GB585629A - Universal joints - Google Patents

Abstract

585,629. Universal joints. DARLI INDUSTRIAL MANAGEMENT, Inc. April 7, 1944, No. 6532. Convention date, April 2, 1943. [Class 80 (ii)] Relates to a constant velocity-ratio universal joint of the kind wherein tongue-and-groove intermediate members 40, 39 are pivotally mounted on the respective shafts 36, 35 by pins 42, 41, the shafts being mounted in non-rotating bearings 38, 37, connected for pivotal movement in one plane as by a pivot-bolt 45, Figs. 2 and 7, or by complementary spherical shells 50, 51, Fig. 9. In such a joint the distance between the centres of the hinge-pins 41, 42 of the intermediate members 39, 40 varies with the included shaft-angle so that axial clearance 48 between the members 39, 40 must be provided to prevent jamming. This joint is required for shiaft-inclinations which are substantially greater to one side of the aligned position than the other and, in order to reduce axial clearance to a minimum, the pivoting axis 45 of the non- rotating shaft-bearings 37, 38 is offset from the shaft axes in the direction in which the greater inclination is desired. The correct position for the shaft-bearing pivot-axis 45 is determined by arranging for the distance d, Fig. 1, between the centre-points 23, 24 of the intermediate-member hinge-pins 41, 42 in one extreme position, with an included shaft-angle a, to be the same as that, d between the same points 23, 24<1> in the other extreme position, with an included shaft-angle a2. The distance d is then a minimum in each extreme position so that a suitable axial clearance 48, Figs. 2 and 7, for such positions can be determined, and jamming in intermediate positions is avoided. The shaft-bearing pivotaxis 45, Fig. 1, must, for this purpose, be equidistant R from all the points 23, 24, 24' and its perpendicular distance from either line d is given by d/2 tan a1-a2/4. Calculations for a range of angular movement of a1=180‹ to a2=90‹ are included. The pivot-bolt 45 of the shaft-bearings 37, 38, Figs. 2 and 7, is tightened to clamp the bearings at any chosen inclination. In Fig. 9, the non-rotating shaft-bearings are integral with oilretaining spherical casing-elements 50, 51, centred about an axis 52 which is offset from the shaft-axes, and capable of being clamped in the set positions by an external ring 53. To prevent spread, the faces of the grooved member 39 may be tied together by a bolt passing through a clearance hole in the member 40. The sliding faces of the member 40 may carry oilimpregnated pads of felt or porous metal, or the faces may be recessed for a cage of ball thrustbearings. The Specification as open to inspection under Sect. 91 states also that the position of the shaftbearing pivot 45 may be automatically varied by cam control means so as always to lie in the correct position for all shaft inclinations. The distance d, Fig. 1, may alternatively be held constant at all shaft-angles by relative axial adjustment between the shafts and their bearings or the shaft-bearing pivot 45 may incorporate suitable adjusting means for this purpose. This subject-matter does not appear in the Specification as accepted.