EP1494873A2

EP1494873A2 - Blanket on a roller, arrangements of the roller relative to a second roller, and printing units of a printing machine equipped with the roller

Info

Publication number: EP1494873A2
Application number: EP03729822A
Authority: EP
Inventors: Ralf Christel; Oliver Frank Hahn; Karl Erich Albert Schaschek
Original assignee: Koenig and Bauer AG
Current assignee: Koenig and Bauer AG
Priority date: 2002-04-18
Filing date: 2003-04-09
Publication date: 2005-01-12
Anticipated expiration: 2023-04-09
Also published as: JP2005532188A; CN101367289B; CN100500451C; EP1669210A3; WO2003086774A3; DE10237205A1; DE50311034D1; EP1669211A2; CN101367289A; AU2003240388A1; US20050166775A1; ATE468972T1; WO2003086774A2; DE50311073D1; EP1661698A3; EP1661698B1; JP2008213492A; DE50310976D1; WO2003086774B1; DE10237205B4

Abstract

Blanket located on the outer surface of a roller, e.g. a printing unit roller, consists of an elastic and or compressible layer with a surface pressure that is defined by the degree of an impression. The layer is designed so that the dependency of the surface pressure on the impression force has a gradient of less than 700 Ncm -> 2> mm -> 1>. The invention also relates to a corresponding roller arrangement and printer mechanism.

Description

description

Elevator on a roller, arrangements of the roller to a second roller and printing units of a printing press with the roller

The invention relates to an elevator on a roller, arrangements of the roller to a second roller and printing units of a printing press with the roller according to the preamble of claims 1, 8, 10, 13 and 34.

From DE 691 07 317 T2 a printing blanket is known which consists of several layers and, in extreme cases, has a total thickness of 0.55 to 3.65 mm. The elastic modulus of layers of cellular rubber is between 0.2 to 50 MPa and 0.1 to 25 MPa. Due to the special structure of the printing blanket and the properties of the layers, a printing blanket is obtained which, when pressed together, does not tend to shift or protrude laterally.

DE 19 40 852 A1 discloses a printing blanket for offset printing, which has a total thickness of approximately 1.9 mm. A shear modulus as tension at 0.25 mm deformation is given in the case of a thickness of the printing blanket with approx. 4.6, 1.9 or 8.23 kg / cm ² . The aim here is to achieve a rapid regression after an indentation as well as a narrow thickness tolerance.

For the transfer of ink or other fluids between two rollers of a printing press, e.g. B. in the dyeing and / or dampening unit and in particular in the offset process between printing unit cylinders, regularly resorted to the material combination hard-soft. The surface pressure required for ink transfer is achieved by pressing in a resilient, e.g. B. elastomeric layer (soft elastomeric cover / elevator, rubber blanket, metal printing blanket, sleeve) on an interacting roller with largely incompressible and non-elastic outer surface. An important criterion for the even transition of the fluid is a setting force specified in narrow areas and its constancy. Now occur fluctuations in the distance between the rollers acting together, for. B. caused by unbalance or by disturbances in the rolling of the rollers on vibrations, changes the contact force (surface pressure) and thus the transmission behavior for the fluid. At points of interrupted or reduced contact, for example on the plate or blanket tensioning channel, the surface pressure is thus periodically reduced, for example, which results in vibration excitation of the printing cylinders. In the area of printing technology, this manifests itself through changes in the color intensity in the printed image. If, for example, the contact force has changed permanently due to external conditions (long-wave disturbance), there is a risk of a print product that is too pale or too intensely colored until it is corrected (waste). If the positioning force changes dynamically due to vibrations (short-wave disturbance), this manifests itself in the formation of visible stripes in the printed product.

The invention has for its object to provide an elevator for or on a roller, arrangements of this roller to a second roller and printing units of a printing press.

The object is achieved by the features of claims 1, 8, 10, 13 and 34, respectively.

The advantages that can be achieved with the invention consist in particular in that a lower sensitivity to changes or fluctuations in the contact force (surface pressure) is achieved, and thus a high quality of the printed product is easier to achieve and to maintain. The influence of the cylinder movements on the ink transfer can be reduced by means of special elevators, an optimized design of the cylinders and their arrangement. In a Particularly favorable embodiment with narrow points of interrupted or reduced contact, the vibration excitation itself is also reduced.

The transmission of the fluid is influenced considerably less by vibrations due to the design of the elevator and / or the arrangement of the rollers with respect to one another. The same applies z. B. also for disturbances induced by process changes (speed, changing material thickness of a web, turning on / off further rollers), for distance deviations due to inaccuracies in the delivery (stops, finite stiffness, manufacturing tolerances) as well as changes in elevator strength due to wear (long-wave) and / or incomplete regression after passing through the nip point (short-wave or long-wave).

This is achieved in particular in that the elevator is designed in such a way or the roller is carried out with a corresponding elevator that a dependency of the resulting surface pressure with a variation in the indentation is considerably flatter than usual. A spring characteristic curve, ie an increase in the dependence of the surface pressure on the indentation, is at least 700 (N / cm ² ) / mm, at least in an advantageous range for the indentation in the pressure-on position.

An advantageous range of a relative indentation of the elevator in the operating state (pressure-on position) lies e.g. B. between 5% and 10%. In particular, depending on the type of the two co-operating rollers, different areas for the relative indentation can be preferred in order to achieve optimal results with regard to the required transition of the fluid with the smallest possible influence of fluctuations.

The surface pressure varies in pressure-on position in an advantageous embodiment highest in a range between 60 and 220 N / cm ² , or different sub-ranges for fluids, eg. B. printing inks, with very different rheological properties and / or different printing processes. In these areas or sub-areas in particular, the curve should meet the slope condition.

The width of the contact zone in the nip resulting from the pressing of the rollers has hitherto been i. d. Usually kept as small as possible. A widened nip point brings with it a higher line force and thus a greater static deflection. However, this disadvantage is more than compensated for by the elevator or the arrangement according to the invention. A width of the nip is z. B. in an advantageous embodiment at least 10 mm, in particular greater than or equal to 12 mm. An advantageous surface pressure can thus be achieved.

In the event that an oscillation due to a disturbance, e.g. B. an interruption, induced on one of the lateral surfaces of the rollers acting directly or via a web, can also be reduced by the execution of the elevator and / or the arrangement of the rollers to each other, the excitation of this vibration or its amplitude. This applies in particular to an embodiment in which the width of the interruption in the circumferential direction is at most a ratio of 1: 3 to the width of the nip (impression strip) resulting from the pressing.

In general, the elevator or the layer allows the use of slimmer or longer printing cylinders, i. H. a large length of the cylinder compared to the diameter.

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

Show it:

Fig. 1 is a schematic representation of the line force between two rollers Using a conventional elevator;

Figure 2 is a schematic representation of the line force between two rollers using an elevator according to the invention.

3 measured surface pressure with variation of the press-in;

Fig. 4 embodiment for a printing unit;

Fig. 5 embodiment for a printing unit;

Fig. 6 embodiment for a printing unit;

Fig. 7 embodiment for a printing unit;

Fig. 8 Schematic representation of an elevator with a support layer.

A work machine, e.g. B. a printing press, has rolling rollers 01; 02 on which a nip 03, z. B. form a nip 03. In the case of the printing press rollers 01; 02 of an inking unit, a coating unit, or cylinder 01; 02 of a printing unit. In the embodiment shown in FIG. 1, the cylinders 01; 02 represents a forme cylinder 01 with an effective diameter D _w pz and a transfer cylinder 02 of an offset printing unit. One of the cylinders 01; 02, e.g. B. the transfer cylinder 02, has on the outer surface of a largely incompressible, non-elastic core 04 with a diameter D _G ZK an elevator 05 or coating 05 with a soft, elastomeric layer 06 of a thickness t. A total thickness T of the elevator 05 is z. B. from the thickness t of the layer 06 and a thickness of an optionally incompressible, inelastic carrier layer 10 connected to the layer 06, for example one Metal plate, (exemplarily shown in Fig. 8) together. If the elevator 05 does not have an additional carrier layer 10, the thickness t corresponds to the total thickness T. The layer 06 can be constructed as an inhomogeneous layer 06, which in total has the required property for the layer 06. Core 04 and elevator 05 or cover 05 together form an effective diameter D _W GZ of the transfer cylinder 02. The effective diameter D _{wPZ is} determined on the outer surface of the forme cylinder 01 which is effective for the unrolling and optionally includes one applied to the outer surface of a base body 07 Elevator 08, e.g. B. a printing form 08. The cylinder 01 hard surface can also be designed as a counter-pressure cylinder 01 cooperating with the transfer cylinder 02. The version of the layer 06 described below is however not related to the version of the rollers 01; 02 as transfer and form cylinder 01; 02 or tied to the version with a printing form 08.

Depending on the provision of the two cylinders 01; 02, d. H. the center distance A, "dips" the largely incompressible, non-elastic outer surface of the forme cylinder 01 into the soft layer 06 and causes an indentation S compared to the undisturbed course of the layer 06. Due to the restoring forces, a fluctuating or changing indentation S usually leads to a fluctuating or changing surface pressure P in the nip 03 and causes the above problems in the quality of the ink transfer and ultimately in the printed product.

In Fig. 1, a profile for a surface pressure P in the nip of the two rollers 01 and 02 is shown schematically. The surface pressure P extends over the entire area of the contact zone, reaching a maximum surface pressure P _max when stationary at the level of a connecting plane V of the axes of rotation. During production, this shifts to the incoming gap side due to the viscous proportion of the force. When projected onto a plane E perpendicular to the connecting plane V, the contact zone and thus the profile have a width B. The maximum surface pressure P _max is ultimately responsible for the color transfer and adjust accordingly.

In comparison to FIG. 1, FIG. 2 shows schematically the profile of the surface pressure P in the case of a larger indentation S, which at the same time causes the width B to widen. If the maximum surface pressure P _ma χ is nevertheless to be achieved, the integration of the surface pressure P over the entire width B leads to an increase in a force between the two rollers 01; 02.

The absolute level of the surface pressure P in the nip 03 and its fluctuation when the indentation S is varied is largely determined by a spring characteristic of the layer 06 used or of the elevator 05 used with the layer 06. The spring characteristic curve represents the surface pressure P as a function of the indentation S. In FIG. 3 some spring characteristic curves of conventional elevators 05, in particular pressure levers 05 with a corresponding layer 06, are shown by way of example. The values are determined on a quasi-static stamp test bench in the laboratory. They are to be transferred in a suitable manner to values determined in another way.

It can be seen from FIG. 3 that a slope ΔP / ΔS of the spring characteristic curve determines the fluctuation in the surface pressure P when the indentation S changes (for example in the case of vibration). In the case of a variation ΔS in the indentation by an average indentation value S, the magnitude of a fluctuation ΔP in the required maximum surface pressure P _max in the nip 03 around the average surface pressure P is approximately proportional to the slope ΔP / ΔS of the spring characteristics at point S. For example, an elevator a (FIG. 3) a reduction in the indentation S from -0.16 mm to -0.14 mm to the surface pressure P by a reduction of approximately 50 N / cm ² , and a reduction in the indentation S of -0, 11 mm to -0.09 mm on the surface pressure P by reducing by approx. 25 N / cm ² . An elevator b has a lower gradient. Elevators 05, which as a whole or their layer 06 as such has a large slope ΔP / ΔS, in particular in the area of the required maximum surface pressure P _max in the pressure-relevant area, are hereinafter referred to as “hard”, those with a small slope ΔP / ΔS referred to as "soft".

Elevator 05 or layer 06 is now designed as a "soft" elevator 05 or "soft" layer 06. Compared to a "hard" elevator 05 or a hard layer 06, the same relative movements of the rollers 01; 02 (or change in the distance A) thus leads to a smaller change in the surface pressure P in a soft elevator 05 and thus to a reduction in the fluctuations The soft elevator 05 thus brings about a lower sensitivity of the printing process to vibrations and / or deviations at intervals from a setpoint value, because of smaller changes in the surface pressure P due to relative movements of the rollers 01, 02, for example, there are oscillation strips in the printed product in the case of soft elevators 05 or with elevators 05 with a soft layer 06 only visible with larger vibration amplitudes.

In an advantageous embodiment, the surface pressure varies in the pressure-on position at most in a range between 60 and 220 N / cm ² . For fluids, e.g. As printing inks, with very different rheological properties, different areas within the above range can be preferred for surface pressure. For example, the range for wet offset (ink and dampening solution) varies. B. between 60 and 120 N / cm ² , in particular from 80 to 100 N / cm ² , while in the case of dry offset (no fountain solution, only ink application on the forme cylinder) z. B. between 100 and 220 N / cm ² , in particular 120 to 180 N / cm ² . In these areas in particular, the slope should meet the condition of the slope.

The pressure-relevant range for the surface pressure P _max is advantageously between 60 to 220 N / cm ² . For fluids, e.g. B. printing inks, with very different rheological properties, different areas within the above range for Surface pressure may be preferred. For example, the range for wet offset varies. B. between 60 and 120 N / cm ² , in particular from 80 to 100 N / cm ² (shown shaded in Fig. 3), while for the case of dry offset z. B. varies between 100 and 220 N / cm ² , in particular from 120 to 180 N / cm ² . In an advantageous embodiment, a soft elevator 05 (or its layer 06) has an inclination ΔP / ΔS of z. At least in the range from 80 to 100 N / cm ² . B. ΔP / ΔS <700 (N / cm ² ) / mm, in particular ΔP / ΔS <500 (N / cm ² ) / mm. The slope .DELTA.P / .DELTA.S should be at least a factor two smaller for the surface pressure P in the relevant area than is currently customary for elevators 05 in offset printing.

In an advantageous embodiment, as indicated schematically in FIG. 2, the layer 06 has a greater thickness t and the elevator 05 has a greater overall thickness T than has been customary hitherto. The thickness t of the layer 06 which is functional with regard to the elasticity or compressibility is, for example, 3.0 to 6.3 mm, in particular 3.7 to 5.7 mm. In addition, the strength of one or more u. U. connected to the layer 06, essentially incompressible and inelastic layers on the side facing the core 04, which are connected to the layer 06 for the purpose of dimensional and / or dimensional stability (not shown). This carrier layer 10 or carrier layers 10, which is effective not for the “softness” of the elevator, but for the dimensional stability, can also be arranged between the “soft” layers. For example, as a metal, in particular stainless steel sheet, it can be approximately 0.1 to 0.3 mm thick. Depending on the design of the elevator 05, the fabric can be 0.1 to 0.6 mm thick. In the case of several layers of layers 06, the indicated thickness t of layer 06 relates to the sum of the “partial layers” that are functionally responsible for the above-described characteristic (dependence on surface pressure / indentation) and the elasticity or compressibility Carrier layer (s) 10 the total thickness T of 3.5 to 6.5 mm, in particular 3.9 to 5.9 mm. The "soft" elevator 05 (or layer 06) is preferably operated with a higher indentation S compared to conventional indentations S (shown schematically in FIG. 2 compared to FIG. 1), ie the two rollers 01, 02 are covered on their respective effective but undisturbed diameter D _wG z, D _wPZ further _adjusted to one another, _{thereby achieving} an optimal maximum surface pressure P _max despite a smaller pitch ΔP / ΔS. The rollers 01, 02 are advantageously positioned against each other in such a way that the Indentation S amounts to at least 0.18 mm, for example 0.18 to 0.60 mm, in particular 0.25 to 0.50 mm.

A relative indentation S *, i.e. H. the indentation S related to the thickness t of layer 06 lies e.g. B. without taking into account the special design of the rollers 01; 02 z. B. between 5% and 10%, but in particular between 6% and 8%.

A width B of the contact zone resulting from indentation S of the layer 06 in a projection perpendicular to a connection plane V of its axes of rotation is in an advantageous embodiment at least 5% of the undisturbed effective diameter D _{WGZ of} the roller 02 with layer 06.

As described above, the design and / or arrangement of the "soft" elevator 05 is particularly advantageous if one of the two co-operating rollers 01; 02 (or both) has at least one disturbance 09; 11 influencing the unwinding on its effective outer surface. This disturbance 09; 11 can be an interruption 09; 11, an axially extending joint 09; 11 of two ends of one or more elevators 05; 08. In particular, however, the disturbance 09; 11 can be caused by an axially extending channel 09; 11 for fastening ends of one or several elevators 05; 08. This channel 09; 11 has an opening through which the ends are guided towards the lateral surface. Inside the channel 09; 11 can be a device for clamping and / or tensioning the elevator 05; 08 or the elevators 05; 08. When rolling over the channel 09; 11 or the channels 09; 11 vibrations are excited. Is a width B09; B11 of channel 09; 11 seen in the circumferential direction larger than the width B of the contact zone, so when the passage 09; 11 excited a vibration with increased amplitude, because due to the above-mentioned larger width B of the contact zone, a greater line force between the two rollers 01; 02 works. Nevertheless, the increase in vibration amplitudes due to the higher line force is less than the decrease in vibration sensitivity due to the softness of layer 06, so that there is an overall reduction in sensitivity to vibrations.

It is particularly advantageous to change the width B09; B11 of channel 09; 11 to be chosen smaller than the width B of the contact zone. In this case, at least areas of the cooperating lateral surfaces in the contact zone are always supported on one another, in addition there is a weakening in height and a flatter course (broadening of the impulse) for the force of the stroke excitation. Softer lifts 05 or softer layers 06 thus lead to a weakening and a lengthening of the channel run in the case of narrow channels 09 11.

In the case of the transfer cylinder 02, ends of a metal printing blanket can be arranged in the channel 11. Layer 06 is in this case on a dimensionally stable support, e.g. B. a thin metal plate (a sheet), the bent ends of which are arranged in the channel 11. The channel 11 can then be extremely narrow in the circumferential direction, for. B. less than or equal to 5 mm, in particular less than or equal to 3 mm. Also in the case of the forme cylinder 01, the channel 09 is designed in an advantageous embodiment with a width in the circumferential direction of less than or equal to 5 mm, in particular less than or equal to 3 mm.

Conversely, the larger contact zone (width of the imprint strip) compared to conventional positions reduces the permissible ratio B09: B or B11: B. An embodiment is particularly advantageous, the width B09; B11 of channel 09; 11 in the area of its opening or mouth to the outer surface of the core 04 or base body 07 in the circumferential direction at most in a ratio of 1: 3 to the width B of the contact zone (impression strip) created by the pressing.

The soft layer 06 preferably has a reduced damping constant compared to the materials normally used, so that despite the higher loading and unloading speeds occurring due to the higher indentation S when rolling, no higher flexing heat is generated. Likewise, the layer 06 must be designed in such a way that a sufficiently rapid regression or resilience takes place after it has passed through the nip 03 into the initial position, so that, for example, the initial thickness is again present when it comes into contact with an ink roller or another cylinder.

4 and 5 show a printing unit 12 configured in an advantageous manner with the layer 06 and designed as a so-called double printing unit 12. The transfer cylinder 02 of a first pair of cylinders 01; 02 acts on a substrate 13, z. B. a web 13 together with a counter-pressure cylinder 14 also designed as a transfer cylinder 14, which is also associated with a forme cylinder 16. All four cylinders 01; 02; 14; 16 are driven mechanically independently of one another by means of different drive motors 17 (FIG. 4). In a modification, forme and transfer cylinders 01; 02; 14; 16 each coupled in pairs by a paired drive motor 17 (on the forme cylinder 01; 16, on the transfer cylinder 02; 14 or in parallel) (FIG. 5).

The forme cylinder 01; 16 and the transfer cylinder 02; 14 are in a first embodiment as cylinder 01; 02; 14; 16 double the scope, ie with a scope of essentially two standing printed pages, in particular of two newspaper pages. They have effective diameters D _wG z; D _wPZ between 260 to 400 mm, executed in particular 280 to 350 mm. On the outer surface of the core 04, the transfer cylinder 02; 14 each have at least one elevator 05 with a total thickness T of 3.5 to 6.5 mm, in particular 3.9 to 5.9 mm. The slope ΔP / ΔS of the spring characteristic is at least in the pressure-relevant range (see above) below 700 (Ncm ² /) mm, in particular below 500 (Ncm ² /) mm. Forme and transfer cylinder 01; 02; 14; 16 are arranged in pairs in such a way that the width B of the contact zone between the forme and transfer cylinder 01; 02; 14; 16 in the working position is 14 to 25 mm, in particular 17 to 21 mm. This configuration largely minimizes sensitivity to vibrations and inexact placement. The individual drives by the drive motor 17 support this through the mechanical decoupling.

In a second embodiment, not shown, the forme cylinders 01; 16 and the transfer cylinder 02; 14 as cylinder 01; 02; 14; 16 simple scope, ie with a scope of essentially a standing print page, in particular from a newspaper page. They have effective diameters D _wG z; D _{wPZ executed} between 150 to 190 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 each have at least one elevator 05 with a total thickness T of 3.5 to 6.5 mm, in particular 3.9 to 5.9 mm. The slope ΔP / ΔS of the spring characteristic is again at least in the pressure-relevant range (see above) below 700 (Ncm ² /) mm, in particular below 500 (Ncm ² /) mm. Forme and transfer cylinder 01; 02; 14; 16 are arranged in pairs in such a way that the width B of the contact zone between the forme and transfer cylinder 01; 02; 14; 16 in the position 10 to 18 mm, in particular 12 to 15 mm.

In a third embodiment, not shown, the forme cylinders 01; 16 as cylinder 01; 16 simple circumference with effective diameters D _wPZ between 150 to 190 mm, and the transfer _cylinder 02; 14 as cylinder 02; 14 double circumference with effective diameters D _W GZ between 260 to 400 mm, in particular 280 to 350 mm. On the outer surface of the core 04, the transfer cylinder 02; 14 in each case at least one elevator 05 with a total thickness T of 3.5 to 6.5 mm, in particular from 3.9 to 5.9 mm. The slope ΔP / ΔS of the spring characteristic is again at least in the pressure-relevant range (see above) below 700 (Ncm ² /) mm, in particular below 500 (Ncm ² /) mm. Forme and transfer cylinder 01; 02; 14; 16 are arranged in pairs in such a way that the width B of the contact zone between the forme and transfer cylinder 01; 02; 14; 16 in employment 12 to 20 mm, in particular 15 to 19 mm.

6 and 7, a printing unit 19 is shown, which is either part of a larger printing unit, such as. B. a five-cylinder, nine-cylinder or ten-cylinder printing unit, or is operable as a three-cylinder printing unit 19. The transfer cylinder 02 acts here with a cylinder 18 not leading an ink, e.g. B. an impression cylinder 18 such as in particular a satellite cylinder 18 together. The "soft" outer surface of the transfer cylinder 02 now interacts with the "hard" outer surface of the forme cylinder 01 on one side and with the "hard" outer surface of the satellite cylinder 18 on the other side. In one embodiment (FIG. 6) at least independently of the transmission cylinder 02 and the satellite cylinder 18, the one or more satellite cylinders 18 have their own drive motor 17, while the pair of form and transmission cylinders 01; 02 is mechanically coupled by a common drive motor (FIG. 6), or in each case by its own Drive motor 17 are driven mechanically independently of one another (FIG. 7).

Forme cylinder 01, transfer cylinder 02 and satellite cylinder 18 are in a first embodiment for FIG. 6 or 7 as cylinder 01; 02; 18 double circumference with effective diameters D _WGZ ; D _wPZ ; D ^ z between 260 to 400 mm, in particular 280 to 350 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 each have at least one elevator 05 with a total thickness T of 3.5 to 6.5 mm, in particular 3.9 to 5.9 mm. The slope ΔP / ΔS of the spring characteristic is below 700 (Ncm ² /) mm at least in the pressure-relevant range (see above), especially less than 500 (Ncm ² /) mm. Forme and transfer cylinder 01; 02 and transfer cylinder 02; and satellite cylinders 18 are in each case positioned in pairs in such a way that the width B of the contact zone in the position of contact is in each case 14 to 25 mm, in particular 17 to 21 mm.

In a second embodiment for FIG. 6 or 7, forme cylinder 01, transfer cylinder 02 and satellite cylinder 18 are cylinders 01; 02; 18 simple scope, ie with a scope of essentially a standing print page, in particular from a newspaper page. They have effective diameters D _WG Z; D _wPZ ; D _wSZ between 120 to 180 mm, in particular 130 to 170 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 each have at least one elevator 05 with a total thickness T of 3.5 to 6.5 mm, in particular 3.9 to 5.9 mm. The slope ΔP / ΔS of the spring characteristic is at least in the pressure-relevant range (see above) again below 700 (Ncm ² /) mm, in particular below 500 (Ncn 7) mm. Forme and transfer cylinder 01; 02 and transfer cylinder 02; and the satellite cylinders 18 are each positioned in pairs in such a way that the width B of the contact zone in the position of contact is 10 to 18 mm, in particular 12 to 15 mm.

In addition, the changes implied by the greater softness (greater indentation S, changed handling behavior, greater strength t or T) must be taken into account when designing the printing press. A printing press that works with soft and stronger elevators 05 or layers 06 thus has, for. B. changed, in particular enlarged cylinder undercuts (development, fabric thickness) and changed gap dimensions when switching on or off (fabric thickness, indentation). This also requires larger cylinder adjustment paths for the pressure-down position (greater indentation).

The aforementioned elevator 05 or layer 06 is e.g. B. in a printing unit with one or more long but slim cylinders 01; 02; 14; 16 arranged. For example, the forme cylinder 01; 16 and the transfer cylinder 02; 14 z. B. in the area of their bales each have a length that four or more widths of a printed page, for. B. a newspaper page, e.g. B. corresponds to 1,100 to 1,800 mm, in particular 1,500 to 1,700 mm. The diameter D _WGZ ; D _wPZ at least of the _forme cylinder 01; 16 is z. B. 145 to 190 mm, in particular 150 to 185 mm, which corresponds essentially to the length of a newspaper page ("simple scope"). The device is also advantageous for other dimensions in which the ratio between the diameter and length of the cylinder 01, 02; 14; 16; 18 is less than or equal to 0.16, in particular less than 0.12, or even less than or equal to 0.08.

In another version of the printing unit, the length of the bale of the form and transfer cylinders is 01; 02; 14; 16 z. B. 1,850 to 2,400 mm, in particular 1,900 to 2,300 mm and is in the axial direction for receiving z. B. dimensioned at least six adjacent printed pages in broadsheet format. The diameter of at least the forme cylinder 01; 16 lies in a variant z. B. at 260 to 340 mm, especially at 280 to 300 mm, and in another variant z. B. at 290 to 380 mm, in particular at 300 to 370 mm, which corresponds to the circumference essentially two lengths of a newspaper page ("double circumference"). A ratio of the diameter D _wG z; D _wPZ at least of the _forme cylinder 01; 16 to its length is 0.11 to 0.17, in particular 0.13 to 0.16.

LIST OF REFERENCE NUMBERS

01 roller, cylinder, forme cylinder, impression cylinder

02 roller, cylinder, transfer cylinder

03 nip, rocking point

04 core

05 Elevator, cover, printing blanket

06 shift

07 basic body

08 elevator, printing form

09 fault, channel

10 carrier layer

11 Malfunction, channel

12 printing unit, double printing unit

13 printing material, web

14 roller, cylinder, transfer cylinder, impression cylinder

15 -

16 roller, cylinder, forme cylinder

17 drive motor

18 roller, cylinder, impression cylinder, satellite cylinder

19 printing unit, three-cylinder printing unit

a elevator

A center distance b elevator

B width, contact zone

B09 width

B11 width

D _W Q _Z diameter D _w pz diameter

Dwsz diameter

E level

P surface pressure

"max surface pressure, maximum t thickness (06)

T total thickness (05)

S indentation s * indentation, relative

V connection level

Claims

Expectations

1. Elevator on a lateral surface of a roller (02; 14), which has an elastic and / or compressible layer (06) with a surface pressure (P) dependent on an indentation (S), characterized in that the layer (06) is a Dependence of the surface pressure (P) on the indentation (S), the slope (ΔP / ΔS) of which is at least in a working range less than 700 (N / cm ² ) / mm.

2. Elevator according to claim 1, characterized in that the slope (ΔP / ΔS) is less than 700 (N / cm ² ) / mm at least in the working area for the surface pressure of 100 N / cm ² .

3. Elevator according to claim 1, characterized in that the differential quotient (ΔP / ΔS) is at least in an area for the indentation of 0.22 to 0.38 mm less than 700 (N / cm ² ) / mm.

4. Elevator according to claim 1, characterized in that the layer (06) has a thickness (t) of at least 3.0 mm.

5. Elevator according to claim 1, characterized in that it is designed as a detachable elevator (05).

6. Elevator according to claim 5, characterized in that, in addition to the layer (06), it has a substantially dimensionally stable support layer 10 firmly connected to it.

7. Elevator according to claim 5 or 6, characterized in that it has a total thickness (T) of at least 3.5 mm.

8. Arrangement of two mutually associated rollers (01; 02), which form a roller gap (03) with one another in an engagement position, one of the rollers (02) having an elastic and / or compressible layer (06) in the region of its lateral surface and the other The roller (01) is essentially incompressible and non-elastic in the area of its lateral surface, characterized in that the two rollers (01; 02) are arranged relative to one another in the position of contact such that a relative indentation (S *) of the layer (06) occurs the essentially incompressible and non-elastic surface area in the nip (03) is at least 5% and at most 10%.

9. Arrangement according to claim 8, characterized in that the absolute indentation (S) is at least 0.18 mm.

10. Arrangement of two rollers (01; 02) assigned to one another, which form a roller gap (03) with one another in an engagement position, at least one of the rollers (02) having an elastic and / or compressible layer (06) in the region of its lateral surface, thereby characterized in that the two rollers (01; 02) are arranged relative to one another in the position of contact such that a width (B) of a contact zone between the two rollers (01; 02) resulting from indentation (S) of the layer (06) is perpendicular to one Connection plane (V) of their axes of rotation in the nip (03) is at least 5% of an undisturbed effective diameter (D _wG z) of the roller (02) with the layer (06).

11. The arrangement according to claim 10, characterized in that the contact zone has at least the width (B) of 10 mm.

12. The arrangement according to claim 8 or 10, characterized in that the layer (06) is designed as an elevator according to one or more of claims 1 to 7.

13. Printing unit with at least two rollers (01; 02; 14; 16; 18) acting together in the contact position, one of the rollers (01; 02; 14; 16; 18) being designed as a transfer cylinder (02; 14) which is in the area its outer surface has an elastic and / or compressible layer (06), characterized in that the transfer cylinder (02; 14) and the other roller (01; 16; 18) are arranged relative to one another in the position of engagement such that an indentation (S) the layer (06) is at least 0.18 mm due to an essentially incompressible and non-elastic outer surface of the other roller (01; 16; 18) in the roller gap (03).

14. Printing unit according to claim 13, characterized in that a contact zone between the two rollers (01; 02) resulting from indentation (S) of the layer (06) perpendicular to a connecting plane (V) of their axes of rotation in the roller gap (03) has at least one width (B) of 10 mm.

15. Printing unit according to claim 13, characterized in that the roller (01; 16) acting together with the transfer cylinder (02; 14) is designed as a forme cylinder (01; 16).

16. Printing unit according to claim 13, characterized in that with the transfer cylinder (02; 14) cooperating roller (18) is designed as a satellite cylinder (18).

17. Printing unit according to claim 13, characterized in that at least one of the two rollers (01; 02; 14; 16) has at least one disturbance (09; 11) influencing the unwinding on its lateral surface.

18. Printing unit according to claim 17, characterized in that the fault (09; 11) is caused by an opening of an axially extending channel (09; 11) for fastening ends of one or more elevators (05; 08).

19. Printing unit according to claim 14 and 18, characterized in that a width (B09; B11) of the channel (09; 11) in the region of its opening to the circumferential surface in the circumferential direction is at a ratio of 1: 3 to the width (B) of the contact zone.

20. Printing unit according to claim 18, characterized in that the width (B09; B11) of the channel (09; 11) in the region of its opening to the lateral surface in the circumferential direction is at most 5 mm.

21. Printing unit according to claim 15, characterized in that the forme and transfer cylinders (01; 02; 14; 16) are mechanically coupled by a common drive motor (17).

22. Printing unit according to claim 21, characterized in that the form and transfer cylinders (01; 02; 14; 16) as a pair of cylinders (01, 02; 14, 16) are mechanically independent of one or more further pairs of cylinders (01, 02; 14, 16) or a satellite cylinder (18) are driven.

23. Printing unit according to claim 15, characterized in that the forme and transfer cylinders (01; 02; 14; 16) are each mechanically driven independently of one another by their own drive motor (17).

24. Printing unit according to claim 16 or 22, characterized in that the satellite cylinder (18) has its own drive motor (17) which is mechanically independent of further cylinders (01; 02; 14; 16).

25. Printing unit according to claim 13, characterized in that at least the transfer cylinder (02; 14) is designed with a circumference of essentially two standing print pages in newspaper format.

26. Printing unit according to claim 25, characterized in that the rollers (01; 02; 14; 16; 18) each have a length in the region of their bale which corresponds to six widths of a printed page in newspaper format.

27. Printing unit according to claim 15, characterized in that at least the forme cylinder (01; 16) is designed with a circumference of essentially one standing printed page in newspaper format.

28. Printing unit according to claim 25 or 27, characterized in that the rollers (01; 02; 14; 16; 18) each have a length in the region of their bale which corresponds to four widths of a printed page in newspaper format.

29. Printing unit according to claim 15, characterized in that a ratio between the effective diameter and length of at least the forme cylinder (01; 16) is less than or equal to 0.16.

30. Printing unit according to claim 13, characterized in that the layer (06) is designed as an elevator according to one or more of claims 1 to 7.

31. Printing unit according to claim 30, characterized in that it is designed as a printing unit for wet offset, and the dependence of the surface pressure (P) on the indentation (S) is at least in the range from 80 to 100 N / cm ² an increase (ΔP / ΔS ) of less than 700 (N / cm ² ) / mm.

32. Printing unit according to claim 30, characterized in that it is designed as a printing unit for dry offset, and the dependency of the surface pressure (P) on the indentation (S) is at least in the range from 120 to 180 N / cm ² an increase (ΔP / ΔS ) of less than 700 (N / cm ² ) / mm.

33. Printing unit according to claim 13, characterized in that the two rollers (01; 02; 14; 16; 18) are arranged to each other in the position of employment according to the arrangement according to claim 10.

34. Printing unit with at least two rollers (01; 02; 14; 16; 18) acting together in the position of adjustment, wherein at least one of the rollers (01; 02; 14; 16; 18) has at least one opening of an axially extending channel in the area of its lateral surface (09; 11) for fastening at least one end of one or more elevators (05; 08) and one of the rollers (01; 02; 14; 16; 18) has an elastic and / or compressible layer (06) in the area of its outer surface, and wherein in contact position by indentation (S) of the layer (06) a contact zone between the two rollers (01; 02) is formed with a resulting width (B) perpendicular to a connecting plane (V) of their axes of rotation, characterized in that a width (B09; B11) of the channel (09; 11) in the area of its opening to the circumferential surface in the circumferential direction to the width (B) of the contact zone is at a ratio of 1: 3.