EP1101721A1 - Corps rotatif pour la correction de la largeur d'une bande - Google Patents

Corps rotatif pour la correction de la largeur d'une bande Download PDF

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Publication number
EP1101721A1
EP1101721A1 EP00810878A EP00810878A EP1101721A1 EP 1101721 A1 EP1101721 A1 EP 1101721A1 EP 00810878 A EP00810878 A EP 00810878A EP 00810878 A EP00810878 A EP 00810878A EP 1101721 A1 EP1101721 A1 EP 1101721A1
Authority
EP
European Patent Office
Prior art keywords
web
body structure
jacket
areas
rotary body
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.)
Granted
Application number
EP00810878A
Other languages
German (de)
English (en)
Other versions
EP1101721B1 (fr
Inventor
Robert Langsch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wifag Maschinenfabrik AG
Original Assignee
Wifag Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Priority to JP2000348866A priority Critical patent/JP2001192158A/ja
Publication of EP1101721A1 publication Critical patent/EP1101721A1/fr
Application granted granted Critical
Publication of EP1101721B1 publication Critical patent/EP1101721B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H23/00—Registering, tensioning, smoothing or guiding webs
    • B65H23/02—Registering, tensioning, smoothing or guiding webs transversely
    • B65H23/032—Controlling transverse register of web
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2301/00—Handling processes for sheets or webs
    • B65H2301/50—Auxiliary process performed during handling process
    • B65H2301/51—Modifying a characteristic of handled material
    • B65H2301/512—Changing form of handled material
    • B65H2301/5122—Corrugating; Stiffening
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/11—Details of cross-section or profile
    • B65H2404/112—Means for varying cross-section
    • B65H2404/1121—Means for varying cross-section for changing diameter
    • B65H2404/11211—Means for varying cross-section for changing diameter by inflation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/12—Rollers with at least an active member on periphery
    • B65H2404/122—Rollers with at least an active member on periphery rotated around an axis parallel to the roller axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/131—Details of longitudinal profile shape
    • B65H2404/1316—Details of longitudinal profile shape stepped or grooved
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/13—Details of longitudinal profile
    • B65H2404/132—Details of longitudinal profile arrangement of segments along axis
    • B65H2404/1321—Segments juxtaposed along axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/10—Size; Dimensions
    • B65H2511/12—Width
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/10—Size; Dimensions
    • B65H2511/17—Deformation, e.g. stretching
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2511/00—Dimensions; Position; Numbers; Identification; Occurrences
    • B65H2511/20—Location in space
    • B65H2511/21—Angle
    • B65H2511/212—Rotary position

Definitions

  • the invention relates to a rotating body structure and a method for a Web width correction between two printing points of a rotary printing press.
  • the Printing machine is preferably a machine that works in wet printing, in particular an offset printing machine and particularly preferably an Web rotary printing machine.
  • One way of correction as described, for example, in DE 195 16 368 C2 is the axial adjustment of pressure plates of plate cylinders, which the transfer the respective print images to the printing cylinders of the printing column.
  • EP 0 838 420 A2 is a device for correcting the fan-out Effect on web-fed rotary printing presses, with which the web is transverse to their Direction of travel is undulated before it enters a subsequent pressure nip comes in.
  • the web is in the device between two groups of rolls passed through. The roles of one group are offset transversely to the web running direction the roles of the other group.
  • the web is the undulating course embossed and thereby the web width for printing in the subsequent printing nip decreased.
  • Comparable devices are known from DE 43 27 646 A1. This publication discloses correction devices arranged on both sides of the web Formed bodies of revolution and also devices with only one side of the web arranged rotary body structures with which the web transverse to its direction is deformed in a wave shape.
  • the web becomes straight through a number of printing sections guided, between each of which a web width correction device is arranged.
  • This comprises a number of circumferential projections laterally spaced apart from one another in Form of rings or brush bodies. Arrived due to the linear path the track only in contact with the circumferential projections. Between the circumferential projections the path is guided freely.
  • WO 99/40006 A1 discloses a guide roller for correcting the lateral position on webs or also of longitudinal folds. These guide rollers are used after printing on the web used, the web can also loop around the guide roller.
  • the guide roller points at least two, variable in diameter, outer, i.e. Expanding elements close to the shaft journal, which are pressurized to expand become.
  • guide rollers are known not to be used to correct the FAN-OUT Effect used.
  • the web is at the deforming Rotary body structures passed, with a decisive contact with the web first as a result of a web width correction is required.
  • the Rotational body structures moved into the path of the web.
  • This type of Web width correction inevitably becomes the web length between the printing nips changed. Circumferential register errors occur when printing in the subsequent printing nip, or circumferential register corrections are matched to the web width correction required.
  • the invention relates to a body of revolution for a web width correction between an upstream pressure gap and a downstream pressure gap one Rotary printing press, which is preferably a newspaper offset web-fed rotary printing press is.
  • a continuous web is printed one after the other.
  • the body of revolution is one the two sides of the web arranged and rotatable in the direction of web travel. It points in axial Direction alternately juxtaposed radially protruding and radially recessed Jacket areas to deform the web wavy transverse to its direction.
  • the rotary body structure is according to the invention in a path of the path between the arranged upstream pressure gap and the downstream pressure gap, or it is the web guided on its way between the pressure gaps in such a way that the web Rotary body structures in the protruding jacket areas and in the rear Constantly wraps around the jacket areas, d. H. the web touched throughout Print production not only always the above jacket areas, but also always the recessed jacket areas. This ensures that the web is kept straight guaranteed at all times.
  • a web for web width correction is not on one for this provided provided rotating body structure that for the purpose of Web width correction would have to be moved into the web path.
  • the web continuously wraps around the body of revolution.
  • Rotational body structures always deflect the web.
  • the train wraps around it Body of revolution by at least 3 °, i.e. it is created by the body of rotation always deflected by at least 3 °.
  • a higher degree of wrap of about 5 ° or more is preferred.
  • the rotary body structure is advantageous by 10 ° or more entwined.
  • the wrap angle can be up to 180 °.
  • such a body of revolution can be made by a single Rotational body are formed, the protruding jacket areas and the has recessed jacket areas as an unchangeable surface shape.
  • the There has been a fixed arrangement of such a rotating body which can be rotated as a whole Surprisingly, it has already been shown to be sufficient to widen the web to be brought back so clearly that further web width corrections can be achieved a sufficiently good passport in the transverse direction is not required. You can Adjustments for the width correction depending on the type of paper, for example and / or the web speed via targeted, minor changes in the Longitudinal path tension can be achieved.
  • Such a rotating body is preferably on it Wavy surface in the longitudinal direction, particularly preferred with continuous merging concave and convex or arched back and forth Jacket areas.
  • the web always lies on its entire body on such a rotating body Spread out.
  • the amplitude of the corrugated surface and preferably also the radial Distance between the protruding and recessed jacket areas of the others Embodiments are preferably between 0.2 and 3 mm, preferably it is about 2 mm.
  • the above jacket areas are relative to the recessed jacket areas radially movable. This allows the area of Width correction can be enlarged, for example in adaptation to different Paper qualities, web speeds or also in adaptation to different ones Pressure assignments of the web and the associated different humidifications. Because of the invention between the above jacket areas and the Relative movement taking place in the rear cladding regions are varying Web width corrections alone with only one side of the web, Rotational body structures according to the invention possible.
  • Relative movements between the projecting and the projecting jacket areas are preferably to maintain a constant path length between the upstream and downstream pressure gap compensated.
  • the above jacket areas and the recessed jacket areas in a neutral position of the body of revolution a common neutral position axis of rotation.
  • the above jacket areas are relative to the Neutral position axis moves towards the web, and the recessed jacket areas are mirror-symmetrical in relation to the neutral axis of rotation opposite direction moved away from the web. Because of the symmetrical The adjustment remains the middle path between the upstream and the downstream pressure point despite the adjustment of the same or changes in relation to the circumferential register at most in a practical, i.e. for print quality, not relevant extent.
  • the protruding jacket areas and the recessed jacket areas in relation to be adjusted asymmetrically in opposite directions on the neutral axis of rotation refers with such an asymmetrical adjustment, the above jacket areas in to a lesser extent with respect to the neutral axis of rotation towards the web moved as the recessed cladding areas with respect to the Neutral axis of rotation are moved away from the web.
  • the protruding jacket areas among themselves and the recessed jacket areas also moved among themselves to the same extent in the adjustment.
  • the symmetrical or asymmetrical adjustment can be done for example by radial Widening of the protruding jacket areas and radial contraction of the protruding ones Jacket areas are effected.
  • the above jacket areas are preferred through a group of pivoted first rollers and the rear ones Shell areas formed by a group of rotatably mounted second rollers.
  • the rotary body structure comprises one Roller body with eccentric sleeves arranged on it in a rotationally fixed manner, on which cylinder sleeves are each independently pivoted.
  • the eccentric sleeves are preferably alternately designed differently in the axial direction of the roller body, so that by simple rotation of the roller body, the cylinder sleeves to and from the web the web can be moved to, preferably alternating, protruding and to form recessed jacket areas.
  • the rotary body structure is a roller with projecting jacket areas that cannot be moved in the radial direction with respect to an axis of rotation of the roller, and with protruding ones that can be pressed relative to it Jacket areas.
  • Rotary body structures in a rotating magazine By turning the magazine around a magazine axis of rotation, one of the rotating body structures is optionally in one Brought to work position, while the other or the rotating body structure of the Rotary magazine are in a rest position or in rest positions, in or in which they do not affect the web. Only the one in the working position Rotational body structures are wrapped in the web in the manner according to the invention.
  • the swivel arm length formed by the rotating magazine can for each of the Rotary body structures of the rotary magazine be the same.
  • Rotary body structures for example, each with a rotational body structure unchangeable surface shape and becomes the amplitude of the lateral surface wave symmetrical about their neutral line of rotational body structures
  • Rotary bodies vary, so changes from rotary bodies to Rotational body structures the ripple impressed on the web and thus the set one Web width, but still the middle path remains the same.
  • the rotational body structure which in one print production is used for web width correction, in another print production can be used as a pure deflection device for a web that either only in the upstream printing nip or only in the first Print production downstream printing gap is printed.
  • Rotational body structures designed for the advantageous dual use so that the protruding and recessed cladding areas if they are relative to each other are movable, can be brought to a height in relation to the web, so that the Rotational body structure of the web offers a smooth, straight-cylindrical outer surface. If the protruding jacket areas crowned, d. H. permanently arched, are shaped, as may be the case according to the invention, is the one based thereon Ripple is so slight that a web width change in a practically relevant one Extent does not occur.
  • a deflection device arranged around the web of the rotating body structure to wrap according to the invention.
  • this will be Rotary body structure as a straight guide device for the subsequent pressure gap used. In this preferred use, it replaces one of the prior art required nip infeed roller.
  • Fig. 1 shows a four-high tower with four superimposed printing units, in which a web W is printed on both sides in four colors.
  • the four printing units are in the Pressure tower arranged one above the other in two H-bridges.
  • Each of the four printing units comprises two printing cylinders designed as rubber blanket cylinders with subordinate ones Plate cylinders.
  • Each of the plate cylinders transfers its print image onto its Printing cylinder, and the printing cylinder transfers it to the web W.
  • the invention is not to the printing unit design shown in H-bridges or a four-high tower and basically not limited to a tower construction either.
  • the web W passes through one after the other Pressure gap 1, the pressure gap 2, the pressure gap 3 and the pressure gap 4 and is in each the printing column 1 to 4 by the employed printing cylinder on both sides with one color each and printed with a different color in each of the printing columns 1 to 4.
  • the Printing unit with the first printing nip 1 is a feed roller and in a known manner behind the printing unit with the last printing nip 4 of the printing tower is known in Way arranged an outlet roller, which can also be designed as a pull-out roller.
  • the web W is printed using wet offset printing.
  • the web W takes moisture and swells.
  • the crosswise to the running direction of the web W measured web width increase from nip to nip, and it would in the Printing columns 1 to 4 printed images in succession in the transverse direction of the web do not match, i.e. there would be register errors in the transverse direction.
  • the Web width on the path of web W from printing nip 2 to that shown in FIG Production immediately following pressure gap 3 reduced.
  • the device comprises a rotating body structure 6, which is shown in FIG. 1 is shown simplified as a simple deflecting roller.
  • the rotary body structure 6 can actually be designed as a one-piece roller. It is preferred in Uses actually only used as a deflection roller.
  • the rotary body structure 6 is, however, in a special way educated.
  • the rotating body structure 6 is arranged and fulfilled immediately in front of the pressure gap 3 in this arrangement also the function of the linear guidance for the web W.
  • the function of the linear guidance is for the two printing units with the printing columns 3 and 4 fulfilled by the rotary body structure 6 and the pull-out roller behind the printing nip 4.
  • the web W is stretched between the rotating body structure 6 and the pull-out roller. Due to the straight guidance, the web W is passed through without wrapping the printing cylinders the two pressure gaps 3 and 4 formed between them.
  • the impression cylinders, which form the printing gaps 3 and 4 can pass from the web while the web W is passing through W swiveled or swung into the illustrated printing positions.
  • the Rotational body structure 6 thus additionally supports the so-called flying page change while production continues.
  • Deflection device arranged a simple deflection roller or another Rotational body structure 5 for the wavy deformation of the web W can be.
  • the Web W is thus not straight between the two pressure gaps 2 and 3, but deflected in order to wrap the rotary body structure 6 according to the invention receive.
  • a deflection device used here can itself be in accordance with the invention wrapped rotary body structure 5 may be formed. It is basically possible although less preferred that the rotational body structure 6 is omitted and the Path width correction solely by means of the wrapped rotating body structure 5 is made.
  • Straight guide means are preferred however, as in the exemplary embodiment, so that all pressure cylinders of the tower for a flying change of sides, i.e. during production, delivered and turned off can be
  • Fig. 1 is the alternative use of the rotating body structure 6 as pure Deflection roller indicated.
  • Rotational body structure 6 shown.
  • the in the way of the train W dem Rotary body structures 6 directly upstream deflection device 5 can be such a body of revolution.
  • FIGS. 2 to 5 A first embodiment of a rotating body structure 6 is shown in FIGS. 2 to 5 shown, always referred to in their entirety in the following description be.
  • the rotating body structure 6 has two groups of Roll on, namely a group of first roles 10 and a group of second roles 11, each pivotable on a pivot axis common to each group Machine frame are stored.
  • Fig. 2 shows the rotary body structure 6 in a longitudinal view X perpendicular to Running direction of the web W.
  • the first rollers 10 and the second rollers 11 are in the axial Direction of the body of revolution 6, i.e. transversely to the direction of web travel, alternately arranged side by side.
  • the first rollers 10 are in this alternating arrangement in the direction of the web further than the second rollers 11.
  • the lateral surfaces of the first rollers 10 form with respect to the web W protruding jacket areas A, and Shell surfaces of the second rollers 11 form in relation to the web W in comparison to the Sheath areas A recessed sheath areas B.
  • the Rotating body structure 6 wraps under tension, the web W in the transverse direction the wavy course shown in Fig. 2, with which they are embossed downstream pressure gap 3 enters.
  • the first Rollers 10 are on their outer surfaces, which in the embodiment with the above Sheath areas A are identical, crowned or domed. The web W is therefore in large areas on the rotating body structure 6.
  • the recessed jacket areas B could be curved inwards accordingly. It is sufficient however, as shown in the exemplary embodiment, a straight-cylindrical design of the second rollers 11.
  • the protruding regions A and the protruding regions B are in the radial direction of the rotating body structure 6 can be moved relative to one another to the extent of To be able to change web width reduction.
  • Fig. 2 shows the rotating body structure 6 in its extreme position, in which the protruding areas A relative to the trailing ones Project areas B furthest in the direction of web W. The ripple and that Extent of the reduction of the web width are in the extreme position of the Rotational body structure 6 largest.
  • FIGS. 3 and 4 show a plan view of the rotary body structure 6 on the web opposite side.
  • Fig. 3 shows in an axial direction of the rotating body structure 6 vertical view an adjustment device for the relative adjustment of the above Areas A and the backward areas B.
  • the rotating body structure 6 shown in the extreme position also shown in FIG. 2.
  • Fig. 4 shows that Rotary body structure 6 in a neutral position, in which the axes of rotation of all rollers 10 and 11 are in alignment and form a common neutral position axis of rotation N.
  • the above areas A stand only by the extent of their Bulging over the recessed jacket areas B in the direction of the web W. in front.
  • the extent of the protrusion in the neutral position is so small that the width of the Path W in the neutral position N is not changed by the rotating body structure 6 or is changed at most to a practically irrelevant extent.
  • the edges of the first rollers 10 and second rollers 11 are in the same neutral position Height, based on the web.
  • the movement of the rollers 10 and 11 and thus in particular of the above areas A and the backward area B from the neutral position to the extreme position or one intermediate position is axisymmetric with respect to the Neutral position axis of rotation N.
  • the above range A are made during the adjustment the neutral position always as far radially with respect to the axes of rotation of the first rollers 10 in Direction towards the web moves radially with respect to the recessed area B the axes of rotation of the second rollers 11 are moved away from the web.
  • the neutral position axis of rotation N remains in every adjustment position of the axes of rotation of the first rollers 10 and obtained in each adjustment position of the axes of rotation of the second rollers 11 as a center line.
  • the first rollers 10 are rotatably supported individually on swivel arms 18 and the second rollers 11 are rotatably supported individually on swivel arms 14.
  • the swivel levers 14 are mounted on a swivel shaft 13 and the swivel arms 18 are fastened on a swivel shaft 17 in a manner which prevents them from rotating and sliding.
  • the two pivot shafts 13 and 17 run parallel and spaced between two opposite side walls 8 and 9 of the machine frame transversely to the direction of web travel and are each rotatably mounted on the side walls 8 and 9 about their longitudinal axes.
  • the pivot arms 14 project vertically from the pivot shaft 13 and the pivot arms 18 from the pivot shaft 17 and towards one another.
  • an adjustment device with a drive M is mounted, with which the two pivot shafts 13 and 17 in opposite directions with exactly the same Angular velocity can be rotated. All swivel arms 14 and 17 are of equal length.
  • the two pivot shafts 13 and 17 are coupled to each other and to the drive M via an angular gear for synchronous adjustment in the sense described above.
  • the drive M and the angular gear form a synchronous adjustment device for the two groups of rollers 10 and 11.
  • the drive comprises a rotary motor with a control and an output shaft 19a is designed as a spindle with a fine thread.
  • the output shaft 19a is on her free end on the side wall 8 again pivoted. Runs on the spindle thread a threaded nut with a slide 19b fastened thereon.
  • On the carriage 19b a lever 12 rotatable about an axis perpendicular to the direction of travel of the slide 19 b attached.
  • the lever 12 is formed by a web that is secured against rotation on the Swivel shaft 13 and on the carriage 19b rotatable about a to the direction of travel Carriage 19b is vertical and attached to the shaft 13 parallel axis.
  • lever 12 becomes a straight movement of the slide 19b into a corresponding rotation of the shaft 13 converted.
  • a synchronous, opposite rotation of the first rollers 10 is by a lever arrangement mirror-symmetrical to the neutral position axis of rotation N and Coupling to the lever 12 by means of a rigid tab 15 causes.
  • For the Coupling is the lever 12 as seen from the carriage 19b via the pivot shaft 13 just extended out.
  • a lever 16 projects from the pivot shaft 17 on the opposite side from.
  • the free ends of the levers 12 and 16 are articulated by means of the tab 15 connected to one another such that when the lever 12 is pivoted about the Pivot axis 13 causes the lever 16 to be given away about the pivot axis 17 and at the same time the lever 16 and the extended region of the opposite of it Lever 12 always stay parallel.
  • the levers 12 and 16 have between the pivot shafts 13 and 17 and the axes of rotation with the tab 15 on the same length.
  • Swivel lever 14 perpendicular to the extended area of the lever 12 on the Swivel shaft 13 and the swivel lever 18 perpendicular to the lever 16 on the Swivel shaft 17 attached and further formed by the swivel levers 14 and 18 Swivel axes are of equal length, a with respect to the neutral position axis of rotation N pivoting the first rollers 10 and the second rollers 11 in opposite directions to the same extent causes.
  • the maximum displacement measured as the radial distance between the axes of rotation of the first rollers 10 and the axes of rotation of the second rollers 11, is 0.5 to 3 mm, preferably up to a maximum of 2 mm.
  • the diameter of the rollers 10 and 11 is between 70 and 120 mm, in the exemplary embodiment it is 90 mm.
  • the width of the rolls 10 and 11, measured in the axial direction of the rotary body structure 6, is between 30 and 70 mm, in the exemplary embodiment it is 50 mm.
  • the distance between two adjacent rolls 10 and 11 is less than the width of the rolls and is preferably less than 30 mm; in the exemplary embodiment there is a clear distance between two adjacent rolls 10 and 11 of 20 mm. The distance is for that Accommodation of the pivot levers 14 and 18 required.
  • the number and dimensions Rolls 10 and 11 are selected so that at least one complete one-quarter web width Wave crest or a complete wave trough is formed. This would be the first Design for a 4/4 wide web the case.
  • the above Areas A and backward areas B are formed in such a number that two or more complete wave crests or wave troughs are formed per 1 ⁇ 4 track width.
  • the above statements apply with regard to the geometric dimensioning analogously also in the other embodiments of the rotating body structure 6.
  • the adjustment of the above area A and the back area B, i.e. in the Embodiment of the rollers 10 and 11 forming them takes place depending on the Web tension S, web speed V, paper type T and web moisture F or one or more selected of these parameters.
  • too regulation of the drive M are used.
  • the manipulated variable directly from the target-actual deviation of the web width.
  • the web width is here via suitable sensors, either on the edges of the web, on the side mirror edge or on suitable print marks.
  • the wrap angle a is entered, which is the angular dimension of the circumferential length of the wrapped lateral surfaces of the protruding jacket areas A and protruding jacket areas B, which are hidden in Fig. 5 indicates.
  • the wrap angle a is at least 3 ° and preferably at least 10 °. in the Embodiment it is 20 °.
  • the information on the wrap angle a applies equally also for the further embodiments of the rotary body structure 6.
  • Figures 6 and 7 show a second, particularly preferred embodiment of the Rotational body structure according to the invention.
  • This comprises a roller body 61 which between a left machine frame and a right machine frame (not shown) is stored.
  • a number of eccentric sleeves 60a, 60b are on the roller body 61 non-rotatably arranged.
  • a single eccentric sleeve in the form of a comparatively long cam body be rotatably arranged on the roller body 61, with a number of different Eccentric sections in the axial direction of the roller body 61 for the storage of each Cylinder sleeves.
  • the roller body 61 itself can also be in the form of a camshaft be formed with eccentric sections formed side by side.
  • Rotary setting of the roller body 61 shown are the sections of the eccentric sleeves 60a with the largest projection above the longitudinal axis of the roller body 61 next to Portions of the eccentric sleeves 60b with the largest projection below the longitudinal axis of the Roller body 61 arranged.
  • the cylinder sleeves 62, 63 and the associated eccentric sleeves 60a, 60b are alternating designed differently, so that alternately protruding or protruding Cylinder sleeves radially projecting jacket areas A and radially projecting Sheath areas B are formed.
  • the alternating arrangement can in principle also another expedient sequence of alternating cylinder sleeves 62, 63 can be selected to suit the peripheral surface of the rotating body structure 6 To give waveform.
  • the cylinder sleeves 62, 63 are cylindrical. Alternatively, you can however, also seen in the axial direction, a concave or convex profile or alternating a different profile, e.g. have cylindrical and concave or convex.
  • the Cylinder sleeves 62, 63 can also have different surface roughnesses.
  • the body of revolution forms a straight line on its outer surface, which extends parallel to the axis of rotation of the rotary body structure. This line will by arranging the eccentric sleeves 60a and 60b in corresponding Angle of rotation positions and thicknesses of the cylinder sleeves 62 and 63 matched thereto receive.
  • the roller body 61 is rotatably adjustable for adjustment about an axis of rotation N.
  • Machine frame mounted the respective rotary setting can be locked mechanically or can be regulated in a suitable manner, for example also electronically controlled.
  • For Adjustment of the roller body 61 is an electric motor M or a drive device provided with a number of control inputs T, S, V, F, which is schematic over the illustrated non-slip spur gear or gear arrangement 64 den Roller body 61 rotated about its axis of rotation.
  • the axes of rotation of the cylinder sleeves 62 and 63 are eccentric to the axis of rotation of the Roller body 61, alternately offset by 180 °.
  • the rotation of the roller body 61 is preferably carried out continuously.
  • the jacket areas A, B move against or away from the Paper web.
  • the transition from the extremely wavy line to that takes place Smooth straight line offset by 180 °.
  • the rotary adjustment of the roller body 61 also takes place in adaptation to the Paper quality, web speed and / or print occupancy of the web is the Roller body 61.
  • the gap s which can be seen in FIG. 6, between two axially adjacent cylinder sleeves 62 and 63 is preferably kept as small as possible in order to enable optimum web guidance on the protruding or protruding jacket areas A, B.
  • a diameter ratio D1: D2 of approximately 0.9-0.98 is preferred, more preferably a diameter ratio D1: D2 of approximately 0.95.
  • a preferred aspect ratio is L1: L2 about 0.05-0.3, more preferably about 0.15.
  • D1 and L1 denote the Outer diameter and the length of the cylinder sleeves 62 and Dl and L2 the outer diameter and the length of the cylinder sleeves 63.
  • the second embodiment is particularly advantageous because it is particularly because of the simple construction can be manufactured inexpensively and is also easy to maintain because the eccentric or cylinder sleeves are individually interchangeable. If you have the Replaces cylinder sleeves with cylinder sleeves with different dimensions, for example even alternately, the rotational body structure shown can be very flexible and can be converted inexpensively. Another particular advantage is that the Adjustment while keeping the path constant only by rotating the roller body 61, i.e. of the rotating body structure 6 as a whole, about the axis of rotation N. The The axis of rotation N of the roller body 61 is at the same time the neutral position axis of rotation of the Rotational body structure 6.
  • FIG. 7 shows the rotary body structure 6 according to the second embodiment in two various rotational settings of the roller body 61, namely in the neutral position N, where the surfaces of the first cylinder sleeve 62 and the second cylinder sleeve 63 im Contact area with the paper web practically aligned, and a maximum adjustment (lower figure), where the roller body 61 is maximally rotated, so that the first Cylinder sleeves 62 have a protruding jacket area A and the second cylinder sleeves 63 form a recessed jacket area B.
  • the jacket area B is in this Adjustment position in relation to the above jacket area A is set back as far as possible.
  • Fig. 8 shows the rotary body structure 6 in a third embodiment, in which it as Roll is formed with axially compressible ring elements 20.
  • the rotary body structure 6 of the third embodiment comprises a roller body 22, which can be pivoted like known deflection rollers or by storage in eccentric bearings is pivoted on the machine frame.
  • a roller body 22 Concentrically on the roller body 22 whose axis of rotation are in the axial direction, i.e. along the axis of rotation, elastically deformable Ring elements 20 and dimensionally stable ring elements 21 alternately immediately tight arranged side by side.
  • the ring elements 20 and 21 are axially on the roller body 22 slidably and preferably arranged against rotation.
  • the extreme of Ring elements 20 and 21, which in the exemplary embodiment is a deformable ring element 20, in principle, however, can also be formed by a dimensionally stable ring element 21, presses against an axial abutment 24.
  • the pressure displacement element 23 is formed by an axial ball bearing.
  • the Pressure shifting element 23 is axially actuated by an actuating means 25 against the extreme of the ring members 20 and 21 pressed.
  • the pressure displacement element 23 has an inner bearing shell with which it presses against the outermost of the ring elements 20 and 21, and an outer bearing shell against which the actuating means 25 presses.
  • the inner one Bearing shell is rotatably but slidably mounted on the roller body 22.
  • the outer bearing shell can also be mounted on the roller body 22, in which If the actuating means 25 is rotatably supported together with the roller body 22 would.
  • the outer bearing shell is preferably rotatable and displaceable on the Roller body 22 mounted so that the actuating means 25 is attached to the machine frame can be.
  • the actuating means 25 is at an angle formed, which is rotatably mounted on a bolt 26 on the machine frame. On one at the front end the angle has a cam with which it bears against the outer Bearing shell of the pressure displacement element 23 presses and thereby axial pressure on the Ring elements 20 and 21 exercises.
  • Fig. 9 shows the rotary body structure 6 in a fourth embodiment in which it is also designed as a roller.
  • the protruding areas A also through the lateral surfaces of completely encircling, elastically deformable ring elements 30 are formed.
  • the backward areas B are by strip-shaped peripheral surfaces of a roller body 32 itself educated.
  • the roller body 32 is like known deflection rollers or by means Eccentric bearings in the machine frame.
  • Fig. 9 shows the rotary body structure 6 in its neutral position, in which the Rotary body structure has a smooth, straight, circular cylindrical outer surface.
  • the protruding areas A by acting on the deformable ring elements 30 formed with compressed air.
  • the roller body 32 is on one end face by means of a Pressure port 33 with a pressure fluid from a pressure reservoir or from one Pump can be charged.
  • the pressure fluid preferably compressed air, passes through the Pressure connection 33 in a central, axial pressure line 34, which extends over almost the extends over the entire length of the roller body 32 and from the radial pressure lines 35 branch off.
  • the radial pressure lines 34 are below the deformable ring elements 30 performed where they are in circumferential, outwardly open ring channels 36 for uniform Distribution of pressure fluid.
  • the deformable ring elements 30 seal the ring channels 36 to the outside.
  • a pressure building up in the ring channels 36 causes an Bulging of the elastically deformable ring elements 30 radially outwards, whereby the protruding jacket areas A of this rotary body structure 6 arise.
  • At Relief of pressure comes the ring elements 30 due to their own elastic Restoring forces in the neutral position.
  • FIG. 10 shows the rotary body structure 6 in one of the fourth embodiment modified fifth embodiment.
  • the main difference from the fourth Embodiment is that the deformable ring elements of the fifth Embodiment formed by hose-like, elastically expandable ring elements 40 become.
  • the deformable ring elements 40 are received in recesses 47 which are circumferentially formed on the outer surface of the roller body 42 and as in Embodiment can be formed for example by simply rectangular grooves.
  • the roller body regions protruding between the recesses 47 form on their Lateral surfaces 41 the protruding lateral regions B of the rotating body structure 6.
  • the deformable ring elements 40 are connected by a pressure connection 43, a central axial pressure line 44 and branching radial pressure lines 45 with a Pressurized fluid, preferably compressed air.
  • a Pressurized fluid preferably compressed air.
  • the application is made by Introduction of the pressure fluid into the ring hoses or elements 40, which thereby by printed on the inside and thereby expanded radially outwards.
  • the protruding jacket areas A are widened. Pull when the pressure is released the ring tubes 40 due to their own elastic restoring forces again to the level of the recessed jacket areas B, so that this too Rotational body structure 6 in its neutral position of the track a straight cylindrical, in offers a substantially smooth surface.
  • FIG. 11 shows a sixth embodiment in which the rotary body structure 6 is formed by a single roller body 52 which has a wavy outer surface.
  • the rotary body structure 6 is in this embodiment in one piece as a steel roller or as Roll formed of another suitable material. Adjusting the ripple is not possible.
  • the roller body 52 has alternately axially thicker roller regions 50 and, in contrast, thinner roller regions 51.
  • the thicker roller regions 50 form the permanently projecting jacket regions A
  • the thinner roller regions 51 form the permanently projecting jacket regions B.
  • the jacket surface of the roller body 52 is rotationally symmetrical and runs sinusoidally with an amplitude of 2 mm in each longitudinal section. In the exemplary embodiment, two adjacent wave crests converge bulging outward bulging.
  • the wave crests are only curved radially inwards in the area of the convergence, ie in their foot areas.
  • the result is a sequence of long, convex wave crests and, in contrast, shorter, concave wave troughs and rounded transitions.
  • the largest diameter D measured as the diameter between two diametrically opposed tangents to the tips of the wave crests, is 4 mm larger than the smallest diameter d, measured as the distance between two parallel tangents to the tops of the troughs.
  • the alternating sequence of protruding regions A and recessed regions B in the exemplary embodiment in FIG. 11 is such that two troughs of the roller body 52 come to lie in 1 ⁇ 4 wide strips of the web.
  • the rotary body structure 6 of FIG. 12 corresponds to that of FIG. 11 with the only exception that the sequence of preceding areas A and backward Areas B in the roll longitudinal direction by 90 ° out of phase with that of the 11 corresponds to the exemplary embodiment. This gives each of the 1 ⁇ 4 Web widths two protruding jacket areas A to lie.
EP00810878A 1999-11-16 2000-09-25 Corps rotatif pour la correction de la largeur d'une bande Expired - Lifetime EP1101721B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2000348866A JP2001192158A (ja) 1999-11-16 2000-11-15 ウェブ幅補正のための回転体構造

Applications Claiming Priority (2)

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DE19955099 1999-11-16
DE19955099A DE19955099B4 (de) 1999-11-16 1999-11-16 Rotationskörpergebilde für eine Bahnbreitenkorrektur

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EP1101721B1 EP1101721B1 (fr) 2003-08-27

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EP (1) EP1101721B1 (fr)
CN (1) CN1187191C (fr)
AT (1) ATE248116T1 (fr)
DE (2) DE19955099B4 (fr)
DK (1) DK1101721T3 (fr)
ES (1) ES2206169T3 (fr)

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EP1369369A1 (fr) 2002-06-06 2003-12-10 Maschinenfabrik Wifag Compensateur d'élargissement avec un courant d'un fluide
EP1369368A1 (fr) 2002-06-06 2003-12-10 Maschinenfabrik Wifag Elément rotatif pour régler l'élargissement d'une bande
EP1640302A2 (fr) * 2004-02-16 2006-03-29 Koenig & Bauer Aktiengesellschaft Dispositif pour influencer la largeur ou la position d'une bande
DE102005001540A1 (de) * 2005-01-13 2006-07-27 Koenig & Bauer Ag Leitwalze zur Führung einer Materialbahn
FR2964343A1 (fr) * 2010-09-07 2012-03-09 Goss Int Montataire Sa Ensemble d'impression et utilisation correspondante
EP2455315A1 (fr) * 2009-07-16 2012-05-23 Mitsubishi Heavy Industries Printing & Packaging Machinery, Ltd. Dispositif pour régler un alignement dans une direction dans le sens de la largeur, et machine d'impression

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DE10340569A1 (de) * 2003-09-01 2005-04-07 Koenig & Bauer Ag Verfahren zur Reduktion von Passerfehlern auf einer in einer bahnverarbeitenden Vorrichtung und ein Druckwerk
ATE389537T1 (de) * 2004-01-28 2008-04-15 Koenig & Bauer Ag Druckmaschine mit einer vorrichtung und einem verfahren zur kompensation der laengsdehnung und der querdehnung einer in verschiedenen druckwerken gedruckten bedruckstoffbahn
DE102004004264C5 (de) * 2004-01-28 2011-02-24 Koenig & Bauer Aktiengesellschaft Verfahren zur Kompensation einer Querdehnung und/oder einer Längsdehnung eines Bedruckstoffes und Druckmaschine mit mehreren mindestens ein Druckbild auf einem Bedruckstoff erzeugenden Druckwerken
DE102005048246B4 (de) * 2005-10-07 2009-09-10 Maschinenfabrik Wifag Rotationsdruckmaschine mit Längendehnungs-Kompensator und Verfahren zum Bedrucken einer längsgeschnittenen Bahn
US20070175346A1 (en) * 2006-02-02 2007-08-02 Goss International Americas, Inc. Reverse air flow web stabilizer
US8042807B2 (en) 2006-12-21 2011-10-25 Palo Alto Research Center Incorporated Transport for printing systems
ES2386932T3 (es) * 2009-07-13 2012-09-06 Texmag Gmbh Vertriebsgesellschaft Rodillo de marcha fácil
US20140102326A1 (en) * 2012-10-12 2014-04-17 Goss International Americas, Inc. Printing press including bowed axis rollers and method of printing
NL2023862B1 (en) * 2019-09-20 2021-05-25 Mps Holding Bv A mandrel for printing apparatus, a printing cylinder, a printing apparatus
DE102021109014A1 (de) 2021-04-12 2022-10-13 Bayerische Motoren Werke Aktiengesellschaft Kalander-Transportrolle sowie Kalandriereinrichtung für die Herstellung von Elektroden für eine Batteriezelle

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EP1369368A1 (fr) 2002-06-06 2003-12-10 Maschinenfabrik Wifag Elément rotatif pour régler l'élargissement d'une bande
DE10225199A1 (de) * 2002-06-06 2004-01-08 Maschinenfabrik Wifag Fluidbeaufschlagter FanOut-Kompensator
DE10225200A1 (de) * 2002-06-06 2004-01-15 Maschinenfabrik Wifag Rotationskörper für eine Kompensation des Fanout
US6729232B2 (en) 2002-06-06 2004-05-04 Maschinenfabrik Wifag Fluid-coated fanout compensator
DE10225199B4 (de) * 2002-06-06 2004-05-06 Maschinenfabrik Wifag Fluidbeaufschlagter FanOut-Kompensator
US6789476B2 (en) 2002-06-06 2004-09-14 Maschinenfabrik Wifag Rotary body for compensating fanout
EP1369369A1 (fr) 2002-06-06 2003-12-10 Maschinenfabrik Wifag Compensateur d'élargissement avec un courant d'un fluide
DE10225200B4 (de) * 2002-06-06 2007-04-26 Maschinenfabrik Wifag Rotationskörper für eine Kompensation des Fanout
EP1640302A3 (fr) * 2004-02-16 2008-07-02 Koenig & Bauer Aktiengesellschaft Dispositif pour influencer la largeur ou la position d'une bande
EP1640302A2 (fr) * 2004-02-16 2006-03-29 Koenig & Bauer Aktiengesellschaft Dispositif pour influencer la largeur ou la position d'une bande
DE102005001540A1 (de) * 2005-01-13 2006-07-27 Koenig & Bauer Ag Leitwalze zur Führung einer Materialbahn
DE102005001540B4 (de) * 2005-01-13 2007-10-31 Koenig & Bauer Aktiengesellschaft Leitwalze zur Führung einer Materialbahn
DE102005001540C5 (de) * 2005-01-13 2009-08-06 Koenig & Bauer Aktiengesellschaft Leitwalze zur Führung einer Materialbahn
EP2455315A1 (fr) * 2009-07-16 2012-05-23 Mitsubishi Heavy Industries Printing & Packaging Machinery, Ltd. Dispositif pour régler un alignement dans une direction dans le sens de la largeur, et machine d'impression
EP2455315A4 (fr) * 2009-07-16 2013-04-17 Mitsubishi Heavy Ind Printing Dispositif pour régler un alignement dans une direction dans le sens de la largeur, et machine d'impression
FR2964343A1 (fr) * 2010-09-07 2012-03-09 Goss Int Montataire Sa Ensemble d'impression et utilisation correspondante
EP2457730A1 (fr) * 2010-09-07 2012-05-30 Goss International Montataire SA Ensemble d'impression et utilisation correspondante

Also Published As

Publication number Publication date
ATE248116T1 (de) 2003-09-15
US6802253B2 (en) 2004-10-12
DK1101721T3 (da) 2003-12-22
CN1187191C (zh) 2005-02-02
DE50003431D1 (de) 2003-10-02
US6550384B1 (en) 2003-04-22
DE19955099A1 (de) 2001-05-23
DE19955099B4 (de) 2010-02-11
EP1101721B1 (fr) 2003-08-27
CN1295924A (zh) 2001-05-23
ES2206169T3 (es) 2004-05-16
US20030172822A1 (en) 2003-09-18

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