EP1925408B1 - Dispositif de poinçonnage et cylindre de contre-poinçonnage pour un dispositif de poinçonnage - Google Patents

Dispositif de poinçonnage et cylindre de contre-poinçonnage pour un dispositif de poinçonnage Download PDF

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Publication number
EP1925408B1
EP1925408B1 EP07022837A EP07022837A EP1925408B1 EP 1925408 B1 EP1925408 B1 EP 1925408B1 EP 07022837 A EP07022837 A EP 07022837A EP 07022837 A EP07022837 A EP 07022837A EP 1925408 B1 EP1925408 B1 EP 1925408B1
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EP
European Patent Office
Prior art keywords
shaft
cylinder
punching
eccentric
counter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07022837A
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German (de)
English (en)
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EP1925408A1 (fr
Inventor
Alfons Linnemann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
wink Stanzwerkzeuge GmbH and Co KG
Original Assignee
wink Stanzwerkzeuge GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE202007007617U external-priority patent/DE202007007617U1/de
Application filed by wink Stanzwerkzeuge GmbH and Co KG filed Critical wink Stanzwerkzeuge GmbH and Co KG
Publication of EP1925408A1 publication Critical patent/EP1925408A1/fr
Application granted granted Critical
Publication of EP1925408B1 publication Critical patent/EP1925408B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D7/26—Means for mounting or adjusting the cutting member; Means for adjusting the stroke of the cutting member
    • B26D7/2628—Means for adjusting the position of the cutting member
    • B26D7/265—Journals, bearings or supports for positioning rollers or cylinders relatively to each other

Definitions

  • the invention relates to a device for punching and a device for a device for punching, in particular a counter-punching cylinder.
  • labels or the like are punched out of a passing between a punching cylinder and a counter-punching cylinder or impression cylinder web in the so-called cutting application or cut in the so-called stamping application.
  • the label falls out of the material web after the cut, while in the so-called stamping application only the label material and, if necessary, the adhesive are severed, leaving the carrier material at least substantially intact, so that the stamped labels are printed on a e.g. rolled-up web can remain.
  • the cutting depth of the cutters must be maintained fairly accurately to avoid too much or too little incision depth. As the blades blunt in the course of operation, the cutting depth is reduced over time.
  • a renewal or rework of the cutting is complex, so that in the prior art punching devices have become known in which the cutting gap between the punching cylinder and the counter-punching cylinder is adjustable so that with decreasing cutting depth, the cutting gap can be adapted to the changed conditions.
  • a device for punching with a rotatable about a rotation axis punching cylinder and a about a rotation axis of the punching cylinder parallel rotation axis rotatable impression cylinder in which the size of the gap between the punching cylinder and the impression cylinder is adjustable.
  • the punching cylinder and the impression cylinder are each equipped with bearer rings, which are made of hardened steel and run on each other. The bearer rings project respectively radially outward beyond the outer surface of the cylinder body, so that the cutting gap results in the area of the cylinder body of the punching cylinder and the impression cylinder.
  • the position of the axis of rotation of the bearer rings of the impression cylinder is provided via an eccentric intermediate ring adjustable.
  • the bearing of the axis of rotation can be changed and the gap can be increased or decreased.
  • a disadvantage of the DE 197 36 762 C2 known system is, however, that changes not only the position of the axis of rotation of the impression cylinder by an angular adjustment of the intermediate ring, but that the position of the axis of rotation of the punching cylinder must be changed accordingly, since the Punch cylinder rests on the bearer rings of the counter-pressure cylinder via its bearer rings.
  • Another disadvantage of this known device is that a retrofitting of existing systems is practically possible only by a complete replacement of the entire punching device.
  • Another punching device has become known, which has a rotatably mounted punching cylinder and a rotatably mounted impression cylinder, between which a material web is feasible.
  • the axis of the impression cylinder is fixed and arranged on the upper side of the fixed shaft oblique surfaces on which an adjustment of a bearing of the impression cylinder is adjustably arranged, so achieved by an axial adjustment of the bearing and a height adjustment of the axis of rotation of the impression cylinder becomes.
  • a disadvantage of this known system is the complicated structure of many items. Another disadvantage is that a fixed shaft is needed to ensure the adjustability of the cutting gap. This leads to that in existing plants, where the drive over the wave of the Counter-pressure cylinder is done, retrofitting is not possible or only with great effort.
  • a punching device with a rotatably mounted punching cylinder and a rotatably mounted on a fixed shaft impression cylinder, in which the distance between the punching cylinder and the impression cylinder is also adjustable.
  • the fixed axis is provided with an eccentric portion on which the impression cylinder is rotatably mounted.
  • the object of the present invention to provide a device for punching and a device for a device for punching available in which a gap width easy to adjust and where a retrofitting of existing facilities is possible.
  • the device according to the invention for a device for punching comprises according to claim 1, a counter-punching cylinder comprising a shaft and a rotatably received around the shaft around the cylinder body, and at least one bearer ring.
  • the shaft is rotatable about an axis of rotation and the cylinder body is mounted on at least one eccentric on the shaft to adjust a gap width. Due to this arrangement, the position of the shaft remains unchanged when adjusting the gap width.
  • the inventive device for punching and / or embossing a material web comprises a rotatably received punching cylinder and a rotatably received counter punch cylinder, wherein the counter punch cylinder comprises a shaft and a rotatably received around it cylinder body, and at least one bearer ring. Between the punching cylinder and the cylinder body of the counter-punching cylinder to be punched and / or to be embossed material web is feasible.
  • the shaft of the counter-punching cylinder is designed to be rotatable about an axis of rotation and rotates during operation.
  • the cylinder body according to the invention is mounted on the shaft via at least one eccentric to set a gap width between the punching cylinder and the counter-punching cylinder or the impression cylinder, wherein when adjusting the gap width, the position of the shaft remains unchanged.
  • the invention has many advantages.
  • the inventive device is particularly suitable for retrofitting existing systems that do not have an adjustable gap.
  • both devices can be retrofitted, which have a rotatable shaft as well as a fixed shaft, so that flexible retrofitting of existing systems is possible.
  • the device according to the invention is particularly simple in construction and ensures reliable operation.
  • a significant advantage of the invention is that the important for installation radial distance from the outer circumference of the bearer rings to the position of the shaft remains the same.
  • the required stability can be ensured both when using magnetic and full cylinders, since vibrations are reliably avoided.
  • the maximum radial distance of the surface of the cylinder body from the axis of rotation of the shaft and thus the gap width is adjusted.
  • the minimum distance of the outer contours of the cylinder body is adjusted by the outer contour of the bearer ring.
  • the cutting depth can be adapted to different material thicknesses or also to the wear of the tool.
  • the position of the shaft remains unchanged even when adjusting the gap width.
  • the pickup points in the device remain fixed.
  • a bearing clearance or the like is not required, e.g. compensate for radial length shifts.
  • the precision can be increased.
  • the shaft of the counter-punching cylinder is formed substantially rotationally symmetrical to the axis of rotation.
  • the shaft is rotationally symmetrical over the entire engagement length or at all portions which are in engagement with other components, and particularly preferably the shaft as a whole is rotationally symmetrical formed to the rotation axis to avoid vibrations during rotation of the shaft.
  • At least one bearer ring and preferably both bearer rings are non-rotatably connected to the shaft, since in a co-rotating shaft bearings between the shaft and the bearer rings are not required.
  • a separate bearing between the shaft and the bearer rings may be provided.
  • At least one outer contour of at least one bearer ring is formed rotationally symmetrical to the axis of rotation of the shaft.
  • At least one bearer ring is secured in an axial direction by at least one circlip.
  • the cylinder body is mounted via at least one bearing relative to the at least one eccentric device.
  • one or more needle bearings are used for storage, since they have a particularly low radial clearance.
  • the eccentric rotatably mounted on at least one bearing relative to the shaft, being used as a bearing needle roller bearings in particular.
  • the eccentric is rotatably supported via a needle bearing relative to the rotatably designed shaft and the cylinder body is rotatably supported via a further needle bearing relative to the eccentric so that in punching operation, the shaft and the cylinder body rotate while the eccentric remains stationary and angularly only is adjusted to adjust the gap width.
  • Such a configuration allows a particularly compact design of the counter-punching cylinder, so that an exchange in existing systems is possible, which do not have an adjustable gap width so far.
  • the eccentric device comprises at least one eccentric ring or is designed as an eccentric ring which has a central bore or a central hole in order to provide a ring eccentrically to the bore.
  • the circular eccentric ring has a slightly offset hole from the center.
  • the eccentricity of the hole or the bore of the ring is preferably in the range of less than 1 mm, in particular in the range of up to 50 or 100 micrometers, preferably about 30 micrometers.
  • the eccentric device is rotatably connected to a gear, which is connected in particular via one or more further gears and one or more shafts with a dial to adjust the angular position of the eccentric and thus the gap width.
  • a gear which is connected in particular via one or more further gears and one or more shafts with a dial to adjust the angular position of the eccentric and thus the gap width.
  • the angular adjustment of the eccentric and / or the dial is fixable. This can be done by locking cams or by other known in the art locking devices.
  • two eccentric devices are preferably provided, one of which is provided in each case in one area at the opposite ends of the counter-punching cylinder.
  • both eccentric rings are adjusted synchronously by turning the dial to achieve a uniform adjustment of the gap.
  • the thumb wheel is connected to a display unit to indicate a measure of the gap width.
  • the counter-punch cylinder is recorded on recordings.
  • two radially protruding bearer rings are provided and a distance between the axes of rotation of the bearer rings and of the cylinder body can be adjusted by means of an adjusting device accommodated on at least one receptacle in order to adjust the gap width during punching.
  • At least one adjusting shaft and in particular two adjusting shafts are provided for adjusting the gap width.
  • the adjusting shafts are in particular rotatably received in at least one receptacle and in particular in the vicinity of the two ends of the cylinder body in each case in a receptacle.
  • the adjusting shafts extend in particular on the two sides approximately parallel to the cylinder body.
  • each receptacle is designed as a sliding block.
  • the shaft is advantageously received in the receptacle or the sliding block.
  • the shaft can be mounted in the receptacle via at least one ball bearing.
  • the adjustment shaft is adjustable in length.
  • At least one axial needle bearing is provided between a bearer ring and an eccentric device.
  • At least one driver for the rotationally fixed connection of the cylinder body and shaft is provided.
  • the driver is designed in particular as a flexible ring and in particular as at least one O-ring.
  • the driver or flexible ring is preferably pressed by a fixed to the cylinder body or on the shaft pulley or sleeve to the shaft or the cylinder body.
  • At least one disengaging button or two disengaging buttons are provided with which an interruption of the transmission of the movement of the adjusting wheel on one or both eccentric rings is possible. This will be a Side-by-side adjustment of the gap width possible, which leads to an even more flexible use of the device according to the invention and the device according to the invention.
  • a display device which displays a measure of the set gap width.
  • each display button still separate display units are arranged, which informs about the extent of page-by-page setting, so that the user can always inform themselves about the current settings and optionally also set the zero point or the original state again.
  • the rotational connection between the locking shaft of the disengaging button and the button itself is interrupted by pressing a disengaging button, so that the adjustment on the central dial only affects the other setting shaft.
  • at least one disengaging button is connected to a display unit to indicate at least one measure of the side-by-side gap width.
  • a limitation of the individual setting per side is limited to one revolution of the latching shaft.
  • the current setting can then be displayed on the latching shaft and the detent button via aligned markings at the zero point. If the gap width has been adjusted on one side, the markings of detent shaft and detent button are no longer aligned and the extent can be read off via the angle adjustment.
  • the eccentric can be connected, for example, with a cable or the like to make a remote adjustment.
  • the eccentric can also be provided with a remotely controllable motor, so that a remote-controlled adjustment is possible.
  • the motor can be performed pneumatically, hydraulically, magnetically and in particular electrically.
  • sensors can be provided which detect the angular position of the eccentric devices and / or the gap width and pass it on to a central control device which determines the current setting values, e.g. on a display or the like outputs and / or via a network connection or the like.
  • FIG. 1 - 4 an embodiment of the device 100 according to the invention, comprising a device 1 according to the invention, is shown.
  • Fig. 1 only schematically and greatly schematically illustrated device 100 is used for stamping or punching, in particular of labels and the like and comprises a frame or housing 40 in which the punching cylinder 3 and the counter-punching cylinder 2 are rotatably received respectively about their shafts 36 and 4 respectively ,
  • the punching cylinder 3 has a cylinder body 35 and the counter-punching cylinder 2 comprises a cylinder body 5.
  • the stamping process requires a high degree of accuracy, although oscillations in the micrometer range are undesirable. Therefore, by means of adjusting wheels 30, which act on pressure liners 31, a biasing force is applied to the hardened steel bearing rings 34 of the punching cylinder 3.
  • biasing force ensures that the set conditions are maintained during operation even when larger forces.
  • FIG. 2 is an external perspective view of the device 1 according to the invention shown, comprising the counter-punching cylinder 2.
  • the counter-punching cylinder 2 has a rotatable and co-rotating in operation shaft 4, which is rotatably received about an axis of rotation 7 in bearings 20 on sliding blocks or receptacles 18 and 19.
  • the sliding blocks or receptacles 18 and 19 are received on the frame 40 and support the counter-punching cylinder 2 and its adjusting shafts 16, so that the counter-punching cylinder 2 with the adjusting shafts and the sliding blocks a compact and exchangeable device 1, which can be exchanged for conventional devices 1, to allow adjustability of the gap width.
  • a rotatably arranged cylinder body 5 is provided, which is rotatably supported in each case via a needle bearing 10 on two eccentric rings 12 of an eccentric 8.
  • the eccentric rings 12 are in turn rotatably supported by needle bearings 11 on the shaft 4.
  • a drive wheel 44 is rotatably attached to the shaft 4, via which the shaft 4 is driven with the bearer rings 6.
  • the drive shaft 4 is mounted in the sliding block or the receptacle 18, which has an enlarged mounting portion 45 for supporting the receiving shafts 16 in the lower area to form a compact device with the components as a whole.
  • the shaft 4 is formed as a whole rotationally symmetrical to the axis of rotation 7.
  • the eccentric 12 of the eccentric 8 have a round outer cross-section, in which eccentrically to a bore is provided so that the axis of symmetry of the outer contour is spaced from the axis of symmetry of the bore.
  • the distance between the two axes is small and is in the embodiment between about 20 and 70 microns, so that there is an adjustability of the gap width of up to about 40 or 140 micrometers.
  • the eccentric ring 12 can remain stationary during operation, while the cylinder body 5 and the shaft 4 rotate. In this way it is achieved that the eccentric position of the axis of rotation of the cylinder body 5 is maintained to the axis of rotation 7 of the shaft 4.
  • the bearer rings 6 are rotatably received.
  • a bearing of the bearer rings 6, which have a hardened surface 6a, is not required with respect to the shaft 4, since the shaft 4 is designed to rotate.
  • axial needle bearings 51 may be provided in the annular grooves 43, which serve for the axial support and support of the cylinder body 5, to prevent friction heat and heavy wear during operation when axial forces occur.
  • O-rings 41 are also provided, which are pressed axially from the outside against radial and / or axial regions of the shaft 4 by clamping sleeves 42.
  • the clamping sleeves 42 are attached to the outer cylinder body 5, so that upon rotation of the shaft 4, the rotational movement is transmitted to the O-rings 41, which transmit the rotational movement of the here outer cylinder body 5 due to the friction occurring. Without such a friction transmission, it could happen that when passing through the punching tracks, the outer cylinder 5 does not rotate when the frictional forces occurring between the web to be punched and the cylinder body 5 are insufficient to enable the cylinder 5 to rotate.
  • the O-ring 41 is subjected to a periodic compression, which is caused by the slightly different positions of the axes of rotation of the cylinder body 5 and the central shaft 4. Since in the embodiment, the material of the O-ring has a thickness of about 4 mm and since the eccentricity of the two axes is only in the range of about 100 microns, the O-ring is exposed to only low loads and is not even warm in operation.
  • Gears 13 and 14 are rotatably connected to the eccentric 12.
  • the gears 13 and 14 are in engagement with gears 25, 27 and 28 which are arranged on adjustment shafts or shafts 16 to cause rotation of the shaft 16, a rotation of the gears 13 and 14 and thus the eccentric 12.
  • the gears 13 and 14 are each arranged between the bearer rings 6 and the cylinder body 5.
  • the shafts 16 are connected via gears 23, 25 and 26, 27 with a shaft 21 in a rotationally fixed connection, on which a sleeve 22 and the adjusting wheel 15 are arranged and on which the gear 49 is provided.
  • a special feature are the two symmetrically arranged Ausrastknexcellent 17, by their pressures in each case the rotational connection between the adjustment knob 15 and one of the gears 13 and 14 can be interrupted to allow a page-wise adjustment of the gap width.
  • the present invention has a particularly compact design, wherein the outer contour of the counter-punching cylinder 2 does not differ in principle from the outer contours of conventional counter-punching cylinders, in which no adjustability of the gap width or the depth of engagement of the punching tools is given. Due to the compact dimensions of the counter-punching cylinder 2 is particularly flexible and especially suitable for retrofitting existing systems.
  • the Fig. 5 shows a further embodiment of the device 1 according to the invention.
  • the counter-punching cylinder 2 in turn has a rotatable shaft 4 which rotates during operation and which is rotatably received around a rotation axis 7 in bearings 20 on the receptacles or sliding blocks 18 and 19.
  • the bearings 20 are provided here as a ball bearing or angular contact ball bearings and not as a needle bearing in order to absorb and divert axial forces can.
  • ball bearings as bearing 20 is that when removing the device 1 from a punching device 100 no separate protection against slipping of the components is required because ball bearings can also absorb axial forces. Otherwise, a separate fuse carrier can be used, which can for example also serve to transport the counter-punch cylinder with a crane.
  • shafts or adjusting shafts 16 are provided on both sides of the cylinder body 5 .
  • shafts or adjusting shafts 16 are provided on the front side of an adjustment shaft 16a and arranged on the rear side of a setting shaft 16b, on the rotation of the gap width can be adjusted during punching.
  • the adjusting shafts 16 and 16a and 16b are rotatably received or supported in the sliding blocks 18 and 19.
  • the adjusting shaft 16a is used for adjusting the gap width at the end adjacent to the adjusting knob 15, while the adjusting shaft 16b for adjusting the gap width is provided at the opposite end of the cylinder body 5.
  • the sliding block or the receptacle 19 is provided, while at the other end of the sliding block or the receptacle 18 is arranged.
  • the sliding blocks 18 and 19 carry the entire assembly and take the central shaft 4, and the adjusting shafts 16a and 16b.
  • the device 1 according to the invention can be exchanged for a conventional device and allows the setting of the gap width without further modification of the punching device.
  • the position of the shaft of the counter-punching cylinder does not change even when changing the gap width 9.
  • the installation dimension remains the same. An additional bearing load does not occur.
  • the device according to the invention is optionally suitable for top and bottom punching.
  • the integration of the adjustment and the arrangement of the adjustment for adjusting the gap in the sliding blocks 18 and 19 allows flexible adjustment of the gap when punching. Subsequent processing of the housing 40 is eliminated.
  • the sliding block comprises the parts 18a and 18b, which are separated by a clamping gap 18c.
  • the sliding block can also be designed as a one-piece slotted part, which also axially clamps the bearing 20 with clamping screws.
  • the adjusting mechanism 50 for adjusting the gap dimension is arranged axially outside the sliding blocks 18 and 19 and comprises disengaging buttons 17, which allows a separate adjustment of the two adjusting shafts 16.
  • Fig. 7 is a front view of the device 1 is shown.
  • the front sliding block 19 with the receptacles for the adjusting shafts 16a and 16b can be seen.
  • Two disengaging buttons 17 are provided, namely a disengaging button 17a for the according to in the illustration Fig. 7 right adjusting shaft 16a and a disengaging button 17b for interrupting transmission to the left adjusting shaft 16b.
  • a display 52 on the adjustment mechanism 50 is used to read the currently set gap.
  • 17 a and 17 b marks or pointers 171 a, 172 a, and 171 b and 172 b are additionally provided so that the operator can see at a glance, which total gap was set and to what extent the settings of the two adjustment shafts 16 a and 16 b of the basic common attitude differs.
  • the adjusting device 55 comprises at least the adjusting shafts 16a and 16b and the adjusting wheel 15 and in particular also the adjusting mechanism 50, which may have a plurality of gears, etc.
  • the disengaging buttons 17 are part of the adjustment device 55.
  • the adjustment mechanism 50 is designed in such a way that an adjustment range of e.g. 100 or 140 microns results.
  • the rotational movement on the in Fig. 8 detectable gear 60 transmitted directly.
  • the gear 60 transmits the rotational movement to the gear 59, which in turn engages in the internal teeth 59 of the adjustment mechanism 50.
  • the internal teeth 59 in turn transmits the rotational movement to the at a different radial point and here symmetrically to the perpendicular bisected gears 57 and 58, which in turn transmit the rotational movement via the gears 23-27 on the adjustment shafts 16a and 16b, if they are not by pressing the release buttons 17 are disengaged.
  • the different adjustability of the front and rear or right and left gap size is preferably limited to a certain portion of the total adjustable range, so as not to confuse the operator with too large Einstellvariationen. If, in fact, the cutting edges on one side of the punching cylinder have worn very heavily, as a rule the punching profile as a whole is no longer in the proper condition and should therefore be exchanged.
  • the page-wise adjustability is limited to about one revolution of the disengaging buttons 17, in which an axial spring protrudes on the locking shaft in an annular groove of the knob.
  • a radial driver is arranged so that at the latest upon rotation of the knob by 360 degrees, the driver abuts the axial spring of the shaft and this entrains in a further rotation.
  • Fig. 9 the adjusting shaft 16a is shown.
  • the gears 23 and 25 can be seen on the left edge, which transmit the rotational movement of the adjustment mechanism 50 on the shaft 16a and the gear 25 on the left eccentric ring 12.
  • a length adjusting unit 60 comprising a spring 61 is provided at the right end.
  • the device 1 can also be used in installations of slightly different dimensions without the need for costly shortening of one or both adjusting shafts 16a and 16b.
  • the sliding blocks are in particular made of steel or another metal, such as e.g. Aluminum, however, can also consist of other materials.

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Details Of Cutting Devices (AREA)

Claims (10)

  1. Cylindre de contre-poinçonnage (2) pour un dispositif (100) de poinçonnage comprenant un arbre (4) et un corps cylindrique (5) pivotant autour de l'arbre (4) ainsi qu'au moins une bague de cylindre (6), tandis que l'arbre (4) est conçu pour pivoter autour d'un axe de rotation (7) et que le corps cylindrique (5) est placé sur l'arbre (4) de telle sorte à pivoter par le biais d'au moins un dispositif d'excentrique (8) pour régler une largeur de fente (9) lors du poinçonnage et/ou du gaufrage de bandes de matériau, tandis que le corps cylindrique (5) peut pivoter par le biais d'au moins un roulement par rapport au moins à ce dispositif d'excentrique (8), caractérisé en ce que le dispositif d'excentrique (8) est placé en face de l'arbre rotatif (4) par le biais d'au moins un roulement, la position de l'arbre rotatif (4) restant inchangée lors du réglage de la largeur de fente (9).
  2. Dispositif (1) selon la revendication 1, l'arbre (4) étant essentiellement conçu de telle sorte à pivoter symétriquement par rapport à l'axe de rotation (7).
  3. Dispositif (1) selon la revendication 1 ou 2, au moins une bague de cylindre (6) étant fixée à l'arbre (4) de façon rigide.
  4. Dispositif (1) selon la revendication précédente, au moins un contour extérieur d'au moins une bague de cylindre (6) étant conçu pour pivoter symétriquement par rapport à l'axe de rotation (7).
  5. Dispositif (1) selon l'une quelconque des revendications précédentes, au moins un roulement étant un roulement à aiguilles.
  6. Dispositif (1) selon l'une quelconque des revendications précédentes, le dispositif d'excentrique (8) comprenant au moins une bague excentrique (12).
  7. Dispositif (1) selon l'une quelconque des revendications précédentes, le dispositif d'excentrique (8) étant fixé de façon rigide à une roue d'engrenage (13, 14).
  8. Dispositif (1) selon l'une quelconque des revendications précédentes, le dispositif d'excentrique (8) étant fixé à une molette de réglage (15).
  9. Dispositif (1) selon l'une quelconque des revendications précédentes, pourvu d'au moins un poussoir de débrayage (17) permettant de régler latéralement la largeur de fente (9) .
  10. Dispositif (100) de poinçonnage et/ou de gaufrage d'une bande de matériau, muni d'un cylindre de poinçonnage (3) rotatif et d'un cylindre de contre-poinçonnage (2) rotatif selon l'une quelconque des revendications précédentes.
EP07022837A 2006-11-27 2007-11-26 Dispositif de poinçonnage et cylindre de contre-poinçonnage pour un dispositif de poinçonnage Not-in-force EP1925408B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006056184 2006-11-27
DE202007007617U DE202007007617U1 (de) 2006-11-27 2007-05-26 Stanzvorrichtung und Gegenstanzzylinder für eine Stanzvorrichtung

Publications (2)

Publication Number Publication Date
EP1925408A1 EP1925408A1 (fr) 2008-05-28
EP1925408B1 true EP1925408B1 (fr) 2010-05-19

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EP07022837A Not-in-force EP1925408B1 (fr) 2006-11-27 2007-11-26 Dispositif de poinçonnage et cylindre de contre-poinçonnage pour un dispositif de poinçonnage

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8821149B2 (en) 2011-05-05 2014-09-02 Kimberly-Clark Worldwide, Inc. Web treatment apparatus having center bearer ring

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009003719A1 (de) 2009-04-01 2010-10-14 Ostedruck Bernhard-J. Borgardt Gmbh & Co. Kg Verfahren zur Stichstanzung, Materialbahn sowie Verwendung dafür
DE102013208909A1 (de) * 2013-05-14 2014-11-20 Kocher + Beck Gmbh + Co. Rotationsstanztechnik Kg Verfahren und Vorrichtung zum Stanzen
ITUB20153958A1 (it) * 2015-09-28 2017-03-28 Cartes S R L Apparato e metodo per lavorare un materiale in nastro.
DE102017122071A1 (de) * 2017-09-22 2019-03-28 Wink Stanzwerkzeuge Gmbh & Co. Kg Verstelleinrichtung und Verfahren zum Einstellen eines Spaltmaßes einer Rotationsstanzvorrichtung

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4130042A (en) * 1977-07-25 1978-12-19 Avery International Corporation Adjustable anvil roll for die-cutting labels
US5083488A (en) * 1991-04-12 1992-01-28 Melvin Stanley Radially adjustable anvil roll assembly for a rotary die cutting press
DE19736762C2 (de) 1997-08-23 2000-05-25 Kocher & Beck Gmbh & Co Rotati Vorrichtung zum Stanzen, insbesondere von Etiketten
DE10305032B3 (de) 2003-02-07 2004-06-24 Spilker Gmbh Stanzvorrichtung
DE102004032030A1 (de) 2004-07-02 2006-01-19 Spilker Gmbh Vorrichtung zum Stanzen und/oder Prägen von Materialbahnen
DE102004054868B4 (de) 2004-11-12 2007-05-16 Spilker Gmbh Stanzvorrichtung
DE102005054766A1 (de) * 2005-11-17 2007-05-31 Gs-Engineering Gmbh Druck- und Prägewerk und Arbeitszylinder und Gegendruckzylinder hierfür
DE102006016410B3 (de) * 2006-04-07 2007-11-08 WINKLER + DüNNEBIER AG Vorrichtung zum Durchtrennen

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8821149B2 (en) 2011-05-05 2014-09-02 Kimberly-Clark Worldwide, Inc. Web treatment apparatus having center bearer ring
US10016312B2 (en) 2011-05-05 2018-07-10 Kimberly-Clark Worldwide, Inc. Method of treating a web using an apparatus having a center bearer ring
US10327958B2 (en) 2011-05-05 2019-06-25 Kimberly-Clark Worldwide, Inc. Method of treating a web using an apparatus having a center bearer ring

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