EP1974878B1 - Rotary cutting device - Google Patents

Abstract

A cutting roller (22) and/or a mating roller (24) have an inner core and an outer sleeve around the inner core. The outer sleeve has a clearance from the inner core, on which there is a thrust bearing to support the outer sleeve and to be so arranged that forces exerted on each other by the cutting roller and the mating roller can be diverted in a defined manner via the thrust bearing.

Description

The invention relates to a rotary cutting device, comprising a machine frame, a cutting roll rotatably mounted on the machine frame and a counter roll rotatably mounted on the machine frame, wherein the cutting roll and / or the counter roll have an inner core and an outer sleeve arranged around the inner core.

From the DE 39 24 053 A1 is a device for rotary cutting material webs with a machine frame and supported on the machine frame in pivot bearings, rotatably driven and a cutting area defining rollers, namely a cutting roller and a counter-cutting roller, which form a nip for performing the material web between them in the cutting area known. The cutting roller and counter-cutting roller are supported by rolling on them outside of the cutting area arranged spacer rings directly rolling on each other. Between the spacers engages at least one of these rollers at least one adjustable pressure roller member, which presses this one roller with adjustable force against the other roller.

From the EP 1 238 765 A2 a cutting device is known in which the cutting tool is biased substantially parallel to a rotation axis. The cutting tool has an outer sleeve on which a cutting edge sits, and an inner part, wherein the outer sleeve and the inner part are clamped against each other with a clamping force action substantially parallel to a rotational axis of the cutting tool.

Other rotary cutting devices are from the EP 0 976 510 A2 , of the EP 1 180 419 A1 , of the EP 1 186 387 A2 and the EP 1 721 712 A1 known.

From the DE 10 2004 033 032 A1 a device for punching and / or embossing of webs is known, with a punching cylinder and a counter-pressure cylinder, between which a material web is feasible, wherein the distance between the punching cylinder and the impression cylinder is adjustable and the impression cylinder mounted on a fixed axis rotatable sleeve having. On the axes of several bearings are provided, the game is adjustable via at least one clamping unit.

From the EP 0 580 576 B1 For example, a radially adjustable anvil roll assembly for use with a die iron roll of a rotary die press is known. The anvil roll assembly includes a cylindrical sleeve having an internal bore, a shaft extending through the internal bore of the sleeve, the shaft being mountable on the rotary die press for selective rotation with respect to the press, and selective rotation of the shaft independent of the rotation of the die roller of the press, as well as a idler roller means mounted on the shaft for maintaining a fixed distance between rotation axes of the shaft and the die roller. At least one cam assembly is provided which is eccentrically mounted on the shaft inside the sleeve inner bore, the cam assembly having a radial adjustment of the sleeve with respect to the die roller and the press in response to rotation of the shaft in any one infinite number of individual positions in relation to the press.

From the EP 1 655 117 A1 For example, a rotatable anvil for a rotary cutting unit is known, which comprises at least one anvil area which is provided for cooperation with a cutting part of a cutting roller. A pair of load transferring regions on the anvil are for abutment with a pair of abutting roller components. The pair of load-transmitting In this case, regions are arranged on each side of the roller region and deflection means are provided which are arranged below at least one of the anvil regions and the load-transmitting regions.

From the EP 0 263 359 A1 a cross cutter for cutting sheet-like material is known, with a pair of knife shafts, which are rotatably mounted on a tube mounted in the machine frame core and driven in common by a drive means. The blades touch each other briefly during the cutting process. At least one end of at least one core is associated with a force unit which generates a bending moment on the core, such that the blades abut each other during the contact or prestressing.

From the US 4,455,903 an anvil roll of variable diameter is known.

From the FR 2 579 507 A1 a cutting roller is known.

The invention has for its object to provide a rotary cutting device of the type mentioned, which provides a high quality cutting with a simple structure.

This object is achieved with the above-mentioned rotary cutting device according to the invention that the outer sleeve is spaced from the inner core, that on the inner core abutment are arranged on which the outer sleeve is supported, wherein between adjacent abutments a gap is formed and that the abutment arranged so and are designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the counter bearings on the counter roller and / or cutting roller, the width of an abutment being less than 30% of the total length of the cutting roller or counter roller.

In the solution according to the invention, the outer sleeve is not supported over its entire inner surface on the inner core, but only by "discrete" abutment. The counter-bearings can be arranged both on the cutting roller and on the counter-roller or only on the counter-roller or only on the cutting roller.

By means of the abutments, a defined force flow can be set on the cutting roller and / or mating roller, via which it can be achieved that the outer sleeve or outer sleeves bend less strongly under the action of cutting forces than the inner core or the inner cores. When cutting occurs, the fundamental problem that, since the cutting roller and the counter-roller are clamped on at least one side of the machine frame, they bend. When cutting forces act, the mating roll bends away from the cutting roll and the cutting roll bends away from the mating roll. This results in an increased distance between the surfaces of the cutting roller and the counter roll, which can lead to a deterioration of the cutting quality.

In the solution according to the invention, the bending of the cutting roller and / or counter-roller on the surface can be reduced since forces can be diverted away from the outer sleeve into the inner core and from there via a bearing. With appropriate arrangement of the abutment leaves thereby reduce the relative deflection on the surface of the cutting roller and / or counter-roller. The arrangement and design of the abutment depends on the particular application.

By the solution according to the invention, it is possible to use "less stiff" cutting rollers and / or counter-rollers, d. H. in particular to use rollers, which have a relatively small diameter and are relatively long. This, in turn, for example, can produce large-scale cuts that are not possible with rotary cutting devices with shorter rolls. Furthermore, this also makes it possible, for example, to achieve a higher cutting rate if longer rollers are provided, on which several cutting areas are arranged.

The abutments are arranged and designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the abutments on the counter roller and / or cutting roller. It can be a force flow at the counter roll and / or cutting roller reach, in which the deflection of the outer sleeve is smaller than the deflection of the inner core.

For the same reason, it is favorable if the abutments are arranged and designed so that the outer sleeve is movable relative to the inner core by elastic deformation. Due to a relative mobility between outer sleeve and inner core, a relative deflection between outer sleeve and inner core is possible. As a result, it is possible that the outer sleeve deflects less than the inner sleeve when cutting forces act.

For the same reason, it is advantageous if the abutments are arranged and designed so that in a cutting operation, a deflection of the outer sleeve is smaller than a deflection of the inner core.

It is favorable if there is a space (clearance) outside the abutment between the outer sleeve and the inner sleeve. The height of this clearance (in the radial direction) may be in an order of magnitude of, for example, between 2 μm and 100 μm. He can be taller too be. By this clearance, a relative deflection between the outer sleeve and the inner core is made possible, so as turn to keep the deflection on the surface of the cutting roller and / or counter roll low.

For the same reason, it is favorable if there is a clearance (clearance) between adjacent thrust bearings. The outer sleeve is then mounted on discrete counter bearing on the inner core.

It is favorable if the abutments are arranged and designed such that an at least approximately symmetrical force flow with respect to the cutting roller length and / or mating roller length results on the cutting roller and / or mating roller during a cutting operation. The force flow is in particular symmetrical to a central transverse plane (which is perpendicular to the axis of rotation) of the cutting roller and / or counter-roller. It can thereby achieve a minimized deflection on the surface of the cutting roller, which is symmetrical to said center plane.

It is fundamentally possible for the abutments to be formed, for example, by a plurality of balls which are arranged on the inner core. In a manufacturing technology simple embodiment, the abutment comprise a ring portion, which is arranged on the inner core. The ring area surrounds in particular band-shaped inner core. The annular region is formed for example by a ring element, which is arranged on the inner core. The annular region can also be formed in one piece on the inner core.

The width of a ring portion is smaller than the total length of the respective counter roll or cutting roll and in particular considerably smaller. It is for example at most 30% of the total length. In principle, it is advantageous if the annular region has the smallest possible width. At the ring area, where forces are transmitted, must however, the specific surface pressure is within the elastic range. This defines the minimum extent of the ring area.

In one embodiment, it is provided that the outer sleeve is fixed to the counter bearings, for example via form-locking elements. As a result, the outer sleeve can be fixed radially and axially with respect to the inner core in a simple manner.

It can be provided that at least one seal is arranged between the outer sleeve and the inner core. The seal is arranged in particular on one or more end faces of the outer sleeve. It can thereby seal a gap between the outer sleeve and the inner core.

It is particularly advantageous if the abutments are arranged symmetrically on the cutting roller and / or counter-roller. If, for example, a single abutment for the cutting roller or counter-roller is provided, then this is arranged centrally (relative to a counter-roller length or cutting roller length). If a plurality of abutment are provided, then these are arranged in particular symmetrically to a median plane of the backing roll or cutting roll.

It can be provided that the cutting roller has an outer sleeve, that one or more cutting edges are arranged on the outer sleeve of the cutting roller.

It is particularly advantageous if the cutting roller and the mating roller are each provided with abutments, arranged opposing bearing opposite. An abutment of the cutting roller and an abutment of the counter-roller then face each other. In this case, the abutments are aligned in a direction transverse to an axis of rotation of the cutting roller. As a result, forces can be derived in a defined manner and the surface deflection both at the cutting roller and at the counter roller can be minimized. This gives an optimized cutting result.

In one embodiment, the cutting roller is supported on the counter-roller via at least one support ring. The at least one support ring can be arranged on the cutting roller or the counter-roller.

In particular, a first support ring and a second support ring are then provided, wherein the abutment are arranged on the counter-roller and / or cutting roller between the first support ring and the second support ring. As a result, an optimization of the power flow can be achieved.

The counter-roller is in particular rotatably mounted. It can be directly driven (via its own drive or via a transmission device which is connected to the drive of the cutting roller). It is also possible in principle that the counter-roller is driven by frictional engagement with material to be fed.

In one embodiment, the cutting roller is mounted on both sides of the machine frame. It is then provided in particular a first pivot bearing and a spaced second pivot bearing.

In this case, it is advantageous if the counter-roller is mounted on both sides of the machine frame.

It is also possible that the cutting roller is mounted on one side (rotatable, for example, via a single bearing) on the machine frame. Such a rotary cutting device with cantilevered cutting roller can be compact.

In this case, then in particular the counter-roller is mounted on one side "flying" on the machine frame.

For example, one or more cross-cutters are arranged on the cutting roller. For example, the rotary cutting device is designed as a cross-cutting device. It can thereby be separated, for example, webs of material with a high cutting rate.

It is also alternatively or additionally possible that one or more longitudinal cutting edges are arranged on the cutting roller. In particular, cutting edges are designed so that it is possible to introduce contour cuts.

Figur 1

eine seitliche Ansicht eines Ausführungsbeispiels einer erfindungsgemäßen Rotationsschneidevorrichtung;

Figur 2

eine schematische Darstellung einer Gegenwalze;

Figur 3

eine stirnseitige Draufsicht auf die Gegenwalze gemäß Figur 2;

Figur 4

eine Schnittansicht der Gegenwalze längs der Linie 4-4 gemäß Figur 3;

Figur 5

eine vergrößerte Darstellung des Bereichs A gemäß Figur 4;

Figur 6

schematisch die Verformung eines Innenkerns der Gegenwalze über deren Länge, wenn eine Schneidkraft ausgewirkt wird;

Figur 7

dazu angepasst die Verformung einer entsprechenden Rotationswalze, wenn diese auf die Gegenwalze wirkt;

Figur 8

schematisch die Verformung einer Außenhülse im Vergleich zum Innenkern bei der erfindungsgemäßen Lösung;

Figur 9

ein zweites Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung (Querschneidvorrichtung);

Figur 10

eine Schnittansicht der Rotationsschneidevorrichtung gemäß Figur 9; und

Figur 11

ein drittes Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung.

The following description of preferred embodiments is used in conjunction with the drawings for a more detailed explanation of the invention. Show it:

FIG. 1

a side view of an embodiment of a rotary cutting device according to the invention;

FIG. 2

a schematic representation of a counter-roller;

FIG. 3

a frontal plan view of the mating roll according to FIG. 2 ;

FIG. 4

a sectional view of the backing roll along the line 4-4 according to FIG. 3 ;

FIG. 5

an enlarged view of the area A according to FIG. 4 ;

FIG. 6

schematically the deformation of an inner core of the counter roll over the length thereof, when a cutting force is affected;

FIG. 7

adapted to the deformation of a corresponding rotation roller, when it acts on the counter-roller;

FIG. 8

schematically the deformation of an outer sleeve compared to the inner core in the inventive solution;

FIG. 9

A second embodiment of a rotary cutting device according to the invention (cross-cutting device);

FIG. 10

a sectional view of the rotary cutter according to FIG. 9 ; and

FIG. 11

A third embodiment of a rotary cutting device according to the invention.

A first embodiment of a rotary cutting device according to the invention, which in FIG. 1 shown and designated therein by 10 is realized as a rotary cutting machine. It comprises a machine frame 12, which is designed like a stand. The machine frame 12 has opposite uprights 14 which are connected by a bottom bridge 16 and a top bridge 18. About the bottom bridge 16, the rotary cutting device 10 is placed on a base.

The respective uprights 14 in turn comprise opposite uprights 20a, 20b.

On the uprights 14 of the machine frame 12 are each a cutting roller 22 and a counter-roller 24 (anvil roller) rotatably mounted. The cutting roller 22 is mounted rotatably about an axis 28 via opposite rotary bearings 26. In FIG. 1 the axis 28 is perpendicular to the plane of the drawing.

The cutting roller 22 is associated with a drive for the rotational movement (not shown in the drawing). Via a biasing device 30, the cutting roller 22 can be pressed against the counter-roller 24.

The cutting roller 22 is supported on opposite support rings 32 on a surface 34 of the counter-roller 24. Alternatively, it is also possible that the counter-roller 24 is provided with support rings, which are supported on a surface of the cutting roller 22.

The pivot bearings 26 for the cutting roller 22 are arranged on a respective bearing device 36, which is linearly displaceable on the machine frame 12. By the biasing means 30, the bearing means 36 as a whole (including the pivot bearings 26 and the cutting roller 22) can be displaced against the counter roll 24 to exert a cutting force.

The cutting roller 22 has one or more cutting edges 38, which are arranged between the support rings 32.

The counter-roller 24 is likewise rotatably mounted about an axis 42 via opposite rotary bearings 40, which are arranged on the respective stator 14. The axis 42 is parallel to the axis 28.

To carry out a cutting operation, a material 44 to be cut, which in particular is in the form of a web, is carried out between the counter-roller 24 and the cutting roller 22 between the support rings 32. The counter roll 24 and the cutting roll 22 rotate in opposite directions to each other. By the biasing means 30, the cutting roller 22 is pressed to exert a cutting force against the counter-roller 24.

The counter-roller 24 has an inner core 46 ( FIGS. 2 to 4 ). The inner core is in particular cylindrically shaped and rotationally symmetrical about an axis 48 which coincides with the axis of rotation 42.

On the inner core, a first stub shaft 50 and a second stub shaft 52 are arranged, which serve for pivotal mounting of the counter-roller 24.

On the inner core 46, a first counter bearing 54a and a second counter bearing 54b are arranged in the embodiment shown. These abutments 54a, 54b are annular and arranged on the inner core 46 in the manner of a band. The anvils 54a, 54b may be integrally connected to the inner core 46 or may be separate parts, which are fixed to the inner core 46.

The first abutment 54a and the second abutment 54b have, as in FIG. 5 indicated, a larger radius r ₁ as a surface area 56 (radius r ₂ ) of the inner core 46 outside the anvil 54a, 54b. The anvils 54a, 54b are thereby stepped above the surface region 56. They each have a contact region 58, which is radially spaced from the surface region 56 of the inner core 46.

The abutments 54a, 54b are "discrete" supports having a width (parallel to the axis 48) which is significantly smaller than the total length of the backing roll 24. More specifically, this width is less than 30% of the total length. In principle, the smaller the width of an abutment 54a, 54b, the more advantageous it is for the introduction of force. The smaller the width, the less the mobility of the outer sleeve 60 relative to the inner core 46 is hindered. It should be noted, however, that the specific surface pressure acting on an abutment is still within the elastic range of the anvil, so that no plastic deformation can take place. For example, the relative width of an abutment relative to the total length of a cutting roller or counter-roller may also be in a range of 0.5% or less. The extent depends on the specific circumstances of the corresponding rotary cutting device.

The counter-roller 24 also has an outer sleeve 60, on which the surface 34 of the counter-roller 24 is formed. This surface 34 is in particular cylindrical. The outer sleeve 60 has the shape of a hollow cylinder. The cutting roller 22 with the support rings 32 acts on this outer sleeve 60th

The outer sleeve 60 is supported on the discrete counter bearings 54a, 54b; the outer sleeve 60 is not supported over the entire surface area 56 on the inner core 46, but only on the contact areas 58 of the abutment 54a, 54b. Between an inner side 62 of the outer sleeve 60 and the surface region 56 of the inner core 46, a gap 64 is formed. This intermediate space 64 permits a relative deflection between the outer sleeve 60 and the inner core 46, in particular via different elastic deformation of the inner core 46 and the outer sleeve 60.

The first abutment 54a and the second abutment 54b are arranged symmetrically on the inner core 46. They have the same distance to a median plane 66 of the counter-roller 24. The center plane 66 is perpendicular to the axis 48. Further, the first abutment 54a has the same distance to a first end 68a of the inner core 46 (outside of the first stub shaft 50) as the second abutment 54b to an opposite second front end 68b.

The outer sleeve 60 is fixed relative to the inner core 46. For example, it is fixed on the inner core 46 via form-fitting means via the abutments 54a, 54b.

It may additionally or alternatively be provided that the outer sleeve 60 is axially clamped. For this purpose, for example, opposite support disks 70a, 70b are provided, which are arranged in the vicinity of the respective first front end 68a and second front end 68b. Between the respective support disk 70a, 70b and a respective end face of the outer sleeve 60, a respective seal 72a, 72b is arranged, this seal in particular has the shape of an O-ring. By the respective seal 72a, 72b of the intermediate space 64 is sealed to the front side of the outer sleeve 60.

The support disks 70a, 70b are retained on the inner core 46 via respective circlips 74a, 74b in a direction away from the outer sleeve 60.

A height h of the gap 64 is for example in the range between 2 microns and 100 microns, depending on the application. The height h can also be smaller or larger than just mentioned.

The counter-roller 24 is provided with at least one counter-bearing as described. It may alternatively or additionally be provided that the cutting roller 22 is provided with one or more abutments. The structure and arrangement of such an abutment on the cutting roller 22 is basically the same as described in connection with the counter-roller 24.

In a rotary cutting operation, the cutting roller 22 is pressed by the biasing means 30 against the counter roll. By the cutting forces, a force is exerted on the counter-roller 24 and on the cutting roller 22, a counter force is exerted.

The counter-roller 24 is clamped via its rotary bearings 40 in the region of the first stub shaft 50 and the second stub shaft 52 on the machine frame 12, respectively. This is in FIG. 6 indicated by the support points 76a, 76b. By the cutting roller 22 forces 78 are exerted from the direction of the cutting roller ago. In the embodiment shown, these forces 78 act with respect to the direction of gravity g from above. These forces 78 cause a deflection of the counter roll 24 (especially the inner core 46) down.

In FIG. 6 is a diagram for a counter-roller having a diameter of 50 mm, in which the deflection dy of the inner core 46 over the length 1 of the counter-roller 24 is shown. In this case, cutting forces in the order of 125 N / mm were exercised.

It can be seen that in a middle region of the counter-roller 24, the inner core 46 undergoes a deflection of the order of magnitude of 22 μm downwards.

In FIG. 7 the cutting roller 22 is shown with a stub shaft 80a and a stub shaft 80b. By the biasing means 30, a force is exerted in the direction of the counter roll 24. In the embodiment shown, this is a force parallel to the direction of gravity g. The cutting roller 22 is clamped at the top. This is in FIG. 7 indicated by support points 82a, 82b.

Due to the forces acting and in particular the reaction forces of the counter roll 24, the cutting roller 22 is bent upwards. In particular, an inner core of the cutting roller 22, when having such an inner core, bent upwards.

In FIG. 7 2, a diagram is shown for the deflection of the cutting roller or of an inner core of the cutting roller over the length I of the cutting roller 22. The data correspond to a cutting roller with a diameter of 40 mm with acting cutting forces of 125 N / mm.

It can be seen that in the central region of the cutting roller 22 there is an upward deflection of approximately 40 μm.

If you have the FIGS. 6 and 7 compares, then based on the corresponding inner cores of the cutting roller 22 and the counter-roller 24 in the central region, a relative deflection of opposite surface areas of the cutting roller 22 and the counter-roller 24 before, if these surface areas would follow the deflection of the inner cores, of about 60 microns before , Such deflections, when present on the surface of mating roll 24 and cutting roll 22, compromise the quality of the cutting result.

In particular, these disturbing deflections on the surfaces are the greater, the longer the cutting roller 22 and the counter-roller 24 are and the smaller the diameter of these rollers.

In the solution according to the invention, the outer sleeve 60 is supported on the inner core 46 via the counter bearings 54a, 54b. (This support can be provided both for the cutting roller 22 and for the counter-roller 24 or only for the cutting roller 22 or only for the counter-roller 24.) It can thereby initiate defined forces during the cutting process and in particular cutting forces and derived. Cutting forces can be introduced from the outer sleeve 60 into the inner core 46 via the abutments 54a, 54b and thereby derive via the corresponding pivot bearings 26 and 40, respectively.

With an appropriate arrangement of the at least one thrust bearing, it can be achieved that the outer sleeve 60 is bent less strong than the corresponding inner core 46. This is greatly exaggerated in FIG. 8 indicated. By the cutting forces of the inner core 46 undergoes elastic deformation and in particular deflection. The outer sleeve 60 also experiences an elastic deformation and deflection. By supporting the outer sleeve 60 on the abutments 54a, 54b with the defined force introduction, the deformation of the outer sleeve 60 can be significantly lower than that of the inner core 46. This results in the construction of cutting forces a relative deflection or relative movement between the outer shell 60 and the inner core 46. If the outer sleeve 60 is less arcuate than the inner core 46, then with respect to the starting point without acting cutting forces, the surface 34 of the outer sleeve 60 (when it comes to the outer sleeve of the backing roll 24) less deflected than the inner core 46. As a result, the deviation of the surface 34 of the outer sleeve 60 from the "ideal line" is less strong than if no discrete counter bearings 54a, 54b are provided. In turn, the relative deflection of the surface 34 to the cutting roller 22 is less strong and gives better cutting results. In particular, thereby longer counter-rollers 24 can be used with a smaller diameter.

The advantages described are also present when the cutting roller 22 is mounted with an outer sleeve on discrete counter-bearing on the corresponding inner core. If the cutting roller 22 is provided with the solution according to the invention, then one obtains an overall lower relative deflection of the surfaces of the cutting roller 22 and the counter-roller 24th

Depending on the application and in particular the formation of the cutting roller 22, one or more abutments are provided. These counter-bearings are arranged and designed such that a symmetrical force flow results on the cutting roller 22 or the counter-roller 24. The power flow is in particular symmetrical to the center plane 66.

The outer solution 60 can be characterized less deform elastically than the corresponding inner core 46. This in turn are surface areas 84 of the cutting roller 22 (if this with one or provided with a plurality of counter-bearings) and / or the counter-roller 24 (if this is provided with one or more abutments) deformed less than when the outer sleeve 60 "full-surface" sits on the inner core 46 or no outer sleeve is provided.

The rotary cutting device 10 is designed, for example, such that cutting edges are arranged on the cutting roller 22 which are arranged in a longitudinal direction (relative to a longitudinal direction 86 (FIG. FIG. 1 ) for transporting material 44) and in a transverse direction thereto.

A second embodiment of a rotary cutting device according to the invention, which in FIG. 9 is shown and designated therein by 88, comprises a machine frame 90 on which basically the same as described above, a cutting roller 92 and a counter-roller 94 are each rotatably mounted are. The counter-roller 94 is basically the same design as the counter-roller 24 as described above.

The cutting roller 92 is driven by, for example, a drive (not shown in the drawing). At a stub shaft 96 of the cutting roller, a gear 98 is arranged, which engages in a gear 100 which is fixed in rotation with respect to the counter-roller 94. As a result, the counter-roller 94 can also be driven by driving the cutting roller 92.

The cutting roller 92 has a first roller portion 102a and a second roller portion 102b, wherein these two roller portions 102a, 102b are spaced from each other. At the first roll portion 102a and the second roll portion 102b, a plurality of cross cutters 104 are respectively disposed. These cross cutters are evenly distributed. For example, they are spaced at an angle of 120 ° (relative to a cross section).

The transverse cutting edges 104 have a cutting surface 106, which is transverse and in particular perpendicular to a direction of transport of material through the rotary cutting device 88. In particular, the cutting surfaces 106 are oriented parallel to a rotational axis 108 of the cutting roller 92.

In a central region of each of the first roller portion 102a and the second roller portion 102b, an abutment 110a, 110b is arranged. The anvil 110a, 110b is basically the same design as described above. In particular, these are annular regions which are arranged on a respective inner core 112 of the cutting roller 92.

The counter-roller 94 also has an inner core 114, on which spaced abutments 116a, 116b are arranged. In particular, the counter bearings 116a, 116b are aligned with the counter bearings 110a, 110b and positioned directly opposite one another, so that a direct introduction of force to the counter bearings is possible. The counter bearing 116a is then the counter bearing 110a opposite and the abutment 116b is opposite the abutment 110b.

Otherwise, the rotary cutter 88 functions as described above.

In a third embodiment of a rotary cutting device, which in FIG. 11 shown and designated there by 118, a machine frame 120 is provided. On the machine frame 120, a first pivot bearing 122 is arranged for a counter-roller 124. Furthermore, a second pivot bearing 126 is arranged on the machine frame 120 at a distance from the first pivot bearing 122, for example above it. About this second pivot bearing 126, a cutting roller 128 is rotatably mounted. The cutting roller 128 and the counter roller 124 are thereby not each two-sided mounted on the machine frame 120, but held only on one side "flying" on the machine frame 120.

The cutting roller 128 has, for example, opposing support rings 130a, 130b. About these support rings 130a, 130b, the cutting roller 128 is supported on a surface 132 of the backing roll 124 from. It is also a version without support ring possible.

The cutting roller 128 is provided with cutting edges 134. The blades 134 are adapted to the material to be cut.

Counter roll 124 and cutting roll 128 each have an inner core and respective outer sleeves 136 and 138 as described above. The outer sleeve 138 of the cutting roller 128 is supported via a single abutment 140 on the corresponding inner core of the cutting roller 128. The outer sleeve 136 of the counter-roller 124 is supported via an abutment 142 on the inner core of the counter-roller 124. The abutments 140 and 142 are directly opposite to allow a direct application of force.

Otherwise, the rotary cutter 118 functions as described above.

Claims (22)

1. Rotary cutting device, comprising a machine frame (12; 90; 120), a cutting roll (22; 92; 128) rotatably mounted on the machine frame (12; 90; 120), and a mating roll (24; 94; 124) rotatably mounted on the machine frame (12; 90; 120), wherein the cutting roll (22; 92; 128) and/or the mating roll (24; 94; 124) comprise an inner core (46) and an outer sleeve (60) disposed around the inner core (46), characterized in that the outer sleeve (60) is spaced from the inner core (46), that on the inner core (46) there are disposed pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142), on which the outer sleeve (60) is supported, an intermediate space (64) being formed between adjacent pressure bearings (54a, 54b), and in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in a way that allows forces, which the cutting roll (22; 92; 128) and mating roll (24; 94; 124) exert on one another, to be dissipated in a defined manner by means of the pressure bearings on the mating roll and/or cutting roll, the width of a pressure bearing (54a, 54b, 110a, 110b; 116a, 116b; 140; 142) being smaller than 30% of the total length of the cutting roll (22; 92; 128) or mating roll (24; 94; 124),
2. Rotary cutting device according to claim 1, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that the outer sleeve (60) is movable by elastic deformation relative to the inner core (46) .
3. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that during the cutting operation a bowing of the outer sleeve (60) is smaller than a bowing of the inner core (46).
4. Rotary cutting device according to one of the preceding claims, characterized in that outside of the pressure bearings between the outer sleeve (60) and the inner core (46) an intermediate space (64) is formed.
5. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that there arises at the cutting roll (22) and/or mating roll (24) during the cutting operation an at least approximately symmetrical distribution of the flow of force in relation to the cutting roll length and/or mating roll length.
6. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) surround an annular region that is disposed on the inner core (46) .
7. Rotary cutting device according to claim 6, characterized in that a width of the annular region is at most 30% of the total length of the mating roll (24) and/or cutting roll (22).
8. Rotary cutting device according to one of the preceding claims, characterized in that the outer sleeve (60) is fixed on the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142).
9. Rotary cutting device according to one of the preceding claims, characterized in that at least one seal (72a, 72b) is disposed between the outer sleeve (60) and the inner core (46).
10. Rotary cutting device according to claim 9, characterized in that the at least one seal (72a, 72b) is disposed on the end face of the outer sleeve (60).
11. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed symmetrically on the cutting roll (22) and/or mating roll (24).
12. Rotary cutting device according to one of the preceding claims, characterized in that one or more cutting edges are disposed on the outer sleeve of the cutting roll (22).
13. Rotary cutting device according to one of the preceding claims, characterized in that, where the cutting roll (128) and the mating roll (124) are each provided with pressure bearings (140; 142), pressure bearings (140, 142) lie opposite one another.
14. Rotary cutting device according to one of the preceding claims, characterized in that the cutting roll (22) is supported on the mating roll (24) by means of at least one supporting ring (32).
15. Rotary cutting device according to claim 14, characterized in that a first supporting ring and a second supporting ring are provided, wherein the pressure bearings are disposed on the mating roll (24) and/or cutting roll (22) between the first supporting ring and the second supporting ring.
16. Rotary cutting device according to one of the preceding claims, characterized in that the mating roll (24) is rotatably mounted.
17. Rotary cutting device according to one of the preceding claims, characterized in that the cutting roll (22) is mounted at two ends on the machine frame (12).
18. Rotary cutting device according to claim 17, characterized in that the mating roll (24) is mounted at two ends on the machine frame (12).
19. Rotary cutting device according to one of claims 1 to 16, characterized in that the cutting roll (128) is mounted at one end on the machine frame (120).
20. Rotary cutting device according to claim 19, characterized in that the mating roll (124) is mounted at one end on the machine frame (120).
21. Rotary cutting device according to one of the preceding claims, characterized in that one or more transverse cutting edges (104) are disposed on the cutting roll (92).
22. Rotary cutting device according to one of the preceding claims, characterized in that one or more longitudinal cutting edges (134) are disposed on the cutting roll (128).

Images