CN1729070A - Tool head, adjuster ring and cutting machine in particular a scalping machine - Google Patents

Abstract

According to the invention, the wear in the region of the tool head of a tool machine, in particular a scalping machine for machining long workpieces with a round cross-section may be reduced, whereby a tool head with a tool holder is adjustable essentially axially to the rotation axis, in which the tool holder and the adjuster device each have planar slide surfaces which correspond with each other.

Description

Cutting heads, adjusting rings and machine tools, especially dehulling machines

The invention relates to a cutting head having a tool holder which is mainly adjustable radially relative to an axis of rotation and an adjustment device which is mainly axially adjustable relative to the axis of rotation, wherein the tool holder and the setting device are on sliding surfaces co-operate. The invention also relates to an adjusting ring for adjusting a tool holder relative to an axis of rotation, wherein the adjusting ring has a conical inner surface for forming a sliding bearing shell. Furthermore, the invention relates to a machine tool, in particular a dehulling machine tool, for machining longitudinally extending, in particular cylindrical and conical, circular cross-section workpieces.

Known dehulling machines have a milling head that rotates about a rotational axis or about a machining axis and has an adjustment device for a tool holder that is swiveled by the milling head. By means of the adjusting device, the tool holder is adjusted relative to a workpiece by the tool arranged on it in such a way that the tool removes, for example, an oxide layer of a hot-rolled material, so that after the round material has been processed, the result is a metallic round material. .

Such a dehulling machine is described in DE 101 29 207 A1, wherein an adjustment device displaceable relative to the hollow shaft is arranged at a milling head. Depending on the displacement of the adjusting device, the tool holder or a tool arranged thereon is moved radially relative to a machining axis. As a result, the tool can be individually adjusted to the diameter of a matrix material to be processed. In particular, very high forces and thus a very high surface pressure are present at the contact surface between the tool holder and the adjustment device, which leads to severe wear not only on the adjustment device but also on the tool holder.

However, the present milling head has a significant disadvantage, since such an adjustment device can only be replaced with considerable assembly effort and considerable expense. Of course, there are also disadvantages with regard to the wear of the tool holders, since a relatively complex assembly has to be carried out in order to replace such tool holders. In connection with this, it often happens that the rotary tool adjustment device on the milling head must be completely disassembled in order to replace worn structural parts. Despite these apparent deficiencies, no solutions to overcome these deficiencies have been proposed so far.

Known by DE 195 03 772 A1 in addition a device for removing the bark of round pipes and round rods. The descaling is performed here by a plurality of descaling knives rotating around a descaling workpiece, which are each arranged on a rod-shaped tool holder. The tool holder is radially displaceably mounted relative to the longitudinal axis of the descaling workpiece and is also mounted relative to the inner surface of a taper sleeve. As a result, the forces acting on the tool, in particular mainly radially with respect to the longitudinal axis of the debarked workpiece, are transmitted via the tool holder to the taper sleeve and from there to the machine frame . However, replacement of structural components still under load, such as tool holders and taper sleeves, is also only possible with considerable assembly effort.

It is therefore the object of the invention to reduce wear on the milling head and to avoid complex assembly work for as long as possible.

This object of the invention is achieved by a cutting head having a tool holder which is mainly adjustable radially with respect to the axis of rotation and an adjustment device which is mainly axially adjustable with respect to the axis of rotation, wherein the tool holder and the adjustment device The respective sliding surfaces cooperate with each other and these sliding surfaces are substantially planar. Unlike the conical sliding surfaces of the previously known adjusting device and the corresponding tool holder, the adjusting device according to the invention and the tool holder according to the invention have a substantially planar sliding surface, so that they cooperate with each other and In particular, machining forces acting radially relative to the axis of rotation are transmitted from the tool holder to the adjusting device.

In contrast to the prior art, the present invention therefore dispenses with a cone for the adjustment device in the area where the main adjustment force is generated. Instead, a flat surface is used in this area, so the contact surface is largely irrelevant for adjustment.

According to the invention, this reduces the risk that only a linear contact occurs between the sliding surfaces, and thus only a small portion of the counter-sliding surface receives and transmits forces, so that this small portion is fully exposed to a large load. A particularly good force distribution is achieved by the substantially planar sliding surface, so that surface pressures occurring in the region of the planar sliding surface can generally be fully absorbed by the entire sliding surface.

This results in a significantly increased service life of the cutting head according to the invention compared to conventional cutting heads.

The concept of "plane" or "planar sliding surface" in the sense of the present invention is to be understood as a surface suitable for creating a sliding surface and essentially without curvature, thus reducing the possibility that two cooperating planar sliding surfaces only contact each other in a straight line Danger. With planar sliding surfaces are meant, in particular within the range of usual measuring accuracy, planes which are in contact with each other over the largest possible surface area.

Wear can be avoided particularly economically by means of flat sliding surfaces. On the other hand, a curved surface with a constant radius of curvature parallel to the axis of rotation can also be advantageous, since in this configuration the radius of curvature of the sliding surface does not change due to the adjustment travel, as is the case with conical surfaces. Therefore, the basic idea of the present invention is to specify a sliding surface whose radius of curvature does not change relative to the adjustment device along the displacement path of the tool holder, wherein a flat sliding surface can also be regarded as a sliding surface with an infinite radius of curvature .

The adjusting device and the tool holder of the cutting head according to the invention have a particularly high life expectancy if the sliding surfaces are additionally hardened.

In a related embodiment variant, at least one sliding surface has a lining, which preferably consists of a wear-resistant material. This liner can be quickly and economically replaced when required. Although it is also possible to separately harden the planar regions of the mostly conical configuration of the adjustment device as described above. However, this is very expensive, so that a very cheap and thus also economically advantageous wear-resistant flat sliding surface is provided by the lining.

It is also advantageous if the lining is a hardened metal plate. As a result, the production costs of the tool holder adjusting device can be further reduced, since the remaining structural components do not have to be subjected to a further surface treatment process. This likewise further reduces processing costs. The realization of a flat sliding surface by using a hardened metal sheet advantageously enables the use of a standard component for forming the flat sliding surface, which can be processed particularly economically as a mass-produced product.

The use of a lining made of a wear-resistant material results on the one hand in softer structural component adjusting device and good damping properties of the tool holder, and on the other hand achieves a wear-resistant structural component surface lining. The adjusting device and the tool holder are thus particularly well protected against premature wear, and the adjusting device and the tool holder can also still dampen mechanical shocks well without risking premature damage as a result.

It is particularly advantageous if the lining is fastened replaceably to the adjusting device and/or the tool holder. It goes without saying that such a lining can be arranged on the adjusting device or on the tool holder in various ways. For example, the backing layer can be glued. It is also advantageous if the lining is detachably and replaceably attached to the adjusting device and/or the tool holder by a screw connection, for example by four cylinder-head screws.

In particular with regard to the lining of the threaded connection, there is the possibility of replacing a worn lining with a new lining without having to completely replace the adjusting device or the tool holder. Disassembly of the cutting head is thus avoided as much as possible.

In a special embodiment, the adjusting device also has a taper sleeve. A tapered sleeve is adapted to offset axially along a shaft and also to displace other structural components radially relative to the shaft through its tapered structural assembly. In particular, the advantages of a tapered sleeve can be fully utilized for other structural components, while wear on highly loaded surfaces is minimized due to the sliding surface according to the invention.

The taper sleeve is preferably an adjusting ring. As a result, it is structurally particularly simple to realize an adjustment device, which can also be shifted relative to a hollow shaft.

In order to make the sliding surface of an adjusting device and the sliding surface of a corresponding tool holder contact each other as large as possible, it is advantageous if a planar sliding surface of the adjusting device is substantially parallel to a mating sliding surface of a tool holder, Preferably a planar sliding surface of a tool holder is provided. A particularly good functional contact and a good force distribution with a correspondingly low surface pressure over a region of the sliding surface that is as large as possible results from a good parallelism between the two sliding surfaces.

The object of the invention is also achieved by an adjusting ring for adjusting a toolholder relative to an axis of rotation, wherein said adjusting ring has a conically structured inner surface for forming a sliding bearing surface and the conical The shaped plain bearing shell surface has at least one substantially planar plain bearing region.

It is therefore particularly advantageous if the inner surface of the setting ring forms a sliding surface at least in regions, in particular at the sliding surface. This results in a force transmission over a large area between the setting ring and a tool holder, which significantly reduces the load on the structural components at this point.

On the one hand, the adjusting ring can make use of rotationally symmetrical sliding surfaces, which also allow a particularly simple constructional displacement of the adjusting ring relative to a hollow shaft. On the other hand, the adjusting ring according to the invention is very stable against wear at a particularly heavily loaded point where the adjusting ring comes into functional contact with the tool holder on its sliding surface according to the invention. This significantly increases the service life of the adjusting ring.

It is particularly advantageous if the plain plain bearing points are detachably and replaceably fastened to the setting ring. When the sliding bearing area is worn, the entire adjusting ring does not have to be replaced immediately, but only partly at the sliding bearing surface. This also reduces maintenance costs, since the adjusting ring itself can be used significantly longer.

A wear-resistant sliding bearing shell surface is realized in a structurally particularly simple manner if the plain bearing part has a lining which, as a wear ring, has hardened material properties. This liner is preferably a standard component which can be produced in large quantities. It goes without saying that the lining can be hardened more easily than the inner side of the plain bearing surface of an adjusting ring.

Furthermore, the object of the invention is achieved by a cutting machine for machining linear workpieces, in particular a dehulling machine, which has a cutting head and/or an adjusting ring for adjusting a tool holder having at least one of the above-mentioned features.

Especially for a dehulling machine tool additionally or alternatively a feed mechanism is proposed, which has feed rollers for accelerating workpieces, especially rods, tubes, rods, wires, steel cables or similar materials, in which machine tools The middle feed rollers are each driven via a feed roller shaft, wherein at least one feed roller shaft is mounted eccentrically in a shaft seat. The feed roller shafts, that is to say the drive shafts of each feed roller, are advantageously mounted in the axle mounts in such a way that when the axle mounts are rotated about their longitudinal axes, the feed roller shafts are deflected. In this way, an adjustment mechanism of the feed roller is realized in a structurally particularly simple manner, which can shift a feed roller from a first position to another position with simple mechanisms. In addition, the feed roller shaft is mounted in such a shaft seat in a particularly reliable and therefore very interference-free manner. The improved guidance achieved thereby, in particular of a workpiece to be dehulled, generates very low machining forces at the milling head, thereby additionally reducing wear at the milling head.

Therefore this in particular is used for making workpiece, as bar, pipe, rod, wire, steel cable or similar material acceleration along the processing axis of a conveying section or the feed roller that constitutes like this is also advantageously independent of itself. The remaining feature of the invention, wherein said feed rollers are each driven by a feed roller shaft.

The feed mechanism itself is known from the prior art and serves to accelerate and transport the workpiece together with the associated workpiece coating processing plant, which then continuously processes, for example, a continuously cast material workpiece. These feed mechanisms are also used in particular in the field of descaling machines, the feed rollers also serving to accelerate and transport the workpieces forward to the descaling machine. In particular for smaller workpiece diameters, the feed rollers are often offset at an angle relative to the workpiece machining axis. The oblique position of the feed rollers achieved here causes the workpieces to be rotated, thereby improving the dehulling effect of the workpieces. In addition, the workpiece is also rotated about its axis of rotation after the dehulling process, which in individual cases is advantageous for the subsequent machining process. In contrast, as is known in the art, the straight-line position of the roller axes is likely to minimize wear on the feed rollers for dehulling of larger diameter workpieces. It is also known from the prior art that a dehulling device can process not only workpieces with the same diameter, but also different workpieces with different diameters. The feed rollers of a dehulling device or feed mechanism are therefore often individually adjusted to the diameter of the workpiece to be processed by an adjustment mechanism. However, these known adjustment mechanisms have the disadvantage that they are susceptible to contamination and thus often lead to inaccuracies in the adjustment of the feed rollers, which increases the risk that due to contamination a satisfactory product can no longer be achieved. Furthermore, there is the risk that the known adjustment means may stick and therefore cannot be adjusted precisely or only with great difficulty. In the case of the known adjusting devices, therefore, critical production parameters always result, and the cleaning or reactivation of the known adjusting devices is usually very complicated. These disadvantages can be overcome by eccentric feed rollers.

In order that the feed roller shaft can be supported in a simple manner by means of the bearing, it is advantageous if the bearing is mounted rotatably about a bearing axis and preferably substantially rotationally symmetrical. Such a support structure is particularly impervious to dirt, so that the adjustment mechanism is very maintenance-friendly. Furthermore, such an adjustment mechanism can be manufactured particularly inexpensively. A particularly advantageous bearing of the feed roller shaft can be achieved by means of such a shaft seat.

A preferred embodiment variant provides that the axle seat is a bearing sleeve and that the bearing sleeve is arranged rotatably about its longitudinal axis, preferably about its central longitudinal axis, in a carrier. This results in a structurally particularly robust and compact adjustment mechanism for the individual adjustment of the feed rollers to the workpieces to be processed.

It has been found to be advantageous to additionally or alternatively make an offset bearing body pass through a bearing for the feed roller, for example the shaft seat described here is preferably in a bearing for a feed roller Guided on the support, the bearing of the feed roller achieves a movement with a rotational component about a component axis lying in a plane parallel to the workpiece and passing through the main pressing direction, in which pressing Direction The feed roller acts on the workpiece. The bearing of the feed roller shaft therefore rotates at least about an axis which is arranged obliquely to the main pressing direction or which intersects an axis parallel to the main pressing direction.

Due to this offset of the main pressing direction, the pressing force on the workpiece is on one side and the fixing forces on the bearing are separated from one another, so that sticking can be substantially reduced.

The axis of rotation of the feed roller shaft is preferably arranged relative to the axis of rotation of the shaft holder such that the axis of rotation of the feed roller shaft describes a cone in space when the shaft holder rotates.

It is advantageous here if the cone has a cone point which is located substantially at the intersection of the axis of rotation of the feed roller shaft and the perpendicular to the machining plane, preferably substantially at the axis of rotation of the feed roller shaft At the point of intersection with the machining plane. The machining plane is defined here by the machining axis and the main pressing direction. Especially when the cone tip of the cone is located at the intersection point of the axis of rotation of the feed roller shaft and the machining plane, particularly low bearing forces are produced which act on the adjustment mechanism, especially also on the axle seat.

In order to be able to adjust the infeed roller shaft at different angles relative to the workpiece, it is advantageous if the axis of rotation of the infeed roller shaft and the axis of rotation of the axle seat form an angle with one another. As a result, the axis of rotation of the feed roller shaft also describes this cone when the axle seat rotates about its axis of rotation, and it is possible to adjust the feed roller to different positions relative to the workpiece or the machining axis of the conveying section. In this context, it has proven to be advantageous if the axis of rotation of the axle seat is arranged obliquely to a perpendicular to the machining axis of the conveying section.

The mounting of the feed roller shaft on the shaft support is structurally particularly simple if the shaft support has a bore for accommodating a feed roller shaft and the bore is arranged obliquely to the axis of rotation of the shaft support, The aforementioned possibilities can be realized by means of the axle seat.

In order that the axis of rotation of the feed roller shaft describes a cone as described during the rotation of the hub, the hub preferably has an opening whose inlet and outlet are at different distances from the axis of rotation of the hub.

In order to arrange the cone point as close as possible to the machining axis, it is advantageous that the opening of the bore of the shaft seat on the end face of the shaft seat facing the feed roller is larger than the opening of the hole on the end face of the shaft seat facing away from the feed roller Set closer to the axis of rotation of the shaft seat.

In order to keep the number of components of the adjusting mechanism as low as possible, it is advantageous if the axle support has a self-locking drive. The self-locking drive can be used to control the axle seat very precisely and no additional mechanisms, such as brakes or fixing devices, are required for securing the axle seat, since the self-locking drive makes it particularly simple to fix the axle seat in its position. at the desired operating position.

In order to further simplify the construction of such a self-locking drive, it is advantageous if the self-locking drive has a self-locking screw or screw gear and/or a hydraulic servomotor.

In order that the advantages of the above-mentioned cutting machine tools, in particular the above-mentioned feed mechanism, can be advantageously used in practice, a corresponding method is proposed here for adjusting the feed roller of the feed mechanism relative to the machining axis of a conveyor section, wherein by using A bearing housing rotates about the axis of rotation of the bearing housing, supports the feed roller shaft in the bearing housing, and the rotation axis of the bearing housing has at least one component parallel to the rotation axis of the feed roller shaft, so that the rotation of the feed roller shaft Axis offset. This makes it possible to achieve a particularly reliable and low-maintenance method for adjusting the feed roller relative to a linearly moving workpiece. Especially with regard to the parallel component the required adjustment force can be radically simplified and better controlled.

It is particularly advantageous if the axis of rotation of the feed roller shaft pivots about the axis of rotation of the bearing sleeve when the bearing sleeve rotates. This movement allows a particularly simple adjustment of an infeed roller to individual needs.

A preferred variant of the method is to adjust an angle between the axis of rotation of the feed roller shaft and the processing axis of the conveyor section during the rotation of the bearing sleeve between 0° and 10°, preferably between 0° and 5° Angle. In order to be able to adjust the feed roller between relatively small-diameter workpieces and relatively large-diameter workpieces sufficiently well, in practice an adjustment method with an angle between 0° and 1.25° is preferably used.

Additionally or alternatively to the above-mentioned features, a cutting machine tool with a feed device is proposed for machining linear workpieces, in particular rods, tubes, rods, wires, cables or similar workpieces, wherein the feed device has a A feed mechanism detachably connected to an introduction guide frame, and the feed mechanism and the introduction guide frame are detachably connected to each other through at least one quick clamping device.

Such a feed device with an insertion guide and a feed mechanism is preferably used for feeding linear workpieces to, for example, a dehulling machine. Here, a workpiece is accelerated and conveyed continuously by means of the feed device, which ensures that the feed device continuously feeds a workpiece for the machine tool. Usually, in such a feed device there is firstly a feed mechanism and then an insertion guide in the feed direction before the workpiece is fed to the corresponding machine tool. The main function of the introduction guide frame is to deliver the workpiece accelerated and continuously conveyed by the feed mechanism to the machine tool in a targeted manner. According to the prior art the feed mechanism and the introduction guide are usually fixedly connected as a unit, ie not detachable under normal operating conditions, and can be moved together, for example for changing the tool on the corresponding machine tool. In order to ensure precise guidance of the workpiece during operation, the feed device is permanently connected to the machine tool during operation. However, there is a disadvantage in the known feed device that the feed mechanism and the insertion guide form a non-detachable unit and cannot be separated from one another, at least in the assembled state. In order to fulfill the task of the feed mechanism and the insertion guide, the feed device needs to be completely, at least partially dismantled, depending on the machining to be carried out. This especially complicates the maintenance and adjustment work required on the structural parts of the feed mechanism and the introduction guide.

For example, DE 40 19 286 A1 discloses a dehulling machine in which individual structural components, such as the feed assembly and the introduction system, are arranged offset relative to a dehulling machine housing. Here, the feed unit is clamped by means of a plurality of bolts to the guide system. In addition, the feed assembly and the introduction system are simultaneously supported in a clampable manner on the dehulling machine housing via additional guide rails. The guide rails here run from the dehulling machine housing as far as the feed unit and are arranged relative to the subassembly in such a way that the guide rails enter this subassembly parallel to the conveying direction of the feed subassembly. The guide rails each have either a locknut or a clamping key at their ends, so that when the guide rail "cuts", not only the feed unit, the introduction system but also the dehulling machine housing are clamped to each other and thus connected to each other . The disadvantage here is that, on the one hand, the feed unit is very complex and difficult to separate from the introduction system. This significantly increases the difficulty of maintenance and adjustment work. On the other hand, guide rails that run through all structural components are disadvantageous, since there is a relatively high self-expansion in the guide rails. There is also self-expansion when the guide rail is machined from high-value materials. As a result, the structural component can only be clamped with a limited clamping force. As a result, such a clamped subassembly has only limited rigidity. This has a negative effect on the machining or descaling effect, since relatively high machining forces are present at the milling head during descaling, which have to be transmitted correspondingly to a rigid frame in order to achieve descaling on the workpiece The precision required for picohours. Above-mentioned defective is overcome by above-mentioned equipment, especially dehulling machine tool and by its feeding device.

As mentioned above, a quick clamp can be constructed in a variety of ways. "Quick clamping device" is generally understood to mean, by means of which a connection between two parts can be quickly and uncomplicatedly established or released. The quick clamping device is preferably automated, so that manual operation by an additional tool is superfluous. This type of connection is completely different from the connection where two parts are connected by a simple bolt connection.

A preferred embodiment provides that the quick clamping device has at least one wedging element. These wedging elements are advantageously presented as standard products, so that the quick clamping device thus presented can be realized economically. In addition, the wedging element has the particular advantage that in the unlocked state of the wedging element, the previously clamped structural parts can be spaced arbitrarily far apart from each other without a possible interference of a clamping device between the separate structural parts. connection parts. As a result, the connection between the feed mechanism and the insertion guide can also advantageously be quickly and structurally particularly simple to be established or released.

In this way, on the one hand, maintenance and adjustment work can also be carried out easily and particularly quickly on both sides of the insertion guide, so that such work processes are significantly easier to implement, which is particularly advantageous in the case of sensitive or knurled introduction guides. of. On the other hand, no additional installation space is required for the associated work on the feed mechanism, especially on the feed mechanism parts on the side of the insertion guide, because the feed device is preferably quickly detached from a machine tool and only The insertion guide is separated from the feed mechanism and needs to be moved back to the machine tool in order to gain access without problems, for example to the feed mechanism components on one side of the insertion guide. This is achieved particularly simply by means of a quick clamping device.

On the other hand, a cutting machine tool is additionally or alternatively proposed for this purpose, which has a feed device, an insertion guide and a dehulling machine reducer, wherein both the feed mechanism and the dehulling machine reducer can be used are detachably connected to the introduction guide frame independently of each other.

A “reducer for dehulling machine tools” is generally understood here to mean a fixed base body of a cutting machine tool, in particular a dehulling machine tool. This basic body is, for example, a machine frame, a frame or a different structure, which reaches essentially as far as the milling head.

The work on the individual parts of a dehulling machine can be performed very easily and efficiently by the operationally reliable connection of the two structural components, the feed mechanism and the dehulling machine reducer, independently and mainly independently of each other, with the introduction guide frame. Achieved at less cost. It is thus possible, for example, to perform work on the area between the insertion guide and the dehulling machine reducer without having to separate the feed mechanism from the insertion guide for this purpose. Instead, the introduction guide frame and the feed mechanism can be removed from the shell of the dehulling machine tool as a fixedly connected structural assembly. This also contributes to the prevention of accidents, since only a very small number of loose, slidable structural components need to be handled during such work. This reduces the risk of accidents.

One of the great advantages is that by means of this independent connection a more rigid feeding device is provided than the current feeding device. This more rigid feed arrangement is achieved in that, on the one hand, the feed mechanism is arranged directly on the insertion guide. As a result, the clamping force is transmitted to the clamped structural component via a very short force flow path, thus achieving a more rigid connection than conventional connections.

On the other hand, the insertion guide is advantageously detachably connected directly to the dehulling machine reducer. As a result, the clamping force is also transmitted via a particularly rigid connection to the connected structural components.

Depending on the application, it is thus not necessary to separate the entire feed device from the machine tool, but only the feed mechanism has to be separated from the insertion guide and removed in such a way that the insertion guide remains in place on the machine tool. For these reasons alone, it is advantageous if the feed mechanism and the insertion guide can be offset relative to each other, in particular also in the assembled state.

In addition, in order to provide a sufficiently large assembly space between the feed mechanism and the introduction guide when the work on the various structural parts or structural assemblies of the feed device is completed, it is advantageously possible to connect the feed mechanism and the introduction A distance greater than 200mm, preferably greater than 500mm or greater than 600mm is adjusted between the guide frames.

In order to make the feed mechanism and the insertion guide frame detachable from each other in a particularly simple construction, it is advantageous if the feed mechanism and the insertion guide frame are detachably fastened to each other by means of a clamping device. As a result, the number of work steps required for clamping and unclamping and their time expenditure can be kept as low as possible.

One embodiment variant provides that the clamping device has at least one positioning means, a clamping part, a tensioning bolt and/or a positioning pin.

The term "positioning means" is to be understood as meaning those devices by which the feed mechanism can be prefixed at least on the introduction guide frame or vice versa, so that the feed mechanism and The introduction guides are connected to each other to form a feeding device. A prefixation facilitates further clamping work, since the structural parts to be clamped are already securely connected to one another and, if necessary, sufficiently aligned.

A “clamping part” includes, for example, all structural parts which are suitable for interconnecting the feed mechanism and the insertion guide in such a way that they are securely but detachably connected to one another, especially during operation.

These clamping parts can also be tension bolts, wherein a tension bolt preferably passes through a frame of the feed mechanism and/or a frame of the introduction guide frame and said tension bolts usually pass through respectively at their ends A nut is clamped, so that the feed mechanism and the guide frame are connected to each other to form a reliable feed device.

Furthermore, the positioning pins can additionally or alternatively serve as a centering aid, so that the feed mechanism and the insertion guide, in particular when guided together, are generally guided in several positions. In addition, the feed mechanism and the insertion guide are connected to one another in a rotationally fixed manner at several points by virtue of the presence of such positioning pins. The term "locating pins" in the sense of the present invention therefore includes those which are suitable for guiding the feed mechanism together with the introduction guide at multiple positions in a targeted manner, in particular perpendicular to the guide path. The structural part, and also the split feed device, can be designed particularly torsion-proof or, despite the split, itself sufficiently rigid by means of two or more positioning pins.

In order to move the mutually detached feed mechanism and the insertion guide without problems and purposefully relative to itself, but also relative to a workpiece processing device, a preferred embodiment variant provides that not only the feed mechanism but also the insertion guide The guide frames are movably supported along a straight guide rail. On such a straight guide rail, the feed mechanism and the insertion guide can be mounted particularly securely and can be moved relative to each other very precisely and quickly. It goes without saying that such a straight guide rail is also advantageously independent of the other features of the invention.

In a practical conversion, the insertion guide can have a torsion-resistant housing, which is preferably connected to the straight guide rail via sliding shoes. Of course, such a box is particularly resistant to twisting if it is closed. A particularly compact unit is achieved by such a housing, which can also be connected particularly well to the feed mechanism, but also to a workpiece processing device. The sliding shoes of the torsion-resistant housing enable precise guidance on straight guide rails. Furthermore, the torsion-resistant box is advantageously very rigidly connected to a foundation via sliding shoes and a straight guide rail fastened to the foundation.

It is therefore also advantageous if the feed mechanism has a torsion-resistant frame, which is preferably connected via sliding shoes to a straight guide rail. Here too, the advantages already described for the torsion-resistant housing are obtained. This torsion-resistant frame for the feed mechanism or the introduction guide is also advantageously independent of the other features of the invention.

In order to be able to deflect the feed mechanism and/or the insertion guide without significant manual effort, it is advantageous if the feed mechanism and/or the insertion guide have means for displacement. Such a moving mechanism is, for example, a hydraulic cylinder which moves the feed mechanism along a straight guide rail. The introduction guide can likewise be moved by such a hydraulic cylinder. However, it is also possible to facilitate the displacement of the feed mechanism and/or the insertion guide relative to one another or to a dehulling machine by means of a steerable crankshaft and a correspondingly favorable reduction ratio.

Furthermore, a device is proposed, for example a dehulling machine, for processing linear workpieces, in particular rods, tubes, rods, wires, cables or the like, wherein the device has a feed device as described above. In particular, the advantages of the feed device in combination with a dehulling machine result in a particularly advantageous application. To facilitate understanding, it should be pointed out here that it is also advantageous to have no further features of the invention with respect to the features of the device for machining the respective workpiece by means of such a feed device.

The use of the feed device on a machine tool can substantially improve known workpiece processing plants, such as dehulling machines, since downtimes of a workpiece processing plant, for example for maintenance or adjustment work, can be substantially shortened.

It is particularly advantageous if the entire feed device or component is detachably connected to the rest of the workpiece processing device. Maintenance and adjustment work can thus be substantially simplified and therefore carried out more quickly, because the feed device is separated as described above into the "first part" of the feed mechanism and the "second part" of the guide frame in the installed state and the two The "parts" can be moved individually or together.

It has also proven to be advantageous if the workpiece processing device has a straight guide rail, on which a feed mechanism and/or an insertion guide can be arranged offset independently of one another. As a result, the feed mechanism and the insertion guide can be moved relatively quickly and reliably relative to each other and individually relative to the rest of the workpiece processing installation.

A particularly preferred embodiment provides that the straight guide rail is designed in such a way that a distance of more than 200 mm, preferably more than 500 mm, can be adjusted between the feed mechanism or the insertion guide and the rest of the workpiece processing device. This distance guarantees a sufficiently large assembly space, so that processing can be carried out without problems on the feed mechanism or on the components on the guide guide side of the infeed and also on the adjustment guide side of the rest of the workpiece processing plant, without the entire structure being Too much structure space. This is especially ensured when the straight guide rails are constructed in combination on a base.

It is also advantageous if the feed device or parts thereof are detachably fastened to the rest of the workpiece processing device by means of a clamping device. Advantageously, the entire feed device can thus be fastened releasably to the rest of the workpiece processing installation. The device can be constructed particularly simply and inexpensively if the clamping device between the feed mechanism and the insertion guide is identical to the clamping device between the feed device and the rest of the workpiece processing device.

In this connection it is particularly advantageous if the clamping device has at least one positioning means, a clamping part, a tensioning bolt and/or a positioning pin.

It should be noted at this point that the other features of the invention are also advantageously absent with respect to the features of the feed device.

Additionally or alternatively, a method for performing machining on an infeed device of a plant is proposed, in which an infeed mechanism and an infeed guide are separated from each other and moved relative to each other such that on the one hand between the infeed guide and the infeed An assembly space is created between the components and, if necessary, between them and the rest of the equipment.

It has been found that this method for processing on a feed device of a plant is also advantageously independent of the other described features of the invention.

Such a method is particularly susceptible to affecting the maintenance and adjustment work of the feed device, so that a device, for example a dehulling machine, can be re-used more quickly in this processing situation. Currently, the parts of a feed device cannot be moved relatively quickly relative to each other, but the conventional feed device has to be dismantled in a complex manner.

This movement of the individual structural components can be achieved particularly simply and quickly if the insertion guide of the feed mechanism and/or of the feed device is moved along a guide rail, preferably along a straight guide rail.

Further advantages, objects and properties of the invention will be explained in greater detail below with the aid of the description of the drawing, which shows by way of example two cutting heads and a dehulling machine with further components.

In the attached picture:

Figure 1 shows a cutting head, in particular a dehulling machine at the milling head, and a feed device with a feed mechanism and an introduction guide,

Fig. 2 shows the dehulling machine tool in Fig. 1, wherein not only the feed mechanism is separated from the introduction guide frame but also the introduction guide frame is separated from the dehulling machine reducer,

Fig. 3 schematically shows an introduction guide frame, which has wedging parts on the conveying direction of the peeled workpieces,

Fig. 4 schematically shows a dehulling machine speed reducer, which has a wedging part on the conveying direction of the dehulling workpiece,

Fig. 5 briefly shows the top view of the introduction guide frame clamped by the feed mechanism,

Fig. 6 schematically shows another dehulling machine tool, which has an introduction guide frame separated from the dehulling machine speed reducer and a feed mechanism separated from the introduction guide frame, wherein not only the introduction guide frame but also the feed mechanism support on a straight rail,

Fig. 7 schematically shows a feeding device of the bark removal machine tool in Fig. 6, which has a feeding mechanism that was originally separated from the introduction guide frame,

Fig. 8 shows the first cutting head of the above-mentioned dehulling machine tool in a perspective view,

Fig. 9 shows another cutting head in partial section, it rotates around a workpiece to be dehulled,

Figure 10 shows an arrangement according to the invention of a bearing housing and a feed roller arranged therein comprising a feed roller motor,

Figure 11 schematically shows a view of the angular adjustment of the feed roller shaft with a corresponding bearing sleeve relative to the machining axis of a conveying section,

Figure 12 schematically shows a perspective view of a feed mechanism with four feed rollers.

Both the descaling machine 1 shown in FIGS. 1 and 2 and the descaling machine 101 shown in FIGS. 6 and 7 each have a feed device 3 or 103 on their milling head 2 or 102 .

The feed device 3 shown in FIGS. 1 and 2 has a feed mechanism 4 and an insertion guide 5 . The feed mechanism 4 and the insertion guide frame 5 are offset on a cross rail 6 of the dehulling machine 1 , wherein the cross rail 6 forms a straight guide rail 7 for the feed mechanism 4 and the insertion guide frame 5 . Both the feed mechanism 4 and the lead-in guide frame 5 can be moved along the straight guide rail 7 in both directions of arrows 11 and 12 by means of slide shoes 108, 109 and 110 (see FIGS. 6 and 7) or similar structures. Therefore on the one hand the feed mechanism 4 and the introduction guide frame 5 can move away from a dehulling machine reducer 13 of the dehulling machine 1 or move towards the dehulling machine reducer 13 of the dehulling machine 1 respectively. On the other hand, the feed mechanism 4 and the guide frame 5 can move relative to each other. This means that the feed mechanism 4 can also be moved independently of the insertion guide 5 on the cross rail 6 and vice versa. In the operating state of the bark removal machine tool shown in Fig. 1, the feed mechanism 4 and the guide frame 5 are connected to each other to form a compact feed device 3, and the feed device 3 is also passed through the guide frame 5 is connected on the bark-removing machine speed reducer 13 of the barren machine tool 1. In order to securely connect not only the feed mechanism 4 but also the insertion guide frame 5 , especially in the operating state shown here, to the dehulling machine reducer 13 of the dehulling machine 1 , on the one hand the feed mechanism 4 and The insertion guides 5 are fixedly but detachably wedged against each other by first upper wedging parts 14 and 15 (see FIG. 3 ) and by first lower wedging parts 16 and 17 (see FIG. 3 ). On the other hand, the introduction guide frame 5 and the dehulling machine speed reducer 13 are fixedly fixed by the second upper wedging parts 18 and 19 (see Fig. 4) and by the second lower wedging parts 20 and 21 (see Fig. 4). However, they are detachably wedged against each other. In this clamped state a workpiece can be guided exactly on the milling head 2 of the dehulling machine 1 by the feed mechanism 4 on the insertion guide 5 . The workpieces 22 are here conveyed continuously by the feed device 3 in the direction of the arrow 24 from an entry zone 23 through the dehulling machine 1 to an exit zone 25 . The feed mechanism 4 is offset from the insertion guide frame 5 as shown in FIG. The end 27 of the feed mechanism 4 on the side can also contact the end 28 of the introduction guide frame 5 on the side of the feed mechanism. In order to realize the assembly space 26 the feed mechanism 4 is at a distance 29 from the insertion guide 5 .

In addition, in the structure according to FIG. 2, the feed mechanism 4 and the introduction guide frame 5 are offset from the de-hulling machine speed reducer 13 of the de-hulling machine tool 1, so that between the introduction guide frame 5 and the de-hulling machine speed reducer 13 creates another assembly space 30. The insertion guide 5 is thus separated from the dehulling machine reducer 13 by a distance 31 . The feed mechanism 4 has a torsion-resistant frame 32 in which, in addition to the feed roller 33 (shown here only as an example), a drive and adjustment mechanism 34 for the feed roller 33 is likewise arranged. Furthermore, in this exemplary embodiment, the insertion guide 5 has a first locking pin 35 and a second locking pin 36 (see FIG. 3 ). The dehulling machine reducer 13 also has a first stop pin 37 and a second stop pin 38 (see FIG. 4 ). The first stop pin 35 of the introduction guide frame 5 works together with a complementary stop sleeve 39 in the operating state of the dehulling machine tool 1 (see FIG. The stop sleeve 40 works together. The locking pins 35 and 36 ensure that the frame 32 of the feed mechanism 4 and a torsion-resistant box 41 (see FIG. 3 ) of the insertion guide 5 are guided relative to each other. Furthermore, the torsion-resistant frame 32 and the torsion-resistant box 41 are supported against each other in a torsion-fixed manner relative to the straight guide rail 6 via locking pins 35 and 36 . The entire feed device 3 is held together very firmly and in a torsion-proof manner by means of the locking pins 35 and 36 . The stop pins 37 and 38 of the dehulling machine speed reducer 13 also have the same effect. They cooperate with corresponding stop sleeves (not explicitly shown here) on the insertion guide 5 . The functional connection between the feed mechanism 4 and the insertion guide 5 is described in detail here only by way of example. According to the actual structure, sufficient guidance and fixing of the above-mentioned structural components can be achieved with each other only by two locking pins and corresponding complementary locking sleeves. Of course, more than two stop pins and stop sleeves may be used in other embodiments. In this exemplary embodiment, the insertion guide 5 additionally has locking pins 14 and 15 , which prefix the feed mechanism 4 and the insertion guide 5 independently of the clamping device 13 relative to each other. In this exemplary embodiment, three guide rollers 42 arranged in a star shape relative to one another are located in the torsion-resistant box 41 of the introduction guide frame 5 (here only shown as an example). Each guide roller is advantageously individually controlled via a servomotor 43 (shown only as an example here) via a corresponding servomotor reducer 44, so that the workpiece 22 to be dehulled in particular High precision is delivered to the milling head 2 (see FIG. 3 ). A first sliding shoe 10 and a second sliding shoe 46 are arranged in the lower part 45 of the torsion-proof box 41 of the insertion guide 5 . The insertion guide frame 5 is connected to the straight guide rail 7 of the dehulling machine 1 via the two slide shoes 10 and 46 in a displaceable offset manner.

The dehulling machine reducer 13 (see FIG. 4 ) has a solid housing 47 on which the second upper wedging parts 18 and 19 and the second lower wedging parts 20 and 21 are arranged. The wedging elements 18 , 19 , 20 and 21 are controlled via a drive motor 48 via a hydraulic system 49 (here only the hydraulics between the wedging elements 18 and 19 are shown). Two stop pins 37 and 38 of the dehulling machine speed reducer 13 are also arranged on the rigid shell 47 . The construction and mode of operation of the wedging elements 14 to 21 present on the entire dehulling machine 1 are illustrated by means of the first upper wedging elements 14 and 15 (see FIG. 5 ). The first upper wedging parts 14 and 15 together with the first lower wedging parts 16 and 17 clamp the feed mechanism 4 with the introduction guide frame 5 . The feed mechanism 4 is represented in the drawing according to FIG. 5 by its two upper feed rollers 33 (shown only by way of example, see FIG. 2 ) and a part 50 of the drive and adjustment mechanism 34 (see also FIG. 2 ). The workpiece 22 to be dehulled (see FIG. 1 ) is transported in the transport direction 24 to the milling head 2 (see FIG. 1 ) by means of the feed rollers 33 of the feed mechanism 4 .

As shown in Figure 5, in order to make the feed mechanism 4 operate reliably and be connected with the guide frame 5, a moving locking key 51 of a first clamping part 52 acts on a rigidly fixed part of a second clamping part 54. Behind the stop key 53. Both the first clamping part 52 and the second clamping part 54 are part of the wedging part 15, wherein the first clamping part 52 is a locking cylinder of the wedging part 15 and the second clamping part 54 is a Solid stop. The first clamping part 52 is arranged in this exemplary embodiment on the insertion guide 5 and the second clamping part 54 is correspondingly arranged on the feed mechanism 4 . If the feed mechanism 4 and the introduction guide frame 5 are moved relative to each other as shown in FIG. Drive out of the locking cylinder of the first clamping part 52 . In this case, the locking catch 51 always cooperates tightly with the stop catch 53 of the second clamping part 54 until finally the feed mechanism 4 is firmly and operationally securely connected to the insertion guide 5 . In order to loosen the connection between the feed mechanism 4 and the introduction guide frame 5 again, the locking key 51 is moved in the opposite direction of the arrow direction 55, thereby enabling the function between the locking key 51 and the stop key 53 The connection is gradually separated and eventually the two clamping parts 51 and 54 are completely separated from each other. Of course, the remaining clamping elements 14 , 16 to 21 of the dehulling machine 1 have an identical design, as described for the wedging element 15 by way of example. Its operating principle therefore also corresponds to that of the wedging element 15 described above. In order to connect the introduction guide 5 to the dehulling machine reducer 13 in the same manner, the introduction guide 5 has both a first clamping part 52 of a wedging part and a second clamping part 19 of the wedging part. Part 56. The wedging member 19 represents representatively all four wedging members 18 , 19 , 20 and 21 . They are used to establish an operationally reliable connection between the insertion guide frame 5 and the dehulling machine reducer 13 . In order to ensure an additional stability between the introduction guide frame 5 and the dehulling machine speed reducer 13, the introduction guide frame 5 has an additional stop pin 57, when the introduction guide frame 5 and the dehulling machine speed reducer 13 When interconnected, it stretches into the rigid shell 47 of the machine tool reducer 13 the inside.

The dehulling machine 101 shown in FIG. 6 has a feed device 103 with a feed mechanism 104 and an insertion guide 105 . The feed mechanism 104 and the guide frame 105 are shiftably arranged on a cross rail 106 of the dehulling machine tool 101, wherein the cross rail 106 constitutes a straight line for the feed mechanism 104 and the guide frame 105. rail107. Both the feed mechanism 104 and the insertion guide 105 can be moved along the straight guide rail 107 in the directions of arrows 111 and 112 via the slide shoes 108 , 109 and 110 . Therefore, on the one hand, the feed mechanism 104 and the introduction guide frame 105 move away from the dehulling machine tool housing 13 or move toward the dehulling machine tool housing 113 respectively. On the other hand, the feed mechanism 104 and the introduction guide frame 105 can move relative to each other. This means that the feed mechanism 104 can also be moved independently of the insertion guide 105 on the cross rail 106 and vice versa. In the configuration according to FIG. 6 , the feed mechanism 104 is offset from the insertion guide 105 in such a way that a mounting space 126 is present between the feed mechanism 104 and the insertion guide 105 , which not only has good access to the insertion guide 105 . The end 127 of the feed mechanism 104 on the side of the guide frame can also be in good contact with the end 128 of the introduction guide frame 105 on the side of the feed mechanism. In order to realize the assembly space 126 , the feed mechanism 104 is spaced apart from the insertion guide 105 .

In addition, in the configuration according to FIG. 6 the feed mechanism 104 and the introduction guide 105 are offset so far from the dehulling machine reducer 113 that a further gap occurs between the introduction guide 105 and the dehulling machine reducer 113 An assembly space 130 . The insertion guide 105 is thus separated from the dehulling machine reducer 113 by a distance 131 . The feed mechanism 104 has a torsion-resistant frame 132 in which, in addition to the feed roller 133 (shown here only as an example), a drive and adjustment mechanism 134 for the feed roller 133 is likewise arranged. Furthermore, both the feed mechanism 104 and the insertion guide 105 have positioning pins 160, 161 and 162, which cooperate with complementary sleeves (not shown and shown in detail) in the feed mechanism 104 or in the dehulling machine reducer 113. kick in. The positioning pins 160 and 161 ensure that the frame 132 of the feed mechanism 104 and a torsion-resistant box 141 of the insertion guide 105 are guided relative to each other at least in the last approach section. Furthermore, the torsion-resistant frame 132 and the torsion-resistant box 141 are additionally supported against one another in a torsion-fixed manner relative to the straight guide rail 107 via positioning pins 160 and 161 . The entire feed device 103 is fixed together more firmly by the additional positioning pins 160 and 161 . The additional positioning pins 162 function similarly between the introduction guide frame 105 and the dehulling machine reducer 113 . Depending on the actual structure, only one or two positioning pins 160, 161 or 162 and corresponding complementary sleeves can achieve sufficient guidance and fixing of the structural components relative to each other. Of course, any number of positioning pins 160, 161 and 162 can be used as desired.

In the running state (see FIG. 7 ), the feeding mechanism 104 is connected with the introduction guide frame 105 to form a feeding device 103 , and the feeding device 103 is also arranged on the dehulling machine reducer 113 . In order to make the feed mechanism 104 and the introduction guide frame 105 reliably connected with the dehulling machine speed reducer 113 especially in the operating state, the feed mechanism 104, the introduction guide frame 105 and the dehulling machine speed reducer 113 are passed through an additional clamp The clamping device 163 is clamped into a compact unit for operation. In this exemplary embodiment, the feed mechanism 104 and the insertion guide 105 additionally have positioning means 164 and 165 , which prefix the feed mechanism 104 and the insertion guide 105 independently of the clamping device 163 relative to each other. In the clamped state a workpiece 122 can be guided precisely on a milling head 102 of the dehulling machine 101 by the feed mechanism 104 via the insertion guide 105 . To this end, the workpieces 122 are conveyed continuously from an entry zone 123 in the direction of the arrow 124 by the feed device 103 and by the dehulling machine 101 to an exit zone 125 . In order to enable the feed mechanism 104 and the introduction guide frame 105 to be offset towards each other on the one hand and to be offset relative to the dehulling machine reducer 113 on the other hand, the feed mechanism 104 and the introduction guide frame 105 each have a hydraulic adjustment Mechanism 166 (shown here as an example only).

The cutting head 201 shown in FIG. 8 is mainly composed of an adjusting ring 202 , a tool holder seat 203 and four tool holders 204 (only shown here as an example) arranged on the tool holder seat 203 . The tool holders 204 each have a tool 205 (shown only as an example here), by means of which a workpiece 217 (see FIG. 9 ) is exposed from an oxide layer 218 (see also FIG. 9 ) or can be as usual for processing. The cutting head 201 rotates about a machining axis 206 when machining a workpiece 217 . The tool holder 204 is adjusted radially relative to the machining axis 206 via an adjusting ring 202 so that the tool 205 can be adjusted accordingly relative to the workpiece 217 . The tool holders 204 are each guided in the tool holder receptacle 203 in such a way that they fix and guide the tool 205 radially offset relative to the workpiece 217 or the machining axis 206 . The individual adjustment of the tool holder 204 is here achieved by deflection of the setting ring 202 in the axial direction 207 , wherein the deflection of the setting ring 202 corresponds to the axial displacement relative to the machining axis 206 . The inner side 219 of the setting ring 202 itself is conical. The tool holder 204 is connected to the planar sliding surface 208 of the setting ring 202 via sliding surfaces 220 , which are located in the conical region. The tool holder 203 is generally fixed relative to a hollow shaft 213 (see FIG. 9 ) when the adjusting ring 202 is axially displaced, so that the adjusting ring 202 is displaced relative to the tool holder 203 . Both the sliding surface 220 of the tool holder 204 and the sliding surface 208 of the setting ring 202 adjoining this sliding surface are formed planarly, so that the sliding surfaces 220 and 208 adjoining one another interact with each other over as large a surface as possible. In order to realize the planar sliding surface 208 on the inner surface 219 of the setting ring 202 in a particularly structurally simple manner, the sliding surface 208 is realized in this exemplary embodiment by a lining 209 . The linings 209 are here small pieces of quenching material which are arranged via four quick-release screws 210 (shown here only as an example) in a groove 211 provided for this purpose on the inner surface 219 of the setting ring 202 . Both transitions are achieved through the liner 209 . Firstly, the lining layers 209 are arranged on the inner surface 219 of the setting ring 202 in such a way that they extend substantially in the same manner as the remaining conical inner surface 219 with respect to the machining axis 206 . Furthermore, the lining 209 has no curved surface on its sliding surface 208 , like the rest of the inner surface 219 , but is designed flat, ie without curvature. The tool holder 204 can thus easily be displaced radially relative to the machining axis 206 along the machining axis 206 when the adjusting ring 202 is axially displaced and also slides with the adjusting ring 202 or the inner surface 219 of the adjusting ring 202 through a plane The surfaces 220 and 208 alternate, so that on these planar sliding surfaces 220 and 208 in particular radially acting forces are better transmitted from the tool holder 204 to the setting ring 202 . The regions around or on the sliding surfaces 220 and 208 are therefore subject to much less wear than conventional cutting heads 201 . It should also be pointed out here that, as shown in this exemplary embodiment, such a planar sliding surface 209 can not only be realized by a lining 209 . Of course, this planar sliding surface 208 can also be machined directly on the inner surface 219 of the adjustment ring 202 . However, the proposed use of the lining 209 is particularly economical, since this lining 209 can be easily replaced by loosening the quick-release screw 210 when critical wear occurs and can be replaced by a new lining 209 . However, the sliding surfaces 220 are advantageous on the tool holder 204 because they can be machined on the tool holder 204 more easily than the known sliding surfaces 220 having a conical structure. However, a lining 209 can preferably also be used here, so that, for example, a lining 209 arranged on the setting ring 202 is connected to a lining 209 arranged on the tool holder 204 .

The cutting head 212 shown in FIG. 9 has a substantially similar structure to the cutting head 201 known from FIG. 8 , so that functionally identical components of both embodiments are assigned the same reference symbols. The cutting head 212 has an adjusting ring 202 , which slides on a hollow shaft 213 in the axial direction 207 along the machining axis 206 . Furthermore, the hollow shaft 213 has, on its end facing the setting ring 202 , a tool holder 203 which guides the individual tool holders 204 . The tool holder 204 has a tool 205 on its side facing the machining axis 206 , by means of which a workpiece 217 can be extruded from its oxide layer 218 or machined as usual. In this case, the workpiece 217 is moved along the machining axis 206 in a feed direction 219 . A lining 209 is arranged between the tool holder 204 and the setting ring 202 and has a planar sliding surface 208 , so that the toolholder 204 also has a planar sliding surface 220 on the planar sliding surface 208 of the lining 209 . The tool holder 204 is thus connected to the planar sliding surface 208 of the adjusting ring 202 by the planar sliding surface 220, although the inner surface 219 of the adjusting ring 202 is generally tapered.

FIG. 10 shows a feed roller shaft 301 which is rotatably mounted in a bearing bush 302 . The bearing sleeve 302 is also mounted rotatably about an axis of rotation 313 (see FIG. 11 ) in a support 303 . Not only the feed roller shaft 301 but also the bearing bush 302 can thus rotate relative to the bracket 303 . Furthermore, the bearing sleeve 302 can be rotated not only relative to the carrier 303 but also relative to the feed roller shaft 301 . When the bearing sleeve 302 does not rotate relative to the bracket 303, the rotation of the feed roller shaft 301 is automatically realized. The feed roller shaft 301 rotates about a rotational axis 330 in a first orientation. Arranged at the first end of the feed roller shaft 301 is a feed roller 304 which, when rotating in a clockwise direction 325 , transports a workpiece 305 along a machining axis 306 in the direction of the arrow 307 . On the end of the feed roller shaft 301 in the direction opposite to the feed roller 304 is provided a drive motor 308 which drives the feed roller shaft 301 . The bearing sleeve 302 has a rotating ring 39 which is provided with helical toothing 310 . Here, the lift angle of the helical tooth 310 is selected so large that the helical tooth 310 is a self-locking drive tooth, which keeps the bearing sleeve 302 in a once-adjusted position for a long time until this position be actively changed. The feed roller shaft 301 is arranged obliquely in the bearing sleeve 302, so that the first rotation axis 330 of the feed roller shaft 301 moves to another position when the bearing sleeve 302 rotates and the feed roller shaft 301 has another The axis of rotation 331 is offset from the first axis of rotation 330 of the feed roller shaft 301 . The feed roller 304 is thus adjusted at another angle relative to the workpiece 305 or relative to the machining axis 306 . The two different positions of the axes of rotation 330 and 331 shown here by way of example represent only a selection of positions which the feed roller shaft 301 can assume by rotation of the bearing sleeve 302 about the axis of rotation 313 . In order to more clearly represent the possibility of the offset of the feed roller shaft 301, the feed roller shaft 301 represents an offset position 332 with a dotted line at its side 311 away from the feed roller 304, so it is easier to see from FIG. 10 It can be seen how the feed roller axis 301 is offset relative to a first position. Furthermore, the drive motor 308 likewise shows an offset position 333 dashed.

The schematic illustration in FIG. 11 shows a bearing housing 302 in which a feed roller shaft 301 is mounted obliquely. The bearing sleeve 302 here rotates about an axis of rotation 313 , while the feed roller shaft 301 itself rotates about an axis of rotation 330 . The axis of rotation 313 of the bearing sleeve 302 is adjusted at an angle 314 relative to the axis of rotation 330 of the feed roller shaft 301 . When the bearing sleeve 302 rotates about its axis of rotation 313, the axis of rotation 330 of the feed roller shaft 301 arranged obliquely inside the bearing sleeve 302 is offset in such a way that the axis of rotation 330 practically describes a cone 315 in the space 316 , and the cone 315 has a conical tip 317 at an intersection point of the feed roller axis plane in which the feed roller axis 330 is located and perpendicular to the drawing plane and thus parallel to the main pressing direction of the feed roller 304 The quasi-workpiece 305 and has its origin point on the machining axis 306 . The feed roller axis plane runs obliquely relative to a perpendicular 334 arranged to the machining plane 306 . The feed roller 304 can thus be adjusted in a structurally simple manner at different angles relative to the machining axis 306 and thus also relative to a workpiece 305 . This construction makes it possible to offset the axis of rotation 330 of the feed roller shaft 301 between 0° and 1.25° and thereby achieve a sufficient adjustment of the feed roller 304 relative to the workpiece 305 . The feed rollers 304 can thus be adapted to the alternating requirements of workpieces 305 of different diameters. This construction also enables a particularly fine and precise adjustment of the corresponding angle.

The feed mechanism 320 shown in FIG. 12 is a part of a dehulling machine tool 321 (shown simply here) and has four adjustment mechanisms 322 (shown only as an example), wherein the adjustment mechanisms 322 are respectively There is a bearing housing 302 (see FIGS. 10 and 11 ) which has a feed roller shaft 301 arranged obliquely therein (see FIGS. 10 and 11 ). In addition to the adjustment mechanism 322 , clamping devices can additionally be provided, by means of which the feed rollers can be offset or adjusted parallel to their main pressing direction on the workpiece. Four feed rollers 304 (see FIGS. 10 and 11 ) arranged on the feed mechanism 320 convey the workpiece 305 to the dehulling machine tool 321 in the conveying direction 307, by which, in this embodiment, for example, the oxide layer (in the (not shown here) is removed from the workpiece 305, whereby the workpiece 305 is given a metallic surface (not shown here) following the dehulling process. A drive and adjustment unit 323 is located at the top of the feed mechanism 320, and it acts on the helical teeth 310 (see Figure 10) of the rotating ring 309 through an adjustment mechanism 324, so that the bearing sleeve 302 can be adjusted to a desired Location.

Claims (42)

1. A cutting head with a tool holder mainly adjustable radially with respect to an axis of rotation and an adjustment device mainly axially adjustable with respect to the axis of rotation, wherein the tool holder and the adjustment device mutually mutually on a sliding surface Fitting, characterized in that the sliding surface is substantially planar or has a constant radius of curvature parallel to the axis of rotation. 2. The cutting head according to claim 1, characterized in that at least one sliding surface (220, 208) has a lining (209), which preferably consists of a wear-resistant material. 3. The cutting head according to claim 2, characterized in that said lining (209) is a small piece of quenching material. 4. The cutting head according to any one of claims 1 to 3, characterized in that a lining (209) is fastened exchangeably to the adjustment device and/or the tool holder (204). 5. The cutting head as claimed in one of claims 1 to 4, characterized in that the adjustment device has a tapered sleeve. 6. The cutting head according to claim 5, characterized in that the taper sleeve is an adjusting ring (202). 7. The cutting head according to any one of claims 1 to 6, characterized in that a planar sliding surface (208) of the adjustment device is substantially parallel to a corresponding sliding surface (220) of a toolholder (204) ), preferably a plane sliding surface (220) of a knife holder (204). 8. An adjusting ring for adjusting a toolholder relative to an axis of rotation, wherein the adjusting ring has an inner surface of a conical configuration for forming a sliding bearing surface, characterized in that the conical sliding The bearing shell surface has at least one substantially planar plain bearing region. 9 . The adjusting ring according to claim 8 , characterized in that the planar sliding bearing point is detachably and replaceably attached to the adjusting ring ( 202 ). 10 . 10. The adjusting ring as claimed in claim 8, characterized in that the plain plain bearing point has a lining (209) which has harder material properties than the adjusting ring (202). 11. A cutting machine tool for machining longitudinally extending workpieces (217), especially a dehulling machine tool, characterized in that a cutting head (201; 212) as claimed in any one of the preceding claims and/or an adjusting ring (202). 12. The machine tool according to claim 11, having a feed mechanism (320) with feed rollers (304) for linear workpieces (305), especially rods, tubes, rods, wires, cables or Similar materials are accelerated along a processing axis (306) of a conveying section, wherein said feed rollers (304) are respectively driven by a feed roller shaft (301), characterized in that at least one feed roller shaft (301) Eccentrically supported in a shaft seat (302). 13. The machine tool according to claim 12, characterized in that the axle seat (302) is mounted rotatably about an axle seat axis (313). 14. The machine tool according to any one of claims 12 or 13, characterized in that said axle seat (302) is a bearing sleeve and the bearing sleeve is rotatable around its longitudinal axis, preferably around its center The longitudinal axis is arranged in a bracket (303). 15. The machine tool according to any one of claims 12 to 14, characterized in that a bearing body is guided on a support by a bearing for the feed roller shaft (301) so that the feed The bearings of the rollers effect a movement with a rotational component about a component axis lying in a plane parallel to the workpiece (305) and passing through the main compacting direction in which the feed rollers Act on the workpiece. 16. The machine tool according to any one of claims 12 to 15, characterized in that the axis of rotation of the feed roller shaft (301) is arranged relative to the axis of rotation (313) of the shaft seat (302) such that at The axis of rotation (330) of the feed roller shaft (301) describes a cone (315) in the space (316) when the shaft seat (302) rotates. 17. The machine tool according to claim 16, characterized in that said cone (315) has a cone point (317), which is substantially positioned at the axis of rotation (330) of the feed roller shaft (301) and the machining center. The point of intersection (318) of the perpendicular (334) of the plane is preferably located substantially at the point of intersection (318) of the axis of rotation (330) of the feed roller shaft (301) and the machining plane. 18. The machine tool according to any one of claims 12 to 17, characterized in that, the rotation axis (330) of the feed roller shaft (301) and the rotation axis (313) of the shaft seat (302) are mutually Form an angle (314). 19. The machine tool according to any one of claims 12 to 18, characterized in that the axis of rotation of the shaft seat (302) is arranged obliquely relative to the perpendicular (334) of the machining axis (306) of the conveying section . 20. The machine tool according to any one of claims 12 to 19, characterized in that said axle seat (302) has a hole for accommodating a feed roller (301) and the hole is relative to the axle seat ( 302) the axis of rotation (313) is arranged obliquely. 21. The machine tool according to any one of claims 12 to 20, characterized in that the shaft seat (302) has a hole whose inlet and outlet are different from the axis of rotation (313) of the shaft seat (302) distance. 22. The machine tool according to any one of claims 20 or 21, characterized in that the opening ratio of the hole of the shaft seat (302) on the end face of the shaft seat (302) facing the feed roller (304) The hole is closer to the axis of rotation (313) of the axle seat (302) on the open end face of the axle seat (302) facing away from the feed roller (304). 23. The machine tool according to any one of claims 12 to 22, characterized in that the axle seat (302) has a self-locking drive. 24. Machine tool according to claim 23, characterized in that the self-locking drive has a self-locking screw or worm gear and/or a hydraulic servomotor. 25. The machine tool according to any one of claims 12 to 24, for processing linear workpieces (22), especially rods, pipes, rods, wires, cables or similar materials, it has a feed device (3 ; 103), which has a feed mechanism (4; 104) detachably connected to an introduction guide frame (5; 105), characterized in that the feed mechanism (4, 104) is connected with the introduction guide frame ( 5; 105) are detachably connected to each other by at least one quick clamping device. 26. Machine tool according to claim 25, characterized in that the quick clamping device has at least one wedging element (14). 27. The machine tool according to any one of claims 12 to 26, wherein the machine tool has a feed device (4; 104), an introduction guide frame (5; 105) and a dehulling machine tool reducer (13 ; 113), characterized in that not only the feed mechanism (4; 104) but also the dehulling machine tool reducer (3; 113) are independently connected with the introduction guide frame (5; 105) separably. 28. The machine tool according to any one of claims 12 to 27, characterized in that the introduction guide (5; 105) is directly detachably connected to a dehulling machine reducer (3; 113). 29. Machine tool according to any one of claims 12 to 28, characterized in that the feed mechanism (4; 104) is offset relative to the insertion guide (5; 105), in particular also in the installed state. 30. The machine tool according to any one of claims 12 to 29, characterized in that a distance greater than 200 mm, preferably Distances greater than 500 mm (29; 129). 31. The machine tool according to any one of claims 12 to 30, characterized in that the feed mechanism (4; 104) and the introduction guide frame (5; 105) are detachable via a clamping device (163) fixed to each other. 32. The machine tool according to claim 31, characterized in that the clamping device (163) has at least one positioning mechanism (164, 165), a clamping part, a tension bolt and/or a positioning pin ( 160, 161, 162). 33. The machine tool according to any one of claims 25 to 32, characterized in that not only the feed mechanism (4; 104) but also the lead-in guide (5; 105) follow a straight guide rail (7; 107) Removably supported. 34. The machine tool according to any one of claims 25 to 33, characterized in that the introduction guide (5; 105) has a torsion-resistant box (41; 141), which preferably passes through the sliding shoe (10, 46; 108, 109, 110) are connected to the straight guide rail (7; 107). 35. The machine tool according to any one of claims 25 to 34, characterized in that the feed mechanism (4; 104) has a torsion-resistant frame (32; 132), preferably via a sliding shoe ( 10, 46; 108, 109, 110) are connected with straight guide rails (7; 107). 36. Machine tool according to any one of claims 25 to 35, characterized in that the feed mechanism (4; 104) and/or the introduction guide (5; 105) have means for movement. 37. A machine tool for machining linear workpieces, in particular rods, tubes, rods, wires, cables or similar materials, characterized by a feed device as claimed in any one of claims 25 to 36. 38. Machine tool according to claim 37, characterized in that the entire feed device (3; 103) or parts thereof (4, 5; 104, 105) are detachably connected to the rest of the machine tool. 39. The machine tool according to any one of claims 37 or 38, characterized by a straight guide rail (7; 107), on which a feed mechanism (4; 104) and an introduction guide frame (5; 105 ) can be offset independently of each other. 40. The machine tool according to claim 39, characterized in that, the straight guide rail (7; 107) is configured such that between the feed mechanism (4; 104) or the introduction guide frame (5; 105) and the workpiece processing equipment A distance (30; 130) greater than 200mm, preferably greater than 500mm can be adjusted respectively. 41. The machine tool according to any one of claims 37 to 40, characterized in that the feed device (3; 103) or parts thereof (4, 5; 104, 105) are passed through a clamping device (163 ) is detachably fixed on the workpiece processing equipment. 42. The machine tool according to claim 41, characterized in that the clamping device (163) has at least one positioning mechanism (164, 165), a clamping part, a tension bolt and/or a positioning pin ( 160, 161, 162).

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