Patent GB-526620-A (GB)
Title: Improvements in the production of cross-section profiles bounded by cycloidal curves
IPC: B24B19/08
Filed: 1939-03-23
Abstract: 526,620. Grinding cycloidal surfaces. KRAUSE & CO. AKT.-GES., E. March 23, 1939, No. 9126. Convention date, March 25, 1938. [Class 60] [Also in Group XXII] In a method of and apparatus for grinding or cutting internal and external profiles of cycloidal form, the point C generating the curve, Fig. 1c, lies at one corner of a parallelogram linkage A B C D, the sides A B, A D, of which rotate at predetermined different speeds above the corner point A opposite the tracing point, while predetermined points on lines A B, A D, determine the normal G H C to the curve at the tracing point, the tool and work having relative motions determined by the linkage so that they are always in correct contact at the tracing point C. In Fig. 1c which shows a closed three lobed curve with maximum and minimum radii of R and r respectively, the length of side A D = R+r/2 and length of side A B = <SP>-</SP>R-/2r. The angular velocity of A B about the centre A is in the same direction and of four times the magnitude of the velocity of A D above the same centre A. Thus if # and a + # are the respective displacements from the position where all the links lie in the line E F, Resolving the velocity at C into components v 1  v 2  perpendicular to B C, C D, respectively the resultant v 3  3 is tangential to the curve at C. Drawing the normal C H G perpendicular to C M it is shown by similar triangles that thus the intercepts AG and A H remain constant throughout the motion. In order to impart the required relative motions to the links AB AD, the link AD is prolonged at 1 and carries the wheels 4, 5, of a reverted train giving a 3 : 1 ratio between a wheel 2 connected to side AB and a wheel 6 connected to the curve. Relative to the curve centre line EAF this gearing will give the indicated relative angular movements to the sides AB, AD, in the same direction. In a modification, Fig. 2a, the links AB AD, rotate in opposite directions relative to line E F and α/# = 3, the mechanism being similar to those described above except that the wheel 3 of the reverted train is omitted. Assuming the line A K to be fixed in space the normal H C G remains always parallel to this line and when the wheel 2 and side AB are rotated the normal H C G moves parallel to itself to positions above and below the line A K. So long as the blank has the motion of the wheel 6 it may be arranged at a different place from the gearing, the tool having the same movement as that of the normal H C G. In one machine embodiment, Figs. 3 and 4, a slide 8 adjustable on the bed 7 by a screw 8b carries the centre A of the mechanism constituted by a shaft mounted in bearings 9, 10 and driven at 11. The shaft A carries cranks A G connected at B to link B C and also cranks A H carrying the link 1 of the gearing. The points H and G are guided in slots in a tool-carrying slide 13 and the point C of the linkage is mounted in a bearing in the slide 13. The slide is constrained to move parallel to itself by means of engaging segmental links 16 pivoted at 15 on the slide A and engaging in slotted guides 14 on slide 13. The work W, mounted on a slide 51, has the motion of the wheel 6 transmitted to it through gears 26, 27, shaft 31, bevel gears 36, shaft 37, and bevel gears 38. The grinding disc S driven from a motor 41 is mounted on the slide 13 to that its motion is controlled by that of the tracing point C corresponding to the point of action 45. The grinding-disc may be replaced by a cutting- tool with its edge at point 45.. Since the point 45 is always located in the normal the cutting angle will be constant. The bearings 9, 10 &c. are divided and the slots 12, 12a open-ended so that the parts determining the movement may be readily substituted. A complete unit for determining the motion is shown in Fig. 6, the cranks being replaced by eccentrics, AB corresponding to one parallelogram side end and B C determining the other side. AG and AH represent the cranks and their bearings 21, 22 and 23 roll in slots in the part 13. In another form of machine, Fig. 8, a table 46 movable either by hand-wheel or by hydraulic pistons 48, 49 carries a swivelling upper part 50, the angular setting being determined by gauge blocks inserted between abutments 46a, 50a, and serving to set the machine for taper work. The part 46 has parallel inclined guides 76, 77 and a front guide 78, the weight of the table causing it to bear on the guide 78 so that the intersection 79 determines the direction of the table movement. The part 50 carries a fixed work headstock 51 and a slidable tail-stock. For external work a sleeve 95 driven by a gear 96 may be connected by a split ring 97 to a driver plate 54, the work rotating on a dead centre 53. Alternatively for internal work the plate 54 may be replaced by a chuck and the tailstock not used. The tool slide 8 moves on sloping guides 80 and is adjusted from a hand wheel 56 through gears 57, 58 and nut 59 running on a stationary screw 60. The nut is formed as a piston and can be moved to move the slide through the distance a determined by a cylinder 61. The slide 8 carries the part 13 which supports a built-in motor driving either an external grinding wheel S by pulleys 65, 66, or an internal grinding wheel by other pulleys. Another motor drives the oil pump for supplying the cylinders and a water pump for cooling water which passes round passages in the motor casing and the grinding spindle mounting and thence through a stop cock to a line which directs the water to either the internal or external grinding wheels. A differential piston 84 carried by the screw 60 is always under pressure of the cylinder 83 to take up back lash to the screw and nut mechanism this pressure being overcome when the piston 81 is moved to withdraw the tool slide. The trueing diamond is moved past the grinding disc at the actual point of operation. For this purpose the trueing device has a rockable arm 88 carrying two diamonds 89, 90 separated by a distance a equal to the tool slide withdrawal movement, the diamond 89 serving to true the internal grinding tool S<SP>1</SP> at its zone of contact with the work while the diamond 90 serves when the slide is withdrawn to true a similar zone on the external grinding wheel S, the line of action on the external tool coinciding when this tool is advanced with the line of action on the tool S<SP>1</SP> so that the two tools produce congruent profiles. The tool S may be trued without removing the work The diamonds lie in a plane parallel to the slide 80 passing through the work axis. The diamonds may be adjusted in this plane by a screw 91. In order to provide a frictionless mounting, the part 13 rests at the corner points on ball bearings 98. Lifting of the part 13 is prevented by slotted guides engaged by other bearings 100. The work is driven from a motor 103, Fig. 10, through spur gearing 107, shaft 109, and gear 110 engaging the wheel 11. The gearing connecting the motor to the wheel 11 is mounted in a pivoted casing 111 which may be moved by a block 117 controlled by an eccentric shaft 116 to disengage the drive to the wheel 11 and render the cycloid generating mechanism inoperative. In this position a sleeve 113 is driven from the motor and is connected by a gear 112 to a wheel 26 and thus to the work. In these conditions plain cylindrical work may be performed.