EP1372963B1 - Drive mechanism of a cylinder - Google Patents

Abstract

A drive mechanism of a cylinder of a printing machine uses a drive motor. The cylinder and the drive motor can be moved relative to one another in an axial direction. A coupling, whose length can be varied in a linear direction by a given amount, and which has a lamella packet connected to flanges in a positive locking manner, is arranged between the drive motor and the cylinder.

Description

The invention relates to a drive of a forme cylinder according to the preamble of claim 1.

By the DE 44 30 693 A1 is a printing unit known, wherein the form cylinder is driven and driven off via spur gears on the transfer cylinder. A designed as a rotor pin of the forme cylinder is in the embodiment axially displaceable in the stator for the purpose of adjusting the side register on the forme cylinder in one embodiment. Shaping and transfer cylinders are driven in pairs in one embodiment.

The EP 07 22 831 B1 also discloses a drive for a cylinder, wherein the driven by a motor cylinder for the purpose of adjusting the side register is arranged axially displaceable. A coaxially arranged on the pin of the cylinder rotor is axially movable in the stator.

In the DE 196 03 663 A1 is a form cylinder via a gearbox axially and via a helical gear in the circumferential direction relative to the transfer cylinder adjustable. The forme cylinder and the transfer cylinder acting together with it are drivable in parallel by means of a motor. By means of a spigot of the forme cylinder arranged spur gear is drivable on a forme cylinder associated inking unit.

The EP 1 000 737 A1 discloses a drive of a cylinder sleeve via a shaft which is axially clamped against a disc. Between the drive motor and sleeve an axial relative movement enabling axial coupling is provided.

In the " Taschenbuch für die Maschinenbau ", Dubbel, 15th edition, are on pages 407 to 411 Among other things, various designs for torsionally rigid compensating couplings disclosed.

The DE 197 55 316 C2 discloses the drive of a cylinder from a drive motor via a transmission and via a "balancing clutch". Other cylinders are driven by their own drive motors. The drive motors are offset relative to each other in relation to the respective cylinder.

From the DE 25 53 768 B2 is a drive network between a driven via a gear cylinder and a transfer cylinder known, wherein for the purpose of an optional release of the drive network, a releasable coupling between the cylinders is arranged.

The DE 38 25 307 C1 shows a drive train from a main motor via a helical gear, via a first, axially fixed shaft piece, via a second, axially movable shaft piece, via a third, axially fixed shaft piece on a bevel gear, and from there to a plate cylinder. In order to influence a circumferential register with varying torsional stress, the axially movable by a drive shaft piece between two eccentrically articulated and elastically deformable spring elements is arranged such that upon axial displacement of the shaft piece torsion occurs.

The invention has for its object to provide a drive of an axially movable forme cylinder with circumferentially minimized game.

The object is achieved by the features of claim 1.

The achievable with the present invention consist in particular in that a drive of axially movable form cylinders is created, with a game in the circumferential direction and a high production cost is minimized.

To an axial relative movement between the Form cylinder, and to enable the form cylinder driving drive motor, a flexible coupling in the axial direction between the drive motor and form cylinder is arranged. It is in an advantageous embodiment as torsionally stiff but flexible in the axial direction or flexible shaft coupling, z. B. as an expansion or compensating coupling executed. Particularly advantageous is the use of a non-switchable form-locking multi-plate clutch, which is virtually no play in the circumferential direction, in contrast to other positive clutches without major manufacturing effort, and at the same time an axial change in length of the clutch itself, ie an axial movement of the forme cylinder allows. The coupling is positively in the axial direction, but flexible in their length or yielding, z. B. by elastic and reversible deformation, executed.

The drive via the coupling is particularly in the case of individual drives on the individually driven cylinders, but in particular on the forme cylinder for the sake of adjustability of the side register, an advantage. If the cylinders of a printing unit are driven individually by a respective drive motor, the circumferential register can be changed by means of changes in the relative angular position of the drive motor, and the side register can be changed relative to one another by means of the axial displacement. In an advantageous embodiment, the drive motors are arranged coaxially with the cylinder to be driven.

In the case of groups, especially in pairs driven cylinders, the arrangement of the drive motor via the coupling on the forme cylinder of a jointly driven cylinder pair is advantageous. By the drive on the forme cylinder no movement of the drive motor must take place when pressure on and off position of the transfer cylinder, as z. T. in the drive directly on the transfer cylinder is the case Also based on such pivotal movements of the transfer cylinder compromise in the position of the drive motor and the engagement of the gears in the arrangement of the drive motor on the transfer cylinder can be omitted when driving the forme cylinder. The latter can lead to tooth breakage in the other case or due to the play in the drive to reduce the print quality.

If only the inking unit and the transfer cylinder are turned on or off, a rigid coupling of the drive motor to a side frame can take place. In general, however, it is advantageous, also with regard to print quality, to improve the concentricity properties by arranging a gear, in particular a reduction gear.

In one embodiment, the drive motor can be arranged directly axially to the forme cylinder or to the driven cylinder. In order to adjust the page register one To allow axial movement of the forme cylinder, which is flexible in the axial direction coupling between pin and drive motor can be arranged. Advantageous in terms of favorable speed ranges, especially in the start-up phase, the design of the drive motor with a arranged between the rotor and the pin of the cylinder gear, z. B. a planetary gear.

In cases where the strength requires a helical toothing for power transmission, an arrangement is advantageous, wherein the pinion of the drive motor does not drive directly on the spur gear of the forme cylinder. In the case of axial movement of the forme cylinder, a simultaneous adjustment of the circumferential register would take place without additional precautions. Precautions may be, for example, a simultaneous correction over the control, which requires control engineering effort, or an allowable relative movement of the pin to the spur of the forme cylinder, but this requires guides, which are not or only with great effort in the circumferential direction to manufacture play. For axial mobility of the forme cylinder, a flexible coupling in the axial direction can again be used.

For the mentioned embodiments of the drive of the forme cylinder, it is advantageous if an inking unit associated with the forme cylinder and, if present, also a dampening unit, is driven by the same drive motor. This saves costs and, with the correct gear ratios, ensures synchronization.

In the case of a common drive during production, it is particularly favorable for an exact unwinding of the cylinders and rollers that an unambiguous direction of torque flow from the drive motor to the various units to be driven is achieved. This is achieved in an advantageous embodiment that is driven by the forme cylinder on the transfer cylinder, and from the transfer cylinder to the inking unit, ie, serially. In this case, an embodiment is particularly economical, in which from the transfer cylinder via a rotatably mounted on the journal of the forme cylinder Gear is driven to the inking unit.

If the inking unit and the transfer cylinder are driven in parallel via the forme cylinder, at least one of the two drive lines requires the use of accessories in the case of gear trains or the use of belt drives that are as free of play as possible.

The measures for the formation of a torsionally stiff but axially changeable in their length coupling and the unique torque flow direction of minimizing the game in the drive and thereby improving the print quality.

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

Fig. 1

ein erstes Ausführungsbeispiel für den Antrieb eines Zylinders;

Fig. 2

ein Beispiel für eine in axiale Richtung flexible Kupplung;

Fig. 3

ein zweites Ausführungsbeispiel für den Antrieb eines Zylinders mit einem zweiten Zylinder und einem Farbwerk;

Fig. 4

ein drittes Ausführungsbeispiel für den Antrieb eines Zylinders mit einem zweiten Zylinder und einem Farbwerk;

Fig. 5

ein viertes Ausführungsbeispiel für den Antrieb eines Zylinders mit einem zweiten Zylinder und einem Farbwerk.

Show it:

Fig. 1

a first embodiment for the drive of a cylinder;

Fig. 2

an example of an axially flexible coupling;

Fig. 3

a second embodiment for driving a cylinder with a second cylinder and an inking unit;

Fig. 4

a third embodiment for driving a cylinder with a second cylinder and an inking unit;

Fig. 5

A fourth embodiment for the drive of a cylinder with a second cylinder and an inking unit.

A first cylinder 01, z. As a forme cylinder 01, a printing machine, in particular a rotary printing press, has on a front side in a side frame, not shown, rotatably mounted pin 04. The pin 04 is the front side via a coupling 06 with a drive motor 07 in operative connection.

In a first embodiment ( Fig. 1 ) is the coupling 06, as a clutch 06, in particular as a non-switchable positive shaft coupling 06 or expansion coupling 06, executed, which is connected on its side facing away from the cylinder 01 coaxially via a shaft 08 with a shaft 09 of the drive motor 07. In an advantageous embodiment, between the drive motor 07 and clutch 06, a transmission 10, in particular a reduction gear 10, such. As a planetary gear 10, arranged. This connection between the shaft 08 and the shaft 09 may also have a non-shiftable coupling 11, z. B. via a dog clutch 11, take place. The clutch 11 may, if deviations in the axial direction of the cylinder 01 and the drive motor 07 are to be compensated, also be designed as a curved tooth coupling.

The non-switchable coupling 06 is designed such that a length L in the axial direction is variable by an amount of .DELTA.L, preferably in both directions. In contrast to jaw clutches or couplings, which have bores engaging pins or bolts, the coupling 06 is formed such that it has no sliding movement in the axial direction of two circumferentially cooperating stop members relative to each other, but torsionally rigid in the circumferential direction and in the axial direction Direction yielding or reversible elastically deformable. The coupling 06 forming parts are positively connected with each other in the axial and circumferential direction and thus allow a large amount of manufacturing effort in the circumferential direction almost backlash drive and by changing the length L axial movement of the cylinder 01. Since no relative movement between two mutually as a stop transversely takes place to the direction of movement surfaces, the clutch 06 is wear and against Pollution insensitive.

An example of such a coupling 06, in Fig. 1 . 3 . 4 and 5 symbolically indicated only in Fig. 2 shown. The coupling 06 has in each case an annular flange 12 at the end face; 13, which in the circumferential direction adjacent axially extending through holes 14; 16; 17; 18 has. Between the two flanges 12; 13 is also a ring-shaped center piece 19 and flange 19 with holes 21; 22, and between each of the middle piece 19 and one of the flanges 12; 13 an annular plate pack 23; 24, in particular with lamellae of steel, with holes 26; 27 arranged. Each disk pack 23; 24 is now alternately in the circumferential direction by means of screws 28; 29 with the adjacent flange 12; 13 and the middle piece 19 so fastened that it alternately on the flange 12; 13 and the middle piece 19 is positively connected. In the area of screws 28; 29, the axial displacement permitting, spacers 30, z. B. washers 30, each between the prestressed disk set 23; 24 and the flange 12; 13; 19 arranged. The preferred blades of steel ensure in the circumferential direction, ie in the plane of their surface and perpendicular to the axis of rotation of the cylinder 01, a high rigidity, while the annular blades have low strength in the axial direction elastic or resilient properties.

Such a coupling 06 is also referred to as a bend-compliant all-metal coupling, as a diaphragm or ring clutch.

Due to this design, the coupling 06 is designed torsionally rigid and positive fit due to the rigidity of the slats in the circumferential direction. The alternating attachment of the plate packs 23; 24 on the flange 12; 13 and the middle piece 19 allows despite form fit in the axial direction due to the spring action of the slats in the disk set 23; 24 is a reversible change in the length L of the clutch 06 by an amount ΔL dependent on the dimensions of the clutch 06. The force to be expended, ie a spring stiffness in the coupling 06, in the axial direction depends on the Number of slats in the plate pack 23; 24. Preferably, a torsion spring value for the torsion in the clutch 06 is greater than 10,000 Nm / °, in particular in the range between 10,000 and 20,000 Nm / °.

If smaller amounts .DELTA.L are required and no axial offset is compensated, then the clutch 06 can also be used with only one disk pack 23; 24 and be executed without a central piece 19 or flange 19, in which case the disk set 23; 24 in the circumferential direction alternately on one and on the other flange 12; 13 is attached.

In the embodiment according to Fig. 1 is a cooperating with the cylinder 01 second cylinder 31, z. B. a transfer cylinder 31 or an impression cylinder 31, driven by a pin 32 of the cylinder 31 by means of its own drive motor 33. The operative connection between the drive motor 33 and the pin 32 can also via non-switchable couplings 06; 11 (not shown). In an advantageous embodiment, a transmission 10 between the drive motor 33 and cylinder 31 is also arranged here.

If the second cylinder 31 is designed, for example, as a transfer cylinder 31, then it acts during printing forming a pressure point with another cylinder, not shown, for example with another transfer cylinder, with a steel cylinder or with a satellite cylinder.

If the second cylinder 31 is formed as a counter-pressure cylinder 31, it forms a pressure point together with the forme cylinder 01.

In both cases, during printing u. U. a lateral displacement of the printed image relative to the printed image of another printing point or other forme cylinder required, so that designed as a forme cylinder 01 first cylinder 01 by the amount .DELTA.L must be moved axially. This amount ΔL is preferably between 0 and ± 4 mm, in particular between 0 and ± 2.5 mm and is absorbed by the change in the length L of the clutch 06 by this amount ± ΔL. The forme cylinder 01 remote from the end of the clutch 06, z. B. the flange 13, is arranged stationary with respect to an axial direction. With the arrangement of the clutch 06, the associated drive motor 07 can thus be arranged stationary or frame-fixed with axial displacement of the cylinder 01.

In a second embodiment ( Fig. 3 ), the drive by the drive motor 07 to the connected to the clutch 06 shaft 08 is not coaxial, but via a gear 35, in particular a reduction gear 35, z. B. by means of a pinion 34 on a shaft 08 arranged on the gear 36. Again, the arrangement of the coupling 11 between the drive motor 07 and the pinion 34 is advantageous for ease of separation. In addition, the drive motor 07 may be pre-set with a planetary gear 10 (not shown).

As in Fig. 3 shown, can from the first cylinder 01 via the clutch 06 via a gear 40, z. B. by means of a pin on the pin 04 of the first cylinder 01 rotatably mounted gear 37 on a on the pin 32 of the second cylinder 31 rotatably mounted gear 38 are driven off. Advantageously, due to the now occurring higher load a helical gear on the pinion 34 and the gear 36. The two co-operating gears 37; 38 on the pin 04; 32 are advantageously made straight toothed, as a relative axial movement is made possible to each other without a compensation in the circumferential register is required. The transmission 40 is located between the clutch 06 and the cylinders 01; 31. Thus, the drive takes place on the respective cylinder 01; 31 as close to the respective bale, which further improves the accuracy of the drive and the print quality.

In one variant, a non-illustrated, with the first cylinder 01 cooperating inking unit 39 and possibly a dampening unit 41 via the drive motor 07 is driven. In this case, a drive with a clear torque flow is advantageous.

For this purpose, via the gears 37; 38 driven off the first cylinder 01 to the second cylinder 31, and the second cylinder 31 via a gear 42, 43, 44 to the inking unit 39 and possibly dampening unit 41. In Fig. 3 is for this purpose on the pin 32 of the second cylinder 31, another gear 42 rotatably, and, cooperating with this, on the pin 04 of the first cylinder 01, a further gear 43 rotatably disposed relative to the pin 04. The latter meshes with a gear 44, which forms the drive for the inking unit 39 and possibly dampening unit 41. The drive train for the inking unit 39 and possibly dampening unit 41 forming gears 42; 43; 44 are straight teeth, so that an axial displacement of the first cylinder 01 does not lead to a relative change in the angular position between the first cylinder 01 and second cylinder 31 and first cylinder 01 and inking unit 39 and possibly dampening unit 41.

The drive of in Fig. 3 illustrated drive connection for the common and serial drive of the cylinder 01; 31 and the inking unit 39 or dampening unit 41 can also be correspondingly Fig. 1 take place by means of a shaft 08 and the cylinder 01 coaxially arranged drive motor 07. For the arrangement of a transmission 10 and possibly a clutch 11 applies accordingly.

In a third embodiment ( Fig. 4 ) is driven by the first cylinder 01 parallel to the second cylinder 31 and the inking unit 39 and possibly dampening unit 41. Thus, despite ambiguous direction in the moment flow a tooth flank change is avoided with changing loads, which is arranged on the pin 04 of the first cylinder 01 gear 37 together with a gear 46, z. B. a Beiläuferzahnrad 46, arranged. About a likewise arranged on the pin 04 of the first cylinder 01 gear 47 can be aborted on the leading to drive the inking unit 39 and possibly dampening 41 gear 44. The drive of the shaft 08 can in one of the above ways either coaxial with the shaft 08 or via a in Fig. 4 not shown pinion 34 done. For the arrangement of the gear 10 and 35 and possibly a clutch 11 applies accordingly.

In a fourth embodiment ( Fig. 5 ), the output from the first cylinder 01 to the second cylinder 31 does not take place on the side of the clutch 06 facing the cylinder 01, but rather on the side of the clutch 06 which is not movable in the axial direction. For this purpose, the drive connection or the transmission 40 between the first cylinder 01 and the second cylinder 01 is not between the axially variable in length L in its coupling 06 and the first cylinder 01, but on the first cylinder 01 remote from the stationary side Coupling 06 arranged.

For the purpose of saving space and shortening the required length of the pin 04; 32, a gear 49, which is arranged for example on a clutch 06 encompassing the socket 48, be connected to the side facing away from the cylinder 01 side of the clutch 06. This gear 49 meshes on one side with a non-rotatably connected to the pin 32 of the second cylinder 31 gear 51 and the pinion 34. With this embodiment, compared to Fig. 3 a drive level can be saved and the drive from the drive motor 07 to the cylinder 01; 31 via a helical toothing. The drive connection formed by the gears 49 and 51 does not lie on the side of the clutch 06 facing the cylinder 01 to be moved axially, but on the side fixed relative to an axial movement.

In the embodiment according to Fig. 5 can be arranged coaxially with the shaft 08, waiving the pinion 34, the drive motor 07, but for a possibly existing transmission 10, the above applies.

For all embodiments, in particular for the embodiment variants with a coaxial with the shaft 08 arranged drive motor 07 is, as already partially set forth on the drive motor 07 or between the drive motor 07 and shaft 08 and between the drive motor 33 and cylinder 31, the planetary gear 10 shown partially advantageous , The transmission 10; 35 are then preferably designed as a single-encapsulated gear, which is a lubricant inside, in particular a thin lubricant, such. As oil, may have. In the case of the drive network between the two cylinders 01; 31 can also be performed encapsulated in an advantageous embodiment of this transmission 40. However, the clutch 06 is advantageous in any of the encapsulated spaces, but outside and therefore arranged easily accessible. The latter is the case in particular in connection with the formation of the coupling 06 as a membrane coupling described above.

The drive connections between the two cylinders 01; 31 and / or one of the cylinders 01; 31 and the inking unit 39 and possibly dampening unit 41 can also be done via timing belt (taking into account a reversal of direction) or other form-locking drive connections.

The operation of the drive of a cylinder 01; 31 is as follows:

During operation, d. H. During the set-up or production operation, the cylinder 01 and, depending on the design, the second cylinder 31 and also the inking unit 39 and possibly dampening unit 41 are driven by means of the drive motor 07.

Is a correction of the page register, i. H. a lateral displacement of the printed image, required, so by means of a not shown, preferably arranged on the drive opposite side of the cylinder 01, drive means the cylinder 01 in the axial direction by an amount .DELTA.L moved without the drive motor 07 must also be moved , The amount .DELTA.L of the displacement is absorbed by the clutch 06, wherein the cylinder 01 facing away from the end fixed, in particular stationary with respect to the axial direction, is fixed. The displacement does not cause simultaneous adjustment of the circumferential register.

Both a correction via an electronic shaft between the cylinders 01; 31, as well as a mechanical readjustment of the circumferential register can be omitted.

LIST OF REFERENCE NUMBERS

01

Cylinder, first, forme cylinder

02

-

03

-

04

Cones (01)

05

-

06

Coupling, elastic, coupling, shaft coupling, yielding, expansion coupling

07

drive motor

08

wave

09

Wave (07)

10

Transmission, reduction gear, planetary gear

11

Clutch, dog clutch

12

Flange (06)

13

Flange (06)

14

Bore (12)

15

-

16

Bore (12)

17

Bore (13)

18

Bore (13)

19

Center piece, flange (06)

20

-

21

Bore (19)

22

Bore (19)

23

Disc pack (06)

24

Disc pack (06)

25

-

26

Bore (23)

27

Bore (24)

28

Screw (06)

29

Screw (06)

30

washers

31

Cylinder, second, transfer cylinder, impression cylinder

32

Cones (31)

33

Drive motor (31)

34

pinion

35

Transmission, reduction gear (34, 36)

36

Gear (08)

37

Gear (04)

38

Gear (32)

39

inking

40

Transmission (37, 38)

41

dampening

42

Gear (32)

43

Gear (04)

44

Gear (39)

45

-

46

Gear, Beveling Gear (37)

47

Gear (04)

48

Rifle

49

Gear (48)

50

-

51

Gear (32)

L

Length (18)

.DELTA.L

Amount of change in length (06), axial displacement (01)

Claims (32)

1. Drive of a cylinder (01) of a printing press, which cylinder (01) is in the form of a forme cylinder (01), by means of a drive motor (07), a clutch (06) which permits a relative movement in the axial direction between the forme cylinder (01) and the drive motor (07) driving the forme cylinder (01) being arranged between the drive motor (07) driving the forme cylinder (01) and the forme cylinder (01), characterized in that the clutch (06) has at least one disc pack (23; 24) connected in an interlocking manner to flanges (12; 13; 19) and is variable in its length (L) by an amount (±ΔL) in the axial direction of the forme cylinder (01; 31), and in that the forme cylinder (01) is mounted by means of a drive device so as to be displaceable by an amount (ΔL) in the axial direction so that the axial movement is taken up by the amount (ΔL) by the clutch (06).
2. Drive according to Claim 1, characterized in that the clutch (06) is arranged outside a lubricant space.
3. Drive according to Claim 1 or 2, characterized in that a gear (10; 35) is arranged between the drive motor (07) and the clutch (06).
4. Drive according to Claim 1 or 2, characterized in that a second cylinder (31) coordinated with the cylinder (01) can be driven from the first cylinder (01) by means of the same drive motor (07) via a gear (40) effective between the cylinders (01; 31).
5. Drive according to Claim 1 or 2, characterized in that a second cylinder (31) coordinated with the cylinder (01) can be driven by means of a separate drive motor (33).
6. Drive according to Claim 1 or 2, characterized in that a gear (10; 35) is arranged between the second cylinder (31) and the drive motor (33).
7. Drive according to Claim 1 or 2, characterized in that the drive motor (07) is arranged fixed with respect to a frame.
8. Drive according to Claim 3 or 6, characterized in that the gear (10; 35) between drive motor (07) and clutch (06) is designed with a closed lubricant space as an independently encapsulated gear (10; 35).
9. Drive according to Claim 8, characterized in that the clutch (06) is arranged outside a lubricant space.
10. Drive according to Claim 1 or 2, characterized in that the clutch (06) is designed as a clutch (06) interlocking in the axial direction.
11. Drive according to Claim 1 or 2, characterized in that the clutch (06) is designed as a clutch (06) yielding in the axial direction.
12. Drive according to Claim 1 or 2, characterized in that the clutch (06) is designed as a nonrotating and unswitchable shaft clutch (06) which is interlocking in the circumferential direction.
13. Drive according to Claim 1, characterized in that the clutch (06) has at least one disc pack (23; 24) connected in an interlocking manner to flanges (12; 13; 19).
14. Drive according to Claim 1 or 13, characterized in that the disc pack (23; 24) is connected in the circumferential direction alternately to the flange (12; 19) facing the cylinder (01; 31) and the flange (19; 13) facing the drive motor (07).
15. Drive according to Claim 1 or 5, characterized in that a shaft (09) of the drive motor (07; 33) driving the cylinder (01; 31) is arranged coaxially with and parallel to an axis of rotation of the cylinder (01; 31).
16. Drive according to Claim 15, characterized in that the shaft (09) of the drive motor (07) or an extended shaft (08) has an operative connection to that side of the clutch (06) which faces away from the cylinder (01; 31).
17. Drive according to Claim 1 or 2, characterized in that a shaft (08) is arranged nonrotatably on that side of the clutch (06) which faces away from the cylinder (01; 31), coaxially with and parallel to an axis of rotation of the cylinder (01; 31).
18. Drive according to Claim 3 or 6, characterized in that the gear (10; 35) has a gear wheel (36) arranged nonrotatably on the shaft (08) and a pinion (34) intermeshing therewith.
19. Drive according to Claim 3 or 6, characterized in that a planetary gear (10) is arranged between drive motor (07; 33) and the cylinder (01; 31).
20. Drive according to Claim 1 or 2, characterized in that an inking unit (39) coordinated with the cylinder (01) and optionally a damping unit (41) can be driven by means of the same drive motor (07).
21. Drive according to Claim 4, characterized in that the inking unit (39) and optionally the damping unit (41) can be driven from the second cylinder (31) via a gear (42, 43, 44).
22. Drive according to Claim 4, characterized in that the gear (40) between the first cylinder (01) and the second cylinder (31) is in the form of a gear train (37, 38; 49, 44) which has a gear wheel (37; 49) connected at least nonrotatably to the journal (04) of the first cylinder (01) and a gear wheel (38; 51) cooperating with said gear wheel (37; 49) and connected nonrotatably to a journal (32) of the second cylinder (31).
23. Drive according to Claim 21, characterized in that the gear (42, 43, 44) between the second cylinder (31) and the inking unit (39) and optionally the damping unit (41) is in the form of a gear train (42, 43, 44) which has a gear wheel (42) arranged nonrotatably on a journal (32) of the second cylinder (31), a gear wheel (43) cooperating with said gear wheel (42) and mounted nonrotatably on the journal (04) of the forme cylinder (01) and a gear wheel (44) of the inking unit (39) and optionally with the damping unit (41), which gear wheel (44) cooperates with said gear wheel (43).
24. Drive according to Claim 1 or 2, characterized in that an inking unit (39) coordinated with the first cylinder (01) and the second cylinder (31) can be driven from the first cylinder (01) in parallel via a respective gear (40; 47, 44).
25. Drive according to Claim 1 or 2, characterized in that the cylinder (01) can be axially displaced for the purpose of adjustment and/or of regulation of the side register.
26. Drive according to Claim 4, characterized in that the second cylinder (31) is in the form of a transfer cylinder (31).
27. Drive according to Claim 4, characterized in that the second cylinder (31) is in the form of a counter pressure cylinder (31) forming a printing point with the forme cylinder (01).
28. Drive according to Claim 25, characterized in that the axial displacement is taken up by a change in a length (L) of the clutch (06).
29. Drive according to Claim 1 or 2, characterized in that a torsion spring value for the torsion in the clutch is greater than 10 000 Nm/°, in particular is between 10 000 and 20 000 Nm/°.
30. Drive according to Claim 1, characterized in that the cylinder (01) is axially displaceable by an amount ΔL of 0 to ± 4mm, in particular to ± 2.5 mm, from a centre position.
31. Drive according to Claim 1 or 13, characterized in that the disc pack (23; 24) is annular.
32. Drive according to Claim 6, characterized in that the gear (10; 35) is in the form of an individually encapsulated gear.

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