RAM UNITS IN TRANSMISSIONS OF THE TOROIDAL RACE, ROLLING TRACTION TYPE

Abstract: A hydraulic ram unit for a transmission of the toroidal-race, rolling-traction type. The ram (8) is connected to the rollers (45) of the transmission so that the position of the ram within its stroke is related to the angular setting of the rollers and so to the transmitted ratio. The ram pistons (15) move within cylinders (17) the inlet (71, 73) and outlet (72, 74) ports of which are located in the cylinder end walls (24), with the outlet ports axially proud of the inlet ports. If a piston overshoots its normal stroke it tends first to restrict flow through the outlet port and then to contact and obstruct it, so creating firstly hydraulic and then contact forces to resist further overshoot, without substantially restricting the inlet port. Novel constructions for the ram (8) itself, and for the ram cylinders (17) and casing (1) are also described.

Description: This invention relates to ram units for use in transmissions of the toroidal-race, rolling-traction type. It relates particularly but not exclusively to hydraulic ram units of a known general kind which are mechanically connected to the carriages that support the rollers by which traction is transmitted between the input and output toroidal discs; movement of the ram results in a change in the attitude of the roller, and thus a change in the transmitted ratio also. Such a mechanism as defined in the preamble of claim 1 is described and illustrated particularly in EP-A 78 125. Further examples are described and illustrated in many other published patent specifications, for instance GB-A-2023753 and EP-A-0133330. It has been customary for such ram units to comprise an integral, double-ended piston moveable within a one-piece cylinder liner mounted in a cylinder housing, and for the piston and liner to be manufactured to a high degree of finish and fit by precision methods. Such methods are expensive, especially where the precision-fit piston is made so that its length can be adjusted. In the patent specifications just recited, means are also provided to set up a "hydraulic end stop" effect, to resist and arrest further movement of the ram piston, should the transmission encounter a driving condition in which the rollers tend to overshoot their normal range of attitudes and so be in danger of running off the edges of the toroidal discs. In such conditions, by resisting and arresting the movement of the piston, the corresponding movement of the connected rollers is resisted and arrested also. In GB-A-2023753 the end stop effect is created by a sleeve which fits over the shaft of the ram piston. If the piston overshoots its normal range of movement, the sleeve is mechanically moved so as to alter the normal flow of the operating fluid and trap a volume of fluid which opposes further piston overshoot. In EP-A-0078125 and EP-A-0133330, as in GB-A-2023753, the ram cylinder cavity is in normal use connected both to a pressurized source of hydraulic fluid and to exhaust. In EP-A-0078125 and EP-A-0133330, however, the outlet ports are formed in the cylindrical side wall of the ram cavity, and as the piston head overshoots its normal range of movement it itself covers the outlet port, so automatically raising the pressure of the volume of fluid now trapped in the cavity end. Aims of the present invention include simplifying the ram, facilitating both the adjustment of the piston and the means of connecting it to the rollers, and providing an improved end-stop mechanism. The invention is defined by the claims, the disclosure of which is to be considered as included within the contents of this specification, and the invention will now be described by way of example with reference to the accompanying drawings in which :- Figure 1 is an end elevation of a ram and associated control valve; Figure 2 is partly in plan, and partly a section on the line II-II in Figure 1, with certain parts removed, and Figure 3 is a schematic view indicating the interconnection between the ram and the rollers of the transmission. A block 1 is formed with cavities 2 and 3. Cavity 3 houses a ram 8 of which only part is visible in Figure 2. The ram comprises a central shank 10 into which bores 11 have been drilled from opposite ends. Shank 10 is externally threaded at 12 to receive two oppositely-facing internally-threaded piston head units 13 held in location by locknuts 14. The ends 15 of the units 13 constitute the ram pistons and are formed with grooves to receive PTFE rings 16. Cylinder units 17 are secured to block 1 by studs 18 and nuts 19, and while there is clearance between the cylinders 17 and the pistons 15, the rings 16 establish the necessary sliding and sealing contact of the pistons within the cylinders. Damping of the motion of the hydraulic ram is effected by plungers 25 which slide within bores 11 and are carried on rods 26 flexibly supported by caps 27 in the end walls 24 of units 17. Pistons 15 and cylinders 17 define between them working spaces 29 and 28 at the top and bottom of Figure 2 respectively. Cavity 2 houses a control valve for the ram unit, the valve being essentially of the kind shown in patent specification EP-A-0133330, already referred to. The control valve comprises two similar spools 4, 5 formed with lands 49 and movable within a stepped bore defined by a liner 6. The spools move under the influence of plungers 50, 51 driven by the controlled operation of opposed solenoids which are not shown but are housed within caps 52. Liner 6 fits within cavity 2 and is separated from it by ring seals 53 which divide the annular clearance between liner 6 and block 1 into a number of separated compartments. The stepped bore of liner 6 is formed with a number of ports each communicating, by way of a separate compartment within the annular clearance, with a separate passage formed within block 1. Ports 55, 56 communicate by way of their associated passages with a pressurised source 57 of hydraulic fluid, and ports 58, 59 communicate similarly with a drain 60. Port 61 communicates with an inlet port 71 to space 29, port 63 with an outlet port 72 from space 29, port 64 with an inlet port 73 to space 28 and port 62 with the outlet port 74 from space 28. In normal operation of the transmission, spools 4, 5 are subjected to opposed and variable control forces by the plungers 50, 51. If the force of plunger 50 exceeds that of 51, spools 4, 5 will move downwards as seen in Figure 2. The lands 49 on the two spools will therefore tend to cover ports 56, 59 and to uncover ports 55, 58. Pressure will therefore tend to rise in working space 29 and fall in 28, so that the forces exerted upon the ram 8 by the fluid in the two working spaces tend to move it downwards also. Conversely if the force of plunger 51 exceeds that of 50, the spools 4, 5 will move upwards so as to cover ports 55, 58 but uncover 56, 59, so tending to raise pressure in space 28 but lower it in space 29, so that the ram 8 is urged to move upwards. According to the invention, inlet and outlet ports 71-74 are formed on the end walls 24 of their respective working spaces 29, 28 and while the inlet ports 71,73 open into the base surfaces 76 of those walls, the outlet ports 72, 74 open into steps 77. Each outlet port therefore lies axially proud of its respective inlet port. Therefore if the ram 8 exceeds its normal stroke so that one of the pistons 15 approaches its end wall 24, the piston will first restrict the outlet port and then - if the approach continues - actually contact the step 77 and block the outlet, without obstructing the inlet port in the same way. When the approaching piston restricts the outlet port (72 or 74), as just described, it increases the flow resistance of the port. The pressure in the working space therefore rises, so opposing further overshoot of the ram and thus exerting a "hydraulic end stop" effect. Should the overshoot nevertheless continue, it will of course cease when the forward face of the piston actually contacts step 77. The outlet port will then be completely blocked, and the same region of the end wall 24 which provided the hydraulic end stop effect will supplement it with a physical stop effect also. A rectangular aperture 30, located symmetrically to either side of the transverse centre line 31 of block 1, is formed in the lower wall of that block beneath cavity 3, and a similar but slightly smaller rectangular aperture 32 is formed in the top wall and is normally covered by a plate 33 (Figure 1) held in place by bolts 34. Plate 33 can be removed to allow access for a spanner to flats 35 on units 13, whereby to adjust their positions on shank 10 and so vary the length of the piston assembly. As Figures 2 and 3 show best, aperture 30 accommodates the mechanism by which the piston assembly is connected to the rollers of the transmission, and the movement of that mechanism. A grip 37, clamped to a central boss 38 on shank 10, supports a pivot point for one end of a lever 39. This lever corresponds to item 51 in Figure 1 of specification GB-A-2023753, already referred to, and the other end of it is fast with a sleeve 40 which is rotatable about the input shaft 41 of a continuously-variable-ratio transmission of the toroidal-race, rolling traction type. The transmission comprises at least one input disc 42, secured to shaft 41 in a manner preventing relative rotation of shaft and discs, and an output disc 44. Rollers 45, mounted in carriages 46, transmit drive from discs 42 to disc 44. By means which are well known in the art, but which are not part of the present invention and are therefore shown only schematically at 47 in Figure 3, sleeve 40 is connected to carriage 46 so that rotation of sleeve 40 by lever 39 causes the orientation of rollers 45 to swing in the sense indicated by arrows 48, so varying the transmitted ratio. The annular clearance between piston ends 15 and the inner walls of cylinder unit 17 allows both these parts to be formed by casting or general machining, without the need for expensive finishing, and the PTFE rings 16, like the similar rings 23 on plungers 25, provide both adequate sealing and adequate freedom of axial movement for a reasonable lifetime, after which they can easily be replaced.

Claims: A transmission of the toroidal-race, rolling traction type including: a hydraulic ram comprising a cylinder (17) and a piston (13) movable within said cylinder so that the piston and cylinder define between them a working space (28, 29) of variable volume, the space being bounded at one axial end by the piston and at the other end by an axial end wall (24) of the cylinder; means (37 - 40, 47, 46) to connect the piston to at least one roller (45) of the transmission, whereby the angular orientation of the roller is related to the axial position of the piston within the cylinder; inlet ports (71, 73) and outlet ports (72, 74) to working space, the inlet port being connectable in use to a source of hydraulic fluid under pressure and the outlet port to exhaust (60); characterised in that the outlet port is formed in the axial end wall of the cylinder, in that the inlet port is at least partly formed in the axial end wall of the cylinder, and in that the outlet port lies axially proud of the inlet port, whereby as the piston approaches the end wall the piston tends firstly to increase the flow resistance of the outlet port and secondly to contact the outlet port and so be prevented from further axial movement, without substantially obstructing the inlet port. A transmission of the toroidal race, rolling-traction type according to Claim 1 in which the axial end wall of the cylinder of the hydraulic ram provides a stepped boundary for the working space, in which the outlet port (74) is located on the step (77) but the inlet port (73) is located below it. A transmission of the toroidal race, rolling-traction type, according to Claim 1 including a double-acting hydraulic ram comprising two rams, in which the two ram pistons (15) are formed at opposite ends of a common shank (10) which is connectable in use to the rollers (45,Figure 3) of the transmission. A transmission of the toroidal-race, rolling-traction type according to Claim 3, in which an axial bore (11) is formed in at least one of the ends of the shank, and receives a damping plunger (25) fixed to the corresponding cylinder (17). A transmission of the toroidal-race, rolling-traction type according to Claim 3, in which the piston heads make screw-threaded (12) engagement with the shank (10). A transmission of the toroidal-race, rolling-traction type according to Claim 3 in which the cylinders are mounted at opposite axial ends of a ram casing (1) formed with a first aperture (30) mid-way along its axial length, the aperture providing access for an operating linkage (37-39, Figure 3) to connect the shank to at least one of the rollers of the transmission. A transmission of the toroidal-race, rolling-traction type according to Claim 6 in which the ram casing is formed with a second aperture (32) located substantially diametrically opposite to the first aperture (30) and providing access whereby the axial positions of the piston heads on the central shank may be adjusted.

Inventors: ROBINSON, LESLIE KENDRICK
Applicants: TOROTRAK (DEVELOPMENT) LIMITED
Application year: 1989
Main classification: F16H15
IPC codes: F16H63, F16H15, F16H61