EP1377453B2 - Printing group pertaining to a printing machine - Google Patents

Abstract

The offset printer has one or more printing station with a transfer cylinder (03,07) on either side of the paper. Each transfer cylinder has a printing cylinder (02,11) in contact with it. The printing cylinders may have thin aluminum printing plates wrapped around them, with their edges held by clamps in longitudinal grooves (4) in their cylindrical surfaces. The transfer cylinders may have blankets with their ends held in longitudinal grooves (6). The grooves in the cylinders are broken up into staggered sections. The cylinders are all the same diameter which corresponds to the length of each section of paper to be printed.

Description

The invention relates to a printing unit of a printing press according to the preamble of claim 1 or 2.

By the DE 100 08 216 A1 discloses a linearly arranged printing unit, wherein a plane through the axes of rotation of the cylinder and the paper web include an obtuse angle. The cylinders are mounted linearly movable in guides in the side frame.

By the DE 198 03 809 A1 is known a printing unit whose form cylinder has at its periphery in the circumferential direction one, and in the longitudinal direction a plurality of printing plates. A cooperating with the forme cylinder transfer cylinder has a double circumference and is performed in the circumferential direction with a blanket and in the longitudinal direction with two, but circumferentially offset from each other arranged blankets.

The JP 100 71 694 discloses printing cylinder with four juxtaposed, and circumferentially offset channels. The printing group cylinders have a so-called double circumference.

By the CH 3 45 906 a device for bumpless printing process is known, wherein shocks of four juxtaposed elevators on transfer cylinders double the circumference and shocks of four juxtaposed elevators on a form cylinder double circumference are arranged offset from each other.

From the DE 198 15 294 A1 a double printing unit is known, wherein the axes of rotation of the printing cylinder are arranged in a plane. The cylinders have a four times the width of a newspaper page (double width) and a circumference of one page height of a newspaper page. The transfer cylinders have endless sleeves, which are laterally replaced by openings in the side wall.

By the US 41 25 073 A are simple printing cylinder known, which have a vibration damper. In the case of wider printing presses, the forme cylinder has a double circumference and two printing plates arranged one behind the other. The longitudinally juxtaposed, the pressure plates receiving channels are circumferentially offset from each other in addition.

By the DE 44 15 711 A1 a double printing unit is known, wherein for the purpose of improving the print quality, a plane perpendicular to the paper web to the two axes of rotation of the transfer cylinder connecting plane is inclined by about 0 ° to 10 °.

The JP 57-131 561 discloses a double printing unit having arranged in a plane axes of the printing cylinder. The printing cylinder are arranged in phase with each other so that channels for attaching the elevators to each other, and simultaneously roll in the two co-operating printing units.

Also in the DE 34 12 812 C1 discloses a double printing unit, wherein the cylinder axes are arranged in a common plane which is inclined relative to the plane of the web to be printed. The switching on and off of the transfer cylinder takes place along a nearly rectilinear direction of movement by means of double eccentrics.

The EP 08 62 999 A2 discloses a double printing with two co-operating transfer cylinders, which are stored for the purpose of switching on and off in eccentric or double eccentric bushes. In another embodiment, they are mounted in levers which are mounted eccentrically to the forme cylinder axis pivotally.

By the EP 10 75 945 A1 is a double printing with arranged in a plane axes of the printing cylinder known, wherein a plurality of printing cylinder mounted in slides, and for the purpose of turning on and off by means arranged on a supporting wall guide elements are designed to be mutually variable.

From the DE 199 37 796 A1 Druckwerkszylinder are known which are movable along a linear travel in order to each other on or off of each other. Each cylinder is assigned a drive motor, which is moved together with the cylinder. The movement takes place in a direction which is parallel to a common plane of the printing cylinder.

In the US 58 68 071 A are, for the purpose of turning on and off the transfer cylinder, these stored in slides, which are linearly displaceable in the side frame along parallel directions of movement in linear bearings having linear guides.

The invention has for its object to provide a compact, low-vibration printing unit of a printing press, which is easy to produce.

The object is achieved by the features of claim 1 or 2.

The achievable with the present invention consist in particular that a pressure machine is created by the measures, which is compact, low-vibration and robust built, has a high production diversity, and requires a relatively low manufacturing and maintenance costs.

The minimization of the number of parts to be moved in normal operation and during setup, z. As the waiver of the movement of all cylinders, frame walls, bearings, etc., ensures the robust and cost-effective design.

With the linear arrangement of the printing cylinder, ie the arrangement of the axes of rotation of the printing cylinder in the print-on position substantially in a plane, the cylinders are mutually supported. This reduces a relative deflection the cylinder. It is even a compensation of the bending line (static) of the forming and the transfer cylinder to each other achievable.

Since the elevators are held on the cylinders not in the over the length of the cylinder continuous, but in circumferentially offset channels, a channel impact during passage of the channel during the rolling of two co-acting cylinder is significantly reduced. In an advantageous embodiment, the channels are arranged offset by 180 ° to each other in the case of two longitudinally juxtaposed channels.

Particularly advantageous is the arrangement of the printing cylinder and the channels such that the mutually offset channels of each cylinder rolls in the region of the opposite, offset channel of the cooperating cylinder. This can be done to compensate for the dynamic forces. With a fixed offset angle of 180 ° and linear arrangement of the cylinder is for all production rates, ie. H. Angular speeds, destructive interference before, without an offset angle of the channels must be varied speed or frequency dependent.

Particularly advantageous is the arrangement of printing cylinders simple scope for printed products smaller and / or variable page size and / or for printers with limited space. Compared to producing the same product on a double-circumference press (without collecting), no "double" plate change is required. In contrast to a double-circumference printing machine in collective operation, it becomes possible to create a side jump from two sides, thereby producing increased flexibility in the printed product.

The construction of all printing cylinders with a simple circumference allows for a much more compact and lighter construction compared to printing units, which have one or more cylinders double the circumference. Also be replaced when damaged blankets smaller and therefore cheaper

The use of blankets and printing plates makes it possible to store the cylinders stable on both sides, with a simple, robust and inexpensive construction of the printing cylinder receiving side frame is possible.

It is also advantageous in terms of a robust and simple construction, if only the transfer cylinder must be moved to turn on and off the printing unit. Although the form cylinder for the purpose of adjustment at a distance to the associated transfer cylinder and possibly color and, if available, dampening be changeable stored, on and off the transfer cylinder from each other and from the associated form cylinders, however, takes place advantageously solely by means of a movement of the transfer cylinder.

By a specially selected in the area of the pressure point movement, the linear arrangement of the cylinder is possible and at the same time avoiding and stopping devices or movements of the forme cylinder avoided. This also contributes to the robust and simple design.

In one embodiment, the transfer cylinders are mounted for example in carriages in linear guides in or on the side frame, which allows a movement substantially perpendicular to the plane of the cylinder axes. If the guides are arranged on specially designed inserts of the side frame, the pins shorten and allow the simple formation of an encapsulated lubricant space. A special arrangement of the direction of movement allows the quick and safe parking of form and impression cylinders and of the web.

In another embodiment, the transfer cylinders are arranged for this purpose in levers which are mounted eccentrically to the forme cylinder axis pivotally. Due to the specific position of the pivot points and the size of the eccentric (to the axis of rotation of the forme cylinder) in conjunction with the selected inclination to the plane of the pressure forming cylinder or between the web and plane of the cylinder is a quick shutdown of the associated cylinders or exemptions of the web possible. The operational switching on and off takes place only by means of the transfer cylinder, in a preferred embodiment by means of only one adjusting movement.

In a third embodiment, the transfer cylinders are mounted in Doppelexzenterbuchsen, which allows at least in the area near the pressure point a nearly linear and largely perpendicular to the plane of the cylinder axes movement.

By the so-called. Metal blankets running lifts on the transfer cylinders, the effective channel width is reduced, whereby the excitation of vibrations advantageously further reduced and the non-printing area on the cylinders, d. H. the "white margin" on the product or the paper waste is reduced.

Particularly advantageous is the one embodiment of the printing unit with cylinders simple scope and the arrangement in a plane with staggered, but mutually rolling on each other channels, and designed as metal blankets elevators on the transfer cylinders.

In particular, for washing, change of elevators, etc. cylinders or rollers in printing units from the operating state "pressure on", ie a print-on position against each other off and on again. The necessary radial movement of the rollers also includes a component of motion in the tangential direction, whose size depends on the structural design (eccentric, lever, linear guide, and their angle to Nippstelle) of the adjusting device. If, due to the adjustment with regard to the operating state, a speed difference arises on the effective lateral surfaces in the nip point, then so Due to the surface friction of the roll materials used, this implies a tangential frictional force component which is in the opposite direction of the adjustment movement. The adjustment is thus thus inhibited, or limits their speed. This is particularly important in printing cylinders in the case of so-called. "Winders" important because resulting from the high pressure occurring also large frictional forces.

Therefore, it is advantageous in a method for stopping and stopping cylinders, a relative tangential velocity in the contact region, d. H. in the area of the nip point of two cylinders or rollers acting together, is reduced by conscious, correlated with the movement rotation or rotation of at least one of the cylinders or rollers involved. In addition to a reduction of the inhibition in the adjustment, an unnecessarily high load (friction, deformation) of the lifts and / or the lateral surfaces of the cylinders or rollers involved is avoided.

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

Fig. 1

eine schematische Darstellung eines Doppeldruckwerkes;

Fig. 2

eine schematische Darstellung eines nicht erfindungsgemäßen Dreizylinder-Offsetdruckwerk;

Fig. 3

eine schematische Darstellung eines doppelt breiten Doppeldruckwerk;

Fig. 4

eine schematische Darstellung eines doppelt breiten Doppeldruckwerk, hochsymmetrisch;

Fig. 5

eine schematische Darstellung eines Doppeldruckwerk im Schnitt B - B gemäß Fig. 1 mit lineare Stellweg;

Fig. 6

eine schematische Darstellung eines nicht linearen Doppeldruckwerks mit linearen Stellwegen;

Fig. 7

eine schematische Darstellung einer H-Druckeinheit mit linearem Stellweg;

Fig. 8

eine Seitenansicht eines ersten Ausführungsbeispiels einer Linearführung für Übertragungszylinder;

Fig. 9

einen Schnitt durch die Linearführung gemäß Fig. 8

Fig. 10

eine Seitenansicht eines zweiten Ausführungsbeispiels einer Linearführung für Übertragungszylinder;

Fig. 11

einen Schnitt durch die Linearführung gemäß Fig. 10;

Fig. 12

eine schematische Darstellung eines linearen Doppeldruckwerkes im Schnitt B - B gemäß Fig. 1 mit kurvenförmigem Stellweg;

Fig. 13

eine schematische Darstellung eines winkeligen Doppeldruckwerkes im Schnitt B - B gemäß Fig. 1 mit kurvenförmigem Stellweg;

Fig. 14

eine schematische Darstellung einer H-Druckeinheit mit kurvenförmigem Stellweg;

Fig. 15

eine Seitenansicht für die Lagerung der Zylinder;

Fig. 16

einen Schnitt der Lagerung gemäß Fig. 15;

Fig. 17

einen Ausschnitt eines paarweisen Antriebes am Übertragungszylinder;

Fig. 18

eine schematische Vorderansicht gemäß Fig. 10;

Fig. 19

eine schematische Vorderansicht eines nicht erfindungsgemäßen Doppeldruckwerkes mit Zylindern verschiedenen Umfangs;

Fig. 20

eine Belegung des Formzylinders mit vier Zeitungsseiten;

Fig. 21

eine Belegung des Formzylinders mit acht Tabloidseiten;

Fig. 22

eine Belegung des Formzylinders mit sechzehn stehenden Seiten im Buchformat;

Fig. 23

eine Belegung des Formzylinders mit sechzehn liegenden Seiten im Buchformat.

Show it:

Fig. 1

a schematic representation of a double printing;

Fig. 2

a schematic representation of a non-inventive three-cylinder offset printing unit;

Fig. 3

a schematic representation of a double-wide double printing;

Fig. 4

a schematic representation of a double-wide double printing, highly symmetrical;

Fig. 5

a schematic representation of a double printing in section B - B according to Fig. 1 with linear travel;

Fig. 6

a schematic representation of a non-linear double printing with linear adjustment paths;

Fig. 7

a schematic representation of a H-pressure unit with linear travel;

Fig. 8

a side view of a first embodiment of a linear guide for transfer cylinder;

Fig. 9

a section through the linear guide according to Fig. 8

Fig. 10

a side view of a second embodiment of a linear guide for transfer cylinder;

Fig. 11

a section through the linear guide according to Fig. 10 ;

Fig. 12

a schematic representation of a linear double printing unit in section B - B according to Fig. 1 with curved travel;

Fig. 13

a schematic representation of an angular double printing unit in section B - B according to Fig. 1 with curved travel;

Fig. 14

a schematic representation of an H-pressure unit with a curved travel;

Fig. 15

a side view for the storage of the cylinder;

Fig. 16

a section of the storage according to Fig. 15 ;

Fig. 17

a section of a pairwise drive on the transfer cylinder;

Fig. 18

a schematic front view according to Fig. 10 ;

Fig. 19

a schematic front view of a non-inventive double printing unit with cylinders of different circumference;

Fig. 20

an assignment of the forme cylinder with four newspaper pages;

Fig. 21

an assignment of the forme cylinder with eight tabloid pages;

Fig. 22

an assignment of the forme cylinder with sixteen standing pages in book format;

Fig. 23

an assignment of the forme cylinder with sixteen lying pages in book format.

A first printing unit 01 of a printing press, in particular a rotary printing press, has a first cylinder 02, z. B. a forme cylinder 02, and an associated second cylinder 03, z. B. a transfer cylinder 03, on ( Fig. 1 ). In a print on position AN, their axes of rotation define R02; R03 is a level E.

The forme cylinder 02 and the transfer cylinder 03 have on their circumference in the circumferential direction on the lateral surface at least one fault, z. B. an interruption 04; 06 in the effective at unwinding lateral surface. It deals itself, as shown below in the embodiments, to channels 04; 06 or slots 04; Act 06, which absorb the ends of elevators.

The forme cylinder 02 and transfer cylinder 03 each have at least two channels 04; 06 on. These two channels 04; 06 are each in the longitudinal direction of the cylinder 02; 03 in succession, and arranged offset from each other in the circumferential direction.

Do the cylinders 02; 03 only a length L02; L03, which substantially corresponds to two widths of a newspaper page, so are only two mutually offset in the circumferential direction and longitudinally successively arranged channels 04; 06 arranged.

The channels 04; 06 are so on the two cylinders 02; 03 arranged to rotate upon rotation of the two cylinders 02; 03 each on one of the channels 06; 04 of the other cylinder 03; 04 unroll. Preferably, the offset of the channels 04; 06 of each cylinder 02; 03 in the circumferential direction about 180 °. Thus, each roll after 180 ° rotation of the cylinder 02; 03 at least one pair of channels 04; 06 on each other, while on a longitudinal section a of the cylinder 02; 03 the cylinders 02; 03 Unroll undisturbed.

The transfer cylinder 01 of the first printing unit 01 forms with a third cylinder 07; over a train 08; z. B. a printing substrate 08, a pressure point 09. This third cylinder 07 is a second transfer cylinder 07 ( Fig. 1 ) or in nichtbeanprüuchter execution as a counter pressure cylinder 07 ( Fig. 2 ), z. B. steel cylinder, or satellite cylinder 07 executed. The axes of rotation R03 and R07 of the pressure point 09 forming cylinder 03; 07 clamp a plane D in the pressure ON position (see, for example, FIG. Fig. 6 or 13 ).

In the execution after Fig. 5 are the axes of rotation R02; R03; R07 of the three cooperating cylinders 02; 03; 07 during a print-on position AN substantially in a common plane E, which in this case coincides with the plane D, and run parallel to each other (see Fig. 5 . 12 ). If the satellite cylinder 07 has two pressure points on its circumference, a second printing unit, not shown, is preferably also arranged in the common plane E. However, it can also define its own level E, which is also different from the level D associated with it.

As in the embodiment according to Fig. 1 shown, acts as a second transfer cylinder 07 executed third cylinder 07 with a fourth cylinder 11, in particular a second forme cylinder 11 with an axis of rotation R11 together, and forms a second printing unit 12. The two printing units 01; 12 form a on both sides of the same time on the web 08 printing printing unit 13, a so-called. Double printing 13th

In Fig. 5 lie all axis of rotation R02; R03; R07; R11 of the four cylinders 02; 03; 07; 11 during printing, ie in the print-on position AN in the common plane E or D and run parallel to each other. Fig. 6 and 13 shows a corresponding printing unit 13, wherein in each case a pair of forming and transfer cylinders 02, 03; 11, 07 a plane E, and the transfer cylinder 03; 07 form the plane D different from the planes E.

In the case of the double printing unit 13 ( Fig. 1 ) also have the cylinder 07; 11 of the second printing unit 12 channels 04; 06 with the properties described above for the first printing unit 01 with respect to the number and the offset to each other. The channels 04; 06 of the four cylinders 02; 03; 07; 11 are now preferably arranged so that in each case two channels 04; 06 two cooperating cylinder 02; 03; 07; 11 roll on each other.

The forme cylinder 02 and the transfer cylinder 03 each have a length L02 in an advantageous embodiment; L03 on which four or more widths of a printed page, z. B. a newspaper page, z. B. 1100 to 1800 mm, in particular 1500 to 1700 mm and a diameter D02; D03, z. B. 130 to 200 mm, in particular. 145 to 185 mm, whose circumference U corresponds substantially to a length of a newspaper page, hereinafter referred to as "single circumference" (US Pat. Fig. 3 and 4 ). Also for other sizes, the device is advantageous in which the ratio between diameter D02; D03 and length L02; L03 of the cylinder 02; 03 is less than or equal to 0, 16, in particular less than 0.12, or even less than or equal to 0.08.

In an advantageous embodiment, each of the two cylinders 02; 03 two channels 04; 06, which in each case extend at least over a length which corresponds to two widths of a newspaper page ( Fig. 3 ).

It can per cylinder 02; 03 but also more than two channels 04; 06 be arranged. In this case, two channels 04; 06 in a flight, or in each case be arranged alternately. However, for example, four channels 04; 06 the two the end faces of the cylinder 02; 03 adjacent channels 04; 06 in a common flight, and the two "inside" channels 04; 06 in a common flight, but circumferentially offset to the former ( Fig. 4 ).

The channels 04; 06 or slots 04; 06 can be made slightly longer than the width or double width of the print page. Possibly. can two longitudinally adjacent channels 04; 06 also overlap slightly in the circumferential direction. This is in the only schematically shown FIGS. 1 to 4 not so detailed.

Particularly advantageous with regard to the excitation or damping of vibrations caused by channel impact is when the channels 04; 06 on the respective cylinder 02; 03; 07; 11 are offset by 180 ° to each other. To roll the channels 04; 06 between the forme cylinders 02; 11 and the transfer cylinders 03; 07 of the two printing units 01, 12 at the same time and in the region of the same section in the longitudinal direction of the cylinder 02; 03; 07; 11 off; z. B. on the same page, z. B. a page I ( Fig. 1 . 3 and 4 ) of the double printing unit 13 in one stage of the cycle, and in the other phase on one side II, or in more than two channels 04; 06 per cylinder 02; 03; 07; 11, for example in the region of the center of the cylinder 02; 03; 07; 11th

Due to the staggered arrangement of the channels 04; 06 and the unrolling of all channels 04; 06 in the manner described, and in addition, if necessary, the linear arrangement of all cylinders 02; 03; 07; 11 in a plane E, the excitation of vibrations is significantly reduced. Due to the synchronous and possibly symmetrical unwinding at the two printing units 01; 12 there is a destructive interference of the excitations, which in the choice of the offset of the channels 04; 06 on the cylinders 02; 03; 07; 11 by 180 ° from the speed of the cylinder 02; 03; 07; 11 or the frequency takes place independently.

The channels 04; 06 are in an advantageous embodiment with a gap of small width, z. B. less than or equal to 3 mm, in the region of a lateral surface of the forme cylinder 02; 11 or transfer cylinder 03; 07 executed, which ends of one or more elevators, z. B. one or more blankets, on the transfer cylinder 03; 07 or ends of one or more elevators, z. B. one or more printing plates on the forme cylinder 02; 11 takes up. The elevator on the transfer cylinder 03; 07 is preferably designed as a so-called. Metal blanket, which has a druckfarbenführende coating on a metallic base plate. The folded ends are in the case of transfer cylinders 03; 07 for example by clamping and / or clamping devices and in the case of Formzylindem 02; 11 by clamping devices in the channels 04; 06 held.

In each of the channels 06 of the transfer cylinder 03, a single, continuous clamping and / or tensioning device or it can - in the case of over several newspaper page widths through channels in the longitudinal direction one after the other several clamping and / or clamping devices can be arranged. The channels 04 of the forme cylinder 02, for example, each also have a single, or more clamping devices.

Preferably, both in the channels 04 of the forme cylinder 02; 11 and in the channels 06 of the transfer cylinder 03; 07 a "minigap technology" used, wherein in a narrow channel 04; 06 inserted with an inclined leading edge a leading end, the elevator on the cylinder 02; 03; 07; 11 is wound, the trailing end also in the channel 04; 06 is inserted, and the ends against slipping, z. B. by means of a rotatable spindle or a pneumatic device to be clamped.

However, it can also be used both for the elevator on the forme cylinder 02; 11, as well as for the designed as a metal blanket elevator of the transfer cylinder 03; 07 as a narrow slot 04; 06 executed channel 04; 06 can be arranged without clamping device which receives the ends of the lifts. The ends are in this case, for example, by their shape and / or the geometry of the slot in the slot 04; 06 held.

The transfer cylinder 03; 07 have z. B. in an advantageous embodiment ( Fig. 3 ) Only two, circumferentially offset by 180 ° to each other elevators, each having at least one width, which corresponds to two widths of a newspaper pages. In this case, the elevators or channels 04 of the forme cylinder 02 run; 11 complementary to this and must either, as shown, two continuous, each having a length of two newspaper page widths having channels 04, or in pairs adjacent and aligned escape channels 04, each having a length of a newspaper page width. In the former case, each executed as a channel 04 interruption 04 of the forme cylinder 02; 11 in an advantageous embodiment, two clamping devices each have a length which substantially corresponds to a width of a newspaper page, on.

The form cylinder 02; 11 are in an advantageous embodiment with four in the longitudinal direction of the forme cylinder 02; 11 juxtaposed bendable elevators occupied, which in the circumferential direction have a length of slightly more than the length of the print image of a newspaper page, and in the longitudinal direction has a width of about one newspaper page. With arrangement of continuous channels 04 and only one clamping device per channel 04; 06, which has a length of two widths of a newspaper page, it is also possible elevators with a width of two newspaper pages, so-called panoramic printing plates to raise.

For printing units 01; 12, for which a need for setup with panorama printing plates can be excluded, can also be an arrangement of advantage, with each of the side I and adjacent to the side II "outer" lifts aligned with each other and the "inner" lifts aligned with each other and the first mentioned are arranged offset by 180 ° ( Fig. 4 ). This highly symmetrical arrangement additionally reduces or avoids the risk of vibration excitation in the plane E, which is due to the non-simultaneous passage of the channels 04; 06 on page I and page II. Also by it alternately on page I and page II alternately tensioning and relaxing the web 08, and thereby caused swinging of the web 08 can be avoided.

The said arrangement of the interruptions 04; 06 on the respective cylinder 02; 03; 07; 11 and between the cylinders 02; 03; 07; 11 and possibly the linear arrangement of the cylinder 02; 03; 07; 11 are in development also particularly on cylinder 02; 03; 07; 11, which has a length L02; L03, which corresponds to substantially six times the width of a newspaper page.

For a technically simple and robust embodiment of the double printing unit 13, the forme cylinder 02; 11 in an advantageous embodiment with respect to their axes of rotation R02; R11 firmly arranged. To turn on and off the printing units 01; 12 are the transfer cylinder 03; 07 with respect to their axes of rotation R03; R07 designed to be movable and at the same time from the associated forme cylinder 02; 11 and cooperating transfer cylinder 03; 07 abstellbar, or adjusable to this. In this embodiment, in normal operation of the printing machine, only the transfer cylinder 03; 07 moves while the forme cylinder 02; 11 remain in their fixed, possibly previously adjusted position. For the purpose of adjustment, the forme cylinder 02; 11 but in corresponding devices, eg. B. in eccentric or Doppelexzenterbuchsen, in linear guides or levers to be stored.

The transfer cylinder 03; 07 can, as in the Fig. 5 to 7 schematic, as well as in 8 to 11 shown in more detail, along a linear travel 16, or as in FIGS. 12 and 13 schematically as well as in Fig. 14 and 15 shown in more detail, along a curved travel 17 to be movable. Travel 16 and 17 and the transfer cylinder 03; 07 in a pressure-off position AB are in the Fig. 5, 6 and 12 shown in dashed lines.

In another embodiment, not shown, the travel 16; 17 by the storage of the transfer cylinder 03; 07 in eccentric bushes, not shown, in particular in Doppelexzenterbuchsen generated. With double eccentric bushings can be in the range of the pressure-on position AN a substantially linear travel 16, in the remainder of the pressure point 09 area, however, if necessary, generate a curved travel 17, which a faster or greater shutdown of the transfer cylinder 03; 07 from the cooperating transfer cylinder 07; 03 as the associated forme cylinder 02; 11 or vice versa. Also for the use of eccentrics storage on page I and on page II of the double printing unit 13 is advantageous.

Hereinafter ( Fig. 5 to 11 ) are exemplary embodiments of the printing unit 01; 12 set forth, wherein at least one of the transfer cylinder 03; 07 is movable along a linear travel path 16 ( Fig. 5 ):

The linear travel 16 is carried out by means not in Fig. 5 shown linear guides, which in or on in Fig. 5 also not shown side frame are arranged. The storage in a linear guide for the robust and low-vibration design preferably on page I and on page II of the double printing 13th

In Fig. 5 the course of the web 08 is represented by the pressure point 09 located in the pressure on position AN. The plane E of the double printing unit 13 ( Fig. 5 ) or the respective printing unit 01; 12 ( Fig. 6 ) and the plane of the web 08 intersect in an advantageous embodiment at an angle a of 70 ° to 85 °. This choice of the angle α contributes to a safe and quick release of the web 08 and / or the parking of the transfer cylinder 03; 07 from each other with minimized travel 16 bill, and minimizes the other negative influences on the print result, which by the degree of a partial wrap of or the transfer cylinder 03; 07 (doubling, lubricating, etc.). With an optimized arrangement, the required linear travel 16 of each transfer cylinder 03; 07 less than or equal to 20 mm for the on / off of the transfer cylinder 03; 07 to each other / each other, for an exemption of the web 08 in an imprint operation, however, up to 35 mm.

When arranging the rotation axes R02; R03; R07 of forming, transfer and impression cylinders 02; 03; 07 in the level E ( Fig. 5 ) forms the direction of the linear travel 16 with the plane E, which here coincides with the plane D, an angle δ, which is substantially 90 °. The direction of the linear travel 16 forms with a plane of the incoming or outgoing web 08 in the region of an obtuse angle β between the web 08 and E plane an angle γ. In the case of a straight run of the web 08 is β = 180 ° - α, where γ z. B. at 5 to 20 °, in particular 7 to 13 °. The obtuse angle β is linear printing unit 01 and straight-ahead web 08 then preferably at 95 ° to 110 °.

In the event that only one of the form and the associated transfer cylinder 02, 03; 11, 07 determine the plane E in position Fig. 6 ), the angle γ between the travel 16 and the plane of the web 08 is preferably greater than or equal to 5 °, z. B. between 5 ° and 30 °, in particular between 5 ° and 20 ° to choose. The angle γ is in particular for forme cylinder 02; 03; 07; 11 simple circumference greater than or equal to 10 °. However, the angle γ is limited upwards so that the angle δ between the in the direction of the forme cylinder 02; 11 facing portion of the plane E and the direction of the Abstellweges 16 is at least 90 °. So is a quick and safe shutdown of the transfer cylinder 03; 07 simultaneously from the web 08 and the associated forme cylinder 02; 11 guaranteed.

The above relations are to be applied accordingly for "non-straight" running of the track 08 taking into account the respective obtuse angle between track 08 and plane E.

Regardless of the relative course of the web 08, the direction of the travel 16 (in the direction of shutdown) is selected so that an angle φ between the plane D and the travel 16 in the direction of shutdown at least 90 ° and at most 120 °, in particular from 90 ° to 115 ° is. However, the angle φ is again limited upward such that the angle δ is at least 90 °.

The double printing unit 13 is multiple, as in Fig. 7 represented, for example, twice, in a printing unit 19, z. B. a so-called. H-printing unit 19, in a common side frame 20 can be used. In Fig. 7 has been dispensed with the separate name of the upper double printing unit 13 similar parts for each underlying double printing unit 13. In arrangement of all cylinders 02; 03; 07; 11 with a circumference which substantially corresponds to a length of a newspaper page can be saved in space, ie at a height h of the printing unit 19. Of course, this also applies to individual printing units 01; 12, for double-printing 13 and for differently configured printing units, which several printing units 01; 12 have. The priority, however, instead of a saving in height h even with improved accessibility of the cylinder 02; 03; 07; 11, z. B. for the purpose of changing elevators, cleaning and washing, maintenance, etc., are.

The pressure on or off position AN; AB is shown exaggerated in all figures for clarity. Fig. 7 indicated by dashed lines the transfer cylinder 03; 07 in a second possible position along the linear travel 16, wherein here, for example, the upper double printing unit 13, z. B. for the printing plate change, in the print-off position AB (solid), and the lower double printing unit 13, z. B. to the continued pressure, in the print-on position ON (solid) is operated.

In an advantageous embodiment, each of the printing units 01; 12 at least one own, but in Fig. 7 only indicated by dashed lines drive motor 14 for the rotary drive of the cylinder 02; 03; 07; 11 on.

This can be done in a Fig. 7 (Above) schematically illustrated embodiment, a single drive motor 14 for the respective printing unit 01; 12, which in this case, in an advantageous embodiment, first on the forme cylinder 02; 11 drives, and from there via a mechanical drive connection, z. B. spur gears, timing belt, etc., on the transfer cylinder 03; 07 is driven. However, it may also be advantageous for reasons of space and for reasons of torque flow, from the drive motor 14 to the transfer cylinder 03; 07 and from there to the form cylinder 02; 11 to drive.

The printing unit 01 has a high degree of flexibility in the various operating situations such as print run, registration, lift change, washing, web feed etc. 12 in one embodiment via its own, and mechanically independent of the other drives drive motor 14 per cylinder 02; 03; 07; 11 ( Fig. 7 , below).

The type of drive out Fig. 7 (top and bottom) are shown as examples and thus transferred to the other example.

The drive by the drive motor 14 takes place in an advantageous embodiment in each case coaxially between the axis of rotation R02; R03; R07; R11 and motor shaft, possibly with an angle and / or offset compensating, explained in more detail below coupling. He may, if a "co-moving" of the drive motor 14 or a flexible coupling between the drive motor and the possibly to be moved cylinder 02; 03; 07; 11 is to be avoided, but also done via a pinion.

A first embodiment of the realization of the linear travel 16 by means of linear guide show the Fig. 8 and 9 ,

The pin 23 at least one of the transfer cylinder 03; For example, bearing housings 24 designed as carriages 24 are rotatably mounted in radial bearings 27 (in FIG Fig. 8 and 9 only the arrangement in the region of one end face of the cylinder 02; 03; 07; 11). The bearing housing 24 or carriage 24 are movable in linear guides 26, which are connected to a side frame 27.

The linear guides 26 are for the linear arrangement of the double printing unit 13 in an advantageous embodiment almost perpendicular to the plane E and D, ie δ = 90 ° (see Fig. 5 ), oriented. In a preferred embodiment, two linear guides 26 are provided for guiding each bearing housing 24 or slide 24, which run parallel to each other Also the linear guides 26 of two adjacent transfer cylinder 03; 07 are preferably parallel to each other.

The linear guides 26 may be arranged in an embodiment not shown directly to walls of the side frame 27, in particular on walls of openings in the side frame 27, which almost perpendicular to the end face of the cylinder 02; 03; 07; 11 run.

In the embodiment according to Fig. 8 and 9 the side frame 27 in an opening an insert 28, z. B. a so-called. Bell 28, on. The linear guides 26 are arranged on or in this bell 28.

In an advantageous embodiment, the bell 28 an area which in the direction of cylinder 02; 03; 07; 11 emerges from the alignment of the side frame 27. The linear guides 26 are arranged in or on this area of the bell 28.

The distance of the two opposite side frames 20 (only one shown) is oriented i. d. R. on the widest aggregate, z. B. at the wider inking unit 21, and usually causes a correspondingly longer pin on the cylinders 02; 03; 07; 11.Previous of the o. G. Arrangement is that the pins of the cylinder 02; 03; 07; 11 can be kept as short as possible.

The bell 28 has in a development on a cavity 29, which is at least partially disposed at the level of the alignment of the side frame 20. In this cavity 29 are, as in Fig. 9 shown schematically, the rotary drives of the cylinder 02; 03; 07; 11 with the pins of the cylinder 02; 03; 07; 11 connected.

Particularly advantageous pairwise drive the cylinder 02; 03; 07; 11 (see eg Fig. 11 ) can also drive connections, such. B. co-acting drive wheels 30 are housed in this cavity 29. On the transfer cylinder 03; 07 can in an advantageous embodiment ( Fig. 9 ) with frame-fixed drive motor 14 between transfer cylinder 03; 07 and drive motor 14 an angle and offset compensating coupling 61 may be arranged to the arrival and Abstellbewegung of the transfer cylinder 03; 07 balance. This can be designed as a double joint 61 or in an advantageous embodiment as all-metal coupling 61 with two torsionally rigid but axially deformable plate packs. The all-metal coupling 61 can simultaneously compensate for the offset and the change in length caused therefrom. It is essential that the rotational movement is transmitted without play.

In particular, in the case of the coaxial drive of the forme cylinder 02; 11, the drive of the forme cylinder-02; 11 between pin 51 and drive motor 14, a clutch 62, which for adjusting the side register at least one axial relative movement between the cylinder 02; 11 and drive motor 14 receives. To include manufacturing tolerances and possibly required movements of the forme cylinder, 02; Receive 11 for adjustment purposes, the coupling 62 is designed as at least slight angle and offset compensating coupling 62. This is also carried out in an advantageous embodiment as all-metal coupling 62 with two torsionally rigid but axially deformable plate packs. The linear movement is absorbed by the disk packs connected in a form-fitting manner in the axial direction with the journal 51 or a shaft of the drive motor 14.

If lubrication, for example a lubricant or oil chamber is required, the cavity 29 can be limited in a simple manner by means of a cover 31 (dashed), without this increasing the width of the machine or protruding from the side frame 20. The cavity 29 can then be carried out encapsulated.

The arrangement of the bell 28 thus shortens the length of the pin, which results in a reduction of the vibration, and allows a simple and variable design, which is suitable for a variety of drive concepts, and largely identical in design, the change between the concepts - with or without drive connections, with or without lubricant, with or without additional couplings - allowed.

The drive of the respective bearing housing 24 or carriage 24 in the linear guides 26 takes place in the in Fig. 8 schematically illustrated embodiment z. B. by linear actuators 32, z. B. in each case a screw drive 32, z. B. a threaded spindle which is driven by an electric motor, not shown. The electric motor can be regulated in this case with respect to a rotational position. To limit travel in pressure-on position AN, a frame-fixed, but adjustable stop for the bearing housing 24 may be provided.

The drive of the bearing housing 24 can also be done by means of a lever mechanism. This can also be driven by means of an electric motor or by means of at least one pressurizable cylinder pressure cylinder. If the lever mechanism is driven by means of one or more cylinders which can be acted upon with pressure medium, the arrangement of a synchronizing spindle synchronizing the adjusting movement on the two sides I and II is advantageous.

The connection of the transfer cylinder 03 to be moved; 07 to the side frame 20 and the bell 28 is in the embodiment according to Fig. 9 As follows: On both sides of the carriage 24 to be guided, the bell 28 has supporting walls 33 which receive one of the two corresponding parts of the linear guide 26. If necessary, this part can already be part of the supporting wall 33 or incorporated into it. The other corresponding part of the linear guide 26 is arranged on the carriage 24 or incorporated in this or having this. In an advantageous embodiment, the carriage 24 is guided by two such, arranged on two opposite sides of the carriage 24 linear guides 26.

The on the support walls 33 (or without bell 28 directly on the side frame 20) arranged parts of the guides 26 so include the arranged between them carriage 24. The active surfaces of the connected to the side frame 20 and the bell 28 parts of the linear guide 26 have in the Pin 23 facing half space. To reduce the friction between the co-operating parts of the guides 26 are in an advantageous embodiment bearing 34, z. B. linear bearings 34, in particular a linear movement enabling rolling bearing cages 34 arranged.

The two parts of the two guides 26 allow in the ideal state, a movement of the carriage 24 only with a degree of freedom as a linear movement. For this purpose, the entire arrangement is in a direction perpendicular to the axis of rotation R03; R07 and perpendicular to the direction of movement of the carriage 24 lying direction against each other clamped essentially free of play. Thus, for example, the respective formzylindernahe part of the guide (in Fig. 9 with larger dimensions) a tensioning device, not shown, on.

The mounted in the manner described slide 24 has, for. B. on a radially inwardly directed side of the transfer cylinder 03; 07 facing recess, the pin 23 receiving radial bearing 27.

In a second, and in particular with regard to the space and a robust construction advantageous embodiment ( Fig. 10 and 11 ), the active surfaces of the parts connected to the side frame 20 and the bell 28 of the linear guide 26 in the pin 23 facing away from the half space. For this purpose, these parts of the linear guide are arranged on a carrier 36 connected to the bell 28 (or the side frame 20). The carriage 24 has its associated parts of the linear guide 26 in a side frame 20 and the bell 28 facing recess. These parts may be arranged in the recess as components, or may already be incorporated in the carriage 24 in an inwardly directed surface of the recess. As in the embodiment according to Fig. 9 the carriage 24 has a transfer cylinder 03; 07 facing recess, in which the radial bearing 27 is arranged to receive the pin 23. In the present embodiment, a running surface for rolling elements of the rolling bearing 27 designed as a radial bearing 27 is already incorporated in an inwardly directed surface of the recess.

The parts of the guides 26 arranged on the carriage 24 thus comprise the carrier 36 or the parts of the guides 26 arranged on the carrier 36, on the side frame 20 or on the bell 28.

At least one of the two the transfer cylinder 03; 07 associated carrier 36 has in an advantageous embodiment, an oriented in the direction of movement of the carriage 24, not visible in the figures long hole for performing the pin 21 to be moved linearly. This slot is aligned at least in part with a likewise not visible, in the bell 28 (or in the associated side frame 20) arranged slot. These slots are penetrated by the pin 23 or connected to the pin 23 shaft, which for the rotary drive of the transfer cylinder 03; 07 with a drive wheel 30 (see Fig. 9 ) or the drive motor 14 is in drive connection.

The drive of the carriage 24 can take place in one of the already mentioned in the first embodiment manner. Fig. 11 shows the execution of an executed as a lever mechanism actuating means. The carriage 24 is pivotally connected via a coupling 37 with a lever 38, which is about a substantially parallel to the axis of rotation R03; R07 of the transfer cylinder 03; 07 extending axis is pivotable. In the embodiment, the synchronization of the adjusting movement of both transfer cylinders 03; 07, the coupling 37 of the two adjacent slide 24 for the co-operating transfer cylinder 03; 07 hingedly connected to the here as three-armed lever 39 running lever 38. The drive of the lever 38 by means of at least one actuator 39, z. B. by means of one or by means of two (as in Fig. 10 Upon actuation of the actuator 39 and pivoting of the lever 38 in one direction (here in the clockwise direction), the two transfer cylinder 03; 07 with their axes of rotation R03; R07 brought into the plane E, while at the same time to each other and to the respective forme cylinder 02; 11 are employed. By pivoting in the other direction, the stopping of the transfer cylinder 03; 07 from each other and from the associated form cylinders 02; 11th

In particular, in the event that the actuator 39 is designed as acted upon by pressure medium cylinder 39, the arrangement of stops 41 is advantageous, against which the respective carriage 24 is placed in the print-on position ON. These stops are made adjustable to adjust the end position for the transfer cylinder 03; 07 to allow in which their axes of rotation R03; R07 come to lie in the plane E. The system becomes very stiff when the carriage 24 against the stop 41, or the stops 41 (in Fig. 10 two each), is pressed with great force.

Be, as in the present case, the carriage 24 of the two adjacent transfer cylinder 03; 07 set over a common adjusting means, it is advantageous in development of the embodiments, when the adjusting means between the respective slide 24 and the first common part of the actuating means is designed to be yielding at least within narrow limits. For this purpose, each coupling 37 in the manner of a strut a spring assembly 42, z. B. a cup spring package 42. While at pressure ON position ON the spring assembly 42 of a transfer cylinder 03; 07 is compressed, that is the other transfer cylinder 07; 03 associated spring package 42 under tensile stress.

For synchronizing the linear movement of both sides of the transfer cylinder 03; 07 is a wave 43, z. B. a synchronous shaft 43, with the on both sides of the transfer cylinder 03; 07 arranged adjusting means in connection. For this purpose, in the example, the shaft 43 with the two, each a side frame 20 on side I and II associated levers 38 rotatably connected. This represents here simultaneously the pivot axis for the lever 38.

For the embodiments of the FIGS. 8 to 11 An adjustment device may be provided, which, in particular during assembly and / or if configurations and / or conditions have changed, a basic setting for the distances of the rotation axis R02; R03; R07; R11 allows. For this purpose, individual cylinders 02; 03; 07; 11, z. B. the forme cylinder 02; 11, possibly stored in an eccentric bush. Also, at least one of the transfer cylinder 03; 07 may be adjustable for adjustment in a radial direction. For example, the parts of the linear guides 26 or the carrier 36 assigned to the side frame 20 or the bell 28 can be connected to the side frame 20 or the bell 28 in oblong holes which are sufficient for adjustment purposes. An eccentric and lockable mounting of the radial bearing 27 in the carriage 24 is possible.

Hereinafter ( FIGS. 12 to 18 ) are exemplary embodiments of the printing unit 01; 12 set forth, wherein at least one of the transfer cylinder 03; 07 along a curved travel path 17 is movable ( Fig. 12 ):

Im schematically in Fig. 12 illustrated lever 18 is one of the transfer cylinder 03 pivotally mounted about a pivot axis S. The pivot axis S is here z. B. in the plane E. The lever 18 in this case has a length between the mounting of the axis of rotation R03; R07 of the transfer cylinder 03; 07 and the pivot axis S on, which is greater than the distance of the rotation axis R03; R07 of the transfer cylinder 03; 07 from the axis of rotation R02; R11 of the associated forme cylinder 02; 11 in pressure ON position. This is a simultaneous shutdown of co-acting transfer cylinder 03; 07 and the associated forme cylinder 02; 11, and vice versa for hiring.

However, the pivot axis S can in particular also, as described in more detail below, in another way eccentric to the axis of rotation R02; R11 of the associated forme cylinder 02; 11, z. B. at a distance to the plane E, be arranged. The storage in a lever 18 is preferably carried out on page I and on page II of the double printing unit thirteenth

Also in FIGS. 12 and 13 the course of the web 08 is represented by the pressure point 09 located in the pressure on position AN. The plane E of the double printing unit 13 ( Fig. 12 ) or the respective printing unit 01; 12 ( Fig. 13 ) and the plane of the web 08 intersect here in an advantageous embodiment at an angle α of 70 ° to 85 °. Assign the transfer cylinder 03; 07 on a circumference, which corresponds to the length of about a newspaper page, so the angle α z. B. about 75 ° to 80 °, preferably about 77 °. Again, this choice of angle α contributes to the safe and quick release of the web 08 and / or stopping the transfer cylinder 03; 07 from each other with minimized travel 16 at. On the other hand, it minimizes negative influences on the print result, which is due to the degree of partial looping of the transfer cylinder or cylinders 03; 07 is significantly influenced (doubling, lubricating, etc.)

The double printing unit 13 (here in linear design) is multiple, as in Fig. 14 represented, for example, twice, in a printing unit 19, z. B. the so-called. H-printing unit 19, in the common side frame 20 can be used. In Fig. 14 has been dispensed with the separate name of the upper double printing unit 13 similar parts for each underlying double printing unit 13. Among the advantages of this arrangement is the comments on Fig. 7 directed.

Fig. 13 indicated by dashed lines (but for clarity oversubscribed) the transfer cylinder 03; 07 in a second possible position along the travel 17, wherein here, for example, the upper double printing unit 13, z. B. for printing form change, in the print-off position AB, and the lower double printing unit 13, z. B. for continued printing, is operated in the print-on position ON.

In an advantageous embodiment also has each of the printing units 01; 12 at least one own drive motor 14 for the rotary drive of the cylinder 02; 03; 07; 11 on.

This can be done in a Fig. 14 below schematically illustrated embodiment, a single drive motor 14 for the respective printing unit 01; 12, which in this case, in an advantageous embodiment, first on the forme cylinder 02; 11 drives, and from there via a mechanical drive connection, z. B. spur gears, timing belt, etc., on the transfer cylinder 03; 07 is driven. However, it may also be advantageous for reasons of space and for reasons of torque flow, from the drive motor 14 to the transfer cylinder 03; 07 and from there to the form cylinder 02; 11 to drive.

As in the above embodiment, the printing unit 01; 12 in a version with its own, mechanically independent of the other drives drive motor 14 per cylinder 02; 03; 07; 11 has a high degree of flexibility ( Fig. 14 shown in dashed lines for upper double printing unit 13).

The type of drive out Fig. 14 (top or bottom) are each exemplified and thus to the respective other printing units 01; 12 and the other double printing unit 13 to transfer.

The drive by the drive motor 14 takes place in an advantageous embodiment in each case coaxially between the axis of rotation R02; R03; R07; R11 and motor shaft, possibly via the above already detailed, angle and / or offset compensating couplings 61; 62. The drive can, if a "co-moving" of the drive motor 14 or a flexible coupling between the drive motor and the possibly to be moved cylinder 02; 03; 07; 11 is to be avoided, but also done via a pinion.

An embodiment of the realization of the curved travel 17 by means of the lever 18 show the Fig. 15 and 16 ,

Fig. 15 shows a side view, wherein two of each frontally on the transfer cylinder 03; 07 (dashed) arranged pin 23 only one is visible.

The lever 18 is pivotally mounted about the pivot axis S, which is preferably fixed relative to the side frame 20 (but possibly adjustable). The rotation axes R02; R03; R07; R11 of the cylinder 02 shown in broken lines; 03; 07; 11 lie in the illustrated embodiment in pressure-on position again in a plane E, which here with the plane D between the pressure point 09 forming cylinders 03; 07 coincides.

The pivot axis S of the lever 18 is eccentric to the rotation axis R02; R11 of the forme cylinder 02; 11 and is located outside the plane E or D. A pivoting of the lever 18 about the pivot axis S by means of a drive means 44, for. B. by means of a pressure medium cylinder 44, via an actuating means 46, z. B. a one- or multi-part coupling 46, for example via a lever or toggle mechanism 46 causes a Ab- or hiring the transfer cylinder 03; 07 at the same time from or to the associated forme cylinder 02; 11 and from or to the respective other transfer cylinder 07; 03. The toggle mechanism 46 is pivotally connected to the lever 18 and a frame-fixed pivot point. The advantageous manner double-acting pressure cylinder acts z. B. on a movable joint of the toggle mechanism. For this process, the axes of rotation remain R02; R11 of the forme cylinder 02; 11 in peace. Thus, the movement of the two frontally arranged lever 18 per transfer cylinder 03; 07 takes place synchronously, the adjusting means 44, a two adjusting means 44 connecting shaft 47, z. B. a synchronous shaft 47, or be connected to such. To the desired, z. B. linear arrangement of the cylinder 02; 03; 07; To ensure 11, a stop 48 is provided for each lever 18, which is preferably carried out adjustable.

The drive and adjusting means 44; 46 are designed and arranged such that a shutdown of the transfer cylinder 03; 07 takes place in each case in the direction of the obtuse angle β (for a straight web run 180 ° -α) between web 08 and plane D or E.

The eccentricity e-S of the pivot axis S to the rotation axis R02; R11 of the forme cylinder 02; 11 is between 7 and 15 mm, in particular about 9 to 12 mm. The eccentricity e-S is in Anstelllage the transfer cylinder 02; 03; 07; 11, d. H. the rotation axes R03; R07 are in the o. G. Plane D, so oriented that an angle ε-S between the plane D of the pressure point 09 forming cylinder 03; 07 and the connection plane V of the pivot axis S and the rotation axis R02; R11 is between 25 ° and 65 °, advantageously between 32 ° and 55 °, in particular between 38 ° and 52 °, the pivot axis S preferably in the region of an obtuse angle β between the plane D and the incoming or outgoing web 08, and spaced further from the pressure point 09 than the axis of rotation R02; R11 of the associated forme cylinder 02; 11. For vertical, and, except for an optionally caused by partial looping offset, straight web course and an angle 77 ° between the plane D and the plane of the web 08, the eccentric e-S z. B. an angle of 12 to 52 °, advantageously 19 to 42 °, in particular 25 to 39 ° to the horizontal H.

Ideally, d. H. with never changing conditions and tolerance-free production, the arrangement is sufficient as previously described without further adjustment mechanisms of the requirement for on and off the printing units 01; 12 and the double printing 13th

However, in order to compensate for any manufacturing tolerances that may occur and / or to be able to make a basic setting for the elevators, printing materials, etc., further adjustment options are provided for adjustment purposes:

The rotation axis R02; R11 of the forme cylinder 02; 11 is adjustable, z. B. also eccentric to its attachment to the side frame 20, here to a bore 49, stored. In the present case, a pin 51 of the forme cylinder 02; 11 arranged in an eccentric bearing 52 and an eccentric bearing bush 52 which is pivotally mounted in the bore 49.

A pivot axis S51 of the forme cylinder 02; 11 is an eccentricity of 5 to 15 mm, in particular about 7 to 12 mm eccentric to the axis of rotation R02; R11 of the forme cylinder 02; 11 is located and lies outside the level E.

The eccentricity e-S51 is in Anstelllage of form and associated transfer cylinder 02, 03; 11, 07, d. H. the axes of rotation R02, R03 and R11, R07 are in the plane E, oriented so that an angle ε-S51 between the plane E of the pair of cylinders 02, 03 and 11, 07 and a connecting plane of the pivot axis S51 and the axis of rotation R02; R11 of the forme cylinder 02; 11 between 25 ° and 65 °, advantageously between 32 ° and 55 °, in particular between 38 ° and 52 °. The pivot axis S5 is preferably in a half-plane which is farther from the axis of rotation R03; R07 of the associated transfer cylinder 03; 07 as the rotation axis R02; R11 of the associated forme cylinder 02; 11 is located.

The pivot axis S51 for the eccentric mounting of the forme cylinder 02; 11 coincides in the embodiment with the pivot axis S of the lever 18 together.

The coincidence of the pivot axis S and S51 is not mandatory, but useful. Especially by the relative to the side frame 20 fixed pivot axis S, which by pivoting the forme cylinder 02; 11 is not affected, allows a simple and accurate adjustment. In principle, the lever 18 could also be arranged on an eccentric flange of the journal 51 receiving bearing bushing 52, which, however, upon rotation, a simultaneous adjustment of the distances between Form 02; 11 and transfer cylinder 03; 07 and between the transfer cylinders 03; 07 would result.

In an advantageous embodiment, the two pivot axis S51 (and / or S) and S23 of a pair of forming and transfer cylinders 02, 03; 11, 07 arranged on two different sides of the plane E.

By means of a second adjusting means 53, the position of the forme cylinder 02; 11 corresponding to the desired position with respect to the plane E or in view of the required distance to the transfer cylinder 03; 07 for the pressure-on position by slight rotation of the eccentric 52 adjustable. This position is fixed, for example after adjustment by means not shown.

In order to set the printing gap at the printing location 09 in the print-on position, at least the pins 23 are one of the two transfer cylinders 03; 07, here the transfer cylinder 07, adjustable. They are z. B. also eccentrically mounted in the associated lever 18. An eccentricity e-S23 of a pivot axis S-23 to the rotation axis R03; R07 of the transfer cylinder 03; 07 is between 1 and 4 mm, in particular about 2 mm. The eccentricity e-S23 is in Anstelllage the pressure point 09 forming cylinder 03; 07, d. H. the rotation axes R03; R07 lie in the plane D, oriented so that an angle ε-S23 between the plane D and the connecting plane of the pivot axis S-23 and the axis of rotation R07 (R03) between 70 ° and 110 °, advantageously between 80 ° and 100 °, in particular between 85 ° and 95 °. In the example, the angle ε-S23 should be about 90 °.

In Fig. 16 is an embodiment according to Fig. 15 given in a representation of a section along the plane E. The pins 51 of the forme cylinder 02; 07 are each in camps 54, z. B. bearings 54 rotatably mounted. In order to make an adjustment or a correction of the side register, allows in an advantageous embodiment of this bearing 54 or an additional, not shown thrust bearing the movement of the forme cylinder 02; 11 and its pin 51 in the axial direction. The bearings 54 are arranged in the eccentric bearing 52 and eccentric bearing bush 52, which in turn is pivotally mounted in the bore 49 in the side frame 20. It can be arranged between the bore 49 and pin 51 in addition to the eccentric bushing 52 and the bearing 54 even more bearing rings and sliding or rolling bearings. The lever 18 is on a forme cylinder 02; 07 out of the side frame 20 projecting part of the bearing bush 52, and pivotally mounted relative to this. The lever 18 takes in its the pivot axis S far end of the pin 23 of the transfer cylinder 03; 07, which is arranged rotatably in a bearing 56, and this in the case of the transfer cylinder 07, about the pivot axis S-23 pivotable in an eccentric bearing 57 and in an eccentric bearing bush 57. Such a pivotable bushing 57 may, if necessary, for both transfer cylinder 03; 07 be arranged.

Advantageously, at least on a drive side of the printing press, that side frame 20 recesses 58, in which the pin 23 of the transfer cylinder 03; 07 are pivotable. The adjusting means 46; 53 and drive means 44 are in Fig. 8 not shown.

The rotary drive of the cylinder 02; 03; 07; 11 takes place by means of their own, mechanically from the drive of the other cylinder 02; 03; 07; 11 independent drive motors 14, which are preferably arranged fixed to the frame. The latter has the advantage that the drive motors 10 need not be moved.

To the pivoting movement of the transfer cylinder 03; 07, the angle and offset compensating coupling 61 is arranged between the transfer cylinder and the drive motor 10, which are designed as double joint 61 or in an advantageous embodiment as all-metal coupling 61. The all-metal coupling 61 simultaneously equalizes the offset and the change in length caused thereby, wherein the rotational movement is transmitted without play.

Also, the drive of the forme cylinder 02; 11 has between pin 51 and drive motor 14, the at least one axial relative movement between the cylinder 02; 11 and drive motor 14 receiving coupling 62 which, in order to also manufacturing tolerances and possibly required adjustment movements of the forme cylinder 02; 11 to be able to accommodate adjustment purposes, at least slight angles and offset can be performed balancing. This is also iri advantageous embodiment designed as all-metal coupling 62, which receives the axial movement through the form-fitting in the axial direction with the pin 51 and a shaft of the drive motor 14 plate packs.

In an in FIGS. 17 and 18 variant shown, a pairwise drive from the drive motor (possibly via other transmission parts not shown) by a pinion 59 on a drive wheel 61 of the transfer cylinder 03; 07 occur when, for example, a special moment flow is to be achieved.

A rotation axis R59 of the pinion 59 is then preferably fixed to the frame in such a way that a straight line G1 fixed by the rotation axis R59 of the pinion 59 and the pivot axis S of the lever 18 with one of the pivot axis S of the lever 18th and the rotation axis R03; R07 of the transfer cylinder 03; 07 defined plane E18 includes an opening angle η in the range of + 20 ° to - 20 °.

In a further development, at the same time one closes by the rotation axis R02; R11 of the associated forme cylinder 02; 11 and the rotational axis R59 of the pinion 59 fixed straight line G2 defined by the rotation axis R59 of the pinion 59 and the pivot axis S of the lever 18 straight line G1 an opening angle λ in the range of 160 ° to 200 °.

If the pressure point is replaced by a transmission 03; 07 and a z. B. as a satellite cylinder 07; 03 executed impression cylinder 07; 03 formed, so can form and transfer cylinder 02; 11; 03; 07 have a single circumference and the associated impression cylinder 07; 03 be designed to be many times larger.

Due to the above-mentioned embodiments, an increased rigidity of the printing unit is also advantageously achieved. This is particularly advantageous in connection with cylinders 02; 03; 07; 11, which have a length corresponding to at least four or even six standing printed pages, especially newspaper pages.

With the measures set out in the exemplary embodiments, it is possible a printing unit 01; 12 with long, slim cylinders 02; 03; 07; 11, which is an o.g. 0.08 to 0.16 diameter to length ratio, robust and low vibration to build or operate, while a small amount of space, operation and frame construction is required. This applies in particular to forme cylinders 02, 11 "simple circumference", d. H. with a newspaper page on the periphery, but with double width, d. H. with four newspaper pages along the length of the cylinders 02; 03; 07; 11th

It is advantageous in the aforementioned embodiments, at least one of the transfer cylinder 03; 07 so far abstellbar that the retracted web 08 can be guided without contact through the pressure point 09 during the printing operation by means of other printing units.

The cylinders 02; 03; 07; 11 can be driven for each embodiment as described either in pairs or individually by each having its own drive motor 14. For special needs, for example, for only a one-sided Imprinterbetrieb or only the need to change the relative angular position of the forme cylinder 02; 11 to each other, a drive is possible, wherein one of the forme cylinder 02; 11 of a printing unit 01; 12 a separate drive motor 14, and the remaining cylinder 02; 03; 07; 11 of the printing unit 01; 12 have a common drive motor 14. Also a configuration of four or five cylinders 02; 03; 07; 11 with three drive motors 14 may be advantageous: In the case of a double printing unit 13 z. B. in each case a drive motor 14 on the forme cylinder 02; 11 and a common for the transfer cylinder 03; 07; in the case of a five-cylinder or satellite printing unit z. B. each pair of forming and transfer cylinder 02; 03; 07; 11 one and for the satellite cylinder own drive motor 14th

As exemplified above in FIG Fig. 11 and 17 illustrated, the four cylinders 02; 03; 07; 11 in pairs by a drive motor 14 depending on the requirements of the forme cylinder 02; 11 or from the transfer cylinder 03; 07 rotationally driven. Each forming a gear drive wheels 30 between the forme cylinder 02; 11 and the respective associated transfer cylinder 03; 07 each form a drive connection with the associated drive motor 14. The two pairs of drive wheels 30 are preferably arranged to one another so that they are disengaged, which takes place, for example, by axially staggered arrangement, ie in two drive levels.

Advantageously, the formation of the co-operating drive wheels (30) between the forming and transfer cylinders 02, 03; 11, 07 each with a straight toothing to a relative axial movement of one of the two cylinders 02; 03; 07; 11, but without changing the relative position in the circumferential direction. The latter also applies to a possibly arranged pinion between the drive motor 14 and the drive wheel of the forme cylinder 02; 11, when the pair on the forme cylinder 02; 11 is not driven coaxially. For this purpose, a cooperating pair of links in the drive connection between the drive motor 14 and forme cylinder 02; 11 straight teeth and against each other to be axially movable to the axial movement of the forme cylinder 02; 11 without ensuring simultaneous rotation. In the Fig. 9 and 11 Each illustrated drive situations are to be transferred alternately to the two illustrated embodiments for the realization of the linear motion.

For all the cases mentioned, the drive motors 14 are arranged fixed to the frame in an advantageous embodiment. If a cylinder 02; 03; 07; 11 driving drive motor 14 deviating from this, however, be arranged fixed to the cylinder, it can during the adjusting movement and / or adjustment of the cylinder 02; 03; 07; 11 in a variant also on a corresponding (or the same) guide or a corresponding lever, for. B. on an outer side of the side frame 20, be carried.

In particular, in the embodiment with a frame-fixed drive motor 14, which on the transfer cylinder 03; 07 (which drives individually or in pairs driven cylinders 02; 03; 07; 11), it is advantageous as in Fig. 9 and 16 shown as an example to arrange the angle and offset compensating coupling 61. As in Fig. 9 . 11 and 16 shown by way of example, has coaxially driven forme cylinder 02; 11 of the drive, the described coupling 62 between pin 51 and drive motor 14.

The drive motor 14 is in each case advantageously designed as an electric motor, in particular as an asynchronous motor, synchronous motor or as a DC motor.

In an advantageous embodiment is between each of the drive motors 14 and the driven cylinder 02; 03; 07; 11, a transmission 63 is arranged. This gear 63 may be connected to the drive motor 14 attachment gear 63, z. B. be a planetary gear 63. However, it may also be used as a gear reducer 63, e.g. B. pinion or belt and drive wheel, be executed.

Advantageously, a single encapsulation of each transmission 63, z. B. as a single-capsulated attachment gear 63. The lubricant spaces thus generated are spatially limited and prevent the contamination of adjacent machine parts and contribute to the quality of the product. In the case of the use of the bell 28 ( Fig. 11 ), the transmission between the forming and transfer cylinders 02, 03; 07, 11 arranged in the cavity 29, and be encapsulated as a lubricant space to the outside.

However, it is generally notwithstanding the design as a single or pair driven cylinder 02; 03; 07; 11 of advantage, the drive units each encapsulated separately, d. H. to run with its own lubricant space. An o. G. individual encapsulation extends, for example, to the pairwise drive of two cylinders 02; 03; 11, 07 or - especially in the case of bell 28 described above - around both pairs. A bell 28 may also each for a pair of two cylinders 02; 03; 07; 11 executed. The latter is for example in the sense of modularization advantage.

In a further development of the embodiments, it is advantageous, although that the respective forme cylinder 02; 11 associated inking unit 21 and, if available, the associated dampening unit 22 of a, independent from the drive of the printing cylinder actuator drive motor is driven in rotation. In particular, the inking unit 21 and the optionally existing dampening unit 22 each have their own drive motor. In the case of an anilox inking unit 21, it may be the anilox roller, and in the case of a roller inking unit 21, the one or more distribution cylinders may be driven individually or in groups in a rotary manner. Also, the one or more distribution cylinders of a dampening unit 22 may or may be driven by rotation individually or in groups.

The execution of the cylinder 02; 03; 07; 11 double-width and "single-circumference" allows significantly higher product variability than double-circumference and single-width presses. Although the maximum number of possible print pages is the same, in the case of the single-width printing units 01; Twelve volumes in collective operation in two different "books" or "stapling". In the present case, the double-wide printing units 01; 12 simple circumference, the (double width) tracks 08 are cut longitudinally after printing. In order to achieve a maximum stitching strength one or more partial webs in the so-called. Falzoberbau or Wendedeck be performed one above the other and z. B. on a folder without collecting operation folded into a booklet. If such stapling strengths are not required, some partial webs can be guided one above the other, but others can be guided together to a second funnel and / or folder. However, it can also be two products of the same strength led without transfer to two folders. A variable strength of two different products is thus given. If at least two product displays are provided in the case of a double-folding apparatus or two folders, then - depending on the arrangement - the two books or products may be side by side or one above the other to one side of the printing press, or else to the two different sides.

A high variability has the double-width printing machine simple scope especially in the gradation of the possible page numbers in the product, in the so-called "fling". While the thickness per booklet (layer) for the printing machine with double circumference and single width in collective mode (ie maximum product thickness) is variable only in steps of four printed pages, the described double-width printing machine simple circumference leaves a "side skip" from two sides (z. B. in newspaper printing) too. The product strength and in particular the "distribution" of the printed pages on different booklets of the overall product or products is considerably more flexible.

After the web 08 has been cut longitudinally, the partial web is thus either guided onto a different former and / or folding apparatus corresponding to the corresponding partial web, or else it is turned on the run of the latter. Ie. in the second case, the sub-web before, during or after turning, but before merging with the "straight paths", placed in the correct longitudinal or cutting register. This is dependent on the mutually circumferentially offset channels 04; 06 of a cylinder 02; 03; 07; 11 in an advantageous embodiment by corresponding design of the turning tail (eg., Preset Distances of the rods or the path sections) taken into account. The fine adjustment or regulation is made with the adjustment paths of the cut register control for the relevant sub-web and / or sub-web strand, in order to bring sub-webs of two different run levels to one another as required.

The form cylinder 02; 11 can now be equipped in the circumferential direction with one and in the longitudinal direction with at least four stationary printed pages in broadsheet format ( Fig. 20 ). Alternatively, this form cylinder 02; 11 also optionally in the circumferential direction with two and in the longitudinal direction with at least four lying printed pages in tabloid format ( Fig. 21 ) or in the circumferential direction with two and in the longitudinal direction with at least eight stationary printed pages in book format ( Fig. 22 ) or in the circumferential direction with four and in the longitudinal direction with at least four lying printed pages in book format ( Fig. 23 ) by means of in the circumferential direction of the forme cylinder 03 each one and its longitudinal direction at least one can be fitted on this, flexible pressure plate.

By means of the double-width printing machine and cylinders 02; 11 and transfer cylinders simple circumference are thus depending on the occupancy of the forme cylinder 02; 11 with horizontal tabloid pages or stationary newspaper pages, in particular broadsheet pages, with horizontal or vertical pages, different products can be produced depending on the width of the web 08 used:

Thus, with the double printing unit 13, the production in a gradation of two stationary arranged on the forme cylinder print pages ("two-sided jump") changeable products in broadsheet format possible.

In the case of four or three or two standing printed pages or a width of the web 08 corresponding to broadsheet format, the production of a product consisting of a layer in the preceding sequence with eight, six, four or two printed pages is in broadsheet format possible.

The double printing unit is web width for a four-paged broadsheet width print page for making two one-ply broadsheet products with four printed pages in one product and four printed pages in the other or two printed pages in the one product and six Print pages in the other product is usable. For a web width corresponding to three standing printed pages, it is useful for making two single-ply broadsheet format products with four printed pages in one product and two printed pages in the other product.

Next is the double printing unit 13 at a four-standing printed pages in broadsheet format corresponding web width for the production of a two-layer product in broadsheet format with four printed pages in one layer and four printed pages in the other layer or two printed pages in one layer and six printed pages usable in the other situation. In the case of a web width corresponding to three standing printed pages, it can be used for the production of a two-layer product in broadsheet format with four printed pages in one layer and two printed pages in the other layer.

In the case of printed pages in tabloid format is the double printing unit for the production in a grading of four lying on the forme cylinder 02; 11 arranged printed pages changeable products ("four-page jump") in tabloid format usable.
Accordingly, the double printing unit 13 is at a four or three or two lying printing pages or a lying printing side corresponding web width for the production of one of a layer in the above order with sixteen or twelve or eight or four printed pages existing product in tabloid format usable.

The double-printing unit is in a tabloid four-width printed pages corresponding web width for the production of two single-layer tabloid products with eight printed pages in one product and eight printed pages in the other product or four printed pages in the one product and twelve Print pages in the other product usable. For a web width corresponding to three horizontal pages, it can be used to make two single-ply tabloid products with four printed pages in one product and eight printed pages in the other.

For products in book format is the double printing unit 13 for the production in a grading of eight standing on the forme cylinder 02; 11 arranged print pages changeable ("eight-page jump") products usable.

With the double printing unit 13, it is possible to produce a book-sized product consisting of one layer in the preceding sequence with thirty-two or twenty-four or sixteen or eight printed pages in the case of eight or six or four or two stationary printed pages.

For a booklet sized 8-page printed pages, the double-printing unit 13 is for the production of two single-book book format products with sixteen printed pages in one product and sixteen printed pages in the other or twenty-four printed pages in the one product and eight Print pages in the other product usable. In a six standing printed pages in book format corresponding web width, it is for the production of two each consisting of one sheet of book-sized products in the one with sixteen pages Product and eight printed pages in the other product suitable.

Next, the double printing unit 13 for products in book format for the production in a gradation of eight lying on the forme cylinder 03 arranged printed pages changeable products ("eight-page jump") used (double transverse fold).

In a four or three or two lying printing pages or a lying printed page in book format corresponding web width is the double printing unit 13 for the production of one of a layer in the above order with thirty-two or twenty four or sixteen or eight printed pages existing product in Book format usable.

The double printing unit is four web pages in book format corresponding web width for the manufacture of two single-ply book sized booklets with sixteen printed pages in one product and sixteen printed pages in the other product or twenty four pages printed in one product and eight printed pages usable in the other product. For a three-page printed pages in book-sized web width, it is useful for making two one-ply book sized products with sixteen printed pages in one product and eight printed pages in the other product.

If the two partial web strands are folded longitudinally on different hoppers and then guided into a common folding apparatus, the above-mentioned for the distribution of the product to different, combined folders or layers with the described variable page number is applied.

LIST OF REFERENCE NUMBERS

01

printing unit

02

Cylinder, forme cylinder

03

Cylinder, transfer cylinder

04

Interruption, channel, slot

05

-

06

Interruption, channel, slot

07

Cylinder, transfer cylinder, impression cylinder, satellite cylinder

08

Web, substrate web

09

bruise

10

-

11

Cylinder, forme cylinder

12

printing unit

13

Printing unit, double printing unit

14

-

15

-

16

Travel, linear

17

Stellweg, curved

18

lever

19

Printing unit, H printing unit

20

-

21

Inking unit, anilox inking unit, roller inking unit

22

dampening

23

spigot

24

Bearing housing, slide

25

-

26

linear guide

27

side frame

28

Insert, bell

29

cavity

30

-

31

cover

32

Drive, linear, screw drive

33

supporting wall

34

Bearing, linear bearing, roller bearing cage

35

-

36

carrier

37

paddock

38

Lever, three-armed

39

Actuator, cylinder

40

-

41

attack

42

Spring package, plate spring package

43

Pivot, shaft, synchronous shaft

44

Drive means, pressure cylinder

45

-

46

Adjusting means, coupling, toggle mechanism

47

Shaft, synchronous shaft

48

attack

49

drilling

50

-

51

Pin (02; 11)

52

Eccentric bearing, bearing bush, eccentric

53

actuating means

54

Bearings, Rolling Bearings

55

-

56

camp

57

Eccentric bearing, bearing bush, eccentric

58

recess

59

pinion

60

-

61

drive wheel

e

level

D

level

V

connecting plane

E18

level

G1

Just

G2

Just

H

horizontal

M

drive motor

S

swivel axis

S23

swivel axis

S51

swivel axis

FROM

Print-off position

AT

Print-on position

a

longitudinal section

D02

diameter

D03

diameter

L02

Length (02)

L03

Length (03)

R02

axis of rotation

R03

axis of rotation

R07

axis of rotation

R11

axis of rotation

5a

axis of rotation

I

page

II

page

α

Angle (E, 08)

β

Angle, dull (E, 08)

γ

Angle (16, 08

δ

Angle (E, 16)

φ

Angle (D, 16)

η

Angle (E18, G1)

λ

angle

ε-S

angle

ε-S23

angle

ε-S51

angle

Claims (24)

1. Printing unit for a press, which has a pair of cylinders (02; 03; 07; 11) comprising a forme cylinder and a transfer cylinder (02; 03; 07; 11), the two cylinders (02; 03; 07; 11) each having a circumference which corresponds substantially to a cut length of a newspaper page, and two cylinder pairs being arranged so as to form a printing point between the cylinders (03; 07) which are configured as transfer cylinders (03; 07), characterized in that at least one of the forme cylinders (02; 11), as viewed in the circumferential direction, has at most one channel (04; 06) on its effective circumferential surface but, as viewed in the longitudinal direction, a plurality of channels (04; 06) arranged beside one another on its effective circumferential surface which, as viewed in the circumferential direction, are arranged offset from one another and in that the rotational axes (R02; R03; R07; R11) of the cylinders (02; 03; 07; 11) of the two cylinder pairs lie in a common plane (E) in a thrown-on position (AN) of the cylinders (02; 03; 07; 11), and in that both interacting cylinders (02; 03; 07, 11) have in each case at least two channels (04; 06) on the effective circumferential surface, which channels (04; 06) are arranged next to one another in the longitudinal direction of the respective cylinder but offset with respect to one another in the circumferential direction, and in that the channels (04; 06) are configured for receiving at least one cover.
2. Printing unit for a press, which has a pair of cylinders (02; 03; 07; 11) comprising a forme cylinder and a transfer cylinder (02; 03; 07; 11), the two cylinders (02; 03; 07; 11) each having a circumference which corresponds substantially to a cut length of a newspaper page, characterized in that at least the forme cylinder (02; 11) has, as viewed in the circumferential direction, at most one channel (04; 06) on its effective circumferential surface but, as viewed in the longitudinal direction, a plurality of channels (04; 06) which are arranged next to one another on its effective circumferential surface, which channels (04; 06) are arranged offset with respect to one another as viewed in the circumferential direction, in that the cylinder (03; 07) which is configured as a transfer cylinder (03; 07) has, as viewed in the circumferential direction, at most one cover but, as viewed in the longitudinal direction, a plurality of covers which are arranged next to one another and are arranged offset with respect to one another on the cylinder (02; 03; 07; 11) as viewed in the circumferential direction, and in that the cover is configured on the transfer cylinder (03; 07) as a printing blanket which has a metal support, and in that both interacting cylinders (02; 03; 07, 11) have in each case at least two channels (04; 06) on the effective circumferential surface, which channels (04; 06) are arranged next to one another in the longitudinal direction of the respective cylinder but offset with respect to one another in the circumferential direction, and in that the channels (04; 06) are configured for receiving at least one cover.
3. Printing unit according to Claim 1 or 2, characterized in that the transfer cylinder (03; 07), as viewed in the circumferential direction, has at most one channel (04; 06) on its effective circumferential surface but, as viewed in the longitudinal direction, has a plurality of channels (04; 06) arranged beside one another on its effective circumferential surface which, as viewed in the circumferential direction, are arranged offset from one another.
4. Printing unit according to Claim 1 or 2, characterized in that both cylinders (03; 07) of the pair of cylinders, as viewed in the circumferential direction, have at most one channel (04; 06) on their effective circumferential surface but, as viewed in the longitudinal direction, have a plurality of channels (04; 06) arranged beside one another on their effective circumferential surface which, as viewed in the circumferential direction, are arranged offset from one another.
5. Printing unit according to Claim 2, characterized in that the printing unit, in addition to forme and transfer cylinders, has an impression cylinder (02; 03; 07; 11), in that their axes of rotation (R02; R03; R07; R11) lie in a common plane (E) in a print-on position (AN) of the three cylinders (02; 03; 07; 11), in that at least the forme cylinder and the transfer cylinder (02; 03; 07; 11) in each case have at least two channels (04; 06) on the effective circumferential surface which, in the longitudinal direction of the respective cylinder (02; 03; 07; 11), are arranged beside one another but, in the circumferential direction, are arranged offset from one another, and in that the interruptions (04; 06) of the two cylinders (02; 03; 07; 11) are arranged to roll alternately on one another.
6. Printing unit according to Claim 1, 2 or 5, characterized in that the cylinders (02; 03; 07; 11) have a diameter (D02; D03) of 130 to 200 mm, in particular 145 to 185 mm.
7. Printing unit according to Claim 1, 2 or 5, characterized in that the channel interruption is designed as a gap having a width less than or equal to 3 mm in the region of a circumferential surface.
8. Printing unit according to Claim 1, 2 or 5, characterized in that the cylinders (02; 03; 07; 11) in each case have a circumference for a single upright newspaper page in broadsheet format.
9. Printing unit according to Claim 1, 2 or 5, characterized in that, in the region of its barrel, in the longitudinal direction the cylinder (02; 03; 07; 11) has a length (L02; L03) which corresponds substantially to four widths of a printed page, in particular of a newspaper page.
10. Printing unit according to Claim 1, characterized in that the cylinder (02; 03; 07; 11), as viewed in the circumferential direction, has at most one cover and, as viewed in the longitudinal direction, has a plurality of covers arranged beside one another, which are arranged on the cylinder (02; 03; 07; 11) offset from one another, as viewed in the circumferential direction.
11. Printing unit according to Claim 1, 2 or 5, characterized in that both interacting cylinders (02; 03; 07; 11) have a plurality of covers arranged beside one another in the longitudinal direction but offset from one another in the circumferential direction.
12. Printing unit according to Claim 1, characterized in that the channels (04; 06) on the effective circumferential surface of the two cylinders (02; 03; 07; 11) of the pair of cylinders are arranged to roll alternately on one another.
13. Printing unit according to Claim 2, characterized in that two pairs of cylinders are arranged between the cylinders (03; 07) constructed as transfer cylinders (03; 07), forming a printing point.
14. Printing unit according to Claim 13, characterized in that the channels (04; 06) on the effective circumferential surface of the two transfer cylinders (03; 07) are arranged to roll alternately on one another.
15. Printing unit according to Claim 13, characterized in that the axes of rotation (R02; R03; R07; R11) of the cylinders (02; 03; 07; 11) of the two pairs of cylinders lie in a common plane (E) in a print-on position (AN) of the cylinders (02; 03; 07; 11).
16. Printing unit according to Claim 5, characterized in that at least one of the cylinders (02; 03; 07; 11) can be set against at least one of the associated cylinders (02; 03; 07; 11) or set off the latter along an actuating path (16; 17).
17. Printing unit according to Claim 16, characterized in that the actuating path (16) is formed linearly by means of a linear guide (26).
18. Printing unit according to Claim 16, characterized in that the actuating path (16) is formed linearly, at least in the region of the printing point (09), by means of a double eccentric.
19. Printing unit according to Claim 16 or 17, characterized in that the linear actuating path (16) runs approximately at right angles to the plane (E) of the axes of rotation (R02; R03; R07; R11).
20. Printing unit according to Claim 16, characterized in that the actuating path (17) is formed curvilinearly by means of a lever (18).
21. Printing unit according to Claim 1, 2 or 5, characterized in that the printing unit (13) is formed as a rubber-against-rubber printing unit, and the cylinders (02; 03; 07; 11) are formed as two transfer cylinders (03; 07) forming a printing point (09) and two forme cylinders (02; 11) in each case interacting with one of the transfer cylinders (03; 07).
22. Printing unit according to Claim 6 or 15, characterized in that the plane (E) of the axes of rotation (R02; R03; R07; R11) of the cylinders (02; 03; 07; 11) runs inclined at an angle (α) of 75° to 85° with respect to the plane of a web (08) passing through the printing unit.
23. Printing unit according to Claim 1 or 2, characterized in that an opening of the channels (04; 06) in the region of the circumferential surface of the cylinder (02; 03; 07; 11) does not exceed a width of 3 mm in the circumferential direction.
24. Printing unit according to Claim 10, characterized in that the cover on the transfer cylinder (03; 07) is designed as a printing blanket having a metal underlay.

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