WO2013113806A1

WO2013113806A1 - Apparatus for cross-cutting a flat object moving in the direction of travel

Info

Publication number: WO2013113806A1
Application number: PCT/EP2013/051882
Authority: WO
Inventors: Andreas Biggel; Roland Zeuschner; Tobias Schellheimer; Markus Fughe
Original assignee: Hochland Se
Priority date: 2012-02-01
Filing date: 2013-01-31
Publication date: 2013-08-08
Also published as: DE102012001837A1; AR089856A1

Abstract

Disclosed is an apparatus for cross-cutting a flat object, in particular a continuously fed product web such as an extruded film (4) on which a large strip of cheese is placed, the cross-cutting action being performed perpendicular to a direction of travel (T) in which the object is conveyed. Said apparatus comprises: a cross-cutting roll (1) that includes at least one cross-cutting blade (2) which is arranged coaxially to the cross-cutting roll (1); and a blade-free pressure roll (3), the cylindrical surface of which forms an abutment for the cross-cutting blade (2) during the cutting process. The axis of rotation (A₂) of the pressure roll (3) is skewed in relation to the axis of rotation (A₁) of the cross-cutting roll (1) such that an axial cutting zone (S) in which the cross-cutting blade (2) is in cutting contact with the pressure roll (3) moves across the surface of the pressure roll during a cutting process, the pressure roll partially yielding to the pressure of the cross-cutting blade.

Description

Device for cross cutting a flat in the transport direction

article

The invention relates to a device for cross-cutting a moving in the transport direction flat object, in particular a continuously fed product tape, such as a covered with a wide cheese strip film strand, wherein the transverse cutting is perpendicular to a transport direction of the article and wherein the device comprises a cross-cutting roller with is provided at least one axially to the cross-cutting roller arranged cross-cutting blade, and wherein a knife-free counter-pressure roller is provided, the cylindrical surface forms an abutment for the cross-cutting blade during the cutting operation.

Devices for cross cutting various objects are generally known from a number of production processes. The cross-cutting wide cheese bands is known. For example, DE 10 2008 081 330 A1 discloses a device for cutting pieces of a predefinable length from a cheese strip. The cheese strip is fed by means of a conveyor belt of the cutting device and initially cut into longitudinal strips. A cross cutting knife then cuts the longitudinal strips into pieces of chisel. This procedure is suitable as long as only the soft cheese needs to be cut. However, this device is not designed to cut a string of juice provided with the cheese, because the "chopping" of the film at one go due to the tear resistance of the film is only possible with significantly higher cutting forces than cutting the quite soft cheese.

The difficulty in cross cutting a z. B. a cheese tape-providing film strand is therefore in the enormous burden that acts on the counter bearing, ie the component on which the film strand rests during cutting and which provides a counterforce for the cutting blade. If, for example, a device according to DE 10 2008 061 330 A1 is used for such an application, the counterpressure roller, which can represent the counterbearing, would have to be dimensioned very large so that the counterpressure roller can also provide a sufficient back pressure in the axially inner region. For this purpose, but then also the bearings of the platen roller would have to be significantly increased, since the platen would then have an enormous weight itself. Alternatively, the film width to be cut could be reduced, which ailerdings is undesirable. In this respect, no wide strip of film provided with a food band has yet been cross-cut.

In particular, the processing of slices of soft and partly sticky cheeses high demands are placed on the production process. Due to the sometimes relatively low mechanical stability, these cheeses are difficult to process into individual slices, as in the required processing steps, such as cooling on belts, transporting, cutting, separating and packing always mechanical loads are applied to the cheese slices, which are the shape of the cheese slices can destroy. To stabilize the mold and to guide it during production, carrier foils are used on which the shaping takes place. The carrier film can also serve as a release sheet between a plurality of disks of a disk stack. However, the cheese strip must be cut into individual slices together with the carrier foil.

DE 1 511 272 A discloses a revolving cutting device for producing straight cuts transversely to the conveying direction by continuously moving webs of paper or film material. In order to avoid a chopping cut, ie chopping in one go, a knife roll with a square cross-section and a longitudinal knife mounted on one of the outer surfaces askew to the axis of the knife roll is provided. In order to obtain a straight-line section perpendicular to the transport direction, either a fixed counter-cutting edge or a counter-roller with a smooth surface is aligned in a skewed manner with respect to the knife roller. By this double skew arrangement, a section through the web is generated perpendicular to the transport direction. Due to the square cross section of the knife roller over the cutting width uniform distance between the intersection on the cutting edge and the intersection on the counter cutting edge and thus a homogeneous load during the cut is achieved. However, the device is quite complicated to produce, inter alia due to the skewed (ie not coaxial) arrangement of the knife on the knife roller and possibly the skewed arrangement of the counter cutting edge on the counter roll.

Furthermore, JP 2010-274350 A also shows an apparatus for cutting a flat object with a cutting roller and a backwashing area. In operation, bearing points of a roller can be moved, so that the rollers can be brought in different orientations to each other. Column between the two rollers can thus be adjusted specifically during operation. The arranged on the cutting roller

Knife is spiral and therefore expensive to manufacture.

In DE 23 32 178 A1 already the principle of skew each other arranged cutting and counter-pressure rollers was used to reduce the forces acting on the counter-pressure roller during cutting loads. In order nevertheless to achieve a clean cut over the entire axial length of the rolls, the knife arranged on the cutting roll has a concave course. This knife is also expensive to produce.

It is therefore an object of the present invention to provide a device for cutting a moving object, in particular a continuously conveyed product strand, which performs a precise cut perpendicular to the direction of movement with a simple and compact mechanical structure and is relatively inexpensive to produce.

This object is achieved by a device according to claim 1. Preferred embodiments are described in the subclaims,

Due to the deliberately skewed arrangement of cross-cutting roller and knife-free counter-pressure roller, it initially results that the cross-cutting blade does not roll exactly parallel on the counter-pressure roller. It should be emphasized at this point that the cross-cutting roller does not have to be a roller in the true sense. In the case of a rigid counter-pressure roller and a rigid cross-cutting blade aligned parallel to the axis of rotation of the cross-cutting roller, it would only occur at the point of intersection of the surface of the counter-pressure control with the helical arrangement Common solder to a touch, where the common solder represents the shortest connecting line between the two axes of rotation, ie the thread would touch the knife-free platen only at one point, ideally in the middle of the platen, in the other axial areas the Querscheidemesser always have a distance from the surface of the Gegenruchwalze, so that cutting the film over the entire film width would not be possible.

However, according to the invention, the counter-pressure roller is not so rigid, but has as defined flexibility as possible, which the invention makes use of. The counterpressure roller, which has no counter cutting edge and in particular a has a cylindrical surface or a continuous cylindrical surface portion, gives in quasi on the order of the "projected diameter increase" resulting from the angle between the cross cutting roll and the counterpressure roll, as shown in the exemplary description, this "projected diameter increase" can be calculated and, accordingly, also can be set via the geometric parameters. Thus, the point of intersection, which in practice is a short partial cutting line of sometimes a few centimeters, moves from one end to the other across the surface of the counter-pressure roller when the cross-cutting knife passes. The particular advantage is that substantially less pressure is generated on the counter-pressure roller over the partial cutting line than when it is acted upon over the entire length of the complete cutting line. An important aspect of the invention is that, during the cutting process, the countershaft rests elastically and with a corresponding pretension on the cutting edge, which may also be uneven due to tolerances.

Compared with previous concepts that reduce the burden on the

Counterpressure roller target, the invention further offers the following advantages:

A transverse cutting knife arranged coaxially with the axis of rotation of the cross cutter is used, which has a constant distance over its entire length between the actual cutting cutting edge of the knife and the central axis of the cross cutter. "Coaxial with the axis of rotation" means parallel to the axis of rotation, without spiraling around the cross-cutting line This embodiment is particularly advantageous since such a cross-cutting knife can be used which has a constant cross-section over its entire length as for example the knife described in DE 23 32 178 A1 with concave course or spiral knife.

The specific resilience of the counter-pressure roller manifests itself, in particular, in the fact that the counter-pressure roller performs a clearly recognizable downward movement and then upward again in its axially inner region during a single cut, while the bearing of the counter-pressure roller (arranged axially outside) always remains in a constant position remains. The targeted flexibility of the counter-pressure roller thus allows an independent setting of the radial gap between the cross-cutting blade and counter-pressure roller, so that a clean cut is possible, despite the skewed Arrangement between cross cutter and counter-pressure roller and the coaxially oriented blade.

It can be used in operation in the position rigid storage for the platen, which is much cheaper to manufacture and maintain than a storage whose position is variable during the implementation of a cut.

The adjustment of the two rollers zueinender can be done by first the counter-pressure roller is brought into abutment with the cross-cutting blade in an end region of the cutting edge, in this intersection, a sufficiently high initial s- cutting pressure must be present to cut the object. Then, taking advantage of the flexibility of the platen, the cross-cutting roll is guided with the cross-cutting blade along the cutting edge to the center to the common solder. If the cut is in the common lot, the largest deflection of the counterpressure roll is given. If the rotation is continued, the cut moves to the other end area, where the initial cutting pressure again adjusts with exact adjustment.

It is also possible to adjust the cutting blade as follows: The countershaft has at both ends an adjustable, in particular eccentric bearing, which also serves to make the opposite angle obliquely. When adjusting the front eccentric! ager from its rear position turned forward until the countershaft rests against pressure rings of the cutting shaft. The rear eccentric bearing is already in the forward position. Now the counter-pressure around the eccentric shaft is ^" offset forward parallel to the cutting shaft. The cutting blades can be adjusted according to the countershaft so that over the entire width of a uniform light gap or even a small top result. After adjustment, the front eccentric bearing is turned back to its rear position until the counter-jewel rests against the pressure rings of the cutting shaft again. The countershaft is now at the desired angle at an angle to the blade shaft.

The skewing arrangement according to the invention thus has the effect that the rolling of the cross-cutting blade on the counter-pressure roller, viewed in the circumferential direction, takes place at different angular ranges of the cross-cutting roller in an indicated spiral. In other words, first the knife attaches to the object on one side, then the point of intersection moves across the object to the other side of the object to be cut. The deflection of the Counterpressure roller towards the center to, and then decrease again, the cutting pressure remains in the

Idealfali constant over the entire width.

The essence of the invention is thus summarized in that while avoiding a "woodcut", which occurs in one fell swoop, nevertheless, a perpendicular to the transport direction section is produced for example in a continuously conveyed film by knife cutting and not by shearing or biting already said, can be significantly reduced by the inventive arrangement, the total pressure on the platen during the cut, so that it can be built with a smaller diameter and correspondingly less technical effort.

In this case, the invention further combines the following advantages: A skewed arrangement of the cross-cutting blade on the cross-cutting roller can be dispensed with, so that the cross-cutting blade can be produced more favorably than such cross-cutting blades which are arranged askew on the cross cutting roller. At the same time, a comparatively quite weakly dimensioned counterpressure roller can be used, which is knife-less, that is to say has no counter-pressure edges or blades, and thus can also be produced inexpensively.

The article is cut through an "effective cut length" which is defined as the axial extent of that portion of the rolls in which the cross cut knife can roll on the backup roll Counterpressure roller determined.

In the context of the present description, the term "axis of rotation" of a roller is understood to mean a straight line through the two bearing axes of the roller, the axis of rotation thus being a theoretical construction line that does not bend in contrast to the central axis of the roller In common soldering, both axes of rotation preferably have an angular offset between 0.2 ° and 10 ^s .) By the common solder is meant a notional straight line which is perpendicular to the axes of rotation of both rollers The common solder intersects both axes of rotation in each case approximately in the middle of the effective one The use of the term rotation axis does not necessarily mean that the counter-pressure roller also has to rotate.The invention also works - although not so well - with a fixed counter-pressure surface According to the invention, it is intended that the counter-pressure surface, in particular the

Counterpressure roller gives way to the pressure of the cross cutter.

The axes of both rollers are preferably aligned parallel to a plane in which the flat object to be cut is arranged. The axis of rotation of the cross-cutting roller is in particular perpendicular (90 °) arranged to the conveying direction of the object to be cut, as far as a vertical section is desired. Otherwise, the axis of rotation of the cross cutting roller can be aligned parallel to the desired section. However, the axis of rotation of the counter-pressure roller is always aligned at an angle (not equal to 90 ° or 180 °) to the axis of rotation of the transverse cutting roller.

The counterpressure roller can be dimensioned such that, in spite of the tension relative to the transverse cutting roller, a cutting pressure is generated in the region of the common solder which is not significantly above the cutting pressure in the axially outer regions of the effective cutting length, although the two rollers are arranged closer to one another there further outside. If the pressure on the counter-pressure roller is so homogeneous, this leads to a better cutting characteristic.

Preferably, the device is adjusted by dimensioning the platen roller and by the alignment of the platen against the cross cutting roller so that the Querschneidemessers axially rolls in the middle with the same cutting pressure, with which also roll the two axial ends of the cross cutter on the platen roller. Deviations of the cutting pressure from max. 10% will still be the same

Considered cutting pressure.

Preferably, the counter-pressure roller has a lower flexural rigidity than the latter

Cross-cutting roll, in particular at most 0.25 times, in particular at most 0.1 times the flexural rigidity. This ensures that the counter-pressure roller relative to the cross-cutting roller has a significantly increased flexibility and can cling to the cross-cutting roller. Such conformability is required so that the counter-pressure roller can come into abutment with the cross-cutting blade even in axially outer regions of the effective cutting length. The lower bending stiffness is advantageously achieved in particular in that the counter-pressure roller has a smaller diameter than the transverse cutting roller, in particular a maximum of 0.5 times, in particular a maximum of 0.2 times the diameter. This also has the advantage that the counter-pressure roller weaker than a rigid counter pressure roller can be dimensioned and thus cheaper to manufacture. A particular advantage is the smaller space required. For example, the upstream and downstream belts can approach very close to the cutting system.

By a defined insertion of a supporting from below support arrangement, the cutting pressure on the platen roller can be selectively influenced and thus eingeeift. Preferably, the counter-pressure roller is supported over its axial extent by a plurality of Abstützanordnungen, each forming an abutment for the counter-pressure roller on that side of the counter-pressure roller, which faces away from the transverse cutting roller. By such Abstützanordnungen the loads on the bearings of the platen, which are generated by the cutting process can be reduced again. The support assemblies may include force transfer means, such as spring means, which act in a direction which is oriented transverse to the axis of rotation of the platen roller. Specifically, the support arrangements can in particular have one or more support rotors, which can roll together with the counter-pressure roller in a portion of the effective cutting length. Due to the majority of the support arrangements used in a defined manner, it is possible to set the cutting pressure to different areas of the effective cutting length in a targeted manner.

The support arrangements preferably each have adjusting means for setting a supporting force, which applies the respective supporting arrangement to the counter-pressure roller. The ability to selectively adjust the support force, there are further advantages, so the counter-pressure roller could theoretically be so soft dimensioned that it sags freely in a central region of the effective cutting length without the support arrangement. Only on the basis of one or more Abstüteanordnungen then each of the locally required cutting pressure can be adjusted. However, it is advantageous if the countershaft has a rigidity which leads to a cutting pressure with which the film can normally be cut. The Abstützungen then serve to increase this cutting pressure as needed, for example, in thicker film or increasing wear.

Because of the significant reduction in cutting pressure, the invention offers the possibility of easily designing cross-cutting devices with an effective cutting length of more than 200 mm. There are even cutting lengths in the order of the roll lengths of 600 mm possible. In this case, the counter-pressure roller in particular a resistance torque between about 785 mm ³ and about 6283 mm ³ . The Conveying speed of the cross cutting machine roller largely corresponds to

Conveying speed of the object to be cut, in particular a provided with food band film strand.

The invention will be explained in more detail with reference to FIGS. Herein shows

Figure 1 shows the schematic arrangement of a Q uersch neidewa Ize and a

Counterpressure roller of a device according to the invention

a) in front view

b) in cross-section along the section line B-B of Figure 1a) with the

Cross-cutting blade in contact with the counter-pressure roller,

c) in cross-section along the section line C-C from FIG. 1a) with the cross-cutting blade in contact with the counter-pressure roller,

d) in cross-section according to the section line D-D from FIG. 1a) with the cross-cutting blade in contact with the counter-pressure roller,

e) in plan view;

Figure 2 shows a device according to the invention in a perspective view;

Figure 3 shows the device of Figure 2 in plan view;

FIG. 4 shows the device according to FIG. 2 in side view,

FIG. 5 shows a device according to the invention in side view with supporting arrangements a) each having a roller,

b) two rollers each;

Figure 6 shows several schematic representations of the rollers to illustrate the

geometric conditions.

1 shows the schematic arrangement of the Querschnsidewalze 1 and the platen roller 3 of a device according to the invention for cutting provided with a food band film strand 4 in a direction transverse to a transport direction T of the film strand 4, ie a device for cross-cutting the Foferstrangs 4. Die Querschneidewaize is provided with at least one cross cutting knife 2. The cross cutting blade 2 is aligned parallel to the axis of rotation A _{t of} the cross cutting roller 1. In the present example, the Querschneidewaize 1 exactly a cross-cutting blade 2; but it is also possible that the Querschneidewaize 1 two or more cross-cutting blade 2, which then usually evenly circumferentially distributed on the transverse cutting roller 1 are arranged. The device further comprises a counter-pressure roller 3, which is dimensioned significantly smaller than the transverse cutting roller 1 and can bend significantly, as Figure 1a shows. The Querschneidewaize 3 has an axis of rotation A ₂ , which is not the center line of the counter-pressure roller, but by a straight line through the bearing axes of the schematically illustrated bearing 12 of the platen 3 is defined. In Figure 1a, the axes of rotation A appear parallel to each other. However, it can be seen from FIG. 1e that the axes of rotation Ai, A _{2 have} an angular offset α relative to one another. FIG. 1e illustrates a plan view of the arrangement of the two rollers 1, 3, the plan view being parallel to the common solder 8 of the rotational axes Α _Ί , A ₂ arranged in _{skewed relationship} to one another.

The deflection of the counter-pressure roller 3 in Figure 1a is exaggerated in the event that loads on the counter-pressure roller 3 side of the cross-cutting blade 2 act, the cross-cutting roller 1 so rolls on the platen roller 3. FIGS. 1b to 1d show sectional views in different regions of the effective cutting length, along the section lines BB, CC and DD from FIG. 1a. In Figure 1b, the section BB is shown. It can be seen that with respect to the transport direction T, the cutting process takes place earlier than in the areas of the effective cutting length corresponding to the illustrations of FIGS. 1 c and d, due to the skew orientations of the two axes of rotation relative to one another. It can be seen that the counter-pressure roller 3 is then always pressed by the cross-cutting blade 2 in an orientation in which the counter-pressure roller 3 in the region of the cutting point S then has the same distance from the transverse cutting roller 1. The cutting point S is that point of the surface of the platen roller 3 in a certain axial position, which can cooperate with the cross-cutting blade 2, at which momentarily the cross-cutting blade 2 rolls on the platen roller 3. The set of all points of intersection S results over the axial course of the counterpressure roller 3 a cutting line SL, which can be seen in FIG. 1e. When cross-cutting knife 2 is aligned parallel to the cross cutting roller 1, the film 4 is first cut first in the left-hand area (FIG. 1e), the cutting point S then traveling along the cutting line SL to the right. In order for a cut to be produced exactly perpendicular to the conveying direction in the film strand, the cross-cutting line 1 and the cross-cutting knife 2 are aligned exactly perpendicular to the conveying direction T. The circumferential speed of the cross-cutting blade corresponds to the conveying speed of the film strand 4. Because the counter-pressure roller 3 is essentially allowed to bend, the counter-pressure roller 3 can be dimensioned correspondingly small. It should also be noted that, due to the deflection, in turn stresses are generated which maintain a contact pressure between the counterpressure roller and the transverse cutting roller. The counter-pressure roller is dimensioned so that a cutting pressure, that is, the contact pressure of the rolling on the counter-pressure roller cross-cutting blade over the axial length is substantially constant.

FIGS. 2 to 4 will be described together below. A cross-cutting device is shown in detail, wherein the cross-cutting roller autoeist four cross-cutting blades 2, which are each offset by 90 ° in Umfartgsrichtung to each other. Again, the axes of rotation of the transverse cutting roller A, and the counter-pressure roller A _{2 are} skewed to each other. Figure 3 shows the view from above parallel to the direction of the common lot 8, from which the angular arrangement of the axes is visible to each other. In Figure 3 it can be seen that in each case an eccentric ring 13 is arranged in the bearings 12 for supporting the counter-pressure roller 3. The eccentric ring 13 has an inner cylindrical surface in which the back pressure 2 stored. The center of the internal-cynical

Surface defines the center of the bearing 12, as shown in Figure 1e. The eccentric ring 13 also has a cylindrical outer surface with which the eccentric ring 13 is mounted in the housing 11. Since the center of the cylindrical outer surface is arranged eccentrically to the center of the cylindrical inner surface, the rotational position of the eccentric 13 now defines the position of the bearing 12 in the housing 11. By changing the rotational positions of the two eccentric rings 13, the axis of rotation of the counter-pressure wave with respect to the axis of rotation of the cross-cutting roller. 1 set. This setting is done only once when installing the system and during regular maintenance. In operation, however, the axes of rotation are detected and rigid in their orientation, but still allows a rotation of the rollers and bending of the platen roller. The eccentric ring 13 can also be seen in FIG.

In the figures 2 and 4 also support arrangements 6 can be seen, which are arranged at regular intervals along the axial length of the platen roller 3 and support it. The support arrangements 6 comprise substantially cylindrical punches 9, which are aligned approximately perpendicularly with respect to the axis of rotation A _{2 of} the counterpressure roller 3 and are in contact with the counterpressure roller 3. The stamp 9 are based on a Housing part 11 of the device and can forward forces applied by the platen 3 on the support assembly 8, axially. On the underside of the Gehäuseteüs 11 adjusting screws 9 are provided with which the support force of the punch 9 can be adjusted.

In Figure 5, alternative embodiments of the support assembly 5 are shown. A

Supporting arrangement comprises in each case a support roller 7 (Figure 1a) or a plurality of support rollers 7 (Figure 2), by means of which in each case a supporting force F can be applied to the platen roller 3.

With reference to FIG. 6, the geometric relationship between the skewed orientation and the deflection of the counterpressure wad is simplified. In

Figure 6a are superimposed on the sections through the rollers 1, 3 shown in Figures 1b and 1c. On the left is a section 3 'of the counter-pressure roller in the region of the bearing in the position F (FIG. 6b). In the middle (position P "in FIG. 6b), section 3" of the deflected counterpressure roller in the region of common billet 8 is shown. In addition, a fictitious cut 3 '"of the counterpressure roller in the region of common billet 8 is shown, for the notional case that the counterpressure roller 3 does not sag, in the center of the roll the deflection amounts to z.

The deflection z is simplified by the "height difference" of the cutting points between the section 3 "of the deflected counter-pressure roller and the section 3 'of the non-deflected counter-pressure roller 3 shown.

The offset x in the conveyor belt direction of the counterpressure roller 2 between the positions P 'and P "can be determined geometrically from the angular offset α and the half roll width B (FIG. 6b):

tan () = _{B / 2} or x = 0.5Β · tan (x)

On the basis of the offset x and the cutting radius R of the cross-cutting knife 2, the first component of the deflection z ₁ can then be calculated (FIG. 6 a): R ² = (Rz + x ² or z = - - ^ RP-rf ^' + R

At B = 0.5m, R = 0.3m, a = 10 ° results in an axial displacement x of about 4 cm. The deflection z is then about 3mm.

LIST OF REFERENCE NUMBERS

1 cross cutting roller

2 cross-cutting blades

3 counter pressure roller

4 rolls of cheese covered with cheese

5 pieces of foil provided with a cheese slice

6 support arrangement

7 support rollers

8 common lot

9 stamps

10 adjusting screws

11 housing part

12 bearings

13 eccentric ring

T transport direction

F support force

S cutting point

α angular offset

z deflection

x offset in conveying direction

D diameter

B roll width

P position

A rotation axis

R knife radius

Claims

Claims Device for cross-cutting a flat object moved in the transport direction, in particular a continuously fed product strip, such as a film strand (4) swept with a wide Kise belt, perpendicular to a transport direction (T) of the object, comprising: a cross-cutting roller (1), which with at least one coaxial with the cross cutting roller

(1) arranged cross cutting knife (2), and

a knifeless counter-pressure roller (3), the cylindrical surface of which forms an abutment for the cross-cutting knife (2) during the cutting process,

characterized,

that the axis of rotation (A ₂ ) of the counter-pressure roller (3) is aligned skewed relative to the axis of rotation (Λ·,) of the cross-cutting roller (1), so that during a cutting process there is an axial cutting area (S) in which the cross-cutting knife

(2) is in cutting contact with the counter-pressure roller (3), moves over the surface of the counter-pressure roller, with the counter-pressure roller partially yielding to the pressure of the cross-cutting knife.

Device according to claim 1,

characterized,

that the axis of rotation (A ₂ ) of the counter-pressure roller (3) is rotated relative to the axis of rotation (Α·,) of the cross-cutting roller (1) when viewed along the common plumb line by an angle (et) which is between 0.2° and 10°,

Device according to claim 1 or 2,

characterized,

that the distance between the cross-cutting roller (1) and the counter-pressure roller (3) is set in the common solder so that both ends of the cross-cutting knife (2) have the same cutting pressure on the counter-pressure roller

(3) roll off.

4. Device according to claim 3,

characterized,

that the cross-cutting knife (2) rolls axially in the middle with the same cutting pressure with which the two axial ends of the cross-cutting knife (2) roll on the counter-pressure roller (3),

5. Device according to claim 3 or 4,

characterized,

that the counter-pressure roller (3) and/or its bearing is designed in such a way that it can yield to the increased cutting pressure at the point, which theoretically results from the distance-related upper level, between the two ends of the counter-pressure roller (3) in such a way that the cutting pressure This point is almost equal to the cutting pressure at the ends.

8, device according to one of the preceding claims,

characterized,

that the alignment of the axis of rotation of the counter-pressure roller (3) relative to the position of the axis of rotation of the cross-cutting roller (1) is not changed during operation.

7 Device according to one of the preceding claims,

characterized,

that the counter-pressure roller (3) has a lower bending resistance than the cross-cutting roller (1), in particular a maximum of 0.25 times, in particular a maximum of 0.1 times the bending resistance.

8. Device according to one of the preceding claims,

characterized,

that the counter-pressure roller (3) has a smaller diameter than the cross-cutting roller, in particular a maximum of 0.5 times, in particular a maximum of 0.2 times the diameter.

9. Device according to one of the preceding claims,

characterized in that the counter-pressure roller (3) is supported over its axial extent by a plurality of support arrangements (6), the support arrangements (6) each having an abutment for the counter-pressure roller (3) on the side of the counter-pressure roller facing away from the cross-cutting roller (1). (3) provide,

10. Device according to the previous claim,

characterized,

that the support arrangements (6) each comprise a support roller (7) or several support rollers (7) arranged parallel to one another.

11,. Device according to one of the preceding claims,

characterized,

that the support arrangements (6) each comprise adjustment means for adjusting a support force (F) which the respective support arrangement (6) applies to the counter-pressure roller {3).

12. Device according to one of the preceding claims,

characterized,

that the transverse cutter waize {1} and the counter-pressure roller (3) each have a length of at least 200 mm.