EP1101721A1 - Rotating body for correcting web width - Google Patents

Abstract

The rotary body arrangement provides for the correction of the web width in a web offset roller-type rotary printing press for newspapers. A rotary body arrangement (5, 6) is fitted on the path of the web between two printing gaps (2, 3) to one side of the web, with the web continuously passing round it so that a corrugation is impressed on it transversely to the running direction.

Description

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. In 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.

In rotary printing presses that work in wet printing occur due to the dampening changes in transverse elongation of the web. This phenomenon known as the fan-out effect has to the undesirable consequence that the width of the web measured transversely to the web running direction changes between two printing columns in which the web is printed one after the other. In the the web dampened in one pressure nip swells on its way and becomes the next Printing gap wider. If corrective measures are not taken, this leads to Printing errors in the cross-web direction in the printing cylinders forming the printing nips.

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.

As an alternative to the printing plate shift, it is known to correct the web width. For example, 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. By at least one of the two groups of Rolling into the web path is movable, 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.

In this device 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. However, guide rollers are known not to be used to correct the FAN-OUT Effect used.

Another device with only local pressurization of the web is disclosed in US 5,553,542. To correct the FAN-OUT effect, there are a number of spaced rollers or compressed air nozzles, the latter in close proximity to the web, provided for pressurizing the web. Because of a straight, vertical Web guide wraps the web only around the pressurization points, otherwise it will however straight, vertically guided.

Further guide roller devices are in Walewski, Wolfgang: the web offset printing, Fachschriften-Verlag 1995, page 94, in DE 33 10 450 C1, in DE 87 03 732 U1 and in EP 0 253 981 B1.

In the known devices, 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. For this purpose the Rotational body structures moved into the path of the web. Through 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.

It is an object of the invention to enable web width correction based thereon coordinated range register corrections are not 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. In the two printing columns is in a print production 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.

According to the invention, 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. According to the invention the web continuously wraps around the body of revolution. The invention 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 °.

According to the invention, 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.

In preferred exemplary embodiments, 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.

In a preferred first embodiment, 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. For variation of the web width correction i.e. to adjust the web width, 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. To keep the length of the path between the upstream pressure point and the downstream pressure point it can also be advantageous be, the protruding jacket areas and the recessed jacket areas in relation to be adjusted asymmetrically in opposite directions on the neutral axis of rotation. Prefers 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. Preferably 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.

In a preferred further embodiment, 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.

In preferred further embodiments, 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.

It is advantageous to compensate for changes in web length caused by a Movement of the protruding shell areas relative to the protruding ones Shell regions could be caused, the whole of the body of the body radially movably arranged. A variation in the web width correction can be done in this case a coordinated, radial displacement of the entire rotating body structure in the sense a constant web length can be compensated. The radial shift takes place For example, by storing the rotating body structure in eccentric bearings, as in Printing machine construction for other purposes is generally known. The radial movement of the Rotary body structure can instead of a pivoting movement by means of a Straight shift can be realized.

In order, especially when the rotary body structure is not designed as a roller changeable surface shape the web width correction to the production needs To be able to adjust adjusted, several will be in a further development 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. Is it the 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. Hit this Prerequisite with regard to the rotary body structures of the rotary magazine not too, so can the web path between the upstream and the downstream printing nip nevertheless be kept constant by the length of the swivel arms on which the Rotational body structures are stored in relation to their common pivot axis, in Matching to the individual rotary body structures of the rotary magazine in the sense of a Track path maintenance can be selected.

Another advantage of the invention is that 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. Preferably that is 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.

Preferably on the path of the web between the upstream pressure gap and the rotating body structure or the rotating body structure and the subordinate Pressure gap a deflection device arranged around the web of the rotating body structure to wrap according to the invention. In a preferred arrangement, 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

einen Druckturm mit zwei Rotationskörpergebilden nach der Erfindung,

Fig. 2

ein Rotationskörpergebilde in einer ersten Ausführungsform in einer Längsansicht X

Fig. 3

das Rotationskörpergebilde der Fig. 2 in einer Queransicht auf eine Verstelleinrichtung,

Fig. 4

das Rotationskörpergebilde der Fig. 2 in einer Längsansicht senkrecht zur Ansicht X,

Fig. 5

das Rotationskörpergebilde der Fig. 2 in einer weiteren Queransicht,

Fig. 6

ein Rotationskörpergebilde gemäß einer zweiten bevorzugten Ausführungsform,

Fig. 7

eine Querschnittsansicht der zweiten Ausführungsform in einer minimalen und maximalen Verstellung,

Fig. 8

ein Rotationskörpergebilde in einer dritten Ausführungsform,

Fig. 9

ein Rotationskörpergebilde in einer vieren Ausführungsform,

Fig. 10

ein Rotationskörpergebilde in einer fünften Ausführungsform,

Fig. 11

ein Rotationskörpergebilde in einer sechsten Ausführungsform und

Fig. 12

eine Abwandlung des Rotationskörpergebildes der Fig. 11.

Preferred embodiments of the invention are explained below with reference to figures. Show it:

Fig. 1

a pressure tower with two rotary body structures according to the invention,

Fig. 2

a rotational body structure in a first embodiment in a longitudinal view X

Fig. 3

2 in a transverse view of an adjusting device,

Fig. 4

2 in a longitudinal view perpendicular to view X,

Fig. 5

2 in a further transverse view,

Fig. 6

a rotational body structure according to a second preferred embodiment,

Fig. 7

2 shows a cross-sectional view of the second embodiment in a minimum and maximum adjustment,

Fig. 8

a rotational body structure in a third embodiment,

Fig. 9

a rotational body structure in a fourth embodiment,

Fig. 10

a rotational body structure in a fifth embodiment,

Fig. 11

a rotational body structure in a sixth embodiment and

Fig. 12

a modification of the rotating body structure of FIG. 11.

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.

In the print production shown in Fig. 1, 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. Before 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. Here, the web W takes moisture and swells. Without corrective measures, 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.

To prevent or at least reduce 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. For this purpose a device for correcting the web width between the printing columns 2 and 3 arranged. 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. For the Double usability, on the one hand as a means for web width correction and on the other hand as a deflection means, 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 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.

As shown by way of example with reference to the first embodiment in FIG. 2, the web W deformed in the transverse direction by means of the rotating body structure 6. The This reduces the web width. To achieve this, the web W between the upstream pressure gap 2 and the downstream pressure gap 3, each based on the rotary body structure 6, guided so that in the print production shown, in which has already printed the web before entering the downstream printing nip 3 and is therefore moistened, the rotary body structure 6 wraps around. For this purpose between the upstream pressure gap 2 and the rotary body structure 6 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. Are in this case immediately behind the pressure gap 2 and immediately in front of the pressure nip 3 straight guide means would not be present, however a flying change of sides is not possible. Such 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

In Fig. 1 is the alternative use of the rotating body structure 6 as pure Deflection roller indicated.

For example, will the same printing tower ever be used in a different print production two-color printing of two webs is used, so one web W 'of these two Lanes from the side between the two printing columns 2 and 3 in the printing tower run in and deflected by the rotary body structure 6 and, like the web W the first print production are fed to the downstream printing nip 3. Act if the web W 'is a web which has not yet been printed, it is one Path width correction is not required and is also by the rotating body structure 6 not effected. In principle, however, the rotational body structure 6 in could also be used this alternative print production the web W 'in width by embossing one wavy course should be corrected based on a previous one Moistening the web W 'may be desirable.

In the following figures, preferred embodiments of the 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.

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. In the first embodiment, 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. Since the moistened web W 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. When wrapping the web W is both in the above jacket areas A as well as in the back jacket areas B. supported and managed, i.e. it also lies in the back of the jacket areas. It you will get a particularly clean, straight line guidance of the web W. 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.

The adjustment of the projecting areas A and the projecting areas B relative one can best recognize one another by looking at FIGS. 3 and 4 together. Fig. 4 shows 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. In FIG. 3, 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. In the neutral position, 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. In the 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 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. In Fig. 2 are the alignment of the axes of rotation of the first rollers 10 with P for the extreme position and the alignment of the axes of rotation of the second rollers 11 is denoted by Q. Through the Axially symmetrical adjustment, the ripple of the web W is changed during the Path of the web, based on a neutral line extending in the transverse direction of the web between the wave crests and wave troughs of the web W is preserved. The web width adjustment according to the invention is therefore carried out without changing the web length between the upstream pressure gap 2 and the downstream pressure gap 3. Die web width adjustment according to the invention does not cause errors in the circumferential register.

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. At their free ends protrude at right angles on which the rollers 10 and 11 are rotatably mounted. On the side wall 8, 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. About the lever 12 becomes a straight movement of the slide 19b into a corresponding rotation of the shaft 13 converted. The in particular secured on the shaft 13 against rotation Swivel arms 14 and thus the second rollers 11 become with the rotation of the shaft 13 pivoted. 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. Since the 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. Preferably 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 ¼ track width. The 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. These are the four Input variables for the automatically supported control of the drive M, i.e. the Control forms the manipulated variable for your actuator, namely the motor of the drive M, in the sense of keeping the web width constant. Instead of a controller, too regulation of the drive M are used. In this case, 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.

5 shows the rotating body structure 6 in a side view in its neutral position. 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 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. Alternatively, instead of the plurality of eccentric sleeves shown 60a, 60b 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. 6 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.

As shown in Figure 6, on the eccentric sleeves 60a, 60b in the axial direction of the Roller body 61 a number of cylinder sleeves 62, 63 rotatably mounted side by side, which can be rotated independently of each other. In the illustrated embodiment 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. Instead of 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.

According to FIG. 6, 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. Due to the use of the eccentric sleeves 60a and 60b in a corresponding manner Arrangement relative to each other takes the distance measured in the radial direction between the protruding jacket areas A and the recessed jacket areas B above the circumference of the body of revolution seen from the straight line to both Sides evenly up to the diametrically opposite side of the Rotary body structure evenly. In Figure 6, the rotational body structure in the Longitudinal section shown, which includes the two extremes, namely the straight line on the one hand and the maximum distance between the above in the radial direction Jacket areas A and recessed jacket areas B on the other hand.

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. In the embodiment 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. By twisting of the roller body 61, the radially projecting sections of the eccentric sleeves 60a, 60b about the axis of rotation of the roller body 61 together with the roller body 61 turned. Thus, 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 °. When adjusting the roller body 61 remains due to the continuous change in the radial distance between the two Extreme of the outer contour of the rotating body structure is the theoretically mean path the paper web always exist, so that also between an upstream and a downstream printing point the web length remains constant and therefore none Circumference register adjustment must be made.

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. When the rotary body structure is converted, the geometric relationships of the eccentric sleeves 60a, 60b and / or the cylinder sleeves 62, 63 can be varied. 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. Herein 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. 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. On the opposite side of the Roller body 22 presses an axially displaceably mounted on the roller body 22 Pressure shifting element 23 against the outermost of the ring elements 20 and 21 there is also a deformable ring element 20, but basically by a dimensionally stable Ring element 21 can be formed. The ring elements 20 lined up next to one another and 21 are between the pressure slide member 23 and the abutment 24th edged and by advancing the Andruchverschiebelements 23 in the direction of Abutment 24 pressed against each other in the axial direction. Under the both sides initiated axial pressure force, the ring members 20 over their entire circumference evenly curved or warped elastically outwards. In the arched State form the lateral surfaces of the deformable ring elements 20 the above Jacket areas A and the jacket surfaces of the dimensionally stable ring elements 21 die recessed jacket regions B of the rotating body structure 6. In FIG. 9 this is Shown body of revolution in its neutral position, in which the ring elements 20th and 21 form a smooth, straight, circular cylindrical outer surface when the axial pressure is taken away.

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. However, 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. In the exemplary embodiment, 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. In the fourth embodiment, 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.

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. 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. Through the 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, and 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. In the formation of the wave valleys, 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 ¼ 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 ¼ Web widths two protruding jacket areas A to lie.

reference numeral

first pressure gap

second pressure gap, upstream pressure gap

third pressure gap, downstream pressure gap

fourth pressure gap

Body of revolution

Body of revolution

Machine frame

Machine frame

first roles

second roles

lever

wave

Swivel arms

Tab

lever

37

wave

38

Swivel arms

19a

spindle

19b

carriage

39

pressable ring elements

40

dimensionally stable ring elements

41

Roller body

42

Pressure shifting element

43

Abutment

44

Actuating means

45

bolt

27-29

-

30th

pressable ring elements

31

dimensionally stable ring elements

32

Roller body

33

Pressure connection

34

Pressure line

35

Pressure line

36

Ring channel

37-39

-

1

pressable ring elements

2nd

dimensionally stable ring elements

3rd

Roller body

4th

Pressure connection

5

Pressure line

6

Pressure line

7

cavity

8th

Recess

9

-

10th

-

11

protruding jacket areas

12th

recessed jacket areas

13

Roller body

60a, b

Eccentric sleeve

61

Roller body

62

1. Cylinder sleeve

63

2. Cylinder sleeve

64

transmission

A

protruding jacket areas

B

recessed jacket areas

D

largest diameter

d

smallest diameter

F

Humidity

M

drive

N

Neutral axis of rotation

P

Axes of rotation of the first roles

Q

Rotation axes of the second rollers

S

Web tension

T

Paper type

V

Web speed

W

train

á

Wrap angle

Claims (23)

Rotary body structures for a web width correction between an upstream printing nip and a downstream printing nip of a rotary printing press, in which a continuous web is printed one after the other in a print production, wherein the rotating body structure (5; 6) is arranged rotatably to one side of the web in the web running direction and in the axial direction alternately next to each other radially projecting and radially projecting jacket regions (A, B) in order to deform the web in a wave shape transverse to its running direction, characterized in that the rotating body structure (5; 6) is arranged in a path of the web between the upstream pressure gap (2) and the downstream pressure gap (3) or the web is guided on its way between these pressure gaps (2, 3) such that the web Rotating body structures (5; 6) in the protruding jacket areas (A) and in the back jacket areas (B) continuously wraps. Rotary body structure according to claim 1, characterized in that the Rotary body structures (5; 6) in a different print production than the deflection roller is used for a web that enters the downstream printing gap (3) or runs out of the upstream pressure gap (2) and the other of these Pressure columns (2, 3) does not run through. Rotary body structure according to one of the preceding claims, characterized characterized in that the above jacket areas (A) and the recessed jacket areas (B) with respect to the web at a height or can be brought up to a height at least to such an extent that the rotational body structure (5; 6) can be used as a deflection roller without web width correction. Rotary body structure according to one of the preceding claims, characterized characterized in that the rotating body structure (5; 6) is radially adjustable, wherein the protruding jacket areas (A) and the recessed jacket areas (B) in a neutral position of the rotary body structure (5; 6) a common one Have neutral position axis of rotation (N) and with an adjustment relative to the Neutral position axis of rotation (N) symmetrically towards and from the web Web be moved away. Rotary body structure according to one of the preceding claims, characterized characterized in that the body of revolution (5; 6) radially as a whole is shiftable to a change in web length between the upstream To be able to compensate for the pressure gap (2) and the downstream pressure gap (3). Device according to one of the preceding claims, characterized in that that the protruding jacket areas (A) by a group of first rollers or sleeves (10; 62) and the recessed jacket areas (B) by a Group of second rollers or sleeves (11; 63) are formed. Rotary body structure according to the preceding claim, characterized characterized in that at least the rollers (10; 11) cross one of the groups Axes of rotation of these rollers (10; 11) and relative to the rollers (11; 10) of the others Group are arranged radially movable. Rotary body structure according to one of claims 1 to 6, characterized by a roller body (61) with eccentric sleeves (60a, 60b) on which cylinder sleeves (62, 63) are each independently pivoted, the eccentric sleeves (60a, 60b) sit non-rotatably on the roller body (61). Rotary body structure according to the preceding claim, characterized characterized in that the eccentric sleeves (60a, 60b) and / or the cylinder sleeves (62, 63) are designed differently in the axial direction of the roller body (61), so that the cylinder sleeves (62, 63) alternately projecting (A) and projecting (B) Form jacket areas. Rotary body structure according to the preceding claim, characterized characterized in that the roller body (61) is rotatably adjustable about an axis of rotation (N) is arranged to the above (A) and / or back (B) To move the cladding areas towards and away from the web. Rotary body structure according to one of claims 1 to 5, characterized in that that the rotary body structure (5; 6) is a rotatably mounted roller which on a Roll surface area the protruding jacket areas (A) and the back Has jacket areas (B). Device according to the preceding claim, characterized in that the rotating body structure (5; 6) comprises a roller body (22; 32; 42) which are arranged radially outward pushable ring elements (20; 30; 40), which form the above jacket areas (A). Rotary body structure according to the preceding claim, characterized characterized in that in the roller body (22; 32; 42) pressure lines (34, 35; 44, 45) and can be connected to a pressure connection (33; 43) through which through the pushable ring elements (20; 30; 40) for pushing with a pressurized fluid can be applied. Rotary body structure according to claim 12, characterized in that the pressable ring elements (20) are elastically deformable, the recessed jacket areas (B) are formed by dimensionally stable ring elements (21), the deformable ring elements (20) and dimensionally stable ring elements (21), which are arranged between two deformable ring elements (20), are axially displaceable relative to one another on the roller body (22)
and the deformable and dimensionally stable ring elements (20, 21) are enclosed between a pressure displacement element (23) mounted axially displaceably on the roller body and an axial abutment (24). Rotary body structure according to one of claims 1, 2, 5 or 11, characterized characterized in that the rotational body structure (5; 6) by a single Roll body (52) is formed, the projecting jacket regions (A) and recessed jacket areas (B) as an unchangeable surface shape having. Arrangement of ration body structures, characterized in that that at least two rotary body structures (5; 6) according to one of the preceding claims are pivotally mounted on pivot arms about a common axis, wherein either only one or only the other of the at least two rotating body structures (5; 6) can be pivoted into a working position in which it is wrapped by the web, while the other of the at least two rotating body structures (5; 6) does not pivot the web influenced, and that protruding jacket areas (A) of one of the at least two rotating body structures (5; 6) protrude further in relation to the web in its working position than projecting jacket areas (A) of the other of the at least two rotating body structures (5; 6) in its working position. Arrangement of rotating body structures according to the preceding claim, characterized in that a swivel arm of that rotary body structure (5; 6), whose protruding jacket regions (A) protrude further, is shorter than one Swivel arm of the other of the at least two rotating body structures (5; 6). Method for web width correction between an upstream printing nip and a downstream printing nip of a rotary printing press, in which a) printed the web in the upstream printing nip (2) and in the downstream printing nip (3) one after the other and b) a wave-shaped course is impressed transversely to the web running direction between the pressure nips (2, 3) by means of a rotary body structure (5; 6),
characterized in that c) the web continuously wraps around the body of revolution (5; 6) with a wrap angle (a) of at least 3 °. Method according to the preceding claim, characterized in that the undulating course only by wrapping the to one side of the web arranged rotary body structure (5; 6) is impressed. A method according to claim 18 or 19, characterized in that the rotating body structure (5; 6) alternately in the axial direction has mutually adjacent and protruding jacket regions (A; B) with respect to the web
and changes in the web width can be corrected by a radial movement of the projecting jacket regions (A) relative to the projecting jacket regions (B). Method according to the preceding claim, characterized in that a Change the length of the web between the upstream printing gap (2) and the downstream pressure gap (3) is prevented by the radial movement of the protruding jacket areas (A) and the recessed jacket areas (B) mirror symmetry with respect to a longitudinal axis of the body of revolution (5; 6) is. A method according to claim 20, characterized in that a change in Path length between the upstream printing gap (2) and the downstream Pressure gap (3) is prevented by the radial movement of the above Jacket areas (A) and the rear jacket areas (B) asymmetrical is opposite in relation to a longitudinal axis of the body of revolution (5; 6). Method according to one of claims 18 to 22, characterized in that a change in the length of the track caused by the correction between the upstream pressure gap (2) and the downstream pressure gap (3) by a radial displacement of the entire rotating body structure (5; 6) is prevented.

Images