EP1412188B2 - Mounting for cylinders of a printing machine - Google Patents

Abstract

At least two cylinders of a printing machine are arranged in the printing machine. An end journal of each of the cylinders is mounted either in or on a common insert. That common insert is, in turn, detachably located in, or on a lateral frame of the printing machine.

Description

The invention relates to a bearing of cylinders of a printing machine according to the preamble of claim 1.

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 Doppelezzenterbüchsen or levers in a side frame.

The US Pat. No. 102,8485 discloses an assembly of cylinders of a printing press, with picks of two cylinders stored in a common insert.

The invention has for its object to provide a storage of cylinders of a printing machine according to the preamble of claim 1.

The object is achieved by the features of claim 1.

The achievable with the present invention consist in particular that is simplified by an insert for the storage of at least two cylinders in the side frame for a production and a modularization is possible. On the other hand, this design contributes significantly to a compact, low-vibration and robust construction of a printing unit.

The insert reduces the local clearance between the bearing points, i. This results in small storage distances in the critical area of the printing unit (printing cylinder), whereas in the surrounding area sufficient space (inking, dampening, paper guide ...) remains. There is no restriction in length in the length of the (drive) pins of the cylinder.

The insert has a high rigidity, since it z. B. has an at least largely closed profile with high edges; there is no displacement of the bearing points due to the so-called "frame softness"

A simple and quick installation is done for example by inserting the cylinder from one side between the frame walls, since the length of the cylinder including pin can be selected smaller than the inside width. However, the opening in the side frame of the insert can also be designed in the size that can be passed after removal of or before loading with the use of the cylinder.

In mechanical drive connection of two or more of the cylinder, this can be accommodated in a cavity of the insert and encapsulated when needed in a simple manner.

If, for example, four impression cylinders of a double printing unit are mounted in a common insert (in particular, for example, in a line), then the bending moments in use are compensated for and the side frame ideally only experiences weight forces.

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.

It is advantageous z. B. an embodiment of the printing unit with the arrangement of the cylinder in a plane, with offset, but mutually rolling on each other channels, and designed as metal blankets lifts on the transfer cylinders.

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 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 linearen Doppeldruckwerks mit kurvenförmigem Stellweg;

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 Ausschnitt eines paarweisen Antriebes am Übertragungszylinder;

Fig. 17

eine schematische Vorderansicht gemäß Fig. 10;

Fig. 18

eine schematische Vorderansicht eines Doppeldruckwerkes mit Zylindern verschiedenen Umfangs;

Fig. 19

eine Belegung des Formzylinders mit vier Zeitungsseiten;

Fig. 20

eine Belegung des Formzylinders mit acht Tabloidseiten;

Fig. 21

eine Belegung des Formzylinders mit sechzehn stehenden Seiten im Buchformat;

Fig. 22

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 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 linear double printing with curved travel;

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 a pairwise drive on the transfer cylinder;

Fig. 17

a schematic front view according to Fig. 10 ;

Fig. 18

a schematic front view of a double printing with cylinders of different circumference;

Fig. 19

an assignment of the forme cylinder with four newspaper pages;

Fig. 20

an assignment of the forme cylinder with eight tabloid pages;

Fig. 21

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

Fig. 22

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. This interruption 04; 06 may be a shock of a leading and a trailing end of one or more elevators, which are arranged for example by means of magnetic force or cohesively on the circumference. However, it may also, as shown below in the embodiments, to channels 04; 06 or slots 04; Act 06, which absorb the ends of elevators. The following as channels 04; 06 designated interference are synonymous with other interruptions 04; 06 on the effective lateral surface, d. H. the outwardly facing surface of the lift cylinder 02; 03.

The forme cylinder 02 and transfer cylinder 03 each have at least two channels 04; 06 (or interruptions 04, 06, etc.) 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; Roll out 02. 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 03 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 can be used as a second transfer cylinder 07 ( Fig. 1 ) or as an impression cylinder 07 ( Fig. 2 ), z. As steel cylinder, or satellite cylinder 07 be 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. 12 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, 12th ). 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 running 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. 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 one in an advantageous embodiment Length L02; 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 "single circumference" ( Fig. 3 and 4 ) called. 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 ).

Are the interruptions 04; 06 actually as channels 04; 06 or slots 04; 06 executed, so in Fig. 1 to 4 schematically illustrated channels 04; 06 be 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 shown in the only schematically 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 simultaneously 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.

Are the interruptions 04; 06 actually as channels 04; Run 06, they 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 cylinders 02; 11 by clamping devices in the channels 04; 06 held.

In each of the channels 06 of the transfer cylinder 03 may be a single, continuous clamping and / or clamping device or it may - in the case of over several newspaper page widths continuous channels - in the longitudinal direction one behind several clamping and / or clamping devices may 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 page. In this case, the elevators or channels 04 run the Forme cylinder 02; 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 actually 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 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. In this case, it may be advantageous, the transfer cylinder 03; 07 and / or the forme cylinder 02; 11 with a diameter D02; D03, which results in a scope that corresponds to substantially twice the length 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 and 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 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 stopping 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 , and 7 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 and the plane of the web 08 intersect 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 °; have the transfer cylinder 03; 07, however, has a circumference which is approximately the length of two newspaper pages corresponds, then the angle α z. B. 80 to 85 °, preferably about 83 °. 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 running web 08.dann 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, 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; 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. It can, if a "co-moving" of the drive motor 14 or a flexible coupling between the drive motor 14 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 housings 24 or slides 24 are movable in linear guides 26, which are connected to a side frame 20.

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 on walls of the side frame 20, in particular on walls of openings in the side frame 20, which almost perpendicular to the end face of the cylinder 02; 03; 07; 11 run.

The side frame 20 has ( Fig. 8 and 9 ) 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. The described use of the bell 28 is intended neither on the described embodiments of the printing units, nor on the special variants for the movement of the cylinder 03; 07 or limited to the special drive composites. The bell 28 may also in connection with an adjustable via eccentric or lever cylinder 03; 07 be applied, in which case z. B. an eccentric bearing or a lever can be mounted on or in use. However, a lever may also be mounted outside the insert, but the drive mechanism (clutches and / or drive connection to the engine or to the other cylinder 02, 11) may be arranged in the bell 28 and the bearing of the cylinder 03; 07 in the lever z. B. takes place in the area of the bell 28.

In accordance with the invention, the bell 28 has an area which, in the direction of the cylinder 02; 03; 07; 11 emerges from the alignment of the side frame 20. 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. Advantageous in 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 Holraum 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 hinge 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 formzylindemahe part of the guide (in Fig. 9 larger dimension) on a tensioning device, not shown.

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. 10 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 articulated with the here designed as a three-armed lever 38 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 ) with pressure medium actuatable cylinder 39. Upon actuation of the actuator 39 and pivoting of the lever 38 in one direction (in this case in the clockwise direction), the two transfer cylinders 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 Übertragungsüngszylinders 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 ). Again, at least two cylinders 02; 03; 07; 11 be stored in an insert 28, not shown. Also the drive mimic, z. B. a mechanical coupling between the rotary drives of the cylinder 02; 03; 07; 11 and possibly existing couplings can again be arranged as described above in a cavity 29 and optionally encapsulated.

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 °; have the transfer cylinder 03; 07 but a circumference, which corresponds approximately to the length of two newspaper pages, so the angle α z. B. 80 to 85 °, preferably about 83 °. 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 shown 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. sprockets, 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 eS 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 eS is in Anstelllage the transfer cylinder 03; 07, ie the axes of rotation R03; R07 are in the above-mentioned plane D, oriented so 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. In the case of vertical, and with the exception of an offset possibly caused by partial looping, a straight web run and an angle 77 ° between the plane D and the plane of the web 08, have the eccentric eS 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

• Die Rotationsachse R02; R11 des Formzylinders 02; 11 ist justierbar, z. B. ebenfalls exzentrisch zu seiner Befestigung am Seitengestell 20, hier zu einer Bohrung 49, gelagert. Im vorliegenden Fall ist ein Zapfen 51 des Formzylinders 02; 11 in einem Exzenterlager 52 bzw. einer exzentrischen Lagerbuchse 52 angeordnet, welches in der Bohrung 49 verschwenkbar gelagert ist.

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 S51 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. In particular, by the respect 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 °.

The pins 51 of the forme cylinder 02; 11 are each in camps, z. B. bearings, rotatably mounted. In order to make an adjustment or a correction of the side register, allows in an advantageous embodiment of this camp or an additional thrust bearing, the movement of the forme cylinder 02; 11 and its pin 51 in the axial direction. The bearings 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. It can be arranged between bore 49 and pin 51 in addition to the eccentric bushing 52 and the bearing even more bearing rings and sliding or roller bearings. The lever 18 is on a forme cylinder 02; 11 out of the side frame projecting part of the bearing bush 52, and mounted pivotally 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 rotatable in a bearing, and this in the case of the transfer cylinder 07, about the pivot axis S-23 is pivotally mounted in an eccentric bearing or in an eccentric bearing bush. If necessary, such a pivotable bearing bush can also be used for both transfer cylinders 03; 07 be arranged.

Advantageously, at least on a drive side of the printing press, the side frame recesses, in which the pin 23 of the transfer cylinder 03; 07 are pivotable.

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, which are preferably arranged fixed to the frame. The latter has the advantage that the drive motors do not have to be moved.

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

Also, the drive of the forme cylinder 02; 11 has between pin 51 and drive motor, the at least one axial relative movement between the cylinder 02; 11 and drive motor receiving coupling 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 carried out in an advantageous embodiment as an all-metal coupling, which receives the axial movement through the form-fitting in the axial direction with the pin 51 and a shaft of the drive motor disk packs.

In an in FIGS. 16 and 17 illustrated variant, a pairwise drive from the drive motor (possibly via other transmission parts not shown) by a pinion 59 on a drive wheel 60 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 such that a straight line G1 defined by the rotation axis R59 of the pinion 59 and the pivot axis S of the lever 18 coincides with one of the pivot axis S of the lever 18 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 with the set 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 °.

The aforementioned embodiments for driving and for moving the transfer cylinder 03; 07 and the design of the lever 18 and the linear guide 26 are equally applicable to printing units, in which the cylinder 02; 03; 07; 11 do not all have the same circumference or diameter ( Fig. 18 ). Thus, in particular, the or the forme cylinder 02; 11 have a circumference U, which in the circumferential direction a pressure side, z. B. the long side of a newspaper page, has (hereinafter "single circumference"). The cooperating transfer cylinder 03; 07 has z. B. a circumference or diameter, which an integer multiple (greater than 1) that of the forme cylinder 02; 11 corresponds, ie he has z. B. a scope of two or even three printed pages in the newspaper format (or adapted to other formats accordingly) on.

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. The ratio of diameter to length of about 0.08 to 0.16 have to build and operate robust and low vibration, 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 16 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 by way of example to arrange the angular and offset compensating coupling 61. As in Fig. 9 and 11 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 - at least the forme cylinder 02; 11 - single-circumference allows significantly higher product variability, unlike 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 sub-webs can be superimposed, while others can be run on a second one Funnel and / or folder are performed. 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 appropriate execution of the turning end (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. 19 ). 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. 20 ) or in the circumferential direction with two and in the longitudinal direction with at least eight stationary printed pages in book format ( Fig. 21 ) or in the circumferential direction with four and in the longitudinal direction with at least four lying printed pages in book format ( Fig. 22 ) by means of in the circumferential direction of the forme cylinder 02 each one and its longitudinal direction at least one can be fitted on this, flexible pressure plate.

• So ist mit dem Doppeldruckwerk 13 die Herstellung in einer Stufung von zwei stehenden auf den Formzylinder angeordneten Druckseiten ("Zweiseitensprung") veränderbaren Produkten im Broadsheetformat möglich.

By means of the double-width printing machine and at least the forme cylinders 02; 11 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 13 is corresponding to a four-lying printed pages in tabloid format Web width for making two single-ply products in tabloid format with eight printed pages in one product and eight printed pages in the other product or four printed pages in one product and twelve printed pages in the other product. 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 a layer in the preceding sequence with thirty-two or twenty-four, sixteen or eight printed pages, with a web width corresponding to eight, six, 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. For a six-page printed page in book-sized web width, it is useful for making two single-book book sized products with sixteen printed pages in one product and eight printed pages in the other product.

Next, the double printing unit 13 for products in book format for the production in a gradation of eight lying on the forme cylinder 02 arranged printed pages modifiable 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 13 is at a four-page printed pages in book format corresponding web width for the production of two single-layer products in book format with sixteen printed pages in one product and sixteen printed pages in the other product or twenty-four printed pages in the product and eight Print pages in the other product usable. 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

drive motor

15

-

16

Travel, linear

17

Stellweg, curved

18

lever

19

Printing unit, H printing unit

20

side frame

21

Inking unit, anilox inking unit, roller inking unit

22

dampening

23

spigot

24

Bearing housing, slide

25

-

26

linear guide

27

Radial bearings, roller bearings

28

Insert, bell

29

cavity

30

drive wheel

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

-

55

-

56

-

57

-

59

pinion

60

drive wheel

61

Clutch, double-jointed coupling, all-metal coupling

62

Clutch, all-metal coupling

63

Gearbox, auxiliary gear, planetary gear, reduction gear

e

level

D

level

V

connecting plane

U

scope

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

H

height

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

R59

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 (18)

1. Arrangement of cylinders of a printing press comprising at least two cylinders (02; 03; 07; 11), in each case an end journal (23; 51) of at least the two cylinders (02; 03; 07; 11) being mounted in or on a common insert (28) which in turn is arranged detachably in or on a side frame (20), characterized in that the insert (28) has a region which goes out of alignment with the side frame (20) in the direction of the cylinder (02; 03; 07; 11) and in that the journals (23; 51) are mounted in the region of this part of the insert (28), which part is outside the alignment.
2. Arrangement according to Claim 1, characterized in that the two cylinders (02; 03; 07; 11) are in the form of a pair comprising a forme cylinder (02; 11) and a transfer cylinder (03; 07) of a printing couple (01; 12).
3. Arrangement according to Claim 2, characterized in that the transfer cylinder (03; 07) can alternatively be brought into a thrown-on position and a thrown-off position (AN, AB).
4. Arrangement according to Claim 2, characterized in that the two cylinders (02; 03; 07; 11) can be rotationally driven by means of at least one drive motor (14), mechanically independently of another printing couple (01; 12).
5. Arrangement according to Claim 1, characterized in that a drive connection between the at least two cylinders (02; 03; 07; 11) is arranged in a cavity (29) of the insert (28).
6. Arrangement according to Claim 1, characterized in that in each case an end journal (23; 51) of four cylinders (02; 03; 07; 11) forming a blanket-to-blanket printing unit (13) is mounted in or on the common insert (28).
7. Arrangement according to Claim 1 or 6, characterized in that the journals (23; 51) are arranged in a cavity (29) of the insert (28), which can be encapsulated as a closed lubricant space.
8. Arrangement according to Claim 5, characterized in that in each case a drive connection between cylinders (02; 03; 07; 11) in the form of transfer cylinder and coordinated forme cylinder (02; 03; 07; 11) is arranged in pairs in a common cavity (29) of the insert (28), but the two pairs are formed without a mechanical drive connection to one another and can be driven in pairs in each case mechanically independently of one another by a separate drive motor (14).
9. Arrangement according to Claim 1, characterized in that the drive motor (14) is arranged so as to be fixed to the frame.
10. Arrangement according to Claim 1, characterized in that the transfer cylinder (03; 07) of the pair cooperates with a satellite cylinder (07) of a nine-cylinder printing unit having altogether four pairs.
11. Arrangement according to Claim 1, characterized in that the transfer cylinder (03; 07) of the pair cooperates with a satellite cylinder (07) of a ten-cylinder printing unit having altogether four pairs and two satellite cylinders (07).
12. Arrangement according to Claim 10 or 11, characterized in that at least one of the transfer cylinders (03; 07) and of the coordinated satellite cylinders (07) are mounted in or on a common insert (28).
13. Arrangement according to Claim 10 or 11, characterized in that at least one satellite cylinder (07) and two coordinated pairs are mounted in or on a common insert (28).
14. Arrangement according to Claim 1, characterized in that the two cylinders (02; 03; 07; 11) are part of a blanket-to-blanket printing unit (13).
15. Arrangement according to Claim 1, characterized in that the two cylinders (02; 03; 07; 11) are driven mechanically independently of one another by in each case one drive motor (14).
16. Arrangement according to Claim 10 or 11, characterized in that the satellite cylinder (07) has a drive motor (14) mechanically independent of the pair.
17. Arrangement according to Claim 1, characterized in that the transfer cylinder (03; 07) is moveable along a linear adjustment path (16).
18. Arrangement according to Claim 1, characterized in that the transfer cylinder (03; 07) is moveable along a curved adjustment path (17).

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