Abstract:
The present invention relates to a transmission system (1) having a differential (10) of the neutral shaft (15) or "zero shaft" type, intended to be fitted to at least one set (12) of front and/or rear wheels of a motor vehicle equipped with a power plant, said system (1) comprising at least one input shaft (11) connected to the power plant, two output shafts (12) connected to the two wheels (12d, 12g) of the set, a neutral shaft (15) for controlling said output shafts (12), characterized in that, with the vehicle being of the hybrid or fully electric type, the differential transmission system (1) further comprises a regenerative braking device (20) mounted on the input shaft (11) and intended to recover the energy of braking and convert it into electrical energy that can be reused immediately or stored in a battery.
Abstract:
The present invention relates to an electric drive system comprising an electric motor (10) arranged to rotate a drive shaft (16); a drive planetary gear configuration (70) being in driving engagement with said drive shaft (16) and an output shaft (50) rotatable relative to said drive shaft (16); and means for providing change in rotational speed of said output shaft (50), wherein said rotational speed changing means (80, 82) are disposed on opposite sides of the motor (10) respectively. The present invention also relates to a motor driven unit, for example a motor vehicle.
Abstract:
A transmission drive system (TDS) for a differential speed steered vehicle, in particular a track-laying vehicle (tank or armored personnel carrier), has two AC induction traction motors, each operatxvely coupled to two semi- independent coaxial traction shafts, and two AC induction steer motors coaxially mounted on a common steer axis parallel to the coaxial traction shafts. A steering gear assembly, preferably between the traction and steering motors, has a common steer input shaft operatively connected to the two AC induction steering motors. Two planetary gear sets have the two traction shafts being operatively connected with one of a two planet gear carriers, or two ring gears, respectively. The other of the planet gear carriers or the ring gears are operatively connected with each other. Two offset gears mounted to the steer input shaft and meshing with two sun gears, respectively, including a reversing idler gear interposed between one of the two offset gears and one of the two sun gears.
Abstract:
A steer-drive interposes respective left and right orbital gear drives (20, 22) into the vehicle drivetrain between the engine/transmission (10, 12) and the respective propulsion axles associated with each side of the vehicle. The orbital drive units comprise only an input gear (54) and an output gear (58) interconnected by at least one orbiting cluster gear (60, 61) that is supported in a rotating housing and also meshes only with the input and output gears. The orbital units are designed so that (a) when rotation of the housing (64) is prevented, driving torque is transferred at speed ratios selected to be as close to 1:1 as is practical, and (b) when steering torque causes rotation of the housing, the steering torque is added simultaneously in equal and opposite directions to the orbital units, causing the drive on one side of the vehicle to slow down at the same rate. The steer-drive is appropriate for the drivetrains of tracked vehicles, boats and airplanes.
Abstract:
An electrically powered vehicle having two primary ground engaging wheels (5) operatively connected to a driving motor (10) by an automatic transmission (50) and to a steering motor (20) by a shiftable bevel gear (7b) which permits opposite variations in rotational speed of the ground engaging wheels (5).
Abstract:
A transmission system for a vehicle comprises a primary shaft (10), a first planetary gear train (22a) and a second planetary gear train. The planetary gear trains comprise a ring gear (12), a carrier (14) for supporting planet gears (26), a first drive shaft mounted on the carrier of the first planetary gear train, a second drive shaft mounted on the carrier of the second planetary gear train, as well as secondary transmission devices for changing the rotation speeds of the ring gears of the first and second planetary gear trains. The secondary transmission devices comprise first control devices for changing the rotation speed of the ring gear of the first planetary gear train, and second control devices for changing the rotation speed of the ring gear of the second planetary gear train, the first and second control devices being independent of each other. Preferably, the ring gears are equipped with an external toothing (34), and said first and second control devices comprise a self- locking worm (20) arranged to engage the external toothing, and a control motor (18) for spinning the worm. In the method, the rotation speeds of the drive shafts of the vehicle are changed by adjusting the rotation speeds of the ring gears by secondary transmission devices independently from each other.
Abstract:
The present invention relates to a driving arrangement (10) for distributing the number of revolutions between two wheel shafts (12a, 12b) of a vehicle by means of a differential arrangement (40), comprising a drive shaft (26) driven by means of a motor arrangement (20), the drive shaft (26) being arranged to drive said wheel shafts (12a, 12b), and means for, by means of a transmission unit (70), providing drive torque change of the driving of said wheel shafts (12a, 12b), characterized in that said differential arrangement (40) is arranged to distribute the number of revolutions between said two wheel shafts (12a, 12b) via a differential shaft configuration (42) drivingly connected to the driving of said wheel shafts (12a, 12b), wherein said differential arrangement (40) is arranged to provide distribution without so called self-locking of the differential arrangement (40), and wherein, by change of number of revolutions of the driving of one of said wheel shafts (12a, 12b), the number of revolutions and hereby the drive torque of said wheel shafts (12a, 12b) is arranged to be distributed equally between the wheel shafts (12a, 12b) by the operation of said differential arrangement.
Abstract:
A controlled differential adapted to couple two shafts (7a, 7b) and steer input, such as those provided in a drive configuration for a skid steered vehicle, the controlled differential comprising: a pair of planet carriers (14a, 14b) arranged to turn with respective shafts; a pair of ring gears (12) interconnected by a cross-shaft such that the ring gears rotate in common; planet gears (11) and a pair of sun gears (10), the sun gears being coupled to at least one steer motor (9) to enable rotation of the sun gears in mutually opposite senses upon input from the steer motor.
Abstract:
A drive configuration for a skid steered vehicle comprises a pair of electric motors (1a, 1 b) for propulsion of the vehicle, one each coupled to drive a respective track (5a, 5b) on a respective side of the vehicle, and one or more electric steer motors (7a, 7b) coupled through a differential gear mechanism (6) to impose a speed difference between the tracks. An associated control system (20, 24, 25, 26) controls the current to each motor so that substantial contributions to the differential torque to turn the vehicle are made both by the steer motors and by the propulsion motors, in variable proportions preferably as a function of the vehicle speed.