Patent GB-1109127-A (GB)
Title: Hydrostatic transmission
IPC: F16H61/46
Filed: 1965-04-27
Abstract: 1,109,127. Hydrostatic transmissions. SUNDSTRAND CORPORATION. 27 April, 1965 [16 Sept., 1964], No. 17755/65. Headings F2C and F2D. A hydrostatic transmission comprises a fixed displacement motor 16 and a swash plate pump 14 having a pressure moment acting through the axial pistons on the swashplate when inclined from neutral to return the swashplate to neutral and being proportional to the pressure in the high pressure side of the pump, and a torque valve 108 controlling the supply of fluid to cylinder 28 or 30 controlling swashplate 24 to establish a predetermined system pressure proportional to the manual pressure on valve 108, and means responsive to pressure in cylinders 28 or 30 to return valve 108 to a central position when the predetermined system pressure exists. A pump 44 delivers fluid to conduit 82 and make-up check valves 52, 54 and draws fluid from reservoir 46 connected by a heat exchanger 69 and valves 59, 60 to conduits 20, 22 between motor 16 and pump 14, these conduits being also connected to high pressure relief valves 57, 58. The transmission is intended for an agricultural combine driven by a constant-speed prime-mover, and provides two modes of operation; a first mode, for agricultural use, giving a constant selected speed-ratio independently of the load; and a second mode, for highway propulsion, varying the speed-ratio to produce an output torque determined by the setting of the torque-valve 108, the manual control of which is then used rather like the accelerator-pedal of an existing vehicle. For this purpose the pressure-supply to the swash-plate-tilting cylinders 28, 30, is selectively controlled either by a manual displacement valve 81 for the first mode, or by the manually-loaded torque-valve 108, for the second mode, according to the setting of a manual selector valve 113, the valves 81, 108 being connected by a conduit 82 to the control pump 44, which is also driven by the prime-mover. With the selector valve 113 set for selected constant speed-ratio (first mode) the manual displacement valve controls swash-plate inclination by follow-up servo action as follows. A hand lever 74 is moved in one direction or the other, for forward or reverse, to a selected setting and acts through a spring 77 and floating lever 87 on the spool 86 of the displacement valve 81, which then pressurizes the swash tilt cylinder 28 or 30 from the control pump 44 through conduit 111 or 111a, the selector valve 113, and conduit 112 or 112a. The subsequent tilting of the swash-plate laps the valve 81 back to neutral through the floating-lever 87, leaving the swash plate in the desired constant setting. The second mode of operation, viz. torque control, depends for its action on the fluid pressure moment acting on the swash plate due to the following factors. The axial cylinders of the pump 14 are grouped uniformly around the centre of the swash-plate, so that static pressure on the pump pistons would have no tendency to tilt the swash-plate. However, due to compressibility of the liquid and porting delay, the rate of pressure increase in a compressing cylinder is less than that of pressure reduction in an exhausting cylinder, resulting in a stroke-decreasing tilting moment on the swash-plate, which appears as a fluid-pressure signal in the cylinder 28 or 30 which is directly proportional to pump delivery pressure and hence to output torque. This fluid-pressure moment reacts on the torque-valve 108, which is constructed as a manually loaded pressureregulating valve, so that swash-plate inclination is automatically varied until output torque corresponds to the torque-demand set by the torque-valve 108. The valve 108 has manually or pedally operated plungers 114, 115 for forward and reverse, respectively, acting through springs on spools 118, 119 controlling fluid flow from pump 44 to cylinder 28 or 30 via conduits 109, 109a, suitably adjusted valve 113 and conduits 112, 112a. The system pressure in conduits 109 or 109a acts via passage 125 or 124 on valve spools 118 or 119 to move the spool back to its shown central position. Control cylinder 28 or 30 will oppose the fluid pressure moment so that as load on shaft 19 increases above the setting of plunger 114 or 115, the pressure moment tends to move the swashplate in a stroke reducing direction causing a pressure rise in cylinder 28 or 30 and conduit 109 or 109a which moves spool 118 or 119 to permit movement of the swashplate toward neutral. To decelerate shaft 19, plunger 114 or 115 is released to decrease the system pressure allowing springs 32 or 34 in cylinders 28 or 30 to move the swashplate to neutral; for a faster deceleration the opposite plunger may be depressed. In Fig. 2, not shown, the torque valve has a single plunger and valve 113 is omitted, the torque valve being in series with the speed valve and either may be preset and the other utilized to control the transmission.