Patent GB-718101-A (GB)
Title: Improvements in or relating to bevel gear generating machines
Inventor: DEAKIN THOMAS MEYRICK
IPC: B23F5/06
Filed: 1951-06-27
Abstract: 718,101. Gauging toothed gears. DEAKIN GEARS, Ltd. June 26, 1952 [June 27, 1951], No. 15306/51.' Class 106 (2). [Also in Groups XXII and XXIII] A bevel gear generating machine for forming or measuring bevel gear profiles, in which the gear is rolled on a plane 3-3, containing a generator represented by the tool or in which the finished gear is meshed with a master gear or tooth represented by the tool, and in which the roll ratio is adjusted by permanent components of the machine, comprises means for controlling the angular displacement of the work axis to modify the tooth shape or profile. The machine as shown is for cutting straight toothed bevel gears, and is similar to that described in Specifications 689,192 and 712,038. The generating motion represents the rolling of the pitch cone of the work 1 on the plane 3-3 against a recipro-. cating grinding wheel 2 so forming an octoid tooth, the line of contact between the tool and the finished flank lying always close to, and at one point on, the plane 3-3. For a spherical involute tooth, the base cone of the gear is rolled on the plane and the line of contact would then always lie in the plane 3-3. The work 1 is mounted on arcuate guideways 108 on a frame 105 oscillating about the axis W of the machine concentric with the axis of the base disc 8 to which a limited displacement can be applied to feed the work an additional amount towards the tool either in intermittent increments for the purpose of depth of cut feed or momentarily for tip or root relief or crowning. When measuring a profile the extent of feed required is a measure of the inaccuracy of the profile. A displacement corresponding to one tooth pitch provides an indexing movement of the blank. For crowning a tooth, a displacement of the tool as well as a displacement of the work is required in order to maintain a correct tooth profile. The displacement of the base disc 8 is controlled by three cams 27, 28, 30. The cams 27, 28 operate through followers on a lever 22 freely mounted for vertical movement in fixed guides, a slide 17 adjustable in length for tooth thickness by a wedge 19, sine bars 15, 16, either one of two followers 13, 14 according to which side of a tooth is to be ground, and a slide 12 connected to the disc 8 by tapes on a sector 11. The cam 27 is effective to feed the work into the tool and may be rotated continuously or at one or both ends of the traverse of the wheel 2. The cam 28 is effective to provide tip or root relief and is rotated for a portion only of the generating roll. The cam 30 displaces the slide 17 laterally either directly or through tape mechanism 155 and iseffective to crown the teeth. A cam 31 is rotated simultaneously with the cam 30 to move the tool 2, in a direction normal to its reciprocating movement, through a crank 33 and tapes 36 mounted on a drum 35 and attached. to the tool slide 37, so maintaining the tooth profile. The followers 13, 14 may be set on the slide 12 so that the blank is correctly indexed to present the opposite flank of a tooth to the oppositely facing grinding wheel 2, when the slide is moved to bring a follower against its sine bar. Additional movement of the slide 12 may serve to index the work through a tooth space. The tools 2, 2<SP>1</SP> are arranged either to straddle a tooth-space or a tooth. Each tool is mounted on a slide 40 and is rotated by a motor 198 mounted on the slide 37. and driving through belts 195. 196, 197 supported by belttensioning devices 204, 205 Each tool-sLide 40 is reciprocated by a motor 189 and crank mechanism 190 mounted on a slide 42 which is movable to and from the work by a hydraulic device, 184 on a slide 43 which is adjustable angularly on a bracket 175 according to the required dedendum angle for octoid teeth. The tool slides are moved respectively into and out of operative position simultaneously with movement of a master piston, and cylinder device 186 connected between the base slide 12 and the frame 105 to bring into operation the required follower 13 or 14. The bracket 175 is itself adjustable angularly according to the required pressure angle. The tool assembly is mounted on the common slide 37 which is moved during crowning. The frame 105 is oscillated by an electric motor 126 driving through shafts 121, 120, 119, 117, 112 and crank 110. The crank reciprocates the slide 6 of the generating mechanism. The motor 126 also rotates the feed and tip relief cams 27, 28 which are interconnected by gearing 164 according to the number of lifts per cam. The tip relief cam 28. Fig. 11, has one lift and is therefore rotated at three times the speed of the feed cam 27 which has three lifts. The two crowning cams 30, 31 are rotated by an electric motor 165. The tapes 36 are connected to the slide 37 by way of a slide 167 which may be adjusted by screw means 170 if it is required to offset the tool permanently. The machine may be modified in the following respects:-the hydraulic cylinders 184 may be replaced by equivalent electrical or mechanical means and the drive from the motor 126 to the slide 6 wholly or in: part by electrical or hydraulic means: the pressure angle adjusting brackets 175 may be interconnected to move in unison: and the cams 27, 28, 30 may be, replaced by screw gearing.