Patent GB-405823-A (GB)
Title: Improvements in or relating to hydraulic variable-speed transmission gear
IPC: F16H39/24
Filed: 1933-03-29
Abstract: 405,823. Hydraulic transmission of power. HEINDL, R., 1, Via Belpoggio Trieste, Italy. March 29, 1933, Nos. 9438, 9439, and 9440. Convention dates, April 23, 1932, Aug. 16, 1932, and Nov. 26, 1932. [Class 69 (ii).] A hydraulic transmission gear comprises members B, C, D, Fig. 1, and an annular space A filled with liquid ; one or more segments A<2> of the space is closed by the walls 16, 18, of the members C, D, an abutment 1 on the member B, and vanes 6, 13 slidable in the members C, D by cam grooves 2, 3. One of the members B, C, or D is the driving member, another is held stationary, and the third is the driven member, the transmission ratio being determined by the relative sizes of the operative pressure surfaces of the vanes 6, 13. Adjustment may be effected by altering the breadth of the space A by axial movement of C or D together with the cam groove 3 or 2, or by altering the breadth of the abutment 1 and the position of the groove 2. In the embodiment shown in Fig. 4, the driving member B is constituted by a shaft 23 carrying a member 28, to which are affixed the outer ends of segmental abutments 1, the inner ends of which are fixed to a sleeve 30. The groove 2 is formed in the sleeve 30, and the groove 3 in a sleeve 38, the sleeve 38 being rigidly connected to key members 37 slidable in the sleeve 30. The driven member D comprises vanes 13 slidable in a block on the driven shaft 41, and engaging the groove 3 preferably through pairs of rollers 14, arranged as shown in Figs. 12 or 13. The normally stationary member C comprises vanes 6 slidable in an axially-displaceable block 5. Control is effected by turning a gear wheel 103. The first part of the movement acts through a cam groove 100<1> and rods 99 to move rods 66 to cause axial adjustment of the block 5 and sleeve 38 ; further movement acts through a cam surface 105 to displace a ring 94 against the action of a spring 92, so as to disengage a coupling 85 when the driving and driven members are rotating at the same speed, thereby allowing the member C also to rotate, followed by subsequent engagement through rods 57 of a coupling 56 which connects the driven and driving shafts mechanically. The vanes 6, 13 have boxes 47, the segments A<2> are connected by channels 64 to an annular chamber 65, and the segments not under pressure communicate with a filled annular chamber 80<1> inside the fixed casing 80. In the modified form shown in Fig. 15, two abutments 1 are secured to the driving shaft 23 or an enlargement thereof, the abutments being preferably integral and mounted in a slot in the shaft, as shown in Fig. 16. Equalization of pressure in the opposite pressure segments is obtained by notches 114 and a bore 115, the other segments being connected by notches 116 and a bore 117 with liquid in the casing not underworking pressure. Charge of working ratio is effected by a worm 120, a worm wheel 119, and a screwed member 116 connected to the body 5 and engaging a member 40 connected to the slidable sleeve 38 in which the cam groove 3 is formed. In order to obtain ease of adjustment, a slot 7 or opposite slots 7 are connected under the control of a valve 125 with a chamber 124, itself connected with a low-pressure chamber 127 under the control of a valve 128. In a modification, the valve 128 and passage 126 are and the valve 125 may be omitted. In a further form, in which control is effected by a manually-operated valve, the body 5 is capable of axial adjustment on a member 130, Fig. 18, which is automatically held fast to the fixed casing 80 by a one-way clutch 131, when the body is in such a position that pressure acts on the vanes 6. When the body 5 is in its outermost position as shown, a chamber 124 communicates with a low-pressure chamber 127. Movement of the valve 141 to the right first closes this communication by shutting the port 149, and then puts a slot or slots 7 into communication with the chamber 124 through ports 147, 148, so that the working pressure moves the body 5 to the right until the port 148 is closed. In a further modification, control is effected by a valve 163, Fig. 21, automatically operated by torque variations, the action being also dependent on the power output of the prime mover. The valve is shown in its mean position, and is oppositely acted on by a spring 174 and the pressure in a chamber 169 connected by a bore 172 with the pressure spaces of the gear. Torque variations move the valve in one or the other direction to place a chamber 124 into communication with the chamber 169 or a'lowpressure chamber 127 to effect movement of the body 5<1> to vary the transmission ratio. The valve has inclined grooves 178, 179, and may be turned by a gear wheel 166, operated by connections with the throttle lever of the prime mover or independently thereof. Two of the members of the gear may be connected to parts of an epicyclic gear, and the load on thrust bearings may be relieved by pressure liquid acting on suitable surfaces.