Abstract: A clamping device is furnished, in particular for peeling machines for metallic bars (21) and tubes. The clamping device clamps the workpieces in a defined way at a preselected position (99) and independent of the diameter of the workpieces. The clamping device includes means for synchronization (64-69) of the motion of the clamping rollers (31, 32). The clamping position of the bar to be clamped can be varied by an adjustment device. The means for synchronization (64-69) of the clamping motion transfer a preselectable part of the clamping force, which is furnished such that the means for synchronization are held free from play via preclamping, during in all clamping phases. This eliminates vibrations of the bar (21) together with the clamping means (31, 62; 32, 63) or any undesired shifting of the clamping position.

Abstract: A peeling machine (1) includes individual device groups (2, 5, 63, 7) which can be centered and clamped at guide rails (23, 24). The guide rails also furnish a particular sliding possibility for a selective moving apart of individual device groups (2, 5, 63). This allows for maintenance, inspection, and repair of the device groups, which are made accessible by moving the individual device groups apart without any heavy equipment. The device groups, which are not to be separated during the pulling apart of the peeling machine at the guide rails, are connected to each other (64, 65) such that the peeling machine can be separated and subdivided at the desired location. The guide rails extend parallel to the rotation axis (62) of the cutter head (26) of the peeling machine and can be quickly bolted and released.

Abstract: A rotary driven spindle (6) comprises sliders (14, 64) arranged on its front face, which can be adjusted radially as the spindle (6) rotates. To this end, an adjustment mechanism (21) comprises a device component (8) which rotates with the spindle and which can be moved relative to the spindle in order to adjust the slider (14). The radial centrifugal, frictional and working forces transmitted to the bearing housing (7) by the adjustment mechanism during adjustment of the slider (14) are compensated to a controllable extent by compensation of the centrifugal forces directly between the spindle and the device component (8). The compensation is effected by means of centrifugal weights (16, 66), the centrifugal force of which is deflected into axial forces. In one embodiment, the centrifugal weights (16, 66) penetrate a gap (12, 13) which tapers outward between two front faces (12, 13) of the component and the spindle.

Abstract: A centerless turning machine for rods. The machine includes a cutter-head mounted at the front end of a rotating hollow shaft, and further includes a plurality of advancing rollers of an infeed device operatively mounted at the inlet end of the turning machine. The turning machine further includes a front guide mechanism and a rear guide mechanism, respectively mounted on opposite sides of the cutter head, and also includes a clamping carriage which is mounted on the outlet side of the turning machine. The rear guide mechanism takes the form of a tubular support which is provided with a flange mounted in the machine housing and which extends into the rotating hollow shaft. The rear guide mechanism has, at its free end, which protrudes into the hollow shaft, three individually spring biased guide elements for the rod. The springs for each individual guide element form a first resilient abutment for each guide element. The movements of the three guide elements are synchronized by a rotatable ring.

Abstract: The invention relates to a bending apparatus for wires having a cross section which varies according to their lengths, and comprising two cylindrical sections and an interleaved conical section. The wire is bent by means of three rollers. The bending roller is mounted on a carriage and determines the bending degree imparted to the fed wire. The wire is bent despite its variable diameter so that it is deposited with a regular curvature on the reception plate. To this effect, the curvature of the conical section is changed between the correct curvature of the thinner cylindrical section of the wire and that of the thicker cylindrical section of the wire. It only requires a simple switching at an appropriate time to obtain a sire bobbin which may be deposited on the reception plate. The appropriate switching time is situated between 20% and 60%, but preferably between 30% and 40%, and is calculated from the beginning of the wire diameter increase.