EP1520668B1 - Cutting device with an elastically deformable bearer ring - Google Patents

Abstract

A rotary cutting anvil drum rests in a machine frame and operates in conjunction with a blade moving around the drum where it cuts a paper or foil web moving between blade and drum. The cutting tool is fixed to a an elastically deformable supporting steel ring that has a larger radius of operation than the blade.

Description

The invention relates to a cutting device comprising a machine frame, an anvil roll rotatably mounted on the machine frame with an anvil, a cutting tool rotatably mounted on the machine frame about an axis of rotation with a cooperating with the anvil cutting edge such that in successive rotational positions each successive cutting sections with successive Anvil surface portions are in an operative position to cut a passing between the cutting tool and anvil material, the cutting tool and the anvil are biased with a biasing force toward each other, the cutting tool by means of at least one rotationally fixed relative to the cutting tool arranged support ring on successive support ring portions relative to Anvil roller rotatably arranged successive support surface portions is supported, the respective effective support ring portion having a bearing force approximately corresponding to the difference between the biasing force and the cutting force acting on the respective effective Stützenlächenabschnitt, and the at least one support ring in the respective effective, the bearing force applying support ring portion is formed relative to the respective effective cutting portion so that at the respectively approximately equal to the difference between preload force and cutting force varying support force of the support ring which is in the operative position cutting section holds at a defined distance from the corresponding effective Anboßflächenabschnitt, and wherein at minimum bearing force the at least one support ring has a greater radial extent with respect to the axis of rotation than the cutting edge and the at least one support ring is elastically deformable , Such a device is from the US-A-3289513 known.

In known from the prior art cutting devices is usually proceeded so that the cutting tool is delivered so far on the anvil roll, that even at maximum cutting forces is still given a sufficient cutting action.

However, this solution has the disadvantage that the cutting in the areas where lower cutting forces occur wear out very much and the cutting tool has a relatively short overall life.

From the US 3,289,513 a rotary cutting device is known which comprises a tool roll and a counter roll. On the tool roll two support rings are arranged, via which these are supported on the counter roll. The tool roll carries a cutting tool which does not touch the counter roll.

The invention has for its object to improve a cutting device of the generic type such that the cutting tool has the largest possible service life.

This object is achieved by a cutting device having the features of claim 1.

It can be assumed that the support ring, even if this is made of steel, due to the bearing force undergoes a deformation in the radial direction, that is, that the radial extent of the support ring relative to the axis of rotation decreases, the varying contact force leads to that the reduction in the radial extent of the support ring is not constant, but also varies with the varying contact force.

These conditional by the varying contact force changes of the support ring can be brought into line with the cutting.

In a preferred embodiment, one possibility is to give the respective successive support ring sections a varying elasticity.

Such varying elasticity would be realized, for example, that the material elasticity of the support ring is formed directly varying, for example by material or structural changes, which can be realized for example by diffusing elements into the structure of the support ring.

Another possibility is to give the support ring a variable elasticity by shape variation. Such a shape variation provides that the support ring is formed of material having homogeneous elastic properties, but by varying the shape of the support ring and the elasticity thereof can be varied. For example, it is possible to achieve such a formula elasticity in that the support ring has a cross-sectional area variation with respect to its cross-sectional areas extending perpendicular to the azimuthal direction.

Such a cross-sectional area variation can be made, for example, by providing a support ring of constant cross-section and introducing suitable recesses therein.

A particularly simple possibility of such a cross-sectional variation is when the support ring has a varying shape in a direction transverse to the radial direction and transverse to the azimuthal direction. Such a shape variation can be realized, for example, by introducing recesses extending in this direction into the support ring of otherwise constant cross-section.

Such recesses may expediently be designed, for example, as recesses extending transversely to the azimuthal direction from an outer edge.

A further alternative embodiment, which allows in particular a direct compensation of varying according to the varying contact force deformation of the support ring in the radial direction, provides that the support ring has a varying relative to the axis of rotation radial extent. This makes it possible to deviate so far, for example by a flattening or a recess of the cylindrical surface, as the radial deformation of the support ring changes with varying contact force. For example, while the flattening or recess in the radial direction is dimensioned so that this change in the radial direction just compensates for the change by which the support ring is less deformed when the contact force changes from the maximum value to the minimum value.

One embodiment provides that the support ring retains a homogeneous material elasticity and an unchanged shape and that the reduction of the deformation of the support ring at the transition is taken into account by maximum contact force to the minimum bearing force, that the effective at minimum contact force cutting portions have a greater extent in the radial direction than the cutting portions, in which the bearing force maximum and the cutting force is minimal.

It can be provided that the cutting tool and the anvil roller are biased toward each other with a biasing force, that the cutting tool is supported by means of at least one rotationally fixed relative to the cutting tool support ring on successive support ring sections relative to the anvil roll rotatably arranged successive support surface portions and thereby each effective support ring portion having an approximately the difference between the biasing force and cutting force corresponding bearing force acting on the respective effective support surface portion and that the support ring is formed in the respective effective, the bearing force applying support ring portion relative to the corresponding effective cutting portion so that at each from about the Difference between biasing force and cutting force corresponding varying contact force of the support ring standing in the operative position cutting nabschnitt holds at a defined distance from the corresponding effective Anboßflächenabschnitt. The supporting effect of the support ring in opposite to the varying cutting force varying contact force is then matched to the radial extent of the cutting portions with respect to the axis of rotation that the support ring, despite the varying bearing force holds the effective cutting portions substantially in a defined distance range of the corresponding Anboßflächenabschnitten the distance range is chosen so that always still a sufficient cutting effect occurs. This is preferably a distance range which is on the order of less than a few hundred micrometers, preferably less than one hundred micrometers.

With regard to the arrangement and design of the support ring a variety of solutions are conceivable. For example, it would be conceivable to provide the support ring as a separate ring, which sits next to the cutting tool, but then the precision of the support effect by the support ring relative to the cutting tool is problematic. For this reason, it is preferably provided that the support ring sits on the cutting tool and preferably the support ring has the same concentricity precision as the cutting tool due to uniform machining together with the cutting tool.

An advantageous possibility for fixing the support ring on the cutting tool is to shrink the support ring on the cutting tool and optionally additionally fix positively.

An alternative solution provides that the support ring is integrally connected to the cutting tool and thus can be produced together with the cutting tool as a unitary part.

With regard to the formation of the support surfaces on which rests the support ring, a variety of ways are also conceivable. Theoretically, it would be conceivable, the support surfaces on a support ring next to the Anvil roll to arrange. However, this would also have disadvantages in terms of accuracy.

For this reason, it is particularly advantageous if the support surfaces are arranged directly on the anvil roll, so that a uniform centric processing of the support surfaces and the anvil surfaces is possible.

The support surfaces can be produced in a particularly simple manner if they form part of the anvil surfaces, since in this case only one surface can be produced with the desired precision.

Further advantages of the invention are the subject of the following description and the drawings of some embodiments.

Fig. 1

einen vertikalen Schnitt durch eine Schneidvorrichtung längs Linie 1-1 in Fig. 2;

Fig. 2

einen vertikalen Schnitt längs Linie 2-2 in Fig. 1;

Fig. 3

eine vergrößerte Darstellung von Amboßwalze und Schneidwerkzeug gemäß Fig. 2;

Fig. 4

eine vergrößerte Darstellung der Bereiche A in Fig. 2 und 3;

Fig. 5

eine schematische Darstellung eines Verlaufs der Schneidkraft über der Azimutalrichtung in Korrelation zu einem Verlauf der Schneiden des Schneidwerkzeugs in Fig. 4;

Fig. 6

eine vergrößerte Darstellung ähnlich Fig. 4 eines zweiten Ausführungsbeispiels;

Fig. 7

eine nochmals vergrößerte Darstellung des Schnitts längs Linie 7-7 in Fig. 6;

Fig. 8

eine ausschnittsweise vergrößerte Darstellung eines radialen Schnitts im Bereich einer Querschneide und

Fig. 9

eine ausschnittsweise vergrößerte Darstellung eines radialen Schnitts ähnlich Fig. 8 im Bereich eines Schneidenschenkels.

In the drawing show:

Fig. 1

a vertical section through a cutting device along line 1-1 in Fig. 2 ;

Fig. 2

a vertical section along line 2-2 in Fig. 1 ;

Fig. 3

an enlarged view of anvil roll and cutting tool according to Fig. 2 ;

Fig. 4

an enlarged view of the areas A in Fig. 2 and 3 ;

Fig. 5

a schematic representation of a curve of the cutting force on the azimuthal direction in correlation to a course of the cutting of the cutting tool in Fig. 4 ;

Fig. 6

an enlarged view similar Fig. 4 a second embodiment;

Fig. 7

a further enlarged view of the section along line 7-7 in Fig. 6 ;

Fig. 8

a fragmentary enlarged view of a radial section in the region of a transverse cutting edge and

Fig. 9

a detail enlarged view of a radial section similar Fig. 8 in the area of a cutting edge.

An in Fig. 1 and 2 each cutting device shown in section comprises a designated as a whole with 10 machine frame, which has two spaced-apart bearing parts 12 and 14.

Each of the bearing parts, for example, the bearing part 12 in Fig. 1 includes two side supports 16 and 18, between which a lower bearing support 20 and an upper bearing support 22 are arranged.

The lower bearing support 20 is guided on the one hand between the side supports 16 and 18 and on the other hand sits firmly on a base plate 24 of the machine frame 10. The bearing support 20 in this case has a bearing receptacle 26, in which a designated as a whole with 28 lower pivot bearing with its outer bearing ring 30th is used, wherein the outer bearing ring 30 abuts with its outer peripheral side on an inner surface of the bearing holder 26. The bearing ring 30 is fixed in the bearing receptacle 26 by an outer holding body 32 and an inner holding body 34 which abut with retaining rings 36 and 38 on lateral annular surfaces of the outer bearing ring 30 and thus fix it in the bearing seat 26. In addition, the outer holding body 32 still includes a cover 40 at the same time.

The upper bearing support 22 is guided between the side supports 16 and 18 and arranged in a direction 42 which extends parallel to the extension of the side support 16 and 18, in the direction of the lower bearing support 20 adjustable. Also, the upper bearing bracket 22 has a bearing receptacle 46, in which an upper pivot bearing 48 is inserted.

The upper pivot bearing 48 is held with its outer bearing ring 50 in the same manner in the bearing seat 46 fitting as the lower pivot bearing 28 with the outer bearing ring 30 and also an outer holding body 32 and an inner holding body 34 are provided, which are formed in the same way as the provided in the lower bearing support 20 holding body and fix the outer bearing ring 50 of the upper pivot bearing 48 in the same way.

The upper bearing support 22 in turn is supported on a designated as a whole by 60 biasing device on an abutment 62, which on a is held parallel to the base plate 24 extending upper plate 64, wherein the upper plate 64, the bearing parts 12 and 14 also connects to each other and also the side supports 16 and 18 fixed relative to each other.

In the same way as the bearing part 12 and the bearing part 14 is formed.

In the two lower pivot bearings 28 each have a stub shaft 72 is mounted, each of which project laterally from a designated as a whole with 70 Anboßwalze and concentric with a rotational axis 74 of the anvil roll 70 are arranged, which has a larger radius than the stub shaft 72 and a coaxial is provided to the rotation axis 74 arranged circular cylindrical anvil surface 76.

By the two lower pivot bearing 28 thus the anvil roller 70 is fixedly mounted in the lower bearing supports 20, which in turn rest on the base plate 24 and are guided between the side supports 16 and 18.

In the upper pivot bearings 48 of the upper bearing support 22, a tool shaft 82 is rotatably mounted about a rotation axis 84, wherein the tool shaft 82, for example, extends through the bearing part 12 and on its opposite side of the rotating tool 80 has a projecting beyond the bearing part 12 drive stub 86 via which by means of a drive, such as a motor, a rotary drive of the rotating tool 80 takes place.

The rotating tool 80 is characterized by the arrangement of the upper pivot bearing 48 in the upper bearing brackets 22 and their displacement in the direction 42 in Direction of the anvil roll 70 movable. By means of the biasing means 60 acting on the upper bearing brackets 22, the rotary tool 80 is biased towards the anvil roll 70 so that it acts on the anvil roll 70 as a whole with a biasing force V.

The rotating cutting tool 80 now has for cutting a designated as a whole by 90 and passed through between the rotary cutting tool 80 and the anvil roll 70 web 90 cutting 92, which from a cylindrical axis, for example, the rotation axis 84 base in the radial direction to the axis of rotation 84 with a constant radial extent survive with respect to the axis of rotation. For example, the cutting edge 92 comprises two cutting edges 92a extending in the azimuthal direction to the rotation axis 84, which transitions into cutting edges 92b extending transversely thereto, which are then connected by a transverse cutting edge 92c which is approximately perpendicular to the azimuthal direction 96 and thus approximately parallel to the rotation axis 84 are ( Fig. 3 ).

For example, the cutting edge 92 has two transverse cutting edges 92c and 92c 'from which extend in opposite directions respectively the cutting arches 92b and 92b', which then pass into the cutting limbs 92a, which are the cutting arcs 92b lying on each side of the cross cutting edges 92c and 92c ' and 92b 'interconnect as enlarged in Fig. 3 and further enlarged partially in Fig. 4 shown.

The cutting action of the cutting edge 92 is now as in Fig. 3 illustrated by cooperation of an effective cutting portion 92s, which a corresponding anvil surface portion 76s with a minimum distance facing each other or nearly touching it, wherein by the rotation of the rotary cutting tool 80 and co-rotation of the anvil roll 70 respectively successive cutting portions 92s and Ansbßflächenabschnitte 76s are in their operative position and cooperate cutting.

In order to define a small distance between the respective co-operating cutting sections 92s and anvil surface sections 76s or so-called light touches thereof, the rotary cutting tool 80 is thus provided with two non-rotatably connected support rings 100 and 102, which are arranged coaxially with the axis of rotation 84 on both sides of the cutting edge 92, for example and thereby have support ring surfaces 104 and 106, which are arranged for example cylindrical to the rotation axis 84 and rest on support surfaces 108 and 110 of the anvil roll 70, wherein the support surfaces 108 and 110 may be formed, for example, by portions of the anvil 76.

The support is in each case via the support ring portions 104 s and 106 s, which rest on corresponding support surface portions 108 s and 110 s of the support surfaces 108 and 110, wherein the rotation of the rotating tool 80 opposite to the direction of rotation of the same successively arranged support ring portions 104 s and 106 s opposite to the direction of rotation of the anvil roller 70th successively arranged support surface portions 108s and 110s cooperate.

The respective cooperating support ring portions 104s, 106s and support surface portions 108s and 110s take a total of one Bearing force A, with which the rotary cutting tool 80 is supported on the Anboßwalze 70 and which represents a part of the biasing force V of the same.

The biasing force V, however, not only leads to the formation of the contact force A, which acts on the anvil roller 70 via the backup rings 100 and 102, but also to a cutting force S, which is associated with an effective cutting length in the respective cutting portion 92s.

Assuming, for example, that the respective cutting portion 92s and the corresponding anvil surface portion 76s which cooperate in the azimuthal direction 96 have a substantially infinitesimally short extent, ideally a punctiform extent, the cutting force required to cut the material 90 is S in the region of the cutting limbs 92a, since the cutting limbs 92a in the effective cutting section 92s likewise act only with their cutting edge length, which is infinitesimally short in the azimuthal direction 96 or even punctiform. In contrast, the effective cutting edge length is large when the transverse cutting edge 92c extending substantially perpendicular to the azimuthal direction 96 forms the effective cutting portion 92s, which cooperates with the corresponding anvil surface portion 76s, since the effective cutting length corresponds to the extent of the transverse cutting edge 92c perpendicular to the azimuthal direction 96. At this point, cutting the material 90 requires the greatest cutting force.

A occurring in such a geometry of the cutting edge 92 course of the cutting force S in relation to the course of the cutting edge 92 is therefore in Fig. 5 represented, according to Fig. 5 the maximum cutting force Smax with respect to the azimuthal direction 96 then occurs when the cross cutters 92c and 92c 'form the effective cutting portions 92s. On the other hand, the cutting force S decreases from the maximum value Smax when the cutting arches 92b form the effective cutting portions, and as the cutting arcs 92b pass through the cutting edges 92c, the effective cutting length and hence the cutting force S decrease as the minimum value Smin increases Cutting force, which occurs when the cutting edges 92a form the effective cutting portions 92s.

Since the sum of cutting force S and bearing force A is equal to the biasing force V and the biasing force V is constant, results from the in Fig. 5 shown running the cutting force S and the variation thereof between the minimum cutting force Smin and the maximum cutting force Smax that the bearing force A has a precisely reversed course, that is, when the cutting force has reached its maximum value Smax, the bearing force is minimal and vice versa ,

Since every material, in particular steel, has elasticity in the forces occurring in a cutting device, the execution of the support rings 100 and 102 as rings invariant in the azimuthal direction 96 would result in their maximum deformation at a high contact force A. and at the minimum contact force A, which coincides with the maximum cutting force Smax, a minimum deformation, so that thus the distance of the effective cutting portion 92s would vary from the respective effective anvil surface portion 76s and, in particular, when the chisel 92c forms the effective cutting portion 72s, the distance thereof from the effective anvil surface portion 76s would be maximum so that ultimately in cut-sensitive materials 90, for example, very fine fiber materials in the range less than 100 μ, the cross cutters 92c would either develop no or only an unsatisfactory cutting action. On the other hand, if the biasing force is adjusted so that the cross cutters still exhibit a satisfactory or cutting action, the distance of the cutting edge 92a forming cutting edge 92s from the corresponding effective anvil face portion 76s would be too small so that the cutting limbs 92a become dull in the course of the cutting would.

For this reason, it is provided to vary the elastic behavior of the support rings 100, 102 in the azimuthal direction 96.

At the in Fig. 1 to 4 illustrated embodiment, the support rings 100 and 102 are provided with cutouts 120, 120 ', which extend, for example, from an outer edge 122 of the support rings 104, 106 in the direction approximately parallel to the axis of rotation 84 in the respective support ring 100, 102 and thus a width B of the support ring Reduce 100, 102 from a width Bmax to a width Bmin. Such, with respect to its width transversely to the Azimutalrichtung 96 reduced support ring 100, 102 deformed at the point of reduced width at a constant contact force A stronger, so that the extension of the cutout 120 can be selected so that the deformation of the support ring 100, 102 in the Width Bmin and maximum cutting force Smax minimum contact force A in the radial direction to the axis of rotation 84 is approximately equal to the deformation in the radial direction, which occurs at minimum cutting force Smin and thus maximum bearing force A and maximum width Bmax of the support ring 104. This ensures that the distance of the transverse cutting edge 92c, if this represents an effective cutting portion 92s, of the anvil surface portion 76s is approximately equal to the distance of a cutting edge 92a, if this represents an effective cutting portion 92s, of the corresponding effective anvil surface portion 76s. Starting from the maximum width Bmax of the support ring, the shape of the cutout 120 can be chosen so that the transition from the maximum width Bmax to the minimum width Bmin either the increase of the cutting force from Smin to Smax and thus the decrease of the bearing force from the maximum value to the minimum Value substantially corresponds. However, it is also possible to select the cutout 120 so that in any case the minimum width Bmin in the azimuthal direction 96 coincides with the position of the transverse cutting edge 92c without adaptation to the increase in the cutting force S from Smin to Smax in the course of the cutting arc 92c is exactly considered.

In a second embodiment, shown in FIG 6 and 7 , primary, there is no adaptation of the elasticity of the respective support ring 100 ', but the respective support ring 100' seen in the azimuthal direction 96 in areas where the maximum cutting force Smax occurs, provided with a flattening or depression 130, 130 'whose deviation from a cylindrical circumferential line 132 substantially corresponds to the change in the radial extent of the support ring surface 104, the occurs when the contact force transitions from its maximum value at minimum cutting force Smin to the minimum value at maximum cutting force Smax.

The course of the flats or depressions 130, 130 'in deviation from the cylindrical surface 132 also makes it possible to substantially simulate or at least approximately ensure the course of the decrease and increase in the contact force A, that when the transverse cutting edge 92c is the effective cutting section 92s, whose distance from the effective anvil surface area 76s is approximately the same size as the distance of a cutting edge 92a from the corresponding anvil surface portion 76s when this cutting leg 92a forms the effective cutting portion 92s.

In the second embodiment, due to the small radial extent of the recess 130, 130 'is primarily based on a little changed elasticity of the respective support ring 100', but that by the recess 130, 130 'an immediate compensation of itself due to the variation of the contact force A reduced radial extent of the corresponding support ring 100 takes place.

But it is also conceivable in the second embodiment, the recesses 130, 130 'as not over the entire width of the respective support ring 100 extending pockets form, so that laterally still remains a up to the cylindrical surface 132 extending portion of the support ring 100, the then in turn becomes effective due to its altered elasticity.

In a third embodiment, the support rings 100 'may be formed with substantially ideal cylindrical shape 132 at the radial extent R ₁ to the axis of rotation 84 and it is instead of the recess 130, 130', a corresponding "increase" Δ of the radial extent R _{2 of} the cross cutters 92c to the rotation axis 84 relative to the radial extent R _{3 of} the cutting limbs 92a provided so that the minimum bearing force greater radial extent of the support rings 100 'is accepted, but this does not deteriorate the cutting action of the cross cutters 92c, as this one by the amount .DELTA have greater radial extent with respect to the axis of rotation 84 than the cutting limbs 92a, since in the region of the support rings 100 ', due to the maximum contact force A and the minimum cutting force Smin have a greater deformation in the radial direction.

Claims (15)

1. Cutting device, comprising a machine frame (10), an anvil drum (70) mounted on the machine frame (10) for rotation about an axis of rotation (74) and having an anvil surface, a cutting tool (80) mounted on the machine frame (10) for rotation about an axis of rotation (84) and having a cutter (92) cooperating with the anvil surface in such a way that in successive rotary positions, respectively successive cutter sections stand in an operative position with successive anvil surface sections in order to cut a material passing through between cutting tool (80) and anvil drum (70), the cutting tool (80) and the anvil drum (70) being pretensioned in a direction towards each other with a pretensioning force (V), the cutting tool (80) being supported by means of at least one supporting ring (100') arranged in a rotationally fixed manner relative to the cutting tool via successive supporting ring sections (104s, 106s) on successive supporting surface sections (108s, 110s) arranged in a rotationally fixed manner relative to the anvil drum (70), the respectively operative supporting ring section (104s, 106s) acting on the respectively operative supporting surface section (108s, 110s) with a bearing force (A) corresponding approximately to the difference between pretensioning force (V) and cutting force (S), and the at least one the supporting ring (100') being of such construction in the respectively operative supporting ring section (104s, 106s) applying the bearing force (A) relative to the operative cutter section (92s) corresponding to this supporting ring section that with the varying bearing force (A) respectively resulting from approximately the difference between pretensioning force (V) and cutting force (S), the supporting ring (100') holds the cutter section (92s) standing in the operative position at a defined spacing from the corresponding operative anvil surface section (76s), and with minimal bearing force, the at least one supporting ring (100') having a greater radial extent with respect to the axis of rotation (84) than the cutter (92), and the at least one supporting ring (100') being elastically deformable, characterized in that the cutter (92) is of such construction that different cutting forces occur when different cutter sections (92a, 92b, 92c) cooperate with corresponding anvil surface sections, and in that a cutter section (92c) requiring a high cutting force (S) in its operative position has a greater radial extent (R₂) with respect to the axis of rotation (84) than a cutter section (92a) requiring a lower cutting force (S).
2. Cutting device in accordance with claim 1, characterized in that the at least one supporting ring (100') has a homogeneous material elasticity.
3. Cutting device in accordance with claim 1 or 2, characterized in that the at least one supporting ring (100') has an essentially ideal cylindrical shape (132).
4. Cutting device in accordance with any one of the preceding claims, characterized in that the at least one supporting ring (100') has the greatest radial extent (R₂) where the bearing force is minimal.
5. Cutting device in accordance with any one of the preceding claims, characterized in that the at least one supporting ring (100') is constructed so that its deformation decreases during the transition from maximal bearing force to minimal bearing force.
6. Cutting device in accordance with any one of the preceding claims, characterized in that the cutter sections (92c) operative where the bearing force is minimal have a greater extent in the radial direction than the cutter sections (92a) where the bearing force (A) is maximal and the cutting force (S) is minimal.
7. Cutting device in accordance with any one of the preceding claims, characterized in that transverse cutters (92) in relation to the axis of rotation (84) are elevated relative to the radial extent (R₃) of cutter legs (92a).
8. Cutting device in accordance with claim 7, characterized in that the at least one supporting ring (100') has a greater radial deformation in the area of the cutter legs (92a) than in the area of the transverse cutters (92c).
9. Cutting device in accordance with any one of the preceding claims, characterized in that the at least one supporting ring (100') is seated on the cutting tool (80).
10. Cutting device in accordance with claim 9, characterized in that the at least one supporting ring (100') is shrunk onto the cutting tool (80).
11. Cutting device in accordance with claim 9, characterized in that the at least one supporting ring (100') is integrally joined to the cutting tool (80).
12. Cutting device in accordance with any one of the preceding claims, characterized in that supporting rings (100') are provided on both sides of the cutting tool (80).
13. Cutting device in accordance with any one of the preceding claims, characterized in that the supporting surfaces (108, 110) are arranged on the anvil drum (70).
14. Cutting device in accordance with claim 13, characterized in that the supporting surfaces (108, 110) form a partial area of the anvil surface (76).
15. Cutting device in accordance with any one of the preceding claims, characterized in that cooperating cutter sections (92s) and anvil surface sections (76) have a defined fixed spacing, or provision is made for a slight contacting.

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