GB876932A - Improvements in or relating to a method and a machine for the cold form generating of profiles on cylindrical workpieces - Google Patents

Abstract

876,932. Rolling profiles. MAAG-ZAHNRADER & -MASCHINEN A.G., MEYER, A., and WENGER, O. May 15, 1959 [May 16, 1958], No. 16827/59. Class 83 (4). In a method of cold-forming profiles on cylindrical workpieces, e.g. on steel rods, the generating tool, which forms the profile without cutting, has a movement directed towards the longitudinal axis of the work in a plane comprising the profile track, the movement being of smaller dimension than the height of the profile, the work being simultaneously rotated in synchronism with the rotation of the tools and relative axial feed being provided between the work and the tools. Work A, Fig. 1, is profiled by generating worms 1 which execute a rapid movement in a flat elliptical path C so that the worms engage the work intermittently while the worms and the work rotate and the work is fed slowing axially. Tool-holders 3 are pivoted about an axis Y to suit the required direction of the profile, e.g. Fig. 7, which shows a helical profile. The shafts 5 of two or three worms may be geared together for synchronous working. To avoid deviations in the direction of the profile, an axial reciprocation may be imparted to the worms 1 and an additional oscillating rotation superposed on the rotation of the work about its longitudinal axis, the oscillating rotation being synchronized with the axial reciprocation of the worm. In a modification, the tools may be fed axially of the work which is held axially stationary. Splined shafts are produced or long profiled bodies which may be subsequently cut into individual spur or helical gears. Alternatively, a number of blanks may be clamped together for profiling. A machine Fig. 8, for profiling cylindrical work A comprises a headstock 11 slidably mounted on a guide 10 and having a clamping device 12 for clamping one end of the work A. An hydraulically-fed counter-support 14 supports the other end of the work and is slidable on a guide 13. Toolholders 3 support the worms 1, the tool-holders being slidable axially of their pivoting axis Y to permit the radial component movement of the elliptical oscillating movement C. A pivoting support 26, Fig. 9, for the tool is provided on each holder 3. The movement C is effected by a motor 16 and an hydraulic supply which actuates pistons 18 and 19, Fig. 9, provides the radial and axial components of the movement, the slide support 28 being slidable on the tool-holder 3 in the plane of the profile and the drive to the worms 1 being through cardan shafts 33 to permit such movement. Return movement of the tool-holders is effected by continuously-applied hydraulic pressure. Radial adjustment of the toolholders for the particular diameter of work is effected by annular nuts 24 fixed in the machine housing 22, a manual drive 25 being provided for simultaneous adjustment of both toolholders. A motor 46 drives the worms 1 through a belt drive 45 and shafts 47, 43, 40, 37, 34 and 33, a differential 42 being included between the shafts 40, 43 and a clutch 38 being provided for phase adjustment of the worms. For synchronizing the rotation of the work with that of the tools pick-off gears 48 engage with the shaft 47 and drive a spline shaft 49 connected to gearing 50 in the headstock 11. The work is fed axially by gearing 51, driven by the shaft 49, the gearing 51 engaging with a shaft 52 and a feed nut 55, a clutch 53 being provided on the drive. When forming helical gears the additional rotation of the tools required relative to the work is applied through a shaft 57, pick-off gears 58, a shaft 59 and differential gearing 42. A profile-directioncompensating axial reciprocation of the worms is effected by a piston 63, Fig. 9, and Fig. 11 which actuates wedges 65 in the support 28 through a pinion 64. Alternatively, a piston 70, Fig. 12 (not shown), may operate wedges through a linkage. A synchronous compensating oscillating rotary motion is also superposed on the constant rotation of the work by an hydraulically reciprocated partial worm 72, Fig. 13 (not shown), which oscillates a worm 73 connected with the gearing 50. The motor 16 produces both compensating movements through a cam-drive which is adjustable relative to the cam-drive for the movement C.