torque upper limit value.

Abstract: When gear shift to second gear shift stage is completed and frictional engagement element is judged to be in slip state by slip state judging unit in a state in which input torque is input torque upper limit value, a value obtained by subtracting first predetermined amount from the input torque upper limit value is set as a decrease side input torque upper limit value. When next gear shift to the second gear shift stage is completed with the decrease side input torque upper limit value set and the frictional engagement element is not judged to be in slip state by the slip state judging unit in a state in which the input torque is the decrease side input torque upper limit value, a value obtained by adding second predetermined amount to the decrease side input torque upper limit value is set as a new input torque upper limit value.

Abstract: An automatic transmission includes: a first planetary gearset including a first sun gear, a first ring gear, and a first pinion carrier; a second planetary gearset including a second sun gear, a second ring gear, and a second pinion carrier; an input shaft constantly coupled to the first sun gear; an output shaft constantly coupled to the second pinion carrier; a first rotary member constantly connecting the first ring gear and the second sun gear; a first friction element selectively connecting the first sun gear and the second ring gear; a second friction element selectively connecting the first pinion carrier and the second ring gear; a third friction element selectively interrupting a rotation of the first pinion carrier; and a fourth friction element selectively interrupting a rotation of the first rotary member, the automatic transmission attaining first to fourth forward speeds and one reverse speed.

Abstract: An automatic transmission includes a double-pinion planetary gearset and two single-pinion planetary gearsets. A first ring gear is held stationary. A second sun gear and a third ring gear are coupled to a first sun gear and a first carrier respectively, constituting first and second rotor units. An output is coupled to a third carrier. A first clutch selectively couples a second carrier to the first rotor unit. A second clutch selectively couples the second carrier to the second rotor unit. A third clutch selectively couples an input to the second carrier. A fourth clutch selectively couples a second ring gear to a third sun gear. A fifth clutch selectively couples the second ring gear to the third carrier. A sixth clutch selectively couples the input to the third sun gear. Nine forward gear ratios and one reverse gear ratio are obtained by simultaneous application of three of the clutches.

Abstract: When an inertia phase of an upshift of the transmission is started during a lockup clutch engagement operation, a following command oil pressure to be used during a following lockup clutch engagement operation is learned on the basis of a slip rotation speed, which is a rotation speed difference between an input side rotation speed of the torque converter and an output side rotation speed of the torque converter, at or after a start point of the inertia phase.

Abstract: An automatic transmission including a single-pinion first planetary gearset having a first sun gear, a first ring gear and a first pinion carrier, a double-pinion second planetary gearset having a second sun gear, a second ring gear and a second pinion carrier, a single-pinion third planetary gearset having a third sun gear, a third ring gear and a third pinion carrier, an input shaft always connected to the first sun gear, an output shaft always connected to the first pinion carrier, the third sun gear always kept in a fixed state, the first ring gear and the second sun gear which are always connected to each other, the second and third ring gears which are always connected to each other, and six friction elements, at least eight forward speeds and one reverse speed being respectively established by simultaneous engagement of two friction elements selected from the six friction elements.

Abstract: An automatic transmission including a double pinion planetary gear unit PG1, two single pinion planetary gear units PG2 and PG3 and six frictional elements (viz., six clutches) C1 to C6 is so constructed as to establish nine forward speeds and one reverse speed by simultaneously putting selected three of the six frictional elements C1 to C6 into their engaged condition. The frictional elements C1 to C6 are of a type including mutually rotatable friction plates that cause production of an oil dragging resistance when the frictional element is under idling condition. With the simultaneously engaged condition of the three frictional elements, each speed is established with a reduced friction loss of the automatic transmission.

Abstract: An automatic transmission comprising: a first planetary gearset of a double pinion; a second planetary gearset of a single pinion; a third planetary gearset of the single pinion, first sun gear and second sun gear being at all times linked together to constitute a first rotary member and second ring gear and third sun gear being at all times linked together to constitute a second rotary member; an input shaft; an output shaft; a first frictional element; a second frictional element; a third frictional element; a fourth frictional element; a fifth frictional element; a sixth frictional element, the six frictional elements being appropriately released or engaged to make a gear shift to a gear shift stage of at least eight forward speeds and, from among the six frictional elements, a combination of simultaneous engagements of three frictional elements achieving at least eight forward speed and one reverse speed.