EP1101721B1 - 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
EP1101721B1
EP1101721B1 EP00810878A EP00810878A EP1101721B1 EP 1101721 B1 EP1101721 B1 EP 1101721B1 EP 00810878 A EP00810878 A EP 00810878A EP 00810878 A EP00810878 A EP 00810878A EP 1101721 B1 EP1101721 B1 EP 1101721B1
Authority
EP
European Patent Office
Prior art keywords
web
rotary
surface regions
printing
machine according
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.)
Expired - Lifetime
Application number
EP00810878A
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German (de)
English (en)
Other versions
EP1101721A1 (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 rotary printing machine with a rotary body structure and a method for a Brubreitkororrektur between two pressure points of a Rotary printing press.
  • the printing press is preferably one Machine that works in wet printing, in particular an offset printing machine and particularly preferably a web-fed rotary printing machine.
  • EP 0 838 420 A2 discloses a device for correcting the fan-out Effects on web-fed rotary printing presses with which the web transversely to their Running direction is deformed wave-shaped, before moving into a subsequent pressure nip enters.
  • the web is placed in the device between two groups of rollers passed.
  • the roles of a group are offset transversely to the web direction arranged the roles of the other group.
  • the web is the wave-shaped course imprinted and thereby the web width for the pressure in the subsequent printing nip reduced.
  • Comparable devices are known from DE 43 27 646 A1 discloses the preamble of claims 1 and 16. This document discloses correcting devices arranged on either side of the web Rotations Congressgesenten and also devices with only one side of the web arranged rotational body structures, with which the web transverse to its direction is deformed wave-like.
  • 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 mutually laterally spaced circumferential projections in FIG Shape of rings or brush bodies. Due to the straight track guide passes the web only in abutment with the circumferential projections. Between the circumferential projections the track is guided freely.
  • WO 99/40006 A1 discloses a guide roller for correcting the lateral position in webs or also of longitudinal folds. These guide rollers are following the printing of the web used, the web can also wrap around the guide roll.
  • the guide roller points at least two end-to-end, variable diameter, outer, i. Wellenzapfennahe, expansion elements, which acts to expand with pressure medium become.
  • guide rolls are not known to correct the FAN-OUT Effect used.
  • JP 06134958 discloses a correction device with one to one side of the web arranged rotational body structure, with which the web transverse to the direction is deformed wave-like.
  • this device is downstream, outside of several pressure points, to a Side of the web a percussion driven rotary body with in the axial direction arranged alternately radially projecting and receding jacket areas, with the web clamped in the last print spot is pulled so hard that in Web running direction imprinting a wave-shaped course or briefly a Narrowing the track sets.
  • the invention relates to a rotary printing press with a rotary body structure for a path width correction between an upstream pressure nip and a downstream printing gap of a rotary printing machine, preferably a Newspaper web offset rotary printing press is.
  • a rotary printing press with a rotary body structure for a path width correction between an upstream pressure nip and a downstream printing gap of a rotary printing machine, preferably a Newspaper web offset rotary printing press is.
  • the Rotational body formation is arranged to one of the two sides of the web and in Web running direction rotatable. It has in the axial direction alternately next to each other radially projecting and radially recessed jacket portions to the web transversely to their To deform wave direction wavy.
  • the rotary body formation is according to the invention in a path of the web between the arranged upstream of the printing gap and the downstream pressure gap, or it the web is guided on its way between the printing columns so that the web the Rotational body in the protruding shell areas and in the recessed Mantle areas constantly wraps around, d. H. the web touches throughout Print production not only always the above jacket areas, but always the receding jacket areas. As a result, a clean linear guidance of the web is too guaranteed at all times.
  • a web for Bruumblerkorrektur not at a for this provided rotational body structure passed, for the purpose of Brubreitkororrektur in the railway path would have to be moved.
  • the web constantly wraps around the rotating body.
  • the invention Rotational body formation always deflects the web.
  • the train wraps around interlocking concave and convex or arched back and forth Cladding regions.
  • the web lies on such a rotating body always over its entire Width up.
  • the amplitude of the corrugated surface and preferably also the radial Distance between the projecting and receding shell areas of the other Embodiments is preferably between 0.2 and 3 mm, preferably it is about 2 mm.
  • the protruding jacket areas are relative to the rearward jacket regions radially movable. This allows the range of Width correction can be increased, for example, in adaptation to different Paper grades, web speeds or in adaptation to different Pressure occupancy of the web and associated different humidification. Due to the invention between the above shell areas and the receding shell areas relative movement are varying Bahnbreit corrections already arranged with only one side of the web, Rotational body structure according to the invention possible.
  • Relative movements between the protruding and the receding jacket areas are preferably to maintain a constant path length between the upstream and the downstream pressure gap compensated.
  • the protruding jacket areas and the recessed jacket areas in a neutral position of the rotary body structure a common neutral rotation axis.
  • the projecting jacket portions are relative to the Neutral position axis moves toward the web, and the receding shell areas be in relation to the neutral position axis of symmetry in the opposite direction away from the web. Because of the symmetrical Adjustment remains the middle track between the upstream and the subordinate pressure point in spite of the adjustment of the same or changes in relation to the perimeter register, if any, in a practical, i. for the print quality, not relevant extent.
  • the protruding jacket portions and the rearward jacket portions in relation to be adjusted asymmetrically in opposite directions to the neutral position axis of rotation may also be advantageous be, the protruding jacket portions and the rearward jacket portions in relation to be adjusted asymmetrically in opposite directions to the neutral position axis of rotation.
  • the protruding jacket areas below and the rearward jacket areas also moved to the same extent during the adjustment.
  • the symmetrical or asymmetrical adjustment can be achieved, for example, by radial Widening of the protruding jacket areas and radial constriction of the recessed ones Sheath areas are effected.
  • the protruding shell portions become by a group of rotatably mounted first rollers and the recessed ones Mantle areas formed by a group of rotatably mounted second rollers.
  • the rotary body formation comprises a Roll body with rotatably mounted eccentric sleeves, on which cylinder sleeves each are independently mounted rotatably.
  • the eccentric sleeves alternately designed differently in the axial direction of the roller body, so that by simple Drehverstellen the roll body, the cylinder sleeves on the web to and from the web can be moved to, preferably alternating, projecting and form projecting jacket areas.
  • the rotary body formation is a roller with receding jacket areas, which in relation to a rotation axis of the roller in radial direction are not movable, and with this projectible protruding Cladding regions.
  • the rotational body structure as a whole radially movably arranged.
  • a variation of the Bahnbreiterkorrektur can in this case by a coordinated, radial displacement of the entire rotating body structure in the sense be compensated for a track length constant maintenance.
  • the radial displacement takes place For example, by storage of the rotary body structure in eccentric bearings, as in the Printing press construction is basically known for other purposes.
  • the radial movement of the Rotationsêtsentes can instead of a pivoting movement by means of a Straightening be realized.
  • the rotation body formation, which in a print production of the web width correction serves, in another print production can be used as a pure deflection device for a train, which is either only in the pressure nip upstream in the first print production or only in the first Print production downstream printing nip is printed.
  • Rotational body structure for the advantageous dual use designed so that the protruding and the recessed jacket portions, if they are relative to each other are movable, in relation to the web can be brought to a height, so that the Rotational body of the web provides a smooth, cylindrical straight surface. If the projecting shell areas crowned or domed, d. H. permanently bulging, are shaped as may be the case according to the invention, then the based thereon Ripple so small that a web width change in a practically relevant Extent does not occur.
  • the Rotational body formation as a straight guide device for the subsequent pressure nip used. In this preferred use, it replaces one of the prior art required pressure gap inlet roller.
  • Fig. 1 shows a four-high tower with four superposed 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 designed as a blanket cylinder pressure cylinder with downstream Plate cylinders.
  • Each of the plate cylinders transfers its print image to his Printing cylinder, and the printing cylinder transfers it to the web W.
  • the invention is not on the illustrated printing unit construction in H-bridges or a four-high tower and basically not limited to a tower construction.
  • the web W passes through one behind the other Printing nip 1, the printing nip 2, the printing nip 3 and the printing nip 4 and is in each the pressure column 1 to 4 by the employed pressure cylinder on both sides, each with a color and printed in each of the pressure column 1 to 4 with a different color.
  • an inlet roller and behind the printing unit with the last printing nip 4 of the printing tower is in known Way an exit roller arranged, which can also be designed as a pull-out roller.
  • the web W is printed in wet offset printing.
  • the web W takes moisture on and swells.
  • the transverse to the direction of the web W would measured web width increase from nip to nip, and it would be in the Printing columns 1 to 4 consecutively printed images in the transverse direction of the web do not match, i. There would be registration errors in the transverse direction.
  • the device comprises a rotary body structure 6, which is shown in FIG. 1 simplified as a simple guide roller is shown.
  • the rotary body structure 6 can actually be designed as a one-piece roller. It is in preferred Uses actually used only as a guide roller.
  • the rotary body structure 6 is in a special way educated.
  • the rotary body structure 6 is arranged immediately in front of the pressure nip 3 and fulfills in this arrangement at the same time the function of the linear guide for the web W. Die
  • the function of the linear guide is for the two printing units with printing columns 3 and 4 fulfilled by the rotary body formation 6 and the pull-out roller behind the pressure nip 4.
  • the web W is stretched between the rotary body 6 and the pull-out roller.
  • the Rotations Energygesente 6 thus additionally supports the so-called flying side change with continuing production.
  • the web W deformed in the transverse direction by means of the rotary body structure 6 wave-shaped.
  • the Web width is thereby reduced.
  • the web W will be between the upstream pressure nip 2 and the downstream pressure nip 3, each based on the rotating body structure 6, so guided that in the illustrated printing production, in who already printed the web before entering the downstream printing nip 3 and is therefore moistened, the rotary body structure 6 wraps around.
  • a Arranged deflection device which is a simple guide roller or another Rotational body formation 5 for wave-shaped deformation of the web W can be.
  • the Web W is thus not straight between the two printing nips 2 and 3, but deflected to the wrap of the rotary body structure 6 according to the invention receive.
  • a deflection device used here can itself as inventively looped body of revolution 5 may be formed. It is basically possible although less preferred that the rotary body structure 6 is omitted and the Path width correction solely by the wrapped body of revolution 5 is made. Are in this case immediately behind the nip 2 and straight ahead of the nip 3 linear guide not available, it would be a flying page change not possible. Preferred are such linear guidance agents however, as in the embodiment, so that all printing cylinder of the tower for a flying page change, i. during production, switched on and off can be
  • Rotational body formation 6 umstoffbar upstream diverter 5 may be a be just such a rotation body formation.
  • FIGS. 2 to 5 A first embodiment of a rotary body structure 6 is shown in FIGS. 2 to 5 shown, referred to in the following description in its entirety be.
  • the rotary body structure 6, in the first embodiment has two groups of Rolls, namely a group of first rollers 10 and a group of second rollers 11, each pivotable about a per group common pivot axis on one 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 axial Direction of the rotary body 6, i. transverse to the direction of web travel, alternating arranged side by side. In this alternating arrangement are the first rollers 10th towards the web further ahead than the second rollers 11.
  • the lateral surfaces of the first rollers 10 form with respect to the web W projecting jacket portions A
  • the Mantle surfaces of the second rollers 11 form with respect to the web W in comparison to the Mantle areas A projecting jacket areas B. Since the moistened web W the Rotational body formation 6 wraps under tension, the web W in the transverse direction imprinted in Fig.
  • the first Rollers 10 are on their lateral surfaces, which in the embodiment with the above Mantle areas A are identical, spherical or cambered shaped. The web W is therefore in large surface areas fed on the rotational body structure 6.
  • the receding jacket portions B may be correspondingly inwardly curved. It is sufficient However, as shown in the embodiment, a straight-cylindrical design of the second rollers 11.
  • Fig. 2 shows the rotary body structure 6 in its extreme position, in which the projecting areas A relative to the receding Regions B project furthest towards the web W.
  • the ripple and that Extent of reduction of web width are in the extreme position of Rotational body formation 6 largest.
  • Fig. 4 shows a plan view of the rotating body structure 6 on the one of the web opposite side.
  • Fig. 3 shows in an axial direction of the rotary body formation 6 vertical view of an adjusting device for the relative adjustment of the above Areas A and the recessed areas B.
  • the rotary body formation 6 represented in the extreme position shown in Fig. 2.
  • Fig. 4 shows that Rotational body structure 6 in a neutral position, in which the axes of rotation of all roles 10 and 11 are in alignment and form a common neutral rotation axis N.
  • the protruding areas A are only the extent of their Prevailing over the recessed jacket portions B in the direction of the web W too in front.
  • the extent of protrusion in the neutral position is so small that the width of the Web W in the neutral position N by the rotating body structure 6 is not changed or if necessary to a practically non-relevant extent.
  • In the Neutral position are the edges of the first rollers 10 and second rollers 11 on the same Height, relative to the train.
  • the movement of the rollers 10 and 11 and thus in particular the protruding areas A and the receding portion B from the neutral position to the extreme position or a intermediate position is axisymmetric with respect to the Neutral rotation axis N.
  • the protruding area A becomes off during the adjustment the neutral position always so far radially with respect to the axes of rotation of the first rollers 10 in Direction to the web moves too as regards the receding area B radially the axes of rotation of the second rollers 11 are moved away from the web.
  • the Neutral position axis of rotation N remains in each 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 the center line.
  • the first rollers 10 are rotatable individually on pivot arms 18 and the second rollers 11 are rotatably mounted individually on pivot arms 14.
  • the pivot lever 14 are on one Swivel shaft 13 and the pivot arms 18 are on a pivot shaft 17 and twisted secured against displacement.
  • the two pivot shafts 13 and 17 are parallel spaced between two opposite side walls 8 and 9 of the Machine frame transverse to the web running direction and are on the side walls 8 and 9 each order their longitudinal axes rotatably mounted.
  • the pivot arms 14 project from the pivot shaft 13 and the pivot arms 18 from the pivot shaft 17 perpendicular from and toward each other. On their free ends protrude from right angles bolts on which the rollers 10 and 11 are rotatably mounted.
  • On the side wall 8 is an adjusting device with a drive M.
  • the two pivot shafts 13 and 17 are for synchronous adjustment in above-described meaning with each other and with the drive M via an angle gear coupled.
  • the drive M and the angle gear form a synchronizer for the two groups of roles 10 and 11.
  • the drive comprises a rotary motor with a control and an output shaft 19 a, the is designed as a spindle with a fine thread.
  • the output shaft 19a is at its rotatably mounted free end on the side wall 8 again.
  • Running on the spindle thread a threaded nut with a carriage 19b mounted thereon.
  • On the carriage 19b is a lever 12 rotatable about an axis of movement of the carriage 19 b axis attached.
  • the lever 12 is formed by a web which is secured against rotation on the Pivot shaft 13 and on the carriage 19b rotatable about a direction of travel of Slider 19b is mounted perpendicular and parallel to the shaft 13 axis.
  • lever 12 becomes a straight process of the carriage 19b in a corresponding rotation of the shaft 13 converted.
  • the particular mounted on the shaft 13 against rotation Swivel arms 14 and thus the second rollers 11 are with the rotation of the shaft 13 pivots.
  • a synchronous, opposing pivoting of the first rollers 10 is by a neutral symmetry to the neutral rotation axis N lever assembly and Coupling to the lever 12 by means of a rigid tab 15 causes.
  • For the Coupling is the lever 12 seen from the carriage 19b via the pivot shaft thirteenth also just extended. Opposite protrudes from the pivot shaft 17, a lever 16th from.
  • the free ends of the levers 12 and 16 are articulated by means of the tab 15 connected to each other, such that upon pivoting of the lever 12 to the Swiveling axis 13 is a giving away of the lever 16 about the pivot axis 17 is effected and at the same time the lever 16 and its opposite extended portion of the Levers 12 always stay parallel.
  • the levers 12 and 16 point between the pivot shafts 13 and 17 and the axes of rotation with the tab 15 the same length.
  • Pivoting lever 14 perpendicular to the extended portion of the lever 12 on the Pivot shaft 13 and the pivot lever 18 perpendicular to the lever 16 on the Pivoting shaft 17 is fixed and further formed by the pivot lever 14 and 18 Swing axes are the same length, with respect to the neutral position of rotation N in the same direction pivoting of the first rollers 10 and the second rollers 11th causes.
  • the maximum adjustment 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 6 is between 30 and 70 mm, in the embodiment, it is 50 mm.
  • the distance between two each adjacent rollers 10 and 11 is smaller than the width of the rollers and amounts preferably less than 30 mm; In the embodiment remains a clear distance between each two adjacent rollers 10 and 11 of 20 mm. The distance is for the Housing the pivot lever 14 and 18 required.
  • the number and dimensions of the rollers 10 and 11 are chosen so that on 1 ⁇ 4 web width at least one complete Wellenberg or a complete wave trough is formed. This would be the first one Embodiment for a 4/4 wide web of the case.
  • the above Areas A and recessed areas B formed in such a number that two or more complete wave crests or troughs per 1 ⁇ 4 web width are formed.
  • the adjustment of the protruding area A and the recessed areas B, i. in the Embodiment of the rollers forming them 10 and 11, takes place in dependence on the Web tension S, the web speed V, the paper type T and the web moisture F or one or more of these selected parameters.
  • the manipulated variable formed directly from the target-actual deviation of the web width.
  • the web width is here via suitable sensors, either at the web edges, at the side mirror edge or at detected suitable print marks.
  • Fig. 5 shows the rotary body structure 6 in a side view in its neutral position. Entered is the wrap angle a, the angle of the circumferential length of the looped lateral surfaces of the protruding jacket areas A and receding jacket portions 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 for the other embodiments of the rotary body structure. 6
  • FIGS. 6 and 7 show a second, particularly preferred embodiment of the invention RotationsMongesentes invention.
  • This comprises a roller body 61, the between a left machine frame and a right machine frame (not shown) is stored.
  • a number of eccentric sleeves 60a, 60b arranged rotationally fixed.
  • a single eccentric sleeve in the form of a comparatively long cam body rotatably be arranged on the roller body 61, with a number of different Eccentric sections in the axial direction of the roller body 61 for storage of respective Cylinder sleeves.
  • the roller body 61 itself can also be in the manner of a camshaft be formed with trained side by side eccentric sections.
  • cylinder sleeves 62, 63 rotatably mounted, which are each independently rotatable.
  • the cylinder sleeves 62, 63 and the associated eccentric sleeves 60a, 60b are alternating designed differently, so that by alternately forward or backward Cylinder sleeves radially projecting jacket portions A and radially recessed Sheath regions B are formed.
  • the alternating arrangement can in principle also another suitable alternating sequence of cylinder sleeves 62, 63 be selected to the peripheral surface of the rotary body structure 6 a suitable To give waveform.
  • the cylinder sleeves 62, 63 are cylindrical. Alternatively, these can however, also seen in the axial direction a concave or convex profile or alternating a different profile, e.g. cylindrical and concave or convex.
  • the Cylinder sleeves 62, 63 may also have different surface roughnesses.
  • the rotary body formation forms on its outer lateral surface a straight line, which extends parallel to the axis of rotation of the rotary body formation. This line will by arranging the eccentric sleeves 60a and 60b in corresponding ones Rotation angle positions and matched thicknesses of the cylinder sleeves 62 and 63 receive.
  • the eccentric sleeves 60a and 60b in the corresponding Arrangement relative to each other takes the distance measured in the radial direction the protruding jacket areas A and the rearward jacket areas B over the circumference of the rotary body seen from the straight line to both Sides evenly to the diametrically opposite side of the Rotational body formation evenly too.
  • the rotary body formation is in the Longitudinal section, which includes the two extremes, namely the straight line on the one hand and in the radial direction maximum distance between projecting Mantle areas A and rearward jacket areas B on the other.
  • the roller body 61 is adjustable in rotation about an axis of rotation N in the Machine frame mounted, with the respective rotary adjustment mechanically locked or is suitably regulated, for example, also electronically controlled.
  • to 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, via the schematic shown slip-free transmitting Stirnrad- or gear assembly 64 the Roll body 61 rotatably adjusted about its axis of rotation.
  • the axes of rotation of the cylinder sleeves 62 and 63 extend eccentrically to the axis of rotation of Roll body 61, and alternately offset by 180 °.
  • the rotation of the roller body 61 is preferably carried out continuously.
  • the roller body 61 By twisting of the roller body 61 are the radially projecting portions of the eccentric sleeves 60a, 60 b about the rotational axis of the roller body 61 together with the roller body 61 turned.
  • the cladding regions A, B move against or away from the Paper web.
  • the transition from the extremely wavy line takes place to the 180 ° offset straight line fluently.
  • the rotational 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 Roll body 61.
  • the discernible gap s in each case between two axially adjacent cylinder sleeves 62 and 63 is preferably kept as low as possible in order to achieve optimum web guidance to allow the protruding or receding jacket areas A, B.
  • the geometric relationships of the Eccentric sleeves 60a, 60b and / or the cylinder sleeves 62, 63 are varied.
  • a preferred aspect ratio is L1: L2 is 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 D1 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 simple structure can be manufactured inexpensively and is also easy to maintain because the eccentric and cylindrical sleeves are individually interchangeable. If you have the Cylinder sleeves replaced by cylinder sleeves with other dimensions, for example each only alternating, the illustrated rotary body structure can be very flexible and inexpensively converted.
  • a special advantage is also that the Adjustment under web path maintenance only by rotation of the roller body 61, i. of the rotary body 6 as a whole, about the axis of rotation N takes place.
  • the rotation axis N of the roller body 61 is at the same time the neutral position rotation axis of the Rotational body formation 6.
  • FIG. 7 shows the rotary body structure 6 according to the second embodiment in two different 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 in Contact area with the paper web are virtually aligned, and a maximum adjustment (lower figure), where the roller body 61 is maximally lubver Surprise, so that the first Cylinder sleeves 62 a protruding jacket portion A and the second cylinder sleeves 63rd form a receding jacket region B.
  • the jacket area B is in this Adjustment position with respect to the protruding jacket region A maximally set back.
  • Fig. 8 shows the rotary body structure 6 in a third embodiment, in which it Roller is formed with axially engageable ring members 20.
  • the rotary body structure 6 of the third embodiment comprises a roller body 22, the pivoting known as deflection rollers or by storage in eccentric bearings is rotatably mounted on the machine frame.
  • elastically deformable Ring elements 20 and dimensionally stable ring elements 21 alternately immediately close arranged side by side.
  • the ring elements 20 and 21 are axially on the roller body 22 slidably and preferably arranged against rotation.
  • the outermost of the 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.
  • roller body 22 On the opposite side of Roller body 22 presses a roller body 22 axially displaceably mounted An fürverschiebeelement 23 against the outermost of the ring members 20 and 21, the also a deformable ring element 20, but in principle by a dimensionally stable Ring element 21 can be formed.
  • the juxtaposed ring elements 20th and 21 are between the An fürverschiebeelement 23 and the abutment 24th bordered and by advancing the Anduchverschiebeelements 23 in the direction of the Abutment 24 to be pressed against each other in the axial direction. Under the two sides introduced axial compressive force, the ring members 20 over their entire circumference evenly curved elastically outwards or warped.
  • the Anyakverschiebeelement 23 is formed by an axial ball bearing.
  • the Anyakverschiebeelement 23 is by an actuating means 25 axially against the outermost of the ring elements 20 and 21 pressed.
  • the Antikverschiebeelement 23 has an inner bearing shell with which it presses against the outermost of the ring elements 20 and 21, and an outer bearing cup against which the actuating means 25 presses.
  • the inner one Bearing shell is against rotation, but slidably mounted on the roller body 22.
  • the outer bearing shell may also be mounted on the roller body 22, wherein in this Case also the actuating means 25 rotatably supported together with the roller body 22 would.
  • the outer bearing shell is rotated and displaceable on the Roller body 22 mounted so that the actuating means 25 attached to the machine frame can be.
  • the actuating means 25 by an angle formed, which is rotatably mounted on a pin 26 on the machine frame. At one front end, the angle on a cam, with which he against the outer Bearing shell of An horrverschiebeelements 23 pushes and thereby axial pressure on the Ring elements 20 and 21 exerts.
  • Fig. 9 shows the rotary body structure 6 in a fourth embodiment in which it also designed as a roller.
  • the projecting areas A also by the lateral surfaces of fully circumferential, elastically deformable ring elements 30 formed.
  • the recessed areas B become by strip-shaped circumferential lateral surfaces of a roller body 32 itself educated.
  • the roller body 32 is like known deflection rollers or by means Eccentric bearings stored in the machine frame.
  • Fig. 9 shows the rotary body structure 6 in its neutral position, in which the Rotational body has a smooth, straight, circular cylindrical surface.
  • the Projecting areas A are by applying the deformable ring elements 30 formed with compressed air.
  • the roller body 32 is at one end by means of a Druckan gleiches 33 with a pressurized fluid from a pressure reservoir or from a Pump acted upon.
  • the pressurized fluid preferably compressed air, passes through the Pressure port 33 in a central, axial pressure line 34, which extends over almost the entire length of the roller body 32 extends and from the radial pressure lines 35th branch.
  • the radial pressure lines 34 are below the deformable ring elements 30 guided, where they in circumferential, outwardly open ring channels 36 for uniform Open pressure fluid distribution.
  • the deformable ring elements 30 seal the ring channels 36 to the outside.
  • a build-up in the annular channels 36 pressure causes a Bulging the elastically deformable ring members 30 radially outwardly, whereby the projecting jacket areas A of this rotary body structure 6 arise.
  • At Pressure relief come the ring elements 30 due to their own elastic Return forces return to the neutral position.
  • Fig. 10 shows the rotating body structure 6 in one of the fourth embodiment modified fifth embodiment.
  • the essential difference to the fourth Embodiment is that the deformable ring elements of the fifth Embodiment formed by tubular, elastically expandable ring members 40 become.
  • the deformable ring elements 40 are received in recesses 47, the are formed circumferentially on the lateral surface of the roller body 42 and as in Embodiment, for example, can be formed by simply rectangular grooves.
  • the protruding between the recesses 47 roll body areas form at their Lateral surfaces 41, the rearward jacket portions B of the rotary body formation.
  • the deformable ring elements 40 are connected by a pressure port 43, a central, axial pressure line 44 and branching off radial pressure lines 45 with a Pressurized fluid, preferably compressed air, applied.
  • a Pressurized fluid preferably compressed air
  • the admission takes place through Introduction of the pressurized fluid in the annular tubes or elements 40, thereby by printed inside and thereby expanded radially outward.
  • the protruding jacket areas A By the Widening arise the protruding jacket areas A. Pull at pressure relief the annular tubes 40 due to their own elastic restoring forces back up back to the height of the receding jacket areas B, so that too Rotations Energygejecte 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 through a single roller body 52 is formed, which has a wavy lateral surface.
  • the Rotational body formation 6 is in this embodiment in one piece as a steel roller or as Roller formed of another suitable material. An adjustment of the ripple can not.
  • the roller body 52 alternately axially thicker side by side Roller areas 50 and on the other hand thinner roller areas 51.
  • the thicker ones Roller areas 50 form the permanently projecting jacket areas A, and the thinner roll areas 51 form the permanently recessed jacket areas B.
  • the lateral surface of the roller body 52 is rotationally symmetric and extends in each Longitudinal section sinusoidal with an amplitude of 2 mm. In the embodiment run ever two adjacent wave crests bulging outward bulging together.
  • the rotary body structure 6 of FIG. 12 corresponds to that of FIG. 11 with the single exception, that the sequence of prominent areas A and lagging Areas B in the roll longitudinal direction by 90 ° out of phase that of Embodiment of Fig. 11 corresponds.

Landscapes

  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Rotary Presses (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
  • Medicines Containing Plant Substances (AREA)
  • Motorcycle And Bicycle Frame (AREA)
  • Soft Magnetic Materials (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Ink Jet (AREA)

Claims (20)

  1. Presse rotative avec un complexe de corps rotatifs pour corriger une largeur de bande d'une bande imprimée par plusieurs postes d'impression l'un derrière l'autre, pour laquelle le complexe de corps rotatifs (5, 6) qui peut tourner présente en direction axiale, alternativement les unes à côté des autres, des zones de surface latérale (A, B) en saillie radiale et en retrait radial afin de déformer la bande de façon ondulée transversalement à sa direction de déplacement,
    caractérisée en ce que le complexe de corps rotatifs (5, 6) peut être déplacé radialement, les zones de surface latérale (A) en saillie et les zones de surface latérale (B) en retrait présentant un axe de rotation de position neutre (N) commun dans une position neutre du complexe de corps rotatifs (5, 6) et étant approchées et éloignées de la bande de façon symétrique en cas de déplacement par rapport à l'axe de rotation de position neutre (N).
  2. Presse rotative selon la revendication 1 caractérisée en ce que le complexe de corps rotatifs (5, 6) est disposé sur un trajet de la bande entre l'intervalle d'impression (2) en amont et l'intervalle d'impression (3) en aval ou la bande est guidée sur son trajet entre ces intervalles d'impression (2, 3) de telle manière que la bande enlace constamment le complexe de corps rotatifs (5, 6) dans les zones de surface latérale (A) en saillie et dans les zones de surface latérale (B) en retrait.
  3. Presse rotative selon l'une des revendications précédentes caractérisée en ce que le complexe de corps rotatifs (5, 6) placé entre l'intervalle d'impression (2) et l'intervalle d'impression (3) est un cylindre déviateur qui agit sans correction de largeur de bande dans une autre production d'impression en ce que les zones de surface latérale (A) en saillie et les zones de surface latérale (B) en retrait peuvent être portées, par rotation ou par pivotement, par rapport à la bande à une hauteur ou au moins jusqu'à une hauteur avec laquelle est déviée la bande qui entre dans l'intervalle d'impression (3) en aval ou la bande qui sort de l'intervalle d'impression (2) en amont.
  4. Presse rotative selon l'une des revendications précédentes caractérisée en ce que le complexe de corps rotatifs (5, 6) peut être décalé radialement comme un tout afin de pouvoir compenser une modification de la longueur de bande entre l'intervalle d'impression en amont (2) et l'intervalle d'impression en aval (3).
  5. Presse rotative selon l'une des revendications précédentes caractérisée en ce que les zones de surface latérale en saillie (A) sont formées par un groupe de premiers rouleaux ou mandrins (10 ; 62) et les zones de surface latérale en retrait (B) par un groupe de deuxièmes rouleaux ou mandrins (11 ; 63).
  6. Presse rotative selon l'une des revendications précédentes caractérisée en ce qu'au moins les rouleaux (10 ; 11) d'un des groupes sont disposés de façon mobile transversalement aux axes de rotation de ces rouleaux (10 ; 11) et radialement par rapport aux rouleaux (11 ; 10) de l'autre groupe.
  7. Presse rotative selon l'une des revendications 1 à 6 caractérisée par un corps de cylindre (61) avec des mandrins à excentrique (60a, 60b) sur lesquels des mandrins de cylindre (62, 63) sont logés de façon rotative chacun indépendamment de l'autre, les mandrins à excentrique (60a, 60b) reposant sur le corps de cylindre (61) de façon à résister à la torsion.
  8. Presse rotative selon l'une des revendications précédentes caractérisée en ce que les mandrins à excentrique (60a, 60b) et/ou les mandrins de cylindre (62, 63) sont dimensionnés différemment en direction du corps de cylindre (61) de sorte que les mandrins de cylindre (62, 63) forment des zones de surface latérale alternativement en saillie (A) et en retrait (B).
  9. Presse rotative selon l'une des revendications précédentes caractérisée en ce que le corps de cylindre (61) est disposé de façon à se déplacer par rotation autour d'un axe de rotation (N) afin d'approcher et d'éloigner de la bande les zones de surface latérale en saillie (A) et/ou en retrait (B).
  10. Presse rotative selon la revendication précédente caractérisée en ce que le complexe de corps rotatifs (5 ; 6) est un cylindre logé de façon rotative qui présente sur une surface de surface latérale du cylindre les zones de surface latérale en saillie (A) et les zones de surface latérale en retrait (B).
  11. Presse rotative selon l'une des revendications 1 à 4 caractérisée en ce que le complexe de corps rotatifs (5 ; 6) comprend un corps de cylindre (22 ; 32 ; 42) sur lequel sont disposés des éléments annulaires (20 ; 30 ; 40) qu'on peut pousser radialement vers l'extérieur et qui forment les zones de surface latérale en saillie (A).
  12. Presse rotative selon la revendication précédente caractérisée en ce que des conduites d'impression (34, 35 ; 44, 45) sont formées dans le corps de cylindre (22 ; 32 ; 42) et peuvent être reliées à un raccord d'impression (33 ; 43), à travers lesquelles les éléments annulaires (20 ; 30 ; 40) qu'on peut pousser peuvent être alimentés en un fluide de pression pour une poussée.
  13. Presse rotative selon la revendication 12 caractérisée en ce que les éléments annulaires (20) qu'on peut pousser peuvent être déformés élastiquement,
    les zones de surface latérale en retrait (B) sont formées par des éléments annulaires (21) à forme stable,
    les éléments annulaires (20) déformables et les éléments annulaires (21) à forme stable qui sont disposés entre deux éléments annulaires (20) déformables peuvent être déplacés axialement sur le corps de cylindre (22) l'un par rapport à l'autre
    et les éléments annulaires (20, 21) déformables et à forme stable sont enchâssés entre un élément de déplacement par pression (23), logé de façon à pouvoir se déplacer axialement sur le corps de cylindre, et une butée (24) axiale.
  14. Presse rotative selon l'une des revendications précédentes caractérisée en ce qu'elle présente au moins un deuxième complexe de corps rotatifs (5 ; 6) semblable et que les deux complexes de corps rotatifs (5 ; 6) sont logés sur des bras oscillants de façon à basculer autour d'un axe commun,
    seulement l'un ou seulement l'autre des complexes de corps rotatifs (5 ; 6) au moins au nombre de deux pouvant au choix être basculé dans une position de travail où il est enlacé par la bande tandis que l'autre des complexes de corps rotatifs (5 ; 6) concerné au moins au nombre de deux n'agit pas sur la bande et
    que des zones de surface latérale en saillie (A) de l'un des complexes de corps rotatifs (5 ; 6) au moins au nombre de deux dans sa position de travail sont plus en saillie par rapport à la bande que les zones de surface latérale en saillie (A) de l'autre des complexes de corps rotatifs (5 ; 6) au moins au nombre de deux dans sa position de travail.
  15. Presse rotative selon la revendication précédente caractérisée en ce qu'un bras oscillant du complexe de corps rotatifs (5 ; 6) dont les zones de surface latérale en saillie (A) forment une plus grande saillie est plus court qu'un bras oscillant de l'autre des complexes de corps rotatifs (5 ; 6) au moins au nombre de deux.
  16. Procédé pour corriger une largeur de bande d'une bande imprimée (W) par plusieurs postes d'impression l'un derrière l'autre, pour lequel, avec un complexe de corps rotatifs qui peut tourner, avec en direction axiale alternativement les unes derrière les autres des zones de surface latérale en saillie radiale et en retrait radial, la bande (W) est soumise à un tracé de forme ondulée transversalement à sa direction de déplacement de bande, le tracé de forme ondulée n'étant appliqué que par l'enlacement du complexe de corps rotatifs (5 ; 6) disposé d'un côté de la bande et
    le complexe de corps rotatifs (5 ; 6) présentant alternativement les unes à côté des autres des zones de surface latérale (A, B) en saillie et en retrait,
    caractérisé en ce que des modifications de la largeur de bande sont corrigées par un mouvement radial des zones de surface latérale en saillie (A) par rapport aux zones de surface latérale en retrait (B).
  17. Procédé selon la revendication précédente caractérisé en ce que la bande enlace constamment le complexe de corps rotatifs (5 ; 6) selon un angle d'enlacement (a) d'au moins 3°.
  18. Procédé selon la revendication précédente caractérisé en ce qu'une modification de la longueur de bande entre l'intervalle d'impression en amont (2) et l'intervalle d'impression en aval (3) est empêchée en ce que le mouvement radial des zones de surface latérale en saillie (A) et des zones de surface latérale en retrait (B) est en symétrie bilatérale par rapport à un axe longitudinal du complexe de corps rotatifs (5 ; 6).
  19. Procédé selon la revendication 18 caractérisé en ce qu'une modification de la longueur de bande entre l'intervalle d'impression en amont (2) et l'intervalle d'impression en aval (3) est empêchée en ce que le mouvement radial des zones de surface latérale en saillie (A) et des zones de surface latérale en retrait (B) est asymétrique en opposition par rapport à un axe longitudinal du complexe de corps rotatifs (5 ; 6).
  20. Procédé selon l'une des revendications 16 à 19 caractérisé en ce qu'une modification - due à la correction - de la longueur de bande entre l'intervalle d'impression en amont (2) et l'intervalle d'impression en aval (3) est empêchée par un décalage radial de tout le complexe de corps rotatifs (5 ; 6).
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)

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

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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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EP1101721A1 EP1101721A1 (fr) 2001-05-23
EP1101721B1 true 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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DE19955099B4 (de) 2010-02-11
US6550384B1 (en) 2003-04-22
DK1101721T3 (da) 2003-12-22
DE19955099A1 (de) 2001-05-23
US20030172822A1 (en) 2003-09-18
ATE248116T1 (de) 2003-09-15
CN1295924A (zh) 2001-05-23
US6802253B2 (en) 2004-10-12
EP1101721A1 (fr) 2001-05-23
ES2206169T3 (es) 2004-05-16
DE50003431D1 (de) 2003-10-02
CN1187191C (zh) 2005-02-02

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