EP1633563B1 - Printing units comprising bearing rings in a rotary press - Google Patents

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

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

When driving cylinders or cylinder groups with separate drives z. B. in satellite printing units can process-related settlement differences between the cylinder pairings occur. These are dependent on the Anstelldruck, the number of active pressure points, the amount of lift, the type or even the manufacturer of the elevator itself, whether the friction is schmitzringlos or formed with bearer rings, of the Schmitzringradien or a total of the radii ratios of the friction gear.

This can be done at z. T. considerable and, under changing conditions, lead to significantly different power flows between the cylinders or the cylinder groups. This is undesirable because they lead to asymmetries in the performance design, depending on conditions and mode of operation to different performances or even overloads on motors and regulators.

Even with cylinder groups, printing units, printing units or printing towers that are driven together via gearboxes, this leads to unwanted moments, increased friction and wear.

In DE 199 27 555 A1 cylinder in pressure-on position are disclosed, wherein diameters of cylinders and bearer rings are adapted to each other.

By DE 195 01 243 A1 cylinders of a rotary printing machine with bearer rings are known, wherein the bearer rings of the satellite cylinder are rotatably mounted to reduce the power transmission.

In WO 00/41887 A1, a friction gear made of process-related friction cylinders has a compensating friction gear in the form of bearer rings superimposed on a radius ratio not equal to 1. The bearer ring of the counter-pressure cylinder is in this case larger than the bale and made larger than the bearer ring of the co-acting transfer cylinder. In the priority document DE 199 27 555 A1, the relationships in a figure between transmission and counter-pressure cylinders are shown in the reverse manner.

The US 31 96 788 discloses a printing unit for the two-sided offset printing, wherein the transfer cylinder and associated forme cylinder have different radii from each other in the bale. Three pairs of co-acting bearer rings are arranged in three different planes. The pairs each have the same diameter.

In US Pat. No. 2,036,835 A, ratios for diameters of the cylinders relative to one another are stated such that the transfer cylinder is smaller, and the impression cylinders and forme cylinders 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 a printing unit of a rotary printing machine.

The object is achieved by the features of claim 1.

The achievable with the present invention consist in particular that a significantly lower power shift can be achieved by the special conditions in the region of the friction gear formed by the cylinder. This also makes higher print quality possible by so-called "true-rolling".

This applies in particular to printing units which have a cylinder which does not convey color, in particular a satellite cylinder and a plurality of transfer cylinders acting together with the latter. Here, the gradation of the three cylinders in their interpretation of each other is of particular advantage, since not only a pair of cylinders but several participate in the potential power shift. A significant advantage results in Schmitzringläufern for a comparison with the satellite cylinder reduced associated Schmitzring.

In an advantageous embodiment, the bearer rings of the three cylinders can each be graded in pairs to each other in size. The gradation of the three bearer rings to each other may optionally be made instead of, or in an advantageous development in addition to the gradation of the cylinder.

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

Fig. 1

eine schematische Darstellung zusammen wirkender Zylinder einer Rotationsdruckmaschine;

Fig. 2

ein Ausschnitt eines Reibgetriebes zweier Zylinder in vergrößerter Ansicht;

Fig. 3

eine schematische Darstellung einer Neunzylinder-Druckeinheit mit paarweisem Antrieb;

Fig. 4

eine schematische Darstellung einer Neunzylinder-Druckeinheit mit Einzelantrieb;

Fig. 5

eine schematische Darstellung einer 10-Zylindersatellitendruckeinheit;

Fig. 6

eine Darstellung der Nippstelle.

Show it:

Fig. 1

a schematic representation of cooperating cylinder of a rotary printing machine;

Fig. 2

a detail of a friction gear of two cylinders in an enlarged view;

Fig. 3

a schematic representation of a nine-cylinder printing unit with paired drive;

Fig. 4

a schematic representation of a nine-cylinder single-drive printing unit;

Fig. 5

a schematic representation of a 10-cylinder satellite pressure unit;

Fig. 6

a representation of the Nippstelle.

A rotary printing press has a printing unit 01 with three cylinders 02, which cooperate with each other in pairs in a pressure-on position; 03; 04 on. The first cylinder 02 is z. B. designed as a forme cylinder 02 and has on its outwardly directed outer surface 06 an 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 or planographic printing directly in a lateral surface of the forme cylinder 02 itself, or on a on a base body 08 of a radius r08 of the forme cylinder 02 releasably arranged printing plate 09 (pressure plate, sleeve, cliché etc.) of a thickness d09, z. B. d09 = 0.25 to 0.33 mm, in particular 0.27 to 0.30 mm. In each of the two cases, the outer surface 06 having the printed image defines an effective radius r02 of the forme cylinder 02. The forme cylinder 02 and optionally one or more intermediate layers, not shown, are substantially incompressible, i. H. executed with a fixed radius r02.

The second cylinder 03, which is designed as a transfer cylinder 03, has at least one layer 11 with compressible and / or elastic properties in the region of its lateral surface on a substantially incompressible, inelastic cylinder core 12 of a radius r12 in the radial direction. The layer 11 is z. B. as a lift 11, in particular as a 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 lateral 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, be defined by the outer surface of the outermost intermediate layer 14. The intermediate layer (s) serves (serve) z. As the adaptation to different thicknesses d11 of blankets 11 and / or thicknesses of substrates. Is the layer 11 as having an incompressible Carrier layer bonded layer 11 carried out, for. B. as a layer of a metal blanket, as is the incompressibility of the radius r12 including the strength of the incompressible carrier layer, z. As the metal plate to understand.

Due to the elastic and / or compressible layer 11, the transfer cylinder 03 has an outer radius r03u in the unloaded state, i. H. in the pressure-off position, and an outer or effective radius r03b in the loaded state, d. H. in pressure-on position of the paired together cylinder 02; 03; 04, up. As "radius in the loaded state", or effective radius, here is generally the distance of the axis of rotation R02; R03; R04 of the relevant cylinder 02; 03; 04 from the considered Nippstelle in the connection plane of the rotation axes R02; R03; R04 to understand. In this case, it may be necessary to distinguish between the radius r03b1 in the loaded state in the region of the nip point 16 to the forme cylinder 02 (FIG. 2) and the radius r03b2 in the loaded state in the region of the nip point 17 to the further cylinder 04. In Fig. 2, the reference numerals for the nip 17 between transfer cylinder 03 and the third cylinder 04 are listed in parentheses. This nip 17 at the same time a printing point 17 for a web to be printed 18 (dashed lines), z. B. paper web 18, is.

With the Überertiagungszylinder 03 a pressure point 17 forming, effective as a counter-pressure cylinder 04 cylinder 04 can be carried out either as a transfer cylinder of a second cylinder pair or as no printing ink leading cylinder 04, to which one or more transfer cylinder 03 can be adjusted via a web, not shown.

In the illustrated embodiment, the impression cylinder 04 is designed as no printing ink leading cylinder 04, which is substantially incompressible, ie executed with a fixed outer radius r04. This radius r04 can optionally not shown, applied to a cylinder body incompressible layers with contain and then in pressure-on position an effective radius r04 (eg also to the Nipppstelle out) is.

The forming in pressure-on position a friction gear forming and transfer cylinder 02; 03 are dimensioned in such an advantageous embodiment and / or hired against each other, that the forme cylinder 02 in the loaded state, a larger radius r02, z. B. at least 0.2 percent greater than the radius r03b1 of the transfer cylinder 03 in the nip 16. A ratio of the radius r02 of the forme cylinder 02 to the radius r03b1 of the transfer cylinder 03 in the loaded state, d. H. in pressure-on position is z. From 1.0015 to 1.0030, preferably from 1.0020 to 1.0025. The ratio of the radius r02 of the forme cylinder 02 to the radius r03u of the transfer cylinder 03 in the unloaded state can in this case z. B. between 1.0000 and 1.0015, especially 1.0010 and 1.0015.

A thickness d11 of the relieved layer 11 is in the unloaded but already used in printing mode (i.e., not unused) e.g. B. between 1.5 to 2.5 mm, in particular between 1.8 and 2.1 mm. The radius r12 of the cylinder core 12 is corresponding to o. G. To carry out relationships. Here u.U. an intermediate layer 14 of e.g. a thickness of 0.14 to 0.22 mm to be considered when the radius r13 of the body 13 is dimensioned.

In the case of a printing unit 01 with cylinders 02; 03 double circumference, ie with a circumference, which essentially two consecutively arranged stationary printed pages, especially newspaper pages, corresponds to the radius r02 of the forme cylinder 02 z. B. between 140 to 190 mm, in particular between 155 and 180 mm. The transfer cylinder 03 now has, in the pressure on position (loaded state), a radius r03b1 which is smaller by 0.14 to 0.20 mm, in particular by 0.16 to 0.18 mm, than the radius r02 of the forme cylinder 02 This is determined by the fixed radius r02 of the incompressible forme cylinder 02 and the relative position of Rotation axes R02; R03 is the cylinder 02; 03 set to each other in the pressure-on position, but at the same time a maximum radius r12 of the incompressible cylinder core 12 and a minimum thickness d11 of the layer 11 is taken into account. In an advantageous embodiment, the thickness d11 is selected so that in the unloaded state an excess T03a of about 0.13 to 0.21 mm, in particular about 0.16 to 0.18 mm compared to the loaded state, ie that at Employment the layer 11 is pressed by the forme cylinder 02 by the said measure (corresponds to the Eindrücktiefe). If a not yet used blanket 11 is used, then the transfer cylinder 03 has first one by an incidence thickness F (dashed lines in Fig. 1), z. B 0.02 to 0.05 mm, increased radius r03u in the unloaded state and a correspondingly increased oversize T03a.

An Anstelllage is, for example, by one or more attacks, set such that the two cylinders 02; 03 in its positioning position in the region of the nip 16 (connection plane of the axes of rotation R02; R03) the o. Have radii ratio and in an advantageous development, a ratio between excess T03a and the thickness d11 of the layer 11 in the unloaded (sunken) state is between 5% and 15%.

The in pressure-on position a friction gear forming transmission and impression cylinder 03; 04 are dimensioned in such an advantageous embodiment and / or hired against each other that the forme cylinder 02 and a larger radius r02, z. B. at least 0.1 percent greater than the radius r04 of the impression cylinder 04. A ratio of the radius r02 of the forme cylinder 02 to the radius r04 of the impression cylinder 04 is preferably from 1.0001 to 1.0002.

In the case of the above-mentioned printing unit 01 with cylinders 02; 03 twice the circumference, the impression cylinder 04 has a radius r04, which is smaller by 0.02 to 0.10 mm, in particular by 0.04 to 0.06 mm than the radius r02 of the forme cylinder 02nd

Between the axes of rotation R03; R04 of transfer cylinder 03 and incompressible impression cylinder 04 is a distance in the manner selected for the print-on position that a ratio of the radius r04 of the impression cylinder 04 to the radius r03b2 of the transfer cylinder 03 in the loaded state z. B. between 1.001 and 1.003. This is due to the fixed radius r04 of the incompressible impression cylinder 04 and the relative position of the axes of rotation R04; R03 of the cylinder 04; 03 set to each other in the pressure-on position, but at the same time a maximum radius r04 of the incompressible cylinder 04 and a minimum thickness d11 of the layer 11 is 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, relative to the loaded state, ie. H. that during employment, the layer 11 is pressed by the impression cylinder 04 to the said extent. If a not yet used blanket 11 is used, then the transfer cylinder 03 as o. G. first one to the incidence strength F (dashed line in Fig. 1), z. B. 0.02 to 0.05 mm, increased radius r03u in the unloaded state and a correspondingly increased excess T03b on.

An Anstelllage is, for example, by one or more attacks, set such that the two cylinders 03; 04 in its positioning position in the region of the nip point 17 (connection plane of the rotational axes R03, R04) the above-mentioned. Have radii ratio and in an advantageous development, a ratio between excess or depression depth T03b and the thickness d11 of the layer 11 in the unloaded (sunken) state is between 5% and 15%.

The conditions mentioned can in a first embodiment for Nosy-ringless cylinder 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 conjunction with the above-mentioned embodiments of the friction gear between the cylinders 02; 03; 04 can in the second embodiment, the bearer rings 21; 22; 23 all have a same radius r21; r22; r23. The radii ratios between each 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 allow specific rolling behavior, for the bearer rings 21; 22; 23 friction-reducing measures, eg. As a reinforced lubrication be provided. The bearer rings 21; 22; 23 but could also be rotatable with the respective cylinder 02; 03; 04, so that a relative rotation of bearer ring 21; 22; 23 and associated cylinder 02; 03; 04 is possible.

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

Thus, in an advantageous embodiment, the bearer ring 21 of the forme cylinder 02 has a radius r21 such that the ratio between the radius r02 of the forme cylinder 02 (surface 06) and that of the bearer ring r21 is from 1.0007 to 1.0015, greater than 1, 0009 to and including 1.0013. For a cylinder 02 twice the circumference is a supernatant Ü02 of the surface 06 relative to the bearer ring 21 of 0.10 to 0.23 mm, in particular from 0.15 to 0.19 mm. At a thickness d09 of the printing forme 09 of z. B. 0.25 to 0.33 mm this is to be considered in dimensioning of the body 08 with an undercut u02 relative to the bearer ring 21 accordingly. The undercut u02 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 double circumference cylinder 04, a protrusion U04 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 r03b1 in pressure on position of the transfer cylinder 03 and that of the bearer ring r22 to 0.9978 to 0.9996, in particular from 0 , 9984-0,9990. For a double-circumference cylinder 03, an overhang Ü22 of the bearer ring 22 to the effective radius r03b1 is from 0.13 to 0.22 mm, in particular from 0.15 to 0.20 mm. At a thickness d11b of the layer 11 in the loaded state of z. B. 1.3 to 2.30 mm this is in dimensioning of the cylinder core 12 (base body 13 and possibly intermediate layer (s) 14) with an undercut u03 relative to the bearer ring 22 to be considered accordingly. The undercut u03 is for example between 1.6 and 2.6 mm.

In particular, in order to ensure the condition of the ratio of the radii r22 and r03b in Anstelllage, are the radii r21; r22; r23 bearer rings 21; 22; 23 with respect to each other in specific, subsequently executed ratios:

The bearer rings 21 and 23 of form and impression cylinder 02; 04 have z. For example, the same radius r21; r23, the ratio is thus 1.000. The ratio of the radii r21; However, r22 of the forme cylinder 02 associated bearer ring 21 to that of the transfer cylinder 03 is in the range of 1.0010 to 1.0020, in particular in the range of 1.0010 to 1.0016. For cylinder 02; 03 twice the circumference of the radius r21, for example, by 0.01 to 0.03 mm, in particular about 0.020 ± 0.005 mm, ie 0.015 to 0.025 mm larger than that of the transfer cylinder 03. The said applies accordingly also for the ratio between the radii r23 of the impression cylinder 04 associated bearer ring 23 to that of the transfer cylinder. The said ratios and dimensions for the radii lead to differences in diameter of 0.02 to 0.06 mm and are therefore distinctively different from the difference due to today's usual manufacturing tolerance of only about 0.004 mm. The stated values are therefore to be realized in a targeted manner and are not based on randomness during production.

In a fourth embodiment, the friction gear in Anstelllage each pairwise a gear ratio or radius ratio of 1.000, wherein only the friction gear between two pairwise acting bearer rings 21; 22; 23 have the above, of 1,000 different radii ratios and gear ratios.

Of particular advantage are the embodiments described in connection with printing units whose cylinders 02, 03, 04 or printing units 01 are driven individually, in pairs or in groups. In particular, this is advantageous in view of undesirable power shifts between the printing units 01 for the case shown in FIG. 3, when several transfer cylinders 03 of several printing couples 01 cooperate with a common impression cylinder 04 designed as a satellite cylinder 04. Fig. 3 shows a running as a nine-cylinder printing unit 24 printing unit 24, in which the satellite cylinder 04 four pairs of forming and transfer cylinders 02, 03 are assigned.

In a non-illustrated embodiment, for example, two adjacent pairs 02, 03 are driven together as a drive assembly by a drive motor 26. The satellite cylinder 04 can be driven by one of the two drive assemblies or else by its own, third drive motor 26.

In the embodiment shown in Figure 3, the cylinders 02, 03; 04 of the nine-cylinder printing unit 24 rotatably driven by five drive motors 26. Each pair 02, 03 and the counter-pressure cylinder 04 designed as a satellite cylinder 04 has its own, at least speed-controlled, drive motor 26 that is mechanically independent of the other drive motors 26. The drive assemblies formed from this have, apart from the above-described friction gears, no mechanical coupling to each other. In one variant, the satellite cylinder 04 is driven simultaneously by two drive motors 26, wherein each one of these two drive motors 26 are fed together with the drive motors 26 of two pairs by a common power supply unit. This allows the symmetrical design of the supply by means of two power supplies for the rotary drives of the nine-cylinder printing unit 24th

The drive motors 26 are z. 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 wave", d. H. Elements for electronically synchronizing the drive motors 26. In a preferred embodiment, the drive motors 26, at least those of the pairs, are designed as drive motors 26 which are controllable with respect to their rotational angle position and are given default values with respect to their rotational angle position by the control and / or computing device 27.

In an embodiment shown in Figure 4, each of the cylinder 02; 03; 04 own, mechanically from other cylinders 02; 03; 04 independent drive motor 26 on. For the execution of the drive motors 26, the control and / or computing device 27, a possibly second drive motor 26 for the satellite cylinder 04 and the supply by means of two power supplies is analogously o.g. 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, then the two satellite cylinders 04 can each be embedded in a drive network of two pairs, one or two common (s). own drive motor (s) 26 have, or in each case by a separate drive motor 26, as shown, be driven mechanically independently. For the pairs, the above pairwise (shown) or a single drive of the cylinder 02 is again; 03; 04 (as in Fig. 4) is provided.

The individually or in pairs driven cylinder 02; 03; 04 are for example directly or indirectly, for example via a not shown gear, z. As a gear, timing belt or a friction gear, driven.

In one embodiment, at least transfer and impression cylinders 03; 04 z. B. a circumference between 850 and 1300 mm, in particular from 940 to 1200 mm. The forme cylinder 02 here also has this circumference (for accommodating, for example, four juxtaposed stationary printed pages, in particular newspaper pages). The length of the usable bale of the cylinder 02; 03; 04 is z. B. 1100 to 1800 mm, in particular 1400 to 1700 mm.

However, the aforementioned embodiments can also on cylinder 02; 03; 04 simple scope, or for example with a forming and / or transfer cylinder 02; 03 simple and a counter-pressure cylinder 04 with double the circumference be applied. The width of the cylinder 02; 03; 04 can be single, double, triple or quadruple.

Of advantage in view of the ehedem high drive performance, the described embodiments are also in connection with particularly wide, z. B. 1,850 to 2,400 wide, and strong, z. B. double circumference, cylinders 02; 03; 04. The scope is to accommodate two stationary pages, z. B. newspaper pages in broadsheet format, by means of two in the circumferential direction of the forme cylinder 02 successively fixable elevators, z. B. flexible printing forms formed. In the axial direction of the forme cylinder 02 for receiving z. B. at least six juxtaposed standing printed pages, especially newspaper pages in broadsheet format, measured. Among other things, it depends on the nature of the product to be produced, whether in each case only one pressure side or several pressure sides in the axial direction are arranged side by side on a printing plate. The transfer cylinder 03 is in the longitudinal direction next to each other z. B. with three elevators 11, z. B. Gummitüchem 11, occupied. They extend in the circumferential direction in essential to the full extent. The blankets 11 are z. B., the vibration behavior of the printing unit 01 in the operating case favorably influencing, alternating, z. B. by 180 °, offset from one another.

A ratio of a length of the usable bale of the cylinders 02; 03; 04 to the 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 here is the width or length of the bale to understand, which is suitable for receiving elevators. This corresponds approximately to a maximum possible web width of a web to be printed. This does not take account of existing bearer rings, operating areas or grooves in the area of the lateral surface close to the face.

LIST OF REFERENCE NUMBERS

01

printing unit

02

Cylinder, forme cylinder

03

Cylinder, transfer cylinder

04

Cylinder, impression cylinder, satellite cylinder

05

-

06

surface

07

-

08

body

09

printing form

10

-

11

Layer, elevator, blanket

12

cylinder core

13

body

14

Liner, beam

15

-

16

nip point

17

Nip point, pressure point

18

Railway, paper web

19

-

20

-

21

Schmitz ring

22

Schmitz ring

23

Schmitzring, 9-cylinder satellite pressure unit

24

Printing unit, nine-cylinder printing unit

25

-

26

drive motor

27

Control and / or computing device

28

Ten-cylinder printing unit

d09

Thickness (09)

d11

Thickness (11)

D11B

Thickness (11), loaded

F

incident intensity

r02

Radius (02)

R03B

Radius (03), loaded

r03b1

Radius (03), loaded

r03b2

Radius (03), loaded

r03u

Radius (03), unloaded

r04

Radius (04)

r08

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

Supernatant (02, 21)

Ü04

Supernatant (04, 23)

Ü22

Supernatant (22, 03)

u02

Undercut (02)

u03

Undercut (03)

Claims (27)

1. A printing unit (24; 28) of a rotary printing press with a first cylinder (02; 04) which with a second cylinder (03) having a compressible surface forms a nipping point in a printing-on setting, wherein the two cylinders (02; 03; 04) have bearer rings (21; 22; 23) which co-operate in the printing-on setting, and a radius (r21; r23) of a bearer ring (21; 23) associated with the first cylinder (02; 04) is larger than a radius (r22) of a bearer ring (22) associated with the second cylinder (03), characterized in that an effective radius (r02; r04) of the first cylinder (02; 04) in the region of its body is larger than the radius (r21; r23) of its bearer ring (21; 23).
2. A printing unit (24; 28) according to Claim 1, characterized in that the first cylinder (04) is constructed in the form of a counter-impression cylinder (04).
3. A printing unit (24; 28) according to Claim 1, characterized in that the first cylinder (04) is constructed in the form of a forme cylinder (02).
4. A printing unit (24; 28) according to Claim 1, characterized in that the second cylinder (03) is constructed in the form of a transfer cylinder (03) carrying a compressible layer (11).
5. A printing unit (24; 28) according to Claims 2 and 4, characterized in that the transfer cylinder (03) co-operates in a printing-on setting with a forme cylinder (02).
6. A printing unit (24; 28) according to Claim 1, characterized in that the second cylinder (03) is constructed in the form of a forme cylinder carrying a compressible printing forme (09).
7. A printing unit (24; 28) according to Claim 3 or 5, characterized in that in the printing-on setting in the region of the nipping point (16) a ratio of an effective radius (r02) of the forme cylinder (02) to an effective radius (r03b1) of the second cylinder (03) is in the range of from 1·0015 to 1·0030.
8. A printing unit (24; 28) according to Claim 5, characterized in that a radius (r21) of a bearer ring (21) associated with the forme cylinder (02) is larger than a radius (r22) of a co-operating bearer ring (22) associated with the second cylinder (03).
9. A printing unit (24; 28) according to Claims 3 and 4 or according to Claim 8, characterized in that the transfer cylinder (03) forms a printing point in a printing-on setting with a counter-impression cylinder (04) having a bearer ring (23).
10. A printing unit (24; 28) according to Claim 2 or 9, characterized in that a ratio of the radius (r04) of the counter-impression cylinder (04) to the radius (r23) of its bearer ring (23) is in the range of from 1 0004 to 1·0012.
11. A printing unit (24; 28) according to Claim 2 or 9, characterized in that a ratio of the radius (r04) of the counter-impression cylinder (04) to the radius (r23) of its bearer ring (23) is in the range of from 1.0006 to 1·0009.
12. A printing unit (24; 28) according to Claims 3 and 4 or according to Claim 9, characterized in that the radius (r23) of the bearer ring (23) associated with the counter-impression cylinder (04) is made from 0.01 to 0·03 mm larger than a radius (r22) of the bearer ring (22) associated with the transfer cylinder (03).
13. A printing unit (24; 28) according to Claim 2 or 9, characterized in that an effective radius (r04) of the counter-impression cylinder (04) in the region of its body is larger than a radius (r23) of its bearer ring (23).
14. A printing unit (24; 28) according to Claim 3, characterized in that a radius (r02) of the forme cylinder (02) in the region of its body is larger than a radius (r21) of its bearer ring (21).
15. A printing unit (24; 28) according to Claim 2 or 13, characterized in that the effective radius (r04) of the counter-impression cylinder (04) is larger by from 0·06 to 0.18 mm than the radius (r23) of its bearer ring (23).
16. A printing unit (24; 28) according to Claim 2 or 13, characterized in that the effective radius (r04) of the counter-impression cylinder (04) is larger by from 0·08 to 0·16 mm than the radius (r23) of its bearer ring (23).
17. A printing unit (24; 28) according to Claims 3 and 4, characterized in that the radius (r21) of the bearer ring (21) associated with the forme cylinder (02) is larger by from 0.015 to 0·25 mm than the radius (r22) of the bearer ring (22) associated with the transfer cylinder (03).
18. A printing unit (24; 28) according to Claim 5 or 9, characterized in that the bearer ring (21) associated with the forme cylinder (02) has a larger radius (r21) than that of the associated transfer cylinder (03), and the bearer ring (22) associated with the transfer cylinder (03) has a smaller radius (r22) than the bearer ring (23) of the counter-impression cylinder (04) associated with it.
19. A printing unit (14, 28) according to Claim 5 or 9, characterized in that in a printing-on setting the forme cylinder (02) has a larger radius (r02) in the region of its body than the associated transfer cylinder (03), and the transfer cylinder (03) has a smaller radius (r03b1; r03b2) in the region of its body than the counter-impression cylinder (04) associated with it.
20. A printing unit according to Claim 2 or 9, characterized in that the counter-impression cylinder (04) is constructed in the form of a satellite cylinder (04) and is arranged so as to co-operate with a plurality of second cylinders (03) having a compressible surface.
21. A printing couple (01) according to Claim 1, 5, 9 or 20, characterized in that each of the cylinders (02; 03; 04) has associated with it a separate drive motor (26) mechanically independent of other cylinders (02; 03; 04).
22. A printing couple (01) according to Claim 4 and any one of Claims 3 or 5 or according to Claim 20, characterized in that the forme cylinder and the associated transfer cylinder (02; 03) have associated with them in pairs a separate drive motor (26) mechanically independent of other cylinders (02; 03; 04).
23. A printing couple (01) according to Claim 3, 9 or 20, characterized in that the counter-impression cylinder (04) has associated with it a separate drive motor (26) mechanically independent of other cylinders (02; 03; 04).
24. A printing unit (24) according to Claim 20, characterized in that it is constructed in the form of a nine-cylinder printing unit (24).
25. A printing unit (24) according to Claim 20, characterized in that it is constructed in the form of a ten-cylinder printing unit (28).
26. A printing unit (28) according to Claim 25, characterized in that two counter-impression cylinders (04) associated with the printing unit (28) are driven jointly by a drive motor (60) independently of other cylinders (02; 03; 04).
27. A printing unit (28) according to Claim 25, characterized in that two counter-impression cylinders (04) associated with the printing unit (28) are driven by separate drive motors (60) in each case independently of other cylinders (02; 03; 04).

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