EP1974878B1 - Rotary cutting device - Google Patents

Rotary cutting device Download PDF

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Publication number
EP1974878B1
EP1974878B1 EP20080152648 EP08152648A EP1974878B1 EP 1974878 B1 EP1974878 B1 EP 1974878B1 EP 20080152648 EP20080152648 EP 20080152648 EP 08152648 A EP08152648 A EP 08152648A EP 1974878 B1 EP1974878 B1 EP 1974878B1
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EP
European Patent Office
Prior art keywords
cutting
roll
roller
cutting device
inner core
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.)
Active
Application number
EP20080152648
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German (de)
French (fr)
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EP1974878A1 (en
Inventor
Wilhelm Aichele
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Individual
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Individual
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Publication of EP1974878A1 publication Critical patent/EP1974878A1/en
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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
    • B26D7/2628—Means for adjusting the position 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
    • 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
    • B26D7/20—Cutting beds
    • B26D2007/202—Rollers or cylinders being pivoted during operation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
    • B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
    • B26F1/38—Cutting-out; Stamping-out
    • B26F1/384—Cutting-out; Stamping-out using rotating drums
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/4766—Orbital motion of cutting blade
    • Y10T83/4795—Rotary tool
    • Y10T83/483—With cooperating rotary cutter or backup

Definitions

  • the invention relates to a rotary cutting device, comprising a machine frame, a cutting roll rotatably mounted on the machine frame and a counter roll rotatably mounted on the machine frame, wherein the cutting roll and / or the counter roll have an inner core and an outer sleeve arranged around the inner core.
  • a cutting device in which the cutting tool is biased substantially parallel to a rotation axis.
  • the cutting tool has an outer sleeve on which a cutting edge sits, and an inner part, wherein the outer sleeve and the inner part are clamped against each other with a clamping force action substantially parallel to a rotational axis of the cutting tool.
  • a device for punching and / or embossing of webs is known, with a punching cylinder and a counter-pressure cylinder, between which a material web is feasible, wherein the distance between the punching cylinder and the impression cylinder is adjustable and the impression cylinder mounted on a fixed axis rotatable sleeve having. On the axes of several bearings are provided, the game is adjustable via at least one clamping unit.
  • a radially adjustable anvil roll assembly for use with a die iron roll of a rotary die press.
  • the anvil roll assembly includes a cylindrical sleeve having an internal bore, a shaft extending through the internal bore of the sleeve, the shaft being mountable on the rotary die press for selective rotation with respect to the press, and selective rotation of the shaft independent of the rotation of the die roller of the press, as well as a idler roller means mounted on the shaft for maintaining a fixed distance between rotation axes of the shaft and the die roller.
  • At least one cam assembly is provided which is eccentrically mounted on the shaft inside the sleeve inner bore, the cam assembly having a radial adjustment of the sleeve with respect to the die roller and the press in response to rotation of the shaft in any one infinite number of individual positions in relation to the press.
  • a rotatable anvil for a rotary cutting unit which comprises at least one anvil area which is provided for cooperation with a cutting part of a cutting roller.
  • a pair of load transferring regions on the anvil are for abutment with a pair of abutting roller components.
  • the pair of load-transmitting regions are arranged on each side of the roller region and deflection means are provided which are arranged below at least one of the anvil regions and the load-transmitting regions.
  • a cross cutter for cutting sheet-like material is known, with a pair of knife shafts, which are rotatably mounted on a tube mounted in the machine frame core and driven in common by a drive means.
  • the blades touch each other briefly during the cutting process.
  • At least one end of at least one core is associated with a force unit which generates a bending moment on the core, such that the blades abut each other during the contact or prestressing.
  • the invention has for its object to provide a rotary cutting device of the type mentioned, which provides a high quality cutting with a simple structure.
  • the outer sleeve is spaced from the inner core, that on the inner core abutment are arranged on which the outer sleeve is supported, wherein between adjacent abutments a gap is formed and that the abutment arranged so and are designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the counter bearings on the counter roller and / or cutting roller, the width of an abutment being less than 30% of the total length of the cutting roller or counter roller.
  • the outer sleeve is not supported over its entire inner surface on the inner core, but only by "discrete” abutment.
  • the counter-bearings can be arranged both on the cutting roller and on the counter-roller or only on the counter-roller or only on the cutting roller.
  • a defined force flow can be set on the cutting roller and / or mating roller, via which it can be achieved that the outer sleeve or outer sleeves bend less strongly under the action of cutting forces than the inner core or the inner cores.
  • the fundamental problem that, since the cutting roller and the counter-roller are clamped on at least one side of the machine frame, they bend.
  • the mating roll bends away from the cutting roll and the cutting roll bends away from the mating roll. This results in an increased distance between the surfaces of the cutting roller and the counter roll, which can lead to a deterioration of the cutting quality.
  • the bending of the cutting roller and / or counter-roller on the surface can be reduced since forces can be diverted away from the outer sleeve into the inner core and from there via a bearing.
  • With appropriate arrangement of the abutment leaves thereby reduce the relative deflection on the surface of the cutting roller and / or counter-roller.
  • the arrangement and design of the abutment depends on the particular application.
  • the abutments are arranged and designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the abutments on the counter roller and / or cutting roller. It can be a force flow at the counter roll and / or cutting roller reach, in which the deflection of the outer sleeve is smaller than the deflection of the inner core.
  • the abutments are arranged and designed so that the outer sleeve is movable relative to the inner core by elastic deformation. Due to a relative mobility between outer sleeve and inner core, a relative deflection between outer sleeve and inner core is possible. As a result, it is possible that the outer sleeve deflects less than the inner sleeve when cutting forces act.
  • the abutments are arranged and designed so that in a cutting operation, a deflection of the outer sleeve is smaller than a deflection of the inner core.
  • this clearance may be in an order of magnitude of, for example, between 2 ⁇ m and 100 ⁇ m. He can be taller too be.
  • the abutments are arranged and designed such that an at least approximately symmetrical force flow with respect to the cutting roller length and / or mating roller length results on the cutting roller and / or mating roller during a cutting operation.
  • the force flow is in particular symmetrical to a central transverse plane (which is perpendicular to the axis of rotation) of the cutting roller and / or counter-roller. It can thereby achieve a minimized deflection on the surface of the cutting roller, which is symmetrical to said center plane.
  • the abutments prefferably be formed, for example, by a plurality of balls which are arranged on the inner core.
  • the abutment comprise a ring portion, which is arranged on the inner core.
  • the ring area surrounds in particular band-shaped inner core.
  • the annular region is formed for example by a ring element, which is arranged on the inner core.
  • the annular region can also be formed in one piece on the inner core.
  • the width of a ring portion is smaller than the total length of the respective counter roll or cutting roll and in particular considerably smaller. It is for example at most 30% of the total length. In principle, it is advantageous if the annular region has the smallest possible width. At the ring area, where forces are transmitted, must however, the specific surface pressure is within the elastic range. This defines the minimum extent of the ring area.
  • the outer sleeve is fixed to the counter bearings, for example via form-locking elements.
  • the outer sleeve can be fixed radially and axially with respect to the inner core in a simple manner.
  • At least one seal is arranged between the outer sleeve and the inner core.
  • the seal is arranged in particular on one or more end faces of the outer sleeve. It can thereby seal a gap between the outer sleeve and the inner core.
  • the abutments are arranged symmetrically on the cutting roller and / or counter-roller. If, for example, a single abutment for the cutting roller or counter-roller is provided, then this is arranged centrally (relative to a counter-roller length or cutting roller length). If a plurality of abutment are provided, then these are arranged in particular symmetrically to a median plane of the backing roll or cutting roll.
  • the cutting roller has an outer sleeve, that one or more cutting edges are arranged on the outer sleeve of the cutting roller.
  • the cutting roller and the mating roller are each provided with abutments, arranged opposing bearing opposite.
  • An abutment of the cutting roller and an abutment of the counter-roller then face each other.
  • the abutments are aligned in a direction transverse to an axis of rotation of the cutting roller.
  • the cutting roller is supported on the counter-roller via at least one support ring.
  • the at least one support ring can be arranged on the cutting roller or the counter-roller.
  • a first support ring and a second support ring are then provided, wherein the abutment are arranged on the counter-roller and / or cutting roller between the first support ring and the second support ring.
  • the counter-roller is in particular rotatably mounted. It can be directly driven (via its own drive or via a transmission device which is connected to the drive of the cutting roller). It is also possible in principle that the counter-roller is driven by frictional engagement with material to be fed.
  • the cutting roller is mounted on both sides of the machine frame. It is then provided in particular a first pivot bearing and a spaced second pivot bearing.
  • the counter-roller is mounted on both sides of the machine frame.
  • the cutting roller is mounted on one side (rotatable, for example, via a single bearing) on the machine frame.
  • Such a rotary cutting device with cantilevered cutting roller can be compact.
  • the counter-roller is mounted on one side "flying" on the machine frame.
  • one or more cross-cutters are arranged on the cutting roller.
  • the rotary cutting device is designed as a cross-cutting device. It can thereby be separated, for example, webs of material with a high cutting rate.
  • one or more longitudinal cutting edges are arranged on the cutting roller.
  • cutting edges are designed so that it is possible to introduce contour cuts.
  • a first embodiment of a rotary cutting device according to the invention which in FIG. 1 shown and designated therein by 10 is realized as a rotary cutting machine. It comprises a machine frame 12, which is designed like a stand. The machine frame 12 has opposite uprights 14 which are connected by a bottom bridge 16 and a top bridge 18. About the bottom bridge 16, the rotary cutting device 10 is placed on a base.
  • the respective uprights 14 in turn comprise opposite uprights 20a, 20b.
  • each a cutting roller 22 and a counter-roller 24 (anvil roller) rotatably mounted.
  • the cutting roller 22 is mounted rotatably about an axis 28 via opposite rotary bearings 26. In FIG. 1 the axis 28 is perpendicular to the plane of the drawing.
  • the cutting roller 22 is associated with a drive for the rotational movement (not shown in the drawing). Via a biasing device 30, the cutting roller 22 can be pressed against the counter-roller 24.
  • the cutting roller 22 is supported on opposite support rings 32 on a surface 34 of the counter-roller 24.
  • the counter-roller 24 is provided with support rings, which are supported on a surface of the cutting roller 22.
  • the pivot bearings 26 for the cutting roller 22 are arranged on a respective bearing device 36, which is linearly displaceable on the machine frame 12.
  • the bearing means 36 as a whole including the pivot bearings 26 and the cutting roller 22
  • the cutting roller 22 has one or more cutting edges 38, which are arranged between the support rings 32.
  • the counter-roller 24 is likewise rotatably mounted about an axis 42 via opposite rotary bearings 40, which are arranged on the respective stator 14.
  • the axis 42 is parallel to the axis 28.
  • a material 44 to be cut which in particular is in the form of a web, is carried out between the counter-roller 24 and the cutting roller 22 between the support rings 32.
  • the counter roll 24 and the cutting roll 22 rotate in opposite directions to each other.
  • the biasing means 30 the cutting roller 22 is pressed to exert a cutting force against the counter-roller 24.
  • the counter-roller 24 has an inner core 46 ( FIGS. 2 to 4 ).
  • the inner core is in particular cylindrically shaped and rotationally symmetrical about an axis 48 which coincides with the axis of rotation 42.
  • first stub shaft 50 and a second stub shaft 52 are arranged, which serve for pivotal mounting of the counter-roller 24.
  • a first counter bearing 54a and a second counter bearing 54b are arranged in the embodiment shown. These abutments 54a, 54b are annular and arranged on the inner core 46 in the manner of a band.
  • the anvils 54a, 54b may be integrally connected to the inner core 46 or may be separate parts, which are fixed to the inner core 46.
  • the first abutment 54a and the second abutment 54b have, as in FIG. 5 indicated, a larger radius r 1 as a surface area 56 (radius r 2 ) of the inner core 46 outside the anvil 54a, 54b.
  • the anvils 54a, 54b are thereby stepped above the surface region 56. They each have a contact region 58, which is radially spaced from the surface region 56 of the inner core 46.
  • the abutments 54a, 54b are "discrete" supports having a width (parallel to the axis 48) which is significantly smaller than the total length of the backing roll 24. More specifically, this width is less than 30% of the total length.
  • the smaller the width of an abutment 54a, 54b the more advantageous it is for the introduction of force.
  • the smaller the width the less the mobility of the outer sleeve 60 relative to the inner core 46 is hindered.
  • the specific surface pressure acting on an abutment is still within the elastic range of the anvil, so that no plastic deformation can take place.
  • the relative width of an abutment relative to the total length of a cutting roller or counter-roller may also be in a range of 0.5% or less. The extent depends on the specific circumstances of the corresponding rotary cutting device.
  • the counter-roller 24 also has an outer sleeve 60, on which the surface 34 of the counter-roller 24 is formed. This surface 34 is in particular cylindrical.
  • the outer sleeve 60 has the shape of a hollow cylinder. The cutting roller 22 with the support rings 32 acts on this outer sleeve 60th
  • the outer sleeve 60 is supported on the discrete counter bearings 54a, 54b; the outer sleeve 60 is not supported over the entire surface area 56 on the inner core 46, but only on the contact areas 58 of the abutment 54a, 54b. Between an inner side 62 of the outer sleeve 60 and the surface region 56 of the inner core 46, a gap 64 is formed. This intermediate space 64 permits a relative deflection between the outer sleeve 60 and the inner core 46, in particular via different elastic deformation of the inner core 46 and the outer sleeve 60.
  • the first abutment 54a and the second abutment 54b are arranged symmetrically on the inner core 46. They have the same distance to a median plane 66 of the counter-roller 24. The center plane 66 is perpendicular to the axis 48. Further, the first abutment 54a has the same distance to a first end 68a of the inner core 46 (outside of the first stub shaft 50) as the second abutment 54b to an opposite second front end 68b.
  • the outer sleeve 60 is fixed relative to the inner core 46.
  • it is fixed on the inner core 46 via form-fitting means via the abutments 54a, 54b.
  • the outer sleeve 60 is axially clamped.
  • opposite support disks 70a, 70b are provided, which are arranged in the vicinity of the respective first front end 68a and second front end 68b.
  • a respective seal 72a, 72b is arranged, this seal in particular has the shape of an O-ring.
  • the support disks 70a, 70b are retained on the inner core 46 via respective circlips 74a, 74b in a direction away from the outer sleeve 60.
  • a height h of the gap 64 is for example in the range between 2 microns and 100 microns, depending on the application.
  • the height h can also be smaller or larger than just mentioned.
  • the counter-roller 24 is provided with at least one counter-bearing as described. It may alternatively or additionally be provided that the cutting roller 22 is provided with one or more abutments. The structure and arrangement of such an abutment on the cutting roller 22 is basically the same as described in connection with the counter-roller 24.
  • the cutting roller 22 is pressed by the biasing means 30 against the counter roll.
  • a force is exerted on the counter-roller 24 and on the cutting roller 22, a counter force is exerted.
  • the counter-roller 24 is clamped via its rotary bearings 40 in the region of the first stub shaft 50 and the second stub shaft 52 on the machine frame 12, respectively. This is in FIG. 6 indicated by the support points 76a, 76b.
  • forces 78 are exerted from the direction of the cutting roller ago. In the embodiment shown, these forces 78 act with respect to the direction of gravity g from above. These forces 78 cause a deflection of the counter roll 24 (especially the inner core 46) down.
  • FIG. 6 is a diagram for a counter-roller having a diameter of 50 mm, in which the deflection dy of the inner core 46 over the length 1 of the counter-roller 24 is shown. In this case, cutting forces in the order of 125 N / mm were exercised.
  • the inner core 46 undergoes a deflection of the order of magnitude of 22 ⁇ m downwards.
  • FIG. 7 the cutting roller 22 is shown with a stub shaft 80a and a stub shaft 80b.
  • a force is exerted in the direction of the counter roll 24. In the embodiment shown, this is a force parallel to the direction of gravity g.
  • the cutting roller 22 is clamped at the top. This is in FIG. 7 indicated by support points 82a, 82b.
  • the cutting roller 22 is bent upwards.
  • an inner core of the cutting roller 22, when having such an inner core bent upwards.
  • FIG. 7 2 a diagram is shown for the deflection of the cutting roller or of an inner core of the cutting roller over the length I of the cutting roller 22.
  • the data correspond to a cutting roller with a diameter of 40 mm with acting cutting forces of 125 N / mm.
  • the outer sleeve 60 is supported on the inner core 46 via the counter bearings 54a, 54b.
  • This support can be provided both for the cutting roller 22 and for the counter-roller 24 or only for the cutting roller 22 or only for the counter-roller 24.
  • It can thereby initiate defined forces during the cutting process and in particular cutting forces and derived.
  • Cutting forces can be introduced from the outer sleeve 60 into the inner core 46 via the abutments 54a, 54b and thereby derive via the corresponding pivot bearings 26 and 40, respectively.
  • the outer sleeve 60 is bent less strong than the corresponding inner core 46. This is greatly exaggerated in FIG. 8 indicated.
  • the outer sleeve 60 also experiences an elastic deformation and deflection.
  • the deformation of the outer sleeve 60 can be significantly lower than that of the inner core 46. This results in the construction of cutting forces a relative deflection or relative movement between the outer shell 60 and the inner core 46.
  • the outer sleeve 60 is less arcuate than the inner core 46, then with respect to the starting point without acting cutting forces, the surface 34 of the outer sleeve 60 (when it comes to the outer sleeve of the backing roll 24) less deflected than the inner core 46.
  • the deviation of the surface 34 of the outer sleeve 60 from the "ideal line" is less strong than if no discrete counter bearings 54a, 54b are provided.
  • the relative deflection of the surface 34 to the cutting roller 22 is less strong and gives better cutting results.
  • thereby longer counter-rollers 24 can be used with a smaller diameter.
  • one or more abutments are provided. These counter-bearings are arranged and designed such that a symmetrical force flow results on the cutting roller 22 or the counter-roller 24.
  • the power flow is in particular symmetrical to the center plane 66.
  • the outer solution 60 can be characterized less deform elastically than the corresponding inner core 46.
  • the rotary cutting device 10 is designed, for example, such that cutting edges are arranged on the cutting roller 22 which are arranged in a longitudinal direction (relative to a longitudinal direction 86 (FIG. FIG. 1 ) for transporting material 44) and in a transverse direction thereto.
  • a second embodiment of a rotary cutting device according to the invention which in FIG. 9 is shown and designated therein by 88, comprises a machine frame 90 on which basically the same as described above, a cutting roller 92 and a counter-roller 94 are each rotatably mounted are.
  • the counter-roller 94 is basically the same design as the counter-roller 24 as described above.
  • the cutting roller 92 is driven by, for example, a drive (not shown in the drawing).
  • a gear 98 is arranged, which engages in a gear 100 which is fixed in rotation with respect to the counter-roller 94.
  • the counter-roller 94 can also be driven by driving the cutting roller 92.
  • the cutting roller 92 has a first roller portion 102a and a second roller portion 102b, wherein these two roller portions 102a, 102b are spaced from each other.
  • a plurality of cross cutters 104 are respectively disposed. These cross cutters are evenly distributed. For example, they are spaced at an angle of 120 ° (relative to a cross section).
  • the transverse cutting edges 104 have a cutting surface 106, which is transverse and in particular perpendicular to a direction of transport of material through the rotary cutting device 88.
  • the cutting surfaces 106 are oriented parallel to a rotational axis 108 of the cutting roller 92.
  • an abutment 110a, 110b is arranged in a central region of each of the first roller portion 102a and the second roller portion 102b.
  • the anvil 110a, 110b is basically the same design as described above. In particular, these are annular regions which are arranged on a respective inner core 112 of the cutting roller 92.
  • the counter-roller 94 also has an inner core 114, on which spaced abutments 116a, 116b are arranged.
  • the counter bearings 116a, 116b are aligned with the counter bearings 110a, 110b and positioned directly opposite one another, so that a direct introduction of force to the counter bearings is possible.
  • the counter bearing 116a is then the counter bearing 110a opposite and the abutment 116b is opposite the abutment 110b.
  • a machine frame 120 is provided on the machine frame 120.
  • a first pivot bearing 122 is arranged for a counter-roller 124.
  • a second pivot bearing 126 is arranged on the machine frame 120 at a distance from the first pivot bearing 122, for example above it.
  • a cutting roller 128 is rotatably mounted. The cutting roller 128 and the counter roller 124 are thereby not each two-sided mounted on the machine frame 120, but held only on one side "flying" on the machine frame 120.
  • the cutting roller 128 has, for example, opposing support rings 130a, 130b. About these support rings 130a, 130b, the cutting roller 128 is supported on a surface 132 of the backing roll 124 from. It is also a version without support ring possible.
  • the cutting roller 128 is provided with cutting edges 134.
  • the blades 134 are adapted to the material to be cut.
  • Counter roll 124 and cutting roll 128 each have an inner core and respective outer sleeves 136 and 138 as described above.
  • the outer sleeve 138 of the cutting roller 128 is supported via a single abutment 140 on the corresponding inner core of the cutting roller 128.
  • the outer sleeve 136 of the counter-roller 124 is supported via an abutment 142 on the inner core of the counter-roller 124.
  • the abutments 140 and 142 are directly opposite to allow a direct application of force.

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Rolling Contact Bearings (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
  • Non-Silver Salt Photosensitive Materials And Non-Silver Salt Photography (AREA)
  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)

Abstract

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

Description

Die Erfindung betrifft eine Rotationsschneidevorrichtung, umfassend ein Maschinengestell, eine am Maschinengestell drehbar gelagerte Schneidwalze und eine am Maschinengestell drehbar gelagerte Gegenwalze, wobei die Schneidwalze und/oder die Gegenwalze einen Innenkern und eine um den Innenkern angeordnete Außenhülse aufweisen.The invention relates to a rotary cutting device, comprising a machine frame, a cutting roll rotatably mounted on the machine frame and a counter roll rotatably mounted on the machine frame, wherein the cutting roll and / or the counter roll have an inner core and an outer sleeve arranged around the inner core.

Aus der DE 39 24 053 A1 ist eine Vorrichtung zum Rotationsschneiden von Werkstoffbahnen mit einem Maschinengestell und mit am Maschinengestell in Drehlagern abgestützten, rotierend angetriebenen und einen Schneidbereich definierenden Walzen, nämlich einer Schneidwalze und einer Gegenschneidwalze, die im Schneidbereich zwischen sich einen Walzenspalt zum Durchführen der Werkstoffbahn ausbilden, bekannt. Die Schneidwalze und Gegenschneidwalze sind durch an ihnen außerhalb des Schneidbereichs angeordnete Distanzringe unmittelbar aufeinander abrollend abgestützt. Zwischen den Distanzringen greift an wenigstens einer diesen Walzen mindestens ein verstellbares Druckrollenglied an, das diese eine Walze mit einstellbarer Kraft gegen die andere Walze drückt.From the DE 39 24 053 A1 is a device for rotary cutting material webs with a machine frame and supported on the machine frame in pivot bearings, rotatably driven and a cutting area defining rollers, namely a cutting roller and a counter-cutting roller, which form a nip for performing the material web between them in the cutting area known. The cutting roller and counter-cutting roller are supported by rolling on them outside of the cutting area arranged spacer rings directly rolling on each other. Between the spacers engages at least one of these rollers at least one adjustable pressure roller member, which presses this one roller with adjustable force against the other roller.

Aus der EP 1 238 765 A2 ist eine Schneidvorrichtung bekannt, bei welcher das Schneidwerkzeug im Wesentlichen parallel zu einer Drehachse vorgespannt ist. Das Schneidwerkzeug weist eine Außenhülse auf, an welcher eine Schneide sitzt, und ein Innenteil, wobei die Außenhülse und das Innenteil gegeneinander verspannt sind mit einer Spannkraftwirkung im Wesentlichen parallel zu einer Drehachse des Schneidwerkzeugs.From the EP 1 238 765 A2 a cutting device is known in which the cutting tool is biased substantially parallel to a rotation axis. The cutting tool has an outer sleeve on which a cutting edge sits, and an inner part, wherein the outer sleeve and the inner part are clamped against each other with a clamping force action substantially parallel to a rotational axis of the cutting tool.

Weitere Rotationsschneidevorrichtungen sind aus der EP 0 976 510 A2 , der EP 1 180 419 A1 , der EP 1 186 387 A2 und der EP 1 721 712 A1 bekannt.Other rotary cutting devices are from the EP 0 976 510 A2 , of the EP 1 180 419 A1 , of the EP 1 186 387 A2 and the EP 1 721 712 A1 known.

Aus der DE 10 2004 033 032 A1 ist eine Vorrichtung zum Stanzen und/oder Prägen von Materialbahnen bekannt, mit einem Stanzzylinder und einem Gegendruckzylinder, zwischen denen eine Materialbahn durchführbar ist, wobei der Abstand zwischen dem Stanzzylinder und dem Gegendruckzylinder verstellbar ausgebildet ist und der Gegendruckzylinder eine an einer feststehenden Achse gelagerte drehbare Hülse aufweist. An den Achsen sind mehrere Lager vorgesehen, deren Spiel über mindestens eine Spanneinheit einstellbar ist.From the DE 10 2004 033 032 A1 a device for punching and / or embossing of webs is known, with a punching cylinder and a counter-pressure cylinder, between which a material web is feasible, wherein the distance between the punching cylinder and the impression cylinder is adjustable and the impression cylinder mounted on a fixed axis rotatable sleeve having. On the axes of several bearings are provided, the game is adjustable via at least one clamping unit.

Aus der EP 0 580 576 B1 ist ein radial einstellbarer Ambosswalzen-Aufbau zur Verwendung mit einer Schneideisenwalze einer Rotationsschneideisen-Presse bekannt. Der Ambosswalzen-Aufbau umfasst eine zylindrische Hülse mit einer Innenbohrung, eine Welle, die sich durch die Innenbohrung der Hülse erstreckt, wobei die Welle auf der Rotationsschneideisen-Presse zur selektiven Rotation in Bezug auf die Presse montierbar ist und die selektive Rotation der Welle unabhängig von der Rotation der Schneideisenwalze der Presse ist, sowie eine Tragrolleneinrichtung, die auf der Welle zur Aufrechterhaltung eines festen Abstands zwischen Rotationsachsen der Welle und der Schneideisenwalze montiert ist. Es ist mindestens ein Nocken-Aufbau vorgesehen, der außermittig auf der Welle im Inneren der Hülsen-Innenbohrung befestigt ist, wobei der Nocken-Aufbau eine radiale Einstellung der Hülse in Bezug auf die Schneideisenwalze und die Presse als Reaktion auf eine Rotation der Welle in irgendeiner unendlichen Anzahl von Einzelpositionen in Bezug auf die Presse bewirkt.From the EP 0 580 576 B1 For example, a radially adjustable anvil roll assembly for use with a die iron roll of a rotary die press is known. The anvil roll assembly includes a cylindrical sleeve having an internal bore, a shaft extending through the internal bore of the sleeve, the shaft being mountable on the rotary die press for selective rotation with respect to the press, and selective rotation of the shaft independent of the rotation of the die roller of the press, as well as a idler roller means mounted on the shaft for maintaining a fixed distance between rotation axes of the shaft and the die roller. At least one cam assembly is provided which is eccentrically mounted on the shaft inside the sleeve inner bore, the cam assembly having a radial adjustment of the sleeve with respect to the die roller and the press in response to rotation of the shaft in any one infinite number of individual positions in relation to the press.

Aus der EP 1 655 117 A1 ist ein drehbarer Amboss für eine Rotationsschneideeinheit bekannt, welcher mindestens einen Ambossbereich umfasst, der zur Kooperation mit einem Schneideteil einer Schneidwalze vorgesehen ist. Ein Paar von lastübertragenden Bereichen an dem Amboss dienen zur Anlage an ein Paar von Anlageteilen der Schneidwalze. Das Paar an lastübertragenden Bereichen ist dabei auf jeder Seite des Walzenbereichs angeordnet und es sind Ablenkungsmittel vorgesehen, welche unterhalb mindestens eines der Ambossbereiche und der lastübertragenden Bereiche angeordnet sind.From the EP 1 655 117 A1 For example, a rotatable anvil for a rotary cutting unit is known, which comprises at least one anvil area which is provided for cooperation with a cutting part of a cutting roller. A pair of load transferring regions on the anvil are for abutment with a pair of abutting roller components. The pair of load-transmitting In this case, regions are arranged on each side of the roller region and deflection means are provided which are arranged below at least one of the anvil regions and the load-transmitting regions.

Aus der EP 0 263 359 A1 ist ein Querschneider zum Schneiden von bahnartigem Material bekannt, mit einem Paar Messerwellen, die rohrartig auf einem im Maschinengestell befestigten Kern drehbar gelagert und mittels einer Antriebseinrichtung gemeinsam angetrieben sind. Die Messer berühren sich während des Schneidvorgangs kurzzeitig. Mindestens einem Ende mindestens eines Kerns ist eine Krafteinheit zugeordnet, die ein Biegemoment am Kern erzeugt, derart, dass die Messer während der Berührung oder Vorspannung gegeneinander anliegen.From the EP 0 263 359 A1 a cross cutter for cutting sheet-like material is known, with a pair of knife shafts, which are rotatably mounted on a tube mounted in the machine frame core and driven in common by a drive means. The blades touch each other briefly during the cutting process. At least one end of at least one core is associated with a force unit which generates a bending moment on the core, such that the blades abut each other during the contact or prestressing.

Aus der US 4,455,903 ist eine Ambosswalze mit variablem Durchmesser bekannt.From the US 4,455,903 an anvil roll of variable diameter is known.

Aus der FR 2 579 507 A1 ist eine Schneidwalze bekannt.From the FR 2 579 507 A1 a cutting roller is known.

Der Erfindung liegt die Aufgabe zugrunde, eine Rotationsschneidevorrichtung der eingangs genannten Art bereitzustellen, welche bei einfachem Aufbau eine hohe Schneidqualität bereitstellt.The invention has for its object to provide a rotary cutting device of the type mentioned, which provides a high quality cutting with a simple structure.

Diese Aufgabe wird bei der eingangs genannten Rotationsschneidevorrichtung erfindungsgemäß dadurch gelöst, dass die Außenhülse zu dem Innenkern beabstandet ist, dass an dem Innenkern Gegenlager angeordnet sind, an welchen sich die Außenhülse abstützt, wobei zwischen benachbarten Gegenlagern ein Zwischenraum gebildet ist und dass die Gegenlager so angeordnet und ausgebildet sind, dass sich Kräfte, welche von der Schneidwalze und Gegenwalze aufeinander ausgeübt werden, definiert über die Gegenlager an der Gegenwalze und/oder Schneidwalze ableiten lassen, wobei die Breite eines Gegenlagers kleiner als 30 % der Gesamtlänge der Schneidwalze oder Gegenwalze ist.This object is achieved with the above-mentioned rotary cutting device according to the invention that the outer sleeve is spaced from the inner core, that on the inner core abutment are arranged on which the outer sleeve is supported, wherein between adjacent abutments a gap is formed and that the abutment arranged so and are designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the counter bearings on the counter roller and / or cutting roller, the width of an abutment being less than 30% of the total length of the cutting roller or counter roller.

Bei der erfindungsgemäßen Lösung ist die Außenhülse nicht über ihre ganze Innenfläche an dem Innenkern abgestützt, sondern nur durch "diskrete" Gegenlager. Die Gegenlager können dabei sowohl an der Schneidwalze als auch an der Gegenwalze oder nur an der Gegenwalze oder nur an der Schneidwalze angeordnet sein.In the solution according to the invention, the outer sleeve is not supported over its entire inner surface on the inner core, but only by "discrete" abutment. The counter-bearings can be arranged both on the cutting roller and on the counter-roller or only on the counter-roller or only on the cutting roller.

Durch die Gegenlager lässt sich ein definierter Kraftfluss an der Schneidwalze und/oder Gegenwalze einstellen, über den erreichbar ist, dass sich bei der Einwirkung von Schneidkräften die Außenhülse bzw. Außenhülsen weniger stark durchbiegen als der Innenkern bzw. die Innenkerne. Beim Schneiden tritt das grundsätzliche Problem auf, dass, da die Schneidwalze und die Gegenwalze mindestens einseitig an dem Maschinengestell eingespannt sind, diese sich verbiegen. Wenn Schneidkräfte einwirken, dann verbiegt sich die Gegenwalze von der Schneidwalze weg und es verbiegt sich die Schneidwalze von der Gegenwalze weg. Dadurch entsteht ein vergrößerter Abstand zwischen den Oberflächen der Schneidwalze und der Gegenwalze, der zu einer Verschlechterung der Schneidqualität führen kann.By means of the abutments, a defined force flow can be set on the cutting roller and / or mating roller, via which it can be achieved that the outer sleeve or outer sleeves bend less strongly under the action of cutting forces than the inner core or the inner cores. When cutting occurs, the fundamental problem that, since the cutting roller and the counter-roller are clamped on at least one side of the machine frame, they bend. When cutting forces act, the mating roll bends away from the cutting roll and the cutting roll bends away from the mating roll. This results in an increased distance between the surfaces of the cutting roller and the counter roll, which can lead to a deterioration of the cutting quality.

Bei der erfindungsgemäßen Lösung lässt sich die Verbiegung der Schneidwalze und/oder Gegenwalze an der Oberfläche verkleinern, da durch die Gegenlager Kräfte von der Außenhülse weg in den Innenkern und von dort über eine Lagerung ableitbar sind. Bei entsprechender Anordnung der Gegenlagers lässt sich dadurch die relative Durchbiegung an der Oberfläche der Schneidwalze und/oder Gegenwalze verringern. Die Anordnung und Ausbildung der Gegenlager hängt von der jeweiligen Anwendung ab.In the solution according to the invention, the bending of the cutting roller and / or counter-roller on the surface can be reduced since forces can be diverted away from the outer sleeve into the inner core and from there via a bearing. With appropriate arrangement of the abutment leaves thereby reduce the relative deflection on the surface of the cutting roller and / or counter-roller. The arrangement and design of the abutment depends on the particular application.

Durch die erfindungsgemäße Lösung ist es möglich, auch "weniger steife" Schneidwalzen und/oder Gegenwalzen einzusetzen, d. h. insbesondere Walzen einzusetzen, welche einen relativ geringen Durchmesser aufweisen und relativ lang sind. Dadurch wiederum lassen sich beispielsweise großflächige Schnitte erzeugen, die mit Rotationsschneidevorrichtungen mit kürzeren Walzen nicht möglich sind. Ferner ist es dadurch beispielsweise auch möglich, eine höhere Schnittrate zu erreichen, wenn längere Walzen vorgesehen werden, an denen mehrere Schneidenbereiche angeordnet sind.By the solution according to the invention, it is possible to use "less stiff" cutting rollers and / or counter-rollers, d. H. in particular to use rollers, which have a relatively small diameter and are relatively long. This, in turn, for example, can produce large-scale cuts that are not possible with rotary cutting devices with shorter rolls. Furthermore, this also makes it possible, for example, to achieve a higher cutting rate if longer rollers are provided, on which several cutting areas are arranged.

Die Gegenlager sind so angeordnet und ausgebildet, dass sich Kräfte, welche von der Schneidwalze und Gegenwalze aufeinander ausgeübt werden, definiert über die Gegenlager an der Gegenwalze und/oder Schneidwalze ableiten lassen. Es lässt sich ein Kraftfluss an der Gegenwalze und/oder Schneidwalze erreichen, bei dem die Durchbiegung der Außenhülse kleiner ist als die Durchbiegung des Innenkerns.The abutments are arranged and designed such that forces which are exerted on one another by the cutting roller and counter roller can be defined via the abutments on the counter roller and / or cutting roller. It can be a force flow at the counter roll and / or cutting roller reach, in which the deflection of the outer sleeve is smaller than the deflection of the inner core.

Aus dem gleichen Grund ist es günstig, wenn die Gegenlager so angeordnet und ausgebildet sind, dass die Außenhülse durch elastische Verformung relativ zum Innenkern beweglich ist. Durch eine relative Beweglichkeit zwischen Außenhülse und Innenkern ist eine relative Auslenkung zwischen Außenhülse und Innenkern möglich. Dadurch lässt es sich erreichen, dass die Außenhülse sich weniger stark durchbiegt als die Innenhülse, wenn Schneidkräfte wirken.For the same reason, it is favorable if the abutments are arranged and designed so that the outer sleeve is movable relative to the inner core by elastic deformation. Due to a relative mobility between outer sleeve and inner core, a relative deflection between outer sleeve and inner core is possible. As a result, it is possible that the outer sleeve deflects less than the inner sleeve when cutting forces act.

Aus dem gleichen Grund ist es günstig, wenn die Gegenlager so angeordnet und ausgebildet sind, dass bei einem Schneidvorgang eine Durchbiegung der Außenhülse kleiner ist als eine Durchbiegung des Innenkerns.For the same reason, it is advantageous if the abutments are arranged and designed so that in a cutting operation, a deflection of the outer sleeve is smaller than a deflection of the inner core.

Günstig ist es, wenn außerhalb der Gegenlager zwischen der Außenhülse und der Innenhülse ein Zwischenraum (Freiraum) liegt. Die Höhe dieses Freiraums (in radialer Richtung) kann in einem Größenordnungsbereich zwischen beispielsweise 2 µm und 100 µm liegen. Er kann auch größer sein. Durch diesen Freiraum ist eine relative Auslenkung zwischen der Außenhülse und dem Innenkern ermöglicht, um so wiederum die Durchbiegung an der Oberfläche der Schneidwalze und/oder Gegenwalze gering halten zu können.It is favorable if there is a space (clearance) outside the abutment between the outer sleeve and the inner sleeve. The height of this clearance (in the radial direction) may be in an order of magnitude of, for example, between 2 μm and 100 μm. He can be taller too be. By this clearance, a relative deflection between the outer sleeve and the inner core is made possible, so as turn to keep the deflection on the surface of the cutting roller and / or counter roll low.

Aus dem gleichen Grund ist es günstig, wenn zwischen benachbarten Gegenlagern ein Zwischenraum (Freiraum) liegt. Die Außenhülse ist dann über diskrete Gegenlager an dem Innenkern gelagert.For the same reason, it is favorable if there is a clearance (clearance) between adjacent thrust bearings. The outer sleeve is then mounted on discrete counter bearing on the inner core.

Günstig ist es, wenn die Gegenlager so angeordnet und ausgebildet sind, dass sich an der Schneidwalze und/oder Gegenwalze bei einem Schneidvorgang ein mindestens näherungsweise symmetrischer Kraftfluss bezogen auf die Schneidwalzenlänge und/oder Gegenwalzenlänge ergibt. Der Kraftfluss ist insbesondere symmetrisch zu einer mittleren Querebene (welche senkrecht zur Rotationsachse ist) der Schneidwalze und/oder Gegenwalze. Es lässt sich dadurch an der Oberfläche der Schneidwalze eine minimierte Durchbiegung erreichen, welche zu der genannten Mittelebene symmetrisch ist.It is favorable if the abutments are arranged and designed such that an at least approximately symmetrical force flow with respect to the cutting roller length and / or mating roller length results on the cutting roller and / or mating roller during a cutting operation. The force flow is in particular symmetrical to a central transverse plane (which is perpendicular to the axis of rotation) of the cutting roller and / or counter-roller. It can thereby achieve a minimized deflection on the surface of the cutting roller, which is symmetrical to said center plane.

Es ist grundsätzlich möglich, dass die Gegenlager beispielsweise durch eine Mehrzahl von Kugeln gebildet sind, welche an dem Innenkern angeordnet sind. Bei einer fertigungstechnisch einfachen Ausführungsform umfassen die Gegenlager einen Ringbereich, welcher an dem Innenkern angeordnet ist. Der Ringbereich umgibt insbesondere bandförmig den Innenkern. Der Ringbereich ist beispielsweise durch ein Ringelement gebildet, welches an dem Innenkern angeordnet ist. Der Ringbereich kann auch einstückig an dem Innenkern gebildet sein.It is fundamentally possible for the abutments to be formed, for example, by a plurality of balls which are arranged on the inner core. In a manufacturing technology simple embodiment, the abutment comprise a ring portion, which is arranged on the inner core. The ring area surrounds in particular band-shaped inner core. The annular region is formed for example by a ring element, which is arranged on the inner core. The annular region can also be formed in one piece on the inner core.

Die Breite eines Ringbereichs ist kleiner als die Gesamtlänge der jeweiligen Gegenwalze bzw. Schneidwalze und insbesondere erheblich kleiner. Sie beträgt beispielsweise höchstens 30 % der jeweiligen Gesamtlänge. Grundsätzlich ist es vorteilhaft, wenn der Ringbereich eine möglichst geringe Breite aufweist. An dem Ringbereich, an dem Kräfte übertragen werden, muss jedoch die spezifische Flächenpressung innerhalb des elastischen Bereichs liegen. Dies definiert die minimale Ausdehnung des Ringbereichs.The width of a ring portion is smaller than the total length of the respective counter roll or cutting roll and in particular considerably smaller. It is for example at most 30% of the total length. In principle, it is advantageous if the annular region has the smallest possible width. At the ring area, where forces are transmitted, must however, the specific surface pressure is within the elastic range. This defines the minimum extent of the ring area.

Bei einer Ausführungsform ist es vorgesehen, dass die Außenhülse an den Gegenlagern beispielsweise über Formschlusselemente fixiert ist. Dadurch lässt sich die Außenhülse bezüglich des Innenkerns auf einfache Weise radial und axial fixieren.In one embodiment, it is provided that the outer sleeve is fixed to the counter bearings, for example via form-locking elements. As a result, the outer sleeve can be fixed radially and axially with respect to the inner core in a simple manner.

Es kann vorgesehen sein, dass zwischen der Außenhülse und dem Innenkern mindestens eine Dichtung angeordnet ist. Die Dichtung ist insbesondere an einer oder mehreren Stirnseiten der Außenhülse angeordnet. Es lässt sich dadurch ein Zwischenraum zwischen der Außenhülse und dem Innenkern abdichten.It can be provided that at least one seal is arranged between the outer sleeve and the inner core. The seal is arranged in particular on one or more end faces of the outer sleeve. It can thereby seal a gap between the outer sleeve and the inner core.

Ganz besonders vorteilhaft ist es, wenn die Gegenlager an der Schneidwalze und/oder Gegenwalze symmetrisch angeordnet sind. Wenn beispielsweise ein einziges Gegenlager für die Schneidwalze oder Gegenwalze vorgesehen ist, dann ist dieses mittig (bezogen auf eine Gegenwalzenlänge bzw. Schneidwalzenlänge) angeordnet. Wenn mehrere Gegenlager vorgesehen sind, dann sind diese insbesondere symmetrisch zu einer Mittelebene der Gegenwalze bzw. Schneidwalze angeordnet.It is particularly advantageous if the abutments are arranged symmetrically on the cutting roller and / or counter-roller. If, for example, a single abutment for the cutting roller or counter-roller is provided, then this is arranged centrally (relative to a counter-roller length or cutting roller length). If a plurality of abutment are provided, then these are arranged in particular symmetrically to a median plane of the backing roll or cutting roll.

Es kann vorgesehen sein, wenn die Schneidwalze eine Außenhülse aufweist, dass an der Außenhülse der Schneidwalze eine oder mehrere Schneiden angeordnet sind.It can be provided that the cutting roller has an outer sleeve, that one or more cutting edges are arranged on the outer sleeve of the cutting roller.

Besonders vorteilhaft ist es, wenn die Schneidwalze und die Gegenwalze mit jeweils Gegenlagern versehen sind, Gegenlager gegenüberliegend anzuordnen. Ein Gegenlager der Schneidwalze und ein Gegenlager der Gegenwalze stehen sich dann einander gegenüber. In diesem Falle sind die Gegenlager in einer Richtung quer zu einer Rotationsachse der Schneidwalze fluchtend ausgerichtet. Dadurch lassen sich Kräfte definiert ableiten und die Oberflächendurchbiegung sowohl an der Schneidwalze als auch an der Gegenwalze lässt sich minimieren. Man erhält dadurch ein optimiertes Schneidergebnis.It is particularly advantageous if the cutting roller and the mating roller are each provided with abutments, arranged opposing bearing opposite. An abutment of the cutting roller and an abutment of the counter-roller then face each other. In this case, the abutments are aligned in a direction transverse to an axis of rotation of the cutting roller. As a result, forces can be derived in a defined manner and the surface deflection both at the cutting roller and at the counter roller can be minimized. This gives an optimized cutting result.

Bei einer Ausführungsform stützt sich die Schneidwalze an der Gegenwalze über mindestens einen Stützring ab. Der mindestens eine Stützring kann dabei an der Schneidwalze oder der Gegenwalze angeordnet sein.In one embodiment, the cutting roller is supported on the counter-roller via at least one support ring. The at least one support ring can be arranged on the cutting roller or the counter-roller.

Insbesondere sind dann ein erster Stützring und ein zweiter Stützring vorgesehen, wobei die Gegenlager an der Gegenwalze und/oder Schneidwalze zwischen dem ersten Stützring und dem zweiten Stützring angeordnet sind. Dadurch lässt sich eine Optimierung des Kraftflusses erreichen.In particular, a first support ring and a second support ring are then provided, wherein the abutment are arranged on the counter-roller and / or cutting roller between the first support ring and the second support ring. As a result, an optimization of the power flow can be achieved.

Die Gegenwalze ist insbesondere drehbar gelagert. Sie kann dabei direkt angetrieben sein (über einen eigenen Antrieb oder über eine Getriebeeinrichtung, welche mit dem Antrieb der Schneidwalze verbunden ist). Es ist grundsätzlich auch möglich, dass die Gegenwalze über Reibschluss mit durchzuführendem Material angetrieben wird.The counter-roller is in particular rotatably mounted. It can be directly driven (via its own drive or via a transmission device which is connected to the drive of the cutting roller). It is also possible in principle that the counter-roller is driven by frictional engagement with material to be fed.

Bei einer Ausführungsform ist die Schneidwalze zweiseitig an dem Maschinengestell gelagert. Es ist dann insbesondere ein erstes Drehlager und ein beabstandetes zweites Drehlager vorgesehen.In one embodiment, the cutting roller is mounted on both sides of the machine frame. It is then provided in particular a first pivot bearing and a spaced second pivot bearing.

In diesem Fall ist es vorteilhaft, wenn auch die Gegenwalze zweiseitig an dem Maschinengestell gelagert ist.In this case, it is advantageous if the counter-roller is mounted on both sides of the machine frame.

Es ist auch möglich, dass die Schneidwalze einseitig (beispielsweise über ein einziges Lager drehbar) an dem Maschinengestell gelagert ist. Eine solche Rotationsschneidevorrichtung mit fliegend gelagerter Schneidwalze lässt sich kompakt aufbauen.It is also possible that the cutting roller is mounted on one side (rotatable, for example, via a single bearing) on the machine frame. Such a rotary cutting device with cantilevered cutting roller can be compact.

In diesem Fall ist dann insbesondere auch die Gegenwalze einseitig "fliegend" an dem Maschinengestell gelagert.In this case, then in particular the counter-roller is mounted on one side "flying" on the machine frame.

An der Schneidwalze sind beispielsweise eine oder mehrere Querschneiden angeordnet. Beispielsweise ist die Rotationsschneidevorrichtung als Querschneidevorrichtung ausgebildet. Es lassen sich dadurch beispielsweise Materialbahnen mit hoher Schneidrate trennen.For example, one or more cross-cutters are arranged on the cutting roller. For example, the rotary cutting device is designed as a cross-cutting device. It can thereby be separated, for example, webs of material with a high cutting rate.

Es ist auch alternativ oder zusätzlich möglich, dass an der Schneidwalze eine oder mehrere Längsschneiden angeordnet sind. Insbesondere sind Schneiden so ausgebildet, dass sich Konturschnitte einbringen lassen.It is also alternatively or additionally possible that one or more longitudinal cutting edges are arranged on the cutting roller. In particular, cutting edges are designed so that it is possible to introduce contour cuts.

Die nachfolgende Beschreibung bevorzugter Ausführungsformen dient im Zusammenhang mit der Zeichnung der näheren Erläuterung der Erfindung. Es zeigen:

Figur 1
eine seitliche Ansicht eines Ausführungsbeispiels einer erfindungsgemäßen Rotationsschneidevorrichtung;
Figur 2
eine schematische Darstellung einer Gegenwalze;
Figur 3
eine stirnseitige Draufsicht auf die Gegenwalze gemäß Figur 2;
Figur 4
eine Schnittansicht der Gegenwalze längs der Linie 4-4 gemäß Figur 3;
Figur 5
eine vergrößerte Darstellung des Bereichs A gemäß Figur 4;
Figur 6
schematisch die Verformung eines Innenkerns der Gegenwalze über deren Länge, wenn eine Schneidkraft ausgewirkt wird;
Figur 7
dazu angepasst die Verformung einer entsprechenden Rotationswalze, wenn diese auf die Gegenwalze wirkt;
Figur 8
schematisch die Verformung einer Außenhülse im Vergleich zum Innenkern bei der erfindungsgemäßen Lösung;
Figur 9
ein zweites Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung (Querschneidvorrichtung);
Figur 10
eine Schnittansicht der Rotationsschneidevorrichtung gemäß Figur 9; und
Figur 11
ein drittes Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung.
The following description of preferred embodiments is used in conjunction with the drawings for a more detailed explanation of the invention. Show it:
FIG. 1
a side view of an embodiment of a rotary cutting device according to the invention;
FIG. 2
a schematic representation of a counter-roller;
FIG. 3
a frontal plan view of the mating roll according to FIG. 2 ;
FIG. 4
a sectional view of the backing roll along the line 4-4 according to FIG. 3 ;
FIG. 5
an enlarged view of the area A according to FIG. 4 ;
FIG. 6
schematically the deformation of an inner core of the counter roll over the length thereof, when a cutting force is affected;
FIG. 7
adapted to the deformation of a corresponding rotation roller, when it acts on the counter-roller;
FIG. 8
schematically the deformation of an outer sleeve compared to the inner core in the inventive solution;
FIG. 9
A second embodiment of a rotary cutting device according to the invention (cross-cutting device);
FIG. 10
a sectional view of the rotary cutter according to FIG. 9 ; and
FIG. 11
A third embodiment of a rotary cutting device according to the invention.

Ein erstes Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung, welche in Figur 1 gezeigt und dort mit 10 bezeichnet ist, ist als Rotationsschneidemaschine realisiert. Sie umfasst ein Maschinengestell 12, welches ständerartig ausgebildet ist. Das Maschinengestell 12 weist gegenüberliegende Ständer 14 auf, welche durch eine Bodenbrücke 16 und eine Oberbrücke 18 verbunden sind. Über die Bodenbrücke 16 ist die Rotationsschneidevorrichtung 10 auf einem Untergrund aufgestellt.A first embodiment of a rotary cutting device according to the invention, which in FIG. 1 shown and designated therein by 10 is realized as a rotary cutting machine. It comprises a machine frame 12, which is designed like a stand. The machine frame 12 has opposite uprights 14 which are connected by a bottom bridge 16 and a top bridge 18. About the bottom bridge 16, the rotary cutting device 10 is placed on a base.

Die jeweiligen Ständer 14 wiederum umfassen gegenüberliegende Ständerpfosten 20a, 20b.The respective uprights 14 in turn comprise opposite uprights 20a, 20b.

An den Ständern 14 des Maschinengestells 12 sind jeweils eine Schneidwalze 22 und eine Gegenwalze 24 (Ambosswalze) drehbar gelagert. Die Schneidwalze 22 ist dabei über gegenüberliegende Drehlager 26 um eine Achse 28 drehbar gelagert. In Figur 1 ist die Achse 28 senkrecht zur Zeichenebene.On the uprights 14 of the machine frame 12 are each a cutting roller 22 and a counter-roller 24 (anvil roller) rotatably mounted. The cutting roller 22 is mounted rotatably about an axis 28 via opposite rotary bearings 26. In FIG. 1 the axis 28 is perpendicular to the plane of the drawing.

Der Schneidwalze 22 ist ein Antrieb für die Drehbewegung zugeordnet (in der Zeichnung nicht gezeigt). Über eine Vorspanneinrichtung 30 kann die Schneidwalze 22 gegen die Gegenwalze 24 gedrückt werden.The cutting roller 22 is associated with a drive for the rotational movement (not shown in the drawing). Via a biasing device 30, the cutting roller 22 can be pressed against the counter-roller 24.

Die Schneidwalze 22 stützt sich über gegenüberliegende Stützringe 32 an einer Oberfläche 34 der Gegenwalze 24 ab. Alternativ ist es auch möglich, dass die Gegenwalze 24 mit Stützringen versehen ist, welche sich an einer Oberfläche der Schneidwalze 22 abstützen.The cutting roller 22 is supported on opposite support rings 32 on a surface 34 of the counter-roller 24. Alternatively, it is also possible that the counter-roller 24 is provided with support rings, which are supported on a surface of the cutting roller 22.

Die Drehlager 26 für die Schneidwalze 22 sind an einer jeweiligen Lagereinrichtung 36 angeordnet, welche an dem Maschinengestell 12 linear verschieblich ist. Durch die Vorspanneinrichtung 30 kann die Lagereinrichtung 36 als Ganzes (einschließlich der Drehlager 26 und der Schneidwalze 22) gegen die Gegenwalze 24 verschoben werden, um eine Schneidkraft auszuüben.The pivot bearings 26 for the cutting roller 22 are arranged on a respective bearing device 36, which is linearly displaceable on the machine frame 12. By the biasing means 30, the bearing means 36 as a whole (including the pivot bearings 26 and the cutting roller 22) can be displaced against the counter roll 24 to exert a cutting force.

Die Schneidwalze 22 weist eine oder mehrere Schneiden 38 auf, welche zwischen den Stützringen 32 angeordnet sind.The cutting roller 22 has one or more cutting edges 38, which are arranged between the support rings 32.

Die Gegenwalze 24 ist ebenfalls über gegenüberliegende Drehlager 40, welche an dem jeweiligen Ständer 14 angeordnet sind, um eine Achse 42 drehbar gelagert. Die Achse 42 ist parallel zur Achse 28.The counter-roller 24 is likewise rotatably mounted about an axis 42 via opposite rotary bearings 40, which are arranged on the respective stator 14. The axis 42 is parallel to the axis 28.

Zur Durchführung eines Schneidvorgangs wird ein zu schneidendes Material 44, welches insbesondere bahnförmig vorliegt, zwischen der Gegenwalze 24 und der Schneidwalze 22 zwischen den Stützringen 32 durchgeführt. Die Gegenwalze 24 und die Schneidwalze 22 rotieren gegensinnig zueinander. Durch die Vorspanneinrichtung 30 wird die Schneidwalze 22 zur Ausübung einer Schneidkraft gegen die Gegenwalze 24 gedrückt.To carry out a cutting operation, a material 44 to be cut, which in particular is in the form of a web, is carried out between the counter-roller 24 and the cutting roller 22 between the support rings 32. The counter roll 24 and the cutting roll 22 rotate in opposite directions to each other. By the biasing means 30, the cutting roller 22 is pressed to exert a cutting force against the counter-roller 24.

Die Gegenwalze 24 weist einen Innenkern 46 auf (Figuren 2 bis 4). Der Innenkern ist insbesondere zylindrisch ausgebildet und rotationssymmetrisch zu einer Achse 48, welche mit der Drehachse 42 zusammenfällt.The counter-roller 24 has an inner core 46 ( FIGS. 2 to 4 ). The inner core is in particular cylindrically shaped and rotationally symmetrical about an axis 48 which coincides with the axis of rotation 42.

An dem Innenkern sind ein erster Wellenstummel 50 und ein zweiter Wellenstummel 52 angeordnet, welche zur Drehlagerung der Gegenwalze 24 dienen.On the inner core, a first stub shaft 50 and a second stub shaft 52 are arranged, which serve for pivotal mounting of the counter-roller 24.

An dem Innenkern 46 sind bei dem gezeigten Ausführungsbeispiel ein erstes Gegenlager 54a und ein zweites Gegenlager 54b angeordnet. Diese Gegenlager 54a, 54b sind ringförmig ausgebildet und in der Art eines Bands an dem Innenkern 46 angeordnet. Die Gegenlager 54a, 54b können dabei einstückig mit dem Innenkern 46 verbunden sein oder es kann sich um getrennte Teile handeln, welche an dem Innenkern 46 fixiert sind.On the inner core 46, a first counter bearing 54a and a second counter bearing 54b are arranged in the embodiment shown. These abutments 54a, 54b are annular and arranged on the inner core 46 in the manner of a band. The anvils 54a, 54b may be integrally connected to the inner core 46 or may be separate parts, which are fixed to the inner core 46.

Das erste Gegenlager 54a und das zweite Gegenlager 54b weisen, wie in Figur 5 angedeutet, einen größeren Radius r1 auf als ein Oberflächenbereich 56 (Radius r2) des Innenkerns 46 außerhalb der Gegenlager 54a, 54b. Die Gegenlager 54a, 54b stehen dadurch stufenförmig über dem Oberflächenbereich 56 ab. Sie weisen jeweils einen Anlagebereich 58 auf, welcher radial beabstandet ist zu dem Oberflächenbereich 56 des Innenkerns 46.The first abutment 54a and the second abutment 54b have, as in FIG. 5 indicated, a larger radius r 1 as a surface area 56 (radius r 2 ) of the inner core 46 outside the anvil 54a, 54b. The anvils 54a, 54b are thereby stepped above the surface region 56. They each have a contact region 58, which is radially spaced from the surface region 56 of the inner core 46.

Die Gegenlager 54a, 54b sind "diskrete" Abstützungen mit einer Breite (parallel zur Achse 48), welche erheblich kleiner ist als die Gesamtlänge der Gegenwalze 24. Insbesondere ist diese Breite kleiner als 30 % der Gesamtlänge. Grundsätzlich ist es so, dass es desto vorteilhafter ist für die Krafteinleitung, je kleiner die Breite eines Gegenlagers 54a, 54b ist. Je kleiner die Breite, desto weniger wird die Beweglichkeit der Außenhülse 60 relativ zum Innenkern 46 behindert. Es ist dabei jedoch zu beachten, dass die spezifische Flächenpressung, welche auf ein Gegenlager wirkt, noch innerhalb des elastischen Bereichs des Gegenlagers liegt, so dass keine plastische Verformung stattfinden kann. Beispielsweise kann die relative Breite eines Gegenlagers bezogen auf die Gesamtlänge einer Schneidwalze oder Gegenwalze auch in einem Bereich von 0,5 % oder kleiner liegen. Die Ausdehnung ist abhängig von den speziellen Gegebenheiten der entsprechenden Rotationsschneidevorrichtung.The abutments 54a, 54b are "discrete" supports having a width (parallel to the axis 48) which is significantly smaller than the total length of the backing roll 24. More specifically, this width is less than 30% of the total length. In principle, the smaller the width of an abutment 54a, 54b, the more advantageous it is for the introduction of force. The smaller the width, the less the mobility of the outer sleeve 60 relative to the inner core 46 is hindered. It should be noted, however, that the specific surface pressure acting on an abutment is still within the elastic range of the anvil, so that no plastic deformation can take place. For example, the relative width of an abutment relative to the total length of a cutting roller or counter-roller may also be in a range of 0.5% or less. The extent depends on the specific circumstances of the corresponding rotary cutting device.

Die Gegenwalze 24 weist ferner eine Außenhülse 60 auf, an welcher die Oberfläche 34 der Gegenwalze 24 gebildet ist. Diese Oberfläche 34 ist insbesondere zylindrisch. Die Außenhülse 60 hat die Form eines Hohlzylinders. Die Schneidwalze 22 mit den Stützringen 32 wirkt auf diese Außenhülse 60.The counter-roller 24 also has an outer sleeve 60, on which the surface 34 of the counter-roller 24 is formed. This surface 34 is in particular cylindrical. The outer sleeve 60 has the shape of a hollow cylinder. The cutting roller 22 with the support rings 32 acts on this outer sleeve 60th

Die Außenhülse 60 ist an den diskreten Gegenlagern 54a, 54b abgestützt; die Außenhülse 60 ist nicht über den gesamten Oberflächenbereich 56 an dem Innenkern 46 gelagert, sondern nur über die Anlagebereiche 58 der Gegenlager 54a, 54b. Zwischen einer Innenseite 62 der Außenhülse 60 und dem Oberflächenbereich 56 des Innenkerns 46 ist ein Zwischenraum 64 gebildet. Dieser Zwischenraum 64 erlaubt eine relative Auslenkung zwischen der Außenhülse 60 und dem Innenkern 46 insbesondere über unterschiedliche elastische Verformung des Innenkerns 46 und der Außenhülse 60.The outer sleeve 60 is supported on the discrete counter bearings 54a, 54b; the outer sleeve 60 is not supported over the entire surface area 56 on the inner core 46, but only on the contact areas 58 of the abutment 54a, 54b. Between an inner side 62 of the outer sleeve 60 and the surface region 56 of the inner core 46, a gap 64 is formed. This intermediate space 64 permits a relative deflection between the outer sleeve 60 and the inner core 46, in particular via different elastic deformation of the inner core 46 and the outer sleeve 60.

Das erste Gegenlager 54a und das zweite Gegenlager 54b sind symmetrisch an dem Innenkern 46 angeordnet. Sie weisen den gleichen Abstand zu einer Mittelebene 66 der Gegenwalze 24 auf. Die Mittelebene 66 liegt dabei senkrecht zur Achse 48. Ferner weist das erste Gegenlager 54a den gleichen Abstand zu einem ersten Stirnende 68a des Innenkerns 46 (außerhalb des ersten Wellenstummels 50) auf wie das zweite Gegenlager 54b zu einem gegenüberliegenden zweiten Stirnende 68b.The first abutment 54a and the second abutment 54b are arranged symmetrically on the inner core 46. They have the same distance to a median plane 66 of the counter-roller 24. The center plane 66 is perpendicular to the axis 48. Further, the first abutment 54a has the same distance to a first end 68a of the inner core 46 (outside of the first stub shaft 50) as the second abutment 54b to an opposite second front end 68b.

Die Außenhülse 60 ist bezüglich des Innenkerns 46 fixiert. Beispielsweise ist sie über Formschlussmittel über die Gegenlager 54a, 54b an dem Innenkern 46 fixiert.The outer sleeve 60 is fixed relative to the inner core 46. For example, it is fixed on the inner core 46 via form-fitting means via the abutments 54a, 54b.

Es kann zusätzlich oder alternativ vorgesehen sein, dass die Außenhülse 60 axial eingespannt ist. Dazu sind beispielsweise gegenüberliegende Stützscheiben 70a, 70b vorgesehen, welche in der Nähe des jeweiligen ersten Stirnendes 68a und zweiten Stirnendes 68b angeordnet sind. Zwischen der jeweiligen Stützscheibe 70a, 70b und einer jeweiligen Stirnseite der Außenhülse 60 ist eine jeweilige Dichtung 72a, 72b angeordnet, wobei diese Dichtung insbesondere die Form eines O-Rings hat. Durch die jeweilige Dichtung 72a, 72b wird der Zwischenraum 64 stirnseitig an der Außenhülse 60 abgedichtet.It may additionally or alternatively be provided that the outer sleeve 60 is axially clamped. For this purpose, for example, opposite support disks 70a, 70b are provided, which are arranged in the vicinity of the respective first front end 68a and second front end 68b. Between the respective support disk 70a, 70b and a respective end face of the outer sleeve 60, a respective seal 72a, 72b is arranged, this seal in particular has the shape of an O-ring. By the respective seal 72a, 72b of the intermediate space 64 is sealed to the front side of the outer sleeve 60.

Die Stützscheiben 70a, 70b sind an dem Innenkern 46 über jeweilige Sicherungsringe 74a, 74b in einer Richtung von der Außenhülse 60 weg gehalten.The support disks 70a, 70b are retained on the inner core 46 via respective circlips 74a, 74b in a direction away from the outer sleeve 60.

Eine Höhe h des Zwischenraums 64 liegt beispielsweise im Bereich zwischen 2 µm und 100 µm je nach Anwendungsfall. Die Höhe h kann auch kleiner sein oder größer als eben erwähnt.A height h of the gap 64 is for example in the range between 2 microns and 100 microns, depending on the application. The height h can also be smaller or larger than just mentioned.

Die Gegenwalze 24 ist mit mindestens einem Gegenlager wie beschrieben versehen. Es kann alternativ oder zusätzlich vorgesehen sein, dass die Schneidwalze 22 mit einem oder mehreren Gegenlagern versehen ist. Der Aufbau und die Anordnung solcher Gegenlager an der Schneidwalze 22 ist grundsätzlich gleich wie im Zusammenhang mit der Gegenwalze 24 beschrieben.The counter-roller 24 is provided with at least one counter-bearing as described. It may alternatively or additionally be provided that the cutting roller 22 is provided with one or more abutments. The structure and arrangement of such an abutment on the cutting roller 22 is basically the same as described in connection with the counter-roller 24.

Bei einem Rotationsschneidevorgang wird die Schneidwalze 22 durch die Vorspanneinrichtung 30 gegen die Gegenwalze gepresst. Durch die Schneidkräfte wird eine Kraft auf die Gegenwalze 24 ausgeübt und auf die Schneidwalze 22 wird eine Gegenkraft ausgeübt.In a rotary cutting operation, the cutting roller 22 is pressed by the biasing means 30 against the counter roll. By the cutting forces, a force is exerted on the counter-roller 24 and on the cutting roller 22, a counter force is exerted.

Die Gegenwalze 24 ist über ihre Drehlager 40 im Bereich des ersten Wellenstummels 50 und des zweiten Wellenstummels 52 jeweils am Maschinengestell 12 eingespannt. Dies ist in Figur 6 durch die Auflagenpunkte 76a, 76b angedeutet. Durch die Schneidwalze 22 werden von Richtung der Schneidwalze her Kräfte 78 ausgeübt. Bei dem gezeigten Ausführungsbeispiel wirken diese Kräfte 78 bezogen auf die Schwerkraftrichtung g von oben. Diese Kräfte 78 bewirken eine Durchbiegung der Gegenwalze 24 (vor allem des Innenkerns 46) nach unten.The counter-roller 24 is clamped via its rotary bearings 40 in the region of the first stub shaft 50 and the second stub shaft 52 on the machine frame 12, respectively. This is in FIG. 6 indicated by the support points 76a, 76b. By the cutting roller 22 forces 78 are exerted from the direction of the cutting roller ago. In the embodiment shown, these forces 78 act with respect to the direction of gravity g from above. These forces 78 cause a deflection of the counter roll 24 (especially the inner core 46) down.

In Figur 6 ist ein Diagramm für eine Gegenwalze mit einem Durchmesser von 50 mm gezeigt, bei dem die Auslenkung dy des Innenkerns 46 über die Länge 1 der Gegenwalze 24 gezeigt ist. Es wurden dabei Schneidkräfte in der Größenordnung 125 N/mm ausgeübt.In FIG. 6 is a diagram for a counter-roller having a diameter of 50 mm, in which the deflection dy of the inner core 46 over the length 1 of the counter-roller 24 is shown. In this case, cutting forces in the order of 125 N / mm were exercised.

Man erkennt, dass in einem mittleren Bereich der Gegenwalze 24 der Innenkern 46 eine Auslenkung in der Größenordnung von 22 µm nach unten erfährt.It can be seen that in a middle region of the counter-roller 24, the inner core 46 undergoes a deflection of the order of magnitude of 22 μm downwards.

In Figur 7 ist die Schneidwalze 22 gezeigt mit einem Wellenstummel 80a und einem Wellenstummel 80b. Durch die Vorspanneinrichtung 30 wird eine Kraft in Richtung der Gegenwalze 24 ausgeübt. Bei dem gezeigten Ausführungsbeispiel ist dies eine Kraft parallel zur Schwerkraftrichtung g. Die Schneidwalze 22 ist dabei nach oben hin eingespannt. Dies ist in Figur 7 durch Auflagepunkte 82a, 82b angedeutet.In FIG. 7 the cutting roller 22 is shown with a stub shaft 80a and a stub shaft 80b. By the biasing means 30, a force is exerted in the direction of the counter roll 24. In the embodiment shown, this is a force parallel to the direction of gravity g. The cutting roller 22 is clamped at the top. This is in FIG. 7 indicated by support points 82a, 82b.

Aufgrund der wirkenden Kräfte und insbesondere der Reaktionskräfte der Gegenwalze 24 wird die Schneidwalze 22 nach oben gebogen. Insbesondere wird ein Innenkern der Schneidwalze 22, wenn diese einen solchen Innenkern aufweist, nach oben gebogen.Due to the forces acting and in particular the reaction forces of the counter roll 24, the cutting roller 22 is bent upwards. In particular, an inner core of the cutting roller 22, when having such an inner core, bent upwards.

In Figur 7 ist ein Diagramm für die Auslenkung der Schneidwalze bzw. eines Innenkerns der Schneidwalze über der Länge I der Schneidwalze 22 gezeigt. Die Daten entsprechen einer Schneidwalze mit einem Durchmesser von 40 mm mit wirkenden Schneidkräften von 125 N/mm.In FIG. 7 2, a diagram is shown for the deflection of the cutting roller or of an inner core of the cutting roller over the length I of the cutting roller 22. The data correspond to a cutting roller with a diameter of 40 mm with acting cutting forces of 125 N / mm.

Man erkennt, dass im mittleren Bereich der Schneidwalze 22 eine Auslenkung nach oben von ca. 40 µm vorliegt.It can be seen that in the central region of the cutting roller 22 there is an upward deflection of approximately 40 μm.

Wenn man die Figuren 6 und 7 vergleicht, dann liegt bezogen auf die entsprechenden Innenkerne der Schneidwalze 22 und der Gegenwalze 24 im mittleren Bereich eine relative Auslenkung von gegenüberliegenden Oberflächenbereichen der Schneidwalze 22 und der Gegenwalze 24 vor, wenn diese Oberflächenbereiche der Durchbiegung der Innenkerne folgen würde, von ca. 60 µm vor. Solche Auslenkungen, wenn sie an der Oberfläche der Gegenwalze 24 und der Schneidwalze 22 vorliegen, beeinträchtigen die Qualität des Schneidergebnisses.If you have the FIGS. 6 and 7 compares, then based on the corresponding inner cores of the cutting roller 22 and the counter-roller 24 in the central region, a relative deflection of opposite surface areas of the cutting roller 22 and the counter-roller 24 before, if these surface areas would follow the deflection of the inner cores, of about 60 microns before , Such deflections, when present on the surface of mating roll 24 and cutting roll 22, compromise the quality of the cutting result.

Diese störenden Auslenkungen an den Oberflächen sind insbesondere desto größer, desto länger die Schneidwalze 22 und die Gegenwalze 24 sind und je geringer der Durchmesser dieser Walzen ist.In particular, these disturbing deflections on the surfaces are the greater, the longer the cutting roller 22 and the counter-roller 24 are and the smaller the diameter of these rollers.

Bei der erfindungsgemäßen Lösung stützt sich die Außenhülse 60 über die Gegenlager 54a, 54b an dem Innenkern 46 ab. (Diese Abstützung kann sowohl für die Schneidwalze 22 als auch für die Gegenwalze 24 oder nur für die Schneidwalze 22 oder nur für die Gegenwalze 24 vorgesehen sein.) Es lassen sich dadurch Kräfte beim Schneidvorgang und insbesondere Schneidkräfte definiert einleiten und ableiten. Über die Gegenlager 54a, 54b lassen sich Schneidkräfte von der Außenhülse 60 in den Innenkern 46 einleiten und dadurch über die entsprechenden Drehlager 26 bzw. 40 ableiten.In the solution according to the invention, the outer sleeve 60 is supported on the inner core 46 via the counter bearings 54a, 54b. (This support can be provided both for the cutting roller 22 and for the counter-roller 24 or only for the cutting roller 22 or only for the counter-roller 24.) It can thereby initiate defined forces during the cutting process and in particular cutting forces and derived. Cutting forces can be introduced from the outer sleeve 60 into the inner core 46 via the abutments 54a, 54b and thereby derive via the corresponding pivot bearings 26 and 40, respectively.

Bei entsprechender Anordnung des mindestens einen Gegenlagers lässt es sich dadurch erreichen, dass die Außenhülse 60 weniger stark gebogen wird als der entsprechende Innenkern 46. Dies ist stark übertrieben in Figur 8 angedeutet. Durch die Schneidkräfte erfährt der Innenkern 46 eine elastische Verformung und insbesondere Durchbiegung. Auch die Außenhülse 60 erfährt grundsätzlich eine elastische Verformung und Durchbiegung. Durch die Abstützung der Außenhülse 60 an den Gegenlagern 54a, 54b mit der definierten Krafteinleitung lässt sich die Verformung der Außenhülse 60 erheblich geringer halten als die des Innenkerns 46. Dadurch erhält man bei dem Aufbau von Schneidkräften eine relative Auslenkung bzw. relative Bewegung zwischen der Außenhülle 60 und dem Innenkern 46. Wenn die Außenhülse 60 weniger stark durchbogen ist als der Innenkern 46, dann ist bezogen auf den Ausgangspunkt ohne wirkende Schneidkräfte die Oberfläche 34 der Außenhülse 60 (wenn es sich um die Außenhülse der Gegenwalze 24 handelt) weniger stark durchgebogen als der Innenkern 46. Dadurch ist die Abweichung der Oberfläche 34 der Außenhülse 60 von der "Ideallinie" weniger stark, als wenn keine diskreten Gegenlager 54a, 54b vorgesehen werden. Dadurch wiederum ist die relative Auslenkung der Oberfläche 34 zu der Schneidwalze 22 weniger stark und man erhält bessere Schneidergebnisse. Insbesondere lassen sich dadurch auch längere Gegenwalzen 24 mit geringerem Durchmesser einsetzen.With an appropriate arrangement of the at least one thrust bearing, it can be achieved that the outer sleeve 60 is bent less strong than the corresponding inner core 46. This is greatly exaggerated in FIG. 8 indicated. By the cutting forces of the inner core 46 undergoes elastic deformation and in particular deflection. The outer sleeve 60 also experiences an elastic deformation and deflection. By supporting the outer sleeve 60 on the abutments 54a, 54b with the defined force introduction, the deformation of the outer sleeve 60 can be significantly lower than that of the inner core 46. This results in the construction of cutting forces a relative deflection or relative movement between the outer shell 60 and the inner core 46. If the outer sleeve 60 is less arcuate than the inner core 46, then with respect to the starting point without acting cutting forces, the surface 34 of the outer sleeve 60 (when it comes to the outer sleeve of the backing roll 24) less deflected than the inner core 46. As a result, the deviation of the surface 34 of the outer sleeve 60 from the "ideal line" is less strong than if no discrete counter bearings 54a, 54b are provided. In turn, the relative deflection of the surface 34 to the cutting roller 22 is less strong and gives better cutting results. In particular, thereby longer counter-rollers 24 can be used with a smaller diameter.

Die beschriebenen Vorteile sind auch vorhanden, wenn die Schneidwalze 22 mit einer Außenhülse über diskrete Gegenlager an dem entsprechenden Innenkern gelagert ist. Wenn auch die Schneidwalze 22 mit der erfindungsgemäßen Lösung versehen wird, dann erhält man eine insgesamt geringere relative Auslenkung der Oberflächen der Schneidwalze 22 und der Gegenwalze 24.The advantages described are also present when the cutting roller 22 is mounted with an outer sleeve on discrete counter-bearing on the corresponding inner core. If the cutting roller 22 is provided with the solution according to the invention, then one obtains an overall lower relative deflection of the surfaces of the cutting roller 22 and the counter-roller 24th

Je nach Anwendungsfall und insbesondere Ausbildung der Schneidwalze 22 sind ein oder mehrere Gegenlager vorgesehen. Diese Gegenlager sind so angeordnet und ausgebildet, dass sich ein symmetrischer Kraftfluss an der Schneidwalze 22 bzw. der Gegenwalze 24 ergibt. Der Kraftfluss ist dabei insbesondere symmetrisch zu der Mittelebene 66.Depending on the application and in particular the formation of the cutting roller 22, one or more abutments are provided. These counter-bearings are arranged and designed such that a symmetrical force flow results on the cutting roller 22 or the counter-roller 24. The power flow is in particular symmetrical to the center plane 66.

Durch die erfindungsgemäße Lösung erhält man eine definierte Kraftflussableitung an der Gegenwalze 24 und/oder der Schneidwalze 22. Die Außenhülse 60 lässt sich dadurch weniger stark elastisch verformen als der entsprechende Innenkern 46. Dadurch wiederum sind Oberflächenbereiche 84 der Schneidwalze 22 (wenn diese mit einem oder mehreren Gegenlagern versehen ist) und/oder der Gegenwalze 24 (wenn diese mit einem oder mehreren Gegenlagern versehen ist) weniger stark verformt, als wenn die Außenhülse 60 "vollflächig" an dem Innenkern 46 sitzt bzw. überhaupt keine Außenhülse vorgesehen ist.The outer solution 60 can be characterized less deform elastically than the corresponding inner core 46. This in turn are surface areas 84 of the cutting roller 22 (if this with one or provided with a plurality of counter-bearings) and / or the counter-roller 24 (if this is provided with one or more abutments) deformed less than when the outer sleeve 60 "full-surface" sits on the inner core 46 or no outer sleeve is provided.

Die Rotationsschneidevorrichtung 10 ist beispielsweise so ausgebildet, dass an der Schneidwalze 22 Schneiden angeordnet sind, welche in einer Längsrichtung (bezogen auf eine Längsrichtung 86 (Figur 1) zum Transport von Material 44) angeordnet sind und in einer Querrichtung dazu.The rotary cutting device 10 is designed, for example, such that cutting edges are arranged on the cutting roller 22 which are arranged in a longitudinal direction (relative to a longitudinal direction 86 (FIG. FIG. 1 ) for transporting material 44) and in a transverse direction thereto.

Ein zweites Ausführungsbeispiel einer erfindungsgemäßen Rotationsschneidevorrichtung, welches in Figur 9 gezeigt ist und dort mit 88 bezeichnet ist, umfasst ein Maschinengestell 90, an dem grundsätzlich gleich wie oben beschrieben eine Schneidwalze 92 und eine Gegenwalze 94 jeweils drehbar gelagert sind. Die Gegenwalze 94 ist grundsätzlich gleich ausgebildet wie die Gegenwalze 24 wie oben beschrieben.A second embodiment of a rotary cutting device according to the invention, which in FIG. 9 is shown and designated therein by 88, comprises a machine frame 90 on which basically the same as described above, a cutting roller 92 and a counter-roller 94 are each rotatably mounted are. The counter-roller 94 is basically the same design as the counter-roller 24 as described above.

Die Schneidwalze 92 ist beispielsweise über einen Antrieb (in der Zeichnung nicht gezeigt) angetrieben. An einem Wellenstummel 96 der Schneidwalze ist ein Zahnrad 98 angeordnet, welches in ein Zahnrad 100 eingreift, das drehfest bezüglich der Gegenwalze 94 fixiert ist. Dadurch kann über Antrieb der Schneidwalze 92 auch die Gegenwalze 94 angetrieben werden.The cutting roller 92 is driven by, for example, a drive (not shown in the drawing). At a stub shaft 96 of the cutting roller, a gear 98 is arranged, which engages in a gear 100 which is fixed in rotation with respect to the counter-roller 94. As a result, the counter-roller 94 can also be driven by driving the cutting roller 92.

Die Schneidwalze 92 weist einen ersten Walzenbereich 102a und einen zweiten Walzenbereich 102b auf, wobei diese beiden Walzenbereiche 102a, 102b beabstandet zueinander sind. An dem ersten Walzenbereich 102a und dem zweiten Walzenbereich 102b ist jeweils eine Mehrzahl von Querschneiden 104 angeordnet. Diese Querschneiden sind gleichmäßig verteilt angeordnet. Beispielsweise sind sie in einem Winkel von 120° (bezogen auf einen Querschnitt) beabstandet.The cutting roller 92 has a first roller portion 102a and a second roller portion 102b, wherein these two roller portions 102a, 102b are spaced from each other. At the first roll portion 102a and the second roll portion 102b, a plurality of cross cutters 104 are respectively disposed. These cross cutters are evenly distributed. For example, they are spaced at an angle of 120 ° (relative to a cross section).

Die Querschneiden 104 weisen eine Schneidfläche 106 auf, welche quer und insbesondere senkrecht zu einer Transportrichtung von Material durch die Rotationsschneidevorrichtung 88 ist. Insbesondere sind die Schneidflächen 106 parallel zu einer Drehachse 108 der Schneidwalze 92 orientiert.The transverse cutting edges 104 have a cutting surface 106, which is transverse and in particular perpendicular to a direction of transport of material through the rotary cutting device 88. In particular, the cutting surfaces 106 are oriented parallel to a rotational axis 108 of the cutting roller 92.

In einem mittleren Bereich jeweils des ersten Walzenbereichs 102a und des zweiten Walzenbereichs 102b ist ein Gegenlager 110a, 110b angeordnet. Das Gegenlager 110a, 110b ist dabei grundsätzlich gleich ausgebildet wie oben beschrieben. Insbesondere handelt es sich um ringförmige Bereiche, welche an einem jeweiligen Innenkern 112 der Schneidwalze 92 angeordnet sind.In a central region of each of the first roller portion 102a and the second roller portion 102b, an abutment 110a, 110b is arranged. The anvil 110a, 110b is basically the same design as described above. In particular, these are annular regions which are arranged on a respective inner core 112 of the cutting roller 92.

Die Gegenwalze 94 weist ebenfalls einen Innenkern 114 auf, an welchem beabstandete Gegenlager 116a, 116b angeordnet sind. Insbesondere sind die Gegenlager 116a, 116b auf die Gegenlager 110a, 110b ausgerichtet und direkt gegenüberliegend positioniert, so dass eine direkte Krafteinleitung an den Gegenlagern möglich ist. Das Gegenlager 116a steht dann dem Gegenlager 110a gegenüber und das Gegenlager 116b steht dem Gegenlager 110b gegenüber.The counter-roller 94 also has an inner core 114, on which spaced abutments 116a, 116b are arranged. In particular, the counter bearings 116a, 116b are aligned with the counter bearings 110a, 110b and positioned directly opposite one another, so that a direct introduction of force to the counter bearings is possible. The counter bearing 116a is then the counter bearing 110a opposite and the abutment 116b is opposite the abutment 110b.

Ansonsten funktioniert die Rotationsschneidevorrichtung 88 wie oben beschrieben.Otherwise, the rotary cutter 88 functions as described above.

Bei einem dritten Ausführungsbeispiel einer Rotationsschneidevorrichtung, welche in Figur 11 gezeigt und dort mit 118 bezeichnet ist, ist ein Maschinengestell 120 vorgesehen. An dem Maschinengestell 120 ist ein erstes Drehlager 122 für eine Gegenwalze 124 angeordnet. Ferner ist an dem Maschinengestell 120 beabstandet zu dem ersten Drehlager 122 beispielsweise oberhalb desselben ein zweites Drehlager 126 angeordnet. Über dieses zweite Drehlager 126 ist eine Schneidwalze 128 drehbar gelagert. Die Schneidwalze 128 und die Gegenwalze 124 sind dadurch jeweils nicht zweiseitig an dem Maschinengestell 120 gelagert, sondern nur einseitig "fliegend" an dem Maschinengestell 120 gehalten.In a third embodiment of a rotary cutting device, which in FIG. 11 shown and designated there by 118, a machine frame 120 is provided. On the machine frame 120, a first pivot bearing 122 is arranged for a counter-roller 124. Furthermore, a second pivot bearing 126 is arranged on the machine frame 120 at a distance from the first pivot bearing 122, for example above it. About this second pivot bearing 126, a cutting roller 128 is rotatably mounted. The cutting roller 128 and the counter roller 124 are thereby not each two-sided mounted on the machine frame 120, but held only on one side "flying" on the machine frame 120.

Die Schneidwalze 128 weist beispielsweise gegenüberliegende Stützringe 130a, 130b auf. Über diese Stützringe 130a, 130b stützt sich die Schneidwalze 128 an einer Oberfläche 132 der Gegenwalze 124 ab. Es ist auch eine Ausführung ohne Stützring möglich.The cutting roller 128 has, for example, opposing support rings 130a, 130b. About these support rings 130a, 130b, the cutting roller 128 is supported on a surface 132 of the backing roll 124 from. It is also a version without support ring possible.

Die Schneidwalze 128 ist mit Schneiden 134 versehen. Die Schneiden 134 sind angepasst an das zu schneidende Material ausgebildet.The cutting roller 128 is provided with cutting edges 134. The blades 134 are adapted to the material to be cut.

Die Gegenwalze 124 und die Schneidwalze 128 weisen jeweils, wie oben beschrieben, einen Innenkern und jeweilige Außenhülsen 136 und 138 auf. Die Außenhülse 138 der Schneidwalze 128 ist dabei über ein einziges Gegenlager 140 an dem entsprechenden Innenkern der Schneidwalze 128 abgestützt. Die Außenhülse 136 der Gegenwalze 124 ist über ein Gegenlager 142 an dem Innenkern der Gegenwalze 124 abgestützt. Die Gegenlager 140 und 142 liegen direkt gegenüber, um eine direkte Krafteinleitung zu ermöglichen.Counter roll 124 and cutting roll 128 each have an inner core and respective outer sleeves 136 and 138 as described above. The outer sleeve 138 of the cutting roller 128 is supported via a single abutment 140 on the corresponding inner core of the cutting roller 128. The outer sleeve 136 of the counter-roller 124 is supported via an abutment 142 on the inner core of the counter-roller 124. The abutments 140 and 142 are directly opposite to allow a direct application of force.

Ansonsten funktioniert die Rotationsschneidevorrichtung 118 wie oben beschrieben.Otherwise, the rotary cutter 118 functions as described above.

Claims (22)

  1. Rotary cutting device, comprising a machine frame (12; 90; 120), a cutting roll (22; 92; 128) rotatably mounted on the machine frame (12; 90; 120), and a mating roll (24; 94; 124) rotatably mounted on the machine frame (12; 90; 120), wherein the cutting roll (22; 92; 128) and/or the mating roll (24; 94; 124) comprise an inner core (46) and an outer sleeve (60) disposed around the inner core (46), characterized in that the outer sleeve (60) is spaced from the inner core (46), that on the inner core (46) there are disposed pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142), on which the outer sleeve (60) is supported, an intermediate space (64) being formed between adjacent pressure bearings (54a, 54b), and in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in a way that allows forces, which the cutting roll (22; 92; 128) and mating roll (24; 94; 124) exert on one another, to be dissipated in a defined manner by means of the pressure bearings on the mating roll and/or cutting roll, the width of a pressure bearing (54a, 54b, 110a, 110b; 116a, 116b; 140; 142) being smaller than 30% of the total length of the cutting roll (22; 92; 128) or mating roll (24; 94; 124),
  2. Rotary cutting device according to claim 1, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that the outer sleeve (60) is movable by elastic deformation relative to the inner core (46) .
  3. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that during the cutting operation a bowing of the outer sleeve (60) is smaller than a bowing of the inner core (46).
  4. Rotary cutting device according to one of the preceding claims, characterized in that outside of the pressure bearings between the outer sleeve (60) and the inner core (46) an intermediate space (64) is formed.
  5. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed and configured in such a way that there arises at the cutting roll (22) and/or mating roll (24) during the cutting operation an at least approximately symmetrical distribution of the flow of force in relation to the cutting roll length and/or mating roll length.
  6. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) surround an annular region that is disposed on the inner core (46) .
  7. Rotary cutting device according to claim 6, characterized in that a width of the annular region is at most 30% of the total length of the mating roll (24) and/or cutting roll (22).
  8. Rotary cutting device according to one of the preceding claims, characterized in that the outer sleeve (60) is fixed on the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142).
  9. Rotary cutting device according to one of the preceding claims, characterized in that at least one seal (72a, 72b) is disposed between the outer sleeve (60) and the inner core (46).
  10. Rotary cutting device according to claim 9, characterized in that the at least one seal (72a, 72b) is disposed on the end face of the outer sleeve (60).
  11. Rotary cutting device according to one of the preceding claims, characterized in that the pressure bearings (54a, 54b; 110a, 110b; 116a, 116b; 140; 142) are disposed symmetrically on the cutting roll (22) and/or mating roll (24).
  12. Rotary cutting device according to one of the preceding claims, characterized in that one or more cutting edges are disposed on the outer sleeve of the cutting roll (22).
  13. Rotary cutting device according to one of the preceding claims, characterized in that, where the cutting roll (128) and the mating roll (124) are each provided with pressure bearings (140; 142), pressure bearings (140, 142) lie opposite one another.
  14. Rotary cutting device according to one of the preceding claims, characterized in that the cutting roll (22) is supported on the mating roll (24) by means of at least one supporting ring (32).
  15. Rotary cutting device according to claim 14, characterized in that a first supporting ring and a second supporting ring are provided, wherein the pressure bearings are disposed on the mating roll (24) and/or cutting roll (22) between the first supporting ring and the second supporting ring.
  16. Rotary cutting device according to one of the preceding claims, characterized in that the mating roll (24) is rotatably mounted.
  17. Rotary cutting device according to one of the preceding claims, characterized in that the cutting roll (22) is mounted at two ends on the machine frame (12).
  18. Rotary cutting device according to claim 17, characterized in that the mating roll (24) is mounted at two ends on the machine frame (12).
  19. Rotary cutting device according to one of claims 1 to 16, characterized in that the cutting roll (128) is mounted at one end on the machine frame (120).
  20. Rotary cutting device according to claim 19, characterized in that the mating roll (124) is mounted at one end on the machine frame (120).
  21. Rotary cutting device according to one of the preceding claims, characterized in that one or more transverse cutting edges (104) are disposed on the cutting roll (92).
  22. Rotary cutting device according to one of the preceding claims, characterized in that one or more longitudinal cutting edges (134) are disposed on the cutting roll (128).
EP20080152648 2007-03-30 2008-03-12 Rotary cutting device Active EP1974878B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710016451 DE102007016451A1 (en) 2007-03-30 2007-03-30 A rotary knife

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EP1974878A1 EP1974878A1 (en) 2008-10-01
EP1974878B1 true EP1974878B1 (en) 2010-11-24

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US (2) US20080237386A1 (en)
EP (1) EP1974878B1 (en)
AT (1) ATE489207T1 (en)
DE (2) DE102007016451A1 (en)

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US20080237386A1 (en) 2008-10-02
DE102007016451A1 (en) 2008-10-02
US20130036889A1 (en) 2013-02-14
DE502008001855D1 (en) 2011-01-05
EP1974878A1 (en) 2008-10-01
ATE489207T1 (en) 2010-12-15

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