Patent GB-983256-A (GB)
Title: Improvements in hydraulic transmission systems
Inventor: FIRTH DONALD
IPC: B60K17/10
Filed: 1962-03-08
Abstract: 983,256. Hydraulic transmission of power; fluid-pressure brakes. COUNCIL FOR SCIENTIFIC & INDUSTRIAL RESEARCH. Feb. 26, 1963 [March 8, 1962], No. 9029/62. Headings F2C, F2D and F2F. [Also in Division B7] An hydraulic transmission for motor cars &c., comprises a variable capacity positive displacement pump feeding a positive displacement motor, an adjustable throttle valve in the return circuit of the motor, and an hydraulic accumulator selectively connected to the pump or to the motor. As shown, a pump 2, Fig. 3, driven by an I.C. engine 1, feeds through a pipe 6 to motors 3 powering the car road wheels, and thence to a return pipe 7 containing a reversing valve 39 and a throttle valve 11. Release of the car speed control pedal for braking partially closes the throttle valve 11, which is in series with a valve 30 actuated by a double-acting two-piston servo 31, 32 subjected to the pressure differential across the throttle valve, to control the pressure in a pipe 35 which can be connected via a two-way valve 28 to an high-pressure accumulator 27. The two-way valve 28 is connected to the speed control pedal which is connected to the fuel injection pump of the engine 1, so that when the speed control is set for the engine to drive the car &c., the accumulator is in communication through the valve with the downstream pipe 27, and has exhausted itself into the system. When the speed control is set to idle, the valve 28 is changed over to connect the pipe 35 to the accumulator 27; however, a resistance pressure in the accumulator, e.g. from compressed air, is sufficient to prevent the accumulator from filling at this stage. By actuating a brake pedal to slow the car, the valve 11 is biased to close, thus loading the pumps 3 &c., and the pressure differential across the valve 11 causes the servo 31, 32 to close the valve 30, so that pressure in the pipe 35 increases and the accumulator 27 is charged. When the pressure in the pipe 35 &c. reaches a predetermined maximum, a valve 37 opens and the servo 31, 32 is moved to open the valve 30 once more. If the speed control is now returned to its drive position, the two-way valve 28 is restored to the position shown, and the accumulator 27 discharges into the pipe 7a &c. to aid acceleration of the pump 21 &c. During reverse running, the reverse valve 39 is operated to isolate the accumulator 27. A low-pressure accumulator 33, connected on the downstream side of the valve 30 through a cooler 25, discharges into the system to make-up the oil received into the high pressure accumulator 27 via one-way valves 10a, 10b. The low-pressure accumulator 33 may consist of a piston 73, Fig. 7, biased downwards against the pressure of oil in its reservoir chamber by two springs 78, 79, the first acting directly on the piston and the second abutting a thrust ring slidden upwards by the piston when the accumulator has been charged, the stem 74 of the piston then successively uncovering valve ports 76 venting excess oil to the sump 5. In a modification, Fig. 8 (not shown), the low and high-pressure accumulators 33, 27 are in a common cylinder and are mechanically ganged together. Control of the vehicle may be effected by a single pedal 47, Fig. 9, acting through a link 49 on the throttle valve 11 for braking in the transmission, and simultaneously acting upon a spring 44 biasing a control cam 40 downwards against the action of engine-driven centrifugal governor masses 43. The control cam 40 has two frusto-conical and one cylindrical surface engaged by two followers 50, 51, the follower 50 actuating the control rack of the fuel injection system of the engine, and the follower 51 actuating the changeover valve 28, Fig. 3. The pedal 47 also actuates two cams 54, 55 engaged by followers 56, 57, effecting adjustment of the capacity of the pump 2 and motors 3, and hence of the ratio of the transmission. In one modification, Fig. 11 (not shown), axial displacement of the cam 40 in dependence on speed is effected by an hydraulic servo fed with speed-proportional pressure from an engine-driven pump. In another modification, Fig. 12 (also not shown), the followers 50, 51 are acted upon directly by two simple liquid servos mechanically interconnected and operated in dependence upon engine speed and control pedal position. Alternatively, speed control may be effected by an electric tachometer device. In descriptive Fig. 1 (not shown), the accumulator is omitted and a shuttle valve, connected across the inlet and outlet pipes, is operated by the differential pressure between them to connect the low-pressure pipe through a cooler to the sump. Maximum pressure in the circuit is limited by a pressure-relief valve. The throttle valve in the hydraulic circuit is connected to a brake pedal simultaneously actuating the conventional service brakes of the motor car. In descriptive Fig. 2 (also not shown), the brake pedal is connected to the engine fuel supply device.