EP1902820A2 - Device for cutting and/or embossing a blank or a web - Google Patents

Abstract

The device has a cutting roller (2) with a longitudinal axis (20) and two ends, where each end is mounted in a bearing to rotate. A counter-roller (3) works together with the cutting roller and is mounted to rotate. A force application device i.e. pivot lever (19), applies a pressure force (F) to a circumference surface (5) of the cutting roller, where the pressure force is diverted into each of the bearings by a part of the cutting roller, so that the pressure force is not applied to the counter-roller.

Description

I. Application area

The present invention relates to a device for cutting and / or embossing a sheet, a blank or a material web. The sheet may, for example, be a cardboard sheet from which folding carton blanks are cut out. The blank can be, for example, envelope blanks, which are trimmed and / or embossed as part of the production of finished envelopes. The material web can be, for example, a paper web from which envelope or label blanks are cut out.

II. Technical background

From the DE 103 05 032 B3 a punching device for the production of labels is known, which has a rotatably mounted punching roller and a rotatably mounted counter-pressure roller. Each of the two rollers has on its periphery two so-called, long known bearer rings in the form of closed circumferential running surfaces. The punching and the counter-pressure roller are pressed against each other on these mutually rolling treads with relatively large forces in order to avoid disturbing roll vibrations during operation of the punching device and thereby to ensure an axially as constant as possible gap width between the two rollers. For this presses a Kraftbeaufschlagungseinrichtung in the form of two pairs of rollers on the running surfaces of the bearer rings of the punching roller.

Bearer rings have the disadvantage that they heat up due to the Hertzian pressure and the slip between the mutually rolling treads and thereby lead to non-uniform deformations of the nip. Some slippage always occurs because the diameters of the bearer rings, e.g. in order to get the possibility of regrinding, never equal, but force the drive gears a synchronization of the rollers. In addition, dirt reaching the bearer rings can cause variations in the gap width, resulting in deterioration of the punching result.

In the known devices with bearer rings acts on the counter-pressure roller in addition to the dead weight and the punching force during the punching operation, the force applied by the force applying pressure force. Therefore, the platen roller is deflected relatively strongly relative to the punching roller, so that the gap between the two rollers is deformed nonuniformly, which in turn may result in deterioration of the quality of the punching result.

Devices of the type in question are also known without bearer rings. If standard bearings with more or less play are always used in these devices for storing the punching roller, it may happen that the punching roller is raised during the punching operation in the context of the bearing clearance, resulting in a change in the gap width between the two rollers and thereby to a deterioration the punching result can lead. To eliminate this disadvantage, must be used in devices without bearer expensive, play-free bearings for storage of the punching roller.

Another disadvantage of the known devices with or without bearer rings is that due to the relatively large distance between the bearings a relatively large deflection of the rollers occurs.

From the WO 2006/004474 A1 is a device with top-mounted cutting roller and arranged below counter-pressure roller known, in which case each of the rollers has bearer rings, with the help of which the rollers are pressed against each other. The bearings of the counter-pressure roller are arranged offset to one another so that their distance is less than the distance between the bearings of the cutting roller. The bearer rings are located in the axial direction in each case between the further outer bearing of the cutting roller and the further inner bearing of the counter-pressure roller.

The bearings of the counter-pressure roller are acted upon in this known device against its own weight force with an upward pressure force, so that the counter-pressure roller between the bearer rings bends upwards. The cutting roller bends upwards due to the pressure applied to it by the bearer rings. During the cutting operation, in which the material to be cut is guided between the rollers, a cutting force occurs which acts on the one hand on the counter-pressure roller down and on the other hand on the cutting roller upwards. This compensates for the upward deflection of the platen so that the latter is horizontally rectilinear, i. essentially without deflection, runs. In contrast, the cutting roller is additionally bent upward, so that in turn results in a non-uniformly deformed nip. Due to the existing bearer rings, the disadvantages associated with these are again given.

III. Presentation of the invention a) Technical task

It is therefore an object of the present invention to provide a device for cutting and / or embossing a sheet, a blank or a material web, which is the setting of a uniform gap width of Gap between the cutting and / or embossing roll and the counter roll over the axial width allows away.

b) Solution of the task

This object is achieved by means of a device having the features of claim 1. Further features of the present invention will become apparent from the dependent claims.

According to the invention, the pressure force applied by the force application device to the circumferential surface of the cutting and / or embossing roller is completely diverted into its bearing by at least part of the cutting and / or embossing roller, so that the counter roller is not subjected to the pressure force. This means that according to the invention no forces are transmitted between the cutting and / or embossing roller on the one hand and the counter-roller on the other hand, in addition to the material located between the rollers during operation. The force transmitted during the cutting and / or embossing operation between the rollers via the material located between them is referred to below as cutting and / or embossing force.

The cutting and / or embossing roller according to the invention always has a certain deflection. The size of this deflection can be varied by adjusting the size of the pressure applied to it, so that sets in the cutting and / or embossing operation a deflection of the counter roll, wherein the bending lines of the cutting and / or embossing roll and the counter roll at least in their have relevant axial curvature during operation substantially the same curvature and accordingly could be placed there substantially congruent to each other. According to the invention, a uniform gap width of the gap between the cutting and / or embossing roller and the counter-roller is achieved at least over the relevant axial width of the rollers. As for the counter roll only nor their self-weight force and the cutting and / or embossing force act, according to the invention advantageously reduces the deflection of the backing roll and the uniformity of the gap width by adjusting the bending lines of the two rolls together can be carried out at a reduced deflection level.

The applied compressive force and the self-weight force push the cutting and / or embossing roll in a certain direction so that the possibly existing bearing clearance in the bearings of the cutting and / or embossing roll is prevented in the manner of a bias voltage, i. not available for movement of the cutting and / or embossing roll. Preferably, play-bearing standard bearings can therefore be used in the context of the present invention. The sum of the self-weight force of the cutting and / or embossing roller and the vertical component of the pressure applied to it is always greater than the vertically acting upwards cutting and / or embossing force according to the invention.

Due to the no longer existing Hertzian pressure and the no longer existing slip between the cutting and / or embossing roll and the counter roll heat generation during the rotation of the rolls is also avoided as it is the case with the successive rolling Schmitzringen in the prior art. As a result, thermal expansions and thus possibly associated deformations of the gap between the two rolls are avoided in an additionally advantageous manner.

A further advantage of the device according to the present invention is that it can be used not only in conjunction with solid rolls but also advantageously in conjunction with rolls, on the lateral surfaces of which detachable foil knives are attached. In the past Schmitzringystemen no use of foil knives with varying thicknesses was possible because a foil blade thickness change would have required a processing of the bearer rings.

To adjust the gap width of the gap between the cutting and / or embossing roller on the one hand and the counter roller on the other hand, a Spaltinstelleinrichtung can be provided, which is acted upon or biased with the derived in the storage of the cutting and / or embossing roller pressure force. The gap adjusting device can be, for example, at least one wedge acting between the two rollers, which can be moved by means of a manually operable adjusting mechanism.

The force application device is preferably at least one pivoting lever pivotably mounted about a pivot axis and on which at least one pressure roller is mounted at a distance from the pivot axis. By applying the pivot lever at its end facing away from the pivot axis end, the pressure roller is pressed against the peripheral surface of the cutting and / or embossing roller and thereby exerted the pressure force on the cutting and / or embossing roller.

Preferably, the pressure roller engages at a location on the peripheral surface of the cutting and / or embossing roller, which is arranged lying horizontally offset to the longitudinal axis thereof. As a result, a stable equilibrium position of the rollers is achieved even with exactly vertical superimposed longitudinal axes of the two rollers. It is also particularly advantageous to displace the longitudinal axes of the two rollers horizontally relative to each other. In conjunction with the offset to the longitudinal axis of the cutting and / or embossing roller point of attack of the pressure roller results in a further improved stable equilibrium position of the rollers relative to each other.

According to the invention, the cutting and / or embossing roller can be driven by a motor and transmit its rotational movement via a gear drive to the counter-roller. For this purpose, the cutting and / or embossing roller on a drive gear, which meshes with a gear driven by it counter-roller. The drive gear or the driven gear according to the invention may be formed divided along a radial plane of the cutting and / or embossing roll or counter-roll and a first part gear and a second partial gear include. The two partial gears are rotatable relative to each other about the longitudinal axis of the cutting and / or embossing roll or counter-roll and rotatably connected in an arbitrarily selected rotational position with the cutting and / or embossing roll or counter-roll connectable. As soon as, in particular due to a change in the gap width by means of the Spaltinstelleinrichtung a backlash between the drive gear and driven by him gear results in the fixation of the gear teeth relative to each other and the backlash can be compensated by turning the gear teeth relative to each other.

Furthermore, in addition to the force application device acting upon the cutting and / or embossing roller, a further force application device can be provided, which acts on the counter roller with a counterforce acting in a radial direction substantially opposite to the direction of the pressure force and with material not located between the rollers is completely derived in the bearings of the backing roll. In this way, it is possible to actively act on the counter roll with a counterforce of such a size that causes the resulting bending lines of both the cutting and / or embossing roll and the counter roll during the cutting and / or embossing operation is substantially rectilinear and no longer curved. The further Kraftbeaufschlagungseinrichtung can its construction according to the same as the cutting and / or embossing roll acting on Kraftbeaufschlagungseinrichtung are formed.

c) embodiment

Fig. 1:

Eine Schnittansicht einer Ausführungsform der erfindungsgemäßen Vorrichtung in einer Radialblickrichtung; und

Fig. 2:

Eine Schnittansicht derselben Ausführungsform der erfindungsgemäßen Vorrichtung in Axialblickrichtung.

An embodiment of the present invention will now be described by way of example with reference to the figures. Show it:

Fig. 1:

A sectional view of an embodiment of the device according to the invention in a Radialblickrichtung; and

Fig. 2:

A sectional view of the same embodiment of the device according to the invention in Axialblickrichtung.

Fig. 1 shows the sectional view of an embodiment of the device according to the invention in a Radialblickrichtung. It is a cutting and embossing roller assembly for simultaneous cutting and embossing of cardboard. In the context of the present invention, however, a pure cutting roller arrangement or a pure embossing roll arrangement is also conceivable.

As shown in Fig. 1, a cutting and embossing roll 2 - hereinafter referred to as a cutting roller 2 for simplicity - rotatably supported by means of two bearings 8 in a frame 1. The bearings 8 are preferably standard rolling bearings. The cutting roller 2 carries on its lateral surface two cutting blades 4 and embossing pins 25 for cutting and embossing cardboard, are made from the Faltschachtelzuschnitte. The geometry of the cutting blade 4 and the embossing pins 25 is designed depending on the application and cutting or embossing task. In the embodiment shown, the cardboard is cut in a straight line and embossed at the same time.

In Fig. 1 below the cutting roller 2, a counter-roller 3 is mounted with bearings in a substantially smooth circumferential surface rotatably. It is also conceivable, however, a non-smooth lateral surface of the counter-roller 3, for example, if it is formed in an embossing roll arrangement as a die roller with recesses for receiving embossing pins. The bearings 22 are preferably roller bearings. In the present case, the distance between the cutting edges of the cutting blade 4 and the lateral surface of the counter-roller 3 is referred to as gap width S, depending on Thickness and type of material to be cut in later described manner is adjustable. The distance of the radially outer ends of the embossing pins 25 from the lateral surface of the counter roll 3 may differ from the gap width S.

The drive of the device according to the invention is carried out by means of a motor 11, which is arranged in Fig. 1 at the left end of the cutting roller 2. The motor 11 causes the cutting roller 2 in rotation, wherein the rotational movement is transmitted by means of a drive gear 7 to the counter-roller 3. As can be seen in Fig. 1, the drive gear 7 is rotatably connected to the motor 11 opposite end of the cutting roller 2 with this. It meshes with an equally large gear 10 which is rotatably connected to the counter-roller 3, so that the rotational movement of the cutting roller 2 is transmitted to the counter-roller 3 with a transmission ratio of 1: 1. Only the direction of rotation of the counter roll 3 is opposite to that of the cutting roller. 2

The cutting roller 2 has, in the embodiment shown, two closed circumferential surfaces 5, which serve as running surfaces for two rotatably mounted pressure rollers 6. The peripheral surfaces 5 may be raised or set back from the adjacent lateral surfaces of the cutting roller 2 or terminate flush with the adjacent lateral surfaces. The pressure rollers 6 form part of a Kraftbeaufschlagungseinrichtung, by means of which the cutting roller 2 is acted upon by a radially acting pressure force F (see FIG. 2).

As shown in Fig. 2, each of the two pressure rollers 6 is rotatably mounted on a pivot lever 19, which in turn is rotatably mounted about a pivot axis 18 on the frame 1. In Fig. 2 engages the pivot axis 18 opposite the end of the pivot lever 19, for example, a hydraulically actuated force transmission member 12 and pushes it down, so that the pressure rollers 6 exert the pressure force F shown in Fig. 2 on the cutting roller 2. In this case, the point at which the pressure roller 6 engages the peripheral surface 5 is offset relative to the longitudinal axis 20 of the cutting roller 2 in Fig. 2 to the left. Even in the event that the longitudinal axis 20 of the cutting roller 2 would lie exactly vertically above the longitudinal axis 21 of the counter-roller 3, the horizontal component F _{H of} the pressure force F causes a relatively stable equilibrium position of the cutting roller 2 relative to the counter-roller 3.

However, as shown in Fig. 2, the longitudinal axis 20 of the cutting roller 2 is offset relative to the longitudinal axis 21 of the backing roll 3 by the horizontal offset a to the right in the embodiment shown. Thus, in the embodiment shown, owing to the horizontal force component F _H and the horizontal offset a, it is reliably avoided that the cutting roller 2 and the counter-roller 3, due to an unstable equilibrium position, perform undesired vibrations relative to each other. The force exerted by the two pressure rollers 6 on the cutting roller 2 pressure force F is inventively by each subsection of the cutting roller 2, which is located between the peripheral surface 5 and the bearing 8, completely derived in the frame 1 held in the bearing 8. In this case, the cutting roller 2 is pressed by the distance of the existing bearing clearance in the effective direction of the pressing force F to be recognized in FIG.

In Fig. 1, three bending lines 13, 14 and 15 of the cutting roller 2 are located. In this case, the course of the longitudinal axis 20 denotes the zero level of the deflection. The bending line 14 results from the cutting and embossing force acting on the cutting roller 2 substantially vertically upward during the cutting and embossing process, depending on the size of the horizontal offset a. The bending line 15 results from the sum of the self-weight force of the cutting roller 2 and the vertical component F _{V of} the pressing force F. The bending line 13 is the sum bending line resulting from an addition of the bending lines 14 and 15.

In FIG. 1, further bending lines 16 and 17 of the counter-roller 3 are shown. Here, the longitudinal axis 21 represents the zero level of the deflection. The bending line 17 results from the self-weight force of the counter roll 3. The bending line 16 represents the resulting from the sum of dead weight and cutting and embossing force deflection.

In the axial section of the cutting roller 2 located between the two circumferential surfaces 5, the bending line 13 of the cutting roller 2 substantially corresponds to the bending line 16 of the counter-roller 3 when the pressing force F is suitably selected. As a result, cutting roller 2 and counter-roller 3 at least in this Axial section bent in the same way and have in this axial section on an axially substantially equal gap width.

The pressure force F applied by the pressure rollers 6 to the cutting roller 2 in no way acts directly on the counter-roller 3, so that the bending line 16 shown in FIG. 1 is subject to substantially less quality than the bending lines of the counter-rollers in devices known from the prior art, which make contact between the cutting roller and the counter roller by means of bearer rings. Due to the relatively low deflection of the counter-roller 3, an equally wide gap is achieved over the relevant axial section of the rollers 2, 3, while at the same time having a comparatively small absolute size of the deflection.

According to the present invention, since there is no contact whatsoever between the cutting roller 2 and the counter roller 3 beyond the material to be cut, no further upwardly directed force acts on the cutting roller 2 except for the cutting and embossing force. In the embodiment shown, the bending line 13 in FIG. 1 hangs still down through. In this way, the occurring cutting and embossing force does not raise the cutting roller 2 from its bias caused by the pressing force F, whereby the cutting edges of the cutting blade 4 and the embossing pins 25 move in the radial direction of the optionally existing game of the bearing 8 could. The preferred storage of the cutting roller 2 in play afflicted standard bearings is thus possible without the risk of poor cutting and embossing results.

The adjustment of the gap width S of the gap takes place with the aid of a gap adjusting device acting between the bearings 8 and 22 of the cutting roller 2 or counter roller 3, which in the embodiment shown is in the form of two adjustable wedges 9. The wedges 9 can be moved, for example, by means of a handwheel, not shown in Fig. 2 to the left or right and are each between two jewels 23 and 24, which are mounted in the frame 1 movably movable in the vertical direction. The jewel 23 each receives the bearing 8 while the jewel 24 each receives the bearing 22. Like on best seen in Fig. 1, the derived in the bearing 8 pressure force F is transferred to the wedges 9 via the jewels 23, so that the wedges 9 when moving in Fig. 2 to the left the cutting roller 2 indirectly on the jewels 23 and the Lift bearing 8 against the derived pressure force F. The counter-roller 3 associated bearing blocks 24 do not move in the adjustment of the gap width S.

When adjusting the gap width S of the gap naturally changes the distance between the longitudinal axes 20 and 21 from each other, so that change the engagement conditions between the drive gear 7 and the driven gear 10. In particular, a backlash may result because the individual tooth flanks no longer abut each other in the same way as before the change of the gap width S. Such backlash can undesirably affect the quality of the cutting and embossing result after changing the gap width S.

To compensate for this disadvantageous backlash is inventively preferably provided to form the drive gear 7 as a gear which is divided in a plane substantially perpendicular to the longitudinal axis 20 of the cutting roller 2 and accordingly has a first part gear 7a and a second part gear 7b. The two partial gears 7a, 7b are rotatable relative to each other, so that at least one of the two partial gears 7a, b can be brought into such a rotational position and fixed there, in which mesh his teeth without backlash with the driven gear 10 of the backing roll 3. The partial gears 7a, 7b are both rotationally fixed to the cutting roller 2 can be fixed. Alternatively, it is conceivable to fix only one of the two partial gears 7a, 7b on the cutting roller 2 and to make the non-fixable on the cutting roller 2 part gear on the other part gear fixed. The split drive gear 7 allows in this way a relatively easy to handle compensation of any existing backlash. Alternatively, the driven gear 10 may be divided in a similar manner instead of the drive gear 7.

As is apparent from the above description, the following advantageous effect is achieved in particular with the present invention:

The gap between the cutting and / or embossing roll and the counter roll can be formed at least in the relevant for the cutting and / or embossing process axial portion of the rolls with uniformly large gap width.

LIST OF REFERENCE NUMBERS

1

frame

2

cutting roller

3

backing roll

4

cutter

5

peripheral surface

6

pressure roller

7

drive gear

7a, 7b

Part gears

8th

camp

9

wedge

10

gear

11

engine

12

A transmission element

13

Bending line of the cutting roller (sum of bending lines 14, 15)

14

Bend line of the cutting roller (cutting force)

15

Bending line of the cutting roller (own weight + vertical component F _V )

16

Bending line of the counter roll (dead weight + cutting force)

17

Bending line of the counter roll (dead weight)

18

swivel axis

19

pivoting lever

20

Longitudinal axis of the cutting roller

21

Longitudinal axis of the counter roll

22

camp

23

Lagerstein

24

Lagerstein

25

embossing tool

a

Horizontal offset

F

thrust

S

gap width

F _H

Horizontal component of compressive force F

F _V

Vertical component of compressive force F

Claims (8)

Apparatus for cutting and / or embossing a sheet, a blank or a material web, comprising a cutting and / or embossing roll (2) having a longitudinal axis (20) which is rotatably mounted at both ends in at least one bearing (8) , a rotatably supported counter roll (3) cooperating with the cutting and / or embossing roller (2), and a force applying means (6, 12) for urging a peripheral surface (5) of the cutting and / or embossing roll (2) with a pressing force (F )
characterized in that
the pressure force (F) applied by the force application device (6, 12) to the peripheral surface (5) is discharged via at least part of the cutting and / or embossing roller (2) into the at least one bearing (8) in such a way that there is no application the counter roll (3) by the pressure force (F). Device according to claim 1,
characterized in that
a gap adjusting device (9) for adjusting the gap width (S) of a gap between the cutting and / or embossing roller (2) and the counter-roller (3) is provided, wherein the derived pressure force acts on the gap adjusting device (9). Device according to claim 2,
characterized in that
the gap adjusting device comprises at least one adjustable wedge (9). Device according to one of the preceding claims,
characterized in that
the force-applying device comprises at least one pivoting lever (19) pivotally mounted about a pivot axis (18), on which at least one pivot lever (19) is mounted with the peripheral surface (5) cooperating pressure roller (6) is mounted at a distance from the pivot axis (18). Device according to claim 4,
characterized in that
the pressure roller (6) acts on the circumferential surface (5) at a position which is offset horizontally from the longitudinal axis (20) of the cutting and / or embossing roller (2). Device according to one of the preceding claims,
characterized in that
the counter roll (3) has a longitudinal axis (21) which is offset by a horizontal offset (a) relative to the longitudinal axis (20) of the cutting and / or embossing roll (2). Device according to one of the preceding claims,
characterized in that
on the cutting and / or embossing roll (2) a drive gear (7) is arranged, which engages in a driven by him gear (10) of the counter roll (3), wherein the drive gear (7) or the driven gear (10) a a split gear comprising a first part gear (7a) and a second part gear (7b) and the two part gears (7a, 7b) for compensating a backlash between the drive gear (7) and the driven gear (10) are rotatable relative to each other. Device according to one of the preceding claims,
characterized in that
a further Kraftbeaufschlagungseinrichtung is provided which acts on the counter-roller (3) with a counter force which acts in a direction of the pressure force (F) substantially opposite direction.

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