DE20220298U1 - Web-fed printing machine has printer unit printing width of six axially adjacent pages, with superstructure, at least one roller and folder and two printing towers - Google Patents

Abstract

The printer unit (02) prints a web (03) with six axially adjacent printed pages and has a superstructure (04) in which the web is divided longitudinally into three part-webs (03a,03b,03c). A folder structure has at least one roller for conveying the part-webs and at least one folder device each driven mechanically separately by drive motors. At least two printing towers (01) each have at least two printer units and s folder structure which has two vertically staggered groups of at least two formers each and at least one group of leading rollers.

Description

Folding structure of a web-fed rotary printing press and web-fed rotary printing press

The invention relates to a folding structure of a web-fed rotary printing press and a web-fed rotary printing press according to the preamble of claim 1.

DE 25 28 008 A1 shows a printing machine for a direct printing process with forme cylinders which can be equipped with six printing plates in the axial direction and two in the circumferential direction, and with counter-pressure cylinders which can be equipped with three printing plates in the axial direction and one printing felt in the circumferential direction. Both the printing plates arranged next to one another and the printing felts arranged next to one another are arranged offset from one another in the circumferential direction.

DE 25 10 057 A1 also discloses a printing machine with a direct printing process, wherein the forme cylinder, which works together with an impression cylinder, carries six printing plates along its width and two along its circumference.

JP 56-021860 A discloses a printing unit with forme, transfer and impression cylinders, whereby each of the three cylinders is driven by its own drive motor.

DE 41 28 797 A1 discloses a triple-width web-fed rotary printing press with two folding formers arranged on two different levels one above the other.

From "Newspapers & Technology", December 2000, a printing machine with six newspaper page wide printing units is known. The printing units are designed as bridge printing units, with the transfer cylinders with rubber blanket sleeves

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are occupied.

WO 01/70608 A1 discloses a turning bar arrangement, wherein two turning bars, each of which is essentially the width of a partial web, are each arranged on a support so as to be displaceable transversely to the direction of the incoming partial web. A register roller is arranged laterally outside the side frame, the longitudinal axis of which runs essentially parallel to the side frame and which is also displaceable along a rail in a direction transversely to the direction of the incoming partial web.

From US 4 671 501 A a folding structure is known, wherein two folding formers are arranged one above the other, wherein the webs are cut lengthwise after passing through run-on rollers in front of a third former, the partial webs are rotated by 90° above a third former and then combined into two strands and fed to the two formers arranged one above the other.

EP 10 72 551 A2 discloses a folding structure with two groups of folding formers offset vertically from one another. Above each of the groups of folding formers there is a harp, i.e. a group of collecting, removal or harp rollers, via which the relevant partial webs are fed to the associated group of folding formers.

WO 97/17200 A2 discloses a folding structure in which cut partial webs offset transversely to one another are fed to different folding formers. The folding formers arranged horizontally next to one another are partly arranged vertically offset from one another.

DE 44 19 217 A1 shows a superstructure of a web-fed rotary printing press with a turning device, whereby partial webs are offset by half a partial web width in order to guide them over one another and feed them to a common folding former.

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The invention is based on the object of creating a folding structure of a web-fed rotary printing press and web-fed rotary printing press.

The object is achieved according to the invention by the features of claim 1.

The advantages that can be achieved with the invention are in particular that a simple, cost-effective and space-saving design is possible while at the same time allowing a high degree of variability in the product or intermediate product.

The advantages are that, compared to a double-width printing machine, production reliability is significantly increased while achieving the same target thickness of a product. However, while maintaining the number of printing units, the output of the printing machine or each printing unit can be increased by 50%.

The number of roll changers (investment), the frequency of roll changes (production reliability) and the set-up time when pulling in webs (cycle times) can be reduced compared to a double-width printing press for the same product thickness.

In an advantageous design, the printing units are designed as nine-cylinder satellite printing units, which results in high precision in the color register and a low-vibration design. Vibrations are also reduced by the advantageous arrangement, design and fastening of the lifts on the cylinders. On the one hand, openings on the lateral surfaces are minimized in the circumferential direction. Furthermore, at least on the transfer cylinder, the openings can be arranged alternately in the circumferential direction so that at least on one section length there is always a closed lateral surface with the form

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or satellite cylinders. Thirdly, out-of-roundness and manufacturing costs are minimized by providing axial channels along the entire effective length of the bale, but openings to the outer surface only exist in the sections mentioned. Devices for attaching elevator ends and/or filler pieces are then optionally inserted into the channels.

At least six devices for axial positioning of printing forms are arranged in the channel or channels of the forme cylinders in the axial direction. These are designed, for example, as register pins that work together in a form-fitting manner with the ends of the printing forms and are arranged within the channel so that they can be moved axially manually or remotely.

With regard to a register-accurate and reproducible loading of the form cylinders with printing forms, it is advantageous to design the printing units with associated pressing devices. With these, the covers resting on the cylinder's outer surface can be fixed by at least one pressing element as required, while one end of a cover or several covers is released for removal or loading.

The mechanically independent drive of the satellite cylinder(s) from the cylinder pairs offers particular advantages in terms of the possibility of variable operation. For example, set-up, e.g. a flying printing forme change or washing, can take place during production. Conversely, a web can be drawn in while other cylinders or cylinder pairs are stationary or running a set-up program. It is also advantageous to operate the satellite cylinder at a surface speed that is different from the other cylinders when using rubber blankets with positive or negative conveying properties.

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In an advantageous embodiment, a superstructure of the printing press has at least one longitudinal cutting device with at least five knives spaced apart transversely to the paper travel direction. In an advantageous embodiment, two register devices that can be moved transversely to the paper travel direction are provided for each printing tower (or eight printing stations) to compensate for the travel paths of the partial webs. In a further development, these can each be structurally connected to a partial web-wide turning device. Subsequent guide elements assigned only to partial webs are also essentially only designed to be partial web-wide, for example. These designs enable the web to be transported with little vibration and thus with a precise fit. Web tension fluctuations caused by the inertia of long, strong guide elements driven only by the partial web(s) (e.g. during load changes, changes in printing speed) can be effectively reduced.

In order to ensure reliable operation and cost-effective construction, it is also advantageous to provide the option of turning a partial web by an odd multiple of half a partial web in the superstructure. This eliminates the need to pull in and print partial webs with half the width of the former (e.g. a newspaper page).

In terms of costs and space-saving design, it is advantageous in one design to arrange a so-called harp, i.e. several generally non-driven take-up rollers, in front of only one of two formers arranged one above the other. Webs from the harp can be transferred to the other former. Strands of variable thickness or number of webs can be fed to the two formers arranged vertically one above the other from the same alignment of partial webs lying one above the other.

In one embodiment, partial webs from a harp assigned to one former group can be loaded onto the other former group and vice versa. In an advantageous embodiment, only one of two formers arranged one above the other is assigned a

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a so-called harp, i.e. several generally non-driven take-up rollers (also called collecting or take-off rollers). Webs from the common harp can then be transferred to the other former. Strands of variable thickness or number of webs can be fed to the two formers arranged vertically one above the other from the same alignment of partial webs lying one above the other.

In an advantageous design of a turning device, the partial web can only be moved or offset by an odd multiple of half the partial web width. This makes it possible to avoid, for example, having to print very narrow webs or having to provide additional printing units with little effort. The design of at least one of the turning bars that can be moved across the web enables a high level of variability.

The mechanically independent drive of the rollers of the former structure and/or the folder from the printing units is particularly advantageous with regard to good registration and variable operation.

Embodiments of the invention are illustrated in the drawings and are described in more detail below.

Show it:

Fig. 1 shows a web-fed rotary printing machine in side view; Fig. 2 shows a schematic front view of a printing unit; Fig. 3 shows a schematic plan view of a printing unit; Fig. 4 shows an elevator in perspective view;

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Fig. 5 a forme cylinder; a: in perspective view, b: in longitudinal section, c: a holding element, d: a holding element with register device;

Fig. 6 a transfer cylinder; a: in perspective view, b: in longitudinal section, c: a holding element, d: a filling element;

Fig. 7 shows a device for pressing a winding mechanism against a cylinder;

Fig. 8 shows a first embodiment for the drive of a nine-cylinder satellite printing unit;

Fig. 9 shows a second embodiment for the drive of a nine-cylinder satellite printing unit;

Fig. 10 shows a third embodiment for the drive of a nine-cylinder satellite printing unit;

Fig. 11 shows an embodiment of the embodiment according to Fig. 8;

Fig. 12 an overview of a superstructure;

Fig. 13 shows a first embodiment of a short register device;

Fig. 14 shows a second embodiment of a short register device;

Fig. 15 an example of a path turn;

Fig. 16 is a front view of the harp with reversed panel according to Fig. 15;

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Fig. 17 shows a folding structure of a web-fed rotary printing press; Fig. 18 shows a side view of the folding structure with web guide; Fig. 19 shows a front view of the folding structure with web guide.

The web-fed rotary printing press shown as an example in Fig. 1 has a left and a right section, each with at least two printing towers 01. The printing towers 01 have printing units 02 which are designed, for example, to be at least three times as wide, i.e. for printing six newspaper pages arranged axially next to one another. The printing units 02 are designed as satellite printing units 02. The advantageous design of the printing units 02 as nine-cylinder satellite printing units 02 ensures very good registration and low fan-out. The printing units 02 can also be designed as ten-cylinder satellite printing units 02 or, if necessary, as printing units that can be operated in rubber-against-rubber printing, such as several bridge printing units or an H-printing unit 02. Webs 03 from rolls (not shown) are fed to the printing units 02, in particular using roll changers.

Downstream of a web 03 passing through the printing towers 01 or printing units 02, here above the printing towers 01, a superstructure 04 is provided for each section, in which the web 03 or webs 03 are cut at longitudinal cutting devices 06, partial webs are offset and/or overturned by means of turning devices 07, are aligned with one another in longitudinal register by means of register devices 08 only indicated in Fig. 1 and can be guided one above the other. Seen downstream in the direction of web travel, the superstructure 04 has at least one so-called harp 09 with a number of harp or run-up rollers arranged one above the other, guiding the webs 03 or partial webs 03a; 03b; 03c. The harp 09 determines the funnel inlet of the webs 03 guided one above the other. The webs 03 experience a change of direction via this harp 09 and

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are then combined either as one strand or as several strands and fed to at least one folding structure 11.

In the example, two folding structures 11 are arranged between the sections, each of which has, for example, folding formers arranged on two different levels one above the other. However, the printing press can also have just one common folding structure 11 arranged between the sections, or just one section and an associated folding structure 11. The respective folding structure 11 can also be designed with just one level of folding formers. One or more folding devices 12 are assigned to each folding structure 11.

The printing unit 02 has several, in the example four, printing units 13, by means of which ink can be applied to the web 03 from an inking unit 14 via at least one cylinder 16 designed as a forme cylinder 16 (Fig. 2). In the present example of an embodiment of the printing unit 02 as a satellite printing unit 02, the printing unit 13 is designed as an offset printing unit 13 for wet offset and, in addition to the inking unit 14, has a dampening unit 20 and a further cylinder 17 designed as a transfer cylinder 17. The transfer cylinder 17 forms a printing point with a printing cylinder 18 forming an abutment. In the example in Fig. 1, the printing cylinder 18 is designed as a satellite cylinder 18, which forms further printing points with further transfer cylinders 17 of further printing units 13 in the print-on position. If the printing units are designed as a double printing unit in rubber-counter-rubber printing, the printing cylinder 18 could also be designed as a transfer cylinder 18. The same parts are given the same reference symbols unless necessary to distinguish them. However, a difference in the spatial position can exist and is generally not taken into account if the same reference symbols are assigned.

In an advantageous embodiment, the inking unit 14 has an ink fountain 15 that extends over six printed pages. In another embodiment, three ink fountains 15, each with a diameter of approximately two

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·

Ink fountains 15 with a width of 15 mm for printing pages are arranged next to one another in the axial direction. The dampening unit 20 is advantageously designed as a four-roller spray dampening unit 20.

In a first embodiment, the forme cylinder 16 has a circumference of between 850 and 1,000 mm, in particular between 900 and 940 mm. The circumference is designed, for example, to accommodate two vertical printed pages, e.g. newspaper pages in broadsheet format, by means of two supports 19, e.g. flexible printing forms 19, that can be fixed one behind the other in the circumferential direction on the forme cylinder 16. The printing forms 19 can be mounted on the forme cylinder 16 in the circumferential direction and, in the embodiment shown in Fig. 3, can each be individually replaced as a single printing plate equipped with a printing page in the axial direction.

The length L16 of the usable bale of the forme cylinder 16 in the first embodiment is, for example, 1,850 to 2,400 mm, in particular 1,900 to 2,300 mm, and is dimensioned in the axial direction to accommodate, for example, at least six vertical printed pages arranged next to one another, in particular newspaper pages in broadsheet format (see Fig. 3, sections A to F). It depends, among other things, on the type of product to be manufactured whether only one printed page or several printed pages are arranged next to one another in the axial direction on a printing forme 19. In an advantageous, wider variant of the first embodiment, the length L16 of the usable bale is between 2,000 and 2,400 mm.

In a second embodiment, the forme cylinder 16 has a circumference of between 1,300 mm and 1,300 mm, in particular 1,000 to 1,200 mm. The length L16 of the usable bale is e.g. 1,950 to 2,400 mm, in particular 2,000 to 2,400 mm. The layout corresponds to the above-mentioned embodiment.

The transfer cylinder 17 in the first version also has a circumference of, for example, between 850 and 1,000 mm, in particular between 900 and 940 mm. The length L17 of the

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The usable roll of the transfer cylinder 17 in the first embodiment is, for example, 1,850 to 2,400 mm, in particular 1,900 to 2,300 mm, and is arranged longitudinally next to one another, for example, with three covers 21, e.g. rubber blankets 21 (sections AB to EF). They extend essentially around the entire circumference in the circumferential direction. The rubber blankets 21 are arranged alternately, e.g. offset by 180°, to one another (Fig. 3), which has a positive effect on the vibration behavior of the printing unit 13 during operation. In the wider variant of the first embodiment, the length L17 of the usable roll is also between 2,000 and 2,400 mm.

In the second embodiment, the transfer cylinder 17 has a circumference of between 980 and 1,300 mm, in particular between 1,000 and 1,200 mm. The length L17 of the usable bale is, for example, between 1,950 and 2,400 mm, in particular between 2,000 and 2,400 mm. The arrangement of lifts 21 corresponds to the first embodiment.

The diameter of the bales of the cylinders 16; 17 in the first above-mentioned version is e.g. from 270 to 320 mm, in particular from approx. 285 to 300 mm. In the second above-mentioned version, the diameter of the bales of the cylinders 16; 17 is e.g. from approx. 310 to 410 mm, in particular from 320 to approx. 380 mm. The ratio of the length of the usable bales of the cylinders 16; 17 to their diameter should be 5.8 to 8.8, e.g. from 6.3 to 8.0, in the wide version in particular from 6.5 to 8.0.

The length L16; L17 of the usable bale is understood here to be the width or length of the bale which is suitable for accommodating lifts 19; 21. This also corresponds approximately to a maximum possible web width of a web 03 to be printed. In relation to the entire length of the bale of the cylinders 16; 17, the width of any existing bearer rings, any existing grooves and/or any existing lateral surface areas which must be accessible, for example, to operate tensioning and/or clamping devices would have to be added to this length L16; L17 of the usable bale.

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In an advantageous embodiment, the satellite cylinder 18 also has essentially the aforementioned dimensions and ratios of at least the associated transfer cylinder 17.

The covers 19; 21 are, as shown schematically in Fig. 4, e.g. designed as flexible plates, wherein the cover 21 designed as a rubber blanket 21 is designed as a so-called metal printing blanket 21 with an elastic and/or compressible layer 22 (dashed line) arranged on a carrier plate 23 (in Fig. 4 the reference numerals relating only to the metal printing blanket 21 are connected in dashed lines). A plate-shaped printing form 19 or a carrier plate 23 for a rubber printing blanket usually consists of a flexible but otherwise dimensionally stable material, e.g. of an aluminum alloy, and has two opposite ends 24; 26 to be fastened in or on the cylinder 16; 17 with a material thickness MS of e.g. 0.2 mm to 0.4 mm, preferably 0.3 mm, wherein these ends 24; 26 are designed as hanging legs 24; 26 are each bent along a bending line based on the extended length I of the cover 19; 21 by an angle α; β between 40° and 140°, preferably 45°, 90° or 135° (Fig. 4). A leading end 24 is bent, for example, at an acute angle α of 40° to 50°, in particular 45°, and a trailing end 26 is bent at an angle β of 80° to 100°, in particular 90°. If only a single cover 21 is applied in the circumferential direction of the cylinder 16; 17, in particular of the transfer cylinder 17, the length I of the cover 21 corresponds almost to the circumference of this cylinder 17.

Basically, the bevelled ends 24; 26 of the lifts 19; 21 can now be inserted into a slot-shaped opening on the circumference of the respective cylinder 16; 17, which is parallel to the axis in the longitudinal direction, whereby the ends 24; 26 are held, for example, by their shape, friction or deformation. However, they can also be additionally held by means of spring force, pressure medium or a force effective during operation.

"y

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Centrifugal force actuated means. The slot-shaped openings for printing plates 19 arranged next to one another in the axial direction on the forme cylinder 16 are, in an advantageous embodiment, each arranged in a line, e.g. as a continuous slot-shaped opening (as described below), while the openings for the rubber blankets 21 arranged next to one another on the transfer cylinder 17 are not continuous, but alternately offset from one another in the circumferential direction by 180°.

Fig. 5a and b) shows a perspective view of an example of an advantageous design of the forme cylinder 16. Two channels 27 are provided in the cylinder 16, with both channels 27 extending continuously in the axial direction of the cylinder 16 at least over the entire length of the six sections A to F in the bale (Fig. 5b). They are arranged offset from one another in the circumferential direction of the cylinder 16, e.g. by 180°. The channels 27 arranged below a jacket surface 30 in the interior of the cylinder 16, e.g. designed as circular bores, have a narrow, slot-shaped opening 28 to the jacket surface 30 of the cylinder 16 at least over the length of the six sections A to F (Fig. 5a). A slot width s16 of the opening 28 on the forme cylinder 16 in the circumferential direction is less than 5 mm and is preferably in the range of 1 mm to 3 mm (Fig. 5c).

The bent ends 24; 26 of the printing form 19 can now each be inserted into one of the openings 28 that are axially parallel in the longitudinal direction on the circumference and can be fixed, at least the trailing end 26, by a holding device 29, 31 arranged in the channel 27.

The holding device 29, 31 here has at least one clamping piece 29 and a spring element 31 (Fig. 5c). The trailing suspension leg 26 (see Fig. 4) which is bent at a right angle and not shown preferably comes to rest on a wall of the opening 28 which is essentially complementary to the bent and is held there by the clamping piece 29 by a spring element 31 on the

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Clamping piece 29 is pressed against the force exerted by ...

In an advantageous embodiment, there is not just one clamping piece 29 in each channel 27, but several clamping pieces in the form of segments, each with at least one spring element 31, are arranged axially next to one another over the length of the sections A to F (shown "pulled out" from the cylinder 16 in Fig. 5a). In the exemplary embodiment, several, e.g. six, such clamping pieces 29 are arranged for each section A to F as shown in Fig. 5c, with a register element 33 (Fig. 5d) having a register stone 35 being arranged centrally between the clamping elements 29 of each section A to F, here between the third and fourth clamping elements 29 of each section A to F. The register stone 35 or register pin 35 can be manually displaced and adjusted in the axial direction, for example in a groove of a base 34. In a further development not shown, the register stone 35 can also be axially inserted into a free cavity in the channel 27 or the An actuating device guided by the fitting element 33, e.g. a motor-driven threaded spindle, must be axially movable.

The adjusting means 32 is designed in the embodiment shown in such a way that when actuated, the holding device(s) 29, 31, i.e. all clamping pieces 29, are simultaneously closed or released over the length of the sections A to F. The adjusting means 32 is shown as "pulled out" from the cylinder 16 in Fig. 5a as a respective extending at least over the length of the sections A to F, running axially in the channel 27 and with

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A reversibly deformable hollow body 32 that can be actuated by pressure medium, e.g. designed as a hose 32. According to Fig. 5c, this hose 32 is arranged in the channel 27 in such a way that it cooperates with the clamping pieces 29 in such a way that it counteracts the spring elements 31 that self-lockingly close the holding device when actuated. It is guided through the areas of the registration elements 33 (Fig. 5d).

Fig. 6a and b) shows a perspective view of an example of an advantageous embodiment of the transfer cylinder 17. Two channels 36; 37 are provided in the cylinder 17, with both channels 36; 37 extending continuously in the axial direction of the cylinder 17 at least over the entire length of the six sections A to F or three sections AB; CD; EF in the bale (Fig. 6b). They are arranged offset from one another in the circumferential direction of the cylinder 17, e.g. by 180°.

The two channels 36; 37 arranged below a jacket surface 40 in the interior of the cylinder 17, e.g. designed as circular bores, have a total of e.g. three narrow, slot-shaped openings 38; 39; 41, each of which runs axially and extends at least over the length of a section AB; CD; EF, towards the jacket surface 40 of the cylinder 17 (Fig. 6a). Two of the three openings 38; 39 are connected to the same channel 36 and are aligned with one another in the axial direction, but spaced apart from one another on the jacket surface 40. Axially between the two openings 38; 39 there is a section U without an opening, which continues the shape of the rest of the jacket surface 40 and is in particular undisturbed. The two aligned openings 38; 39, e.g. connected to the same channel 36, are preferably the openings 38; 39 close to the front side. 39, the third opening 41 extending axially at least over the middle gate CD and being arranged offset by 180° to the other openings 38; 39. A slot width s17 of the uncovered opening 38; 39; 41 on the transfer cylinder 17 in the circumferential direction is less than 5 mm and is preferably in the range of 1 mm to 3 mm (Fig. 6c). For manufacturing purposes, radial

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extending bores 42 may be provided which can be closed or are closed in the operating state of the cylinder by means of a plug (not shown) (Fig. 6b). The plug has an outer surface which continues the otherwise cylindrical contour of the cylinder 17 in the assembled state in the area of the bore 42. In the circumferential direction of the cylinder 17 in a section perpendicular to the axis of rotation, in an advantageous embodiment only one of the openings 38; 39; 41 or one of the openings 38; 39; 41 shortened by the plugs is arranged one behind the other. Viewed in this section, the openings 38; 39; 41 or the openings 38; 39; 41 shortened by the plugs do not overlap.

The bent ends 24; 26 of the rubber blanket 21 can now each be inserted into one of the openings 38; 39; 41 that are parallel to the axis in the longitudinal direction on the circumference and can be fixed, at least the trailing end 26, by at least one holding device 43, 44 arranged in the channel 36; 37. Preferably, the two ends 24; 26 of the same rubber blanket 21 are guided through the same opening 38; 39; 41 into the same channel 36; 37.

The holding device 43, 44 here has at least one clamping piece 43 and one spring element 44 (Fig. 6c). The trailing suspension leg 26 (see Fig. 4), which is bent at a right angle and is not shown, preferably comes to rest on a wall of the opening 38; 39; 41 that is essentially complementary to the bent and is pressed there by the clamping piece 43 by a force exerted by the spring element 44 on the clamping piece 43. The leading suspension leg 24 (see Fig. 4), which is bent at an acute angle and is not shown, preferably comes to rest on a wall of the opening 38; 39; 41 that is essentially complementary to the bent and which forms a suspension edge or nose with the outer surface 40 at an acute angle α' of 40° to 50°, in particular 45°. To release the clamping of the trailing end 26, at least one actuating means 46; 47; 48 is provided in the channel 36; 37, which, when actuated, moves the spring element 44 onto the

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clamping piece 43 counteracts the force exerted by the clamping piece 43 and pivots the clamping piece 43 away from the wall. Advantageously, at least one adjusting means 46; 47; 48 is provided for each of the three openings 38; 39; in the respectively associated channel 36; 37 (shown "pulled out" from the cylinder 17 in Fig. 6a).

In an advantageous embodiment, there is not only one clamping piece 43 in each channel 36; 37, but over the length of the sections AB; CD; EF, a plurality of clamping pieces 43 are arranged axially next to one another as individual segments, each with at least one spring element 44 (shown "pulled out" from the cylinder 17 in Fig. 6a). In the exemplary embodiment, a plurality of, e.g. ten, such clamping pieces 43 are arranged according to Fig. 6c for each section AB; CD; EF and each opening 38; 39; 41. In sections AB; CD; EF of the respective channel 36; 37, which do not have an opening to the jacket surface 40, at least one filling element 49 (Fig. 6d) is arranged in the channel 36; 37 instead of the holding device 43, 44 or the holding devices 43. In the example, a plurality of, e.g. eleven, of these filling elements 49 are arranged as individual segments in the relevant section AB; CD; EF of the channel 36; 37, which does not have an opening. CD; EF, i.e. in the area between the sections A and B or E and F, here between the fifth and sixth clamping element 43, a filling element 49 (Fig. 6d) can also be arranged. The filling element 49 essentially has a cross-section modeled on the cross-section of the channel 36; and at least one opening 51 extending in the axial direction through which an operating means for the actuating means 46; 47; 48 can be guided.

The adjusting means 46; 47; 48 is designed in the embodiment shown in such a way that when actuated, the holding device 43, 44 of a section AB; CD; EF, i.e. all clamping pieces 43 of a section AB; CD; EF, are closed or released simultaneously. The adjusting means 46; 47; 48 is shown "pulled out" of the cylinder 17 in Fig. 6a. In the channel 36 (with two openings 38; 39) a

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Adjusting means 46; 47 over at least the corresponding length of the section AB; EF. The adjusting means 48 assigned to the middle opening 41 also extends over at least the corresponding length of the assigned section CD. However, it can also extend at least on one side to the front side of the cylinder 17 if this is advantageous for the supply of operating materials (Fig. 6a). The adjusting means 46; 47; 48 are each designed as a reversibly deformable hollow body 46; 47; 48, e.g. as a hose 46; 47; 48, which runs axially in the channel 36; 37 and can be actuated with pressure medium. This hose 46; 47; 48 is arranged in the channel 36; 37 in accordance with Fig. 6c so as to cooperate with the clamping pieces 43 in such a way that it counteracts the spring elements 44 which self-lockingly close the holding device 43, 44 when actuated. It is guided through the areas of filling elements 49 to be passed through these or their opening 51 (Fig. 6d).

In another embodiment of the channels 36; 37, these may not be continuous over the entire length. For example, in the area of each section AB; CD; EF, a channel 36; 37 is provided, if necessary with a corresponding holding device, with the channel 37 of the middle elevator 21 being offset by 180° from the two outer ones. This is only indicated schematically in Fig. 6e.

In an embodiment that is particularly advantageous in connection with the six-page-wide printing units 02 or cylinders 16; 17, at least two cylinders 16; 17, in particular two forme cylinders 16, of at least one of the printing towers 01 are each assigned a device 52 for pressing a cover 19; 21 onto a cylinder 16; 17, in particular a printing forme 19 onto the forme cylinder 16 (hereinafter referred to as pressing device 52). This is advantageous, for example, if a quick, e.g. flying plate change is to be carried out in two corresponding printing units 13. In particular, it is advantageous for a quick, safe and precise product change if all forme cylinders 16 of a printing tower 01 are assigned such a pressing device 52. A corresponding pressing device

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52 has one or more pressing elements 53; 54, e.g. strips, tappets or rolling elements 53; 54, which can be selectively attached to one and/or more elevators 19; 21. This enables a controlled and guided pulling in or clamping and/or detaching or removing of the elevator 19; 21. It is also possible to move an end 24; 26 of the elevator 19; 21 into the corresponding channel 27; 36; 37 or the opening 28; 38; 39; 41 or to hold down a detached end 24; 26 or the partially detached elevator 19; 21 in a desired position. The pressing device 52 extends along the cylinder 16; 17 at least in the entire area of sections A to F ₁ , ie in the area of the bale effective for printing.

The design of the pressing device 52 described in Fig. 7 is particularly advantageous in conjunction with the design described in Fig. 5 for the common actuating means 32 extending over all sections A to F. In this configuration, individual or group-wise mounting, changing and/or removing is also possible for six printing forms 19 arranged next to one another on the forme cylinder 16, without an increased outlay on actuating devices or operating medium supply having to take place within the forme cylinder 16. This also significantly simplifies production, assembly and maintenance.

The pressing device 52 has at least one first pressing element 53, e.g. rolling element 53, for each section A to F (with six adjacently arranged elevators 19) or section AB; CD; EF (with three adjacently arranged elevators 21). In an advantageous embodiment according to Fig. 7, it has a second pressing element 54, e.g. rolling element 54, for each section A to F or section AB; CD; EF, which is spaced from this first rolling element 53 in the circumferential direction of the cylinder 16; 17. In Fig. 7, for the case of the forme cylinder 16, only middle sections B, C and D and the rolling elements 53; 54 assigned to these sections B, C and D are shown. For each section A to F or AB to EF, a first rolling element 53 or a group of

mm

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first rolling elements 53 arranged next to one another in the axial direction and, for example, a second rolling element 54 or a group of second rolling elements 54 arranged next to one another in the axial direction. In the example, a first rolling element 53 and a group of three second rolling elements 54 are shown for each section A to F or AB to EF. With regard to the risk of possible tilting and possibly incorrect axial alignment, the arrangement of groups of at least two rolling elements 53; 54 that can move independently of one another is advantageous. A single rolling element 53; 54 for a section A to F or AB to EF is, for example, designed as a roller 53; 54 that extends in the longitudinal direction almost over the length of the section A to F or AB to EF, whereas a rolling element 53; 54 of a group, for example, B. only the roller 53; 54 having a fraction of the length of the section A to F or AB to EF is considered as the highest.

The rolling elements 53; 54 arranged axially next to one another and, if provided, the rolling elements 53; 54 arranged one behind the other in the circumferential direction are basically arranged so as to be movable independently of one another, for example on a cross member 56 (or several cross members 56). The only first rolling element 53 or the group of first rolling elements 53 of each section A to F or AB to EF and, if provided, the only second rolling element 54 or the group of second rolling elements 54 of each section A to F or AB to EF can be actuated independently of one another by their own actuating means 57; 58. These actuating means 57; 58 are designed, for example, as reversibly deformable hollow bodies 57; 58 to which pressure medium can be applied, in particular as a hose 57; 58. However, other types of electrically or magnetically actuated actuating means can also be provided.

To clamp a cover 16; 17 in one of the sections A to F or AB to EF, the leading end 24 of the cover 16; 17, which is bent at an acute angle, is inserted into the relevant opening 28; 38; 39; 41. The first or first rolling elements 53 assigned to this section A to F or AB to EF and, if provided, the

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or the second rolling elements 54 assigned to this section A to F or AB to EF are attached to the cylinder 16; 17 or to the already attached elevator 19; 21 to be wound up. If one or more further elevators 19; 21 are already arranged on the cylinder 16; 17 and are to remain there, the first and/or second rolling elements 53; 54 relating to this section A to F or AB to EF are also attached to the respective elevator 19; 21. If first and second rolling elements 53; 54 are provided, when the cylinder 16; 17 rolls with the rolling elements 53; 54, the second rolling element 54 presses the trailing, bent end 26 of the elevator 19; 21 into the opening 28; 38; 39; 41. If only first rolling elements 53 are provided, the pressing in is carried out by these. The rolling elements 53; 54 preferably remain stationary while the cylinder 16; 17 is rotated in a production direction P. The holding means for the sections A to F or AB to EF, e.g. one or more clamping pieces 29; 43, which were previously in a release position (open), change to their holding or clamping position (closed). After the holding means has changed from its release position to its holding position, all rolling elements 53; 54 of the relevant section A to F or AB to EF are released by the cylinder 16; 17 or its elevator 19; 21.

When unclamping a cover 19; 21, a distinction must be made as to whether one or more other covers 19; 21 are to remain on the cylinder 16; 17. In this case, at least one of the rolling elements 53; 54 assigned to the cover 19; 21 to be left must first be positioned or positioned in the area of its trailing end 26 or near the opening 28; 38; 39;. The rolling element 53; 54 assigned to the cover 19; 21 to be released can remain or be positioned. The holding means for sections A to F or AB to EF is opened. The trailing end 26 of the cover 19; 21 to be released is removed from the channel 27; 36; 37 by the inherent stress, while the covers 19; 21 to be left are held down by the rolling elements 53; 54. The retaining device is closed again. If the

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If the pressing device 52 has first and second rolling elements 53; 54, the packings 19; 21 to be left are advantageously held down by at least the second rolling elements 54. In the case of the packing 19; 21 intended for removal, at least the second rolling element 54 is initially turned off so that the end 26 can escape from the channel 27; 36; 37, and the first rolling element 53 is turned on so that the packing 19; 21, which has already been partially released, is still guided and held on the cylinder 16; 17. The cylinder 16; 17 can then be rotated, preferably against the production direction P, until the leading end 24 is removed from the channel 27; 36; 37 and the packing 19; 21 can be removed. If there are no remaining packings 19; 21 when the packing 19; 21 is unclamped. 21, the rolling elements 53; 54 of the sections A to F or AB to EF not relating to the elevator 19; 21 to be released can in principle assume any operating position during the procedure, preferably parked.

Thus, lifts 19; 21 resting on the outer surface 30; 40 of the cylinder 16; 17 can be fixed by at least one pressing element 53; 54 as required, while one end 24; 26 of a lift 19; 21 or several lifts 19; 21 is or are released, i.e. is or are not pressed at this time.

In an advantageous embodiment, the cylinders 16; 17; 18 of the printing unit 02 are driven in such a way that the printing units 13 of the printing unit 02 can each be driven in rotation by at least one drive motor 61 that is mechanically independent of the other printing units 13. In the case of the satellite printing unit 02, the satellite cylinder(s) 18 can also be driven in rotation by a drive motor 61 that is mechanically independent of the associated printing units 13. The drive motors 61 are preferably designed as electric motors 61 that are regulated with respect to their angular position, e.g. as asynchronous motors, synchronous motors or direct current motors. In an advantageous further development, at least one gear 62 is arranged between the drive motor 61 and the cylinder 16; 17; 18 or cylinder pair 16, 17; 18, 18 to be driven.

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in particular, at least one reduction gear 62 (such as pinion, front gear and/or planetary gear) is arranged. The individual drives contribute to the high flexibility and to the avoidance of vibrations in the mechanical drive system, and thus also to the high quality of the product. In the following figures 8 to 10, only the components in the right half of the image have corresponding reference numerals, since the left side is a mirror image of the right. Alternative configurations for any inking or dampening units 14; 20 that may be present are indicated for the upper and lower printing units, which are to be transferred alternately to one another.

In Fig. 8, all nine cylinders 16; 17; 18 each have their own drive motor 61, which drives the cylinder 16; 17; 18, for example, via a gear 62. The inking unit 14 shown above has, in addition to other rollers (not shown), two distribution cylinders 63, which can be driven in rotation together by means of their own drive motor 64. The two distribution cylinders 63 can be moved and driven axially by a drive means (not shown) to generate an axial stroke. The inking unit 14 shown below has only one distribution cylinder 63. The dampening unit 20 shown above has, in addition to other rollers (not shown), two distribution cylinders 66, which can be driven in rotation together by means of their own drive motor 67. The two distribution cylinders 66 can be moved and driven axially by a drive means (not shown) to generate an axial stroke. The dampening unit 20 shown below has only one distribution cylinder 66. In a variant, which is indicated by dotted lines in the upper printing units 13, the inking and/or dampening unit 14; 20 is not driven in rotation by its own drive motor 64; 67, but by one of the cylinders 16; 17; 18, in particular by the forme cylinder 16 via a mechanical coupling, e.g. via gears and/or belts.

In contrast to Fig. 8, the two cylinders 16; 17 of each printing unit 13 in the embodiment according to Fig. 9 are each driven by a common drive motor 61 on the transfer cylinder 17. The drive can be axial, e.g. via a gear 62.

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or via a pinion driving on a drive wheel of the transfer cylinder 17. The drive wheel of the transfer cylinder 17 can then be driven onto a drive wheel of the forme cylinder 16. The drive connection 68 (shown as a connecting line) can be a gear connection or via a belt and is designed to be encapsulated in a further development. For driving the inking and possibly dampening unit 14; 20 via separate drive motors 64; 67 or a cylinder 16; 17; 18, the method shown in Fig. 8 is generally used.

In contrast to Fig. 9, the two cylinders 16; 17 of each printing unit 13 in the embodiment according to Fig. 10 are each driven by a common drive motor 61, but on the forme cylinder 16. The drive can again be axial, e.g. via a gear 62, or via a pinion driving a drive wheel of the forme cylinder 16. The drive wheel of the forme cylinder 16 can then be driven to a drive wheel of the transfer cylinder 17. The drive connection 68 can be designed as shown in Fig. 9. For driving the inking and possibly dampening unit 14; 20 via separate drive motors 64; 67 or a cylinder 16; 17; 18, the same principle applies as in Fig. 8.

In contrast to the design indicated by dotted lines in Fig. 8 or 9 without its own rotary drive of the inking and/or dampening unit 14; 20, it is advantageous in a further development to drive from the transfer cylinder 17 to the inking and/or dampening unit 14; 20. In this way, a clear torque flow can be achieved and any tooth flank changes that would otherwise occur can be avoided. One design of such a drive train is shown schematically in Fig. 11.

The drive motor 61 drives via a pinion 71 on a drive wheel 72 which is torsionally rigidly connected to the forme cylinder 16, which in turn drives on a drive wheel 73 which is torsionally rigidly connected to the transfer cylinder. The drive wheel 73 is either widened or a second drive wheel 74 is connected to the transfer cylinder 17.

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The widened or additional drive wheel 73; 74 drives a drive wheel 78 of the inking and/or dampening unit 14; 20 via a drive wheel 77 arranged rotatably on a pin 76 of the forme cylinder 16. The drive wheels 72; 73; 74; 77; 78 are preferably designed as gear wheels. In the event that the forme cylinder 16 is designed to be axially movable in order to adjust the axial position by, for example, +AL, at least the pinion 71 and the drive wheels 72 to 74 are designed with straight teeth. An encapsulated auxiliary gear 62' indicated by dashed lines can also be arranged between the drive motor 61 and the gear 62 comprising the pinion 71 and the drive wheel 72. Alternatively, the drive to the forme cylinder 16 can also be axial on the pin 76, where an axial movement of the forme cylinder 16 may be effected via a coupling (not shown) that accommodates an axial relative movement between the forme cylinder 16 and the drive motor 61. In this illustration, the satellite cylinder 18 is also driven via a pinion 71 on a drive wheel 79 assigned to it, in particular gear wheel 79. In an advantageous embodiment, each drive train driven by an independent drive motor 61 is encapsulated at least individually, possibly in even smaller units (shown in dashed lines in Fig. 11).

The described designs of the printing unit 02 or the printing units 13 or their cylinders 16; 17; 18 or the drive enable low-vibration, precise printing of high quality with little technical and spatial effort in relation to the achievable product thickness.

After printing on the web 03, which is, for example, six pages wide, it runs, if necessary via guide elements and/or pull rollers not specified in more detail, into the area of the superstructure 04 and is guided, for example, by the longitudinal cutting devices 06 (Fig. 12). This has, for example, a roller 81, for example a pull roller 81 driven by its own drive motor 80, with which pressure rollers can work together to prevent slippage. The longitudinal cutting device 06 and the pull roller 81 can also be designed separately from one another, but preferably with the

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Longitudinal cutting device 06 acts as a support and another roller. In this longitudinal cutting device 06, the web 03 is cut lengthwise into several, e.g. three, partial web-wide webs 03a; 03b; 03c, in short partial webs 03a; 03b; 03c (symbolized by center lines, lines 03a, 03b merely indicated), before these partial webs 03a; 03b; 03c are fed to subsequent guide elements, e.g. rollers of register devices 08, turning bars of turning devices 07, take-up rollers for the funnel inlet or pull rollers. In order to achieve web transport with low vibration in terms of web tension, individual, several or all of the guide elements that are not driven or are only driven by friction with the web 03a; 03b; 03c and are used to guide partial webs 03a; 03b; 03c are designed with a reduced length. In this way, in addition to the length, the thickness of the guide elements, which would otherwise be large for machines with a width of six printing pages, for example, and thus the inertia, can be significantly reduced. The risk of oscillations in the web tension, which otherwise exists particularly when the speed changes, is effectively reduced, which in turn is reflected in the register accuracy and thus in the quality of the print. The following explanations about guide elements of reduced length, lateral relocation and the assignment of a register roller to another guide element can be used on a wide variety of printing machines, but are particularly advantageous in conjunction with wide machines, e.g. six plate wide machines.

Fig. 12 shows a perspective oblique view of a first embodiment for at least part of the superstructure 04. As an example, in Fig. 12 the partial web 03b is shown as a partial web 03b turned from the center outwards. A second of the partial webs 03a; 03c could also be turned into a different alignment by means of a second such turning device 07. A second turning device can be located, for example, above or below the first turning device 07.

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The turning device 07 has, as usual, two parallel or crossed turning bars 82 as a guide element 82, which form an angle of approximately 45° or 135° with the transport direction of the incoming partial web 03a; 03b; 03c, and by means of which an incoming web 03a; 03b; 03c can be displaced laterally and/or tilted. The turning bars 82 advantageously have a length L82, the projection of which onto the transverse extent of the incoming partial web 03a; 03b; 03c is insignificantly larger, e.g. 0% to 20% larger, than the width of the incoming partial web 03a; 03b; 03c, i.e. the length L82 is approximately 1.4 to 1.7 times the partial web width. At least the length L82 is selected such that its projection is less than or equal to twice the width of a two-sided partial web 03a; 03b; 03c, i.e. the length L82 is at most 2.8 times the partial web width. In an advantageous further development, the turning bars 82 are each individually mounted on supports 83, which can be moved transversely to the direction of the incoming partial web 03a; 03b; 03c on at least one guide 84. The now "short" turning bars 82 can now be moved from the desired web guide into the required position as required. Under certain circumstances, both turning bars 82 can also be mounted on such a support 83.

Offset, turned, transferred and/or turned partial webs 03a; 03b; 03c are generally offset in the running direction compared to other partial webs 03a; 03c and are therefore corrected in the longitudinal register by means of a register device 08. The register device 08 has at least one roller 86 that can be moved parallel to the running direction as a guide element 86. The roller 86 or several rollers 86 of the register device 08 advantageously have a length L86 that is insignificantly larger, e.g. 0% to 20% larger, than the width of the incoming partial web 03a; 03b; 03c. At least the length L86 is less than or equal to twice the width of a two-sided wide partial web 03a; 03b; 03c. In an advantageous further development, the register device 08 is mounted transversely to the direction of the incoming partial web 03a; 03b; 03c on at least one guide 87 so that it can be moved. The now narrow register device 08 or its short rollers 86 can now be moved from the desired web guide into the

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required position.

In addition to cutting, turning if necessary and registering if necessary, the partial web 03a; 03b; 03c is possibly guided over further, non-driven guide elements, such as guide rollers (not shown), in the superstructure 04 before it is finally fed to a run-up or harp roller 88 of the so-called harp 09 (Fig. 1) arranged upstream of the folding structure 11. For webs 03 or partial webs 03a; 03b; 03c running straight out, a register roller 91 extending over the full web width bO3 and movable in the transport direction, as well as a deflection roller 92 are arranged in the superstructure 04 upstream of the harp roller 89.

In an advantageous embodiment, a length L88 of a guide roller and/or harp roller 88; 93 is insignificantly greater, e.g. 0% to 20% greater, than the width of the incoming partial web 03a; 03b; 03c. At least the length L88; L93 (Fig. 13) is less than or equal to twice the width of a two-sided partial web 03a; 03b; 03c. In the embodiment according to Fig. 12, the "short" harp roller 88 is implemented as a section 88 of a harp roller 89 which is divided in this embodiment but extends over a web 03 which is six printed pages wide. The sections 88 are mounted here so that they can rotate independently of one another.

The "short" harp roller 88; 93 as a guide element 88; 93 can, however, instead of or in addition to a section 88, also be designed as a harp roller 93 arranged individually on a frame, as shown in Fig. 13. This can then either be fixed to the frame or be arranged on a carrier 94 on a guide 96 transversely to the direction of the incoming partial web 03a; 03b; 03c in a position that can be moved.

Since the offset during turning, shifting, falling, etc. only affects this partial web 03a; 03b; 03c and is tied to its special web guidance, in an advantageous embodiment the required register device 08 of at least one of the

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Guide elements determining partial web 03a; 03b; 03c, such as &zgr;. &Bgr;. the turning device or a turning bar 82 or the harp 09 or a "short" harp roller 93, can be assigned.

In Fig. 13, the "short" register device 08 is assigned, for example, to the "short" harp roller 93 and can be moved together with the latter on the guide 96 transversely to the direction of the incoming partial web 03b; 03c.

In Fig. 14, the "short" register device 08 is assigned, for example, to one of the "short" turning bars and can be moved together with it on the guide 84 transversely to the direction of the incoming partial web 03b. Although this arrangement is shown here for crossed turning bars 82, it can be applied to parallel turning bars 82 from Fig. 11. In the case of crossed or orthogonal turning bars 82, at least one (here two) deflection roller 97 is provided with a rotation axis running perpendicular to the rotation axis of the roller 81.

In an advantageous further development, in the superstructure 04 of a triple-width printing press, two such "short" devices, which can be moved together with a register and turning device 08; 07 or with a register and harp roller 93, are arranged one above or one below the other for each entire web 03.

The guides 84; 96 (Fig. 13 and 14) of the above-mentioned embodiments can be implemented in a wide variety of ways. For example, the guides 84; 96 can be designed as spindles with at least some sections of thread, which are rotatably mounted on both sides and can be driven in rotation, for example by a drive (not shown). The supports 83; 94 can also be guided in the manner of sliding blocks in rigid guides 84; 96, e.g. on profiles. The support 83; 94 can also be driven via a drivable spindle or in another way.

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By means of the transversely movable turning bar 82, variable transfers or offsets of partial webs 03a; 03b; 03c over one or two partial web widths (or multiples of half a partial web width) are possible. In this case, the printed partial webs 03a; 03b; 03c are brought into alignment with one of several, here three, folding formers 101; 102; 103 (Fig. 15) of the folding structure 11 arranged next to one another transversely to the running direction. The transfer takes place, for example, in order to meet the requirement for different thicknesses of individual strands or, ultimately, intermediate or end products, while at the same time effective printing should take place with the fullest possible web widths.

For full webs 03; 03' (e.g. e.g. printing towers 01) to be printed with a respective maximum width bO3 of m printed pages, the superstructure 04 has, in an advantageous embodiment, at least (n * (m/2 -1)) turning devices 07. In the case of a six-page wide printing press and, for example, three webs 03; 03' (or three printing towers 01) per section, six turning devices 07 per section are advantageous.

In a design of a printing press with, for example, two sections of three printing towers 01 each and a total of six four-page-wide webs 03; 03'; 03" intended for double-sided four-color printing, at least three turning devices are arranged per section.

In an advantageous embodiment of a printing press with, for example, two sections of two printing towers 01 each and a total of four six-page-wide webs 03; 03'; 03" intended for double-sided four-color printing, four turning devices 07 are arranged per section. In this printing press with two sections or a total of four printing towers 01 (four webs 03; 03'), a product with a total thickness of 96 pages can then be produced in collective operation.

In addition to the offset of a partial track 03a; 03b; 03c by an integer multiple of its

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Partial web width bO3a, an operating mode is advantageous in which a partial web 03a; 03b; 03c is offset by an odd multiple of half a partial web width bO3a and/or funnel width (i.e. by a factor of 0.5; 1.5; 2.5) (Fig. 15). This can be done by means of long turning bars (not shown) that extend over the entire width of the printing press or the width bO3 of the entire web 03, but also advantageously by means of the above-described movable "short" turning bars 82. The turning bars 82 are then arranged, for example, as shown in Fig. 15, such that the turning bar 82 first wrapped around by the partial web 03a; 03b; 03c is aligned at least over the entire width of a subsequent former 101; 102; 103, while the second turning bar 82 is aligned at least with two adjacent halves of two subsequent formers 101; 102; 103 arranged next to one another.

The partial web 03a; 03b; 03c offset by an odd multiple of half a former width b101 or partial web width bO3a thus runs "between" the formers 101; 102; 103. This is shown in Fig. 15 and 16 using the example of the six-page-wide former arrangement on a two-page-wide partial web 03a; 03b; 03c, but can also be applied to machines of other widths. This means that partial webs 03a; 03b; 03c that are only one page wide or partial webs 03a; 03b; 03c that are half a former width b101 do not have to be printed as such and fed through the machine. A high degree of product diversity is still possible.

The partial web 03a; 03b; 03c offset by an odd multiple of half a partial web width bO3a is cut lengthwise in front of the former 101; 102; 103 in an alignment lying between the two aligned formers 101; 102; 103 and runs towards the folding structure 11 or the harp 09, i.e. undivided and/or divided harp roller 89 and/or "short" harp roller 93 (Fig. 16).

In Fig. 16, a schematic section of Fig. 15 is shown with exemplary differently designed harp rollers 89; 93, whereby, for example, the partial web 03c consists of

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its original position (shown unfilled) has been offset by one and a half partial web widths bO3a. If it is cut, for example, with a further longitudinal cutting device 104 in front of the formers 101; 102; 103 (then each one printed page or newspaper page wide), it can be guided halfway with the partial webs 03a and 03b onto a respective former 101; 102. The two (intermediate) products then each have, for example, at least one partial web 03c1; 03c2 that is one printed page wide from a partial web 03a; 03b; 03c that was previously two printed pages wide. In addition, partial webs 03a';03b';03c' from other webs 03', e.g. printed in another printing unit 02 or another printing tower 01, can be guided onto one or more of the harp rollers 89; 93. The partial webs 03a, 03a', 03c1; 03b, 03b', 03c2; 03c' running in the same alignment above or below one another can now be combined to form a strand 109; 111; 112 and fed to a former 101; 102; 103. In the exemplary embodiment, two webs 03; 03', each printed on both sides in double-sized and triple-width printing units (e.g. four-color), can be used to form a folding former. 03' produce products or intermediate products (also called booklets or books) with the following different numbers of pages depending on the utilization of the forme cylinder 16 and the corresponding operating mode of the folding device 12: In the case of single production, i.e. the forme cylinder 16 is circumferentially loaded with two printing formes 19 of different printed pages A1, A2 to F1, F2 (or A1', A2' to F1', F2' for the second web 03') and cross-cutting and gathering takes place in the folding device 12, two different booklets, each with 10 printed pages, can be produced via the strands 109 and 111, and two different booklets, each with 4 printed pages, can be produced via the strand 112. A total product has, for example, 48 pages. If this printing press is operated in double production, i.e. the forme cylinder 16 is circumferentially loaded with two printing formes 19 of the same printed pages A1, A1; to F1, (or AT, Af to Ff ₁ Ff) and no gathering takes place in the folding device 12, two identical consecutive booklets with the above page numbers can be produced via the strands 109, 111 and 112. A total product with only 24 pages is produced, but with double the output.

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The harp rollers 89; 93, especially if they are designed undivided over the full length, can be driven in rotation by their own drive motors (not shown) in a further development. These are then designed to be adjustable, for example, in terms of their speed and possibly also their position, and are connected to the machine control or an electronic master axis to take over current setpoints.

As shown in Fig. 17, the folding structure 11 has at least two folding formers 101, 106; 102, 107; 103, 108 arranged one above the other, the planes of symmetry S of which each lie in a common alignment of a partial web 03a; 03b; 03c running straight through the printing press. In particular, the planes of symmetry S of the two folding formers 101, 106; 102, 107; 103, 108 arranged one above the other essentially coincide with a center plane M of a partial web 3a; 3b; 3c (3a'; 3b'; 3c' or 3a"; 3b"; 3c" or 3a'"; 3b'"; 3c'" etc. which is two printing pages wide, runs straight ahead and is only deflected in the vertical direction. 3b; 3c etc. are shown in Fig. 17 partly as solid lines and partly as dashed lines for a reason explained below (see Fig. 18).

For the six-page-wide printing press, according to Fig. 17, two vertically offset groups of three formers 101, 102, 103 and 106, 107, 108 are arranged. For four-page-wide printing presses, this can be two formers, and for eight-page-wide printing presses, four formers next to each other. An upper and a lower former 101, 106; 102, 107; 103, 108 are aligned in pairs in the manner described above with each other and with a center plane M. The three formers 101; 102; 103 and 106; 107; 108 of a group are offset from each other transversely to the running direction of the partial webs 03a; 03b; 03c and, in an advantageous embodiment, are arranged essentially at the same height. However, they may also be vertically offset from each other and/or have different vertical dimensions, but in this case they are, for example, in a horizontal plane

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at least partially overlap.

Viewed in the web travel direction, the folding structure 11 has, at least in front of one of the superimposed groups of folding formers 101; 102; 103 or 106; 107; 108, the harp 09 which defines the former inlet of the webs 03; 03'; or partial webs 03a; 03b; 03c, i.e. a group of several parallel run-up or harp rollers 89; 93 which are offset from one another in the radial direction and via which various webs 03; 03' or partial webs 03a; 03b; 03c; or 03a'; 03b'; 03c' etc. are transferred from the superstructure 04 into the folding structure 11. Following the harp rollers 89; 93, they are combined to form a strand 109; 111; 112 or combined into several strands 109; 111; 112. The later position of the partial web 03a; 03b; 03c; or 03a'; 03b'; 03c' in the strand 109; 111; 112 or their printed sides in the intermediate and/or final product is determined, among other things, by the choice of a relative position to other partial webs 03a; 03b; 03c; or 03a'; 03b'; 03c' passing through the harp 09. The harp rollers 89; 93 of a harp 09 are offset vertically and/or horizontally from one another and are preferably mounted as a structural unit in a common frame. In principle, a roller system can be used for each of the vertically offset groups of formers 101; 102; 103 or 106; 107; 108 such a harp 09 may be provided.

In order to save on overall height, in an advantageous embodiment, as shown in Fig. 1 and Fig. 19, the two folding formers 101, 106; 102, 107; 103, 108 which are arranged one above the other but are aligned with one another in their plane of symmetry have a common harp 09. For n full webs 03; 03' (n. B. n printing towers 01 of a section) to be printed with a respective maximum width bO3 of m printed pages, the harp 09 in an advantageous embodiment has at least (n * m / 2) harp rollers 88; 89; 93 whose axes of rotation lie, for example, essentially in a common plane, and which are preferably mounted in a common frame. In the case of the six-page wide printing press present here and, for example, two webs 03; 03' (or two printing towers 01) at least six harp cylinders 88; 89; 93 per harp 09 of

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Advantage.

In one version of a section of the printing press with three printing towers 01 and three webs 03; 03'; 03" intended for double-sided four-color printing, at least nine harp rollers 88; 89; 93 are arranged per harp 09. In this section, a product with a total thickness of 72 pages can then be produced in collective operation.

In an advantageous embodiment of a printing press with, for example, two sections of two printing towers 01 each and a total of four six-page-wide webs 03; 03'; 03" intended for double-sided four-color printing, at least six harp rollers 88; 89; 93 are arranged per harp 09 of a section. These six harp rollers 88; 89; 93 per section, i.e. twelve here, can be arranged in two structurally separate harps 09, e.g. above a common folding structure 11 or two folding structures 11, but also in a structurally common harp 09, e.g. in two lines. In this printing press with two sections or a total of four printing towers 01 (four webs 03; 03'), a product with a total thickness of 96 pages can then be produced in collective operation.

In a design of a printing press with, for example, two sections of two printing towers 01 each and a total of four six-page-wide webs 03; 03'; 03" intended for double-sided four-color printing, at least six harp rollers 88; 89; 93 are arranged per harp 09 of a section. These six harp rollers 88; 89; 93 per section, i.e. twelve here, can be arranged in two structurally separate harps 09, e.g. above a common folding structure 11 or two folding structures 11, but also in a structurally common harp 09, e.g. in two lines. In this printing press with two sections or a total of four printing towers 01 (four webs 03; 03'), a product with a total thickness of 96 pages can then be produced in collective operation.

If only one folding structure 11 is provided for two sections, the number of

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required harp rollers 89; 93 are to be determined according to the configuration of the two sections. If the folding structure 11 is arranged between these two sections, then either all harp rollers 89; 93 are in a line or, in order to save construction height, the harp rollers 89; 93 of each section are arranged in a line and the lines are horizontally offset from one another in the radial direction. The harp rollers 89; 93 of the two lines are here again arranged in a common frame, for example.

If, as indicated in Fig. 1, two folding structures 11 are provided for the two sections, it can still be advantageous to provide a number of harp rollers 89; 93 for at least one of the two harps 09, possibly in the two above-mentioned alignments, which would be required for both sections. This provides an even greater degree of flexibility in product thickness and composition. Webs 03; 03' printed in one section can now be fed to the other section for further processing of the harp 09 and vice versa if required.

According to Fig. 18, at least one of the partial webs 03a; 03b; 03c etc., which runs through the common harp 09 arranged in front of the upper former 101; 102; 103, can be or is guided to the lower former 106; 107; 108. Depending on the desired thickness of the individual intermediate products (booklets, books), more or fewer of the partial webs 03a; 03b; 03c etc. are to be transferred to the upper or lower former 101; 102; 103 or 106; 107; 108. Depending on production requirements, strands 109; 111; 112; 113; 114; 116 of different thicknesses can be fed to the lower or upper former 101; 102; 103 or 106; 107; 108. For example, the partial webs shown in dashed lines in Fig. 17 are guided as strands 113; 114; 116 to the respective lower folding formers 106; 107; 108, and the solid lines to the respective upper folding formers 101; 102; 103. This allows, depending on where the "separation" is in superimposed partial webs 03a; 03b; 03c etc. from the common harp 09, a flexible production of intermediate products of different thicknesses (booklets, books) or end products with

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reduced effort. In Fig. 18, a second row of harp rollers 89; is shown in dashed lines, by means of which, as described above, for example, partial webs 03a; 03b; 03c etc. can be picked up from another section.

In the case of multi-colored products, when using the described folding structure with a common harp 09, it is advantageous in terms of flexibility to design all printing units 02 or printing towers 01 or the paths of the web 03; 03' with the same color. For example, the web 03; 03' and/or partial web 03a; 03b; 03c etc. or the printing unit 13 for a colored cover sheet can be flexibly selected and the thickness of the intermediate products can be varied.

The above-mentioned folding structure 11 with just one harp 09 for two folding formers 101; 102; 103; 106; 107; 108 arranged one above the other is also suitable for other printing machines with other cylinder widths and cylinder circumferences. A folding superstructure 11 of this type consisting of two folding formers 101; 102; 103; 106; 107; 108 arranged one above the other and a common harp 09 can also be arranged above a third folding former with its own harp 09. The described folding structure 11 with a harp 09 assigned to several folding formers 101; 102; 103; 106; 107; 108 that are offset vertically from one another can also be used on three folding formers 101; 102; 103; 106; 107; 108 are well applicable.

Outer pages of an outer book, for example, can thus be assigned to a specific web path and/or a specific printing tower/printing unit.

The harp 09 assigned to several formers 101; 102; 103; 106; 107; 108 makes it possible to flexibly process the superimposed partial webs 03a; 03b; 03c etc. into books of different thicknesses depending on the desired product, without a high level of effort for additional, superfluous displacement of partial webs 03a; 03b; 03c etc. This means that, for example, four superimposed partial webs

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Partial webs 03a; 03b; 03c etc. in one case three webs are guided to one former 101; 102; 103; 106; 107; 108 and one to the other, while in another case two partial webs 03a; 03b; 03c etc. are combined and guided to one former 101; 102; 103; 106; 107; 108. It is particularly advantageous that strands 109; 111; 112; 113; 114; 116 lying next to one another can be combined to different degrees, as shown in Fig. 17.

In an advantageous embodiment, the pull rollers 117 and the former inlet rollers 118 arranged upstream of the formers 101; 102; 103; 106; 107; 108 each have their own drive motors 119, just like the pull rollers 121 provided in the folding structure 11 (Fig. 19). In Fig. 19, the pull roller 117 for the lower group of formers 106; 107; 108 is not visible. The respective drive motor 119 of the pull rollers 121 is shown in Fig. 19 only by filling the respective pull roller 121. Each of the formers 101; 102; 103; 106; 107; In an advantageous embodiment, at least one such driven pull roller 121 is arranged downstream of 108, which interacts with pressure rollers or a pressure roller over the strand 109; 111; 112; 113; 114; 116. In addition, the folding structure 11 preferably has non-driven guide rollers 122, over which the strands 109; 111; 112; 113; 114; 116 that are wide on one printing side can be guided.

Particularly advantageous, e.g. with regard to maintaining/setting longitudinal registers, the folding apparatus 12 also has at least one drive motor 120 of its own, which is mechanically independent of the printing units 02. While the drive motors 119 of the pull or former infeed rollers 117; 118; 121 of the folding structure 11 and/or driven pull rollers 81 of the superstructure 04 only have to be designed to be regulated with respect to a speed (or can be designed with respect to an angular position), the drive motor 120 on the folding apparatus 12 is advantageously designed to be adjustable or regulated with respect to its angular position.

Thus, it is possible in one version to mechanically independently

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driven printing units 02 and the folding apparatus 12 (or their drive motors 61; 120) to specify an angular position with respect to a virtual electronic guide axis. In another embodiment, for example, the angular position of the folding apparatus 12 (or its drive motor 120) is determined and the relative angular position of the printing units 02 or printing units 13 to it is specified based on this. The drive motors 80; 119 of the driven rollers 81; 117; 118, which are only regulated with regard to their speed, receive their speed specification from the machine control, for example.

By designing the web-fed rotary printing press with triple-width and double-sized transfer and form cylinders and the corresponding design of the folding structure, it is possible to produce double production using one web, for example.

- a book with twelve pages, or

- a book with four pages and a book with eight pages, or

- two books with six pages, or

- three books with four pages

and produce further variations.

In collective production, the number of pages of the intermediate products, which are then collected from two longitudinally folded sections, is doubled.

For printing in tabloid format, the respective page numbers must be doubled. The dimensions of the cylinders 16; 17; 18 and the groups of formers 101; 102; 103; 106; 107; 108 are to be applied accordingly to "horizontal" printed pages, whereby in the circumferential direction or running direction of the web 03; 03'; 03a; 03b; 03c a section A; B; C has two horizontal printed pages, the forme cylinder 16 then having a circumference corresponding to four horizontal printed pages in tabloid format. The number of printed pages in the longitudinal direction remains the same for each web 03; 03'; 03a; 03b; 03c or cylinder 16; 17; 18 or former width.

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List of reference symbols

01 Printing tower

02 Pressure unit, satellite pressure unit, nine-cylinder satellite pressure unit, ten-cylinder satellite pressure unit, H-pressure unit

03 track, partial track 03a track, partial track 03b track, partial track 03c track, partial track 03c1 partial track 03c2 partial track

04 Superstructure 05

06 Longitudinal cutting device

07 Turning device, turning mechanism

08 Register setup

09 Harp 10

11 Fold structure

12 Folder

13 Printing unit, offset printing unit

14 inking units

15 paint boxes

16 cylinders, forme cylinder

17 cylinders, transfer cylinder

18 printing cylinders, satellite cylinders

19 Elevator, printing form, printing plates

20 Dampening system, spray dampening system

21 Elevator, rubber blanket, metal printing blanket

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22 layer 23 Carrier plate 24 End, leading, hanging leg 25 - 26 End, trailing, hanging leg 27 channel 28 opening 29 clamping piece, clamping element 30 Shell surface 31 Spring element 32 Actuator, hollow body, hose 33 Registration element 34 base 35 Register stone, registration pin 36 channel 37 channel 38 opening, slot 39 opening, slot 40 Shell surface 41 opening, slot 42 drilling 43 clamping piece, clamping element 44 Spring element 45 - 46 Actuator, hollow body, hose 47 Actuator, hollow body, hose 48 Actuator, hollow body, hose 49 Filling element 50 _

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51 Opening

52 Pressing device

53 pressure element, first, rolling element, roller, roll

54 Pressure element, second, rolling element, roller, roll 55

56 Traverse

57 Actuator, hollow body, hose

58 Adjusting agent, hollow body, hose 59

61 Drive motor, electric motor

62 Gearbox, Reduction Gear 62' Gearbox

63 friction cylinders

64 Drive motor 65

66 friction cylinders

67 Drive motor

68 Drive connection 69

71 pinion

72 Drive wheel

73 Drive wheel

74 Drive wheel 75

76 cones

77 Drive wheel

78 Drive wheel

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79 drive wheel, gear 80 Drive motor 81 roller, pulling roller 82 Turning bar, guide element 83 carrier 84 guide 85 - 86 Roller, guide element 87 guide 88 Run-up roller, harp roller, section 89 Overrun roller, harp roller, guide element 90 - 91 Register roller 92 Deflection roller 93 Run-up roller, harp roller, register roller, guide element 94 carrier 95 - 96 guide 97 Deflection roller 98 — 99 - 100 - 101 Former 102 Former 103 Former 104 Longitudinal cutting device, medium 105 — 106 Former 107 Former

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108 A2 Former 109 B2 strand 110 C2 — 111 D2 strand 112 E2 strand 113 F2 strand 114 strand 115 — 116 strand 117 Pull roller 118 Funnel inlet roller 119 Drive motor 120 Drive motor 121 Pull roller 122 Guide roller A Section B Section C Section D Section E Section F Section A1, Print page B1, Print page C1, Print page D1, Print page E1, Print page F1. Print page

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bO3 width, track, track width

bO3a Width, partial track

b23 Width (23)

b27 Width (27)

b101 funnel width

I length L16 length L17 length L82 length L86 length L88 length L93 length M Middle level MS Material thickness P Production direction S plane of symmetry S16 Slot width S17 Slot width U Section

corresponding designation of a second track or partial track

&agr; angle &bgr; Angle α' angle

Claims (25)

1. Web-fed rotary printing machine with at least one printing unit (02) for printing six printed pages arranged axially next to one another and with a folding structure ( 11 ) which has at least a first group of three folding formers ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) and at least one further folding former ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) offset vertically to the first group, wherein the folding formers ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) of the first group are arranged offset from one another transversely to the running direction of partial webs (03a; 03b; 03c) next to one another and at least partially overlapping in a horizontal plane, and wherein planes of symmetry (S) have at least a former ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) of the first group and the further former ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) lie essentially in a common alignment of a partial web (03a; 03b; 03c) running straight through the printing press, characterized in that a common group of take-up rollers ( 88 ; 89 ; 93 ) is assigned to the two aligned formers ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ). 2. Web-fed rotary printing press according to claim 1, characterized in that it has at least one section with at least two printing units (02) for printing at least two webs (03; 03'). 3. Web-fed rotary printing press according to claim 2, characterized in that the section has at least two printing towers, each with two printing units (02) arranged vertically offset from one another. 4. Web-fed rotary printing machine according to claim 2, characterized in that the section has two printing towers, each with two printing units (02) arranged vertically offset from one another. 5. Web-fed rotary printing machine according to claim 2, characterized in that the section has three printing towers, each with two printing units (02) arranged vertically offset from one another. 6. Web-fed rotary printing press according to claim 2, characterized in that the section has four printing towers, each with two printing units (02) arranged vertically offset from one another. 7. Web-fed rotary printing press according to claim 4, 5 or 6, characterized in that the printing units (02) are each designed for printing a web (03; 03') six printing pages wide. 8. Web-fed rotary printing machine according to claim 4, 5 or 6, characterized in that the printing units (02) are each designed for printing a web (03; 03') four printing pages wide. 9. Web-fed rotary printing machine according to claim 2, characterized in that the printing unit (02), at least one roller ( 117 ; 118 ) of the downstream folding structure ( 11 ) and a downstream folding apparatus ( 12 ) are each driven mechanically independently of one another by drive motors ( 61 ; 80 ; 119 ; 120 ). 10. Web-fed rotary printing machine according to claim 1, characterized in that the printing unit (02) is designed as a nine-cylinder satellite printing unit (02). 11. Web-fed rotary printing machine according to claim 1, characterized in that the printing unit (02) is designed as a ten-cylinder satellite printing unit (02). 12. Web-fed rotary printing machine according to claim 1, characterized in that the printing unit (02) is designed as an H-printing unit (02) with four printing units ( 13 ) working together in pairs. 13. Web-fed rotary printing press according to claim 1, characterized in that the web-fed rotary printing press has two sections, and that between the two sections two folding structures ( 11 ) each with at least one upper and at least one lower folding former ( 101 ; 102 ; 103 ; 106 ; 107 ; 108 ) are arranged. 14. Web-fed rotary printing machine according to claim 13, characterized in that two folding devices ( 12 ) are assigned to the two folding structures ( 11 ). 15. Web-fed rotary printing machine according to claim 13, characterized in that a first row of take-up rollers ( 88 ; 89 ; 93 ) offset vertically and/or horizontally from one another for receiving partial webs (03a; 03b; 03c) from one section, and a second row of take-up rollers ( 88 ; 89 ; 93 ) offset vertically and/or horizontally from one another for receiving partial webs (03a; 03b; 03c) from the other section are mounted as a structural unit in a common frame. 16. Web-fed rotary printing machine according to claim 1, characterized in that the forme cylinder ( 16 ) of the printing unit (02) has a circumference which corresponds to at least two vertical printed pages arranged one behind the other in the circumferential direction, in particular newspaper pages, and that a folding apparatus ( 12 ) arranged downstream of the folding structure ( 11 ) is designed such that it can be operated at least in a collecting operation for gathering two successive sections (A1; A2). 17. Web-fed rotary printing machine according to claim 1, characterized in that all webs (03; 03') running simultaneously through the printing units (02) of the section can be printed with the same color. 18. Web-fed rotary printing machine according to claim 1, characterized in that the folding structure ( 11 ) is assigned a superstructure (04) with one or more guide elements ( 82 ; 86 ; 89 ; 93 ) for guiding partial webs (03a; 03b; 03c), and that at least one of the guide elements ( 82 ; 86 ; 89 ; 93 ) is movable transversely to the running direction of the incoming partial web (03a; 03b; 03c) and its length (L82; L86; L93) is dimensioned such that its projection is less than or equal to twice the width (b03a) of an incoming partial web (03a; 03b; 03c) that is two printing pages wide. 19. Web-fed rotary printing machine according to claim 1, characterized in that a register device (08) and a further guide element ( 82 ; 86 ; 89 ; 93 ) which imposes a change in direction or an offset on the web run are arranged on a common guide ( 84 ; 96 ) so as to be movable transversely to a direction of an incoming web (03, 03a; 03b; 03c). 20. Web-fed rotary printing machine according to claim 19, characterized in that the register device (08) and the further guide element ( 82 ; 86 ; 89 ; 93 ) are arranged on a common carrier on the common guide ( 84 ; 96 ). 21. Web-fed rotary printing machine according to claim 18 or 19, characterized in that the guide element ( 82 ) is designed as a turning bar ( 82 ). 22. Web-fed rotary printing machine according to claim 18 or 19, characterized in that the guide element ( 89 ; 93 ) is designed as a run-up roller ( 89 ; 93 ). 23. Web-fed rotary printing press according to claim 1, characterized in that a superstructure (04) assigned to the section for n printing towers with a respective maximum width (b03) of m printed pages has at least (n.(m/2 - 1)) turning devices (07). 24. Web-fed rotary printing press according to claim 1, characterized in that the section has three printing towers, each with two printing units (02) arranged vertically offset from one another, a maximum width (b03) of four printed pages and six turning devices (07). 25. Web-fed rotary printing machine according to claim 1, characterized in that the section has two printing towers, each with two vertically offset printing units (02) with a maximum width (b03) of six printed pages, as well as four turning devices (07).