EP1633563A1

EP1633563A1 - Printing units comprising bearing rings in a rotary press

Info

Publication number: EP1633563A1
Application number: EP04713088A
Authority: EP
Inventors: Bernd Kurt Masuch
Original assignee: Koenig and Bauer AG
Current assignee: Koenig and Bauer AG
Priority date: 2003-06-17
Filing date: 2004-02-20
Publication date: 2006-03-15
Anticipated expiration: 2024-02-20
Also published as: EP1707356B1; US7441501B2; DE502004001960D1; WO2004110761A1; EP1707356A1; US20070022886A1; ATE344731T1; DE10327490A1; ATE367922T1; EP1633563B1; DE502004004467D1; DE10327490B4

Abstract

Printing unit comprises a first cylinder (02, 04) having an effective radius (r02, r04) which is larger in the area of its barrel than the radius (r21, r23) of a bearing ring (21, 23). Preferred Features: The first cylinder is formed as a counter pressure cylinder or as a molding cylinder. A second cylinder (03) is formed as a transfer cylinder supporting a compressible layer (11). The transfer cylinder interacts with a molding cylinder.

Description

description

PRINTING UNITS WITH BEAUTIFUL RINGS IN A ROTARY PRINTING MACHINE

The invention relates to printing units of a rotary printing press according to the preamble of claims 1, 2 or 9.

When driving cylinders or cylinder groups with separate drives z. B. in satellite printing units process-related processing differences between the cylinder pairs can occur. These depend on the contact pressure, the number of active pressure points, the lift strength, the type or even the manufacturer of the lift itself, whether the friction gear is designed without a bearer ring or with bearer rings, on the bearer ring radii or overall on the radius ratio of the friction gear.

This can lead to e.g. T. considerable and, under changing conditions, lead to significantly different power flows between the cylinders or cylinder groups. This is undesirable because they lead to asymmetries in the power design, depending on the conditions and operating mode, to different powers or even to overloads on motors and controllers.

Even with cylinder groups, printing units, printing units or printing towers that are jointly driven via gears, this leads to undesirable moments, to increased friction and wear.

From DE 195 01 243 A1 cylinders of a rotary printing press with bearer rings are known, the bearer rings of the satellite cylinder being rotatably mounted for the purpose of reducing the power transmission. In WO 00/41887 A1, a compensating friction gear in the form of bearer rings having a radius ratio unequal to 1 is superimposed on a friction gear made of process-related friction cylinders. The bearer ring of the impression cylinder is larger than its bale and larger than the bearer ring of the cooperating transfer cylinder. In the priority document DE 199 27 555 A1, the relationships in a figure between the transfer and impression cylinders are shown in reverse.

US 31 96 788 discloses a printing unit for double-sided offset printing, transfer cylinder and associated forme cylinder having radii different from one another in the region of their bale. Three pairs of bearer rings working together are arranged in three different levels. The pairs each have the same diameter.

In US 2,036,835 A, ratios for the diameters of the cylinders to one another are specified in such a way that the transfer cylinder is smaller and the impression cylinder and forme cylinder are larger than the diameter of the bearer rings, which is the same for all three cylinders.

The invention has for its object to provide printing units of a rotary printing press.

The object is achieved by the features of claims 1, 2 or 9.

The advantages which can be achieved with the invention consist in particular in that the special conditions in the area of the friction gear formed by the cylinders result in a considerably smaller power shift. This also enables a higher print quality through so-called "true rolling". This applies in particular to printing units which have a cylinder which does not carry any ink, in particular a satellite cylinder and a plurality of transfer cylinders which cooperate with it. The gradation of the three cylinders in their design with respect to one another is particularly advantageous, since not just one pair of cylinders but several contribute to the potential power shift. A significant advantage results in bearer rings for an associated bearer ring that is smaller than the satellite cylinder.

In an advantageous embodiment, the bearer rings of the three cylinders can be graduated in pairs in relation to one another in size. The gradation of the three bearer rings with respect to one another can optionally be carried out instead of, or in an advantageous development, in addition to the gradation of the cylinders.

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

Show it:

Figure 1 is a schematic representation of interacting cylinders of a rotary printing press.

2 shows a detail of a friction mechanism of two cylinders in an enlarged view;

3 shows a schematic illustration of a nine-cylinder printing unit with a paired drive;

Fig. 4 is a schematic representation of a nine-cylinder printing unit with a single drive; 5 shows a schematic illustration of a 10-cylinder satellite printing unit;

Fig. 6 shows the nipple.

A rotary printing press has a printing unit 01 with three cylinders 02; each of which works together in pairs in a print-on position; 03; 04 on. The first cylinder 02 is e.g. B. designed as a forme cylinder 02 and has on its outward outer surface 06 information of an image to be printed. The image to be printed can be provided in the form of a structure for high pressure, gravure printing or planographic printing directly in a lateral surface of the forme cylinder 02 itself, or else on a printing form 09 (printing plate, sleeve, cliché) detachably arranged on a base body 08 of a radius rO8 of the forme cylinder 02 etc.) of a thickness dO9, e.g. B. dO9 = 0.25 to 0.33 mm, in particular 0.27 to 0.30 mm. In each of the two cases, the outer surface 06, which has the printed image, defines an effective radius rO2 of the forme cylinder 02. The forme cylinder 02, which has the printing forme 09 and possibly one or more intermediate layers, not shown, is essentially incompressible, i. H. with a fixed radius rO2.

The second cylinder 03, designed as a transfer cylinder 03, has in the area of its outer surface at least one layer 11 with compressible and / or elastic properties on an inelastic cylinder core 12 of radius r12 that is essentially incompressible in the radial direction. Layer 11 is e.g. B. as an elevator 11, in particular as a rubber blanket 11 (finally, as a sleeve, etc.) detachably arranged on the cylinder core 12. The radius r12 of the cylinder core 12 can either directly through the outer surface of a base body 13 of a radius r13, or in the presence of one or more intermediate layers 14, z. B. a beam 14, defined by the outer surface of the outermost intermediate layer 14. The intermediate layer (s) serves (serve) z. B. the adaptation to different thicknesses d11 of blankets 11 and / or thicknesses of substrates. Layer 11 is considered to be incompressible Carrier layer connected layer 11 executed, for. B. as a layer of a metal printing blanket, the radius r12 including the thickness of the incompressible carrier layer, e.g. B. the metal plate to understand.

Due to the elastic and / or compressible layer 11, the transfer cylinder 03 has an outer radius rO3u in the unloaded state, i. H. in the pressure-down position, and an outer or effective radius rO3b in the loaded state, d. H. in the pressure-on position of the cylinders 02; 03; 04, on. The “radius in the loaded state”, or effective radius, is here to be understood in general as the distance of the axis of rotation R02; R03; R04 of the cylinder 02; 03; 04 in question from the considered nip point in the connection plane of the axes of rotation R02; R03; R04. A distinction may be made here between the radius rO3b1 in the loaded state in the area of the nip 16 for the forme cylinder 02 (FIG. 2) and the radius rO3b2 in the loaded state in the area of the nip 17 for the further cylinder 04. In FIG in brackets for the nip 17 between the transfer cylinder 03 and the third cylinder 04. This nip 17 also represents a printing point 17 for a web 18 to be printed (dashed), for example paper web 18.

The cylinder 04 which forms a printing point 17 with the transfer cylinder 03 and acts as an impression cylinder 04 can either be designed as a transfer cylinder of a second pair of cylinders or as a cylinder 04 which does not carry any printing ink and on which one or more transfer cylinders 03 can be set via a path (not shown).

In the embodiment shown, the impression cylinder 04 is designed as a cylinder 04 which does not carry any printing ink and which is essentially incompressible, ie is designed with a fixed outer radius rO4. This radius rO4 may include incompressible layers, not shown, applied to a cylinder base body and then represents an effective radius rO4 in the pressure-on position (e.g. also towards the nip point).

The form and transfer cylinders 02; In an advantageous embodiment, 03 are dimensioned and / or placed against one another in such a way that the forme cylinder 02 has a larger radius rO2, for. B. at least 0.2 per thousand greater than the radius rO3b1 of the transfer cylinder 03 in the nip 16. A ratio of the radius rO2 of the forme cylinder 02 to the radius rO3b1 of the transfer cylinder 03 in the loaded state, i. H. is in the print-on position. B. from 1.0015 to 1.0030, preferably from 1.0020 to 1.0025. The ratio of the radius rO2 of the forme cylinder 02 to the radius rO3u of the transfer cylinder 03 in the unloaded state can, for. B. between 1, 0000 and 1, 0015, in particular 1, 0010 and 1, 0015.

A thickness d11 of the relieved layer 11 lies in the unloaded but already used case in the printing operation (i.e. not unused) e.g. B. between 1.5 and 2.5 mm, in particular between 1.8 and 2.1 mm. The radius r12 of the cylinder core 12 is corresponding to the above. Conditions. Here it may be an intermediate layer 14 of e.g. a thickness of 0.14 to 0.22 mm to be taken into account when dimensioning the radius r13 of the base body 13.

In the case of a printing group 01 with cylinders 02; 03 double the circumference, ie with a circumference which essentially corresponds to two standing printed pages, in particular newspaper pages, arranged one behind the other, the radius rO2 of the forme cylinder 02 is z. B. between 140 to 190 mm, in particular between 155 and 180 mm. The transfer cylinder 03 now has a radius rO3b1 in the pressure-on position (loaded state), which is 0.14 to 0.20 mm, in particular 0.16 to 0.18 mm smaller than the radius r02 of the forme cylinder 02 This is determined by the fixed radius rO2 of the incompressible forme cylinder 02 and the relative position of Axes of rotation R02; R03 the cylinder 02; 03 set to each other in the pressure-on position, but at the same time a maximum radius ri2 of the incompressible cylinder core 12 and a minimum thickness d11 of the layer 11 must be taken into account. In an advantageous embodiment, the thickness d11 is selected such that in the unloaded state there is an excess T03a of approximately 0.13 to 0.21 mm, in particular approximately 0.16 to 0.18 mm, compared to the loaded state, ie that at The layer 11 is pressed in by the forme cylinder 02 by the stated amount (corresponds to the indentation depth). If a rubber blanket 11 that has not yet been used is used, the transfer cylinder 03 first has an incidence F (shown in broken lines in FIG. 1), e.g. B 0.02 to 0.05 mm, increased radius rO3u in the unloaded state and a correspondingly enlarged oversize T03a.

An angle of attack is predetermined, for example by one or more stops, in such a way that the two cylinders 02; 03 in their position in the area of the nipple 16 (connecting plane of the axes of rotation R02; R03) the above. Have a ratio of radii and, in an advantageous development, a ratio between the oversize T03a and the thickness d11 of the layer 11 in the unloaded (collapsed) state is between 5% and 15%

The transmission and impression cylinder 03; In an advantageous embodiment, 04 are dimensioned and / or placed against one another such that the forme cylinder 02 also has a larger radius rO2, for. B. greater by at least 0.1 per thousand than the radius rO4 of the impression cylinder 04. A ratio of the radius rO2 of the forme cylinder 02 to the radius rO4 of the impression cylinder 04 is preferably from 1,0001 to 1,0002.

In the case of the above printing group 01 with cylinders 02; 03 of double circumference, the impression cylinder 04 has a radius rO4 which is 0.02 to 0.10 mm, in particular 0.04 to 0.06 mm smaller than the radius rO2 of the forme cylinder 02. Between the axes of rotation R03; R04 of transfer cylinder 03 and incompressible impression cylinder 04, a distance is chosen for the pressure on position that a ratio of the radius rO4 of the impression cylinder 04 to the radius rO3b2 of the transfer cylinder 03 in the loaded state, for. B. is between 1, 001 and 1, 003. This is due to the fixed radius rO4 of the incompressible impression cylinder 04 and the relative position of the axes of rotation R04; R03 the cylinder 04; 03 set to each other in the pressure-on position, but at the same time a maximum radius rO4 of the incompressible cylinder 04 and a minimum thickness d11 of the layer 11 must be taken into account. In an advantageous embodiment, the thickness d11 is selected such that in the unloaded state there is an excess T03b of approximately 0.13 to 0.21 mm, in particular approximately 0.16 to 0.18 mm, compared to the loaded state, ie that at Employment layer 11 is pressed by the impression cylinder 04 by the amount mentioned. If a rubber blanket 11 that has not yet been used is used, the transfer cylinder 03, as mentioned above, first has one around the incidence F (dashed line in FIG. 1), for. B. 0.02 to 0.05 mm, increased radius rO3u in the unloaded state and a correspondingly enlarged oversize T03b.

An angle of attack is specified, for example by one or more stops, in such a way that the two cylinders 03; 04 in their position in the area of the nipple 17 (connecting plane of the axes of rotation R03; R04) the above. Have a ratio of radii and, in an advantageous development, a ratio between the oversize or indentation T03b and the thickness d11 of the layer 11 in the unloaded (sunken) state is between 5% and 15%.

In a first embodiment, the conditions mentioned can be used for cylinders 02; 03; 04 or in another version also for cylinder 02; 03; 04 with bearer rings 21; 22; 23, as shown in Fig. 1, are used.

In connection with the mentioned versions of the friction gear between the cylinders 02; 03; 04, the bearer rings 21; 22; 23 all have the same radius r21; r22; have r23. The radius ratio between two cylinders 02; 03; 04 and those of the associated bearer rings 21; 22; 23 are different from each other in this case. To a primarily by the described friction gear of the cylinder 02; 03; 04 to enable certain rolling behavior can be for the bearer rings 21; 22; 23 measures to reduce friction, e.g. B. increased lubrication may be provided. The bearer rings 21; 22; 23 could also be rotatable with the respective cylinder 02; 03; 04 be connected so that a relative rotation of the bearer ring 21; 22; 23 and associated cylinder 02; 03; 04 is possible.

In an advantageous third embodiment, both the friction gear of the cylinders 02; 03; 04 as described above, as well as the friction gear of the bearer rings 21; 22; 23, as described below, have special radius ratios not equal to 1:

In an advantageous embodiment, the bearer ring 21 of the forme cylinder 02 has a radius r21, so that the ratio between the radius rO2 of the forme cylinder 02 (surface 06) and that of the bearer ring r21 is 1, 0007 to 1, 0015, greater than 1. 0009 to 1,0013 inclusive. For a cylinder 02 of double circumference, an overlap Ü02 of the surface 06 with respect to the bearer ring 21 is from 0.10 to 0.23 mm, in particular from 0.15 to 0.19 mm. With a thickness dO9 of the printing form 09 of z. B. 0.25 to 0.33 mm, this must be taken into account when dimensioning the base body 08 with an undercut uO2 relative to the bearer ring 21. The undercut uO2 is, for example, between 0.11 and 0.15 mm.

The bearer ring 23 of the impression cylinder 04 has a radius r23, so that the ratio between the radius r04 of the impression cylinder 04 and that of the bearer ring r23 is from 1 0004 to 1 0012, in particular from 1 0006 to a maximum of 1 0009. For a cylinder 04 of double circumference, an overlap Ü04 of the surface 06 with respect to the bearer ring 21 is from 0.06 to 0.18 mm, in particular from 0.08 to 0.16 mm.

The bearer ring 22 of the transfer cylinder 03 has a radius r22, so that the ratio between the (effective) radius rO3b1 in the pressure-on position of the transfer cylinder 03 and that of the bearer ring r22 is from 0.9978 to 0.9996, in particular from 0 , 9984 to 0.9990. For a cylinder 03 of double circumference, a protrusion Ü22 of the bearer ring 22 to the effective radius rO3b1 is from 0.13 to 0.22 mm, in particular from 0.15 to 0.20 mm. With a thickness d11b of the layer 11 in the loaded state of z. B. 1, 3 to 2.30 mm, this is to be taken into account when dimensioning the cylinder core 12 (base body 13 and possibly intermediate layer (s) 14) with an undercut uO3 relative to the bearer ring 22. The undercut uO3 is, for example, between 1.6 and 2.6 mm.

The radii r21 are in particular in order to ensure the condition of the ratio of the radii r22 and rO3b in the contact position; r22; r23 bearer rings 21; 22; 23 in relation to each other in special relationships as follows:

The bearer rings 21 and 23 of the forme and impression cylinder 02; 04 have z. B. the same radius r21; r23, the ratio is 1,000. The ratio of the radii r21; However, r22 of the bearer ring 21 associated with the molding cylinder 02 and that of the transfer cylinder 03 is in the range from 1,0010 to 1,0020, in particular in the range from 1,0010 to 1,0016. For cylinder 02; 03 twice the circumference, the radius r21 is, for example, 0.01 to 0.03 mm, in particular approximately 0.020 ± 0.005 mm, ie 0.015 to 0.025 mm larger than that of the transfer cylinder 03. The same also applies accordingly to the ratio between the radii r23 of the bearer ring 23 associated with the impression cylinder 04 to that of the transfer cylinder. The stated ratios and dimensions for the radii lead to differences in the diameter of 0.02 to 0.06 mm and are therefore markedly different from the difference due to the current manufacturing tolerance of only approx. 0.004 mm. The specified values are therefore to be implemented in a targeted manner and are not based on randomness during production.

In a fourth embodiment, the friction gears each have a gear ratio or radius ratio of 1,000 in pairs, with only the friction gears between two bearer rings 21; 22; 23 have the above-mentioned radius ratios or gear ratios different from 1,000.

The explanations given are particularly advantageous in connection with printing units whose cylinders 02, 03, 04 or printing units 01 are driven individually, in pairs or in groups. This is particularly advantageous with regard to undesired power shifts between the printing units 01 for the case shown in FIG. 3 when a plurality of transfer cylinders 03 of a plurality of printing units 01 interact with a common impression cylinder 04 designed as a satellite cylinder 04. FIG. 3 shows a printing unit 24 designed as a nine-cylinder printing unit 24, in which four pairs of forme and transfer cylinders 02, 03 are assigned to the satellite cylinder 04.

In an embodiment that is not shown, two adjacent pairs 02, 03 are each driven together as a drive system by a drive motor 26. The satellite cylinder 04 can be driven by one of the two drive assemblies or by its own third drive motor 26.

In the embodiment shown in Fig. 3, the cylinders 02, 03; 04 of the nine-cylinder printing unit 24 driven in rotation by five drive motors 26. Each pair 02, 03 and the counter-pressure cylinder 04 designed as a satellite cylinder 04 have their own, at least speed-controlled drive motor 26, which is mechanically independent of the other drive motors 26. The drive networks formed from this have, apart from the friction gears described above, no mechanical coupling to one another. In one variant, the satellite cylinder 04 is driven simultaneously by two drive motors 26, one of these two drive motors 26 being fed together with the drive motors 26 each by two pairs by a common power supply unit. This allows the supply to be configured symmetrically by means of two power supply units for the rotary drives of the nine-cylinder printing unit 24.

The drive motors 26 are e.g. B. with a control and / or computing device 27 in signal connection from which they receive setpoint specifications with respect to their speed. It contains a so-called “electronic shaft”, ie elements for the electronic synchronization of the drive motors 26. In a preferred embodiment, the drive motors 26, at least those of the pairs, are designed as drive motors 26 that can be regulated with respect to their angular position and are obtained by the control and / or Computing device 27 default values with respect to their angular position.

In an embodiment shown in FIG. 4, each of the cylinders 02; 03; 04 own, mechanically from other cylinders 02; 03; 04 independent drive motor 26. For the execution of the drive motors 26, the control and / or computing device 27, possibly a second drive motor 26 for the satellite cylinder 04 and the supply by means of two power supplies, the above is analogous. apply.

If the printing unit 24, as shown in FIG. 5, is designed as a ten-cylinder printing unit 28 with two satellite cylinders 04 assigned to the four pairs, the two satellite cylinders 04 can each be integrated into a drive system of two pairs, as mentioned above, one or two common ones. have their own drive motor (s) 26, or in each case be driven mechanically independently of one another by their own drive motor 26, as shown. For the pairs, the above-mentioned pairs (shown) or a single drive of the cylinder 02; 03; 04 (as in Fig. 4).

The individually or in pairs driven cylinder 02; 03; 04 are, for example, directly or indirectly, for example via a gear, not shown, for. B. a gear, toothed belt or friction gear can be driven.

In one embodiment, at least transfer and impression cylinders 03; 04 z. B. a circumference between 850 and 1,300 mm, in particular from 940 to 1,200 mm. The form cylinder 02 also has this scope here (for accommodating, for example, four standing printed pages arranged next to one another, in particular newspaper pages). The length of the usable bale of the cylinder 02; 03; 04 is z. B. 1,100 to 1,800 mm, in particular 1,400 to 1,700 mm.

However, the aforementioned statements can also be made on cylinder 02; 03; 04 simple scope, or for example with a form and / or transfer cylinder 02; 03 simple and an impression cylinder 04 with double circumference can be applied. The width of the cylinder 02; 03; 04 can be single, double, triple or quadruple.

With regard to the formerly high drive powers, the designs described are also advantageous in connection with particularly wide, e.g. B. 1,850 to 2,400 wide, and strong, e.g. B. double circumference, cylinders 02; 03; 04. The scope is to accommodate two standing pages, z. B. newspaper pages in broadsheet format, by means of two elevators which can be fixed one after the other in the circumferential direction on the forme cylinder 02, e.g. B. flexible printing forms. In the axial direction, the forme cylinder 02 is for receiving z. B. dimensioned at least six adjacent printed pages, especially newspaper pages in broadsheet format. It depends, among other things, on the type of product to be produced, whether only one print page or several print pages are arranged next to one another in the axial direction on a printing form. The transfer cylinder 03 is z. B. with three elevators 11, z. B. rubber blankets 11. They range in circumferential direction essential to the full extent. The rubber blankets 11 are, for. B., the vibration behavior of the printing group 01 in the operating case favorably influencing, alternating, for. B. 180 °, offset from each other.

A ratio of a usable bale length of cylinders 02; 03; 04 to their diameter is advantageously 5.8 to 8.8, z. B. at 6.3 to 8.0, in a broad version (six printed pages wide) in particular at 6.5 to 8.0.

The length of the usable bale is understood to be the width or length of the bale that is suitable for receiving lifts. This roughly corresponds to a maximum possible web width of a web to be printed. Any bearer rings, operating areas or grooves in the area of the lateral surface near the face are also not taken into account.

LIST OF REFERENCE NUMBERS

01 printing unit

02 cylinders, form cylinders

03 cylinder, transfer cylinder

04 cylinder, impression cylinder, satellite cylinder 05

06 surface 07

08 basic body

09 printing form 10

11 layer, elevator, rubber blanket

12 cylinder core

13 basic body

14 liner, beam 15

16 nip point

17 nip point, pressure point

18 web, paper web 19

20

21 bearer ring

22 bearer ring

23 Bearer ring, 9-cylinder satellite printing unit

24 Printing unit, nine-cylinder printing unit 25 6 drive motor

27 control and / or computing device 28 ten-cylinder printing unit

dO9 thickness (09) d11 thickness (11) d11b thickness (11), loaded

F Single strength

rO2 radius (02) rO3b radius (03), loaded rO3b1 radius (03), loaded rO3b2 radius (03), loaded rO3u radius (03), unloaded rO4 radius (04) rO8 radius (02) r12 radius (12) r13 radius (13) r21 radius (21) r22 radius (22) r23 radius (23)

R02 rotation axis (02)

R03 rotation axis (03)

R04 rotation axis (04)

T03a oversize (11)

T03b oversize (11)

Ü02 overhang (02, 21) U04 overhang (04, 23)

Ü22 overhang (22, 03)

uO2 undercut (02) uO3 undercut (03)

Claims

Expectations

1. Printing unit (24; 28) of a rotary printing press with a first cylinder (02; 04), which forms a nip point in a print-on position with a second cylinder (03) having a compressible surface, the two cylinders (02; 03; 04) have bearer rings (21; 22; 23) cooperating in the pressure-on position and a radius (r21; r23) of a bearer ring (21; 23) assigned to the first cylinder (02; 04) is larger than a radius (r22) of a bearer ring (22) assigned to the second cylinder (03), characterized in that an effective radius (r02; r04) of the first cylinder (02; 04) is larger in the region of its barrel than the radius (r21; r23) his bearer ring (21; 23).

2. Printing unit (24; 28) of a rotary printing press with a first cylinder (02; 04), which forms a nip point (17) with a second cylinder (03) having a compressible surface in a print-on position, and in the region an effective radius (rO2; rO4) of the first cylinder (02; 04) is greater than an effective radius (rO3b2) of the second cylinder (03), characterized in that a radius ( r21; r23) of a bearer ring (21; 23) assigned to the first cylinder (02; 04) is larger than a radius (r22) of a bearer ring (22) associated with the second cylinder (03) and interacting with the former in pressure-on position ).

3. Printing unit (24; 28) according to claim 1 or 2, characterized in that the first cylinder (04) is designed as an impression cylinder (04).

4. Printing unit (24; 28) according to claim 1 or 2, characterized in that the first cylinder (04) is designed as a forme cylinder (02).

5. Printing unit (24; 28) according to claim 1 or 2, characterized in that the

second cylinder (03) as a transfer cylinder (03) carrying a compressible layer (11).

6. Printing unit (24; 28) according to claim 3 and 5, characterized in that the transfer cylinder (03) cooperates in a print-on position with a forme cylinder (02).

7. Printing unit (24; 28) according to claim 1 or 2, characterized in that the second cylinder (03) is designed as a form cylinder carrying a compressible printing form (09).

8. Printing unit (24; 28) according to claim 4 or 6, characterized in that in the pressure-on position in the area of the nip point (16) a ratio of an effective radius (rO2) of the forme cylinder (02) to an effective radius (rO3b1 ) of the second cylinder (03) is in the range of 1, 0015 to 1.0030.

9. Printing unit (24; 28) of a rotary printing press with a forme cylinder (02), which forms a nip point (16) with a second cylinder (03) in a print-on position, characterized in that in the print-on position in Area of the nip (17) is a ratio of an effective radius (rO2) of the forme cylinder (02) to an effective radius (rO3b1) of the second cylinder (03) in the range of 1, 0015 to 1, 0030.

10. Printing unit (24; 28) according to claim 6 or 9, characterized in that a radius (r21) of a bearer ring (21) assigned to the forme cylinder (02) is larger than a radius (r22) of a cooperating second cylinder ( 03) assigned bearer ring (22).

11. Printing unit (24; 28) according to claim 9, characterized in that the second

Cylinder (03) is designed as a transfer cylinder (03) carrying a compressible layer (11).

12. Printing unit (24; 28) according to claims 4 and 5 or according to claim 11, characterized in that the transfer cylinder (03) with a bearer (23) having impression cylinder (04) forms a pressure point in a print-on position ,

13. Printing unit (24; 28) according to claim 3 or 12, characterized in that a ratio of the radius (rO4) of the impression cylinder (04) to the radius (r23) of its bearer ring (23) in the range of 1, 0004 to 1, 0012 lies.

14. Printing unit (24; 28) according to claim 3 or 12, characterized in that a ratio of the radius (rO4) of the impression cylinder (04) to the radius (r23) of its bearer ring (23) in the range of 1, 0006 to 1, 0009 lies.

15. Printing unit (24; 28) according to claims 4 and 5 or according to claim 12, characterized in that the radius (r23) of the bearer ring (23) associated with the impression cylinder (04) is made larger by 0.01 to 0.03 mm is as a radius (r22) of the bearer ring (22) assigned to the transfer cylinder (03).

16. Printing unit (24; 28) according to claim 3 or 12, characterized in that an effective radius (rO4) of the impression cylinder (04) in the region of its bale is larger than a radius (r23) of its bearer ring (23).

17. Printing unit (24; 28) according to claim 4 or 9, characterized in that a radius (rO2) of the forme cylinder (02) in the region of its bale is larger than a radius (r2i) of its bearer ring (21).

18. Printing unit (24; 28) according to claim 3 or 16, characterized in that the effective radius (rO4) of the impression cylinder (04) is 0.06 to 0.18 mm larger than the radius (r23) of its bearer ring (23 ).

19. Printing unit (24; 28) according to claim 3 or 16, characterized in that the effective radius (rO4) of the impression cylinder (04) is 0.08 to 0.16 mm larger than the radius (r23) of its bearer ring (23 ).

20. Printing unit (24; 28) according to claims 4 and 5 or according to claim 11, characterized in that the radius (r21) of the bearer ring (21) associated with the forme cylinder (02) is 0.015 to 0.25 mm larger than that Radius (r22) of the bearer ring (22) assigned to the transfer cylinder (03).

21. Printing unit (24; 28) according to claim 6 or 12, characterized in that the bearer ring (21) assigned to the forme cylinder (02) has a larger radius (r21)

• than that of the assigned transfer cylinder (03) and the bearer ring (22) assigned to the transfer cylinder (03) has a smaller radius (r22) than the bearer ring (23) of the counter-pressure cylinder (04) assigned to it.

22. Printing unit (14; 28) according to claim 6 or 12, characterized in that in a pressure-on pitch of the forme cylinder (02) in the area of its bale a larger radius (r02) than the assigned transfer cylinder (03), and the Transfer cylinder (03) has a smaller radius (rO3b1; rO3b2) in the area of its bale than the counter-pressure cylinder (04) assigned to it.

23. Printing unit according to claim 3 or 12, characterized in that the impression cylinder (04) is designed as a satellite cylinder (04) and together with a plurality of second cylinders (03) having a compressible surface

is arranged acting.

24. Printing unit (01) according to claim 1, 2, 6, 9, 12, or 23, characterized in that each of the cylinders (02; 03; 04) has its own, mechanically independent of other cylinders (02; 03; 04) Drive motor (26) is assigned.

25. Printing unit (01) according to claim 5 and one of claims 4 or 6, or according to claim 9 or claim 23, characterized in that the form and the associated transfer cylinder (02; 03) in pairs, its own, from other cylinders (02 ; 03; 04) mechanically independent drive motor (26) is assigned.

26. Printing unit (01) according to claim 3, 12 or 23, characterized in that the impression cylinder (04) is assigned its own drive motor (26) which is mechanically independent of other cylinders (02; 03; 04).

27. Printing unit (24) according to claim 23, characterized in that it is designed as a nine-cylinder printing unit (24).

28. Printing unit (24) according to claim 23, characterized in that it is designed as a ten-cylinder printing unit (28).

29. Printing unit (28) according to claim 28, characterized in that two counter-pressure cylinders (04) assigned to the printing unit (28) are driven jointly by a drive motor (26) independently of other cylinders (02; 03; 04).

30. Pressure unit (28) according to claim 28, characterized in that two counter-pressure cylinders (04) assigned to the printing unit (28) are each driven by their own drive motors (26) independently of other cylinders (02; 03; 04).