Patent GB-1124931-A (GB)
Title: Hydrostatic power transmission
Inventor: FLINT JOHN CHRISTOPHER EGLINGT
IPC: F16H39/14
Filed: 1965-03-01
Abstract: 1,124,931. Hydrostatic transmission. DOWTY TECHNICAL DEVELOPMENTS Ltd. 7 Feb., 1966 [1 March, 1965], No. 8705/65. Heading F2C. [Also in Division F1] A continuously variable hydrostatic transmission comprises piston - and - cylinder type pump and motor units, each comprising a rotary cylinder block 7, a valve plate 12 having two arcuate ports 15, 16 with which the cylinders are alternately connected during block rotation, and means to adjust the plate 12 about the block rotation axis to vary effective displacement of the unit by varying the phase angle between piston reciprocation and alternate connection between the cylinders and the arcuate ports 15, 16. The pump and motor may be relatively remote or, as shown, connected to form a single transmission unit. The pump or motor unit or both may have cylinders parallel or nearly parallel to the block rotation axis. As shown, pump and motor casings 1, 2 are bolted to a central valve head 3 and comprise stationary, fixed inclination swash plate surfaces 9, 26 engaged by pump and motor pistons which may be provided with slippers. The pump and motor cylinder blocks 7, 24 are rotatable with, but axially slidable on, coaxial driving and driven shafts 4, 21. The arcuate ports 15, 16 and 31, 32 of the pump and motor valve plates 12, 29 may co-operate, as shown, with two main passages 17, 18 extending through the valve head 3. Alternatively, the valve plate ports and valve head passages may co-operate at cylindrical surfaces to avoid unbalanced hydraulic forces; or the valve plates themselves may have cylindrical surfaces and fit one within each cylinder block. The ports 15, 16 and 31, 32 have equal areas in the opposite surfaces of each plate. The distance between adjacent ends of the valve plate ports approximately equals the arcuate length of each cylinder port. The valve plates 12, 29 are adjusted between limits about the shaft axis by racks 14, 30 meshing teeth on the valve plate peripheries. The adjustment limit prevents overlap between the main passages 17, 18 and the valve plate flat surface portions, to avoid unbalanced hydraulic forces. Small centrifugal pressure developed by rotation of the block 7 in the casing 1 forces liquid from a sump 33 through a filter 34, an external coiled pipe 35, the valve head 3 and non-return valves to the main passage 17 or 18 which is at the lower pressure. Leakage from the motor casing 2 flows back to the sump 33 through a valve head passage 38. Liquid topping-up is through a filler 37. A high pressure relief and other conventional valves are provided, preferably in the valve head 3. A driving shaft mounted fan 36 cools the pipe 35. Although not shown, the swash-plate surfaces 9, 26 are phased at about 90 degrees to each other to enable the passages 17, 18 to extend parallel to the shaft axis. Operation. Forward.-With the motor valve plate 29 set for maximum effective motor displacement, approximately 70 degrees rotation of the pump valve plate 12 in one direction from a zero (neutral) to a maximum effective displacement position provides approximately 1/1 Forward drive. To increase motor speed to twice pump speed, the motor valve plate 29 is rotated approximately 60 degrees in the same direction to its approximately half displacement position. Reverse.-The pump valve plate 12 is rotated approximately 30 degrees in the opposite direction, the motor valve plate 29 being moved to its maximum displacement position for a slow reverse drive or to its half displacement position for an increased speed reverse drive. The pump and motor valve plates 12, 29 may have a single or separate controls.